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2869015

Asymmetric corrugated fins with louvers

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

As per figure 1, a brazed air-fluid heat exchanger 10 comprises two parallel tanks 12 extending along a normal axis N, a plurality of longitudinal L flat tubes 14 extending between the tanks 12 and corrugated fins 16 arranged between the tubes 14. The fins 16 are made of a metal strip 18 fanfold so to form flat panels 20 substantially parallel to each other's, and only joining along the fold lines 22 brazed to the tubes 14. As visible on the figure, the heat exchanger 10 has a large front face 24 perpendicular to a transversal axis T. In operation, an air flow F crosses the heat exchanger 10 flowing between the fins 16 from the leading edge 26 to a trailing edge 28. As represented in figure 2, between the two edges 26, 28, the fins 16 have a leading portion 30 followed by a trailing portion 32. The leading portion 30 is provided with slit louvers 34 oriented to deviate and skew the air flow F of the transversal axis T and, the trailing portion 32 is provided with ribs 36 extending between the fold lines 22. A first embodiment is represented on figure 3 where the leading edge 26 is on the left of the figure. The leading portion 30 and the trailing portion 32 have equal transversal length, approximately half the width W of the strip 18. The louvers 34 are represented by a series of parallel skewed lines and the ribs 36, on the trailing portion 32, have trapezoidal profiles. In this first embodiment the ribs 36 are not slit and consequently the air flow that enters the trailing portion 32 remains between the same two fins until exiting by the trailing edge 28. While many alternatives can be made, it appears that a good dimensional compromise resides in an inter-louvers distance 38 of approximately 1 mm and in a trapezoidal base width of approximately 3mm for the ribs, each of the three sides of the rib having approximately the same dimension. In second embodiment represented by figure 4, the leading edge portion 30, containing louvers 34, is much wider/longer along the transversal axis T than the trailing portion 32. Other alternatives, not represented, can be made. The ribs do not need to be trapezoidal and other shapes such as square, semi-circular or triangular are also possible. The following references have been utilized in this description. - 10: heat exchanger - 12: tank - 14: tube - 16: fins - fluid flow guide member - 18: metal strip - 20: panels - 22: fold line - 24: front face - 26: leading edge - 28: trailing edge - 30: leading portion - 32: trailing portion - 34: louvers - 36: strengthening ribs - 38: inter-louvers distance - N: normal axis - T: transversal axis - F: air flow

1. Fluid flow guide member (16) of a heat exchanger (10), adapted to be traversed by fluid flow (F), the guide member (16) being made from a corrugated metallic strip (18), the width (W) of which extending along a transversal axis (T) from a leading edge (26) to a trailing edge (28), the leading edge portion (30) of the guide member (16) being provided with slit louvers (34) adapted to deviate the flow (F), characterized in that the trailing edge portion (32) is free of slit louvers.

2. Fluid flow guide member (16) as set in the preceding claim further provided with strengthening ribs (36) arranged in the trailing edge portion (28). 3. Fluid flow guide member (16) as set in claim 2, wherein the ribs (36) are not slit. 4. Fluid flow guide member (16) as set in any of the claims 2 or 3, wherein the ribs (36) are formed by corrugating the trailing edge portion (32) of the strip (18). 5. Fluid flow guide member (16) as set in any of the claims 2 to 4, wherein the ribs (36) have a trapezoidal cross section. 6. Fluid flow guide member (16) as set in any of the preceding claims wherein the leading edge portion (30) and the trailing edge portion (32) are of equal length. 7. Fluid flow guide member (16) as set in any of the claims 1 to 5 wherein the leading edge portion (30) and the trailing edge portion (32) are of unequal length. 8. Heat exchanger (10) having tubes (14) between which are arranged fluid flow guide members (16) as set in any of the preceding claims.

2871672

Semiconductor device

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In the foregoing and following discussion like reference numerals refer to like features. The invention will now described further hereinafter by way of example only with reference to the accompanying drawings in which: - Figure 1a is a cross-sectional schematic of a typical individual SOI device; - Figure 1b is a cross-sectional schematic of a of an individual SOI device with an integrated heat sink; - Figure 2a is a schematic plan view of a typical high power SOI device, formed of multiple individual SOI devices, of the type illustrated in Figure 1 b; - Figure 2b is a schematic cross-sectional view of a typical high power SOI device, formed of multiple individual SOI devices, of the type illustrated in Figure 1 b; - Figure 2c is an exploded schematic plan view of a pair of individual SOI devices, of the type illustrated in Figure 1 b; - Figure 3a is a schematic plan view of a high power SOI device according to an embodiment; - Figure 3b is a schematic cross-sectional of a high power SOI device according to an embodiment; - Figure 4a is a schematic plan view of a high power SOI device according to an embodiment; - Figure 4b is a schematic cross-sectional of a high power SOI device according to an embodiment; - Figure 5a is a simulated two-dimensional device surface temperature map for a SOI device according to the prior art; - Figure 5b is a plot of temperature versus distance from the centre to edges of an SOI device according to the prior art; - Figure 6a is a simulated two-dimensional device surface temperature map for a SOI device according to an embodiment; - Figure 6b is a plot of temperature versus distance from the centre to edges of an SOI device according to an embodiment; - Figure 7a is a simulated two-dimensional device surface temperature map for a SOI device according to an embodiment; - Figure 7b is a plot of temperature versus distance from the centre to edges of an SOI device according to an embodiment; Figures 3a and 3b illustrate schematic views of a high power SOI device 20 formed of multiple unit cell SOI devices 1. In figure 3a, which is a plan view the of the high power SOI device 20, the SOI devices 1 (here arranged as pairs as discussed above) are arranged as a regular n x m array, where n is the number of rows of the array, and m is the number of columns in the array. The SOI devices may be formed as semiconductor device dies, typically as SOI MOS devices, where each of the device dies of the array shares a substrate 10, an SOI layer 14 and a BOX layer 12. The skilled person will understand that the number of rows n and the number of columns m of the array may be any positive integer as required by the particular application of the device. In this context the skilled person will also understand that the term "regular" array refers to the situation where the number of SOI devices 1 in all rows n of the array may be the same and that the number of SOI devices 1 in all columns m of the array may be the same. Figure 3b shows a cross-section of the SOI device 20 array taken through line A-A of Figure and shows the SOI MOS devices 1 corresponding to the number of columns n formed on the BOX layer and the substrate. This arrangement of layers is discussed in more detail below. The number of rows n in the array may, or may not, be equal to the number of columns m in the array. In the example the array is a 1 x 24 array, that is, there is one SOI device per column m, and twenty four SOI devices 1 per row. A heat sink element 16' may be integrated with each, or some of the SOI devices 1. Integration of a heat sink element 16' with an SOI device 1 is discussed in more detail below. Heat sink elements 16' may be omitted from the SOI devices 1 at the edge of the high power SOI device 20 as those edge SOI devices will be less prone to heating than centrally arranged SOI devices. This may be due to improved heat dissipation effects at the edge of the high power SOI device 20. With reference to Figures 3a the width of an inner heat sink element 16' associated with the central, or inner SOI device 1 is designated W _hs_0. The width of subsequent, or outer heat sink elements 16' associated with subsequent, or outer SOI devices 1 are generally designated W _hs_0+m, where m is column integer of the array integer corresponding to a particular SOI device 1. In particular, W _hs_1 and W _hs_-1 may designate the widths of the heat sink elements 16' adjacent to the central SOI device 1 (or devices) of the high power SOI device 20. The width of the heat sink element 16' W _hs_0 associated with the central SOI device 1 may be greater than the width of each of the heat sink elements 16' associated with the each of the subsequent SOI devices 1 away from the centre, forming the high power SOI device 20. Starting with the central heat sink element 16' the widths of the subsequent heat sink elements 16' may gradually and incrementally reduce to the smallest width at the edge of the SOI device 20 (or as discussed above at the SOI devices adjacent the edges of the SOI device 20). Therefore, the widths of the heat sink elements 16' may fulfil the requirement: [MATHS id=math0001]: and [MATHS id=math0002]: where m is the column integer associated with the SOI device 1 at (or adjacent to) the edge of the device. Thermal conductance is defined as the quantity of heat that passes in unit time through a plate of particular area and thickness when the plates opposite faces differ in temperature by one Kelvin. Thermal conductance is given by the expression: [MATHS id=math0003] - Where k is the thermal conductivity of the material of the heat sink, - A is the area and L is the depth of the material. From Eqn.1 above, the skilled person will appreciate that the thermal conductance of any heat sink is therefore dependent on the volume (area _x depth, where are is given as width time breadth) of the material, assuming that the thermal conductivity of the material k, remains constant. Therefore, as a result of a variation in width of the heat sink, which the skilled person will understand will vary the volume of the heat sink (all other dimensions being constant), from the centre to the edge of high power SOI device 20, the thermal conductance of each heat sink element 16' will also vary. This variation in thermal conductance between heat sink elements 16' has the result that during operation of the SOI device 20 the heat generated in the central SOI devices 1 of the high power device 20 will be reduced more efficiently than at the edge devices, so that more uniform temperature peaks across all of the SOI devices 1 can be achieved. In other words, the temperature may be substantially constant across the array of SOI devices 1 forming the high power SOI device 20. The width of heat sinks 16 in the central region of the high power SOI device 20 may be in the region of 2 to 3 µm where the width of successive heat sinks may reduce by a factor of 0.8 from the central region of the high power SOI device 20 to the edge region. Of course, the skilled person will understand that there will be a minimum limit on the width of the heat sink this limit may be determined by any lithography process used. For example in CMOS Typically, the depth of the heat sinks 16 may be 2.5 µm. However, any appropriate depth may be used where the depth is dependent on the thickness of the SOI layers 14 and BOX layers 12 used in any particular device provided that the heat sink extends from the top of the SOI layer 14 through the BOX layer 12 to the substrate. Alternately, in an embodiment and based on the general principles disclosed above the skilled person will appreciate that the volume of the heat sink elements, and thus the thermal conductance of the heat sinks may be varied by changing the depth of the heat sink elements. Therefore, starting with the central heat sink element the volume of the subsequent heat sink elements will incrementally reduce to the smallest volume at the edge of the SOI device 20. Therefore, the volume of the heat sink devices V _hs_0 fulfil the requirement: [MATHS id=math0004]: and [MATHS id=math0005]: where m is the column integer associated with the SOI device 1 at the edge of the device. To vary the volume of each of the heat sink elements the area of the window for the heat sink element on the mask design may be changed as would be understood by the skilled person. In an embodiment as shown in Figures 4a and 4b, rather than providing single heat sink elements 16' for each SOI device 1, the heat sinks 16' may sub-divided into smaller heat sinks, known as plugs. In this case the density of the plugs, that is the distance between each of the plugs may increase from the centre towards the edge of the SOI device 1. In other words, the spacing between adjacent plugs is smaller at the centre of the SOI device 1 than the spacing between adjacent plugs moving away from the centre of the SOI device 1. The skilled person will understand therefore that the distance between two adjacent plugs in a column m will decrease from the edge for towards the centre of the high power SOI device 20. The distance between two adjacent plugs may follow a geometric series. From the centre to the edge the distance between adjacent plugs increases by a factor of 0.8 from one plug to its adjacent plug in a column M. This ratio is may be dependent on the size of the device and also the required operation of the high power device SOI. Such an arrangement allows for ease of manufacture because the mask windows dimensions used to define the plug may be fixed for each SOI device 1. In other words the window dimensions of the mask used for form the heat sinks 16' will be fixed, but the distance between windows will vary dependent on the the required density. In embodiments, an isolation ring is provided around the periphery of the SOI device 20. The isolation ring is typically formed as a ring of oxide to prevent high voltage applied the device from damaging other low voltage components connected to it. Whilst the skilled person will appreciate regular n x m arrays are preferred so as to maximise area layout for high power SOI devices 20, the skilled person will also appreciate that the principles described above may also be applied to irregular arrays, in the form of circular, triangular, or any other layout of SOI devices 1. Figures 5a, 6a and 7a show simulated two-dimensional (2D) device surface temperature maps in Kelvin for the high power SOI device 20 operating at a power of 5.2 watts. In those figures the x and y -axis correspond to the lengths from the centre to respective top and side edges of the high power SOI device 20. In overview, Figures 5b, 6b and 7b show plots of temperature versus distance from the centre to edges of high power SOI devices 20. Figures 5a and 5b illustrate the device temperature for a prior art device of the type discussed above. The operating temperature for each of the prior art SOI devices 1 is in the range 517K for the centre device to 470K for an edge device. From this it is evident that for a prior art high power SOI device 20 heat is not evenly distributed across each of the SOI devices 1 and that a hot spot, which can result in device failure, occurs at the central devices. Figures 6a and 6b illustrate the device temperatures for a high power SOI device 20 according to embodiments discussed above. In comparison to the prior art device, the operating temperature for each of the SOI devices 1 is lower and substantially constant in the range 420K to 440K from the centre SOI devices 1 to the edge SOI devices 1. From this it is evident that heat generated during operation of the device is evenly distributed across each of the devices and that hot spots do not occur, as opposed to the prior art. Figures 7a and 7b illustrate the device temperatures for device according to embodiments discussed above. In comparison to the prior art device, the operating temperature for each of the SOI MOS devices 1 is lower and substantially constant at 438K from the centre SOI devices 1 to the edge SOI devices 1. From this it is evident that heat generated during operation of the device is evenly distributed across each of the devices and that a hot spots do not occur, as opposed to the prior art. According to the embodiments, the heat sink 16 is processed in the SOI device 1 by known techniques. A trench, corresponding in dimensions those of the heat sink, is etched through the SOI layer 14 and the BOX layer 12 to the substrate 10. The trench is then filled with a polysilicon heat sink material and the SOI device 1 structure such as the gate G, source S and drain D are then formed. To avoid negative effects on SOI device 1 characteristics such as junction leakage current and parasitic device capacitance the trenches are located near the source terminal which is grounded by arranging the heat sink on the same side of the SOI device as the source S contact. By providing the heat sinks as described, the heat sinks are optimised for such that that they sacrifices less area on the high power SOI device 20 whilst maintaining adequate heat dissipation purpose. As a consequence the high power SOI device 20 lower will have a lower Rdson. The embodiments presented herein can be implemented, either alone or in combination in for example, automotive applications such as relay driver applications, or as the skilled person will appreciate any other type of power driver in which the non-uniform rise of the temperature in the device is a concern for device reliability. Features which are described in the context of separate embodiments may also be provided in combination in a single embodiment. Conversely, various features which are, for brevity, described in the context of a single embodiment, may also be provided separately or in any suitable sub combination.

1. A semiconductor device comprising an array of heat sinks; the heat sinks being arranged such that the spacing between adjacent heat sinks is smaller at the centre of the semiconductor device than the spacing between adjacent heat sinks outside the centre of the semiconductor device.

2. The semiconductor device of claim 1, wherein the density of heat sinks is greater at the centre of the semiconductor device than the density of heat sinks outside the centre of the semiconductor device. 3. The semiconductor device of claims 1 or 2, wherein the distance between adjacent heat sinks increases with distance from the centre of the semiconductor device towards an edge of the semiconductor device. 4. The semiconductor device of claims 1 to 3, wherein said heat sinks at the centre of the semiconductor device are inner heat sink elements and said heat sinks outside the centre of the semiconductor device are outer heat sink elements. 5. The semiconductor device of claim 1, wherein a thermal conductance of an inner heat sink elements is greater than a thermal conductance of an outer heat sink elements. 6. The semiconductor device of claim 5, said inner heat sink elements having a first volume and said outer heat sink elements having a second volume, wherein the first volume is greater than the second volume. 7. The semiconductor device of claim 6, said inner heat sink elements having a first cross-sectional area and said outer heat sink elements having a second cross-sectional area, wherein the first cross-sectional area is greater than the second cross-sectional area. 8. The semiconductor device of any of claims 4 to 7, further comprising intermediate heat sink elements disposed between the inner heat sink elements and said outer heat sink elements, and having a thermal conductance intermediate that of said inner heat sink elements and said outer heat sink elements. 9. The semiconductor device of any one or more of the preceding claims, wherein said heat sink elements are disposed on a corresponding semiconductor die. 10. An array of semiconductor devices as claimed in any preceeding claim. 11. The semiconductor device of claim 10, wherein each of the semiconductor devices arranged as an array share a common substrate. 12. The semiconductor device of claims 10 to 11, wherein the array of semiconductor devices is a regular array. 13. The semiconductor device of claim 12, wherein the regular array is an n x m array, where n and m are positive integers. 14. The semiconductor device of any preceding claim further comprising an isolation ring is provided around the periphery of said device.

2871051

Device and method for attachment of an opening device on a flexible package

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention relates to a device and a method for attaching a resealable opening device on a flexible package. By a flexible package is meant a package or container which is made of a flexible material in the sense that the material is pliable. A flexible package of this kind may thus be made of a single-layered or multi-layered film material. The film material may comprise layers of plastic, such as PE, PP, PET, EVOH, and/or aluminium foil. Layers of plastic such as PE or PP may also comprise a filler, such as a mineral material. By a resealable opening device is meant a device enabling resealing and subsequent reopening of a flexible package once it has been initially opened. The invention is especially suitable for an opening device in the form of a thin-walled body which is to be attached to a side wall of a flexible package in an opening portion thereof. A flexible package 1 provided with such an opening device 2 in the form of a thin-walled body is shown in Figure 1 to which reference now is made. The flexible package 1 is of the stand-up pouch type and comprises two side walls 3 and a bottom wall 4. The package may, as shown in the figure, comprise a gas filled handle. The opening device 2 is applied to the package 1 in an opening portion 5 of the package 1, which opening portion 5 is formed by the two opposing side walls 3 of the flexible package 1 in an upper corner section of the same. The opening portion 5 of the flexible package 1 comprises in the unopened state of the package 1 an end tab 6, which for initial opening of the package 1 is separable from the package 1 by detachment along a separation line 7. The package 1 is shown in its unopened state in Figure 1. The opening device 2 is disposed on an application area 8 in said opening portion 5 on one of the said opposing side walls 3 adjacent to the end tab 6, and, more precisely, is disposed on that side of the separation line 7 situated opposite the end tab 6, adjacent to and parallel with this same separation line 7. After initial opening of the package 1 by removal of the end tab 6, the package 1 may be opened and closed by means of the opening device 2. In Figure 2a, removal of the end tab 6 is disclosed, and in Figures 2b and 2c, opening and closing, respectively, of the package 1 is shown. More precisely, in order to open the package 1, the opening device 2 is folded about a transverse hinge joint 9; and in order to close or reseal the package, the opening device 2 is folded about a longitudinal hinge joint 10 and locked in the folded position by means of a locking means 11. According to the invention, the opening devices to be attached on the flexible packages are provided by means of a web of semi-finished and interconnected opening devices, and such a web 12 is disclosed in Figure 3. The web 12 has been provided with a succession of transverse and longitudinal hinge joints 9 and 10, respectively, as well as locking means 11. In the shown embodiment, a single semi-finished opening device comprises a longitudinal hinge joint 10 and a transverse hinge joint 9 crossing said longitudinal hinge joint 10; and a locking means 11 comprising protrusions 13 forming two pairs of a male and female member 14 and 15, respectively, such that a male member 14 will engage a female member 15 by folding about the longitudinal hinge joint 10. The opening device may be attached to the flexible package by means of a welding operation or by means of an adhesive. The adhesive may be applied to the opening device and/or the application area of the package just prior to the application of the opening device. Alternatively, the opening device may be provided with an activable adhesive arranged on an application surface thereof. The adhesive may of the kind which is non-sticky in an non-activated state. The adhesive may be activable by means of heating. In Figure 4, to which reference now is made, an attachment unit 100 for an inventive device for attaching a resealable opening device 2 on a flexible package 1 is schematically shown. The attachment unit 100 comprises a carrier member 101 supported by a supporting structure. Thus, in the figure, a single carrier member 101 has been depicted in four different positions. It is of course possible for the supporting structure of the attachment unit to support more than one carrier member, such as two carrier members. In such a case, the carrier members may be arranged at opposing sides of the supporting structure. Alternatively, the supporting structure may support one carrier member along each side, i.e. four carrier members in total. The attachment unit 100 is rotatably arranged about an axis 103 such that the carrier member 101 may be indexed between the different positions. The different positions comprises a first position A corresponding to a pick-up position; a second position B corresponding to a heating position; a third position C corresponding to a attachment position; and a fourth position D corresponding to an idle position. The carrier member 101 has a carrier surface 104 and in the shown embodiment, the carrier surface 104 is provided with recesses 105 arranged for reception of protrusions 13 of the opening device 2 forming the locking means 11. The carrier means 101 further comprises a retention means indicated at 106 and arranged to hold the opening device 2 being picked up. The retention means 106 may as indicated in the figure be provided in at least one of the recesses 105 formed in the carrier surface 104 of the carrier member 101. The operation of the attachment unit 1 of the inventive device will now be described with reference to Figures 5a-5c. In Figure 5a, the carrier member of the attachment unit 100 is arranged in position A, i.e. the pick-up position. A web 12 of semi-finished and interconnected opening devices is fed by a not shown feeding device to the pick-up position with an inclined orientation in order to align one semi-finished opening device to be picked up with the carrier member 101. In the pick-up position, the carrier member 101 is brought to engagement with the web 12 in order to form and pick up the opening device 2. The carrier member 101 may be movable towards the web 12 and/or the web 12 may be movable towards the carrier member 101 in order to cause said engagement. The opening device 2 may be formed by a punch engagement. As evident from the figure, the opening devices are punched out from the web 12 such that the web 12 is provided with a succession of holes 16. Thus, the integrity of the web 12 is maintained which facilitates the recovery of surplus material. In the drawing, the carrier member 101 is depicted as having been pressed through the web 12 in order to clearly illustrate the disengaging of the opening device 2 from the web 12. It is understood that alternative methods exist for the forming of the opening devices while they are picked up by means of the carrier member. For instance, the opening devices may be pulled from the web along pre-made perforations outlining the opening devices. The carrier means 101 further comprises a retention means indicated at 106 and arranged to hold the opening device 2 being picked up. The retention means 106 may as indicated in the figure be provided in at least one of the recesses 105 formed in the carrier surface 104 of the carrier member 101. In Figure 5b, the carrier member 101 has been moved to position B, i.e. the heating position, by means of rotating the attachment unit 100 about the axis 103. In the heating position, the carrier member 101 and the opening device 2 supported thereof is positioned in front of a first heating unit 107 which in the shown embodiment forms part of the inventive device. In the shown embodiment, the opening device 2 is provided with an adhesive layer 17 on its application surface 18, and the first heating unit 107 is arranged for activation of said adhesive layer 17 by means of contact heating. To this end, the first heating 107 unit comprises a engagement surface 108 arranged to engage or abut the adhesive layer 17 of the opening device 2 by means of relative movement between the carrier member 101 and the first heating unit 107. The engagement surface 108 of the first heating unit 107 may be heated by means of one or more electrical heating element arranged in ducts provided in the body of the first heating unit 107. The engagement surface may be replaceable arranged. For instance, the engagement surface 108 may be provided on a section of the first heating unit which is separate from the body of the first heating unit. Upon activation of the adhesive layer of the opening device, the body is pressed against the section comprising the engagement surface, which in turn is pressed against the adhesive layer. The provision of the engagement surface on a section separate from the body of the first heating unit enables easy maintenance or exchange of the engagement surface. The first heating 107 unit ensures controlled heat transfer to the adhesive layer 17 and the engagement surface 108 may be provided with a surface treatment in order to prevent the adhesive layer 17 from adhering to said engagement surface 108. The engagement surface 108 may be planar or may be provided with a profile, such as an undulated or wave shaped surface. By using a profiled engagement surface 108, such as an undulated surface, it will be possible to reshape an initially planar adhesive layer 17 into a profiled adhesive layer 17 corresponding to the profile of the engagement surface 108. Hereby the capacity of the adhesive layer 17 to accumulate heat in its activated state may be improved and it may thus be ensured that the adhesive layer 17 is still active in connection with application of the opening device 2 on the flexible package 1. In Figure 5c, the carrier member 101 is moved to position C, i.e. the attachment position, by means of continued rotation of the attachment unit 100 about the axis 103. As evident from the figure, a web 19 of interconnected packages 1 is provided, and the opening device 2 supported by the carrier member 101 is, in the attachment position, positioned in front of one flexible package 1 on which an opening device 2 is about to be applied. More specifically, the web 19 of packages 1 is fed to the attachment position such that the application area 8 of the package 1 about to be provided with an opening device 2 is aligned with the carrier member 101. In order to ensure an improved reliability of the application of the opening device 2 on the flexible package 1, the inventive device may as in the shown embodiment further comprise a second heating unit 109. The second heating unit 109 is arranged for preheating of the application area 8 of the package 1. In the shown embodiment, the second heating unit 109 is arranged up-stream of the attachment unit 100, such that while one flexible package 1 is being preheated, a subsequent flexible package 1 in the down-stream direction is being provided with an opening device 2. By preheating of said application area 8, a difference in temperature between the adhesive layer 17 and the application area 8 may, in connection with the attachment of the opening device 2 on the package 1, be reduced. The reduced difference in temperature may improve the attachment of the opening device on the package. The second heating unit 109 may comprise heating elements arranged for preheating by means of radiation. The carrier member 101 is arranged to attach the opening device 2 supported thereof on the application area 8 of the flexible package 1 by means of relative movement between the carrier member 101 and the flexible package 1. Once the opening device 2 has been pressed against the flexible package 1, the retention means 106 is operated to release the opening device 2, and subsequently the carrier member 2 and the flexible package 1 are separated, leaving the opening device 2 behind and attached to the flexible package 1. Subsequently, the carrier member 2 is indexed or moved from the attachment position back to the pick-up position in order to form and pick up the next opening device 2. The movement may be accomplished by continued rotation of the attachment unit 100 about the axis 103 such that the carrier member 2 passes position D, i.e. the idle position. Alternatively, the attachment unit 100 may be rotated in the opposite direction and the carrier member 101 thus being moved to the pick-up position by passing position C. Hereafter, the operation of the inventive device will be explained more in detail with reference to Figures 6a-6k showing cross sectional views of the attachment unit 100 and the carrier member 101 supported thereof in different situations. The carrier member 101 is supported by supporting structure 102 which in turn is rotatably arranged about the axis 103. The carrier member 101 is further reciprocally movable in a direction perpendicular to the carrier surface 104 of the carrier member 101 by means of said supporting structure 102. The supporting structure 102 may be arranged to move of the carrier member 101 in any suitable manner such as by a pneumatically or electrically controlled mechanism (not shown). The protrusions 13 forming the female members 15 of the locking means 11 of the opening device 2 are evident from the figures. More precisely, each female member 15 is formed by a protrusion 13 provided with an upper opening 20 adapted for reception of the male member 14 through a snap fit action when the opening device 2 is folded about the longitudinal hinge joint as previously described. The figures further depict the retention means 106 for holding the picked up opening device 2. In the shown embodiment, the retention means 106 is formed by a pin 110 movably arranged in each of the recesses 105 provided in the carrier surface 104 of the carrier member 101 for reception of the female members 15 of the locking means 11 of the opening device 2. More precisely, the pins 110 are movable from a first position corresponding to an idle position to a second position corresponding to a holding position. Each pin 110 is provided with an end cavity 111 arranged to receive an associated female member 15 with a tight fit when being moved to said second position. Figures 6a-6d disclose the operation while the carrier member 101 is in position A, i.e. the pick-up position. As shown in Figure 6a, a semi-finished opening device 2, forming part of the web 12 of semi-finished and interconnected opening devices, is aligned in front of the carrier member 101 of the attachment unit 100 in said pick-up position. In Figure 6b, the carrier member 101 has been moved in the direction indicated by arrow P1 by the supporting structure 102 towards the web 12 such that carrier surface 104 of the carrier member 101 engages a knife arrangement 112 provided on the opposite side of the web 12. As a consequence, a punch engagement is accomplished for forming or outlining the opening device 2 in the web 12. In Figure 6c, the pins 110 of the retention means 106 have been moved in the direction indicated by arrows P2 from the first position, i.e. the idle position, to the second position, i.e. the holding position. As evident, the female members 15 of locking means 11 of the opening device 2 are each received by an associated end cavity 111 of the pins 110. As mentioned above, the end cavities 111 are arranged to receive the female members 15 with a tight fit, whereby a retention action is achieved ensuring that the opening device 2 is reliable secured to the carrier member 101. The operation of the retention means 106 may by achieved by a pneumatic, hydraulic, electric, magnetic arrangement or the like. In Figure 6d, the carrier member 101 is retracted in the direction indicated by arrow P3 by means of the supporting structure 102, picking up the opening device 2 and leaving a hole 16 in the web 12 caused by the picked up opening means 2. However, the opening device 2 is punched out of the web 12 such that the integrity of the web 12 is maintained which facilitates the recovery of surplus material. For instance, the surplus may be wound up, and the resulting roll may by used as raw material for manufacturing of other products, such as new webs of semi-finished and interconnected opening devices. Figures 6e-6g disclose the operation while the carrier member 101 is in position B, i.e. the heating position. Figure 6e shows the carrier member 101 and the opening device 2 supported thereby moved to said heating position by rotation of the supporting structure 102 about the axis 103 in the direction indicated by arrow P4. In the heating position, the application surface 18 of the opening device 2 is positioned in front of the engagement surface 108 of the first heating unit 107. In Figure 6f, the carrier member 101 has been moved in the direction indicated by arrow P5 towards the first heating 107 unit by means of the supporting structure 102 such that the application surface 18 of the opening device 2 is pressed against the engagement surface 108, whereby the adhesive layer 17 applied on the application surface 18 of the opening device 2 is activated. The engagement surface 108 is planar in the shown embodiment, but as explained above, the engagement surface may be profiled in order to produce an activated adhesive layer with a profiled shape and improved capacity to accumulate heat. In Figure 6g, the carrier member 101 has been retracted in the direction indicted by arrow P6 from the first heating unit 107 by means of the supporting structure 102. Figures 6h-6k disclose the operation while the carrier member 101 is in position C, i.e. the attachment position. Figure 6h shows the carrier member 101 and the opening device 2 supported thereby moved to said application position by rotation about the axis 103 in the direction indicated by arrow P7. In the attachment position, the opening device 2 and its application surface 18 with activated adhesive layer 17 is positioned in front of the application area 8 of a flexible package 1. The application area 8 may, as previously has been described, be preheated. Also, the package 1 may be included in a web of interconnected packages. In Figure 6i, the carrier member 101 has been moved towards the flexible package 1 by means of the supporting structure 102 and indicated by arrow P8 such that the application surface 18 of the opening device 2 is pressed against the application area 8 of the flexible package 1. Since the adhesive layer 17 on the application surface 18 has been activated in the previous position B, the opening device 2 will adhere to the application area 8 of the package. 1 Cooling, either forced or natural, will case the opening device 2 to be fixedly attached to the flexible package 1. By moving the pins 110 back to the first position, as shown in Figure 6j and indicated by arrows P9, while the carrier member 101 is being maintained against the flexible package 1, the end cavities 111 of the pins 110 will disengage the female members 15 of the opening device 2, that is, the female members 15 will be released from the tight fit grip by the end cavities 111 of the pins 110. Thus, by moving the pins 110 to the first position, the retention means 106 releases its hold of the opening device 2. In Figure 6k, the carrier member 101 has been retracted in the direction indicated by arrow P10 from the flexible package 1 by means of the supporting structure 102 while the opening device 2 remains attached to the flexible package 1. Figure 6I shows the carrier member 101 moved to position D, i.e. the idle position, by rotation about the axis 103 in the direction indicated by arrow P11. By continued rotation about the axis 103, the carrier member 101 will be returned to position A, and the cycle of operation may be repeated for attachment of the next opening device on the next flexible package. It will be appreciated that the present invention is not limited to the embodiments shown. It is thus possible to replace the above described knife arrangement positioned on the opposite side of the web of semi-finished and interconnected opening devices with a knife arrangement supported by the carrier member itself. An abutment may be provided, against which the carrier member and its knife arrangement is pressed in order to form a opening device by punch engagement. It is also possible to replace the first heating unit in the form of a contact-heater with a radiation-heater or hot-air heater. Further, the opening devices may not comprise an adhesive layer. In such a case, the first heating unit may be replaced with a hot-melt applicator applying a hot-melt adhesive on the application area of the flexible package just prior to the attachment of the opening device. As mentioned above, it is also possible for the attachment unit to comprise several carrier members operating simultaneous in different positions. It is also possible for the inventive device to comprise several attachment units operating in parallel. For instance, the inventive device may comprise three attachment units arranged in parallel and cooperating for attaching opening devices on a single web on interconnected flexible packages. The opening devices included in the web of semi-finished and interconnected opening device may be of other types than the thin-body type described above. For instance, the web may carry opening devices in the form of the screw cap type.

1. Device for attaching a resealable opening device (2) on a flexible package (1), comprising: an attachment unit (100) having at least one movably arranged carrier member (101),: the at least one carrier member (101) being movable between a pick-up position and an attachment position,: wherein the at least one carrier member (101), in said pick-up position, is arranged for engagement with a web (12) of semi-finished and interconnected opening devices in order to form and pick-up the opening device (2), and: wherein the at least one carrier member (101), in said attachment position, is arranged for attachment of the opening device (2) on an application area (8) of the flexible package (1).

2. Device according to claim 1, wherein the at least one carrier member, (101) in said pick-up position, is arranged to form the opening device (2) by punch engagement with the web (12) of semi-finished and interconnected opening devices. 3. Device according to claim 1 or 2, wherein the attachment unit (100) is rotatably arranged and wherein the at least one carrier member (101) is movable between said pick-up position and said attachment position by means of rotation of the attachment unit (101). 4. Device according to any one of claims 1-3, further comprising a first heating unit (107) provided at a heating position, wherein the at least one carrier member (101) is arranged to pass the heating position during movement from said pick-up position to said attachment position, the first heating unit (107) being arranged for activation of an adhesive layer (17) of the opening device (2) by heating. 5. Device according to claim 4, wherein the first heating (107) unit comprises a engagement surface (108) arranged for activation of said adhesive layer (17) by means of contact heating. 6. Device according to claim 5, wherein the engagement surface (108) is profiled. 7. Device according to any one of claims 1-6, further comprising a second heating unit (109) for preheating of an application area (8) of the flexible package (1). 8. Device according to claim 7, wherein the second heating unit (109) is arranged for preheating of the application area (8) by means of radiation. 9. Device according to any one of claim 1-8, wherein the at least one carrier member (101) comprises a carrier surface (104) provided with a recess (105) arranged for reception of a protrusion (13) of the opening device (2). 10. Device according to claim 9, further comprising a pin (110) arranged in said recess (105) and movably between an first position and a second position in which it lockingly engages the protrusion (13) received into the recess (105).

2871051

Device and method for attachment of an opening device on a flexible package

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention relates to a device and a method for attaching a resealable opening device on a flexible package. By a flexible package is meant a package or container which is made of a flexible material in the sense that the material is pliable. A flexible package of this kind may thus be made of a single-layered or multi-layered film material. The film material may comprise layers of plastic, such as PE, PP, PET, EVOH, and/or aluminium foil. Layers of plastic such as PE or PP may also comprise a filler, such as a mineral material. By a resealable opening device is meant a device enabling resealing and subsequent reopening of a flexible package once it has been initially opened. The invention is especially suitable for an opening device in the form of a thin-walled body which is to be attached to a side wall of a flexible package in an opening portion thereof. A flexible package 1 provided with such an opening device 2 in the form of a thin-walled body is shown in Figure 1 to which reference now is made. The flexible package 1 is of the stand-up pouch type and comprises two side walls 3 and a bottom wall 4. The package may, as shown in the figure, comprise a gas filled handle. The opening device 2 is applied to the package 1 in an opening portion 5 of the package 1, which opening portion 5 is formed by the two opposing side walls 3 of the flexible package 1 in an upper corner section of the same. The opening portion 5 of the flexible package 1 comprises in the unopened state of the package 1 an end tab 6, which for initial opening of the package 1 is separable from the package 1 by detachment along a separation line 7. The package 1 is shown in its unopened state in Figure 1. The opening device 2 is disposed on an application area 8 in said opening portion 5 on one of the said opposing side walls 3 adjacent to the end tab 6, and, more precisely, is disposed on that side of the separation line 7 situated opposite the end tab 6, adjacent to and parallel with this same separation line 7. After initial opening of the package 1 by removal of the end tab 6, the package 1 may be opened and closed by means of the opening device 2. In Figure 2a, removal of the end tab 6 is disclosed, and in Figures 2b and 2c, opening and closing, respectively, of the package 1 is shown. More precisely, in order to open the package 1, the opening device 2 is folded about a transverse hinge joint 9; and in order to close or reseal the package, the opening device 2 is folded about a longitudinal hinge joint 10 and locked in the folded position by means of a locking means 11. According to the invention, the opening devices to be attached on the flexible packages are provided by means of a web of semi-finished and interconnected opening devices, and such a web 12 is disclosed in Figure 3. The web 12 has been provided with a succession of transverse and longitudinal hinge joints 9 and 10, respectively, as well as locking means 11. In the shown embodiment, a single semi-finished opening device comprises a longitudinal hinge joint 10 and a transverse hinge joint 9 crossing said longitudinal hinge joint 10; and a locking means 11 comprising protrusions 13 forming two pairs of a male and female member 14 and 15, respectively, such that a male member 14 will engage a female member 15 by folding about the longitudinal hinge joint 10. The opening device may be attached to the flexible package by means of a welding operation or by means of an adhesive. The adhesive may be applied to the opening device and/or the application area of the package just prior to the application of the opening device. Alternatively, the opening device may be provided with an activable adhesive arranged on an application surface thereof. The adhesive may of the kind which is non-sticky in an non-activated state. The adhesive may be activable by means of heating. In Figure 4, to which reference now is made, an attachment unit 100 for an inventive device for attaching a resealable opening device 2 on a flexible package 1 is schematically shown. The attachment unit 100 comprises a carrier member 101 supported by a supporting structure. Thus, in the figure, a single carrier member 101 has been depicted in four different positions. It is of course possible for the supporting structure of the attachment unit to support more than one carrier member, such as two carrier members. In such a case, the carrier members may be arranged at opposing sides of the supporting structure. Alternatively, the supporting structure may support one carrier member along each side, i.e. four carrier members in total. The attachment unit 100 is rotatably arranged about an axis 103 such that the carrier member 101 may be indexed between the different positions. The different positions comprises a first position A corresponding to a pick-up position; a second position B corresponding to a heating position; a third position C corresponding to a attachment position; and a fourth position D corresponding to an idle position. The carrier member 101 has a carrier surface 104 and in the shown embodiment, the carrier surface 104 is provided with recesses 105 arranged for reception of protrusions 13 of the opening device 2 forming the locking means 11. The carrier means 101 further comprises a retention means indicated at 106 and arranged to hold the opening device 2 being picked up. The retention means 106 may as indicated in the figure be provided in at least one of the recesses 105 formed in the carrier surface 104 of the carrier member 101. The operation of the attachment unit 1 of the inventive device will now be described with reference to Figures 5a-5c. In Figure 5a, the carrier member of the attachment unit 100 is arranged in position A, i.e. the pick-up position. A web 12 of semi-finished and interconnected opening devices is fed by a not shown feeding device to the pick-up position with an inclined orientation in order to align one semi-finished opening device to be picked up with the carrier member 101. In the pick-up position, the carrier member 101 is brought to engagement with the web 12 in order to form and pick up the opening device 2. The carrier member 101 may be movable towards the web 12 and/or the web 12 may be movable towards the carrier member 101 in order to cause said engagement. The opening device 2 may be formed by a punch engagement. As evident from the figure, the opening devices are punched out from the web 12 such that the web 12 is provided with a succession of holes 16. Thus, the integrity of the web 12 is maintained which facilitates the recovery of surplus material. In the drawing, the carrier member 101 is depicted as having been pressed through the web 12 in order to clearly illustrate the disengaging of the opening device 2 from the web 12. It is understood that alternative methods exist for the forming of the opening devices while they are picked up by means of the carrier member. For instance, the opening devices may be pulled from the web along pre-made perforations outlining the opening devices. The carrier means 101 further comprises a retention means indicated at 106 and arranged to hold the opening device 2 being picked up. The retention means 106 may as indicated in the figure be provided in at least one of the recesses 105 formed in the carrier surface 104 of the carrier member 101. In Figure 5b, the carrier member 101 has been moved to position B, i.e. the heating position, by means of rotating the attachment unit 100 about the axis 103. In the heating position, the carrier member 101 and the opening device 2 supported thereof is positioned in front of a first heating unit 107 which in the shown embodiment forms part of the inventive device. In the shown embodiment, the opening device 2 is provided with an adhesive layer 17 on its application surface 18, and the first heating unit 107 is arranged for activation of said adhesive layer 17 by means of contact heating. To this end, the first heating 107 unit comprises a engagement surface 108 arranged to engage or abut the adhesive layer 17 of the opening device 2 by means of relative movement between the carrier member 101 and the first heating unit 107. The engagement surface 108 of the first heating unit 107 may be heated by means of one or more electrical heating element arranged in ducts provided in the body of the first heating unit 107. The engagement surface may be replaceable arranged. For instance, the engagement surface 108 may be provided on a section of the first heating unit which is separate from the body of the first heating unit. Upon activation of the adhesive layer of the opening device, the body is pressed against the section comprising the engagement surface, which in turn is pressed against the adhesive layer. The provision of the engagement surface on a section separate from the body of the first heating unit enables easy maintenance or exchange of the engagement surface. The first heating 107 unit ensures controlled heat transfer to the adhesive layer 17 and the engagement surface 108 may be provided with a surface treatment in order to prevent the adhesive layer 17 from adhering to said engagement surface 108. The engagement surface 108 may be planar or may be provided with a profile, such as an undulated or wave shaped surface. By using a profiled engagement surface 108, such as an undulated surface, it will be possible to reshape an initially planar adhesive layer 17 into a profiled adhesive layer 17 corresponding to the profile of the engagement surface 108. Hereby the capacity of the adhesive layer 17 to accumulate heat in its activated state may be improved and it may thus be ensured that the adhesive layer 17 is still active in connection with application of the opening device 2 on the flexible package 1. In Figure 5c, the carrier member 101 is moved to position C, i.e. the attachment position, by means of continued rotation of the attachment unit 100 about the axis 103. As evident from the figure, a web 19 of interconnected packages 1 is provided, and the opening device 2 supported by the carrier member 101 is, in the attachment position, positioned in front of one flexible package 1 on which an opening device 2 is about to be applied. More specifically, the web 19 of packages 1 is fed to the attachment position such that the application area 8 of the package 1 about to be provided with an opening device 2 is aligned with the carrier member 101. In order to ensure an improved reliability of the application of the opening device 2 on the flexible package 1, the inventive device may as in the shown embodiment further comprise a second heating unit 109. The second heating unit 109 is arranged for preheating of the application area 8 of the package 1. In the shown embodiment, the second heating unit 109 is arranged up-stream of the attachment unit 100, such that while one flexible package 1 is being preheated, a subsequent flexible package 1 in the down-stream direction is being provided with an opening device 2. By preheating of said application area 8, a difference in temperature between the adhesive layer 17 and the application area 8 may, in connection with the attachment of the opening device 2 on the package 1, be reduced. The reduced difference in temperature may improve the attachment of the opening device on the package. The second heating unit 109 may comprise heating elements arranged for preheating by means of radiation. The carrier member 101 is arranged to attach the opening device 2 supported thereof on the application area 8 of the flexible package 1 by means of relative movement between the carrier member 101 and the flexible package 1. Once the opening device 2 has been pressed against the flexible package 1, the retention means 106 is operated to release the opening device 2, and subsequently the carrier member 2 and the flexible package 1 are separated, leaving the opening device 2 behind and attached to the flexible package 1. Subsequently, the carrier member 2 is indexed or moved from the attachment position back to the pick-up position in order to form and pick up the next opening device 2. The movement may be accomplished by continued rotation of the attachment unit 100 about the axis 103 such that the carrier member 2 passes position D, i.e. the idle position. Alternatively, the attachment unit 100 may be rotated in the opposite direction and the carrier member 101 thus being moved to the pick-up position by passing position C. Hereafter, the operation of the inventive device will be explained more in detail with reference to Figures 6a-6k showing cross sectional views of the attachment unit 100 and the carrier member 101 supported thereof in different situations. The carrier member 101 is supported by supporting structure 102 which in turn is rotatably arranged about the axis 103. The carrier member 101 is further reciprocally movable in a direction perpendicular to the carrier surface 104 of the carrier member 101 by means of said supporting structure 102. The supporting structure 102 may be arranged to move of the carrier member 101 in any suitable manner such as by a pneumatically or electrically controlled mechanism (not shown). The protrusions 13 forming the female members 15 of the locking means 11 of the opening device 2 are evident from the figures. More precisely, each female member 15 is formed by a protrusion 13 provided with an upper opening 20 adapted for reception of the male member 14 through a snap fit action when the opening device 2 is folded about the longitudinal hinge joint as previously described. The figures further depict the retention means 106 for holding the picked up opening device 2. In the shown embodiment, the retention means 106 is formed by a pin 110 movably arranged in each of the recesses 105 provided in the carrier surface 104 of the carrier member 101 for reception of the female members 15 of the locking means 11 of the opening device 2. More precisely, the pins 110 are movable from a first position corresponding to an idle position to a second position corresponding to a holding position. Each pin 110 is provided with an end cavity 111 arranged to receive an associated female member 15 with a tight fit when being moved to said second position. Figures 6a-6d disclose the operation while the carrier member 101 is in position A, i.e. the pick-up position. As shown in Figure 6a, a semi-finished opening device 2, forming part of the web 12 of semi-finished and interconnected opening devices, is aligned in front of the carrier member 101 of the attachment unit 100 in said pick-up position. In Figure 6b, the carrier member 101 has been moved in the direction indicated by arrow P1 by the supporting structure 102 towards the web 12 such that carrier surface 104 of the carrier member 101 engages a knife arrangement 112 provided on the opposite side of the web 12. As a consequence, a punch engagement is accomplished for forming or outlining the opening device 2 in the web 12. In Figure 6c, the pins 110 of the retention means 106 have been moved in the direction indicated by arrows P2 from the first position, i.e. the idle position, to the second position, i.e. the holding position. As evident, the female members 15 of locking means 11 of the opening device 2 are each received by an associated end cavity 111 of the pins 110. As mentioned above, the end cavities 111 are arranged to receive the female members 15 with a tight fit, whereby a retention action is achieved ensuring that the opening device 2 is reliable secured to the carrier member 101. The operation of the retention means 106 may by achieved by a pneumatic, hydraulic, electric, magnetic arrangement or the like. In Figure 6d, the carrier member 101 is retracted in the direction indicated by arrow P3 by means of the supporting structure 102, picking up the opening device 2 and leaving a hole 16 in the web 12 caused by the picked up opening means 2. However, the opening device 2 is punched out of the web 12 such that the integrity of the web 12 is maintained which facilitates the recovery of surplus material. For instance, the surplus may be wound up, and the resulting roll may by used as raw material for manufacturing of other products, such as new webs of semi-finished and interconnected opening devices. Figures 6e-6g disclose the operation while the carrier member 101 is in position B, i.e. the heating position. Figure 6e shows the carrier member 101 and the opening device 2 supported thereby moved to said heating position by rotation of the supporting structure 102 about the axis 103 in the direction indicated by arrow P4. In the heating position, the application surface 18 of the opening device 2 is positioned in front of the engagement surface 108 of the first heating unit 107. In Figure 6f, the carrier member 101 has been moved in the direction indicated by arrow P5 towards the first heating 107 unit by means of the supporting structure 102 such that the application surface 18 of the opening device 2 is pressed against the engagement surface 108, whereby the adhesive layer 17 applied on the application surface 18 of the opening device 2 is activated. The engagement surface 108 is planar in the shown embodiment, but as explained above, the engagement surface may be profiled in order to produce an activated adhesive layer with a profiled shape and improved capacity to accumulate heat. In Figure 6g, the carrier member 101 has been retracted in the direction indicted by arrow P6 from the first heating unit 107 by means of the supporting structure 102. Figures 6h-6k disclose the operation while the carrier member 101 is in position C, i.e. the attachment position. Figure 6h shows the carrier member 101 and the opening device 2 supported thereby moved to said application position by rotation about the axis 103 in the direction indicated by arrow P7. In the attachment position, the opening device 2 and its application surface 18 with activated adhesive layer 17 is positioned in front of the application area 8 of a flexible package 1. The application area 8 may, as previously has been described, be preheated. Also, the package 1 may be included in a web of interconnected packages. In Figure 6i, the carrier member 101 has been moved towards the flexible package 1 by means of the supporting structure 102 and indicated by arrow P8 such that the application surface 18 of the opening device 2 is pressed against the application area 8 of the flexible package 1. Since the adhesive layer 17 on the application surface 18 has been activated in the previous position B, the opening device 2 will adhere to the application area 8 of the package. 1 Cooling, either forced or natural, will case the opening device 2 to be fixedly attached to the flexible package 1. By moving the pins 110 back to the first position, as shown in Figure 6j and indicated by arrows P9, while the carrier member 101 is being maintained against the flexible package 1, the end cavities 111 of the pins 110 will disengage the female members 15 of the opening device 2, that is, the female members 15 will be released from the tight fit grip by the end cavities 111 of the pins 110. Thus, by moving the pins 110 to the first position, the retention means 106 releases its hold of the opening device 2. In Figure 6k, the carrier member 101 has been retracted in the direction indicated by arrow P10 from the flexible package 1 by means of the supporting structure 102 while the opening device 2 remains attached to the flexible package 1. Figure 6I shows the carrier member 101 moved to position D, i.e. the idle position, by rotation about the axis 103 in the direction indicated by arrow P11. By continued rotation about the axis 103, the carrier member 101 will be returned to position A, and the cycle of operation may be repeated for attachment of the next opening device on the next flexible package. It will be appreciated that the present invention is not limited to the embodiments shown. It is thus possible to replace the above described knife arrangement positioned on the opposite side of the web of semi-finished and interconnected opening devices with a knife arrangement supported by the carrier member itself. An abutment may be provided, against which the carrier member and its knife arrangement is pressed in order to form a opening device by punch engagement. It is also possible to replace the first heating unit in the form of a contact-heater with a radiation-heater or hot-air heater. Further, the opening devices may not comprise an adhesive layer. In such a case, the first heating unit may be replaced with a hot-melt applicator applying a hot-melt adhesive on the application area of the flexible package just prior to the attachment of the opening device. As mentioned above, it is also possible for the attachment unit to comprise several carrier members operating simultaneous in different positions. It is also possible for the inventive device to comprise several attachment units operating in parallel. For instance, the inventive device may comprise three attachment units arranged in parallel and cooperating for attaching opening devices on a single web on interconnected flexible packages. The opening devices included in the web of semi-finished and interconnected opening device may be of other types than the thin-body type described above. For instance, the web may carry opening devices in the form of the screw cap type.

11. Method for attaching a resealable opening device (2) on a flexible package (1), comprising: providing a web (12) of semi-finished and interconnected opening devices (2,): forming and picking up an opening device (2) by bringing a carrier member (101) of an attachment unit (100) to engagement with the web (12) of semi-finished and interconnected opening devices (2), and: attaching the opening device (2) on an application area (8) of the flexible package (1).

12. Method according to claim 11, wherein the opening device (2) is formed by a punching engagement. 13. Method according to claim 11 or 12, further comprising activation of an adhesive layer (17) of the opening device (2) by contact heating prior to the attaching of the opening device (2). 14. Method according to claim 13, wherein the activation of the adhesive layer (17) comprises engaging said adhesive layer (17) with a profiled engagement surface (108) of a first heating unit (107). 15. Method according to any one of claims 12-14, further comprising preheating of said application area (8) of the package (1) prior to the attaching of the opening device (2).

2871099

Cargo protection device and a corner element therefor

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The invention will, in the following, be exemplified by embodiments. It should however be realized that the embodiments are included in order to explain principles of the invention and not to limit the scope of the invention, defined by the appended claims. Details from two or more of the embodiments may be combined with each other. Figure 1 schematically illustrates a portion of an interior 10 of a vehicle 12. A cargo protection device 14 is attached in a position, wherein the cargo protection device 14 will help to protect the users of the vehicle from cargo being thrown from the luggage compartment 15 onto the users of the vehicle, e.g. when braking the vehicle 12. The cargo protection device 14 of Figure 1 occupies a front position located behind a backrest 16 of the driver's seat and a backrest 18 of a seat of a possible front passenger. The cargo protection device 14 then protects the driver and a possible front seat passenger. As an alternative, the cargo protection device 14 may instead be attached in a back position, which will be further explained in conjunction with Figure 4. The cargo protection device 14 comprises a fabric portion 20 forming a main portion of the cargo protection device 14. The fabric portion 20 is made of a flexible material, such that it may be folded and/or rolled. Suitable materials are a fabric, a net or a plastic film. Figure 1 illustrates a fine net. The fabric portion 20 is preferably at least partly transparent, such that it is possible for the driver of the vehicle to see through it when looking backwards in the vehicle 12, e.g. through a mirror. Positional references used herein, such as upper, lower back and front, relate to when the cargo protection device 14 is mounted in the interior 10 of the vehicle 12. However, the cargo protection device 14 can be dismounted from the interior 10 of the vehicle 12, and stored or transported as folded and/or rolled. The cargo protection device 14 may be sold as a separate item or it may be sold together with the vehicle 12. The fabric portion 20 comprises an edge trim 22, e.g. made of a belt. The edge trim 22 is also made of a flexible material, such that it may be folded and/or rolled together with the rest of the fabric portion 20. The edge trim 22 may e.g. comprise a belt similar to the belts, which are used as safety belts. The edge trim 22 is formed in one part and encloses a circumference of the fabric portion 20. The edge trim 22 is attached to the rest of the fabric portion 20. It may e.g. be sewn to and/or glued to the rest of the fabric portion 20. The edge trim 22 may be used to distribute forces applied at the fabric portion 20, e.g. from the cargo, in case of a braking or a collision, to attachment points to the vehicle interior 10 at upper corners 24, 26 and lower corners 28, 30 of the fabric portion 20. The edge trim 22 is also used to tension the fabric portion 20, as will be described below. The cargo protection device 14 has a height h, which is adapted to substantially cover the interspace between a back rest 32, 34 of a back seat in a folded position and a ceiling 36 of the vehicle 12. Thereby, the cargo protection device 20 covers the lateral interspace between the backrest 16 of the driver's seat and the back rest 18 of the seat of a possible front passenger, such that cargo cannot pass in between the two front seats. Each of the upper corners 24, 26 comprises a corner element 38, 40, which is described in detail in conjunction with Figure 2. The corner elements 38, 40 are used to attach the upper corners 24, 26 of the fabric portion 20 to the vehicle interior 10. The corner elements 38, 40 may be made of a rigid material, e.g. a metal or alloy, such as steel. They help to receive and distribute impact forces in case of a collision involving the vehicle 12, e.g. a frontal collision pushing the cargo forwards against the cargo protection device 14. As may be gleaned from Figure 2, the corner element 38 comprises a holding portion 42 and an attachment portion 44. The corner element is in Figure 2 illustrated in untensioned state. The holding portion 42 comprises a first leg 46 and a second leg 48 connected by a central portion 50. The central portion 50 is in the illustrated case rather short. It bridges the legs 46, 48 and provides a suitable location for fixing the attachment portion 44 to the rest of the corner element 38. If the corner element 38 is made of a metal or alloy, such as steel, the attachment portion 44 may be welded to the central portion 50. The edge trim 22 forms a channel in which the legs 46, 48 are, at least partly, but in this case substantially fully inserted. The fabric portion 20 has a small opening 51 through which the attachment portion 44 protrudes from the central portion 50. The first leg 46 extends from the central portion 50 in a first direction D _1 and the second leg 48 extends from the central portion 50 in a second direction D _2, such that the first D _1 and second directions D _2 in an untensioned state, as in Figure 2, form an angle α with each other, with 90° < α < 110°. The holding portion 42 has an arcuate shape. Therefore the directions D _1, D _2 of the respective legs 46, 48 are determined as the direction of a tangent to the arcuate shape at the ends 52, 53 of the respective leg 46, 48. The angle α is preferably chosen, such that the cargo protection device 14 substantially follows the shape of the ceiling 36, which typically has a certain curvature. The attachment portion 44 comprises an elongated portion 54 ending by an attachment means 56. The attachment means 56 is adapted for easy attachment to the vehicle, preferably without any use of tools. The illustrated embodiment show a mushroom-shaped head adapted to fit into a receiving cavity 58 in the ceiling 36 or an upper portion of a side wall 60 of the vehicle 12. As an alternative, the attachment portion 44 may be attached by a hook comprised in either the attachment portion 44, or in the ceiling 36 or side wall 60. The attachment portion 44 extends from the central portion 50 in a third direction D _3, which is partly opposite to the first direction D _1 and partly opposite to the second direction D _2. The third direction D _3 of the attachment portion 44 forms an angle β _1 with the first direction D _1, such that 90° ≤ β _1 ≤ 180°, preferably 100° ≤ β _1 ≤ 165°, more preferably 110° ≤ β _1 ≤ 150 most preferably 120° ≤ β _1 ≤ 140°. Thereby the angle β _2 to the second direction D _2 is given by β _2 = 360°- β _1 - α. The attachment portion 44 is non-rotationally connected to the holding portion 42. There is hence no rotational movement in a location 59, where the attachment portion 44 meets the holding portion 42, even when the fabric portion 20 is tensioned. Figure 3 illustrates an alternative embodiment of the corner element 38, wherein the central portion 50 is reinforced by a reinforcement 55. Preferably, the reinforcement 55 has a shape and a size fitting in the channel formed by the edge trim 22, or the channel may be locally wider. The other details of the alternative embodiment are similar to those of the corner element of Figure 2 and will not be explained again. Returning again to Figure 1, it may be gleaned from the figure that the fabric portion 20 of the cargo protection device 14 further comprises a pocket wall 62. The pocket wall 62 is attached to a lower edge 64 of the fabric portion 20, e.g. by sewing and/or gluing it together with the edge trim 22 to the fabric portion 20. The pocket wall 62 is also attached to a lower portion of a first side edge 66 of the fabric portion 20 and a lower portion of a second opposite side edge 68 of the fabric portion 20. The fabric portion also comprises a fourth edge, an upper edge 70 being opposite to the lower edge 64. One or more engagement means 72a, 72b, 72c are arranged at or adjacent to an upper edge 73 of the pocket wall 62. The fabric portion 20 comprises corresponding engagement means 74a, 74b, 74c for receiving the engagement means 72a, 72b, 72c of the pocket wall 62. Thereby a pocket 76 is formed by the pocket wall 62 and a portion of the fabric portion 20, which portion is extending between the lower edge 64 and a position of the fabric portion 20 corresponding to the upper edge 73 of the pocket wall 62. The pocket 76 may be used for storing items, when the cargo protection device 14 is in use. When the cargo protection device 14 is not in use, the pocket 76 may be used to store the rest of cargo protection device 14 by folding or rolling the rest of the fabric portion 20 into the pocket 76. In that case it is beneficial, if the pocket wall 62 extends all the way out to the side edges 66, 68, such that the pocket 76 has the same width as the rest of the fabric portion 20. The cargo protection device 14 further comprises at least one connection means 78, 80 for connecting the lower edge 64 to the interior 10 of the vehicle 12. In the illustrated embodiment of Figure 1, there is one at each lower corner 28, 30. The connection means 78, 80 comprises a belt with an adjustable length, which belt is adapted to be attached to the vehicle interior 10, e.g. to an attachment means at a floor of the vehicle 12, e.g. an ISO fix attachment means, or to an attachment means fixed to the chair rail of one the front seats (not visible in Figure 1 ). The connection means 78, 80 are attached in the vicinity of the lower corners 28, 30 of the fabric portion 20. The attachment means at the floor or chair rail may comprise a loop and the connection means 78, 80 may comprise a hook (not visible in Figure 1 ), which is adapted to grip into the loop. In addition to being adjustable, or as a complement, the connection means 78, 80 may be resilient, e.g. comprising an elastic material, such that it is easy to connect the connection means 78, 80 in an elongated state and the connection means 78, 80 then springs back and retains the cargo protection device 14 in the intended position. The resiliency may be between 1 and 10 cm, preferably between 3 and 7 cm. The resiliency may also be used to compensate for variation in size between different cargo protection devices 14 and/or vehicles 12 due to production tolerances. The cargo protection device 14 may also be utilized in a back position, as is illustrated in Figure 4. The backrests 32, 34 of the back seats are then in a substantially upright position, suitable for passengers in the back seat. The cargo protection device 14 extends substantially from the ceiling 36 to a floor 82 of the luggage compartment 15. The lower corners 28, 30 are attached by a connection means, here in the form of a hook 84, 86 at each lower corner 28, 30 gripping around a respective receiving loop 88, 90 in the interior 10 of the vehicle 12. The hooks 84, 86 may be resiliently attached to the fabric portion 20, such that they are adapted to be easily attached to the loops 88, 90 and yet spring back and retain the cargo protection device 14 in position. The upper corners 24, 26 are attached in a similar way as for Figure 1. Normally, the cargo protection device 14 is adapted for attachment at either the front position or the back position. It is thus provided with both the connection means 78, 80 illustrated in Figure 1 and the connection means, the hooks 84, 86 of Fig 3. By providing ready connection means for both the front and back positions, the cargo protection device 14 is ready to use without any additional manual resetting of the connection means. When mounting the cargo protection device 14 to the interior 10 of the vehicle 12, the attachment means 56 of the corner elements 38, 40 are engaged with the ceiling 36 or the upper portion of a side wall 60. In the illustrated embodiment, the mushroom-shaped head is inserted into the receiving cavity 58 in the ceiling 36 in either the front position of the cargo protection device 14, as in Figure 1, or in the back position, as in Figure 4. The receiving cavity 58 has an opening portion, where it is possible to insert the mushroom-shaped head of the attachment means 56 and another opening having a width less than that of the mushroom-shaped head but larger than or as large as that of elongated portion 54, keeping the mushroom-shaped head in place, once it has been inserted. Thereafter the cargo protection device 14 is tensioned by applying a tension force at a lower portion of the cargo protection device 14, e.g. at the lower edge 64. Preferably the force is applied at or in the vicinity of the lower corners 28, 30, e.g. by tensioning the connection means 78, 80. Thereby the fabric portion 20 is stretched. In particular, the corner element 38, 40 will stretch the upper edge 70 of the fabric portion 20. It is hence possible to omit using an elongated stiff element, such as one or more elongated stiff bars along the upper edge 70 of the fabric portion 20, which is commonly used according to prior art technology. In fact, it is according to the invention possible to provide a cargo protection device 14 without any other stiff element than the corner element, such that the cargo protection device 14 may be folded and/or rolled as a whole.

1. A corner element (38, 40) for attachment of a cargo protection device (14) to an interior (10) of a vehicle (12), said corner element (38, 40) comprising - a holding portion (42), adapted to be located at least partly in or at a corner (24, 26) of said cargo protection device (14) intended to be upwards, when said cargo protection device (14) is mounted in the vehicle (12), - an attachment portion (44), for attachment of said corner element (38, 40) to said interior (10) of said vehicle (12),: said holding portion (42) comprising a first leg (46) and a second leg (48) connected by a central portion (50), said first leg (46) extending from said central portion (50) in a first direction (D_1) and said second leg (48) extending from said central portion (50) in a second direction (D_2), such that the first (D_1) and second (D_2) directions in an untensioned state of said holding portion (42) form an angle α with each other with 90° < α < 110°,: said attachment portion (44) extending from said central portion (50) of said holding portion (42) in a third direction (D_3), which third direction (D_3) has a first component in a direction opposite to said first direction (D_1) and a second component in a direction opposite to said second direction (D_2).

2. The corner element (38, 40) according to claim 1, wherein said holding portion (42) has at least partly an arcuate shape, said first and second legs (46, 48) forming portions of said arcuate shape. 3. The corner element (38, 40) according to claim 1 or 2, wherein said third direction (D_3) forms an angle β_1 with said first direction (D_1), such that 90° ≤ β_1 ≤ 180°, preferably 100° ≤ β_1 ≤ 165°, more preferably 110° ≤ β_1 ≤ 150°, most preferably 120° ≤ β_1 ≤ 140°. 4. A cargo protection device (14) comprising - a foldable and/or rollable fabric portion (20) having two corners (24, 26) intended to be upwards, when said cargo protection device (14) is mounted in a vehicle (12), and - at least one corner element (38, 40) according to any one of the preceding claims located in or at one or each of said corners (24, 26) of said fabric portion (20). 5. The cargo protection device (14) according to claim 4, wherein said fabric portion (20) comprises an edge trim (22), said edge trim (22) also being foldable and/or rollable, said edge trim (22) being formed in one part and enclosing at least 50%, preferably at least 70%, more preferably at least 90%, most preferably substantially all of a circumference of said fabric portion (20). 6. The cargo protection device (14) according to claim 5, wherein said foldable edge trim (22) comprises a belt. 7. The cargo protection device (14) according to any one of claims 4-6, wherein said fabric portion (20) further comprises a pocket wall (62), said pocket wall (62) together with a portion of said fabric portion (20) forming a pocket (76). 8. The cargo protection device (14) according to claim 7, wherein said pocket (76) is formed along an edge (64) of said fabric portion (20), preferably said edge (64) being intended to be a lower edge, when said cargo protection device (14) is mounted in a vehicle (12). 9. The cargo protection device (14) according to claim 7 or 8, wherein said pocket wall (62) has a first long side edge attached to said edge (64) of said fabric portion (20), a first side edge attached to a portion of a first side edge (66) of said fabric portion (20), a second side edge attached to a portion of a second side edge (68) of said fabric portion (20), and wherein one or more engagement means (72a, 72b, 72c) are arranged at or adjacent to a second long side edge (73) of said pocket wall (62) for engagement with said fabric portion (20), said engagement means (72a, 72b, 72c) for example comprising a button and/or a hook and loop arrangement. 10. The cargo protection device (14) according any one of claims 4-9, wherein said fabric portion (20) has two additional corners (28, 30) intended to be downwards when said cargo protection device (14) is mounted in a vehicle (12), said cargo protection device (14) further comprising at least one connection means (78, 80; 84, 86) at or adjacent to one or each of said additional corners (28, 30) for attachment to said interior (10) of said vehicle (12). 11. The cargo protection device (14) according to claim 10, wherein said connection means (78, 80) comprises a belt adapted for attachment to said interior (10) of said vehicle (12), when said cargo protection device (14) is mounted in a front position in said vehicle (12), preferably said belt having an adjustable length. 12. The cargo protection device (14) according to claim 10 or 11, wherein said connection means (84, 86) comprises a hook adapted for attachment to said interior (10) of said vehicle (12), when said cargo protection device (14) is mounted in a back position in said vehicle (12). 13. The cargo protection device (14) according to any one of claims 10-12, wherein said connection means (78, 80; 84, 86) is resilient. 14. A vehicle (12) comprising a cargo protection device (14) according to any one of claims 4-13. 15. A method of attaching a cargo protection device (14) according to any one of claims 4-13 to an interior (10) of a vehicle (12), said method comprising - attaching both of said corners (24, 26) to said interior (10) of said vehicle (12) at a ceiling (36), or at a respective upper portion of a respective side wall (62) of said vehicle (12), by means of said corner elements (38, 40), - tensioning said cargo protection device (14) by applying a tension force at a lower portion of said cargo protection device (14), preferably at a lower edge (64) of said fabric portion (20), more preferably at or adjacent to one or each of said additional corners (28, 30) of said fabric portion (20), - attaching said additional corners (28, 30) to said interior (10) of said vehicle (12).

2871636

Sound reduction system

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 schematically shows a sound reduction device 1 used in a sound reduction system (not shown) according to the invention. The sound reduction device 1 comprises a supporting structure 2 and a frame 3. The frame 3 is arranged to be supported by the supporting structure 2. A sound reducing material 4 is placed in the frame 3. The sound reduction device 1 further comprises fastening means 5 arranged to secure the frame 3 to the supporting structure 2 by means of interacting with openings 6 in the supporting structure 2. The frame 3 has a length L measured from a frame front edge 7 to a frame rear edge 8. The frame 3 further has a thickness T measured from a top side 9 of the frame 3 to a bottom side 10 of the frame 3 and a width W measured in a direction perpendicular to both the thickness T and the length L. The length L, thickness T and width W determines the area and volume of the frame 3. The area and volume are adapted depending on which frequencies are desired to reduce. The thickness T can be the same over the entire length L of the frame or vary over the entire length L. Similarly the width W can be the same over the entire length L and/or thickness T or vary over the length L and/or thickness T. In figure 1 the frame 3 is supported by the supporting structure 2 such that the sound reducing material 4 is located inside the supporting structure 2. It is possible to have other configurations wherein the frame 3 is supported by the supporting structure 2 such that the sound reducing material 4 is located outside of the supporting structure 2. The supporting structure 2 in figure 1 is closed and is essentially oval shaped. The supporting structure 2 further comprises a collar 11 located along a front edge () of the supporting structure 2. The collar 11 is a portion of the supporting structure 2 which has a larger circumference than the remaining supporting structure 2. As can be seen from figure 1, the frame 3 is aerodynamically shaped with a cross section in the shape of an airfoil or wing. The frame 3 may be curved as in figure 1, but it may also be straight depending on the desired characteristics of the frame 3. Figure 2 schematically shows a sound reduction system 12 according to the invention. The sound reduction system 12 comprises a channel 13 and a sound reduction device 1 mounted inside the channel 13. This particular system is taken from a vehicle engine (not shown) where the channel 13 is an air intake channel. The sound reduction device 1 is placed after the air filter (not shown), i.e. the gaseous medium is in this case clean air. The sound reduction device 1 is placed before a compressor (not shown) in the clean air system of the engine. Further illustrated in figure 2 is a resonator 14 with resonator openings 15. As can be seen the sound reduction device 1 is placed inside the channel 13 such that it does not interfere with the resonator openings 15 thereby complementing already present sound reducing components of the engine. The channel 13 in figure 2 comprises a first channel part 16 and a second channel part 17. In figure 2 the first channel part 16 is enclosed by the second channel part 17. The sound reduction device 1 is mounted in the channel 13 such that the collar 11 rests against a first channel part edge 18. This arrangement allows for the sound reducing material 4 to be placed in the desired location in the channel 13. The location of the sound reducing material 4 in the channel 13 is determined by the shape of the channel 13 and the location of other sound reducing components. Adapting the supporting structure 2 and the placement of the sound reducing material 4 in relation to each other are adaptations which fall well within the scope of the invention. As can be seen from figure 2 the frame 3 follows the curved shape of the channel 13 as well as having a cross section which is aerodynamic. This ensures that a low pressure drop is achieved over the sound reduction device 1. The frame 3 is placed horizontally in the channel 13 in figure 2. This is merely an example of an orientation of the frame 3. Depending on the layout of for instance other sound reducing components, the frame 3 can be oriented vertically or at an angle between horizontally and vertically. Figure 3 schematically shows an exploded view of a sound reduction device 1 according to the invention. Figure 3 illustrates how the sound reduction device 1 is assembled and similarly can be disassembled. The frame 3 comprises a first frame part 19 and a second frame part 20 in between which a sound reducing material 4 is placed. This is in this example illustrated by a solid member. The first frame part 19 and second frame part 20 are after being assembled optionally covered by a first fastening arrangement 21 and a second fastening arrangement 22. The first fastening arrangement 21 and second fastening arrangement 22 are, as described above mainly used when a fibre mat is placed in between the first frame part 19 and second frame part 20. After assembly of the frame 3 the frame 3 is inserted into the supporting structure 2. Fastening means 5 on the frame 3 may form for instance a snap-in connection with the corresponding openings 6 on the supporting structure 2. The supporting structure 2 is preferably flexible such that it expands when the frame 3 is inserted, thereby ensuring a secure snap-in fit with the frame 3. The fastening means 5 comprises in this example three protrusions on each longitudinal side interacting with corresponding openings on the supporting structure 2. The fastening means 5 may alternatively take the shape of rails or a similar elongated protrusion on the frame 3 and a corresponding elongate slit on the supporting structure 2. The sound reduction device 1 can be disassembled in the reverse order. The fastening means 5 can alternatively to a snap-in connection be melted or welded, depending on the material of the supporting structure 2 and frame 3, to firmly secure the frame 3 to the supporting structure 2. The first frame part 19 and second frame part 20 can similarly be assembled securely by melting or welding, or have frame fastening means (not shown) which allows disassembly of the frame 3. Figure 4 schematically shows a diagram showing the effect of the sound reduction system 12 in an engine with the system installed compared to an engine without the system. The x-axis in the diagram represents frequency measured in Hz. The y-axis represents the measurement of the sound pressure measured in dB(A). The dashed line indicates measurements made without the sound reducing system. As can be seen for some frequencies around 2200 Hz and 2500 Hz the sound pressure exceeds 100 dB(A). The solid line represents measurements made with the sound reduction system 12. For higher frequencies above ca 1150 Hz a reduction in the sound pressure can be observed. The effect in this particular example is greatest for higher frequencies and it can be observed that sound pressure does not exceed 100 dB(A) for any frequencies measured. The diagram is merely intended to illustrate the effect of the inventive system and is not to be seen as a limiting example. The invention, depending on the design of the sound reduction device 1, is effective over a wider frequency range than illustrated in figure 4. Figures 2 and 4 relate to an air intake duct in a vehicle engine. This is merely an illustrative example of the invention and is not intended to be limiting for the application of the invention. Alternative applications wherein similar effects can be achieved can for instance be in channels in a ventilation system or in a system comprising a pump pumping a gaseous medium.

1. Noise reduction system (12) comprising a sound reduction device (1), the sound reduction device (1) comprising a sound reducing material (4); and a channel (13) wherein a gaseous medium is arranged to flow, characterized in that the sound reduction device (1) is mounted inside the channel (13), thereby placing the sound reducing material (4) inside the channel (13).

2. Sound reduction system (12) according to claim 1, wherein the sound reduction device (1) comprises a supporting structure (2) and a frame (3) arranged to be supported by the supporting structure (2), wherein the sound reducing material (4) is placed in the frame (3). 3. Sound reduction system (12) according to claim 2, wherein the supporting structure (2) of the sound reduction device (1) is a closed structure and that the frame (3) is placed in the supporting structure (2) such that the sound reducing material (4) is located inside the supporting structure (2). 4. Sound reduction system (12) according to claim 2 or 3, wherein the supporting structure (2) comprises a collar (11). 5. Sound reduction system (12) according to any one the preceding claims, wherein the sound reduction device (1) is removably mounted inside the channel (13). 6. Sound reduction system (12) according to any one of claims 2-5, wherein the sound reducing material (4) is a solid member placed in the frame (3) and/or the sound reducing material (4) comprises a fibre mat placed in the frame (3). 7. Sound reduction system (12) according to any one of claims 2-6, wherein the sound reduction device (1) further comprises fastening arrangements (21, 22) attached to the frame (3), thereby keeping the sound reducing material (4) from escaping from the frame (3). 8. Sound reduction system (12) according to any one of claims 2-6, wherein sound reduction device (1) is arranged to be disassembled. 9. Sound reduction system (12) according to any one of the preceding claims, wherein the sound reducing material (4) is one of or a combination of glass fibre, polar fleece or polyurethane. 10. Sound reduction system (12) according to any one of the preceding claims, wherein the frame (3) is aerodynamically shaped such that the pressure drop of the gaseous medium over the frame (3) is reduced. 11. Sound reduction system (12) according to claim 10, wherein a cross-section of the frame (3) is wing-shaped. 12. Sound reduction system (12) according to any one of claims 2-11, wherein the supporting structure (2) and frame (3) is made of a plastic and/or a metal such as aluminium or stainless steel, the supporting structure (2) and frame (3) preferably being made of the same material as the channel (13) in which it is placed. 13. Sound reduction system (12) according to any one of the preceding claims, wherein the pressure of the gas in the channel (13) is above atmospheric pressure, at atmospheric pressure or below atmospheric pressure. 14. Vehicle comprising a sound reduction system (12) according to any one of the preceding claims, wherein the channel (13) is an air intake channel.

2871437

Heat exchanger

Based on the following detailed description of an invention, generate the patent claims. There should be 11 claims in total. The first, independent claim is given and the remaining 10 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In reference to figure 1, a brazed fluid-air heat exchanger 10 as per the invention comprises a plurality of flat tubes 12 received at both extremities 14, where only one is represented, into a double header plate 16 which construction is detailed below. To improve the heat exchange, corrugated fins are arranged between the tubes 12. The double header plate 16 comprises a main header plate 18 and, against its external face 20 visible on figure 1, a reinforcement header plate 22. The external face 20 designates the face external to the tank, not represented. The main header plate 18 and the reinforcement plate 22 as well as their manufacturing processes are now described in reference to figure 2, 3 and 4. The main header plate 18 is made in using a deformation process, such as punching, out of a first rectangular metal plate 24 mainly extending along a longitudinal axis L. Transversal openings 26 are operated across the width of the first plate 24 for receiving the tubes 12. The openings 26 have in the present embodiment been punched and are provided with a peripheral wall 28 protruding away from the plate 18. Furthermore, two rectangular slots 30 are cut in the middle of the transversal width of the first plate 24. As the illustration example of figure 2, height transversal openings 26 are between the slots 30. The main header plate 18 further comprises peripheral bent tabs enabling crimping of a tank, not represented. These are just illustrative examples as the teachings of the present invention may apply to any types of tanks. Similarly to the main plate 18, the reinforcement plate 22 is made in using a deformation process, such as punching, out of a second rectangular metal plate 32 mainly extending along the longitudinal axis L. Transversal openings 34 are operated across the width of the second plate 32 for arranging the tubes 12. The openings 34, have in the present embodiment been punched, and are also provided with a peripheral wall 36 protruding away from the second plate 22. The inter-openings distance D is identical on the main header plate 18 and on the reinforcement plate 22. As the illustration example, the reinforcement plate 32 of figure 3 comprises height transversal openings 34. Furthermore, at the longitudinal extremities of the second plate 32, on the width of said plate 32, two rectangular tabs 38 are cut and bent. The distance between the two tabs 38 is equal to the distance between the two slots 30. To ease the bending of the tabs 38, a transversal V-notch 40, detailed in figure 4, is provided by the foot of the tabs 38, the notch 40 creating a weak line for bending. The assembly of the double header plate 16 is now described in reference to figures 5 where can be observed that the reinforcement plate 22 is arranged against the external face of the main header plate 18, either in contact with the main plate 18 or at a small distance without exceeding 20 mm. The tabs 38 are complementary engaged into the slots 30 and the transversal openings 26, 34, of the heads are aligned. This mechanical arrangement requires manufacturing accuracy of the header plates 18, 22, so when assembling them together, the tabs engage the slots and the openings of both header plates are aligned enabling engagement of the tubes 12. In the embodiment represented the reinforcement header plate (22) is symmetrical and can be assembled in engaging any of the tabs 38 in any of the slots 30. The final assembly of the heat exchanger 10 consists in engaging the tubes 12 through the reinforcement plate 22, the extremities 14 engaging the peripheral walls 28 of the openings of the main header plate 18. As can be seen, while the main header plate 18 receives all the tubes 12, the reinforcement plate 22 may be made to receive only few of the tubes 12. In the illustrative example of the figures, the reinforcement plate 22 receives height tubes 12 only. In such embodiment a double header plate 16 may comprises a plurality of reinforcement plates 22, each arranged against the external face 20 of the main header plate 18 receiving a sub-set of the tubes 12. As well known in the art, the double header plate 16, the tubes 12 and the fins are brazed together after assembly. The following references have been utilised in this description: - 10: heat exchanger - 12: tubes - 14: extremity of a tube - 16: double header plate - 18: main header plate - 20: external face of the main header plate - 22: reinforcement header plate - 24: main rectangular plate - 26: elongated openings - 28: peripheral wall - 30: slots - 32: other rectangular plate - 34: transversal openings reinforcement plate - 36: peripheral wall - 38: tabs - 40: V-notch - L: longitudinal axis - T: transversal axis - D: inter opening distance

1. Heat exchanger (10) wherein flat tubes (12) are received in a double header plate (16) comprising the complementary arrangement of a main header plate (18) and a reinforcement header plate (22).

2. Heat exchanger (10) as set in the preceding claim wherein the reinforcement header plate (22) is arranged against the main header plate (18). 3. Heat exchanger (10) as set in claim 2 wherein both header plates (18, 22) are provided with openings (26, 34) for arranging the flat tubes (12), the openings being surrounded by a peripheral wall (28, 36) extending away from the header plate (18, 22). 4. Heat exchanger (10) as set in claim 3 wherein the peripheral walls (34) of the reinforcement plate (22) extend toward the main header plate (18). 5. Heat exchanger (10) as set in claim 4 wherein the top edge of the peripheral walls (34) of the reinforcement plate (22) is at a maximum distance of 20 mm of the main header plate (18). 6. Heat exchanger (10) as set in claim 5 wherein the top edge of the peripheral walls (34) of the reinforcement plate (22) abut the main header plate (18). 7. Heat exchanger (10) as set in any of the preceding claims further comprising means (30, 38) enabling a complementary alignment of the two header plates (18, 22). 8. Heat exchanger (10) as set in claim 7 wherein the alignment means (30, 38) comprise slots (30) arranged in one of the header plate and complementary tabs (38) arranged in the other header plate, the tabs (38) engaging in the slots (30). 9. Heat exchanger (10) as set in any of the preceding claims wherein the reinforcement plate is arranged around a sub-set of the tubes (12). 10. Heat exchanger (10) as set in claim 9 wherein a plurality of reinforcement plates (22) are arranged under one main header plate (18), each reinforcement plate (22) receiving a sub-set of tubes (12). 11. Heat exchanger (10) as set in any of the preceding claim wherein the tubes (12) extend between two main header plates (18), at least one having a reinforcement header plate (22).

2871437

Heat exchanger

Based on the following detailed description of an invention, generate the patent claims. There should be 2 claims in total. The first, independent claim is given and the remaining 1 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In reference to figure 1, a brazed fluid-air heat exchanger 10 as per the invention comprises a plurality of flat tubes 12 received at both extremities 14, where only one is represented, into a double header plate 16 which construction is detailed below. To improve the heat exchange, corrugated fins are arranged between the tubes 12. The double header plate 16 comprises a main header plate 18 and, against its external face 20 visible on figure 1, a reinforcement header plate 22. The external face 20 designates the face external to the tank, not represented. The main header plate 18 and the reinforcement plate 22 as well as their manufacturing processes are now described in reference to figure 2, 3 and 4. The main header plate 18 is made in using a deformation process, such as punching, out of a first rectangular metal plate 24 mainly extending along a longitudinal axis L. Transversal openings 26 are operated across the width of the first plate 24 for receiving the tubes 12. The openings 26 have in the present embodiment been punched and are provided with a peripheral wall 28 protruding away from the plate 18. Furthermore, two rectangular slots 30 are cut in the middle of the transversal width of the first plate 24. As the illustration example of figure 2, height transversal openings 26 are between the slots 30. The main header plate 18 further comprises peripheral bent tabs enabling crimping of a tank, not represented. These are just illustrative examples as the teachings of the present invention may apply to any types of tanks. Similarly to the main plate 18, the reinforcement plate 22 is made in using a deformation process, such as punching, out of a second rectangular metal plate 32 mainly extending along the longitudinal axis L. Transversal openings 34 are operated across the width of the second plate 32 for arranging the tubes 12. The openings 34, have in the present embodiment been punched, and are also provided with a peripheral wall 36 protruding away from the second plate 22. The inter-openings distance D is identical on the main header plate 18 and on the reinforcement plate 22. As the illustration example, the reinforcement plate 32 of figure 3 comprises height transversal openings 34. Furthermore, at the longitudinal extremities of the second plate 32, on the width of said plate 32, two rectangular tabs 38 are cut and bent. The distance between the two tabs 38 is equal to the distance between the two slots 30. To ease the bending of the tabs 38, a transversal V-notch 40, detailed in figure 4, is provided by the foot of the tabs 38, the notch 40 creating a weak line for bending. The assembly of the double header plate 16 is now described in reference to figures 5 where can be observed that the reinforcement plate 22 is arranged against the external face of the main header plate 18, either in contact with the main plate 18 or at a small distance without exceeding 20 mm. The tabs 38 are complementary engaged into the slots 30 and the transversal openings 26, 34, of the heads are aligned. This mechanical arrangement requires manufacturing accuracy of the header plates 18, 22, so when assembling them together, the tabs engage the slots and the openings of both header plates are aligned enabling engagement of the tubes 12. In the embodiment represented the reinforcement header plate (22) is symmetrical and can be assembled in engaging any of the tabs 38 in any of the slots 30. The final assembly of the heat exchanger 10 consists in engaging the tubes 12 through the reinforcement plate 22, the extremities 14 engaging the peripheral walls 28 of the openings of the main header plate 18. As can be seen, while the main header plate 18 receives all the tubes 12, the reinforcement plate 22 may be made to receive only few of the tubes 12. In the illustrative example of the figures, the reinforcement plate 22 receives height tubes 12 only. In such embodiment a double header plate 16 may comprises a plurality of reinforcement plates 22, each arranged against the external face 20 of the main header plate 18 receiving a sub-set of the tubes 12. As well known in the art, the double header plate 16, the tubes 12 and the fins are brazed together after assembly. The following references have been utilised in this description: - 10: heat exchanger - 12: tubes - 14: extremity of a tube - 16: double header plate - 18: main header plate - 20: external face of the main header plate - 22: reinforcement header plate - 24: main rectangular plate - 26: elongated openings - 28: peripheral wall - 30: slots - 32: other rectangular plate - 34: transversal openings reinforcement plate - 36: peripheral wall - 38: tabs - 40: V-notch - L: longitudinal axis - T: transversal axis - D: inter opening distance

12. Process to manufacture heat exchanger (10) comprising the steps of: - providing a first rectangular metal sheet (24) having a long longitudinal side and a short transversal side, - forming a main header plate (18) by operating in said first sheet transversal openings (26) and two slots (30), each slot being between two transversal openings, - providing a second rectangular metal sheet (32) having a long longitudinal side and a short transversal side, - forming a reinforcement header plate (22) by operating in said second sheet transversal openings (34) with identical inter-opening distance as in the first sheet and, - forming in said second sheet two tabs (38) extending perpendicularly to the second sheet, - assembling the header plates (18, 22) by approaching the reinforcement header plate from the main header plate and engaging the tabs into the slots, - providing flat tubes (12) and, engaging said tubes through the openings (26, 34) of the reinforcement plate and of the main plate.

13. Process as set in claim 12 further comprising the steps of: - forming the tabs (38) in the second sheet by: - cutting said second sheet (32) along its short transversal sides so to form extending tabs coplanar with the sheet, - operating a transversal notch (40) at the junction of the tabs and the sheet so to create a weak line, - bending the tab over the weak line so the tab extend perpendicularly to the sheet.

2871303

A temporary edge protection system

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

According to an embodiment of the temporary edge protection system 1, as shown in Figures 1, 2 and 3 it comprises barrier panels 2, 3, 4, posts 5, panel holders 6 adjustably mountable on the posts 5, and post holders 7. The post holders 7 are arranged on a base 8, such as a floor, a concrete slab, or some other structure of a building. The edge protection system 1 is arranged close to the edge of the base, often several floors up, i.e. tens of meters above ground. There are different standards stating the requirements that the edge protection system must fulfill in order to be allowed for a particular use. For flat surfaces, and/or close to the ground, the requirements are of course lower than for sloping bases and/or high heights. Other parameters have an influence as well. The present edge protection system 1 is easily adaptable to the requirement of different standards due to its flexibility. For the users the weight of the system parts is an important factor, since they often assemble several hundreds of system parts during a working day. Therefore it is not optimal to provide one single embodiment which qualifies for the highest standard, since it becomes unnecessarily heavy for use in large volumes of lower standard applications. According to the illustrated embodiment, the barrier panels 2-4, which are most cumbersome to handle, and the weight of which is particularly important, are made flexible to be easily adaptable to different standards, and applications. Furthermore, aluminum has been applied to a high extent for manufacturing different parts of the system. However even plastics has been found usable to some extent as will be explained below. The flexibility is illustrated with three example assemblies in Figures 4 to 6. In order to obtain this flexibility, as shown in these figures as well as more detailed in Figures 7-10, the barrier panels 2-4 comprise at least three types of bars in slightly different combinations. In other words, each barrier panel 2-4 comprises a set of aluminum bars including a top bar 10, a bottom bar 11, two side bars 12, and an intermediate bar 13. According to one embodiment three different types of bars, i.e. aluminum profiles, have been employed, where the side bars 12 are of the same kind, and so are the top and bottom bars 10, 11. However, it would be possible to use a single kind for all bars, or to introduce further diversification. On the other hand, the three types employed in this embodiment have individual advantages for the chosen use as will be evident below. The side bars 12 are connected at their ends with first respectively second ends of the top and bottom bars to form a rectangular section. Thus, at top ends 14 of the side bars 12, the ends 15 of the top bar 10 are connected, and at bottom ends 16 of the side bars 12 the ends 17 of the bottom bar 11 are connected. The intermediate bar 13 is attached to the side bars 12 between the top and bottom bars 10, 11, wherein the intermediate bar 13 is provided with a top connection groove 18 extending along its length and facing the top bar 10, and a bottom connection groove 19 extending along its length and facing the bottom bar 11, wherein each side bar 12 is provided with several bar attachment portions 22 spaced along the side bar. The top bar 10 is provided with a connection groove, or bottom connection groove, 20 facing the intermediate bar 13, and the bottom bar 11 has a connection groove, or top connection groove, 21, which faces the intermediate bar 13 as well. More particularly, each bar attachment portion 22 has a through hole 23 extending laterally through the side bar 12, i.e. in parallel with the top bar 10, and the bottom bar 11. For instance, at the intermediate bar 13, a fastening member 24, here a screw, has been inserted through the hole 23 and received in as well as engaged with, here threaded into, one of the connection grooves 18, 19, from the end of the connection groove 18, 19. This mounting is easily done by simply screwing the screw into the groove 18, 19, which has an internal diameter that is slightly less than the outer diameter of the thread of the screw 24. The aluminum is soft enough to admit this, and additionally the screw 24 can be designed to have a particular cutting thread. The width of the mouth 25, 26, 27 of each connection groove 18-21 is smaller than the largest width of the connection groove 18-21. The connection grooves 18-21 are used for connecting cover elements 28, 29, 30 having complementary connection elements which are designed to be received in the grooves. For instance the complementary connection element, in cross-section can have a bulb shape or the like. Typically, a cover element 28-30 is connected with a bar by sliding the complementary element into the groove from one of its ends. Then the bar and cover element assembly is connected with the side bars 12. In the figures some examples of cover elements and their mutual positions are shown. In a first barrier panel embodiment 2, the barrier panel 2 has two intermediate bars 13, and one cover element, which is a toe board 28, arranged between a lower one of the intermediate bars 13 and the bottom bar 11 and engaged with the bottom connection groove 19 of the intermediate bar 13 and the top connection groove 21 of the bottom bar 11. The openings between the intermediate bars 13 and between the top bar 10 and an upper one of the intermediate bars 13 are uncovered. A second barrier panel embodiment 3 has the same parts as the first barrier panel embodiment, and additionally a lower mesh section 29a arranged between the intermediate bars 13, and a similar upper mesh section 29b, arranged between the upper one of the intermediate bars 13 and the top bar 10. A third barrier panel embodiment 4 has one intermediate bar 13, a toe board 28, and a mesh section 30 arranged between the top bar 10 and the intermediate bar 13. Furthermore, according to embodiments of the barrier panel 2-4, each side bar 12 is provided with at least one friction element 35, e.g. two friction elements 35 as shown in Figure 7, on its inner surface 36 facing the opposite side bar. Here the side bar 12 is provided with a groove 37 extending along the length thereof at said inner surface 36, having a primary function of connecting mesh, plastic or other types of infill to the side of the frame. The friction elements 35 are provided as parallel ribs at either side of the groove 37 and extend along the whole length of the side bar 12. The friction elements are arranged to engage with an end surface 38, 39 of each bar 10, 11, 13, which is connected with the side bar 12. The height of the friction elements 35 is low, they are merely like ribs slightly raised from the surface, i.e. like a surface pattern. The friction elements 35 raise the resistance against turning of the horizontal bar 10, 11, 13, when only one fastening element 24, in particular a screw, is used. The use of a single fastening element 24 is advantageous in that it is simpler to prepare the end of the horizontal bar 10, 11, 13 for one fastening element than two or more. As mentioned above, also plastic materials are employable, at least for the toe board 28, which can be a plastic plate, and in particular a corrugated plastic plate. Properly oriented the corrugated plastic is strong enough already at thin and light dimensions, counted as weight per area unit. In order to support the flexibility of the system while keeping the number of parts down, according to this invention adjustable panel supports 42, 43 are provided, as shown in Figures 11-13. The panel holder 6 is capable of supporting many different kinds of edge protection members, such as the barrier panels 2-4, more particularly the aluminum bars 10, 12 thereof, the rails 9, and any combination of them, from a single bar 10, 12, which is the thinnest alternative, to two rails 9, which is the thickest alternative of these edge protection members. Hence, the first embodiment of the panel holder 6 comprises a post slider 40, movably arrangeable at a post 5 to extend in parallel with the post, and arranged to be locked in an arbitrary position along the post 5. The post slider 40 comprises an elongated guide portion 41, and upper and lower post engagement portions 43, 44, respectively arranged at top and bottom end portions 45, 46 of the guide portion 41. The guide portion 41 is plate shaped and is arranged to be received in a groove 85, which extends along the length of the post 5 at one side thereof. More particularly, the post 5 is rectangular in cross-section and has a longitudinal flange 86 at each of its corners, see Figure 17. The flanges 86 are arranged in pairs at opposite sides of the post 5, and protrude from a base surface 87 of the post, thereby defining the groove 85 between them. In other words the post 5 has two opposite grooves 85, at opposite sides of the post 5. Each one of the upper and lower post engagement portions 43, 44 extends around the post when mounted, and comprises a respective channel portion 55, 56 generally U-shaped in cross-section, which is for instance obtained by bending a plate. Thus, referring to the upper channel portion 55, it has three walls; a base wall 57, and first and second side walls 58, 59, which are opposite to each other. Furthermore, it comprises a locking element 60, which is engaged with the side walls 58, 59, and is arranged to clamp them towards each other, and thus clamp the post 5 between them, to thereby lock the panel holder 6 in the chosen position. Like in this embodiment the locking element 60 can simply be a screw extending through holes of the first and second side walls 58, 59 and through a nut 66 attached to the second wall 59 in alignment with the hole. The lower channel portion 56 is similar to the upper channel portion 55, having a base wall 61 and side walls 62, 63, but instead of having a locking element connecting the side walls 62, 63, it has a general connection element 64 just closing the opening between the side walls 62, 63, since it has appeared that the upper locking element generates enough locking force to prevent the panel holder 6 from moving unintentionally. Two panel supports 47, 48 are connected with the post slider 40 at a distance from each other. More particularly, the panel supports 47, 48 are connected with the upper and lower post engagement portions 43, 44, respectively. Each panel support 47, 48 comprises an adjustable clamping element 49, 50 and an adjustment element 51, 52 arranged to change the distance between the clamping element 49, 50 and the post slider 40. Each clamping element 49, 50 comprises a horizontal elongated support portion 91, 92, on which the barrier panels/rails are to rest, and a vertical tongue portion 93, 94 attached to one end of the support portion 91, 92. The support portion 91, 92 is longitudinally displaceably connected with the post engagement portion 43, 44. The support portion 91, 92 is channel shaped, having its opening turned sideways towards the first wall 58, 62 of the channel portion 55, 56. Each one of the upper and lower post engagement portions 43, 44 comprises a panel clamping surface 53, 54 positioned opposite of the tongue portion 93, 94 of the clamping element 49, 50, and the barrier panels/rails are clamped between them by operating the adjustment element 51, 52 for displacing the clamping element 49, 50 relative to the post engagement portion 43, 44. In this embodiment, the adjustment element of each panel support 47, 48 is a screw, which is rotationally connected with the support portion 91, 92, and is in threaded engagement with a sleeve 95, 96 which is comprised in the post engagement portion 43, 44. The post engagement portion 43, 44 comprises an angle bar 97, 98 attached to the first side wall 58, 62 at the outside thereof. The angle bar 97, 98 includes a vertical wall portion containing the clamp surface 53, 54, which is placed adjacent to the base wall 57, 61 and extends in the same plane as the base wall, and a bottom plate portion 99, 100 extending perpendicular to the clamp surface 53, 54. The sleeve 95 is attached to the outside of the first wall 58, 62, and the support portion 91, 92 extends adjacent to and in parallel with the first side wall 58, 62. The sleeve 95, 96 is received in the groove formed by the walls of the support portion 91, 92. The screw 51, 52 is longitudinally fixed relative to the support portion 91, 92, and extends along the full length of the support portion 91, 92. Thus, when the screw 51, 52 is operated it brings the clamping element 49, 50 along with it, while the support portion 91, 92 slides along the sleeve 95, 96, thereby adjusting the distance between the tongue portion 93, 94 and the clamp surface 53, 54 of the post engagement portion 43, 44. Thus, when mounting the temporary edge protection, the panel holder 6 is mounted on a post 5 by slipping the post engagement portions 43, 44 onto the post 5 from one end thereof, such that the guide element 41 is received in a corresponding groove 85 extending along the post 5. Then the panel holder 6 is moved to the desired position along the post 5, and the locking element 60 is tightened. The barrier panel(s) and/or rail(s) are placed on the panel supports 47, 48, i.e. they are received in the space between the clamping elements 49, 50 and the panel clamping surfaces 53, 54. Then the adjustment elements 51, 52 are operated to fix the barrier panels/rails by reducing the space and thus clamp the barrier panels/rails between the clamping elements 49, 50 and the post slider 40. According to another embodiment of the panel holder 110, as shown in Figure 18, similar to the above embodiment, it comprises a post slider 111, having an elongated guide portion 112 and upper and lower port engagement portions 113, 114 arranged at end portions of the guide element; and upper and lower panel supports 115, 116 connected with a respective one of the post engagement portions 113, 114. However, each panel holder 115, 116 comprises a bracket 117, 118, which protrudes from the base wall 119, 120 of the channel portion 121, 122 of the post engagement portion 113, 114. The legs of the bracket 117, 118 are substantially longer than its width. The panel holder comprises an adjustment element 123, 124, which is a screw extending within the bracket 117, 118. The screw 123, 124 is rotatable and has a fixed longitudinal position, by extending through a hole of the bracket portion 125, 126 joining the legs at the outer ends thereof, and a hole of an opposite cross wall 127, 128 extending between the legs close to the base wall 119, 120 of the post slider 112, and having a screw head and a fixed nut at its respective ends. The clamping element 129, 130 is engaged with the threads of the screw 123, 124, and is limited in its lateral movement by the legs of the bracket 117, 118, thereby moving along the screw 123, 124 when the screw is rotated. The barrier panels/rails are clamped between the clamping element 129, 130 and the base wall 119, 120. Referring to Figures 14 to 16, the post holder 7 comprises an elongated vertical post retaining portion 67, and a base support portion 68 protruding horizontally from the post retaining portion 67, and arranged to rest on the base 8. The post retaining portion 67 is generally channel-shaped and has a bottom wall 80, and opposite side walls 81 raising from the bottom wall 80, the side walls 81 having a J-shaped cross-section. Thus, when the post 5 is in a mounted state, the edges of the side walls 81 are engaged with two flanges 86, a portion of the post 5 thus extending through the post retaining portion 67. The post 5 has a snap lock device 71, which comprises a spring biased locking pin 72, which is received in a recess 73 of the post holder when the post 5 is in the mounted state. This kind of post shape and connection of the post holder 7 and the post 5 is advantageous in that the opposite side of the post, having a similar groove shape, is free to use in the full length of the post for connecting other parts. Furthermore, the post holder 7 comprises a post tightening assembly 70. The post tightening assembly 70 comprises a movable element 74 and a fixed element 75, wherein the movable element 74 is arranged to exert a tightening force on a surface 76 of the post 5 when moved to a tightening position. The surface 76 extends between the flanges 86 that the side wall edges of the post holder 7 are engaged with. It should be noted that this post surface 76 is typically opposite to the above mentioned post surface 63 facing the panel holder 6. That is, the post holder 7 and the panel holder 6 are mounted on opposite sides of the post 5. The movable element 74 constitutes a filling piece between the fixed element 75 and the surface 76 of the post 5. The fixed element 75 is arranged within the post retaining portion 67. The fixed element 75 comprises a guide surface 84, which is inclined relative to the surface 76 of the post, and relative to the bottom wall 80. The movable element 74 is vertically adjusted by means of a tightening screw 82, which is arranged in a fixed nut element 83, and which is loosely connected with the movable element 74. The nut element is arranged at an outside of the post retaining portion 67, and the movable element 74, constituted by a bent plate, extends into the retaining portion 67 from an upper end thereof, and abuts against the guide surface 84 of the fixed element 75. When tightening the tightening screw 82, the movable element 74 is forced downwards between the guide surface 84 and the surface 76 of the post 5 like a wedge. Thereby the post 5, and more particularly the flanges 86 thereof, is pushed against the edges of the side walls 81 of the post retaining portion 67. The post tightening assembly is eqully applicable for other post shapes, such as a conventional tube shaped post, rectangular or circular, which is received in a slightly wider, tube portion of the post holder. That is, the tube portion of the post holder can be provided with a similar arrangement of fixed and movable parts and inclined surface(s), as understood by the person skilled in the art.

1. A barrier panel for a temporary edge protection system, the barrier panel (2-4) comprising a set of aluminum bars including a top bar (10), a bottom bar (11), two side bars (12), and an intermediate bar (13), wherein the side bars are connected at their ends (14, 16) with first respectively second ends (15, 17) of the top and bottom bars to form a rectangular section, wherein the intermediate bar is attached to the side bars between the top and bottom bars, wherein the intermediate bar is provided with a top connection groove (18) extending along its length and facing the top bar, and a bottom connection groove (19) extending along its length and facing the bottom bar, wherein each side bar is provided with several bar attachment portions (22) spaced along the side bar.

2. The barrier panel according to claim 1, wherein each bar attachment portion (22) comprises a through hole (23) extending in parallel with the top bar (10). 3. The barrier panel according to claim 1 or 2, wherein the width of the mouth (25) of each connection groove (18, 19) is smaller than the largest width of the connection groove. 4. The barrier panel according to any one of the preceding claims, further comprising fastening members (24), wherein a first fastening member is engaged with one of the side bars (12) at a bar attachment portion (22) thereof, and is received in and engaged with one of the connection grooves (18, 19) of the intermediate bar (13) at one end thereof, and wherein a second fastening member (24) is engaged with the other side bar (12) at a bar attachment portion (22) thereof, and is received in and engaged with one of the connection grooves (18, 19) of the intermediate bar at the other end thereof. 5. The barrier panel according to any one of the preceding claims,: wherein each side bar (12) is provided with at least one friction element (35) on its surface (36) facing the opposite side bar, said at least one friction element being arranged to engage with an end surface (38, 39) of a bar (10-13) which is connected with the side bar. 6. The barrier panel according to claim 5, said at least one friction element (35) comprising a rib (35) extending along the length of the side bar (12). 7. The barrier panel according to any one of the preceding claims, further comprising a toe board (28) arranged between an intermediate bar (13) and the bottom bar (11) and engaged with a bottom connection groove (19) of the intermediate bar and a top connection groove (21) of the bottom bar. 8. The barrier panel according to claim 7, wherein the toe board (28) is a plastic plate. 9. The barrier panel according to claim 8, wherein the toe board (28) is made of corrugated plastic. 10. A temporary edge protection system comprising a barrier panel according to any one of the preceding claims, further comprising a post holder (7) being arranged to be provided on a base (8), and to receive a post (5), wherein the post holder comprises a post tightening assembly (70). 11. The temporary edge protection system according to claim 10,: wherein the post tightening assembly (70) comprises a movable element (74) and a fixed element (75), wherein the movable element is arranged to exert a tightening force on a surface (76) of the post when moved to a tightening position, wherein the movable element constitutes a filling piece between the fixed element and the surface, and wherein at least one of the movable element and the fixed element comprises a guide surface (84), which is inclined relative to the surface of the post. 12. A temporary edge protection system comprising a barrier panel according to any one of claims 1 to 9, further comprising a panel holder (6, 110) adjustably mountable on a post, wherein the panel holder comprises an elongate post slider (40, 111), movably arrangeable at the post to extend in parallel with the post, and two panel supports (47, 48, 115, 116), attached to the post slider at a distance from each other, each panel support comprising a an adjustable clamping element (49, 50, 129, 130), and an adjusting element (51, 52, 123, 124) arranged to change the distance between the clamping element and the post slider. 13. The temporary edge protection system according to claim 12, each panel support (47, 48, 115, 116) comprises a horizontal elongated support portion (91, 92, 117, 118), on which the edge protection members (2-4, 9) are to rest, and a vertical tongue portion (93, 94, 129, 130) arranged to clamp the edge protection members (2-4, 9) against a clamp surface (53, 54, 119, 120) of the post slider (40, 111). 14. The temporary edge protection system according to claim 12 or 13, wherein the post slider (40, 111) comprises an elongated guide portion (41, 112), and upper and lower post engagement portions (43, 44, 121, 122) respectively arranged at top and bottom end portions (45, 46) of the guide portion (41, 112), wherein the support portion (91, 92) is comprised in the clamping element (49, 50), wherein the tongue portion (93, 94) is attached to the support portion, and wherein the support portion is longitudinally displaceably connected with the post engagement portion (43, 44). 15. The temporary edge protection system according to any one of claims 12 to 14, further comprising a post holder (7) arranged to be provided on a base (8), wherein the post holder comprises a post tightening assembly (70).

2870905

Vacuum cleaner noise and vibration reduction system

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an embodiment of the noise reducing assembly and the vibration reducing assembly according to the invention. Figure 2 shows a view of a cross section perpendicular to the plane of Figure 1. Figure 3 illustrates a housing of a vacuum cleaner including the noise reducing assembly and the vibration reducing assembly of Figure 1. Moreover, Figures 4 and 5 illustrate an embodiment of the mounting suspension for a vacuum cleaner motor according to the invention. The embodiment of the invention as shown in Figures 1, 2 and 3 relates to a noise and vibration reduction assembly which effectively reduces the transfer of vibrations and reduces noise caused by operation of the vacuum cleaner motor 11. The operation of the vacuum cleaner appliance 9 causes the noise which is of aerodynamic and structural origin. The vacuum cleaner appliance 9 collects the solid and fluid particles where the airflow is used for their transport from cleaning surfaces to the dust collecting compartment. From the dust collecting compartment the airflow path 6 continues towards the inlet of a noise reduction assembly. This noise reduction assembly includes a motor enclosure 1, 2 that is configured to enclose the vacuum cleaner motor 11, wherein the motor enclosure 1, 2 forms a channel structure around the vacuum cleaner motor 11 for guiding at least a part of an airflow exiting the outlet of the vacuum cleaner motor 11 during use to turn by an angle of 360 ° or more about an axis that is perpendicular to the line between the inlet and the outlet of the vacuum cleaner motor 11. Moreover, this embodiment also includes the vibration reducing assembly according to the invention that comprises the vacuum cleaner motor 11; the motor enclosure 1, 2 enclosing the vacuum cleaner motor 11; and the mounting suspension 3, 4 according to the invention. The mounting suspension 3, 4 is configured for connecting the vacuum cleaner motor 11 to the housing of the vacuum cleaner, and the mounting suspension 3, 4 is further configured for suspending the motor enclosure 1, 2, in particular such that the motor enclosure 1, 2 is only connected to the suspension 3, 4 and the motor enclosure 1, 2 is connected to the motor 11 and the housing of the vacuum cleaner 9 only via the suspension 3, 4. Furthermore, the upper 3 and bottom 4 rubber suspension reduce the transfer of vibrations from the vacuum cleaner motor 11 to the vacuum cleaner appliance 9. The upper suspension rubber 3 guides the airflow 6 to the inlet of the vacuum cleaner motor 11. The airflow 8 exits from the vacuum cleaner motor 11 back into the motor enclosure 1, 2. The airflow 7 is further guided within the noise reduction assembly through the air path formed by the vacuum cleaner motor 11, the motor enclosure housing 1, the upper 3 and bottom 4 suspension rubbers and foam 5. The airflow 7 makes the turn for an angle of 360° to 450° within the noise reduction assembly. The airflow 7 exits from the noise reduction assembly into the vacuum cleaner appliance inner housing 10 and is further guided towards the exit of the vacuum cleaner appliance 9. In the inner housing 10 of the vacuum cleaner, the airflow may be turned by another 90° (upwards), yielding a total of 540°. As an option, additional sound absorbing material can be applied on an arbitrary surface which forms the airflow path 7 within the noise reduction assembly. The upper 3 and bottom 4 rubber suspension elastically attach the motor enclosure, comprising parts 1 (lower) and 2 (upper), to the vacuum cleaner motor 11, where the motor enclosure is not connected to any other part of the vacuum cleaner appliance 9 and can freely move in space. The motor enclosure comprising parts 1 and 2, together with upper 3 and bottom 4 rubber suspensions, form a tuned mass damper. Figure 4 illustrates the detailed structure of the lower part 4 of the mounting suspension 3, 4. Figure 4A is a cross sectional view while Figure 4B is a perspective view. Similarly, Figure 5 illustrates the detailed structure of the upper part 3 of the mounting suspension 3, 4. Figure 5A is a cross sectional view and Figure 5B is a perspective view. The lower suspension 4 of Figure 4 is in this embodiment manufactured as an integral part 4 with two elements thereof having a hollow portion to be connected to respective pins of the housing of the vacuum cleaner 9 shown in Figure 3. Moreover, these elements each have a circumferential protrusion of which the lower part of the motor enclosure, i.e. the capsule housing 1 can be suspended. The upper part 3 of the suspension according to Figure 5 is to be placed between the motor and the capsule cover 2 and thus also suspends the motor enclosure and further suspends the motor to the housing of the vacuum cleaner 9 shown in Figure 3. As shown by the experiment the noise and vibration reduction assembly reduces the noise level by 12 dB compared to the noise level of the vacuum cleaner motor and the vibration level on the motor is reduced by 25%. Some of the existing noise reduction configurations achieve similar or higher level of noise reduction by forcing the airflow through sound absorption foams; however the efficiency of such design drops after some usage time and the noise increases. On the other hand; when using the proposed noise reduction assembly the efficiency and noise level do not change significantly. After normal operational life time of the vacuum cleaner appliance (> 500 hours) the optimal efficiency and optimal noise level change for less than ±1%. #### Short Summary: The vacuum cleaner noise and vibration reduction assembly according to this embodiment of the invention comprises a capsule housing 1, a capsule cover 2, a bottom 4 and an upper 3 suspension rubber and foam 5. The noise reduction assembly effectively reduces aerodynamic and structurally born noise. The noise reduction assembly airflow path makes the airflow exiting from the vacuum cleaner motor to turn for an angle of 360 to 450 degrees within the noise reduction assembly. The rubber suspension assembly reduces the vibration transmission to the vacuum cleaner appliance. The rubber suspension parts are unique, because with one rubber part on each side the motor fixation in the vacuum cleaner appliance is assured and at the same time the noise reduction assembly is attached to the motor. The noise reduction assembly guides the airflow exiting from the vacuum cleaner motor to make a turn of 360 to 450 degrees before exiting into inner housing 10 of the vacuum cleaner appliance 9. Sound absorption foam can optionally be applied to the surface which is normal to the airflow 8 direction exiting the vacuum cleaner motor. Sound absorption foam can optionally be applied in addition so that the airflow flows through it. The sound reduction assembly housing 1 has a cylindrical shape from which the airflow exists only through one opening which is parallel to the bottom of the housing. The upper 3 and bottom 4 rubber suspension together with sound reduction assembly comprising parts 1 and 2, form a harmonic absorber. The housing of the sound reduction assembly is not attached to any part of the vacuum cleaner appliance except through the rubber suspension of the motor.

1. A motor enclosure for a vacuum cleaner motor having an air inlet and an air outlet,: the motor enclosure being configured to enclose the vacuum cleaner motor, wherein the motor enclosure forms a channel structure around the vacuum cleaner motor for guiding at least a part of an airflow exiting the outlet of the vacuum cleaner motor during use to turn by an angle of 360° or more about an axis that is perpendicular to the line between the inlet and the outlet of the vacuum cleaner motor.

2. The motor enclosure of claim 1, wherein the turning angle is in the range of 360 ° to 450° in particular wherein the turning angle is 360° or 450°. 3. The motor enclosure of claim 1 or 2, wherein the motor enclosure comprises one or more baffles to form the channel structure, in particular wherein the material of the one or more baffles comprises foam. 4. The motor enclosure of any one of claims 1 to 3, wherein the motor enclosure comprises a double-walled section forming a part of the channel structure for guiding the airflow having turned by an angle of at least 360°, in particular wherein the double-walled section comprises an outlet for the airflow to exit the motor enclosure. 5. The motor enclosure of any one of claims 1 to 4, further comprising sound absorbing material provided on a surface of the channel, in particular on a surface of the channel that deflects the airflow exiting the outlet of the vacuum cleaner motor. 6. The motor enclosure of any one of claims 1 to 5, wherein the motor enclosure comprises a bottom part for being connected to a bottom part of a mounting suspension and a top part for being connected to a top part of the mounting suspension. 7. A noise reducing assembly for a vacuum cleaner comprising: the motor enclosure according to any one of claims 1 to 6; and the vacuum cleaner motor being enclosed by the motor enclosure. 8. The noise reducing assembly of claim 7, further comprising: the mounting suspension of any one of claims 9 to 14.

2870905

Vacuum cleaner noise and vibration reduction system

Based on the following detailed description of an invention, generate the patent claims. There should be 7 claims in total. The first, independent claim is given and the remaining 6 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an embodiment of the noise reducing assembly and the vibration reducing assembly according to the invention. Figure 2 shows a view of a cross section perpendicular to the plane of Figure 1. Figure 3 illustrates a housing of a vacuum cleaner including the noise reducing assembly and the vibration reducing assembly of Figure 1. Moreover, Figures 4 and 5 illustrate an embodiment of the mounting suspension for a vacuum cleaner motor according to the invention. The embodiment of the invention as shown in Figures 1, 2 and 3 relates to a noise and vibration reduction assembly which effectively reduces the transfer of vibrations and reduces noise caused by operation of the vacuum cleaner motor 11. The operation of the vacuum cleaner appliance 9 causes the noise which is of aerodynamic and structural origin. The vacuum cleaner appliance 9 collects the solid and fluid particles where the airflow is used for their transport from cleaning surfaces to the dust collecting compartment. From the dust collecting compartment the airflow path 6 continues towards the inlet of a noise reduction assembly. This noise reduction assembly includes a motor enclosure 1, 2 that is configured to enclose the vacuum cleaner motor 11, wherein the motor enclosure 1, 2 forms a channel structure around the vacuum cleaner motor 11 for guiding at least a part of an airflow exiting the outlet of the vacuum cleaner motor 11 during use to turn by an angle of 360 ° or more about an axis that is perpendicular to the line between the inlet and the outlet of the vacuum cleaner motor 11. Moreover, this embodiment also includes the vibration reducing assembly according to the invention that comprises the vacuum cleaner motor 11; the motor enclosure 1, 2 enclosing the vacuum cleaner motor 11; and the mounting suspension 3, 4 according to the invention. The mounting suspension 3, 4 is configured for connecting the vacuum cleaner motor 11 to the housing of the vacuum cleaner, and the mounting suspension 3, 4 is further configured for suspending the motor enclosure 1, 2, in particular such that the motor enclosure 1, 2 is only connected to the suspension 3, 4 and the motor enclosure 1, 2 is connected to the motor 11 and the housing of the vacuum cleaner 9 only via the suspension 3, 4. Furthermore, the upper 3 and bottom 4 rubber suspension reduce the transfer of vibrations from the vacuum cleaner motor 11 to the vacuum cleaner appliance 9. The upper suspension rubber 3 guides the airflow 6 to the inlet of the vacuum cleaner motor 11. The airflow 8 exits from the vacuum cleaner motor 11 back into the motor enclosure 1, 2. The airflow 7 is further guided within the noise reduction assembly through the air path formed by the vacuum cleaner motor 11, the motor enclosure housing 1, the upper 3 and bottom 4 suspension rubbers and foam 5. The airflow 7 makes the turn for an angle of 360° to 450° within the noise reduction assembly. The airflow 7 exits from the noise reduction assembly into the vacuum cleaner appliance inner housing 10 and is further guided towards the exit of the vacuum cleaner appliance 9. In the inner housing 10 of the vacuum cleaner, the airflow may be turned by another 90° (upwards), yielding a total of 540°. As an option, additional sound absorbing material can be applied on an arbitrary surface which forms the airflow path 7 within the noise reduction assembly. The upper 3 and bottom 4 rubber suspension elastically attach the motor enclosure, comprising parts 1 (lower) and 2 (upper), to the vacuum cleaner motor 11, where the motor enclosure is not connected to any other part of the vacuum cleaner appliance 9 and can freely move in space. The motor enclosure comprising parts 1 and 2, together with upper 3 and bottom 4 rubber suspensions, form a tuned mass damper. Figure 4 illustrates the detailed structure of the lower part 4 of the mounting suspension 3, 4. Figure 4A is a cross sectional view while Figure 4B is a perspective view. Similarly, Figure 5 illustrates the detailed structure of the upper part 3 of the mounting suspension 3, 4. Figure 5A is a cross sectional view and Figure 5B is a perspective view. The lower suspension 4 of Figure 4 is in this embodiment manufactured as an integral part 4 with two elements thereof having a hollow portion to be connected to respective pins of the housing of the vacuum cleaner 9 shown in Figure 3. Moreover, these elements each have a circumferential protrusion of which the lower part of the motor enclosure, i.e. the capsule housing 1 can be suspended. The upper part 3 of the suspension according to Figure 5 is to be placed between the motor and the capsule cover 2 and thus also suspends the motor enclosure and further suspends the motor to the housing of the vacuum cleaner 9 shown in Figure 3. As shown by the experiment the noise and vibration reduction assembly reduces the noise level by 12 dB compared to the noise level of the vacuum cleaner motor and the vibration level on the motor is reduced by 25%. Some of the existing noise reduction configurations achieve similar or higher level of noise reduction by forcing the airflow through sound absorption foams; however the efficiency of such design drops after some usage time and the noise increases. On the other hand; when using the proposed noise reduction assembly the efficiency and noise level do not change significantly. After normal operational life time of the vacuum cleaner appliance (> 500 hours) the optimal efficiency and optimal noise level change for less than ±1%. #### Short Summary: The vacuum cleaner noise and vibration reduction assembly according to this embodiment of the invention comprises a capsule housing 1, a capsule cover 2, a bottom 4 and an upper 3 suspension rubber and foam 5. The noise reduction assembly effectively reduces aerodynamic and structurally born noise. The noise reduction assembly airflow path makes the airflow exiting from the vacuum cleaner motor to turn for an angle of 360 to 450 degrees within the noise reduction assembly. The rubber suspension assembly reduces the vibration transmission to the vacuum cleaner appliance. The rubber suspension parts are unique, because with one rubber part on each side the motor fixation in the vacuum cleaner appliance is assured and at the same time the noise reduction assembly is attached to the motor. The noise reduction assembly guides the airflow exiting from the vacuum cleaner motor to make a turn of 360 to 450 degrees before exiting into inner housing 10 of the vacuum cleaner appliance 9. Sound absorption foam can optionally be applied to the surface which is normal to the airflow 8 direction exiting the vacuum cleaner motor. Sound absorption foam can optionally be applied in addition so that the airflow flows through it. The sound reduction assembly housing 1 has a cylindrical shape from which the airflow exists only through one opening which is parallel to the bottom of the housing. The upper 3 and bottom 4 rubber suspension together with sound reduction assembly comprising parts 1 and 2, form a harmonic absorber. The housing of the sound reduction assembly is not attached to any part of the vacuum cleaner appliance except through the rubber suspension of the motor.

9. A mounting suspension for a vacuum cleaner motor,: wherein the mounting suspension is configured for connecting a vacuum cleaner motor to a housing of the vacuum cleaner, and: wherein the mounting suspension is further configured for suspending a motor enclosure, in particular such that the motor enclosure is only connected to the suspension and the motor enclosure is connected to the vacuum cleaner motor and the housing of the vacuum cleaner only via the suspension.

10. The mounting suspension of claim 9, wherein the mounting suspension comprises: a bottom part configured to be connected to a bottom section of the vacuum cleaner motor and configured to be connected to a housing of a vacuum cleaner;: and a top part configured to be connected to a top section of the vacuum cleaner motor and configured to be connected to the housing of the vacuum cleaner. 11. The mounting suspension of claim 10, wherein the bottom part of the mounting suspension comprises one, two or more cylindrical elements, each having a circumferential protrusion to which a bottom part of the motor enclosure is connectable. 12. The mounting suspension of any one of claims 9 to 11, wherein the top part of the mounting suspension is configured to be at least partially arranged between a top part of the motor enclosure and the motor. 13. The mounting suspension of any one of claims 9 to 11, wherein the material of the suspension comprises rubber. 14. A vibration reducing assembly for a vacuum cleaner, the vibration reducing assembly comprising: a vacuum cleaner motor; a motor enclosure enclosing the vacuum cleaner motor; and the mounting suspension of any one of claims 9 to 13. 15. A vacuum cleaner, comprising the sound reducing assembly of claim 7 or 8 or the vibration reducing assembly of claim 14.

2870999

Gyratory crusher main shaft and assembly

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to figure 1, a crusher comprises a frame 100 having an upper frame 101 and a lower frame 102. A crushing head 103 is mounted upon an elongate shaft 107 having a longitudinal axis 115. A first (inner) crushing shell 105 is fixably mounted on crushing head 103 and a second (outer) crushing shell 106 is fixably mounted at upper frame 101. A crushing zone 104 is formed between the opposed crushing shells 105, 106. A discharge zone 109 is positioned immediately below crushing zone 104 and is defined, in part, by lower frame 102. A drive (not shown) is coupled to main shaft 107 via a drive shaft 108 and suitable gearing 116 so as to rotate shaft 107 eccentrically about a longitudinal axis 126 of the crusher and to cause head 103 to perform a gyratory pendulum movement and crush material introduced into crushing chamber 104. A first (axial upper) end region 113 of shaft 107 is maintained in a rotatable position by a top-end bearing assembly 112 positioned intermediate between main shaft 107 and a central boss 117. Similarly, a second (axial bottom) end 118 of shaft 107 is supported by a bottom-end bearing assembly 119. Upper frame 101 is divided into an upper frame part (commonly termed a topshell 111) mounted upon lower frame part 102 (commonly termed a bottom shell), and a spider assembly 114 having arms 110 that extend from topshell 111 and represents an upper portion of the crusher. Upper end region 113 comprises a radial taper that defines an upper conical region of main shaft 107. The conical region 113 is tapered so as to decrease in cross sectional area in a direction from shaft second (lower) end 118 to an upper end surface 123 positioned uppermost within the crusher. To avoid excessive wear of the conical region 113, by contact with bearing assembly 112, a substantially cylindrical wear sleeve 124 is mounted over and about region 113. Sleeve 124 is held in position at region 113 by an interference or friction fit and is provided in close touching contact over an axial length of both sleeve 124 and region 113. Accordingly, sleeve 124 is positioned radially intermediate bearing assembly 112 and an outer surface of region 113 to absorb the radial and axial loading forces resultant from the crushing action of the gyratory pendulum movement. To facilitate mounting and dismounting of sleeve 124 at shaft region 113, shaft 107 is configured to enable a fluid to be introduced into the contact region between the sleeve 124 and shaft region 113. In particular, a fluid supply conduit 120 extends axially and radially along shaft 107 (within region 113) from end surface 123 to the contact region between sleeve 124 and region 113. A channel (alternatively termed a groove) 121 is indented within the external facing surface of shaft 107 at region 113 and is provided in fluid communication with conduit 120. Referring to figures 2 to 4 tapered region 113 comprises a lowermost end 300 and an uppermost end 301. The radial taper is uniform along the axial length between ends 300, 301 such that a cross sectional area decreases from lower end 300 to upper end 301 at a uniform rate to define a frusto-conical region (113) of main shaft 107. Sleeve 124 comprises a first (lower) end 216 for mating at the end 300 of region 113 and a second (upper) end 215 for positioning at uppermost end 301 substantially coplanar with shaft end surface 123. Sleeve 124 comprises a radially inward facing surface 201 and a radially outward facing surface 202 with a substantially cylindrical wall 203 defined between surfaces 201, 202. Wall 203 is tapered so as to decrease in radial thickness from uppermost end 215 to lowermost end 216. In particular, external surface 202 is substantially cylindrical whilst internal surface 201 comprises a conical shape profile corresponding to the conical shape profile of main shaft region 113. Region A, illustrated in figure 2, corresponds to a mid-axial length position as defined by the cross sectional area of wall 203 (in a plane extending along axis 115) such that the cross sectional area axially above region A is equal to the cross sectional area axially below region A. Sleeve 124 and in particular radially inward facing surface 201 is mated in close fitting contact with the external facing surface 200 of main shaft region 113 between respective lower (216, 300) and upper (215, 301) ends. Sleeve lower end 216 comprises a chamfer region 207 of decreasing wall thickness such that very a lowermost end region of sleeve 124 is chamfered to sit close to a radius section of main shaft region 113 below region end 300. A disc-like retainer 125 is releasably mounted over shaft end surface 123 during mounting and dismounting of sleeve 124 at main shaft region 113. Retainer 125 comprises a suitable bore 122 aligned coaxially with an end region of conduit 120 to allow fluid to be introduced through retainer 125 to groove 121 via conduit 120. Retaining disc 125 comprises a plurality of perimeter bores 214 distributed circumferentially around retainer 125 immediately inside of a perimeter 209. Bores 214 are configured to receive attachment bolts (not shown) received within corresponding bores (not shown) extending axially from sleeve upper end 215 so as to lock retainer 125 to sleeve 124 during mounting and dismounting procedures. Retainer 125 further comprises a plurality of additional bores 213 positioned radially inside perimeter bores 214 that are configured to receive attachment bolts (not shown) to secure retainer 125 to main shaft region 113. In particular, an underside surface 211 of retainer 125 is positioned in contact and aligned substantially coplanar with the shaft end surface 123. In this orientation, an upward facing retainer surface 212 is orientated away from main shaft 107. An annular recess 210 extends circumferentially around retainer perimeter 209 and is indented in surface 211 so as to create a small axially and radially extending annular gap region immediately axially above the annular sleeve end 215. Accordingly, during a sleeve dismounting operation, the sleeve attachment bolts (not shown) are removed. Sleeve 124 is capable of sliding axially into the gap region defined by recess 210 to contact the underside surface 211 (at the recess 210) when fluid pressure is applied. In an alternative mounting operation, retainer 125 is inverted such that disc surface 212 is mated against sleeve end 215 and main shaft end surface 123 to force sleeve 124 axially over and about region 113 as the attachment bolts (not shown) are tightened. Fluid supply conduit 120 comprises an axial section 204 extending downwardly from end surface 123. A lowermost end 206 of axial section 204 is terminated by a radially extending section 205 that terminates at shaft external facing surface 200. A radially outermost end of the conduit section 205 is provided in fluid communication with an axially upper groove 121a that extends circumferentially around shaft region 113. According to the specific implementation, conical region 113 further comprises a second circumferentially extending groove 121b axially separated from the first upper groove 121a by a distance approximately half the axial length of region 113 and sleeve 124. Additionally, each groove 121a, 121b is spaced axially from region A by an equal axial distance. Grooves 121a and 121b also extend the full 360° circumference of shaft surface 200. An interconnecting fluid flow channel 208 extends axially from upper groove 121a to lower groove 121b to provide fluid communication between the two grooves 121a, 121b. According to further specific implementations, region 113 may comprise a plurality of interconnecting fluid flow channels 208 distributed circumferentially around surface 200. According to yet further embodiments, region 113 may comprise a single circumferentially extending groove optionally in the form of at least one spiral or helix. According to a further embodiment, external facing surface 200 may comprise a network of grooves orientated and extending axially parallel or transverse to axis 115 and/or in a circumferential direction entirely or partly around the conical surface 200. The subject invention is compatible for use with conventional fluid supply systems (comprising reservoirs, pumps, conduits, seals etc.) coupled to bore 122 via suitable enclosures or conduits. Accordingly, a fluid is capable of being delivered to grooves 121a, 121b via supply conduits 120, 208 to lubricate the interface between shaft surface 200 and sleeve surface 201. Such an arrangement facilitates both a slide mounting of sleeve 124 and imparts a radial expansion force (to sleeve 124) to promote sleeve demounting. According to further specific embodiments, shaft region 113 may be devoid of conduit 120 such that sleeve 124 comprises a conduit bore extending through sleeve wall 203 in fluid communication with grooves 121a, 121b and/or channel 208.

1. A gyratory crusher main shaft (107) comprising: a shaft body having a radially outward facing external surface (200) and having a first end (118) for positioning at a lower region of the crusher and a second end (123) for positioning at an upper region of the crusher relative to the first end (118); an axial region (113) of the shaft body extending from the second end (123) is tapered relative to a longitudinal axis (115) of the shaft body such that a cross sectional area of the shaft body at the tapered region (113) decreases in a direction from the first end (118) to the second end (123), the tapered region (113) configured to mount a shaft sleeve (124); characterised by: at least one groove (121) indented at the external surface (200) and positioned at the tapered region (113) and capable of receiving a pressurised fluid to facilitate mounting and dismounting of the sleeve (124) at the shaft body.

2. The main shaft as claimed in claim 1 further comprising a fluid inlet conduit (120) extending axially from the second end (123) and provided in fluid communication with the groove (121) to allow a fluid to be supplied to the groove (121) from the second end (123). 3. The main shaft as claimed in claim 2 wherein the conduit (120) extends internally within the shaft body such that a part (205) of the conduit (120) extends radially outward to the groove (121). 4. The main shaft as claimed in claim 3 wherein the groove (121) extends in a circumferential direction around the shaft body. 5. The main shaft as claimed in claim 4 wherein the groove (121) extends substantially completely circumferentially around the shaft body. 6. The main shaft as claimed in claim 5 comprising a plurality of grooves (121a, 121b) at the external surface (200). 7. The apparatus as claimed in claim 6 comprising a first groove (121a) extending in a circumferential direction around the shaft body and second groove (121b) extending in a circumferential direction around the shaft body, the first groove (121a) separated axially from the second groove (121b) and coupled in fluid communication. 8. The main shaft as claimed in claim 7 wherein at least a part of the conduit (120) is indented and extends axially at the external surface (200) as a channel (208) to couple the first (121a) and second (121b) grooves in fluid communication. 9. A gyratory crusher main shaft assembly comprising: a shaft body as claimed in any preceding claim; a sleeve (124) fitted over the tapered region (113), the sleeve (124) having a tapered wall thickness such that a wall thickness at a second upper end (215) of the sleeve (124) is greater than a wall thickness at a first lower end (216) of the sleeve(124). 10. The assembly as claimed in claim 9 further comprising an end retainer (125) releasably mounted at the second end (123) of a shaft body and having a perimeter region (209) extending radially outward beyond the external surface (200) at the tapered region (113), the perimeter region (209) positioned to radially overlap the sleeve (124) at the second end (215) of the sleeve (124) to inhibit axial separation of the sleeve (124) from the shaft body. 11. The assembly as claimed in claim 10 wherein the retainer (125) comprises a disc-like configuration having a recess (210) extending circumferentially at the perimeter region (209) to allow axial movement of the sleeve (124) into the recess (210). 12. The assembly as claimed in any one of claims 9 to 11 further comprising a fluid inlet conduit (120) extending axially from the second end (123) of the shaft body in fluid communication with the groove (121) to allow a fluid to be supplied to the groove (121) from the second end (123). 13. The assembly as claimed in any one of claims 9 to 11 further comprising a fluid inlet conduit extending radially through the wall (203) of the sleeve (124) in fluid communication with the groove (121) to allow a fluid to be supplied to the groove (121) through the sleeve (124). 14. A gyratory crusher comprising a main shaft or main shaft assembly as claimed in any preceding claim.

2871864

Battery assembly for a hearing device and associated method

Based on the following detailed description of an invention, generate the patent claims. There should be 12 claims in total. The first, independent claim is given and the remaining 11 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The disclosed battery assembly enables a user to use a rechargeable hearing device even when the rechargeable battery in the hearing device runs out by providing a secondary power supply that is easy and convenient to use for a hearing device user. The electronic circuit comprises a first input terminal or input node and a second input terminal or input node. The first input terminal is connected, connectable or configured to connect to a first output terminal of a direct current (DC) source, and the second input terminal is connected, connectable or configured to connect to a second output terminal of the DC source. The input terminals may be connectable or configured to connect to the DC source via a number of pads connected to the input terminals via input electrodes. The electronic circuit comprises one or more output terminals or nodes including a first output terminal and optionally a second output terminal. First and second output terminals of the electronic circuit may be connected to respective ends or points of the first electrode forming an inductive coil. The electronic circuit may comprise an oscillator for converting DC from the DC source to alternating current (AC). The oscillator may be configured to provide an output signal with a frequency in the range from 125 kHz to 15 MHz. The battery assembly may comprise one or more first pads connected to the first input terminal of the electronic circuit via first input electrode(s). The battery assembly may comprise one or more second pads connected to the second input terminal of the electronic circuit via second input electrode(s). The battery assembly may comprise a primary second pad, a secondary second pad and optionally a tertiary second pad each connected to the second input terminal via second input electrode(s). A pad facilitates electrical connection between an input terminal of the electronic circuit and an output terminal of the DC source for feeding power from the DC source to the electronic circuit. The first attachment member may be a first adhesive layer or part. A first adhesive layer or part on a first surface of the battery assembly enables removable attachment of the battery assembly to a hearing device housing. The first adhesive layer may cover or at least partly cover the first inductive coil, e.g. for ensuring accurate and stable positioning of the inductive coil in relation to an inductive charging or power coil of the hearing device. The first adhesive layer for attaching the battery assembly to a hearing device housing may be arranged on the first surface or a second surface of the main part. The first attachment member may be the first adhesive layer. The first attachment member may be a resilient spring clamp configured for fitting partially or completely around the hearing device housing of the hearing device. The first attachment member may be an engagement member configured for engaging the hearing device housing and fitting partially or completely around the hearing device housing of the hearing device. The first attachment member may comprise an elastic band or strap. The battery assembly may comprise one or more removable protective sheets, including a first protective sheet. The first protective sheet may cover or at least partly cover the first adhesive layer. The purpose of the removable first protective sheet may be that the user may handle the battery assembly without the first adhesive layer being exposed, and when the user wishes to attach the battery assembly to the hearing device, the first adhesive layer can be exposed by removal of the first protective sheet and the battery assembly can then be attached to the hearing device. The direct current source may be any direct current source, such as a battery. The direct current source may be any type of battery. The battery may be of the same type as conventionally used in hearing devices, e.g. a zinc-air battery. The DC source may provide a supply voltage in the range from 1.1 V to 3 V. Some batteries, e.g. zinc-air batteries, aluminum-air batteries or lithium-air batteries, rely on a reaction with oxygen, and may be activated by unsealing or revealing activation opening(s) to let air into the battery. Thus, the direct current source may be a battery having a housing with one or more activation openings. The one or more activation openings may be sealed with a battery activation tab. The one or more activation openings may alternatively or additionally be sealed and/or covered by a part of the main part, e.g. the primary part of the first surface with the first attachment member, such as the first adhesive layer. In an exemplary battery assembly, the main part of the battery assembly may be in the form of a sheet. The battery assembly may also be configured for holding or attaching a DC source to the sheet or the battery assembly may comprise a DC source. The battery assembly may comprise one or more second attachment members for attaching the DC source to the battery assembly and/or providing electrical contact between pad(s) and output terminal(s) of the DC source. The one or more second attachment members may include one or more second adhesive layers. The second adhesive layer or second adhesive layers, such as a primary second adhesive layer and/or a secondary second adhesive layer may each be configured for electrically connecting a pad or an input terminal of the plurality of input terminals of the electronic circuit to an output terminal of the direct current source. Hence, the direct current source may be fixed to the battery assembly by the second adhesive layer(s). The primary second adhesive layer or the secondary second adhesive layer may be integrated in the first adhesive layer. The second attachment member may be a battery seat or compartment with electrical connector members or pads connected to the first input terminal and the second input terminal, respectively. The battery seat or compartment may be configured for holding a battery or other DC source, e.g. in a press-fit engagement. In exemplary battery assemblies, the second attachment member fix the direct current source to the battery assembly, e.g. the first and/or second output terminals of the direct current source is fixed to the battery assembly. For example, electrically conductive glue or other fastener, may be used for fixing the DC source to the battery assembly and forming electrical connections between respective output terminals and pads. The battery assembly may comprise a plurality of removable protective sheets, including the removable first protective sheet and optionally removable second protective sheet(s). The removable second protective sheet(s) may cover the second adhesive layer(s). Hence before use, the user may handle the battery assembly without exposing the second adhesive layer(s). When the direct current source is ready to be attached to the sheet and/or ready to be activated, the user may remove the second protective sheet, thereby exposing the second adhesive layer in order to affix an input terminal of the electronic circuit to an output terminal of the direct current source. A single protective sheet, e.g. the first protective sheet, may cover the first adhesive layer and the second adhesive layer(s). The removable second protective sheet may include a plurality of removable second protective sheets, such as a primary second protective sheet, a secondary second protective sheet and/or a tertiary second protective sheet. Each of the plurality of removable second protective sheets may cover one of the plurality of second adhesive layers. Whether second protective sheets are employed depends on whether a DC source is pre-attached or not. One or more second protective sheets, e.g. all second protective sheets, are optional and may be dispensed with in case of a DC source being pre-attached to the battery assembly. To allow an electrical connection between an input terminal of the electronic circuit and an output terminal of the direct current source, the second adhesive layer may be made of an electrically conducting material. Alternatively, the second adhesive layer(s) may leave a part of the input terminals/pads exposed, such that an electrical connection is possible even if the second adhesive layer is made of an electrically insulating material. The battery assembly may comprise an activation part between an input terminal of the electronic circuit and an output terminal of the direct current source. The activation part may be an electrically insulating layer between an input terminal of the electronic circuit and an output terminal of the direct current source. Hence, unintentional discharging of the direct current source before use is avoided or at least limited. In an exemplary battery assembly, the first adhesive layer may adhere to the direct current source. Hence, the first adhesive layer may be configured to adhere to the hearing device and to the direct current source. This may lower production costs, since a single adhesive layer, i.e. the first adhesive layer, can be applied to a substantial part of the first and/or second surface. The first adhesive layer may be an adhesive that allows the battery assembly to be detached from the hearing device after use. The second adhesive layer may be an adhesive that do not allow easy detachment. Hence, the second adhesive layer may prevent easy detachment of the direct current source from the battery assembly. This may be beneficial to ensure a firm connection between an input terminal of the electronic circuit and an output terminal of the direct current source, and to eliminate or at least limit the risk of the direct current source unintentionally detaching from the battery assembly. The main part may be a printed circuit board. Hence, manufacturing is easy and production costs can be lowered. If the main part is embodied as a sheet, the sheet may be a printed circuit board. The main part may be an elongated sheet having a first end and a second end. The sheet and/or the main part may have a length in the range from 10 mm to 50 mm. The sheet and/or the main part may have a shape selected from T-shaped, L-shaped, I-shaped or cross-shaped. Different shapes may be beneficial for different purposes, and may further be a compromise between reliability and production costs. The sheet and/or the main part may comprise one or more folding lines including a first folding line. One or more of the folding lines, e.g. the first folding line, may be configured to bring an input terminal of the electronic circuit in contact with an output terminal of the direct current source. In an exemplary battery assembly, the first folding line may be configured to bring the second input terminal in contact with the second output terminal. The sheet and/or the main part may comprise a plurality of folding lines including the first folding line, a second folding line, a third folding line, a fourth folding line and/or a fifth folding line. In an exemplary battery assembly, the first folding line may be configured to bring a second primary input terminal in contact with the second output terminal, and a second folding line may be configured to bring a second secondary input terminal in contact with the second output terminal. The direct current source and the sheet may be bundled together, or distributed individually. The battery assembly may be provided together with the direct current source. Alternatively, the battery assembly may be provided without the direct current source, and thus be configured to receive a direct current source. Further, a method for powering a hearing device is disclosed. The method comprises: providing a battery assembly as described herein; optionally attaching the direct current source to the main part of the battery assembly; and activating the direct current source. The method may further comprise attaching the battery assembly to the hearing device, e.g. to a hearing device housing of the hearing device. Activating the DC source may comprise connecting one or more output terminals, e.g. the second output terminal and/or the first output terminal, of the DC source with a pad of the battery assembly. Activating the DC source may comprise removing or peeling off a battery activation tab from the DC source. Activating the DC source may comprise removing or peeling of one or more protective sheets of the battery assembly. Attaching the battery assembly to the hearing device may comprise attaching the first attachment member to the hearing device housing. Attaching the battery assembly to the hearing device may comprise aligning the first inductive coil with an inductive coil of the hearing device. Attaching the battery assembly to the hearing device may comprise exposing a first adhesive layer, e.g. by removing a first protective sheet covering the first adhesive layer. Figure 1 schematically illustrates an exemplary hearing device system 1 comprising a hearing device 3 with an exemplary battery assembly 2 attached thereto. The battery assembly 2 comprises a main part 4A in the form of a sheet 4, an electronic circuit 22, and optionally a direct current source 12 attached to or attachable to the sheet 4. The DC source 12 has a first output terminal 16 and a second output terminal 18 and may be attached to the sheet during manufacture or by the user prior to attachment to a hearing device. A first attachment member (not shown), such as a first adhesive layer on at least a primary part of the first surface, affix the sheet/battery assembly to the hearing device 3. The sheet 4 has a first surface 6 and a second surface 8 and comprises a first electrode 10 formed as an inductive coil 11. The electronic circuit 22 has a first input terminal 23 and a second input terminal 27 that are connected to the direct current source 12 via first pad 24 and second pad 26. The electronic circuit 22 converts direct current from the direct current source 12 to alternating current in the inductive coil 11. The alternating current in the inductive coil 11 generates an alternating magnetic field that induces electromagnetic power in an inductive coil (not shown) in the hearing device 3 when the inductive coil 11 of the battery assembly 2 is in close vicinity of the inductive coil in the hearing device 3. The illustration in Figure 1 depicts the battery assembly 2 with an attached direct current source 12, here exemplified as a button cell battery. The battery assembly 2 is attached to the hearing device 3 and creates an inductive coupling between the inductive coil 11 of the battery assembly 2 and an inductive coil (not shown) of the hearing device 3. Hence, the battery assembly 2 allows the direct current source 12 to power and/or charge the hearing device 3 via an inductive coupling. A user may on a daily basis charge an internal battery of the hearing device 3. However, the internal battery (not shown) of the hearing device 3 may run out of power while no inductive charger is available, or the hearing device is in use. If the internal battery should run out of power, the battery assembly 2 can easily and conveniently be attached to the hearing device 3 as shown. The hearing device 3 is then able, via an inductive coupling, to be powered by power provided by the direct current source 12. Figure 2 schematically illustrates an exemplary battery assembly 2. The battery assembly comprises a main part 4A in the form of a sheet 4 and a direct current source 12. The direct current source 12 comprises a housing 14 and has a first output terminal 16 and a second output terminal 18. The battery assembly 2 comprises an electronic circuit 22 having a first input terminal 23 and a second input terminal 27. The first input terminal 23 is connected to the first output terminal 16 of the direct current source 12 via a first pad 24. The first output terminal 16 is glued or fastened to the sheet 4 with an electrically conductive glue or other fastener, which attaches the DC source 12 to the sheet 4 and electrically connects the first pad 24 and the first output terminal 16. The second input terminal 27 is connectable to the second output terminal 18 of the direct current source 12 via second pad 26. The electronic circuit 22 is connected to the first pad 24 and second pad 26 for converting direct current from the direct current source 12 to alternating current in the inductive coil 11. In Figure 2, the second input terminal 27 is connected to the second output terminal 18 by performing a folding of the sheet 4 along a first folding line 28 as shown by the arrow. The battery assembly 2 in Figure 2 comprises a first attachment member 19 in the form of a first adhesive layer 20 and a second attachment member 21' in the form of a second adhesive layer 21. The second adhesive layer 21 is adapted to adhere to the direct current source 12 and to electrically connect the second output terminal 18 and the second pad 26 by contact and/or via electrically conductive second adhesive layer 21. A first protective sheet 34 covers and protects the first adhesive layer 20 prior to use. The first protective sheet 34 is removed when a user wishes to attach the battery assembly to a hearing device. A second protective sheet 36 covers and protects the second adhesive layer 21 prior to use. The second protective sheet 36 is removed when a user wishes to activate the battery assembly/DC source. Figure 3 schematically illustrates an exemplary battery assembly 2 with a main part 4A formed as an I-shaped sheet 4. The direct current source 12 is in Figure 3 exemplified as a battery that is activated by air and comprises a battery activation tab 13 sealing one or more activation openings in the housing 14. Upon removal of the battery activation tab 13 air is allowed to enter the activation openings of the housing 14, thus activating the battery 12. The battery assembly 2 comprises two second adhesive layers 21A and 21 B configured for adhering the direct current source 12 to the sheet 4. Further, the primary second adhesive layer 21A electrically connects the first pad 24 and the first output terminal 16 of the battery 12, and the secondary second adhesive layer 21 B electrically connects the second pad 26 and the second output terminal 18 of the battery 12. Optionally, the sheet 4 has a second folding line 30 and/or a third folding line 32 to allow folding of the sheet 4 around the battery 12 to provide a more compact battery assembly with DC source. Figure 4-6 schematically illustrates exemplary main parts 4A in the form of sheets 4 of different shapes but comprising similar functional features. Figure 4 shows an exemplary sheet 4 comparable to the sheet as explained in relation to Figure 3, wherein the initial shape of the sheet 4 is I-shaped. The first folding line 28 guides a folding along a line perpendicular to a longitudinal direction of the sheet 4. Figure 5 shows an exemplary sheet 4 wherein the initial shape of the sheet 4 is T-shaped. The sheet 4 comprises a first folding line 28 and a second folding line 30. Further, the sheet 4 as illustrated in Figure 5 comprises a primary second pad 26A and a secondary second pad 26B. The first folding line 28 allows the primary second pad 26A to connect to a second output terminal of an attached direct current source. The second folding line 30 allows the secondary second pad 26B to connect to a second output terminal of an attached direct current source. The sheet 4 as illustrated in Figure 5 comprises a plurality of second adhesive layers 21A, 21 B, 21C including a primary second adhesive layer 21A, a secondary second adhesive layer 21 B and a tertiary second adhesive layer 21C. The plurality of second adhesive layers 21 A, 21 B, 21C allow each of the first pad 24, primary second pad 26A and secondary second pad 26B, respectively, to adhere to a direct current source 12. The first folding line 28 and the second folding line 30 as illustrated in Figure 5, guides a folding of the sheet 4 along a line parallel to a longitudinal direction of the sheet 4. Figure 6 shows an exemplary sheet 4 wherein the initial shape of the sheet 4 is L-shaped. The sheet 4 comprises a first folding line 28, wherein the first folding line 28 guides a folding of the sheet along a line parallel to a longitudinal direction of the sheet 4. Figure 7 schematically shows an exemplary interface between a direct current source 12 and the sheet 4. The direct current source 12 comprises a first output terminal 16 and a second output terminal 18. Further, the direct current source 12 encloses an electrolyte 44. The sheet 4 has a base layer 40 and a non conductive layer 42 with a first surface 6 and a second surface 8. A primary second adhesive layer 21 on the first surface 6 electrically connects the first pad 24 and the first terminal 16. Figure 8 schematically shows an inductive coupling between a battery assembly 2 and a hearing device 3. The battery assembly 2 comprises a direct current source 12, an electronic circuit 22 and an inductive coil 11. The electronic circuit 22 comprises an oscillator 58 that converts the direct current from the direct current source 12 to an alternating current which induces an alternating electromagnetic field in the inductive coil 11. The hearing device 3 comprises an inductive coil 60, a diode 62, a capacitor circuit 64, a processing unit 66, a microphone 68 and a receiver 70. The inductive coil 11 induces an alternating electromagnetic field in the inductive coil 60 of the hearing device 3 giving rise to an alternating current. The alternating current thus produced by the inductive coil 60 of the hearing device 3 is rectified by the diode 62 and capacitor circuit 64 and a direct current is fed to the functional parts of the hearing device 3, effectively powering the hearing device circuit, here illustrated as being fed to the processing unit 66. Figure 9 illustrates a flow-diagram of a method of powering a hearing device 100. The method 100 comprises providing a battery assembly with a direct current source 102, activating the direct current source 104 and attaching the battery assembly to the hearing device housing 106. The battery assembly provided may be a battery assembly as described herein and in particular in relation to Figures 1-8.

1. Battery assembly for powering a hearing device, the battery assembly comprising - a main part having at least a first surface and a second surface and comprising a first electrode formed as an inductive coil; - first attachment member on at least a primary part of the first surface for attaching the main part to a hearing device housing of the hearing device; - second attachment member for attaching a direct current source to the main part; and - an electronic circuit having a first input terminal and a second input terminal connectable to a first output terminal and a second output terminal, respectively, of the direct current source, wherein the electronic circuit is connected to the first electrode, and wherein the electronic circuit is configured for converting direct current from the direct current source to alternating current in the inductive coil.

2. Battery assembly according to claim 1, wherein the main part is embodied as a sheet. 3. Battery assembly according to any of claims 1-2, wherein the first attachment member is a first adhesive layer covering at least a part of the first or the second surface. 4. Battery assembly according to any of the preceding claims, wherein the second attachment member comprises second, electrically conductive, adhesive layer(s) electrically connected to the first input terminal and/or the second input terminal. 5. Battery assembly according to claim 3, wherein the battery assembly comprises a removable first protective sheet covering the first adhesive layer. 6. Battery assembly according to any of the preceding claims, wherein the battery assembly comprises a direct current source being a battery having a housing with one or more activation openings sealed with a battery activation tab or a part of the first surface. 7. Battery assembly according to claim 4, wherein the battery assembly comprises second protective sheet(s) covering the second adhesive layer(s). 8. Battery assembly according to any of the preceding claims, the battery assembly comprising an activation part between an input terminal of the electronic circuit and an output terminal of the direct current source. 9. Battery assembly according to any of the preceding claims, wherein the main part is a printed circuit board. 10. Battery assembly according to any of the preceding claims, wherein the first adhesive layer is configured to adhere to a hearing device housing of the hearing device. 11. Battery assembly according to any of the preceding claims, wherein the main part or sheet is an elongated sheet having a first end and a second end with a length in the range from 10 mm to 50 mm. 12. Battery assembly according to any of the preceding claims, wherein the main part or sheet has a shape selected from T-shaped, L-shaped, I-shaped or cross-shaped.

2871864

Battery assembly for a hearing device and associated method

Based on the following detailed description of an invention, generate the patent claims. There should be 3 claims in total. The first, independent claim is given and the remaining 2 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The disclosed battery assembly enables a user to use a rechargeable hearing device even when the rechargeable battery in the hearing device runs out by providing a secondary power supply that is easy and convenient to use for a hearing device user. The electronic circuit comprises a first input terminal or input node and a second input terminal or input node. The first input terminal is connected, connectable or configured to connect to a first output terminal of a direct current (DC) source, and the second input terminal is connected, connectable or configured to connect to a second output terminal of the DC source. The input terminals may be connectable or configured to connect to the DC source via a number of pads connected to the input terminals via input electrodes. The electronic circuit comprises one or more output terminals or nodes including a first output terminal and optionally a second output terminal. First and second output terminals of the electronic circuit may be connected to respective ends or points of the first electrode forming an inductive coil. The electronic circuit may comprise an oscillator for converting DC from the DC source to alternating current (AC). The oscillator may be configured to provide an output signal with a frequency in the range from 125 kHz to 15 MHz. The battery assembly may comprise one or more first pads connected to the first input terminal of the electronic circuit via first input electrode(s). The battery assembly may comprise one or more second pads connected to the second input terminal of the electronic circuit via second input electrode(s). The battery assembly may comprise a primary second pad, a secondary second pad and optionally a tertiary second pad each connected to the second input terminal via second input electrode(s). A pad facilitates electrical connection between an input terminal of the electronic circuit and an output terminal of the DC source for feeding power from the DC source to the electronic circuit. The first attachment member may be a first adhesive layer or part. A first adhesive layer or part on a first surface of the battery assembly enables removable attachment of the battery assembly to a hearing device housing. The first adhesive layer may cover or at least partly cover the first inductive coil, e.g. for ensuring accurate and stable positioning of the inductive coil in relation to an inductive charging or power coil of the hearing device. The first adhesive layer for attaching the battery assembly to a hearing device housing may be arranged on the first surface or a second surface of the main part. The first attachment member may be the first adhesive layer. The first attachment member may be a resilient spring clamp configured for fitting partially or completely around the hearing device housing of the hearing device. The first attachment member may be an engagement member configured for engaging the hearing device housing and fitting partially or completely around the hearing device housing of the hearing device. The first attachment member may comprise an elastic band or strap. The battery assembly may comprise one or more removable protective sheets, including a first protective sheet. The first protective sheet may cover or at least partly cover the first adhesive layer. The purpose of the removable first protective sheet may be that the user may handle the battery assembly without the first adhesive layer being exposed, and when the user wishes to attach the battery assembly to the hearing device, the first adhesive layer can be exposed by removal of the first protective sheet and the battery assembly can then be attached to the hearing device. The direct current source may be any direct current source, such as a battery. The direct current source may be any type of battery. The battery may be of the same type as conventionally used in hearing devices, e.g. a zinc-air battery. The DC source may provide a supply voltage in the range from 1.1 V to 3 V. Some batteries, e.g. zinc-air batteries, aluminum-air batteries or lithium-air batteries, rely on a reaction with oxygen, and may be activated by unsealing or revealing activation opening(s) to let air into the battery. Thus, the direct current source may be a battery having a housing with one or more activation openings. The one or more activation openings may be sealed with a battery activation tab. The one or more activation openings may alternatively or additionally be sealed and/or covered by a part of the main part, e.g. the primary part of the first surface with the first attachment member, such as the first adhesive layer. In an exemplary battery assembly, the main part of the battery assembly may be in the form of a sheet. The battery assembly may also be configured for holding or attaching a DC source to the sheet or the battery assembly may comprise a DC source. The battery assembly may comprise one or more second attachment members for attaching the DC source to the battery assembly and/or providing electrical contact between pad(s) and output terminal(s) of the DC source. The one or more second attachment members may include one or more second adhesive layers. The second adhesive layer or second adhesive layers, such as a primary second adhesive layer and/or a secondary second adhesive layer may each be configured for electrically connecting a pad or an input terminal of the plurality of input terminals of the electronic circuit to an output terminal of the direct current source. Hence, the direct current source may be fixed to the battery assembly by the second adhesive layer(s). The primary second adhesive layer or the secondary second adhesive layer may be integrated in the first adhesive layer. The second attachment member may be a battery seat or compartment with electrical connector members or pads connected to the first input terminal and the second input terminal, respectively. The battery seat or compartment may be configured for holding a battery or other DC source, e.g. in a press-fit engagement. In exemplary battery assemblies, the second attachment member fix the direct current source to the battery assembly, e.g. the first and/or second output terminals of the direct current source is fixed to the battery assembly. For example, electrically conductive glue or other fastener, may be used for fixing the DC source to the battery assembly and forming electrical connections between respective output terminals and pads. The battery assembly may comprise a plurality of removable protective sheets, including the removable first protective sheet and optionally removable second protective sheet(s). The removable second protective sheet(s) may cover the second adhesive layer(s). Hence before use, the user may handle the battery assembly without exposing the second adhesive layer(s). When the direct current source is ready to be attached to the sheet and/or ready to be activated, the user may remove the second protective sheet, thereby exposing the second adhesive layer in order to affix an input terminal of the electronic circuit to an output terminal of the direct current source. A single protective sheet, e.g. the first protective sheet, may cover the first adhesive layer and the second adhesive layer(s). The removable second protective sheet may include a plurality of removable second protective sheets, such as a primary second protective sheet, a secondary second protective sheet and/or a tertiary second protective sheet. Each of the plurality of removable second protective sheets may cover one of the plurality of second adhesive layers. Whether second protective sheets are employed depends on whether a DC source is pre-attached or not. One or more second protective sheets, e.g. all second protective sheets, are optional and may be dispensed with in case of a DC source being pre-attached to the battery assembly. To allow an electrical connection between an input terminal of the electronic circuit and an output terminal of the direct current source, the second adhesive layer may be made of an electrically conducting material. Alternatively, the second adhesive layer(s) may leave a part of the input terminals/pads exposed, such that an electrical connection is possible even if the second adhesive layer is made of an electrically insulating material. The battery assembly may comprise an activation part between an input terminal of the electronic circuit and an output terminal of the direct current source. The activation part may be an electrically insulating layer between an input terminal of the electronic circuit and an output terminal of the direct current source. Hence, unintentional discharging of the direct current source before use is avoided or at least limited. In an exemplary battery assembly, the first adhesive layer may adhere to the direct current source. Hence, the first adhesive layer may be configured to adhere to the hearing device and to the direct current source. This may lower production costs, since a single adhesive layer, i.e. the first adhesive layer, can be applied to a substantial part of the first and/or second surface. The first adhesive layer may be an adhesive that allows the battery assembly to be detached from the hearing device after use. The second adhesive layer may be an adhesive that do not allow easy detachment. Hence, the second adhesive layer may prevent easy detachment of the direct current source from the battery assembly. This may be beneficial to ensure a firm connection between an input terminal of the electronic circuit and an output terminal of the direct current source, and to eliminate or at least limit the risk of the direct current source unintentionally detaching from the battery assembly. The main part may be a printed circuit board. Hence, manufacturing is easy and production costs can be lowered. If the main part is embodied as a sheet, the sheet may be a printed circuit board. The main part may be an elongated sheet having a first end and a second end. The sheet and/or the main part may have a length in the range from 10 mm to 50 mm. The sheet and/or the main part may have a shape selected from T-shaped, L-shaped, I-shaped or cross-shaped. Different shapes may be beneficial for different purposes, and may further be a compromise between reliability and production costs. The sheet and/or the main part may comprise one or more folding lines including a first folding line. One or more of the folding lines, e.g. the first folding line, may be configured to bring an input terminal of the electronic circuit in contact with an output terminal of the direct current source. In an exemplary battery assembly, the first folding line may be configured to bring the second input terminal in contact with the second output terminal. The sheet and/or the main part may comprise a plurality of folding lines including the first folding line, a second folding line, a third folding line, a fourth folding line and/or a fifth folding line. In an exemplary battery assembly, the first folding line may be configured to bring a second primary input terminal in contact with the second output terminal, and a second folding line may be configured to bring a second secondary input terminal in contact with the second output terminal. The direct current source and the sheet may be bundled together, or distributed individually. The battery assembly may be provided together with the direct current source. Alternatively, the battery assembly may be provided without the direct current source, and thus be configured to receive a direct current source. Further, a method for powering a hearing device is disclosed. The method comprises: providing a battery assembly as described herein; optionally attaching the direct current source to the main part of the battery assembly; and activating the direct current source. The method may further comprise attaching the battery assembly to the hearing device, e.g. to a hearing device housing of the hearing device. Activating the DC source may comprise connecting one or more output terminals, e.g. the second output terminal and/or the first output terminal, of the DC source with a pad of the battery assembly. Activating the DC source may comprise removing or peeling off a battery activation tab from the DC source. Activating the DC source may comprise removing or peeling of one or more protective sheets of the battery assembly. Attaching the battery assembly to the hearing device may comprise attaching the first attachment member to the hearing device housing. Attaching the battery assembly to the hearing device may comprise aligning the first inductive coil with an inductive coil of the hearing device. Attaching the battery assembly to the hearing device may comprise exposing a first adhesive layer, e.g. by removing a first protective sheet covering the first adhesive layer. Figure 1 schematically illustrates an exemplary hearing device system 1 comprising a hearing device 3 with an exemplary battery assembly 2 attached thereto. The battery assembly 2 comprises a main part 4A in the form of a sheet 4, an electronic circuit 22, and optionally a direct current source 12 attached to or attachable to the sheet 4. The DC source 12 has a first output terminal 16 and a second output terminal 18 and may be attached to the sheet during manufacture or by the user prior to attachment to a hearing device. A first attachment member (not shown), such as a first adhesive layer on at least a primary part of the first surface, affix the sheet/battery assembly to the hearing device 3. The sheet 4 has a first surface 6 and a second surface 8 and comprises a first electrode 10 formed as an inductive coil 11. The electronic circuit 22 has a first input terminal 23 and a second input terminal 27 that are connected to the direct current source 12 via first pad 24 and second pad 26. The electronic circuit 22 converts direct current from the direct current source 12 to alternating current in the inductive coil 11. The alternating current in the inductive coil 11 generates an alternating magnetic field that induces electromagnetic power in an inductive coil (not shown) in the hearing device 3 when the inductive coil 11 of the battery assembly 2 is in close vicinity of the inductive coil in the hearing device 3. The illustration in Figure 1 depicts the battery assembly 2 with an attached direct current source 12, here exemplified as a button cell battery. The battery assembly 2 is attached to the hearing device 3 and creates an inductive coupling between the inductive coil 11 of the battery assembly 2 and an inductive coil (not shown) of the hearing device 3. Hence, the battery assembly 2 allows the direct current source 12 to power and/or charge the hearing device 3 via an inductive coupling. A user may on a daily basis charge an internal battery of the hearing device 3. However, the internal battery (not shown) of the hearing device 3 may run out of power while no inductive charger is available, or the hearing device is in use. If the internal battery should run out of power, the battery assembly 2 can easily and conveniently be attached to the hearing device 3 as shown. The hearing device 3 is then able, via an inductive coupling, to be powered by power provided by the direct current source 12. Figure 2 schematically illustrates an exemplary battery assembly 2. The battery assembly comprises a main part 4A in the form of a sheet 4 and a direct current source 12. The direct current source 12 comprises a housing 14 and has a first output terminal 16 and a second output terminal 18. The battery assembly 2 comprises an electronic circuit 22 having a first input terminal 23 and a second input terminal 27. The first input terminal 23 is connected to the first output terminal 16 of the direct current source 12 via a first pad 24. The first output terminal 16 is glued or fastened to the sheet 4 with an electrically conductive glue or other fastener, which attaches the DC source 12 to the sheet 4 and electrically connects the first pad 24 and the first output terminal 16. The second input terminal 27 is connectable to the second output terminal 18 of the direct current source 12 via second pad 26. The electronic circuit 22 is connected to the first pad 24 and second pad 26 for converting direct current from the direct current source 12 to alternating current in the inductive coil 11. In Figure 2, the second input terminal 27 is connected to the second output terminal 18 by performing a folding of the sheet 4 along a first folding line 28 as shown by the arrow. The battery assembly 2 in Figure 2 comprises a first attachment member 19 in the form of a first adhesive layer 20 and a second attachment member 21' in the form of a second adhesive layer 21. The second adhesive layer 21 is adapted to adhere to the direct current source 12 and to electrically connect the second output terminal 18 and the second pad 26 by contact and/or via electrically conductive second adhesive layer 21. A first protective sheet 34 covers and protects the first adhesive layer 20 prior to use. The first protective sheet 34 is removed when a user wishes to attach the battery assembly to a hearing device. A second protective sheet 36 covers and protects the second adhesive layer 21 prior to use. The second protective sheet 36 is removed when a user wishes to activate the battery assembly/DC source. Figure 3 schematically illustrates an exemplary battery assembly 2 with a main part 4A formed as an I-shaped sheet 4. The direct current source 12 is in Figure 3 exemplified as a battery that is activated by air and comprises a battery activation tab 13 sealing one or more activation openings in the housing 14. Upon removal of the battery activation tab 13 air is allowed to enter the activation openings of the housing 14, thus activating the battery 12. The battery assembly 2 comprises two second adhesive layers 21A and 21 B configured for adhering the direct current source 12 to the sheet 4. Further, the primary second adhesive layer 21A electrically connects the first pad 24 and the first output terminal 16 of the battery 12, and the secondary second adhesive layer 21 B electrically connects the second pad 26 and the second output terminal 18 of the battery 12. Optionally, the sheet 4 has a second folding line 30 and/or a third folding line 32 to allow folding of the sheet 4 around the battery 12 to provide a more compact battery assembly with DC source. Figure 4-6 schematically illustrates exemplary main parts 4A in the form of sheets 4 of different shapes but comprising similar functional features. Figure 4 shows an exemplary sheet 4 comparable to the sheet as explained in relation to Figure 3, wherein the initial shape of the sheet 4 is I-shaped. The first folding line 28 guides a folding along a line perpendicular to a longitudinal direction of the sheet 4. Figure 5 shows an exemplary sheet 4 wherein the initial shape of the sheet 4 is T-shaped. The sheet 4 comprises a first folding line 28 and a second folding line 30. Further, the sheet 4 as illustrated in Figure 5 comprises a primary second pad 26A and a secondary second pad 26B. The first folding line 28 allows the primary second pad 26A to connect to a second output terminal of an attached direct current source. The second folding line 30 allows the secondary second pad 26B to connect to a second output terminal of an attached direct current source. The sheet 4 as illustrated in Figure 5 comprises a plurality of second adhesive layers 21A, 21 B, 21C including a primary second adhesive layer 21A, a secondary second adhesive layer 21 B and a tertiary second adhesive layer 21C. The plurality of second adhesive layers 21 A, 21 B, 21C allow each of the first pad 24, primary second pad 26A and secondary second pad 26B, respectively, to adhere to a direct current source 12. The first folding line 28 and the second folding line 30 as illustrated in Figure 5, guides a folding of the sheet 4 along a line parallel to a longitudinal direction of the sheet 4. Figure 6 shows an exemplary sheet 4 wherein the initial shape of the sheet 4 is L-shaped. The sheet 4 comprises a first folding line 28, wherein the first folding line 28 guides a folding of the sheet along a line parallel to a longitudinal direction of the sheet 4. Figure 7 schematically shows an exemplary interface between a direct current source 12 and the sheet 4. The direct current source 12 comprises a first output terminal 16 and a second output terminal 18. Further, the direct current source 12 encloses an electrolyte 44. The sheet 4 has a base layer 40 and a non conductive layer 42 with a first surface 6 and a second surface 8. A primary second adhesive layer 21 on the first surface 6 electrically connects the first pad 24 and the first terminal 16. Figure 8 schematically shows an inductive coupling between a battery assembly 2 and a hearing device 3. The battery assembly 2 comprises a direct current source 12, an electronic circuit 22 and an inductive coil 11. The electronic circuit 22 comprises an oscillator 58 that converts the direct current from the direct current source 12 to an alternating current which induces an alternating electromagnetic field in the inductive coil 11. The hearing device 3 comprises an inductive coil 60, a diode 62, a capacitor circuit 64, a processing unit 66, a microphone 68 and a receiver 70. The inductive coil 11 induces an alternating electromagnetic field in the inductive coil 60 of the hearing device 3 giving rise to an alternating current. The alternating current thus produced by the inductive coil 60 of the hearing device 3 is rectified by the diode 62 and capacitor circuit 64 and a direct current is fed to the functional parts of the hearing device 3, effectively powering the hearing device circuit, here illustrated as being fed to the processing unit 66. Figure 9 illustrates a flow-diagram of a method of powering a hearing device 100. The method 100 comprises providing a battery assembly with a direct current source 102, activating the direct current source 104 and attaching the battery assembly to the hearing device housing 106. The battery assembly provided may be a battery assembly as described herein and in particular in relation to Figures 1-8.

13. Method for powering a hearing device with a direct current source, the method comprising: - providing a battery assembly comprising - a main part having at least a first surface and a second surface and comprising a first electrode formed as an inductive coil; - first attachment member on at least a primary part of the first surface for attaching the main part to a hearing device housing of the hearing device; - second attachment member for attaching a direct current source to the main part; and - an electronic circuit having a first input terminal and a second input terminal respectively connectable to a first output terminal and a second output terminal of a direct current source, the electronic circuit connected to the first electrode for converting direct current from the direct current source to alternating current in the inductive coil; - attaching a direct current source to the main part of the battery assembly; and - activating the direct current source.

14. Method according to claim 13, wherein the method comprises attaching the battery assembly to the hearing device and aligning the first inductive coil with an inductive coil of the hearing device. 15. Method according to claim 14, wherein attaching the battery assembly to the hearing device comprises exposing a first adhesive layer by removing a first protective sheet covering the first adhesive layer.

2873637

A hoisting machine, an elevator assembly, and improvement in vibration damping of a hoisting machine and in an elevator assembly

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The concept of vibration damping method according to the present invention and the hoisting machine according to the present invention, and in particular the vibration concept emploeyed in the vibration damping between the drive-sheave protection plate and mounting frame are explained in more details within the context of the elevator assembly disclosed in certain applicants prior applications, namely - o [PATCIT WO2011154614A1], of which the structure of the elevator assembly, the operation mechanism of the hoisting machine and of the rotor, and the fixing arrangement and fixing points and optionally also its vibration damping, machinery brakes, brake drums and brake shoes; - ○ [PATCIT WO2011036348A1], of which the rotor stucture, in particular also including the rotor bearings; and - ○ optionally, also [PATCIT WO2010063869A1], of which the details of the dampers arranged between the stator and the machine frame, or between the stator winding and machine frame are incorporated in the present application by reference. FIG 1 illustrates the concept of elevator assembly 1 including a hosting machine 2, and FIG 2 shows certain details of the structure of a hosting machine 2. FIG 1 and the respective part of the description can also be found in international patent application published under publication number [PATCIT WO2011154614A1]. FIG 2 and the respective part of description can be seen in FIG 2 of international patent application published under publication number [PATCIT WO2011036348A1], with slight modifications in the shape of the rotor. Also the sensor arrangement has been omitted for clarity. FIG 1 is a block diagram an elevator assembly 1, in which the elevator car 15 and the counterweight 29 are suspended in the elevator hoistway 30 with suspension ropes 16. Elevator car 15 is movable with the hoisting machine 2 of the elevator assembly 1. The hoisting machine 2 is disposed in the top part of the elevator hoistway 30, along a guide rail 9 fixed to a wall part 17 of the elevator hoistway 30 by exerting a force effect on the elevator car 15 with suspension ropes 16 traveling via the traction sheave 5 of the hoisting machine 2. On the surface of the traction sheave 5 are rope grooves 6 (see also FIG 2 ), in which the suspension ropes 16 move along with the rotational movement of the traction sheave 5 such that the suspension ropes 16 are rotatably supported in the rope grooves 6. The power supply to the hoisting machine 2 most preferably takes place with a frequency converter (not shown in FIG 1 ) connected between an electricity network and the hoisting machine 2. The frequency converter and the hoisting machine 2 are most preferably disposed in the elevator hoistway 30, in connection with wall part 28 of the elevator hoistway 30 outside the path of movement of the elevator car 15. The hoisting machine 2 may be fixed to a guide rail 9, most preferably by using the fixing arrangement as disclosed in international patent application published under publication number [PATCIT WO2011154614A1] in such a manner that the hoisting machine 2 is apart from the wall part 17 of the elevator hoistway 30. The guide rail 9 bears the force exerted on the rope grooves 6 of the traction sheave 5 via the suspension ropes 16. The guide rail 9 is fixed to the wall part 17 of the elevator hoistway with guide rail fixings 31. The hoisting machine 2 of the elevator is disposed in the space between the aforementioned wall part 17 and the guide rail 9 such that the axis of rotation 19 of the hoisting machine is situated essentially orthogonally with respect to the wall part 17. Hoisting ropes 16 arriving at the rope grooves 61 of the traction sheave 5 as well as the hoisting ropes 16 leaving from the rope grooves 6 travel closer to the wall part 17 than the rear part of the guide rail 9 of the elevator car 15. [PATCIT WO2011154614A1] discloses in more detail the fixing arrangement 7 for a hoisting machine 2 used in the elevator assembly 1. The hoisting machine 2 is fixed at its top part to the guide rail 9 from at least two points, which are at the same height and which are situated apart from each other in the width direction w of the guide rail 9 of the elevator car 15, with the fixing arrangement 7 comprising rigid fixing means 7 which continues essentially as an integral piece between the fixing points 3A, 3B. Fixing points 3A, 3B of hoisting machine 2 comprise fixing pins/fixing bolts. The fixing arrangement is fixed rigidly to guide rail 9 e.g. with fixing pins, fixing bolts or fixing screws. Hoisting machine 2 is fixed at its bottom part to guide rail 9 from only one fixing point 3C with a fixing arrangement 10. The fixing pins of the fixing points 3A, 3B of the top part of the hoisting machine 2 as well as the fixing point 3C of the bottom part are connected to the rigid fixing arrangements 7, 10 with an elastomer, which damps the vibration caused by the operation of the hoisting machine 2, e.g. from the effect of groove harmonics. The brake ring of the drum brake is formed as an extension of the rotating structure of the hoisting machine. Two drum brakes (omitted in FIG 1 ) movably supported on the stationary structure of the hoisting machine 2 are the machinery brakes of the hoisting machine 2, the brake shoes of which drum brakes engage, pressed by a spring pack, against the brake ring to brake the movement of the traction sheave 5 of the hoisting machine 2. For example, in connection with an emergency stop the brake shoes of the machinery brakes engage to brake a traction sheave 5 that is moving rotationally; in this case, owing to the kinetic energy of the elevator car 15, an essentially large force braking the movement of the traction sheave is formed between the rotating structure and the stationary structure of the hoisting machine 2, which force tries to produce vibration of the hoisting machine. For damping the vibrations of the hoisting machine 2, the distance s between the fixing points 3A, 3B of the top part of the hoisting machine is selected to be equal to, or even greater than the diameter D of the traction sheave 5. The distance s between the fixing points 3A, 3B could also be selected e.g. such that the ratio of the distances to the diameter D1 of the brake ring is greater, e.g. greater than 0.5. This type of fixing arrangement stiffens the structure of the hoisting machine 2, reducing the vibration of the hoisting machine. FIG 2 shows a sectional drawing of hoisting machine 2. For detecting the position of a magnetic pole of the rotor 31, or for measurement of position data and/or movement, the hoisting machine 2 may -but it does not need to- comprise an optical encoder or a resolver, or a magnetic band and reader (as the hoisting machine disclosed in [PATCIT WO2011036348A1] ) comprising combinations of a magnetic band and a reader. The hoisting machine 2 in FIG 2 is a permanent-magnet synchronous motor, in which the permanent magnets are mounted on the rotor 31. The drive sheave 5 is integrated with the rotor 31. The air gap 33 between the stator 32 and the rotor 31 is substantially parallel to the rotational axis 19 of the rotor 31. The rotor 31 and the drive sheave 5 are rotatably supported by bearings 27 on the body part of the hoisting machine 2. The bearing 27 is mounted in a bearing housing 34, which is integrated in the same body with the traction sheave 5. The traction sheave 5 protection plate 28 secured to the body part 35 of the hoisting machine 2 extends to the side of the traction sheave 5 so that the traction sheave 5 is housed in the space remaining between the protection plate 28 and the body part 33. FIG 3 illustrates a hoisting machine 2' according to the invention as seen in perspective from the stator 32 side. FIG 4 illustrates the hoisting machine 2' as seen in perspective from the rotor 31 side. FIG 5 is a top view of the hoisting machine 2' and FIG 6 is the section VI-VI. The hoisting machine 2' is shown in right-hand side in FIG 7. It should be understood that rotor 31 has been omitted from FIG 3 - 7 for the sake of clarity. The hoisting machien 2' comprises an axial flux motor comprising a rotor 31 having rope grooves 6 and arranged in rotor compartment 58 between a body part 35 and a protection plate 28, and a stator 32 arranged against the rotor 31 in such a manner that the rotor 31 is separated by the stator 32 by an air gap. Body part 35 serves as a fixing for the stator 32 that most preferably is welded to the body part 35. Alternatively of welding or in addition to it, also the fixing arrangement described in [PATCIT WO2010063869A1] can be used to fix the stator to the body part. The hoisting machine 2' further comprises at least one rail fixing arrangement 60 for fixing the hoisting machine 2' to guide rail 9. The rail fixing arrangement 60 is most probably integral to the base part 35 and contains suitable protruding lips that can be mounted around the guide rail 9, and also stiffening wing 63 and stiffening ribs 64 to increase the mechanical rigidity of the hoisting machine 2'. Furthermore, the hoisting machine 2' comprises lateral brake shoes 55 movably attached to brake shoulders 57 that are attached to the base part 35 in a form-locking manner, such as by using bolts 56. Brake shoes 55 are used to brake the movement of the rotor 31. They Additionally, the hoisting machine 2' comprises braking control system that ensures that the brake shoes 55 are normally in the locking position i.e. engage with the rotor 31, and disengage from the rotor only when the braking control system is activated. The hoisting machine 2' further comprising a first cover plate 51 and a second cover plate 53, arranged at opposide sides of the hoisting machine 2', and both being equipped with a damper 59. Preferably, the first cover plate 51 and the second cover plate 53 that both serve as carrier for the respective damper 59 are made of iron, or comprise iron. 10. The damper 59 is a layer of elastic material, such as rubber or elastomer. The first cover plate 51 and the second cover plate 53 form an external damper to the axial flux motor. The tightness between the first cover plate 51 and the second cover plate 53 is adjustable. The first cover plate 51 can be located on the body part 35 or, as can be seen in FIG 6, in a recess in the body part 35. Respectively, the second cover plate 53 can be located on the protection plate 28 or as also can be seeen in FIG 6, in a recess in the protection plate 28. The first cover plate 51 and the second cover plate 53 are interconnected through a tightness adjustion mechanism that comprises a bolt 50 (with bolt head 54) and a nut 52. The tightness adjustion mechanism penetrates the rotor 31 and the stator 32. Instead of bolt 50 and nut 52, the tightness adjustion mechanism can be realized by using any other suitable form-locking arrangement. The bolt head 54 and the nut 52 are so arranged that they are at opposite sides of respective cover plate 51, 53 than the dampers 59 so that the dampers 59 are tightenable or loosenable by rotating the bolt head 54 and/or the nut 52. In the simulations carried out by the inventor, around the cover plates 51, 53 vibration amplitudes |U| < 0,25 (in arbitrary units) could be obtained (ref. FIG 8 ). Vibration amplitudes generally depend on load, speed and certain other factors and in general are described as mobility (displacement/force). As can be seen, at noisiest (0,5 < |U| < 1,25) the hoisting machine 2' is around brakes. A respective simulation carried out by the inventor for hoisting machine 2 shows that vibration amplitudes 0,5 < |U| < 1,25 were present all over the hoisting machine 2. The hoisting machines 2' and 2 compared with each other, it can readily be seen that the hoisting machine 2' according to the invention is from noise/vibration viewpoint superior to a hoisting machine 2 known from background art. #### List Of Reference Numerals Used - 1: elevator assembly - 2, 2': hoisting machine - 3A, 3B, 3C: fixing point - 5: traction sheave - 6: rope grooves - 7: fixing arrangement - 9: guide rail - 10: fixing arrangement - 15: elevator car - 16: suspension ropes - 17: wall part of the elevator hoistway - 27: bearing - 28: protection plate - 29: counterweight - 30: elevator hoistway - 31: rotor - 32: stator - 33: air gap - 34: bearing housing - 35: body part - 50: bolt - 51: cover plate - 52: nut - 53: cover plate - 54: bolt head - 55: brake shoe - 56: bolt - 57: brake shoulder - 58: rotor compartment - 59: damper - 60: rail fixing arrangement - 61: damper - 62: bearing housing - 63: stiffening wing - 64: stiffening rib

1. A hoisting machine (2'), comprising: an axial flux motor comprising a rotor (31) having rope grooves (6) and arranged in rotor compartment (58) between a body part (35) and a protection plate (28), and a stator (32) arranged against the rotor (31) in such a manner that the rotor (31) is separated by the stator (32) by an air gap (33);: the hoisting machine (2') further comprising a first cover plate (51) and a second cover plate (53), arranged at opposide sides of the hoisting machine (2'), and both being equipped with a damper (59);: wherein: the tightness between the first cover plate (51) and the second cover plate (53) is adjustable.

2. A hoisting machine (2') according to claim 1, wherein: the first cover plate (51) is located on the body part (35) or in a recess in the body part (35). 3. A hoisting machine (2') according to claim 1 or 2, wherein: the second cover plate (53) is located on the protection plate (28) or in a recess in the protection plate (28). 4. A hoisting machine (2') according to any one of claims 1 to 3, wherein: the first cover plate (51) and the second cover plate (53) are interconnected through a tightness adjustion mechanism (50, 52, 54). 5. A hoisting machine (2') according to claim 4, wherein: the tightness adjustion mechanism (50, 52, 54) penetrates the rotor (31) and the stator (32). 6. A hoisting machine (2') according to claim 4 or 5, wherein: the tightness adjustion mechanism (50, 52, 54) is carried out by using at least one form-locking arrangement, preferably with a bolt (50) and a nut (52). 7. A hoisting machine (2') according to claim 6, wherein: the form-locking arrangement comprises a bolt (50) and a nut (52) and wherein the bolt (50) has a bolt head (54), and wherein the bolt head (54) and the nut (52) are so arranged that they are at opposite sides of respective cover plate (51, 53) than the dampers (59) so that the dampers (59) are tightenable or loosenable by rotating the bolt head (54) and/or the nut (52). 8. A hoisting machine (2') according to any one of the preceding claims, wherein: the first cover plate (51) and the second cover plate (53) form an external damper. 9. A hoisting machine (2') according to any one of the preceding claims, wherein: the first cover plate (51) and the second cover plate (53) that both serve as carrier for the respective damper (59) are made of iron, or comprise iron. 10. A hoisting machine (2') according to any one of the preceding claims, wherein: the damper (59) is a layer of elastic material, or comprises at least one layer of elastic material. 11. A hoisting machine (2') according to any one of the preceding claims, wherein: the hoisting machine (2') further comprises at least one rail fixing arrangement (60) for fixing the hoisting machine to a guide rail (9). 12. An elevator assembly (1), comprising: an elevator car (15) movable in elevator hoistway (30) by rotation of a hoisting machine (2') according to any one of the preceding claims causing movement of suspension ropes (16) in rope grooves (6). 13. An elevator assembly (1) according to claim 11 with a hoisting machine (2') according claim 10, wherein: the elevator car (15) is movable along one, two or more guide rails (9) in the elevator hoistway (30); and wherein: the hoisting machine (2') has been installed between between a wall part (17) of the elevator hoistway (30) and the guide rail (9) in such a manner that suspension ropes (16) of the elevator assembly (1) are operable by the rotor (31) via rope grooves (6) in such a manner that the suspension ropes (16) are located between the hoisting machine (2') and the movable elevator car (15). 14. Improvement in vibration damping of a hoisting machine and in an elevator assembly, wherein the improvement is characterized by: adjusting tightness between the first cover plate (51) and the second cover plate (53) of a hoisting machine (2') according to any one of the preceding claims 1 to 11 that is installed and/or operated in an elevator assembly (1) according to any one of the preceding claims 13 to 14, to modify the operating noise caused by operation of the hoisting machine (2').

2873489

Impact device and method of dismounting the same

Based on the following detailed description of an invention, generate the patent claims. There should be 11 claims in total. The first, independent claim is given and the remaining 10 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a feasible rock drilling unit 1 which may be connected by means of a boom 2 to a movable carrier, which is not shown. The drilling unit 1 may comprise a feed beam 3 and a rock drilling machine 4 supported on it. The rock drilling machine 4 may be moved on the feed beam 3 by means of a feed device 5. The rock drilling machine 4 comprises a shank 6 at a front end of the rock drilling machine 4 for connecting a tool 7. The tool 7 may comprise one or more drill rods 8 and a drill bit 9 located at a distal end of the tool 7. The rock drilling machine 4 may further comprise a rotating device 10 for rotating the shank 6 and the tool 7 connected to the shank 6. Inside a frame 11 of the rock drilling machine 4 is an impact device 12 comprising a reciprocating percussion piston for generating impact pulses to the tool 7. At a drilling site, one or more drill holes are drilled with the drilling unit 1. The drill holes may be drilled in a horizontal direction, as shown in Figure 1, or in a vertical direction. The disclosed solution is known as top-hammer drilling. The features disclosed in this application may be applied in such drilling machines. In an alternative drilling solution, which is known as down-the-hole or DTH -drilling, the impact device is located inside a bore hole. Then the impact device and a rotating device are located at opposite ends of the drilling equipment. The features disclosed in this application may also be applied in drilling machines of this type. Figure 2 discloses an excavator 13 provided with a boom 2. At a distal end of the boom 2 there is a breaking hammer 14, which comprises an impact device 12 arranged inside a frame 11 of the breaking hammer 14. The impact device 12 may be in accordance with the solution disclosed in this application. In Figures 1 and 2 two different breaking devices 15, namely a rock drilling machine 4 and a breaking hammer 14, are shown. As already mentioned above, the impact device 14 of the breaking device 15 may be in accordance with the disclosed solution and include the features disclosed above. The frame 11 of the breaking device 15 may also comprise the features disclosed in this application. Figure 3 shows a rear portion of a breaking device 15 comprising an impact device 12. The impact device 12 comprises a bush 16 which is a sleeve-like piece. The bush 16 is an elongated object and has a total axial length Ltot, an outer surface 17 and an inner surface 18. The bush 16 is arranged inside an impact device space, which is located at the rearmost end of a frame 20 of the breaking device 15. Inside the bush 16 is a percussion piston 21, which is supported to the bush 16 by means of a front bearing 22 and a rear bearing 23. During operation the percussion piston 21 is moved forwards in an impact direction A for striking a tool and is moved backwards in a return direction B. Thus, the percussion piston 21 is reciprocating during a work cycle of the impact device 12. The impact device 12 is hydraulically operated whereby the percussion piston 21 comprises one or more first working pressure surfaces 24 affecting in the impact direction A and one or more second working pressure surfaces 25 affecting in the return direction B. The percussion piston 21 is moved back and forth by changing hydraulic pressure acting on the working pressure surfaces. In the solution disclosed in Figure 3 pressure affecting the first working pressure surfaces 24 is controlled by means of a control valve 26. Hydraulic pressure affecting the second working pressure surfaces 25 is not varied by the control valve 26. However, the impact device may also be constructed so that pressure affecting in a front pressure chamber 27 is varied as well as pressure in a rear pressure chamber 51 for implementing the work cycle of percussion piston. Hydraulic pressure medium is fed from a hydraulic system to a feed duct or port 29 and the pressure medium is discharged from the impact device through a discharge duct or port 30. The control valve 26 may be a sleeve-like piece arranged around the rear end portion of the piston 21. The control valve 26 may slide in the impact direction A and return direction B in an annular valve space arranged between the inner surface of the bush 16 and the percussion piston 21. The control valve 26 may be pressure controlled whereby it is provided with pressure surfaces, and pressure medium is directed to the these pressure surfaces for moving the sliding valve between front and rear positions according to the working cycle. The bush 16 comprises radial openings at the control valve space for directing pressure medium flows controlled by the control valve 26. The bush 16 may further comprise one or more axial control pressure ducts 31 for directing pressure medium to control pressure surfaces of the control valve 26. The control of the working cycle of the impact device 12 is known to skilled persons and is therefore not described in more detail in the present application. The impact device 12 is construed so that the bush 16 may be extracted from the impact space inside the frame 20 by means of the percussion piston 21. Therefore the rear end of the frame 20 is provided with a rear cover 32, or a corresponding rear element, which closes the rear end of the frame 20. When the rear cover 32 is removed, the impact device 12 can be pulled out by directing an axial dismounting force FB to the rear end portion of the percussion piston 21. The dismounting force FB is external to the impact device, which in practice means that the percussion piston 21 is pulled by means of a lifting device or a corresponding actuator or auxiliary device. In order to transmit the dismounting force FB from the percussion piston 21 to the bush 16, the percussion piston 21 is provided with a pull shoulder 33. The pull shoulder 33 is located somewhere behind the front bearing 22. In the solution disclosed in Figure 3 the pull shoulder 33 is in the front pressure chamber 37. Alternatively, the pull shoulder 33 may be located in a middle section or even in a rear end section of the percussion piston 21, depending on the location of the control valve 26 and the basic structure of the impact device 12. In order words, the pull shoulder may be located between the front bearing 22 and the rear end of the percussion piston 21. The pull shoulder 33 comprises an axial first counter surface 34 facing the return direction B. The inner surface 18 of the bush 16 is provided with a counter section 35 comprising a second counter surface 36 facing the impact direction A. When the percussion piston 21 is pulled in the return direction B, the percussion piston 21 moves relative to the bush 16 and the first counter surface 34 becomes into contact with the second counter surface 36 of the bush 16. Then, the force effect of the dismounting force FB is transmitted from the percussion piston 21 to the bush 16 causing the percussion piston 21 and the bush 16 to move together axially in the return direction B. The outer dimension of the pull shoulder 33 is greater than the inner dimension of the counter section 35, whereby the percussion piston 21 may not be pulled completely out of the bush 16 in the return direction B. The pull shoulder 33 may form a closed space 38 when the percussion piston 21 moves close to a forward extreme position. The bush 16 may be supported to the frame 20 by means of support surfaces 39 and 40 on the outer surface 17 of the bush 16. A first support surface 39 is at the front end portion of the bush 16 and a second support surface 40 is at the rear end portion of the bush 16. The first support surface 39 has a first axial length L1 and a first diameter D1. The second support surface 40 has a second axial length L2 and a second diameter D2. The first length L1 and the second length L2 may be equal or the lengths may differ from each other. The first diameter D1 is smaller than the second diameter D2, whereby the bush 16 has a narrow front end and a wide rear end. Between the first support surface 39 and the second support surface 40 may be an intermediate section 41, which has a third axial length L3 and third outer diameter D3. The frame 20 comprises an impact device space wherein the bush 16 is arranged. The frame 20 comprises in the impact device space surfaces that are dimensioned to correspond with the diameters D1 and D2 of the bush 16 so that the bush 16 is supported firmly in place when being mounted inside the impact device space. However, the third diameter D3 may be dimensioned so that between the frame 20 and the outer surface of the intermediate section 41 remains a clearance 42. The clearance 42 facilitates mounting and dismounting of the impact device 12. Figure 3 further shows that at the front end of the bush 16 may be a front bearing module 43 comprising a supporting body and the front bearing 22. Correspondingly, the rear end of the bush 16 may comprise a rear bearing module 44 comprising a supporting body and the rear bearing 23. The bearing modules 43 and 44 may also comprise one or more seals. The bearing modules 43 and 44 may be extracted simultaneously with the percussion piston 21 and the bush 16. Alternatively, the front bearing module 43 may be construed and supported in such a way that it is not extracted together with the other components of the impact device 12. In this alternative embodiment the front bearing module 43 is dismounted in a separate step. In an additional alternative embodiment the pull shoulder 33 may be located elsewhere as compared to the embodiment shown in Figure 3. Thus, a shoulder 45 may serve as a pull shoulder and the working pressure surface 24 may then serve as a first counter surface. When the percussion piston is pulled in the return direction during the dismounting procedure, then the surface 24 abuts a surface 46 of the bush 16. In this embodiment the first counter surface of the pull shoulder serves during the normal operating cycle of the impact device 12 as a dampening component, since the shoulder 45 forms a closed dampening space when the percussion piston 21 moves to an extreme rear position. Figure 3 also shows that the bush 16 comprises pressure surfaces 47 and 48, which are connected to the feed duct 29 either directly or by means of one or more axial pressure channels 49. The pressure surfaces 47 and 48 produce an axial force in the return direction B when the impact device 12 is pressurized. The pressure surface 47 exists because of a difference in diameters D1 and D3, and correspondingly the pressure surface 48 exists because the diameter D2 is greater than the diameter D3. Thanks to the pressure surfaces and the generated force, the bush 16 is pushed continuously towards the rear cover 32 during the operation. Thus, the bush is always positioned in an accurate position and the impact device operates as designed. Let it be mentioned that in this application the terms front and front direction mean impact direction A, and the terms rear and rear direction mean return direction B. Figure 4 shows that the rear end of the percussion piston 21 may comprise a fastening point 50 allowing a fitting tool to be connected to the rear end of the piston 21. The fastening point 50 may comprise an axial blind opening with inner threads, for example. In Figure 4 some of the seals S are marked with reference markings. As can be noted in Figure 4, the impact device 12 may have a modular or cartridge structure that comprises all the necessary components in one uniform package. The impact device 12 may be pre-assembled by mounting the rear bearing module 44 to the rear end of the bush 16. Thereafter the rear end of percussion piston 21 may be inserted in the front end of the bush 16 and may be pushed in the rearward direction until the pull shoulder 33 abuts the second counter surface 36. After this, the front bearing module 43 may be mounted to the front end of the bush 16. The bearing modules 43 and 44 are provided with the needed bearings 22, 23 and seals S. Figures 5 to 7 show another embodiment, which has only few differences compared to the solution disclosed in Figures 3 and 4. As can be noted, in Figure 5 the frame 20 does not comprise the axial pressure channel 49 for conveying pressure medium from the feed port 29 to a rear pressure chamber 51 via the control valve 26. Instead, the intermediate section 41 of the bush 16 is provided with one or more pressure channels 52 allowing pressure medium to flow from the feed port 29 to a space 53 and further under control of the control valve 26 to the rear pressure space 51. As already discussed above, between the outer surface of the intermediate section 41 and the inner surface of the bush 16 there may be a clearance needed to facilitate the mounting and dismounting of the impact device 12. In addition to the clearance, the outer surface of the intermediate section 41 may comprise one or more grooves 54 or corresponding flow passages. As shown in Figure 6 the outer surface of the intermediate section 41 may have splined configuration and may then have several axial grooves 54 between radial splines 55. Figures 8a and 8b show in a simplified manner a mounting principle of the impact device 12 to the frame 20 of the braking device 15. The outer dimensions of the bush 16 as well as the inner dimensions of supporting surfaces 56a - 56c are exaggerated for ease of understanding. The bush 16 tapers towards the front end, which facilitates mounting. The tapered first support surface 39 passes easily through the supporting surfaces 56b and 56c of the frame 20 having greater dimensions. The mounting may be executed in a vertical position whereby the rear end of the frame is pointing upwards. The rear cover is removed and an impact device space 57 is open to receive the impact device 12. In Figure 8a the impact device 12 is lifted by means of a lifting device above the frame 20 and is positioned to a center line 58 of the impact device space 57. The bush 16 is supported by the pull shoulder 33 of the percussion piston 21. A fitting tool 59 is attached to the rear end of the percussion piston 21 enabling the lifting and handling of the impact device by means of the lifting device. In Figure 8b the impact device 12 is lowered and the impact device 12 has penetrated into the impact device space 57. Figure 9 shows a simplified chart wherein some steps and features relating to dismounting of an impact device are shown. These issues are disclosed already above in this application. Figure 10 shows a simplified chart, wherein some steps and features relating to mounting of an impact device are shown. These issues are disclosed already above in this application, Figure 11 shows an alternative impact device 12 and bush 16. The above disclosed principles and features apply also in the solution of Figure 11. However, in the disclosed impact device 12 the percussion piston 21 may be bearing mounted to the bush 16 without any special rear bearing element. Alternatively, an inner surface 18 of the bush 16 may be provided with an integrated bearing portion 60. Another difference is that the control valve 26 may be arranged outside the bush 16. The rear end of the percussion piston 21 comprises a shoulder, which may serve as a pull shoulder 33. When the percussion piston 21 is pulled in the return direction B by means of an external dismounting force, a first counter surface 34 of the pull shoulder 33 becomes into contact with a second counter surface 36 of the bush 16. Thus, also in this embodiment the bush 16 may be removed by means of the percussion piston 21. The dismounting of the impact device 12 is shown in Figure 12.

1. An impact device comprising: a percussion piston (21), which is an elongated object and provided with at least one first working pressure surface (24) for moving the percussion piston (21) in an impact direction (A) by means of pressure medium, and at least one second working pressure surface (25) for moving the percussion piston (21) in a return direction (B), and the percussion piston (21) comprising a front end facing the impact direction and a rear end facing the return direction; a bush (16), which is an elongated object and provided with an outer surface (17) and an inner surface (18); and wherein the percussion piston (21) is located inside the bush (16); the outer surface (17) of the bush (16) being provided with support surfaces for supporting the bush (16) to a device frame (20) separate from the impact device (14); at least one bearing (22) for supporting the percussion piston (21) to the bush (16); and pressure medium ducts for connecting the working pressure surfaces (24, 25) of the percussion piston (21) to a pressure medium system; characterized in that the percussion piston (21) comprises at least one pull shoulder (33), which comprises an outer diameter and further a first counter surface (34) facing the return direction (B); the inner surface (18) of the bush (16) is provided with at least one counter section located between the pull shoulder (33) and a rear end of the bush (16), and the counter section comprises an inner diameter and further a second counter surface facing the impact direction (A); the outer diameter of the pull shoulder (33) is greater than the inner diameter of the counter section; and the first counter surface (34) of the pull shoulder (33) and the second counter surface (36) of the counter section are allowed to abut when the percussion piston (21) is pulled in the return direction (B).

2. The impact device as claimed in claim 1, characterized in that: the impact device (12) comprises at least one front bearing (22) at the front end portion of the percussion piston (21) for supporting the percussion piston (21) to the bush (16); and: the pull shoulder (33) is located between the front bearing (22) and the rear end of the percussion piston (21). 3. The impact device as claimed in claim 1 or 2, characterized in that: the inner diameter of the counter section is the smallest diameter in the inner surface (18) of the bush (16). 4. The impact device as claimed in any one of the preceding claims 1 to 3, characterized in that: the pull shoulder (33) and the counter section are allowed to form a closed pressure space between the percussion piston (21) and the bush (16) when the percussion piston (21) is moved to an extreme position in the return direction (B); and: the closed pressure space is serving as an end cushion in the return direction (B) during an operating cycle of the impact device (12). 5. The impact device as claimed in any one of the preceding claims 1 to 4, characterized in that: the impact device (12) comprises at least one control valve (26) for controlling pressure medium affecting working pressure surfaces (24, 25) of the percussion piston (21); and: the control valve (26) is a sleeve-like piece and is located in an annular space between the percussion piston (21) and the bush (16). 6. The impact device as claimed in any one of the preceding claims 1 to 5, characterized in that: the outer surface (17) of the bush (16) is provided with two circular support surfaces (39, 40) locating at an axial distance from each other, and both have outer diameters (D1, D2);: the front end of the bush (16) is provided with a first support surface (39) and the rear end is provided with a second support surface (40);: the first support surface (39) has a first axial length (L1) and the second support surface (40) has a second axial length (L2);: the outer surface (17) of the bush (16) is provided with an intermediate section (41) between the first support surface (39) and the second support surface (40);: the diameter (D1) of the first support surface (39) is smaller than the diameter (D2) of the second support surface (40); and: a diameter (D3) of the intermediate section (41) is smaller than the diameter (D2) of the second support surface (40). 7. The impact device as claimed in claim 6, characterized in that: the bush (16) has an axial length (Ltot) which is at least double compared to the greatest axial length (L1, L2) of either of the first support surface (39) and the second support surface (40). 8. A rock drilling machine (4) comprising: a frame (20); an impact device (12) inside the frame (20); and a rotating device (10); characterized in that the impact device (12) is in accordance with claims 1 to 7. 9. The rock drilling machine as claimed in claim 8, characterized in that: the frame (20) comprises a rear end, which is provided with a rear cover; and: the bush (16) inside the frame (20) is allowed to be extracted by means of the percussion piston (21) in the return direction (B) when the rear cover is removed. 10. A breaking hammer (14) comprising: a frame (20); and an impact device (12) inside the frame (20); characterized in that the impact device (12) is in accordance with claims 1 to 7. 11. The breaking hammer as claimed in claim 10, characterized in that: the frame (20) comprises a rear end, which is provided with a rear cover; and: the bush (16) inside the frame (20) is allowed to be extracted by means of the percussion piston (21) in the return direction (B) when the rear cover is removed.

2873489

Impact device and method of dismounting the same

Based on the following detailed description of an invention, generate the patent claims. There should be 4 claims in total. The first, independent claim is given and the remaining 3 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a feasible rock drilling unit 1 which may be connected by means of a boom 2 to a movable carrier, which is not shown. The drilling unit 1 may comprise a feed beam 3 and a rock drilling machine 4 supported on it. The rock drilling machine 4 may be moved on the feed beam 3 by means of a feed device 5. The rock drilling machine 4 comprises a shank 6 at a front end of the rock drilling machine 4 for connecting a tool 7. The tool 7 may comprise one or more drill rods 8 and a drill bit 9 located at a distal end of the tool 7. The rock drilling machine 4 may further comprise a rotating device 10 for rotating the shank 6 and the tool 7 connected to the shank 6. Inside a frame 11 of the rock drilling machine 4 is an impact device 12 comprising a reciprocating percussion piston for generating impact pulses to the tool 7. At a drilling site, one or more drill holes are drilled with the drilling unit 1. The drill holes may be drilled in a horizontal direction, as shown in Figure 1, or in a vertical direction. The disclosed solution is known as top-hammer drilling. The features disclosed in this application may be applied in such drilling machines. In an alternative drilling solution, which is known as down-the-hole or DTH -drilling, the impact device is located inside a bore hole. Then the impact device and a rotating device are located at opposite ends of the drilling equipment. The features disclosed in this application may also be applied in drilling machines of this type. Figure 2 discloses an excavator 13 provided with a boom 2. At a distal end of the boom 2 there is a breaking hammer 14, which comprises an impact device 12 arranged inside a frame 11 of the breaking hammer 14. The impact device 12 may be in accordance with the solution disclosed in this application. In Figures 1 and 2 two different breaking devices 15, namely a rock drilling machine 4 and a breaking hammer 14, are shown. As already mentioned above, the impact device 14 of the breaking device 15 may be in accordance with the disclosed solution and include the features disclosed above. The frame 11 of the breaking device 15 may also comprise the features disclosed in this application. Figure 3 shows a rear portion of a breaking device 15 comprising an impact device 12. The impact device 12 comprises a bush 16 which is a sleeve-like piece. The bush 16 is an elongated object and has a total axial length Ltot, an outer surface 17 and an inner surface 18. The bush 16 is arranged inside an impact device space, which is located at the rearmost end of a frame 20 of the breaking device 15. Inside the bush 16 is a percussion piston 21, which is supported to the bush 16 by means of a front bearing 22 and a rear bearing 23. During operation the percussion piston 21 is moved forwards in an impact direction A for striking a tool and is moved backwards in a return direction B. Thus, the percussion piston 21 is reciprocating during a work cycle of the impact device 12. The impact device 12 is hydraulically operated whereby the percussion piston 21 comprises one or more first working pressure surfaces 24 affecting in the impact direction A and one or more second working pressure surfaces 25 affecting in the return direction B. The percussion piston 21 is moved back and forth by changing hydraulic pressure acting on the working pressure surfaces. In the solution disclosed in Figure 3 pressure affecting the first working pressure surfaces 24 is controlled by means of a control valve 26. Hydraulic pressure affecting the second working pressure surfaces 25 is not varied by the control valve 26. However, the impact device may also be constructed so that pressure affecting in a front pressure chamber 27 is varied as well as pressure in a rear pressure chamber 51 for implementing the work cycle of percussion piston. Hydraulic pressure medium is fed from a hydraulic system to a feed duct or port 29 and the pressure medium is discharged from the impact device through a discharge duct or port 30. The control valve 26 may be a sleeve-like piece arranged around the rear end portion of the piston 21. The control valve 26 may slide in the impact direction A and return direction B in an annular valve space arranged between the inner surface of the bush 16 and the percussion piston 21. The control valve 26 may be pressure controlled whereby it is provided with pressure surfaces, and pressure medium is directed to the these pressure surfaces for moving the sliding valve between front and rear positions according to the working cycle. The bush 16 comprises radial openings at the control valve space for directing pressure medium flows controlled by the control valve 26. The bush 16 may further comprise one or more axial control pressure ducts 31 for directing pressure medium to control pressure surfaces of the control valve 26. The control of the working cycle of the impact device 12 is known to skilled persons and is therefore not described in more detail in the present application. The impact device 12 is construed so that the bush 16 may be extracted from the impact space inside the frame 20 by means of the percussion piston 21. Therefore the rear end of the frame 20 is provided with a rear cover 32, or a corresponding rear element, which closes the rear end of the frame 20. When the rear cover 32 is removed, the impact device 12 can be pulled out by directing an axial dismounting force FB to the rear end portion of the percussion piston 21. The dismounting force FB is external to the impact device, which in practice means that the percussion piston 21 is pulled by means of a lifting device or a corresponding actuator or auxiliary device. In order to transmit the dismounting force FB from the percussion piston 21 to the bush 16, the percussion piston 21 is provided with a pull shoulder 33. The pull shoulder 33 is located somewhere behind the front bearing 22. In the solution disclosed in Figure 3 the pull shoulder 33 is in the front pressure chamber 37. Alternatively, the pull shoulder 33 may be located in a middle section or even in a rear end section of the percussion piston 21, depending on the location of the control valve 26 and the basic structure of the impact device 12. In order words, the pull shoulder may be located between the front bearing 22 and the rear end of the percussion piston 21. The pull shoulder 33 comprises an axial first counter surface 34 facing the return direction B. The inner surface 18 of the bush 16 is provided with a counter section 35 comprising a second counter surface 36 facing the impact direction A. When the percussion piston 21 is pulled in the return direction B, the percussion piston 21 moves relative to the bush 16 and the first counter surface 34 becomes into contact with the second counter surface 36 of the bush 16. Then, the force effect of the dismounting force FB is transmitted from the percussion piston 21 to the bush 16 causing the percussion piston 21 and the bush 16 to move together axially in the return direction B. The outer dimension of the pull shoulder 33 is greater than the inner dimension of the counter section 35, whereby the percussion piston 21 may not be pulled completely out of the bush 16 in the return direction B. The pull shoulder 33 may form a closed space 38 when the percussion piston 21 moves close to a forward extreme position. The bush 16 may be supported to the frame 20 by means of support surfaces 39 and 40 on the outer surface 17 of the bush 16. A first support surface 39 is at the front end portion of the bush 16 and a second support surface 40 is at the rear end portion of the bush 16. The first support surface 39 has a first axial length L1 and a first diameter D1. The second support surface 40 has a second axial length L2 and a second diameter D2. The first length L1 and the second length L2 may be equal or the lengths may differ from each other. The first diameter D1 is smaller than the second diameter D2, whereby the bush 16 has a narrow front end and a wide rear end. Between the first support surface 39 and the second support surface 40 may be an intermediate section 41, which has a third axial length L3 and third outer diameter D3. The frame 20 comprises an impact device space wherein the bush 16 is arranged. The frame 20 comprises in the impact device space surfaces that are dimensioned to correspond with the diameters D1 and D2 of the bush 16 so that the bush 16 is supported firmly in place when being mounted inside the impact device space. However, the third diameter D3 may be dimensioned so that between the frame 20 and the outer surface of the intermediate section 41 remains a clearance 42. The clearance 42 facilitates mounting and dismounting of the impact device 12. Figure 3 further shows that at the front end of the bush 16 may be a front bearing module 43 comprising a supporting body and the front bearing 22. Correspondingly, the rear end of the bush 16 may comprise a rear bearing module 44 comprising a supporting body and the rear bearing 23. The bearing modules 43 and 44 may also comprise one or more seals. The bearing modules 43 and 44 may be extracted simultaneously with the percussion piston 21 and the bush 16. Alternatively, the front bearing module 43 may be construed and supported in such a way that it is not extracted together with the other components of the impact device 12. In this alternative embodiment the front bearing module 43 is dismounted in a separate step. In an additional alternative embodiment the pull shoulder 33 may be located elsewhere as compared to the embodiment shown in Figure 3. Thus, a shoulder 45 may serve as a pull shoulder and the working pressure surface 24 may then serve as a first counter surface. When the percussion piston is pulled in the return direction during the dismounting procedure, then the surface 24 abuts a surface 46 of the bush 16. In this embodiment the first counter surface of the pull shoulder serves during the normal operating cycle of the impact device 12 as a dampening component, since the shoulder 45 forms a closed dampening space when the percussion piston 21 moves to an extreme rear position. Figure 3 also shows that the bush 16 comprises pressure surfaces 47 and 48, which are connected to the feed duct 29 either directly or by means of one or more axial pressure channels 49. The pressure surfaces 47 and 48 produce an axial force in the return direction B when the impact device 12 is pressurized. The pressure surface 47 exists because of a difference in diameters D1 and D3, and correspondingly the pressure surface 48 exists because the diameter D2 is greater than the diameter D3. Thanks to the pressure surfaces and the generated force, the bush 16 is pushed continuously towards the rear cover 32 during the operation. Thus, the bush is always positioned in an accurate position and the impact device operates as designed. Let it be mentioned that in this application the terms front and front direction mean impact direction A, and the terms rear and rear direction mean return direction B. Figure 4 shows that the rear end of the percussion piston 21 may comprise a fastening point 50 allowing a fitting tool to be connected to the rear end of the piston 21. The fastening point 50 may comprise an axial blind opening with inner threads, for example. In Figure 4 some of the seals S are marked with reference markings. As can be noted in Figure 4, the impact device 12 may have a modular or cartridge structure that comprises all the necessary components in one uniform package. The impact device 12 may be pre-assembled by mounting the rear bearing module 44 to the rear end of the bush 16. Thereafter the rear end of percussion piston 21 may be inserted in the front end of the bush 16 and may be pushed in the rearward direction until the pull shoulder 33 abuts the second counter surface 36. After this, the front bearing module 43 may be mounted to the front end of the bush 16. The bearing modules 43 and 44 are provided with the needed bearings 22, 23 and seals S. Figures 5 to 7 show another embodiment, which has only few differences compared to the solution disclosed in Figures 3 and 4. As can be noted, in Figure 5 the frame 20 does not comprise the axial pressure channel 49 for conveying pressure medium from the feed port 29 to a rear pressure chamber 51 via the control valve 26. Instead, the intermediate section 41 of the bush 16 is provided with one or more pressure channels 52 allowing pressure medium to flow from the feed port 29 to a space 53 and further under control of the control valve 26 to the rear pressure space 51. As already discussed above, between the outer surface of the intermediate section 41 and the inner surface of the bush 16 there may be a clearance needed to facilitate the mounting and dismounting of the impact device 12. In addition to the clearance, the outer surface of the intermediate section 41 may comprise one or more grooves 54 or corresponding flow passages. As shown in Figure 6 the outer surface of the intermediate section 41 may have splined configuration and may then have several axial grooves 54 between radial splines 55. Figures 8a and 8b show in a simplified manner a mounting principle of the impact device 12 to the frame 20 of the braking device 15. The outer dimensions of the bush 16 as well as the inner dimensions of supporting surfaces 56a - 56c are exaggerated for ease of understanding. The bush 16 tapers towards the front end, which facilitates mounting. The tapered first support surface 39 passes easily through the supporting surfaces 56b and 56c of the frame 20 having greater dimensions. The mounting may be executed in a vertical position whereby the rear end of the frame is pointing upwards. The rear cover is removed and an impact device space 57 is open to receive the impact device 12. In Figure 8a the impact device 12 is lifted by means of a lifting device above the frame 20 and is positioned to a center line 58 of the impact device space 57. The bush 16 is supported by the pull shoulder 33 of the percussion piston 21. A fitting tool 59 is attached to the rear end of the percussion piston 21 enabling the lifting and handling of the impact device by means of the lifting device. In Figure 8b the impact device 12 is lowered and the impact device 12 has penetrated into the impact device space 57. Figure 9 shows a simplified chart wherein some steps and features relating to dismounting of an impact device are shown. These issues are disclosed already above in this application. Figure 10 shows a simplified chart, wherein some steps and features relating to mounting of an impact device are shown. These issues are disclosed already above in this application, Figure 11 shows an alternative impact device 12 and bush 16. The above disclosed principles and features apply also in the solution of Figure 11. However, in the disclosed impact device 12 the percussion piston 21 may be bearing mounted to the bush 16 without any special rear bearing element. Alternatively, an inner surface 18 of the bush 16 may be provided with an integrated bearing portion 60. Another difference is that the control valve 26 may be arranged outside the bush 16. The rear end of the percussion piston 21 comprises a shoulder, which may serve as a pull shoulder 33. When the percussion piston 21 is pulled in the return direction B by means of an external dismounting force, a first counter surface 34 of the pull shoulder 33 becomes into contact with a second counter surface 36 of the bush 16. Thus, also in this embodiment the bush 16 may be removed by means of the percussion piston 21. The dismounting of the impact device 12 is shown in Figure 12.

12. A method of dismounting an impact device (12) from a breaking device (15),: wherein the breaking device (15) comprises at least a frame (20), an impact device (12) arranged inside the frame (20) and a rear cover at a rear end of the frame (20), and wherein the impact device (12) comprises at least a bush (16) and a percussion piston (21) inside the bush (16);: the method comprising: removing the rear cover; and dismounting the impact device (12) from inside the frame (20) in a return direction (B) of the impact device (12); characterized by generating an external axial dismounting force (FB) in the return direction (B) of the impact device (12) and directing the external dismounting force (FB) to the percussion piston (21) during the dismounting; and extracting the bush (16) outside the frame (20) by means of the percussion piston (21).

13. The method according to claim 12, characterized by dismounting the impact device (12) as one single object comprising the bush (16), the percussion piston (21), and bearings (22, 23) and seals between the percussion piston (21) and the bush (16). 14. The method according to claim 12 or 13, characterized by: dismounting the impact device (12) while the frame (20) of the breaking device (15) is fastened to a work machine. 15. The method as claimed in any one of claims 12 to 14 characterized by: connecting a separate fitting tool (59) to the rear end of the percussion piston (21);: transmitting the dismounting force (FB) via the fitting tool (59) to the percussion piston (21); and: transmitting the dismounting force (FB) by means of at least one pull shoulder (33) in the percussion piston (21) to at least one counter surface (36) inside the bush (16).

2873640

An apparatus and a method for alignment of an elevator guide rail

Based on the following detailed description of an invention, generate the patent claims. There should be 11 claims in total. The first, independent claim is given and the remaining 10 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a vertical cross section of an elevator. The elevator comprises a car 10, an elevator shaft 20, a machine room 30, lifting machinery 40, ropes 41, and a counter weight 42. The car 10 is supported on a sling 11 surrounding the car 10. The lifting machinery 40 moves the car 10 in a vertical direction S1 upwards and downwards in the vertically extending elevator shaft 20. The car 10 is carried through the sling 11 by the ropes 41, which connect the car 10 to the counter weight 42. The sling 11 of the car 10 is further supported with gliding means 70 at guide rails 50 extending in the vertical direction in the shaft 20. The figure shows two guide rails 50 at opposite sides of the car 10. The gliding means 70 can comprise rolls rolling on the guide rails 50 or gliding shoes gliding on the guide rails 50 when the car 10 is mowing upwards and downwards in the elevator shaft 20. The guide rails 50 are supported with fastening brackets 60 at the side wall structures 21 of the elevator shaft 20. The figure shows only two fastening brackets 60, but there are several fastening brackets 60 along the height of each guide rail 50. The gliding means 70 engaging with the guide rails 50 keep the car 10 in position in the horizontal plane when the car 10 moves upwards and downwards in the elevator shaft 20. The counter weight 42 is supported in a corresponding way on guide rails supported on the wall structure 21 of the shaft 20. The car 10 transports people and/or goods between the landings in the building. The elevator shaft 20 can be formed so that the wall structure 21 is formed of solid walls or so that the wall structure 21 is formed of an open steel structure. The guide rails 50 extend vertically along the height of the shaft 20. The guide rails 50 are thus formed of rail elements of a certain length. The rail elements are connected in the installation phase end-on-end one after the other. It is time consuming to install the guide rails 50 so that they are properly aligned along the whole height of the shaft 20. The alignment is in prior art solutions done manually by forcing or moving the support bracket 60 with a hand tool. The quality of the alignment varies depending of the person who is doing the manual alignment. Deviations in the alignment of the guide rail 50 will result in lateral forces acting on the gliding means 70 when the car 10 moves upwards and downwards in the shaft 20. These lateral forces might cause vibrations to the gliding means 70 and thereby also to the car 10. The vibrations acting on the car 10 will also cause noise disturbing the passengers in the car 10. Figure 2 shows an axonometric view of an apparatus according to the invention and fig. 3 shows the apparatus of figure 2 attached to a support bracket of a guide. The apparatus 500 for aligning a guide rail 50 in a shaft 20 comprises a first part 100, a second part 200 and a link arm mechanism 300 connecting the first part 100 and the second part 200. The first part 100 of the apparatus 500 can be attached to a support bracket 60 supporting the guide rail 50 on the wall structure 21 of the shaft 20. The guide rail 50 can be attached to the second part 200 of the apparatus 500. The link arm mechanism 300 comprises a first link arm 310 having a first end and an opposite second end 102 and a second link arm 320 having a first end 321 and an opposite second end 322. The first end 311 of the first link arm 310 is attached with a first articulated joint J1 movably to the first part 100 of the apparatus 500 and the second end 312 of the first link arm 310 is attached with a fourth articulated joint J4 movably to the second part 200 of the apparatus 500. The first end 321 of the second link arm 320 is attached with a second articulated joint J2 movably to the first part 100 of the apparatus 500 and a second opposite end 322 of the second link arm 320 is attached with a third articulated joint J3 to the second part 200 of the apparatus 500. The crosswise running first link arm 310 and second link arm 320 are attached to each other with a fifth articulated joint J5 in the point where the first link arm 310 and the second link arm 320 are crossing each other. Each link arm 310, 320 is formed of two superimposed bars being connected to each other with an intermediate member at both sides of the fifth joint J5. The first part 100 of the apparatus 500 comprises a first end 101 and an opposite second end 102 as well as a longitudinal first direction X1. The first part 100 is attached to a support bracket 60 so that the back side B1 of the first part 100 sets against the support bracket 60. The support bracket 60 is formed of a first L-shaped part 61 attached to the wall structure 21 of the shaft 20 and a second L-shaped part 62 attached to the first L-shaped part 61. The support bracket 60 comprises further a plate 63 that has been attached to the second L-shaped part 62. The guide rail 50 can be attached with clamps 64 and bolts and nuts to the plate 63. The first L-shaped part 61 and the second L-shaped part 62 are attached to each other with bolts and nuts. The holes for the bolts are longitudinal allowing adjustment of the position between the first and the second L-shaped part 61, 62. The first part 100 of the apparatus 500 is thus a stationary part. The second part 200 of the apparatus 500 comprises a first end 201 and an opposite second end 202 as well as a second longitudinal direction X2. The second part 200 can be moved with the link arm mechanism 300 in relation to the first part 100. The guide rail 50 is attached to the front side F2 of the second part 200 of the apparatus 500. The second part 200 of the apparatus 500 can be moved in the first direction X1 with a first actuator A1 being formed of a first adjustment screw A1, in a third direction Y with a second actuator A2 being formed of a second adjustment screw A2, and in a fourth angular direction α with a third actuator A3 being formed of a third adjustment screw A3. The first direction X1 runs essentially parallel to the plane of the wall structure 21 onto which the support bracket 60 is fastened in the shaft 20. The third direction Y is perpendicular to the first direction X1. The fourth angular direction α is the angular direction of the second part 200 of the apparatus 500 in relation to the fourth articulated joint J4. The second part 200 can thus be turned with the third adjustment screw A3 so that the first part 100 and the second part 200 are non-parallel i.e. the first direction X1 and the second direction X2 are non-parallel. Figure 3 shows also the fairing equipment used in connection with the adjustment of the guide rail 50. The fairing equipment comprises a sheet 410 adapted on the guide rail 50, a support arm 420 with a laser prism 430 and a laser beam L1. The guide rails 50 at opposite side walls 21 of the shaft 20 are faired in the fourth angular direction α with a horizontal laser beam L1 extending from the fairing equipment on one guide rail 50 to the fairing equipment on the opposite guide rail 50. The guide rail 50 is faired in the first direction X1 and the third direction Y with a vertical laser beam passing through the laser prism 430 in the support arm 420. Figure 4 shows a front view of a first part of the apparatus of figure 3. The first part 100 of the apparatus 500 has an essentially rectangular form and comprises an upper section 110 and a lower section 120. The upper section 110 comprises further a first sub-section 111 and a second sub-section 112 located at the second end 102 of the first part 100. A first quick clamping means 115 is located in the first sub-section 111 and a second quick clamp means 116 is located in the second sub-section 112. The first sub-section 111 is stationary and the second sub-section 112 is movable in the first direction X1. The second sub-section 112 can glide on guide bars 113 in the first direction X1 between an inner position and an outer position. This makes it possible to adjust the distance X10 in the first direction X1 between the quick clamping means 115, 116 of the first part 100. The first part 100 is attached with the quick clamping means 115, 116 to the outer end of the anchor bolts of the support bracket 60. Each quick clamping means 115, 116 can comprise a spherical plain bearing that grip on the outer ends of the anchor bolts. The spherical bearing can be operated with a nut at the front surface of the first part 100. The first part 100 can thus simply be pushed on the support bracket 60 so that the outer ends of the anchor bolts of the support bracket 60 become seated in the spherical plain bearings. The tightening of the first part 100 against the support bracket 60 is then done by turning the nuts at the front surface of the first part 100. The lower section 120 of the first part 100 comprises a first guide rod 122 extending in the first direction X1. A first 123 support element and a second support element 124 are attached to the first guide rod 122. The first support element 123 and the second support element 124 can glide on the first guide rod 122 in the first direction X1 to the left and to the right in the figure. The first end 311 of the first link arm 310 is attached with the first articulated joint J1 to the first support element 123. The first end 321 of the second link arm 320 is attached with the second articulated joint J2 to the second support element 124. The lower section 120 of the first part 100 comprises further a first support part 121 that is attached to the lower section 120 at the first end 101 of the first part 100. The first support part 121 is provided with a first hole 121a that extends in the first direction X1 through the first support part 121. The first hole 121a is provided with an internal threading. The first adjustment screw A1 is provided with an external threading and extends through the first hole 121a in the first support part 121. One end of the first adjustment screw A1 is attached to the first support element 123. Rotation of the first adjustment screw A1 in the first hole 121a will thus move the first support element 123 on the first guide rod 122 in the first direction X1 either to the left or to the right in the figure. The first adjustment screw A1 will also retain the first support element 123 in place on the first guide rod 122. The second support element 124 is connected via the second articulated joint J2, the fifth articulated joint J5 in the intersection of the link arms 310, 320 and the first articulated joint J1 to the first support element 123. The second support element 124 will thus follow the movement of the first support element 123 in the first direction X1. The fourth articulated joint (J4) will be stationary. The second part 200 of the apparatus 500 will thus move in synchronism with the first adjustment screw A1 in the first direction X1. Figure 5 shows a back view and fig. 6 shows a front view of the second part of the apparatus of figure 3. The second part 200 comprises a first section 210 and a second section 220 at the first end 201 of the second part 200. The second section 220 forms an angle of 90 degrees with the first section 210. The first section 210 and the second section 220 can be formed of a rectangular bar that is bent 90 degrees at one end. A second guide rail 212 extending in the first direction X1 is attached to the first section 210. A third support element 213 is attached to the second guide rail 212. The third support element 213 can glide on the second guide rail 212 in the second direction X2 to the left and to the right in the figure. A second support part 230 is attached to the second end 202 of the second part 200 so that the second support part 230 forms an angle of 90 degrees with the first section 210 of the second part 200. The second support part 230 is provided with a second hole 230a extending in the second direction X2 through the second support part 230. The second hole 230a is provided with an internal threading. The second adjustment screw A2 is provided with an external threading and extends through the second hole 230a in the second support part 230. One end of the second adjustment screw A2 is attached to the third support element 213. Rotation of the second adjustment screw A2 in the second hole 230a will thus move the third support element 213 on the second guide rod 212 in the second direction X2 either to the left or to the right in the figure. The second adjustment screw A2 will also retain the third support element 213 in place on the second guide rod 212. A third support part 240 is attached to the second section 220 of the second part 200. The third adjustment screw A3 extends in the third direction Y into the third support part 240. The second part 200 will turn around the fourth articulated joint J4 when the third adjustment screw A3 moves the second section 220 in relation to the third support part 240. The third adjustment screw A3 will also retain the second part 200 in place in a given angular position. The second end 322 of the second link arm 320 is attached with a third articulated joint J3 to the third support part 240. The second end 312 of the first link arm 310 is attached with a fourth articulated joint J4 to the third support element 213. Rotation of the second adjustment screw A2 will move the second part 200 in the third direction Y in relation to the first stationary part 100. Rotation of the second adjustment screw A2 moves the third support element 213 on the second guide rail 212 in the second direction X2 either to the left or to the right in the figure. The first articulated point J1 will be stationary, the second articulated joint J2 will move in the first direction X1 along the first guide rod 122, the fourth articulated joint J4 and the fifth articulated joint J5 will move along respective circular paths around the centre point i.e. the first articulated joint J1 and the third articulated joint J3 will move in the third direction Y. The second part 200 of the apparatus 500 will thus move in the third direction Y when the second adjustment screw A2 is rotated. Movement of the third support element 213 to the left in figure 2 will increase the distance between the second part 200 and the first part 100 in the third direction Y, and vice a versa. Rotation of the third adjustment screw A3 will move the second section 220 in relation to the third support part 240. The second part 200 will thus turn around the fourth articulated joint J4 when the third adjustment screw A3 is rotated. The third articulated joint J3 will be stationary during the rotation of the third adjustment screw A3. This means that the second part 200 of the apparatus can be turned in the fourth angular direction α around the fourth articulated joint J4 with the third adjustment screw A3. The first direction X1 and the second direction X2 are parallel when the third adjustment screw A3 is in a zero position. The first part 100 and the second part 200 are in such a situation parallel. An angular displacement of the second part 200 from the neutral position will make the second direction X2 non-parallel with the first direction X1. The second part 200 of the apparatus 500 comprises quick clamping means 250, 251 for fastening the guide rail 50 to the front surface F2 of the second part 200. The quick clamping means 250, 251 can comprise screws and washers. The circular perimeter of the washer forms at a certain sector a straight line as a part of the washer has been cut away. The guide rail 50 can be positioned between the washers against the outer surface F2 of the second part 200. The washers are then rotated so that the edge of the washers set on the guide rail 50. Figure 7 shows a further axonometric view of the second part of the apparatus showing the angular adjustment in more detail. The second section 220 of the second part 200 comprises a protrusion 221 and two glide members 222, 223. The third support part 240 comprises a first cavity 241 receiving the protrusion 231 of the second section 212 and two oval holes 242, 243 receiving the glide members 222, 223 of the second section 220. The third adjustment screw A3 extends in the third direction Y through a third hole 240a into the third support part 240. The internal end of the third adjustment screw A3 comprises an outer threading. The protrusion 221 comprises a fourth threaded hole 221a extending in the third direction Y. The third adjustment screw A3 can be screwed into the fourth threaded hole 221a in the protrusion 221 when the protrusion 221 is located in the first cavity 241 in the third support part 240. The third adjustment screw A3 is locked in the third direction Y to the third support part 240. The second section 220 of the second part 200 is supported within the third support part 240 through the glide members 222, 223 gliding in the two oval holes 242, 243 in the third support part 240. The second part 200 will turn around the fourth articulated joint J4 when the third adjustment screw A3 moves the protrusion 221 in the cavity 241. The third adjustment screw A3 will also retain the second part 200 in place in a given angular α position. The guide rail 50 is first adjusted into the correct position with the apparatus 500 after which the guide rail 50 is fastened to the support bracket 60. The adjustment possibilities in the support bracket 60 are used so that the guide rail 50 becomes attached to the support bracket 60 exactly in the position determined by the apparatus 500. The apparatus 500 is then released and moved to the next fastening point. The arrangement could naturally also be reversed so that the first adjustment screw A1 would be located at the second end 102 of the first part 100, whereby the first adjustment screw A1 would act on the second support element 124. Also the arrangement in the second part 200 would then have to be reversed so that the first end 201 of the second part 200 would be at the right in figure 2 and the second end 202 of the second part 200 would be at the left in figure 2. The fourth articulated joint J4 would be attached to the stationary third support part 240 and the third articulated joint J3 would be attached to the movable third support element 213. The support elements 123, 124, 213 are in the figures gliding on the guide rods 122, 212. The arrangement could naturally also be such that the support elements 123, 124, 213 roll instead of glide on the guide rods 122, 212. The adjustment of the second part 200 in relation to the first part 100 is in the embodiment shown in the figures done manually with actuators in the form of adjustment screws A1, A2, A3. The adjustment could naturally be done automatically. The adjustment screws A1, A2, A3 could be replaced with other kind of actuators in the form of e.g. electric motors or hydraulic or pneumatic cylinder-piston apparatuses. These other kind of actuators would then be used to move the first support element 123, the third support element 213 and the movable part in the stationary third support part 240. The third adjustment screw A3 is in the embodiment shown in the figures extending into the third support part 240 and acts on the protrusion 221 of the second section 220 of the second part 200 within the third support part 240. This is a compact and advantageous arrangement, but this could be done in varies other ways. The essential aspect is to have the second part 200 movably supported on the third support part 230 and to use a third actuator A3 moving the second part 200 in a fourth angular direction α around the fourth articulated joint J4. The third actuator A3 could be positioned on the third support part 240 or on the second part 200. The first adjustment screw A1 and the second adjustment screw A2 could further be provided with quick releasing means in the first support part 121 and the second support part 230. The quick releasing means would unlock and lock the screws to the threads 121a, 230a in the support parts 121, 230. This would make it faster to adjust the second part 200 into approximately the right position before starting the actual alignment of the guide rail 50. The first part 100 comprises in the embodiment shown in the figures an upper section 110 and a lower section 120. The upper section 110 comprises further a stationary first sub-section 111 and a movable second sub-section 112 gliding on guide bars 13 in the first direction X1 between an inner position and an outer position. The upper section 110 could instead be formed of a single part. There adjustment of the distance X10 between the quick clamping means 115, 116 could be achieved by arranging a longitudinal hole in connection with at least one of the quick clamping means 115, 116. The upper section 110 and the lower section 120 in the first part 100 could be formed of separate parts or of a single part. The use of the invention is naturally not limited to the type of elevator disclosed in figure 1, but the invention can be used in any type of elevator e.g. also in elevators lacking a machine room and/or a counterweight.

1. An apparatus for alignment of an elevator guide rail, characterized in that the apparatus (500) comprises: a stationary first part (100) having a first end (101) and an opposite second end (102) and a first longitudinal direction (X1), a movable second part (200) having a first end (201) and an opposite second end (202) and a second longitudinal direction (X2), a link arm mechanism (300) connecting the first part (100) and the second part (200), said link arm mechanism (300) comprising a first link arm (310) having a first end (311) and an opposite second end (312) and a second link arm (320) having a first end (321) and an opposite second end (322), whereby: the first end (311) of the first link arm (310) is attached with a first articulated joint (J1) to a first support element (123) being movable and retainable with a first actuator (A1) in the first direction (X1) along the first part (100) of the apparatus (500) and the second end (312) of the first link arm (310) is attached with a fourth articulated joint (J4) to a third support element (213) being movable and retainable with a second actuator (A2) in the second direction (X2) along the second part (200) of the apparatus (500), the first end (321) of the second link arm (320) is attached with a second articulated joint (J2) to a second support element (124) being movable in the first direction (X1) along the first part (100) of the apparatus (500) and the second end (322) of the second link arm (320) is attached with a third articulated joint (J3) to a third support part (240), the first end (201) of the second part (200) being movably supported on the third support part (240), a third actuator (A3) moving and retaining the second part (200) in relation to the third support part (240), the first link arm (310) and the second link arm (320) is connected to each other with a fifth articulated joint (J5) in a point where the first link arm (310) and the second link arm (320) intersect, the first actuator (A1) moves the second part (200) in the first direction (X1), the second actuator (A2) moves the second part (200) in a third direction (Y) being perpendicular to the first direction (X1), the third actuator (A3) moves the second part (200) in a fourth angular direction (α) around the fourth articulated joint (J4).

2. An apparatus according to claim 1, characterized in that a first guide rod (122) extending in the first direction (X1) is attached to the first part (100), whereby the first support element (123) and the second support element (124) are attached to the first guide rod (122) so that they glide along the first guide rod (122). 3. An apparatus according to claim 1 or 2, characterized in that a second guide rod (212) extending in the second direction (X2) is attached to the second part (200), whereby the third support element (213) is attached to the second guide rod (212) so that it glides along the second guide rod (212). 4. An apparatus according to any one of claims 1 to 3, characterized in that the first actuator (A1) is formed of a screw (A1) extending in the first direction (X1) through a first threaded hole (121a) in a first support part (121) being supported on the first part (100) in the first end (101) of the first part (100), whereby one end of the first adjustment screw (A1) is attached to the first support element (123) so that the first support element (123) moves in the first direction (X1) when the first adjustment screw (A1) is turned in the first threaded hole (121a). 5. An apparatus according to any one of claims 1 to 4, characterized in that the second actuator (A2) is formed of a second adjustment screw (A2) extending in the second direction (X2) through a second threaded hole (230a) in a second support part (230) being supported on the second part (200) in the second end (202) of the second part (200), whereby one end of the second adjustment screw (A2) is attached to the third support element (213) so that the third support element (213) moves in the second direction (X2) when the second adjustment screw (A2) is turned in the second threaded hole (230a). 6. An apparatus according to any one of claims 1 to 5, characterized in that the third actuator (A3) is formed of a third adjustment screw (A3) extending in the third direction (Y) through a fourth hole (240a) into a cavity (241) in the third support part (240), the cavity (241) receiving a protrusion (221) comprising a third threaded hole (221a) extending in the third direction (Y) and being attached to the first end (201) of the second part (200), whereby an inner end of the third adjustment screw (A3) passes into the third threaded hole (221a) so that the second part (200) moves in an angular (α) direction around the fourth articulated joint (J4) when the third adjustment screw (A3) is turned in the third threaded hole (221a). 7. An apparatus according to any one of claims 1 to 6, characterized in that the first part (100) is attached to a support bracket (60) supporting the elevator guide rail (50) on a wall structure (21) of an elevator shaft (20) and that the guide rail (50) is attached to a front side (F2) of the second part (200). 8. An apparatus according to claim 7, characterized in that the first part (100) of the apparatus (500) comprises first quick clamping means (115) and second quick clamping means (116) for attaching the first part (100) to the anchor bolts of the support bracket (60). 9. An apparatus according to claim 7 or 8, characterized in that the second part (200) of the apparatus (500) comprises third quick clamping means (250) and fourth quick clamping means (251) for attaching the guide rail (50) to the front side (F2) of the second part (200). 10. An apparatus according to any one of claims 1 to 9, characterized in that the first part (100) comprises an upper section (110) and a lower section (120), the upper section (110) comprising further a stationary first sub-section (111) and a movable second sub-section (112) gliding on guide bars (13) in the first direction (X1) between an inner position and an outer position, whereby a distance (X10) in the first direction (X1) between first quick clamping means (115) located in the first sub-section (111) and second quick clamping means (116) located in the second sub-section (112) is adjustable. 11. Method for aligning an elevator guide rail, characterized in that the method comprises the steps of: fastening the first part (100) of the apparatus (500) according to any one of claims 1-10 to anchoring bolts of a support bracket (60) of the guide rail (50), fastening the guide rail (50) to the second part (200) of the apparatus (500), adjusting the guide rail (50) into a desired position with the apparatus (500), fastening the guide rail (50) to the support bracket (60), unfastening the guide rail (50) from the second part (200) of the apparatus (500), unfastening the first part (100) of the apparatus (500) from the anchoring bolts of the support bracket (60), removing the apparatus (500).

2873358

Pivoting handle for a surface cleaning device

Based on the following detailed description of an invention, generate the patent claims. There should be 4 claims in total. The first, independent claim is given and the remaining 3 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 is an enlarged partial perspective view of a conventional handle 10 for a cleaning device or upright-type vacuum cleaner 20. The handle 10 is coupled to the cleaner housing 30 at a pivot joint 40. A "handle" as used herein includes definitions that are generally known in the mechanical art, and may include a handgrip. For example, the handle 10 includes any structure that extends generally upwardly from the cleaner housing 30 that transfers forces caused by the operator to the cleaning device 20 to move the cleaning device 20 over a surface to be cleaned. Referring also to Figures 2 and 3, the cleaner housing 30 defines a centerline 50. The pivot joint 40 is configured to rotate the handle 10 about a pivot axis 60 that is perpendicular to the centerline 50. In both the operating (see Figure 1 ) and the storage (see Figures 2 and 3 ) positions, the handle 10 extends substantially parallel to the centerline 50. For operating the vacuum cleaner 20, the handle 10 is rotated upwardly about the pivot axis 60 so that the handle 10 extends upwardly and away from the cleaner housing 30. As used herein, the terms "top," "bottom," "front," "rear," "side," "upwardly," "downwardly," and other directional terms are not intended to require any particular orientation, but are instead used for purposes of description only. For storing or stowing, the handle 10 is rotated downwardly. In this configuration, when viewed from a direction perpendicular to the centerline 50 (see Figure 2 ), the handle 10 protrudes from the outer profile of the cleaner housing 30, thereby requiring additional space for storing the vacuum cleaner 20. Thus, there has developed a need for a mechanism that enables storing the vacuum cleaner in a compact footprint. Figure 4 illustrates a vacuum cleaner 100 with an elongate handle 110. Referring also to Figure 5, the vacuum cleaner 100 includes a suction nozzle 120, a cleaner housing or body 130 connected to the suction nozzle 120, a suction generator (not shown) in the cleaner housing 130, and a dirt collection vessel (not shown) in the cleaner housing 130. The handle 110 is coupled to the cleaner housing 130 at a pivot or hinge joint 140. The cleaner housing 130 defines a central longitudinal axis or centerline 150. The pivot joint 140 is configured to rotate the handle 110 about a pivot axis 160 that is non-perpendicular to the longitudinal axis 150. Referring also to Figure 6, the handle 110 extends non-perpendicular to the pivot axis 160. That is, the handle 110 is offset from an orientation 164 perpendicular to the pivot axis 160 at an acute angle θ. As such, when the handle 110 is folded downwardly, the handle 110 is rotated substantially conically about the pivot axis 160. In some embodiments, the pivot axis 160 is offset from an orientation perpendicular to the longitudinal axis 150 by approximately 5° to approximately 7°. In other embodiments, however, the pivot axis 160 may extend at other angles that are non-perpendicular to the longitudinal axis 150. Referring also to Figure 7, when the handle 110 is rotated or folded downwardly for storing or shipping, the handle 110 moves to a position adjacent to and offset from the cleaner housing 130 of the vacuum cleaner 100. In contrast to prior art configurations, the handle 110 does not substantially protrude from the outer profile or contour of the cleaner housing 130 when the handle 110 is rotated downwardly. As such, the vacuum cleaner 100 can be shipped or stored with the handle 110 in the folded position in a compact package without substantially increasing the footprint of the product compared to prior art configurations. In the illustrated embodiment, the pivot joint 140 includes a female member 170 coupled to the cleaner housing 130 and a male member 180 coupled to the handle 110. In other embodiments, however, the female member 170 can be coupled to the handle 110 and the male member 180 can be coupled to the cleaner housing 130. The male member 180 is positioned proximate the female member 170, and a pin 190 is insertable through the female and male members 170, 180 to couple the cleaner housing 130 and the handle 110 together. The female and male members 170, 180 are so dimensioned as to give a smooth substantially bulbous appearance when the pin 190 is inserted through the female and male members 170, 180. Although in the illustrated embodiment only a single male member 180 on the handle 110 and only a single female member 170 on the cleaner housing 130 are shown, in further embodiments, the handle 110 may include one or more male members 180, one or more female members 170, or a combination thereof. Similarly, the cleaner housing 130 may also include one or more female members 170, one or more male members 180, or a combination thereof. The pivot joint 140 thus suitably includes one or more female and male members 170, 180. Moreover, although Figures 4-6 illustrate the female and male members 170, 180 as integrally formed with the cleaner housing 130 and handle 110, respectively, in other embodiments the female and male members 170, 180 may be separately formed and attached to a respective one of the cleaner housing 130 and handle 110 via glue or fasteners. In some embodiments, the vacuum cleaner 100 includes a locking unit 200, which includes a detent 204 and a corresponding catch mechanism 208 (not shown in Figures 4-7 ; see, e.g., Figure 11 ) between the cleaner housing 130 and the handle 110, and a release member 210 connected to the detent 204. The locking unit 200 is configured to releasably lock the handle 110 solely in a position substantially parallel to the longitudinal axis 150, i.e., the operating position. The release member 210 may be spring-loaded or biased by any other suitable mechanisms. The detent is selectively movable between a locked position where the detent 204 contacts the corresponding catch mechanism 208, and an unlocked position where the detent 204 is released out of the locking position. When the user rotates the handle 110 upwardly from the storage position toward the operating position, the detent 204 contacts the catch mechanisms 208 and locks the handle 110 so that the handle 110 fixedly extends upwardly and away from the cleaner housing 130. When the user depresses the release member 210 against the bias toward the handle 110, the detent 204 is released out of the locking position, thereby enabling the handle 110 to rotate or fold downwardly toward the storage position. The surface cleaning device 100 is a vacuum cleaner adapted to clean a variety of surfaces, such as carpets, hardwood floors, tiles, or the like. More specifically, the illustrated surface cleaning device 100 is an upright wet vacuum cleaner capable of drawing in air and dirt such as liquid and debris. In alternative embodiments, the surface cleaning device 100 may not be a wet vacuum cleaner. Rather, the surface cleaning device 100 may be a dry vacuum cleaner capable of drawing in air and dirt such as dry debris. Alternatively, the surface cleaning device 100 may be an extractor capable of both dispensing liquid and drawing in air and dirt such as liquid and debris. In yet other embodiments, the surface cleaning device 100 may be a steam cleaner that dispenses liquid or steam but does not include a suction source. In still other embodiments, the surface cleaning device 100 may be a stick vacuum that does not include the brush rolls of other traditional upright cleaners. In additional embodiments, surface cleaning device 100 may be a sweeper that includes a handle and a pivoting base that supports a wet or dry cloth that is positioned below the base. These sweepers do not dispense liquid and do not include a suction source. Figures 8-11 illustrate the vacuum cleaner 100 including a pivot joint 140 according to another embodiment of the invention. Like parts are identified using like reference numerals. The pivot joint 140 in this embodiment is configured to rotate the handle 110 about the pivot axis 160, and also to translate the handle 110 along the pivot axis 160. In the illustrated embodiment, the pivot axis 160 is non-perpendicular to the longitudinal axis 150 so as to store or stow the handle 110 at an orientation offset from the longitudinal axis 150. In other embodiments, however, the pivot axis 160 can be perpendicular to the longitudinal axis 150. As such, the handle 110 can be stored or stowed at a position that is linearly, but not angularly, offset from the longitudinal axis 150. The pivot joint 140 includes a female member 220 coupled to the handle 110 and a male member 230 coupled to the cleaner housing 130. The male member 230 is received into the female member 220 to couple the cleaner housing 130 and the handle 110 together. In the illustrated embodiment, the male member 230 includes a projection or thread 240, and the female member 220 includes a groove 250 that corresponds to the projection 240. In some embodiments, the projection 240 extends helically about the pivot axis 160. The projection 240 and the groove cooperate together to translate the handle 110 along the pivot axis 160. That is, when viewed from the rear in a direction substantially perpendicular to the longitudinal axis 150, the handle 110 is translated generally from right to left along the pivot axis 160 as the handle 110 is rotated from the operating position (see Figures 8 and 10 ) to the storage position (see Figures 9 and 11 ). In other embodiments, the male member 230 may include the groove 250 and the female member 220 may include the projection 240. In still other embodiments, the female member 220 may be coupled to the cleaner housing 130 and the male member 230 may be coupled to the handle 110. Although the invention has been described in detail with reference to certain preferred embodiments, variations and modifications exist within the scope and spirit of one or more independent aspects of the invention as described.

1. A surface cleaning device, the device defining a longitudinal axis, the device comprising: a nozzle; a cleaner housing connected to the nozzle; and a handle coupled to the cleaner housing at a pivot joint, wherein the pivot joint is configured to rotatably store the handle at a position offset from the longitudinal axis.

2. The surface cleaning device of claim 1, wherein the pivot joint is configured to rotate the handle about a pivot axis that is non-perpendicular to the longitudinal axis. 3. The surface cleaning device of claim 1 or 2, wherein the pivot joint is configured to rotate the handle about a pivot axis and to translate the handle in a direction along the pivot axis. 4. The surface cleaning device of claim 1, 2 or 3, further comprising a suction generator and a dirt collection vessel in the cleaner housing.

2873358

Pivoting handle for a surface cleaning device

Based on the following detailed description of an invention, generate the patent claims. There should be 6 claims in total. The first, independent claim is given and the remaining 5 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 is an enlarged partial perspective view of a conventional handle 10 for a cleaning device or upright-type vacuum cleaner 20. The handle 10 is coupled to the cleaner housing 30 at a pivot joint 40. A "handle" as used herein includes definitions that are generally known in the mechanical art, and may include a handgrip. For example, the handle 10 includes any structure that extends generally upwardly from the cleaner housing 30 that transfers forces caused by the operator to the cleaning device 20 to move the cleaning device 20 over a surface to be cleaned. Referring also to Figures 2 and 3, the cleaner housing 30 defines a centerline 50. The pivot joint 40 is configured to rotate the handle 10 about a pivot axis 60 that is perpendicular to the centerline 50. In both the operating (see Figure 1 ) and the storage (see Figures 2 and 3 ) positions, the handle 10 extends substantially parallel to the centerline 50. For operating the vacuum cleaner 20, the handle 10 is rotated upwardly about the pivot axis 60 so that the handle 10 extends upwardly and away from the cleaner housing 30. As used herein, the terms "top," "bottom," "front," "rear," "side," "upwardly," "downwardly," and other directional terms are not intended to require any particular orientation, but are instead used for purposes of description only. For storing or stowing, the handle 10 is rotated downwardly. In this configuration, when viewed from a direction perpendicular to the centerline 50 (see Figure 2 ), the handle 10 protrudes from the outer profile of the cleaner housing 30, thereby requiring additional space for storing the vacuum cleaner 20. Thus, there has developed a need for a mechanism that enables storing the vacuum cleaner in a compact footprint. Figure 4 illustrates a vacuum cleaner 100 with an elongate handle 110. Referring also to Figure 5, the vacuum cleaner 100 includes a suction nozzle 120, a cleaner housing or body 130 connected to the suction nozzle 120, a suction generator (not shown) in the cleaner housing 130, and a dirt collection vessel (not shown) in the cleaner housing 130. The handle 110 is coupled to the cleaner housing 130 at a pivot or hinge joint 140. The cleaner housing 130 defines a central longitudinal axis or centerline 150. The pivot joint 140 is configured to rotate the handle 110 about a pivot axis 160 that is non-perpendicular to the longitudinal axis 150. Referring also to Figure 6, the handle 110 extends non-perpendicular to the pivot axis 160. That is, the handle 110 is offset from an orientation 164 perpendicular to the pivot axis 160 at an acute angle θ. As such, when the handle 110 is folded downwardly, the handle 110 is rotated substantially conically about the pivot axis 160. In some embodiments, the pivot axis 160 is offset from an orientation perpendicular to the longitudinal axis 150 by approximately 5° to approximately 7°. In other embodiments, however, the pivot axis 160 may extend at other angles that are non-perpendicular to the longitudinal axis 150. Referring also to Figure 7, when the handle 110 is rotated or folded downwardly for storing or shipping, the handle 110 moves to a position adjacent to and offset from the cleaner housing 130 of the vacuum cleaner 100. In contrast to prior art configurations, the handle 110 does not substantially protrude from the outer profile or contour of the cleaner housing 130 when the handle 110 is rotated downwardly. As such, the vacuum cleaner 100 can be shipped or stored with the handle 110 in the folded position in a compact package without substantially increasing the footprint of the product compared to prior art configurations. In the illustrated embodiment, the pivot joint 140 includes a female member 170 coupled to the cleaner housing 130 and a male member 180 coupled to the handle 110. In other embodiments, however, the female member 170 can be coupled to the handle 110 and the male member 180 can be coupled to the cleaner housing 130. The male member 180 is positioned proximate the female member 170, and a pin 190 is insertable through the female and male members 170, 180 to couple the cleaner housing 130 and the handle 110 together. The female and male members 170, 180 are so dimensioned as to give a smooth substantially bulbous appearance when the pin 190 is inserted through the female and male members 170, 180. Although in the illustrated embodiment only a single male member 180 on the handle 110 and only a single female member 170 on the cleaner housing 130 are shown, in further embodiments, the handle 110 may include one or more male members 180, one or more female members 170, or a combination thereof. Similarly, the cleaner housing 130 may also include one or more female members 170, one or more male members 180, or a combination thereof. The pivot joint 140 thus suitably includes one or more female and male members 170, 180. Moreover, although Figures 4-6 illustrate the female and male members 170, 180 as integrally formed with the cleaner housing 130 and handle 110, respectively, in other embodiments the female and male members 170, 180 may be separately formed and attached to a respective one of the cleaner housing 130 and handle 110 via glue or fasteners. In some embodiments, the vacuum cleaner 100 includes a locking unit 200, which includes a detent 204 and a corresponding catch mechanism 208 (not shown in Figures 4-7 ; see, e.g., Figure 11 ) between the cleaner housing 130 and the handle 110, and a release member 210 connected to the detent 204. The locking unit 200 is configured to releasably lock the handle 110 solely in a position substantially parallel to the longitudinal axis 150, i.e., the operating position. The release member 210 may be spring-loaded or biased by any other suitable mechanisms. The detent is selectively movable between a locked position where the detent 204 contacts the corresponding catch mechanism 208, and an unlocked position where the detent 204 is released out of the locking position. When the user rotates the handle 110 upwardly from the storage position toward the operating position, the detent 204 contacts the catch mechanisms 208 and locks the handle 110 so that the handle 110 fixedly extends upwardly and away from the cleaner housing 130. When the user depresses the release member 210 against the bias toward the handle 110, the detent 204 is released out of the locking position, thereby enabling the handle 110 to rotate or fold downwardly toward the storage position. The surface cleaning device 100 is a vacuum cleaner adapted to clean a variety of surfaces, such as carpets, hardwood floors, tiles, or the like. More specifically, the illustrated surface cleaning device 100 is an upright wet vacuum cleaner capable of drawing in air and dirt such as liquid and debris. In alternative embodiments, the surface cleaning device 100 may not be a wet vacuum cleaner. Rather, the surface cleaning device 100 may be a dry vacuum cleaner capable of drawing in air and dirt such as dry debris. Alternatively, the surface cleaning device 100 may be an extractor capable of both dispensing liquid and drawing in air and dirt such as liquid and debris. In yet other embodiments, the surface cleaning device 100 may be a steam cleaner that dispenses liquid or steam but does not include a suction source. In still other embodiments, the surface cleaning device 100 may be a stick vacuum that does not include the brush rolls of other traditional upright cleaners. In additional embodiments, surface cleaning device 100 may be a sweeper that includes a handle and a pivoting base that supports a wet or dry cloth that is positioned below the base. These sweepers do not dispense liquid and do not include a suction source. Figures 8-11 illustrate the vacuum cleaner 100 including a pivot joint 140 according to another embodiment of the invention. Like parts are identified using like reference numerals. The pivot joint 140 in this embodiment is configured to rotate the handle 110 about the pivot axis 160, and also to translate the handle 110 along the pivot axis 160. In the illustrated embodiment, the pivot axis 160 is non-perpendicular to the longitudinal axis 150 so as to store or stow the handle 110 at an orientation offset from the longitudinal axis 150. In other embodiments, however, the pivot axis 160 can be perpendicular to the longitudinal axis 150. As such, the handle 110 can be stored or stowed at a position that is linearly, but not angularly, offset from the longitudinal axis 150. The pivot joint 140 includes a female member 220 coupled to the handle 110 and a male member 230 coupled to the cleaner housing 130. The male member 230 is received into the female member 220 to couple the cleaner housing 130 and the handle 110 together. In the illustrated embodiment, the male member 230 includes a projection or thread 240, and the female member 220 includes a groove 250 that corresponds to the projection 240. In some embodiments, the projection 240 extends helically about the pivot axis 160. The projection 240 and the groove cooperate together to translate the handle 110 along the pivot axis 160. That is, when viewed from the rear in a direction substantially perpendicular to the longitudinal axis 150, the handle 110 is translated generally from right to left along the pivot axis 160 as the handle 110 is rotated from the operating position (see Figures 8 and 10 ) to the storage position (see Figures 9 and 11 ). In other embodiments, the male member 230 may include the groove 250 and the female member 220 may include the projection 240. In still other embodiments, the female member 220 may be coupled to the cleaner housing 130 and the male member 230 may be coupled to the handle 110. Although the invention has been described in detail with reference to certain preferred embodiments, variations and modifications exist within the scope and spirit of one or more independent aspects of the invention as described.

5. A surface cleaning device, the device defining a longitudinal axis, the device comprising: a nozzle; a cleaner housing connected to the nozzle; and a handle coupled to the cleaner housing at a pivot joint, wherein the pivot joint is configured to rotate the handle about a pivot axis that is non-perpendicular to the longitudinal axis.

6. The surface cleaning device of claim 5, wherein the pivot joint includes a female member coupled to one of the cleaner housing and the handle, a male member coupled to the other of the cleaner housing and the handle and positioned proximate the female member, and a pin insertable through the female and male members to couple the cleaner housing and the handle together. 7. The surface cleaning device of claim 5 or 6, wherein the pivot axis is offset from an orientation perpendicular to the longitudinal axis by approximately 5° to approximately 7°. 8. The surface cleaning device of claim 5, 6 or 7, further comprising a locking unit, the locking unit configured to releasably lock the handle solely in a position substantially parallel to the longitudinal axis. 9. The surface cleaning device of claim 8, wherein the locking unit includes a detent between the cleaner housing and the handle, and a release member connected to the detent. 10. The surface cleaning device of any one of claims 5 to 9, further comprising a suction generator in the cleaner housing and a dirt collection vessel in the cleaner housing.

2873358

Pivoting handle for a surface cleaning device

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 is an enlarged partial perspective view of a conventional handle 10 for a cleaning device or upright-type vacuum cleaner 20. The handle 10 is coupled to the cleaner housing 30 at a pivot joint 40. A "handle" as used herein includes definitions that are generally known in the mechanical art, and may include a handgrip. For example, the handle 10 includes any structure that extends generally upwardly from the cleaner housing 30 that transfers forces caused by the operator to the cleaning device 20 to move the cleaning device 20 over a surface to be cleaned. Referring also to Figures 2 and 3, the cleaner housing 30 defines a centerline 50. The pivot joint 40 is configured to rotate the handle 10 about a pivot axis 60 that is perpendicular to the centerline 50. In both the operating (see Figure 1 ) and the storage (see Figures 2 and 3 ) positions, the handle 10 extends substantially parallel to the centerline 50. For operating the vacuum cleaner 20, the handle 10 is rotated upwardly about the pivot axis 60 so that the handle 10 extends upwardly and away from the cleaner housing 30. As used herein, the terms "top," "bottom," "front," "rear," "side," "upwardly," "downwardly," and other directional terms are not intended to require any particular orientation, but are instead used for purposes of description only. For storing or stowing, the handle 10 is rotated downwardly. In this configuration, when viewed from a direction perpendicular to the centerline 50 (see Figure 2 ), the handle 10 protrudes from the outer profile of the cleaner housing 30, thereby requiring additional space for storing the vacuum cleaner 20. Thus, there has developed a need for a mechanism that enables storing the vacuum cleaner in a compact footprint. Figure 4 illustrates a vacuum cleaner 100 with an elongate handle 110. Referring also to Figure 5, the vacuum cleaner 100 includes a suction nozzle 120, a cleaner housing or body 130 connected to the suction nozzle 120, a suction generator (not shown) in the cleaner housing 130, and a dirt collection vessel (not shown) in the cleaner housing 130. The handle 110 is coupled to the cleaner housing 130 at a pivot or hinge joint 140. The cleaner housing 130 defines a central longitudinal axis or centerline 150. The pivot joint 140 is configured to rotate the handle 110 about a pivot axis 160 that is non-perpendicular to the longitudinal axis 150. Referring also to Figure 6, the handle 110 extends non-perpendicular to the pivot axis 160. That is, the handle 110 is offset from an orientation 164 perpendicular to the pivot axis 160 at an acute angle θ. As such, when the handle 110 is folded downwardly, the handle 110 is rotated substantially conically about the pivot axis 160. In some embodiments, the pivot axis 160 is offset from an orientation perpendicular to the longitudinal axis 150 by approximately 5° to approximately 7°. In other embodiments, however, the pivot axis 160 may extend at other angles that are non-perpendicular to the longitudinal axis 150. Referring also to Figure 7, when the handle 110 is rotated or folded downwardly for storing or shipping, the handle 110 moves to a position adjacent to and offset from the cleaner housing 130 of the vacuum cleaner 100. In contrast to prior art configurations, the handle 110 does not substantially protrude from the outer profile or contour of the cleaner housing 130 when the handle 110 is rotated downwardly. As such, the vacuum cleaner 100 can be shipped or stored with the handle 110 in the folded position in a compact package without substantially increasing the footprint of the product compared to prior art configurations. In the illustrated embodiment, the pivot joint 140 includes a female member 170 coupled to the cleaner housing 130 and a male member 180 coupled to the handle 110. In other embodiments, however, the female member 170 can be coupled to the handle 110 and the male member 180 can be coupled to the cleaner housing 130. The male member 180 is positioned proximate the female member 170, and a pin 190 is insertable through the female and male members 170, 180 to couple the cleaner housing 130 and the handle 110 together. The female and male members 170, 180 are so dimensioned as to give a smooth substantially bulbous appearance when the pin 190 is inserted through the female and male members 170, 180. Although in the illustrated embodiment only a single male member 180 on the handle 110 and only a single female member 170 on the cleaner housing 130 are shown, in further embodiments, the handle 110 may include one or more male members 180, one or more female members 170, or a combination thereof. Similarly, the cleaner housing 130 may also include one or more female members 170, one or more male members 180, or a combination thereof. The pivot joint 140 thus suitably includes one or more female and male members 170, 180. Moreover, although Figures 4-6 illustrate the female and male members 170, 180 as integrally formed with the cleaner housing 130 and handle 110, respectively, in other embodiments the female and male members 170, 180 may be separately formed and attached to a respective one of the cleaner housing 130 and handle 110 via glue or fasteners. In some embodiments, the vacuum cleaner 100 includes a locking unit 200, which includes a detent 204 and a corresponding catch mechanism 208 (not shown in Figures 4-7 ; see, e.g., Figure 11 ) between the cleaner housing 130 and the handle 110, and a release member 210 connected to the detent 204. The locking unit 200 is configured to releasably lock the handle 110 solely in a position substantially parallel to the longitudinal axis 150, i.e., the operating position. The release member 210 may be spring-loaded or biased by any other suitable mechanisms. The detent is selectively movable between a locked position where the detent 204 contacts the corresponding catch mechanism 208, and an unlocked position where the detent 204 is released out of the locking position. When the user rotates the handle 110 upwardly from the storage position toward the operating position, the detent 204 contacts the catch mechanisms 208 and locks the handle 110 so that the handle 110 fixedly extends upwardly and away from the cleaner housing 130. When the user depresses the release member 210 against the bias toward the handle 110, the detent 204 is released out of the locking position, thereby enabling the handle 110 to rotate or fold downwardly toward the storage position. The surface cleaning device 100 is a vacuum cleaner adapted to clean a variety of surfaces, such as carpets, hardwood floors, tiles, or the like. More specifically, the illustrated surface cleaning device 100 is an upright wet vacuum cleaner capable of drawing in air and dirt such as liquid and debris. In alternative embodiments, the surface cleaning device 100 may not be a wet vacuum cleaner. Rather, the surface cleaning device 100 may be a dry vacuum cleaner capable of drawing in air and dirt such as dry debris. Alternatively, the surface cleaning device 100 may be an extractor capable of both dispensing liquid and drawing in air and dirt such as liquid and debris. In yet other embodiments, the surface cleaning device 100 may be a steam cleaner that dispenses liquid or steam but does not include a suction source. In still other embodiments, the surface cleaning device 100 may be a stick vacuum that does not include the brush rolls of other traditional upright cleaners. In additional embodiments, surface cleaning device 100 may be a sweeper that includes a handle and a pivoting base that supports a wet or dry cloth that is positioned below the base. These sweepers do not dispense liquid and do not include a suction source. Figures 8-11 illustrate the vacuum cleaner 100 including a pivot joint 140 according to another embodiment of the invention. Like parts are identified using like reference numerals. The pivot joint 140 in this embodiment is configured to rotate the handle 110 about the pivot axis 160, and also to translate the handle 110 along the pivot axis 160. In the illustrated embodiment, the pivot axis 160 is non-perpendicular to the longitudinal axis 150 so as to store or stow the handle 110 at an orientation offset from the longitudinal axis 150. In other embodiments, however, the pivot axis 160 can be perpendicular to the longitudinal axis 150. As such, the handle 110 can be stored or stowed at a position that is linearly, but not angularly, offset from the longitudinal axis 150. The pivot joint 140 includes a female member 220 coupled to the handle 110 and a male member 230 coupled to the cleaner housing 130. The male member 230 is received into the female member 220 to couple the cleaner housing 130 and the handle 110 together. In the illustrated embodiment, the male member 230 includes a projection or thread 240, and the female member 220 includes a groove 250 that corresponds to the projection 240. In some embodiments, the projection 240 extends helically about the pivot axis 160. The projection 240 and the groove cooperate together to translate the handle 110 along the pivot axis 160. That is, when viewed from the rear in a direction substantially perpendicular to the longitudinal axis 150, the handle 110 is translated generally from right to left along the pivot axis 160 as the handle 110 is rotated from the operating position (see Figures 8 and 10 ) to the storage position (see Figures 9 and 11 ). In other embodiments, the male member 230 may include the groove 250 and the female member 220 may include the projection 240. In still other embodiments, the female member 220 may be coupled to the cleaner housing 130 and the male member 230 may be coupled to the handle 110. Although the invention has been described in detail with reference to certain preferred embodiments, variations and modifications exist within the scope and spirit of one or more independent aspects of the invention as described.

11. A surface cleaning device, the device defining a longitudinal axis, the device comprising: a nozzle; a cleaner housing connected to the nozzle; and a handle coupled to the cleaner housing at a pivot joint, wherein the pivot joint is configured to rotate the handle about a pivot axis, and to translate the handle in a direction along the pivot axis.

12. The surface cleaning device of claim 11 including one or more of the following features: a) the pivot joint includes a female member coupled to one of the cleaner housing and the handle, and a male member coupled to the other of the cleaner housing and the handle, the male member received into the female member to couple the cleaner housing and the handle together; b) the pivot axis is non-perpendicular to the longitudinal axis; c) the pivot axis is offset from an orientation perpendicular to the longitudinal axis by approximately 5° to approximately 7°; d) a locking unit, the locking unit configured to releasably lock the handle solely in a position substantially parallel to the longitudinal axis; and e) a suction generator and a dirt collection vessel in the cleaner housing. 13. The surface cleaning device of claim 12, wherein one of the female and male members includes a projection, the other of the female and male members includes a groove corresponding to the projection, and the projection and the groove cooperate together to translate the handle. 14. The surface cleaning device of claim 13, wherein at least one of the projection and the groove extends helically about the pivot axis. 15. The surface cleaning device of claim 12, wherein the locking unit includes a detent between the cleaner housing and the handle, and a release member connected to the detent.

2873821

Exhaust gas aftertreatment device

Based on the following detailed description of an invention, generate the patent claims. There should be 13 claims in total. The first, independent claim is given and the remaining 12 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an embodiment of an inventive exhaust gas aftertreatment device 1 for an Internal Combustion Engine (ICE) (not shown), comprising a catalytic converter 2. The catalytic converter 2 comprises an encapsulating member 3. In turn, the encapsulating member 3 comprises a first end portion 4, a second end portion 6, wherein the second end portion 6 is provided at the opposite end of the catalytic converter 2 as the first end portion 4, and a midsection 5, wherein the midsection 5 is provided between the first end portion 4 and the second end portion 6 such that the midsection 5 connects the first end portion 4 with the second end portion 6. The outside of the encapsulating member 3 defines an outer perimeter of the catalytic converter 2 and the inside of the encapsulating member 3 defines a converter volume 7 of the catalytic converter 2. According to the invention the cross sectional area of the encapsulating member 3 can be of any suitable shape, such as round, rectangular, square etc. A first catalytic converter substrate 8 and a second catalytic converter substrate 9 are arranged within the encapsulating member 3. The first catalytic converter substrate can preferably be a Diesel Oxidation Catalyst (DOC) and/or a Lean NOx Trap (LNT) or a Three Way Catalyst (TWC) and the second catalytic converter substrate can preferably be a substrate with SCR functionality (SCR). The functionality of the possible catalytic substrates, used as first and second catalytic converter substrate, are not described herein since this is considered to be part of common knowledge. According to the embodiment of the invention shown in Figure 1, the converter volume 7 is divided in a first volume 21, a second volume 22 and a third volume 23, wherein the first volume 21 is provided adjacent to the first catalytic converter substrate 8, the third volume 23 is provided adjacent to the second catalytic converter substrate 9 and the second volume 22 is provided between the first catalytic converter substrate 8 and the second catalytic converter substrate 9. Additionally, an exhaust gas guiding means 12 is arranged within the encapsulating member 3 in the second volume 22. The exhaust gas guiding means 12 comprises a first open section 13 and a second open section 14, wherein the first open section 13 is substantially smaller than the second open section 14. The first and second open sections 13;14 are connected by a circumferential surface. As shown in Figure 1 the exhaust gas guiding means 12 comprises a curved section 24 between the first open section 13 and the second open section 14. The curved section 24 is provided such that when the exhaust gas guiding means 12 is exposed to hot exhaust gas emissions, which if the exhaust gas guiding means 12 is provided in a metallic material can cause thermal expansion of the exhaust gas guiding means 12, the curved section 24 can absorb stress created in the metallic material due to said thermal expansion, and thus prevent excess force on the inside of the encapsulating member 5. The curved section 24 makes the exhaust gas guiding means 12 resilient to hot exhaust gas emissions. As is obvious since the first open section 13 has smaller cross sectional area than the second open section 14, the curved section 24 of the exhaust gas guiding means 12 is slightly tapered. According to fig. 1 is the circumferential surface of the exhaust gas guiding means 12 tapered in an inwardly convex manner. The first open section 13 is arranged to a pipe member 11 such that a circumferential edge of the first open section 13 seals against the circumferential edge of the pipe member 11. The second open section 14 is circumferentially arranged to the midsection 5 of the encapsulating member 3 such that the second open section 14 seals against the midsection 5 of the encapsulating member 3. This arrangement provides that the second volume 22 is divided into a first part of the second volume 22a and a second part of the second volume 22b. The cross sectional area of the pipe member 11 as well as the exhaust gas guiding means 12 can be of any suitable shape, such as round, rectangular, square etc., as long as the exhaust gas guiding means 12 can be arranged to seal against the pipe member 11 and the midsection 5 of the encapsulating member 3. According to the invention disclosed in Figure 1 the pipe member 11 is provided within the second catalytic converter substrate 9, wherein the pipe member 11 is extending in the longitudinally direction of the catalytic converter 2, such that said pipe member 11 is connecting the first part of the second volume 22a with the third volume 23. The pipe member 11 provides improved mixing of the exhaust gases by guiding said exhaust gases in a first flow direction A from said first part of the second volume 22a to said third volume 23 by prolonging the mixing period before the exhaust gases reaches the second catalytic converter substrate 9. Thus, the pipe member 11 enables that the catalytic converter 2, comprising two catalytic converter substrates 8;9, can be designed to be more compact without having negative impact on the exhaust gas emissions mixing characteristics. According to the embodiment if the inventive catalytic converter 2 disclosed in Figure 1 the pipe member 11 is arranged substantially centrally in the second catalytic converter 9. Additionally, according to the embodiment of the invention shown in Figure 1 a first port 10 is arranged in connection to the first volume 21. According to the embodiment in Figure 1 the first port 10 is acting as an inlet port receiving exhaust gases from the ICE (not shown). The exhaust gases will enter the first port in a first flow direction A. A second port 15 is arranged in fluid connection to the second part of the second volume 22b, wherein the second port 15 according to the embodiment in Figure 10 is acting as an outlet port discharging exhaust gases after catalytic conversion thereof. The discharged exhaust gases will flow through the second port in a third flow direction C. The first port 10 and the second port 15 can be formed together with the encapsulating member 3 or be separate components arranged to the encapsulating member 3. Additionally, according to the embodiment of the invention shown in Figure 1 a portion of the second end portion 6 constitutes a deflector means 18. The deflector means 18 deflects the exhaust gases from the pipe member 11, wherein the exhaust gases approaches the deflector means 18 in the first flow direction A, in a second flow direction B. According to the embodiment in Figure 1, the second flow direction B is substantially opposite to the first flow direction A. Mixing of the exhaust gases is further promoted by this deflection, resulting in improved catalytic conversion by the second catalytic converter substrate 9. Finally, the catalytic converter 2 comprises a porous material 16. According to the embodiment of the invention shown in Figure 1, the porous material is 16 provided at the end of the third volume 23 provided furthest away from the first port 10, adjacent to the deflector means 18. The porous material 16 is arranged between the pipe member 11 and the portion of the second end portion 6 constituting the deflector means 18, such that a flow flowing through the pipe member 11 in the first flow direction A is directed at the porous material 16 before reaching the deflector means 18. The porous material is arranged at a distance from the deflector means 18 such that a space 17 is formed between the porous material 16 and the deflector means 18. According to the embodiment of the inventive exhaust gas aftertreatment device 1 shown in Figure 1, the exhaust gas aftertreatment device is configured to function as follows: - Exhaust gases from the ICE (not shown) is entering the catalytic converter 2 of the exhaust gas aftertreatment device 1 through the first port 10 in a first flow direction A. When entering the first volume 21 the exhaust gas flow rate is decreased, enabling the exhaust gases to flow through the subsequently arranged first catalytic converter substrate 8 at lower rate. After the first catalytic converter substrate 8, the exhaust gases enter the first part of the second volume 22a. The subsequently arranged exhaust gas guiding means 12 guides the exhaust gas flow into the pipe member 11. The cross sectional area of the pipe member 11 and the first open section 13 of the exhaust gas guiding means 12, wherein the first open section 13 is arranged to the edge of the pipe member 11, is smaller than the cross sectional area of the second open section 14 of the exhaust gas guiding means 12, resulting in an increased exhaust gas flow rate through the pipe member 11. The increase in exhaust gas flow rate will improve the mixing of the exhaust gas, thus contribute to improved catalytic conversion. The exhaust gas emissions will flow through the pipe member in a first flow direction A into the third volume 23, wherein the flow rate once again will be decreased. According to Figure 1 the porous material 16 is arranged in the flow direction A downstream of the pipe member 11, such that the exhaust gas flow will pass through the porous material 16. After passing the porous material 16, the exhaust gases reaches the deflector means 18. The deflector means will redirect the exhaust gas flow in the second flow direction B. The exhaust gas emissions will thereafter pass through the second catalytic converter substrate 9, in the second flow direction B, and into the second part of the second volume 22b. Finally, the exhaust gas emissions will exit through the second port 15 in the third flow direction C. The inventive catalytic converter 2 can also be provided without the porous material. Figure 2a and Figure 2b shows two schematic side views of two embodiments of the inventive exhaust gas aftertreatment device 1, each comprising one possible development of reductant injection arrangement. According to Figure 2a and 2b, the second converter substrate is a substrate with SCR functionality 26. The presence of a substrate with SCR functionality26 requires that a reductant, typically anhydrous ammonia, aqueous ammonia urea etc., is added to the exhaust gas emissions flow and is absorbed onto the downstream arranged substrate with SCR functionality. Operations and the functionality of a substrate with SCR functionality are not further described herein since this is common knowledge and does not form part of the invention. According to the development of the invention shown in Figure 2a, a first example of an injector pipe 25a is provided longitudinally in the catalytic converter 2, wherein the injector pipe 25a enters the catalytic converter 2 through the second end portion 6, such that a reductant can be added to the exhaust gas emissions before the substrate with SCR functionality26. The reductant may preferably be added within the volume of the exhaust gas guiding means 12 or the volume of the pipe member 11, such that the beneficial mixing properties provided by the exhaust gas guiding means 12 and the pipe member 11 is facilitated to provide high degree of mixing between the reductant and the exhaust gas emissions. Also, this will improve the evaporation of the reductant since it will be exposed to hot exhaust gas emissions and possibly heated components for a longer period of time. Further, according to Figure 2a, the injector pipe 25a is provided such that it extends substantially centrally of the pipe member 11, into the volume of the exhaust gas guiding means 12. According to the development of the inventive exhaust gas aftertreatment device 1 shown in Figure 2b, a second example of an injector pipe 25b is entering the volume of the exhaust gas guiding means 12 in a direction substantially perpendicular to the extension of the catalytic converter 2. In the development of the invention according to fig. 2b is the injector pipe 25b inserted through the midsection 5 of the encapsulating member 3. This arrangement allows the reductant to be added to the exhaust gas emission flow within the area of the exhaust gas guiding means 12. According to a further development of the inventive exhaust gas aftertreatment device 1, the second example of an injector pipe can also be provided such that the reductant is injected to the exhaust gas emission flow within the volume of the pipe member 11. Figure 2a and Figure 2b shows developments of the inventive exhaust gas aftertreatment device 1 where the first port 10 receives exhaust gas emissions from an ICE (not shown) and exhaust gas emissions are discharged through the second port 15. In view of this, the intended exhaust gas flow is indicated by arrows in before mentioned figures. Also, in the developments of the inventive exhaust gas aftertreatment device shown in Figure 2a and Figure 2b, any injector pipe is preferably arranged to a reductant tank (not shown) and to associated components for controlling and enabling the injection of reductant. This is not further described herein since this is common knowledge and does not form part of the invention. Figure 3a and Figure 3b shows two schematic side views of the exhaust gas aftertreatment device 101 comprising two developments of exhaust gas guiding means 1012 according to the invention. According to the development of the inventive exhaust gas aftertreatment device 101 shown in Figure 3a and Figure 3b, the curved section 1024 is provided between the first open section 1013 and the second open section 1014 of the exhaust gas guiding means 1012. In the developments of the invention shown in Figure 3a and Figure 3b the entire circumferential surface connecting the first open section 1013 to the second open section 1014 is curved. It is also possible that just a smaller section of the circumferential surface is curved. The curved section 1024 connects the first open section 1013 with the second open section 1014 by forming a circumferential surface of the exhaust gas guiding means 1012. Additionally, in the development of the inventive exhaust gas aftertreatment device 101 shown in Figure 3a and Figure 3b, the curved section 1024 is provided with a circumferential section 1027a;1027b, wherein the circumferential section 1027a;1027b is provided substantially in the middle of the curved section 1024. The circumferential section 1027a;1027b is preferably configured to add additional resilience, or in other ways desirable, properties to the exhaust gas guiding means 1012. In Figure 3a, the circumferential section 1027a is in the form of a membrane, which membrane can be configured to add additional ability to withstand thermal expansion, or add other desirable properties to the exhaust gas guiding means 1012, and in Figure 3b, the circumferential section 1027b is in the form of a corrugated section of the curved section 1024, which also can improve the resilience of the curved section 1024. Finally, the operations of a catalytic converter and additional components of catalytic converters not described herein are considered to be part of common knowledge and does not form part of, nor have any impact on, the present invention.

1. An exhaust gas aftertreatment device (1) for an Internal Combustion Engine wherein the exhaust gas aftertreatment device (1) comprises a catalytic converter (2), wherein the catalytic converter (2) comprises: an encapsulating member (3) comprising a first and a second opposing end portions (4;6), and a midsection portion (5) arranged there between,: wherein an outside of the encapsulating member (3) defines the outer perimeter of the catalytic converter (2), and wherein the inside of the encapsulating member (3) defines a converter volume (7) of the catalytic converter (2),: wherein a first catalytic converter substrate (8) and a second catalytic converter substrate (9) are arranged within the converter volume (7) of the catalytic converter (2),: and wherein a first port (10) is connected to the first end portion (4) for fluid communication with the converter volume (7),: characterized in: that within the converter volume (7), starting from the first end portion (4), the following is provided in order: a first volume (21) being defined between the first end portion (4), and the first catalytic converter substrate (8), the first catalytic converter substrate (8) being arranged between the first volume (21) and a subsequently provided second volume (22), the second volume (22) being defined between the first catalytic converter substrate (8) and the second catalytic converter substrate (9), wherein the first volume (21) is in fluid communication with the second volume (22) through the first catalytic converter substrate (8), the second catalytic converter substrate (9being arranged between the second volume (22) and a subsequently provided third volume (23), and the third volume (23) being defined between the second catalytic converter substrate (9) and the second end portion (6), wherein the third volume (23) is in fluid communication with the second volume (22) through the second catalytic converter substrate (9), wherein the exhaust gas aftertreatment device (1) additionally comprises an exhaust gas guiding means (12) and a pipe member (11) within said encapsulating member (3), wherein the pipe member (11) is arranged within the second converter substrate (9) and connects the second volume (22) with the third volume (23) for fluid communication, and wherein the exhaust gas guiding means (12) is arranged in the second volume (22),: wherein a first open section (13) of the exhaust gas guiding means (14) is connected to the pipe member (11) and sealed against the pipe member (11), and a second open section (14) of the exhaust gas guiding means (12) is arranged adjacent the first catalytic converter substrate (8),: wherein the second open section (14) of the exhaust gas guiding means (12) seals against the midsection portion (5) of the encapsulating member (3) such that the second volume (22) is divided into a first part of the second volume (22a) and a second part of the second volume (22b),: wherein the first part of the second volume (22a) is provided adjacent to the first catalytic converter substrate (8) and the second part of the second volume (22b) is provided adjacent to the second catalytic converter substrate (9),: wherein a second port (15) is connected to the midsection portion (5) of the encapsulating member (3) for fluid communication with the second part of the second volume (22b),: and wherein the cross sectional area of the first open section (13) of the exhaust gas guiding means (12) is smaller than the cross sectional area of the second open section (14) of the exhaust gas guiding means (12).

2. The exhaust gas aftertreatment device (1) according to claim 2,: characterized in: that the exhaust gas guiding means (12) comprises a resilient section that changes shape when the exhaust gas guiding means (12) changes shape due to change in heat load from the exhaust gas emissions, for hindering excess force on the inside of the encapsulating member (3). 3. The exhaust gas aftertreatment device (1) according to claim 2,: : characterized in: that the exhaust gas guiding means (12) comprises a curved section (24) between the first open section (13) and the second open section (14), which curved section (24) changes shape when the exhaust gas guiding means (12) changes shape due to change in heat load from the exhaust gas emissions, for hindering excess force on the inside of the encapsulating member (3). 4. The exhaust gas aftertreatment device (1) according to claim any of the preceding claims,: characterized in: that the pipe member (11) is located centrally in the encapsulating member (3) of the catalytic converter (2), extending in the longitudinal direction thereof. 5. The exhaust gas aftertreatment device (1) according to claim any of the preceding claims,: characterized in: that the second end portion (6) forms a deflector means (18), configured to deflect the exhaust gas emissions. 6. The exhaust gas aftertreatment device (1) according to any of the preceding claims,: characterized in: that the exhaust gas emission flow is directed from the first port (10) to the second port (15). 7. The exhaust gas aftertreatment device (1) according to claim 6,: characterized in: that the first catalytic converter substrate (8) is a Diesel Oxidation Catalyst, DOC, and/or a Lean NOx Trap, LNT. 8. The exhaust gas aftertreatment device (1) according to claim 6,: characterized in: that the first catalytic converter substrate (8) is a Three Way Catalyst, TWC. 9. The exhaust gas aftertreatment device (1) according to one of the claim 6 to 8,: characterized in: that the second catalytic converter substrate (9) is a substrate with SCR functionality, SCR. 10. The exhaust gas aftertreatment device (1) according to any of the claims 1 to 5,: characterized in: that the exhaust gas emission flow is directed from the second port (15) to the first port (10). 11. The exhaust gas aftertreatment device (1) according to claim 10,: characterized in: that the second catalytic converter substrate (9) is a Diesel Oxidation Catalyst, DOC, and/or a Lean NOx Trap, LNT. 12. The exhaust gas aftertreatment device (1) according to claim 10,: characterized in: that the second catalytic converter substrate (9) is a Three Way Catalyst, TWC. 13. The exhaust gas aftertreatment device (1) according to one of the claim 10 to 12,: characterized in: that the first catalytic converter substrate (8) is a substrate with SCR functionality, SCR.

2873821

Exhaust gas aftertreatment device

Based on the following detailed description of an invention, generate the patent claims. There should be 2 claims in total. The first, independent claim is given and the remaining 1 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an embodiment of an inventive exhaust gas aftertreatment device 1 for an Internal Combustion Engine (ICE) (not shown), comprising a catalytic converter 2. The catalytic converter 2 comprises an encapsulating member 3. In turn, the encapsulating member 3 comprises a first end portion 4, a second end portion 6, wherein the second end portion 6 is provided at the opposite end of the catalytic converter 2 as the first end portion 4, and a midsection 5, wherein the midsection 5 is provided between the first end portion 4 and the second end portion 6 such that the midsection 5 connects the first end portion 4 with the second end portion 6. The outside of the encapsulating member 3 defines an outer perimeter of the catalytic converter 2 and the inside of the encapsulating member 3 defines a converter volume 7 of the catalytic converter 2. According to the invention the cross sectional area of the encapsulating member 3 can be of any suitable shape, such as round, rectangular, square etc. A first catalytic converter substrate 8 and a second catalytic converter substrate 9 are arranged within the encapsulating member 3. The first catalytic converter substrate can preferably be a Diesel Oxidation Catalyst (DOC) and/or a Lean NOx Trap (LNT) or a Three Way Catalyst (TWC) and the second catalytic converter substrate can preferably be a substrate with SCR functionality (SCR). The functionality of the possible catalytic substrates, used as first and second catalytic converter substrate, are not described herein since this is considered to be part of common knowledge. According to the embodiment of the invention shown in Figure 1, the converter volume 7 is divided in a first volume 21, a second volume 22 and a third volume 23, wherein the first volume 21 is provided adjacent to the first catalytic converter substrate 8, the third volume 23 is provided adjacent to the second catalytic converter substrate 9 and the second volume 22 is provided between the first catalytic converter substrate 8 and the second catalytic converter substrate 9. Additionally, an exhaust gas guiding means 12 is arranged within the encapsulating member 3 in the second volume 22. The exhaust gas guiding means 12 comprises a first open section 13 and a second open section 14, wherein the first open section 13 is substantially smaller than the second open section 14. The first and second open sections 13;14 are connected by a circumferential surface. As shown in Figure 1 the exhaust gas guiding means 12 comprises a curved section 24 between the first open section 13 and the second open section 14. The curved section 24 is provided such that when the exhaust gas guiding means 12 is exposed to hot exhaust gas emissions, which if the exhaust gas guiding means 12 is provided in a metallic material can cause thermal expansion of the exhaust gas guiding means 12, the curved section 24 can absorb stress created in the metallic material due to said thermal expansion, and thus prevent excess force on the inside of the encapsulating member 5. The curved section 24 makes the exhaust gas guiding means 12 resilient to hot exhaust gas emissions. As is obvious since the first open section 13 has smaller cross sectional area than the second open section 14, the curved section 24 of the exhaust gas guiding means 12 is slightly tapered. According to fig. 1 is the circumferential surface of the exhaust gas guiding means 12 tapered in an inwardly convex manner. The first open section 13 is arranged to a pipe member 11 such that a circumferential edge of the first open section 13 seals against the circumferential edge of the pipe member 11. The second open section 14 is circumferentially arranged to the midsection 5 of the encapsulating member 3 such that the second open section 14 seals against the midsection 5 of the encapsulating member 3. This arrangement provides that the second volume 22 is divided into a first part of the second volume 22a and a second part of the second volume 22b. The cross sectional area of the pipe member 11 as well as the exhaust gas guiding means 12 can be of any suitable shape, such as round, rectangular, square etc., as long as the exhaust gas guiding means 12 can be arranged to seal against the pipe member 11 and the midsection 5 of the encapsulating member 3. According to the invention disclosed in Figure 1 the pipe member 11 is provided within the second catalytic converter substrate 9, wherein the pipe member 11 is extending in the longitudinally direction of the catalytic converter 2, such that said pipe member 11 is connecting the first part of the second volume 22a with the third volume 23. The pipe member 11 provides improved mixing of the exhaust gases by guiding said exhaust gases in a first flow direction A from said first part of the second volume 22a to said third volume 23 by prolonging the mixing period before the exhaust gases reaches the second catalytic converter substrate 9. Thus, the pipe member 11 enables that the catalytic converter 2, comprising two catalytic converter substrates 8;9, can be designed to be more compact without having negative impact on the exhaust gas emissions mixing characteristics. According to the embodiment if the inventive catalytic converter 2 disclosed in Figure 1 the pipe member 11 is arranged substantially centrally in the second catalytic converter 9. Additionally, according to the embodiment of the invention shown in Figure 1 a first port 10 is arranged in connection to the first volume 21. According to the embodiment in Figure 1 the first port 10 is acting as an inlet port receiving exhaust gases from the ICE (not shown). The exhaust gases will enter the first port in a first flow direction A. A second port 15 is arranged in fluid connection to the second part of the second volume 22b, wherein the second port 15 according to the embodiment in Figure 10 is acting as an outlet port discharging exhaust gases after catalytic conversion thereof. The discharged exhaust gases will flow through the second port in a third flow direction C. The first port 10 and the second port 15 can be formed together with the encapsulating member 3 or be separate components arranged to the encapsulating member 3. Additionally, according to the embodiment of the invention shown in Figure 1 a portion of the second end portion 6 constitutes a deflector means 18. The deflector means 18 deflects the exhaust gases from the pipe member 11, wherein the exhaust gases approaches the deflector means 18 in the first flow direction A, in a second flow direction B. According to the embodiment in Figure 1, the second flow direction B is substantially opposite to the first flow direction A. Mixing of the exhaust gases is further promoted by this deflection, resulting in improved catalytic conversion by the second catalytic converter substrate 9. Finally, the catalytic converter 2 comprises a porous material 16. According to the embodiment of the invention shown in Figure 1, the porous material is 16 provided at the end of the third volume 23 provided furthest away from the first port 10, adjacent to the deflector means 18. The porous material 16 is arranged between the pipe member 11 and the portion of the second end portion 6 constituting the deflector means 18, such that a flow flowing through the pipe member 11 in the first flow direction A is directed at the porous material 16 before reaching the deflector means 18. The porous material is arranged at a distance from the deflector means 18 such that a space 17 is formed between the porous material 16 and the deflector means 18. According to the embodiment of the inventive exhaust gas aftertreatment device 1 shown in Figure 1, the exhaust gas aftertreatment device is configured to function as follows: - Exhaust gases from the ICE (not shown) is entering the catalytic converter 2 of the exhaust gas aftertreatment device 1 through the first port 10 in a first flow direction A. When entering the first volume 21 the exhaust gas flow rate is decreased, enabling the exhaust gases to flow through the subsequently arranged first catalytic converter substrate 8 at lower rate. After the first catalytic converter substrate 8, the exhaust gases enter the first part of the second volume 22a. The subsequently arranged exhaust gas guiding means 12 guides the exhaust gas flow into the pipe member 11. The cross sectional area of the pipe member 11 and the first open section 13 of the exhaust gas guiding means 12, wherein the first open section 13 is arranged to the edge of the pipe member 11, is smaller than the cross sectional area of the second open section 14 of the exhaust gas guiding means 12, resulting in an increased exhaust gas flow rate through the pipe member 11. The increase in exhaust gas flow rate will improve the mixing of the exhaust gas, thus contribute to improved catalytic conversion. The exhaust gas emissions will flow through the pipe member in a first flow direction A into the third volume 23, wherein the flow rate once again will be decreased. According to Figure 1 the porous material 16 is arranged in the flow direction A downstream of the pipe member 11, such that the exhaust gas flow will pass through the porous material 16. After passing the porous material 16, the exhaust gases reaches the deflector means 18. The deflector means will redirect the exhaust gas flow in the second flow direction B. The exhaust gas emissions will thereafter pass through the second catalytic converter substrate 9, in the second flow direction B, and into the second part of the second volume 22b. Finally, the exhaust gas emissions will exit through the second port 15 in the third flow direction C. The inventive catalytic converter 2 can also be provided without the porous material. Figure 2a and Figure 2b shows two schematic side views of two embodiments of the inventive exhaust gas aftertreatment device 1, each comprising one possible development of reductant injection arrangement. According to Figure 2a and 2b, the second converter substrate is a substrate with SCR functionality 26. The presence of a substrate with SCR functionality26 requires that a reductant, typically anhydrous ammonia, aqueous ammonia urea etc., is added to the exhaust gas emissions flow and is absorbed onto the downstream arranged substrate with SCR functionality. Operations and the functionality of a substrate with SCR functionality are not further described herein since this is common knowledge and does not form part of the invention. According to the development of the invention shown in Figure 2a, a first example of an injector pipe 25a is provided longitudinally in the catalytic converter 2, wherein the injector pipe 25a enters the catalytic converter 2 through the second end portion 6, such that a reductant can be added to the exhaust gas emissions before the substrate with SCR functionality26. The reductant may preferably be added within the volume of the exhaust gas guiding means 12 or the volume of the pipe member 11, such that the beneficial mixing properties provided by the exhaust gas guiding means 12 and the pipe member 11 is facilitated to provide high degree of mixing between the reductant and the exhaust gas emissions. Also, this will improve the evaporation of the reductant since it will be exposed to hot exhaust gas emissions and possibly heated components for a longer period of time. Further, according to Figure 2a, the injector pipe 25a is provided such that it extends substantially centrally of the pipe member 11, into the volume of the exhaust gas guiding means 12. According to the development of the inventive exhaust gas aftertreatment device 1 shown in Figure 2b, a second example of an injector pipe 25b is entering the volume of the exhaust gas guiding means 12 in a direction substantially perpendicular to the extension of the catalytic converter 2. In the development of the invention according to fig. 2b is the injector pipe 25b inserted through the midsection 5 of the encapsulating member 3. This arrangement allows the reductant to be added to the exhaust gas emission flow within the area of the exhaust gas guiding means 12. According to a further development of the inventive exhaust gas aftertreatment device 1, the second example of an injector pipe can also be provided such that the reductant is injected to the exhaust gas emission flow within the volume of the pipe member 11. Figure 2a and Figure 2b shows developments of the inventive exhaust gas aftertreatment device 1 where the first port 10 receives exhaust gas emissions from an ICE (not shown) and exhaust gas emissions are discharged through the second port 15. In view of this, the intended exhaust gas flow is indicated by arrows in before mentioned figures. Also, in the developments of the inventive exhaust gas aftertreatment device shown in Figure 2a and Figure 2b, any injector pipe is preferably arranged to a reductant tank (not shown) and to associated components for controlling and enabling the injection of reductant. This is not further described herein since this is common knowledge and does not form part of the invention. Figure 3a and Figure 3b shows two schematic side views of the exhaust gas aftertreatment device 101 comprising two developments of exhaust gas guiding means 1012 according to the invention. According to the development of the inventive exhaust gas aftertreatment device 101 shown in Figure 3a and Figure 3b, the curved section 1024 is provided between the first open section 1013 and the second open section 1014 of the exhaust gas guiding means 1012. In the developments of the invention shown in Figure 3a and Figure 3b the entire circumferential surface connecting the first open section 1013 to the second open section 1014 is curved. It is also possible that just a smaller section of the circumferential surface is curved. The curved section 1024 connects the first open section 1013 with the second open section 1014 by forming a circumferential surface of the exhaust gas guiding means 1012. Additionally, in the development of the inventive exhaust gas aftertreatment device 101 shown in Figure 3a and Figure 3b, the curved section 1024 is provided with a circumferential section 1027a;1027b, wherein the circumferential section 1027a;1027b is provided substantially in the middle of the curved section 1024. The circumferential section 1027a;1027b is preferably configured to add additional resilience, or in other ways desirable, properties to the exhaust gas guiding means 1012. In Figure 3a, the circumferential section 1027a is in the form of a membrane, which membrane can be configured to add additional ability to withstand thermal expansion, or add other desirable properties to the exhaust gas guiding means 1012, and in Figure 3b, the circumferential section 1027b is in the form of a corrugated section of the curved section 1024, which also can improve the resilience of the curved section 1024. Finally, the operations of a catalytic converter and additional components of catalytic converters not described herein are considered to be part of common knowledge and does not form part of, nor have any impact on, the present invention.

14. An exhaust gas guiding means (1012) for guiding of an exhaust gas emission flow within an exhaust gas aftertreatment device (101) for an Internal Combustion Engine, wherein: the exhaust gas aftertreatment device (101) comprises a catalytic converter (102), wherein the catalytic converter (102) comprises an encapsulating member (103) with a first and a second opposing end portion (104;106), and a midsection portion (105) there between, wherein an outside of the encapsulating member (103) defines the outer perimeter of the catalytic converter (102), and wherein the inside of the encapsulating member (103) defines a converter volume (107) of the catalytic converter (102), wherein: the exhaust gas guiding means (1012) is provided within the converter volume (107) of the catalytic converter (102) and comprises a first open section (1013), a second open section (1014) and a circumferential surface (1027a;1027b) connecting the first open section (1013) with the second open section (1014), such that an enclosed passage is formed between the second open section (1014) and the first open section (1013), wherein the first open section (1013) has smaller cross sectional area than the second open section (1014),: characterized in: that the exhaust gas guiding means (1012) comprises a resilient section in the circumferential surface (1027a;1027b) that changes shape when the exhaust gas guiding means (1012) changes shape due to change in heat load from the exhaust gas emissions, for hindering excess force on the inside of the encapsulating member (103).

15. An exhaust gas guiding means (1012) according to claim 14,: characterized in: that the exhaust gas guiding means (1012) comprises a curved section (1024), which curved section (1024) changes shape when the exhaust gas guiding means (1012) changes shape due to change in heat load from the exhaust gas emissions, for hindering excess force on the inside of the encapsulating member (103).

2874478

Slide rail assembly for rack system

Based on the following detailed description of an invention, generate the patent claims. There should be 12 claims in total. The first, independent claim is given and the remaining 11 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure shows a preferred embodiment of the present invention, which comprises a rack 10, a first slide rail assembly 12, a second slide rail assembly 14 and a chassis 16. The rack 10 comprises a first post 18a, a second post 18b, a third post 18c and a fourth post 18d. The first slide rail assembly 12 is connected between the first and second posts 18a, 18b. The second slide rail assembly 14 is connected between the third and fourth posts 18c, 18d. The chassis 16 is connected between the first and second slide rail assemblies 12, 14. The first slide rail assembly 12 and the second slide rail assembly 14 are disposed symmetrically, and at least one of the first slide rail assembly 12 and the second slide rail assembly 14 has an outer rail 19 and an inner rail 20, wherein the inner rail 20 is longitudinally movable relative to the outer rail 19. Specifically, the outer rail 19 has a top plate 22a, a bottom plate 22b and a side plate 24, wherein the side plate 24 is connected between the top plate 22a and the bottom plate 22b. The top plate 22a, the bottom plate 22b and the side plate 24 of the outer rail 19 form a longitudinal passage 26, and the inner rail 20 is configured to move along the longitudinal passage 26 of the outer rail 19 such that the inner rail 20 is able to be pushed or pulled to move toward or away from the outer rail 19. Preferably, the present invention further comprises a middle rail 28. The middle rail 28 is movably connected between the outer and inner rails 19, 20 such that the inner rail 20 is able to be pulled to move further away from the outer rail 19 in cooperation with the relative movement between the middle rail 28 and the outer rail 19. In additional, the distance that the inner rail 20 is able to move relative to the outer rail 19 can be adjusted according to needs. For example, in one embodiment, the middle rail 28 is fixed to the outer rail 19 by a bar 25, a pin, a cotter, or the like such that the middle rail 28 is unable to move relative to the outer rail 19, and thus only the inner rail 20 is pulled out when a pull force is applied to the end of the inner rail 20. Furthermore, as shown in Figures 2A and 3, the chassis 16 comprises a first chassis 30 and a second chassis 32. At least one retaining member 34 is connected to a side of the first chassis 30, and at least one sliding member 36 is connected to a side of the second chassis 32. Wherein, the first chassis 30 is connected to the inner rail 20 by the at least one retaining member 34, and the second chassis 32 is movably connected to the inner rail 20 by the at last one sliding member 36. The inner rail 20 further comprises a top wall 38a, a bottom wall 38b and a side wall 40, wherein the side wall 40 is connected between the top and bottom walls 38a, 38b. The side wall 40 of the inner rail 20 has at least one fixing portion 42 and at least one sliding portion 44. The at least one fixing portion 42 comprises a first installation hole 46 and a retaining hole 48. The first installation hole 46 communicates with the retaining hole 48, as shown in Figures 2B, and has a diameter D1 larger than a diameter D2 of the retaining hole 48 such that the at least one retaining member 34 is allowed to be inserted in or pulled out from the at least one fixing portion 42 via the first installation hole 46 although the at least one retaining member 34 is not allowed to be inserted in or pulled out from the at least one fixing portion 42 via the retaining hole 48. The at least one sliding portion 44 comprises a second installation hole 50 and a slot 52. The second installation hole 50 communicates with the slot 52, as shown in Figure 2C, and has a diameter D3 larger than a width W1 of the slot 52 such that the at least one sliding member 36 is allowed to be inserted in or pulled out from the at least one sliding portion 44 via the second installation hole 50 although the at least one sliding member 36 is not allowed to be inserted in or pulled out from the at least one sliding portion 44 via the slot 52. It is should be noted that a length L2 of the slot 52 is longer than a length L1 of the retaining hole 48. More specifically, when the at least one retaining member 34 is inserted through the first installation hole 46 and further shifted to the retaining hole 48, the first chassis 30 is installed to the inner rail 20. When the at least one sliding member 36 is inserted through the second installation hole 50 and further shifted to the slot 52, the second chassis 32 is installed to the inner rail 20. In one preferred embodiment, a first positioning member 54 and a second positioning member 55 are connected to the inner rail 20, wherein the first positioning member 54 is located corresponding to the at least one fixing portion 42 of the inner rail 20, and the second positioning member 55 is located corresponding to the at least one sliding portion 44 of the inner rail 20. The first positioning member 54 comprises a resilient section 56 and a contact portion 58, wherein the contact portion 58 is connected to the resilient section 56. Preferably, the contact portion 58 extends from the resilient section 56 and is configured to cover up the first installation hole 46 to prevent the at least one retaining member 34 of the first chassis 30 from being pulled out from the first installation hole 46 when the first chassis 30 is installed to the inner rail 20. More specifically, when installation, the at least one retaining member 34 of the first chassis 30 is inserted through the first installation hole 46 to prop up the first positioning member 54 until the at least one retaining member 34 is further shifted to the retaining hole 48. Thereby, after the at least one retaining member 34 is further shifted to the retaining hole 48, the first positioning member 54 is recovered to cover up the first installation hole 46 by the elastic recovery force of the resilient section 56 such that the at least one retaining member 34 is kept in the retaining hole 48 and is not allowed to be shifted back to the first installation hole 46, and the inner rail 20 is therefore securely installed to the first chassis 30. In contrast, when removing the inner rail 20 from the first chassis 30, a user has to pull the first positioning member 54 outwardly from the inner rail 20 and shift the at least one retaining member 34 of the first chassis 30 back to the first installation hole 46 at the same time such that the at least one retaining member 34 is allowed to be pull out from the first installation hole 46, and the inner rail 20 is therefore removed from the first chassis 30. Similarly, the second positioning member 55 is configured to prevent the at least one sliding member 36 from being pulled out from the second installation hole 50 when the second chassis 32 is installed to the inner rail 20. As the configuration of the second positioning member 55 is similar to that of the first positioning member 54, the related description is omitted herein. Figures 4 and 5 show that the first positioning member 54 covers up the first installation hole 46 upon the at least one retaining member 34 of the first chassis 30 is shifted to the retaining hole 48 such that the at least one retaining member 34 is kept in the retaining hole 48 and is not allowed to be shifted back to the first installation hole 46, and thereby the first chassis 30 is fixed to the inner rail 20. Figures 4 and 5 also show that the second positioning member 55 covers up the second installation hole 50 upon the at least one sliding member 36 of the second chassis 32 is shifted to the slot 52 such that the at least one sliding member 36 is kept in the slot 52 and is not allowed to be shifted back to the second installation hole 50, and thereby the at least one sliding member 36 is limited to move in the slot 52 within a distance S1 (as shown in Figure 5 ). Furthermore, referring to Figure 6, when the second chassis 32 is moved away from the first chassis 30 by a force F applied to the second chassis 32 and reaches a maximum extended position (as shown in Figure 6 ), the at least one sliding member 36 contacts and is stopped by a stop portion 60 of the sliding portion 44. On the contrary, when the second chassis 32 is moved toward the first chassis 30 and reaches a minimum extended position (as shown in Figure 4 ), the at least one sliding member 36 contacts and is stopped by the contact portion 58 of the second positioning member 55. The present invention provides an extra function of the inner rail 20 by the at least one sliding member 36, which is inserted through the at least one sliding portion 44 of the inner rail 20, and provides a sufficient space for removing the cables which are connected between different modules as well. While we have shown and described the embodiment in accordance with the present invention, it should be clear to those skilled in the art that further embodiments may be made without departing from the scope of the present invention.

1. A slide rail assembly (12), comprising: an outer rail (19); and an inner rail (20) longitudinally movable relative to the outer rail (19), the inner rail (20) having a top wall (38a), a bottom wall (38b) and a side wall (40), the side wall (40) connected between the top and bottom walls (38a, 38b), being characterized in that the side wall (40) of the inner rail (20) has at least one fixing portion (42) and at least one sliding portion (44), the at least one fixing portion (42) comprising a first installation hole (46) and a retaining hole (48), the first installation hole (46) communicating with the retaining hole (48) and having a diameter (D1) larger than a diameter (D2) of the retaining hole (48), the at least one sliding portion (44) comprising a second installation hole (50) and a slot (52), the second installation hole (50) communicating with the slot (52) and having a diameter (D3) larger than a width (W1) of the slot (52).

2. The slide rail assembly as claimed in claim 1, further comprising a first positioning member (54) connected to the side wall (40) of the inner rail (20), the first positioning member (54) having a resilient section (56) and a contact portion (58), wherein the resilient section (56) is connected to the contact portion (58), and the contact portion (58) covers up the first installation hole (46) of the at least one fixing portion (42). 3. The slide rail assembly as claimed in claim 1, wherein a length (L2) of the slot (52) is longer than a length (L1) of the retaining hole (48). 4. The slide rail assembly as claimed in claim 1, wherein the outer rail (19) has a top plate (22a), a bottom plate (22b) and a side plate (24), the side plate (24) connected between the top plate (22a) and the bottom plate (22b). 5. The slide rail assembly as claimed in claim 1, further comprising a middle rail (28) movably connected between the outer and inner rails (19, 20) such that the inner rail (20) is allowed to move away from the outer rail (19) in cooperation with the relative movement between the middle rail (28) and the outer rail (19). 6. The slide rail assembly as claimed in claim 1, wherein the slide rail assembly (20) is adapted to be installed to a chassis (16), the chassis (16) comprising a first chassis (30) and a second chassis (32), the first chassis (30) having a retaining member (34), the second chassis (32) having a sliding member (36), and wherein the retaining member (34) of the first chassis (30) is allowed to be inserted in the at least one fixing portion (42) via the first installation hole (46) and be further shifted to the retaining hole (48), and the sliding member (36) of the second chassis (32) is allowed to be inserted in the at least one sliding portion (44) via the second installation hole (50) and be further shifted to the slot (52). 7. The slide rail assembly as claimed in claim 6, further comprising a first positioning member (54) connected to the side wall (40) of the inner rail (20) and located corresponding to the at least one fixing portion (42) of the inner rail (20), wherein the first positioning member (54) is used to prevent the retaining member (34) from being pulled out from the at least one fixing portion (42) via the first installation hole (46). 8. The slide rail assembly as claimed in claim 6, further comprising a first positioning member (54) connected to the side wall (40) of the inner rail (20), wherein the first positioning member (54) has a resilient section (56) and a contact portion (58), the contact portion (58) connected to the resilient section (56) and covering up the first installation hole (46) of the at least one fixing portion (42). 9. The slide rail assembly as claimed in claim 8, further comprising a second positioning member (55) connected to the side wall (40) of the inner rail (20), wherein the second positioning member (55) covers up the second installation hole (50) of the at least one sliding portion (44). 10. A rack system having a slide rail assembly (12) as claimed in claim 1, comprising: a rack (10) having a first post (18a), a second post (18b), a third post (18c) and a fourth post (18d), wherein the slide rail assembly (12) is connected between the first and second posts (18a, 18b); and a second slide rail assembly (14) connected between the third and fourth posts (18c, 18d); being characterized in that the rack system comprises a chassis (16) connected between the slide rail assembly (12) and the second slide rail assembly (14), the chassis (16) comprising a first chassis (30) and a second chassis (32), the first chassis (30) connected to the at least one fixing portion (42) of the inner rail (20) by a retaining member (34), the second chassis (32) movably connected to the at least one sliding portion (44) of the inner rail (20) by a sliding member (36) such that the second chassis (32) is allowed to slide toward or away from the first chassis (30). 11. The rack system as claimed in claim 10, further comprising a first positioning member (54) connected to the inner rail (20), the first positioning member (54) having a resilient section (56) and a contact portion (58), the contact portion (58) connected to the resilient section (56) and covering up the first installation hole (46) of the at least one fixing portion (42). 12. The rack system as claimed in claim 10, wherein the at least one sliding portion (44) has a stop portion (60), and the stop portion (60) contacts and stops the at least one sliding member (36) when the second chassis (32) slides away from the first chassis (30) to reach a maximum extended position.

2873799

Down-the-hole hammer drill bit assembly

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to figure 1, a down-the-hole (DTH) hammer drill assembly 100 comprises a substantially hollow cylindrical casing 101 having an axially rearward end 101a and an axially forward end 101b. A top sub 102 is at least partially accommodated within rearward end 101a of casing 101 whilst a drill bit 105 is at least partially accommodated within the casing forward end 101b. Drill bit 105 comprises an elongate shaft 106 having internal passageway 116. A drill bit head 107 is provided at a forward end of shaft 106 and comprises a plurality of wear resistant cutting buttons 108. An axially rearward face 117 of shaft 106 represents an anvil end of drill bit 105. A distributor cylinder 121 extends axially within casing 101 and in contact with an inward facing substantially cylindrical casing surface 112 that defines an axially extending internal cavity. An elongate substantially cylindrical piston 103 extends axially within cylinder 121 and casing 101 and is capable of shuttling back and forth along central longitudinal axis 109 extending through the assembly 100. Piston 103 comprises an axially rearward end 114 and an axially forward end 115. An internal bore 113 extends axially between ends 114, 115. A foot valve 104 projects axially rearward from the anvil end of drill bit shaft 106 and comprises a generally cylindrical configuration having a rearward end 119 and a forward end 110. An external passageway 118 extends axially between ends 119, 110 in fluid communication with drill bit passageway 116 and piston passageway 113. In particular, an axially forward region of foot valve 104 is embedded and locked axially within the rearward anvil end region of drill bit shaft 106. In particular, just over half of the axial length of foot valve 104 extends rearward from anvil end 117. Casing 101 and distributor cylinder 121 define the internal chamber having an axially rearward region 111a and axially forward region 111b. Piston 103 is capable of reciprocating axially to shuttle within chamber regions 111a, 111b. In particular, a pressurised fluid is delivered to drill assembly 100 via a drill string (not shown) coupled to top sub 102. Distributor cylinder 121 and top sub 102 control the supply of the fluid to the chamber regions 111a, 111b. In particular, and as will be appreciated, with fluid supplied to the axially rearward region 111a, piston 103 is forced axially towards drill bit 105 such that the piston forward end 115 strikes anvil end 117 to provide the percussive drilling action to the cutting buttons 108. Fluid is then supplied to the forward cavity region 111b to force piston 103 axially rearward towards top sub 102. With piston 103 in the axially forwardmost position, foot valve 104 is mated within piston passageway 113 to isolate and close fluid communication between drill bit passageway 116 and cavity region 111b. As piston 103 is displaced axially rearward, piston end 115 clears foot valve end 119 to allow the pressurised fluid to flow within drill bit passageway 116 and to exit drill bit head 107 via flushing channels 120. Accordingly, the distributed supply of fluid to cavity regions 111a, 111b creates the rapid and reciprocating shuttling action of piston 103 that, in turn, due to the repeated mating contact with foot valve 104, provides a pulsing exhaust of pressurised fluid at the drill bit head 107 as part of the percussive drilling action. Referring to figures 2 and 3, foot valve 104 may be considered to comprise an axially rearward length section 306 and an axially forward length section 305, with section 305 comprising a larger outside diameter than section 306. A radially projecting annular collar 303 is positioned axially at the junction between sections 306, 305. Passageway 118 is defined by a substantially cylindrical inward facing surface 301 extending between rearward end 119 and forward end 110. Rearward length section 306 projects axially rearward from drill bit shaft anvil end 117 such that a radially outward facing valve surface 300 is exposed and is capable of sliding contact against and within the forwardmost end of piston passageway 113. A corresponding radially outward facing valve surface 309 is configured for positioning opposed to a radially inward facing surface 307 of drill bit shaft 106 that defines shaft passageway 116. In particular, an axially rearward region 302 of passageway 116 is radially enlarged to accommodate the larger outside diameter length section 305. When valve 104 is locked in position at the anvil end of shaft 106, the axially forwardmost valve end 110 is very closely axially co-located at an axially forwardmost end 308 of passageway region 302. The inside diameter of valve passageway 118 is substantially uniformed between ends 119, 110 such that the larger outside diameter of section 305 relative to section 306 is provided by a greater valve wall thickness at this section 305. Such a configuration is advantageous to provide both a friction-fit arrangement between valve 104 and drill bit shaft 106 and to withstand the stresses and stress concentrations at valve 104 during initial coupling, operational use and decoupling of valve 104 from shaft 106. The friction-fitting and axial locking of valve 104 at drill shaft 106 is also provided, in part, by a plurality of radially spaced lugs 304 that are distributed circumferentially (relative to axis 109) at and around forward length section 305. Referring to figure 4, each lug 304 is formed as a discrete raised hump at the radially outward facing surface 309 axially between collar 303 and forwardmost end 110. Each lug 304 comprises a generally rectangular shape profile and is defined by an axially rearward face 402, an axially forward face 401 and a pair of lengthwise side faces 403 that collectively terminate at their radially outermost ends in a common plateau face 400 that also comprises a generally rectangular shape profile. The forward, rearward and side faces, 401, 402, 403 are tapered such that each lug 304 is formed as a smooth raised lump. Referring to figure 4, a circumferential length A of each lug 304 is less than a corresponding axial length B. In particular, valve 104 comprises three lugs 304 equally spaced apart in the circumferential direction around surface 309 such that the circumferential separation distance between lugs 304 is greater than the lug circumferential length A and axial length B. Referring to figure 5, a plurality of radially extending shoulders 502 are distributed circumferentially around the inward facing surface 307 of the axially rearward passageway region 302. Each shoulder 502 projects radially inward from surface 307 and is equally spaced in a circumferential direction from neighbouring shoulders 502 by intermediate channels 501. Each channel 501 extends axially and comprises an axially rearward end 504, positioned approximately coaxially with anvil end 117, and an axially forward end 505 approximately co-located at region end 308. The circumferential ends 503 of each shoulder 502 are tapered radially such that each channel 501 comprises a smooth curved shape profile between shoulders 502. According to the specific embodiment, drill shaft 106 comprises three circumferentially spaced shoulders 502 and channels 501. Each shoulder 502 is defined axially by an axially rearward surface 507 and an axially forward surface 506. Each surface 506, 507 extends circumferentially between channels 501 and is tapered radially such that a radial thickness of each shoulder 502 increases gradually in the axial direction from above and below. A circumferential length C of each channel 501 between the circumferential shoulder ends 503 is slightly greater than lug circumferential length A so as to allow each lug 304 to pass axially between adjacent shoulders 502 and to slide axially within a respective channel 501 during an initial coupling and subsequent decoupling of foot valve 104 at drill shaft 106. Additionally, an axially forward portion 509 of region 302 is radially tapered to be generally conical and configured to mate with a tapered generally conical end region 310 of valve 104. Figure 6 illustrates a cross section through A-A of figure 3. As shown, each lug 304 represents a radially outermost portion of valve length section 305 between collar 303 and forwardmost end 110. Accordingly, each lug 304 is positioned in close touching contact with the radially inward facing surface 309 of passageway 116. Section A-A corresponds to the axial region 508 axially beyond (or below) each shoulder 502 with valve 104 in a locked position at drill bit 105. In this position, each lug 304 is positioned to radially overlap a corresponding shoulder 502 that represents innermost region of passageway 116 at rearward region 302. Axial coupling and decoupling of valve 104 at drill shaft 106 is illustrated and described referring to figures 7 and 8. With each lug 304 circumferentially aligned with a respective channel 501, valve 104 may be displaced axially at drill shaft 106. The axial locking of valve 104 at shaft 106 is illustrated and described with reference to figures 9 and 10. In particular, valve 104 is rotated about axis 109 to displace lugs 304 circumferentially relative to shoulders 502 and channels 501. In particular, each lug rearward face 402 is capable of being rotated into contact with shoulder face 506 to provide a friction-fitting of valve 104 within passageway 116. Due to the radial projection of each lug 304 and each shoulder 502, the lugs 304 and shoulders 502 overlap radially as illustrated in figure 10 to prevent valve 104 being withdrawn axially from drill shaft 106. In particular, axial movement is prevented by the abutment contacts between the three pairs of respective surfaces 402, 506. The present configuration is advantageous to allow initial coupling of valve 104 at drill shaft 106 by simply pressing the valve 104 into passageway 116 by hand. Valve 104 may then be locked or unlocked axially via a convenient rotation about axis 109 to engage lugs 304 into contact with the axial end surfaces 506 of shoulders 502. The present assembly may be conveniently coupled and decoupled without the need for specific swaging apparatus (mechanical, hydraulic or pneumatic presses) and may be manipulated on-site by operational personnel by hand and/or using common standard tools.

1. A down-the-hole hammer drill bit assembly (100) comprising: a drill bit (105) having a forward cutting end (107) and rearward anvil end (117), an internal passageway (116) extending along a longitudinal axis (109) of the assembly (100) from the anvil end (117) towards the cutting end (107); a foot valve (104) seated partially within the passageway (116) to extend axially from the anvil end (117); complementary abutment regions (304, 502) provided respectively at a radially inward facing surface (307) of the passageway (116) and a radially outward facing surface (309) of the foot valve (104), the respective abutment regions (304, 502) configured to abut one another and axially lock the foot valve (104) to the drill bit (105); characterised in that: the abutment regions (304, 502) comprise: a plurality of radially projecting lugs (304) spaced apart in a circumferential direction around the axis (109); and a plurality of radially extending shoulders (502) spaced apart in a circumferential direction around the axis (109); wherein a circumferential separation distance (C) between the shoulders (502) is at least equal to or greater than a circumferential length (A) of the lugs (304) to allow the lugs (304) to pass axially between the shoulders (502) without substantially deforming the foot valve (104) radially; and wherein a radial length of the lugs (304) and shoulders (502) is configured such that the lugs (304) and the shoulders (502) overlap radially within the passageway (116) with the lugs (304) positioned axially beyond and abutting the shoulders (502) to axially lock the foot valve (104) at the drill bit (105).

2. The assembly as claimed in claim 1 comprising three lugs (304) and three shoulders (502). 3. The assembly as claimed in claims 1 or 2 wherein each lug (304) is formed as a discrete raised bump. 4. The assembly as claimed in any preceding claim wherein an axially rearward end of each lug (304) is tapered radially to provide an inclined contact surface (402) and an axially forward end of each shoulder (502) is tapered radially to provide a declined contact surface (506) such that the inclined and declined surfaces (402, 506) are complementary to mate together via overlapping contact. 5. The assembly as claimed in claim 4 wherein each lug (304) and each shoulder (502) is defined, in part, by a pair of respective lengthwise side surfaces (403, 503) tapered radially such that each lug (304) and each shoulder (502) is formed by a smooth transition with the respective surface (309, 307) of the foot valve (104) and the passageway (116). 6. The assembly as claimed in claim 5 wherein the lugs (304) and shoulders (502) are positioned axially closest to the anvil end (117) relative to the cutting end (107). 7. The assembly as claimed in any preceding claim further comprising at least one friction fit region (402, 506) at the passageway (116) and/or the foot valve (104) to rotatably lock the foot valve (104) at the drill bit (105) to inhibit independent rotation of the foot valve (104) at the drill bit (105). 8. The assembly as claimed in claim 7 wherein a region (506, 508) of the surface (307, 402) of the passageway (116) and/or the foot valve (104) is radially tapered in the circumferential direction to friction fit the foot valve (104) at the drill bit (105) on rotation of the foot valve (104) at the drill bit (105). 9. The assembly as claimed in any preceding claim wherein the foot valve (104) comprises a plastic material and the drill bit (105) comprises a metal or metal alloy material. 10. The assembly as claimed in any preceding claim wherein the lugs (304) project radially outward from the surface (309) of the foot valve (104) and the shoulders (502) extend radially inward from the surface (307) of the passageway (116). 11. The assembly as claimed in claim 10 wherein within a lengthwise region (305) of the foot valve (104) configured to be positioned within the passageway (116), the lugs (304) represent a radially outermost part of the foot valve (104); and: within a lengthwise region (302) of the drill bit (105) configured for mating opposed to the foot valve (104), the shoulders (502) represent a radially innermost part of the passageway (116). 12. The assembly as claimed in claim 11 wherein the shoulders (502) are positioned radially inward relative to a radial position of an opening (500) of the passageway (116) located at the anvil end (117). 13. The assembly as claimed in claim 12 wherein the foot valve (104) comprises a first length section (306) and a second length section (305), the second length section (305) having a larger outside diameter relative to the first length section (306), the lugs (304) positioned within the second length section (305). 14. The assembly as claimed in claim 13 further comprising an annular collar (303) extending radially outward beyond the second length section (305) and positioned axially at the junction between the first (306) and second (305) length sections. 15. A down-the-hole hammer for percussive rock drilling comprising an assembly according to any preceding claim.

2874292

Thermoacoustic magnetohydrodynamic electric generator

Based on the following detailed description of an invention, generate the patent claims. There should be 9 claims in total. The first, independent claim is given and the remaining 8 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described with reference to the accompanying drawings. The drawings are intended to provide one example of how the invention can be implemented and are not intended to limit the applicability of the present invention. Figures 1 and 2 represent an electric generator 1 comprising a first thermoacoustic engine 2, a magneto hydrodynamic (MHD) generator 3 and a resonator 4. The first thermoacoustic engine 2 enables to convert thermal energy in kinetic energy. To that purpose, the first thermoacoustic engine 2 comprises a first thermoacoustic housing 5 filed with a fluid. The fluid is a gas. The gas will be preferably helium which has a relatively good thermal conductivity which is important in the process of conversion of heat in mechanical power. It is possible to adjust the physical properties of the fluid by mixing helium with another gas. Air is an example and has been tested allowing modifying the frequency of the thermo acoustic waves and the performance of the thermo acoustic engine. The first thermo acoustic housing 5 forms preferably a loop. The first thermo acoustic engine 2 comprises a thermo acoustic structure 7 placed in the first thermo acoustic housing 5. The thermo acoustic structure 7 comprises preferably a stack. The thermo acoustic structure 7 comprises a first extremity 9 and a second extremity 10. The first extremity 9 is thermally coupled with a warm source 11 in order to inject heat in the fluid, while the second extremity 10 is coupled with a cold source 12 in order to withdraw heat from the fluid. The difference of temperature between the two extremities of the thermo acoustic structure induces oscillations in the fluid within the first thermo acoustic housing. The thermo acoustic structure into which heat is introduced and withdrawn from the fluid enables then to induce and maintain resonant acoustic oscillation in the fluid. The thermo acoustic engine 2 enables then to convert a difference of temperature between the warm source 11 and the cold source 12 in an oscillating movement of the fluid. The MHD generator 3 enables to convert the oscillating movement of the fluid into electricity. To that purpose, the MHD generator 3 comprises a MHD housing 13. The MHD housing preferably extends along a reference axis 15. The MHD housing 13 comprises a first extremity 22 and a second extremity 23. The first extremity 22 is connected to the first thermo acoustic housing 5. The second extremity 23 is connected to the resonator 4. The MHD housing 13 is filed with the same fluid as the first thermo acoustic housing 5. The MHD housing 13 is in fluidic communication with the first thermo acoustic housing 5 so that the fluid of the MHD housing is subjected to an oscillatory movement when the fluid of the first thermoacoustic housing 5 is subjected to an oscillatory movement. The oscillatory movement of the fluid in the MHD housing occurs along the reference axis 15 of the MHD housing 15. The MHD generator 3 also comprises ionization means 17 enabling to ionize the gas. The ionization means 17 comprise a high tension generator 18 able to generate an electric arc enabling to ionize the gas. To that purpose, the high tension generator 18 maintains a high voltage between ionization electrodes 19. The ionization electrodes 19 are preferably placed within the MHD housing 13. The level of voltage necessary to maintain the gas in ionized form depends on the level of power that must be produced by the MHD generator and of the gas properties. It depends also of the global geometry of the stack of electrodes and specifically on the gap between them. Typically a value of several times ten thousand volts can be required to produce a good ionization able to give a sufficiently high electrical conductivity to the fluid The MHD generator 3 also comprises MHD means 16 enabling to convert the oscillating movement of the fluid into electricity. These MHD means 16 comprises a first coil 20 and a second coil 21. These coils are preferably toroidal. Each coil surrounds one extremity 22, 23 of the MHD housing. The MHD means 16 also comprise polarized electrodes 24, 25 enabling to separate the positive loads from the negative loads of the ionized gas. To that purpose, the polarized electrodes 24, 25 are connected to a high voltage power supply 26. The polarized electrode 24 maintains the positive loads of the ionized gas in the part of the MHD housing which is surrounded by the first coil 20. The polarized electrode 25 maintains the negative loads of the ionized gas in the part of the MHD housing which is surrounded by the second coil 21. The thermoacoustic structure 7 creates oscillating movements in the gas of the thermoacoustic housing 5. Consequently, the positive loads oscillate in the part of the MHD housing which is inside the first coil so that a current is generated in the first coil. For the same reasons, the negative loads oscillated in the part of the MHD housing which is inside the second coil so that a current is generated in the second coil. The first coil 20 and the second coil 21 are preferably connected to a load 27 receiving the current generated in the first and the second coil. Each coil surrounds a torroidal ferromagnetic core 28 to obtain a sufficiently high magnetic field. The electric generator enables to produce easily current, with a low inertia and even in the absence of gravity.

1. Electric generator (1) comprising: - At least a first thermo acoustic engine (2) comprising: - a first thermo acoustic housing (5) filed with a fluid, - a thermo acoustic structure (7) positioned in said fluid and able to have a first part (9) thermally connected to a warm source (11) and a second part (10) thermally connected to a cold source (12) for inducing an oscillating movement of the fluid within the first thermoacoustic housing (5); - a magneto hydrodynamic generator (3) comprising: - an MHD housing (13) filed with the same fluid as the first thermo acoustic housing (5), the MHD housing (13) being in fluidic communication with the first thermo acoustic housing (5) so that the fluid of the MHD housing (13) is subjected to an oscillating movement when the fluid of the first thermo acoustic housing (5) is subjected to an oscillating movement; - MHD means (16) to convert the oscillating movement of the fluid into electricity; characterized in that the fluid is a gas, the magneto hydrodynamic generator (3) further comprising ionization means (17) to maintain the gas in ionized form in the MHD housing (13) so that it becomes electrically conductive.

2. Electric generator (1) according to claim 1, wherein the ionization means (17) comprise a high tension generator (18) able to generate high voltage enabling to ionize the gas. 3. Electric generator according to any of the previous claims, wherein the gas 29 comprises either pure helium or a mixing of helium with another gas. 4. Electric generator according to any of the previous claims, wherein the MHD means (16) comprise a first coil (20) and a second coil (21), the first coil (20) and the second coil (21) surrounding the MHD housing (13). 5. Electric generator (1) according to any of the previous claims, wherein the ionized gas comprises positive loads and negative loads, the MHD means (16) comprising several polarized stack electrodes (24, 25) able to separate the positive loads from the negative loads. 6. Electric generator (1) according to claims 5 and 6, wherein the polarized electrodes (24, 25) are able to locate the positive loads in a part (22) of the MHD housing (13) surrounded by the first coil (20) and the negative loads in a part (23) of the MHD housing (13) surrounded by the second coil (21). 7. Electric generator (1) according to any of the previous claims, further comprising a resonator (4) connected to the MHD housing. 8. Electric generator (1) according to the previous claim, wherein the resonator (4) can be replaced by a second thermo acoustic engine comprising a second thermo acoustic housing in fluidic communication with the MHD housing. 9. Electric generator according to any of the previous claims, wherein each thermo acoustic housing (5) forms a loop.

2873877

Self-drilling expansion fastener and method of forming same

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described with a preferred embodiment thereof and with reference to the accompanying drawings. Please refer to Figures 3 to 6. A self-drilling expansion fastener 20 according to a preferred embodiment of the present invention is integrally formed of a sheet metal material, and includes an expansion structure 21 and a drill structure 30 located at a head of the expansion structure 21. The expansion structure 21 has a front portion formed into an internally threaded body portion 22 and a rear portion formed into a barrel body portion 23. The internally threaded body portion 22 is a cylindrical hollow body and defines a plurality of internal threads 24. The barrel body portion 23 is a hexagonal hollow body and internally defines a hex bore. The barrel body portion 23 includes a plurality of laterally spaced force-distributing bars 25. Once the barrel body portion 23 is subjected to an axial pull, stress occurs at the force-distributing bars 25. In other words, the force-distributing bars 25 together form a weakening zone. In the preferred embodiment as shown in Figure 5, there are six axially extended force-distributing bars 25 being laterally equally spaced on the barrel body portion 23, such that a spacing slot 26 is formed between any two adjacent force-distributing bars 25. Further, the barrel body portion 23 includes at least one retaining wing 27. In the illustrated preferred embodiment, as shown in Figure 5, there are two retaining wings 27 formed on the barrel body portion 23 by stamping, so that these retaining wings 27 are outward protruded from a wall surface of the barrel body portion 23 and are slant at a fixed angle relative to a horizontal rear end of the barrel body portion 23. And, the barrel body portion 23 includes at least one stopper 28 formed on the rear end thereof. Again, as can be seen in Figure 5, the illustrated preferred embodiment of the present invention has two diametrically opposite stoppers 28, which are respectively upward bent from the rear end of the barrel body portion 23 to a sidewardly projected position. The drill structure 30 includes a chip guard 31 and a drill 32. As can be seen in Figure 3, the chip guard 31 includes two side covers 33, which are extended from the internally threaded body portion 22 and bent toward each other to together cover a front end of the internally threaded body portion 22. It is noted two slits 35 are formed at two lateral sides of the joint of each side cover 33 and the internally threaded body portion 22. The drill 32 consists of two drill bits 34, which are forward projected from top surfaces of the two side covers 33. The expansion structure 21 further includes at least one coupling device 40, which consists of a lug portion 41 and a notch portion 42 correspondingly located opposite to the lug portion 41, such that the lug portion 41 and the notch portion 42 can be engaged with and locked to each other. Figures 7A to 7C illustrate the steps of installing the self-drilling expansion fastener 20 on sheet workpieces. First, as shown in Figure 7A, apply a rotating force on the barrel body portion 23 of the self-drilling expansion fastener 20, so that the drill 32 is brought to drill through multiple layers of sheet workpieces, such as an attached object 50 and a supporting object 51, for the stoppers 28 to tightly press against the attached object 50. In addition to the two layers of sheet worpieces shown in the embodiment, more than two layers may be fastened by the fastener of the invention. At this point, as shown in Figure 7B, the force-distributing bars 25 are located behind the supporting object 51 and the retaining wings 27 are embedded in a peripheral wall of the drilled hole on the attached object 50, bringing the self-drilling expansion fastener 20 to firmly associate with the attached object 50 and the supporting object 51. In practical installation of the self-drilling expansion fastener 20, a matching hexagonal tool 54 can be inserted into the barrel body portion 23 to facilitate the rotation of the self-drilling expansion fastener 20, allowing the drill 32 to drill a hole on the attached object 50 and the supporting object 51. The chip guard 31 functions to prevent any chips of the workpieces 50, 51 from getting into the expansion structure 21. Thereafter, as shown in Figure 7C, screw an externally threaded element 52 into the barrel body portion 23 to fully mesh with the internal threads 24 in the internally threaded body portion 22. When the externally threaded element 52 is gradually screwed deeper into the internally threaded body portion 22, the latter is gradually pulled backward to thereby compress the force-distributing bars 25, bringing the latter to expand outward and finally be compressed into a fully folded state. The fully folded force-distributing bars 25 are now tightly pressed against an inner side of the supporting object 51, allowing the self-drilling expansion fastener 20 to firmly lock the attached object 50 to the supporting object 51. At this point, the externally threaded element 52 has a front end extended beyond the drill 32 by a predetermined length to push open the side covers 33 of the chip guard 31, so that the drill bits 34 of the drill 32 are separated from one another. In brief, the self-drilling expansion fastener 20 according to the present invention is integrally formed and has the ability of self-drilling a hole, and can therefore be manufactured with fewer components to reduce the production and installation costs thereof. The self-drilling expansion fastener 20 according to the present invention is formed of a sheet metal material through a series of punching and stamping procedures. Figures 8A to 8I sequentially illustrate the steps included in a method of the present invention for forming the self-drilling expansion fastener 20. First, as shown in Figure 8A, unnecessary portions are removed from a sheet metal raw material to obtain the sheet metal material having dimensions for forming the self-drilling expansion fastener 20; a reference line "a" is defined to determine an expansion structure zone 60 and a drill structure zone 70 on the obtained sheet metal material; and the expansion structure zone 60 is punched at a specified location to obtain at least one coupling device 61 and at a rear portion to obtain required stoppers 62. Then, as shown in Figure 8B, the expansion structure zone 60 is stamped at a specified location, which is defined as a thread forming zone 64, to obtain required threads 63. Then, as shown in Figure 8C, the expansion structure zone 60 is punched at a predetermined location, which is defined as a barrel body forming zone 66, to obtain a plurality of required force-distributing bars 65; and the drill structure zone 70 is punched at predetermined locations to obtain required side covers 71 and drill bits 72. Thereafter, as can be seen in Figure 8D, the barrel body forming zone 66 is stamped at predetermined locations to obtain required retaining wings 67, and the thread forming zone 64 is punched at predetermined locations to obtain slits 73 at joints of the side covers 71 and the thread forming zone 64. Then, as shown in Figure 8E, the stoppers 62, the side covers 71 and drill bits 72 are bent, so that the side covers 71 together form a required chip guard 74 and the drill bits 72 together form a required drill 75. As shown in Figures 8F to 8H, when the steps shown in Figures 8A to 8E are completed, the thread forming zone 64 and the barrel body forming zone 66 are subjected to a series of stamping to respectively obtain a required configuration. For example, the thread forming zone 64 is formed into a near-cylindrical hollow body and the barrel body forming zone 66 is formed into a hexagonal hollow body internally defining a hexagonal bore. Finally, as shown in Figure 8I, when the thread forming zone 64 and the barrel body forming zone 66 have been suitably shaped, the coupling devices 61 are closed to complete the self-drilling expansion fastener 20 of the present invention. By forming through a series of punching and stamping, the self-drilling expansion fastener 20 can be easily and quickly completed with largely simplified procedures, shortened working time and lowered manufacturing cost.

1. A self-drilling expansion fastener (20) being integrally formed of a sheet metal material for use with an externally threaded element to tightly lock multiple layers of sheet workpieces to one another, comprising: an expansion structure (21) having a plurality of internal threads (24) and a plurality of force-distributing bars (25); and a drill structure (30) being integrally formed at a head of the expansion structure (21); the drill structure (30) including a chip guard (31) connected to the expansion structure (21) for covering the head of the expansion structure (21), and a drill (32) forward projected from the chip guard (31) for self-drilling a hole on the multiple layers of sheet workpieces, so that the expansion structure (21) can be extended through the sheet workpieces and tightly received in the drilled hole with the force-distributing bars (25) fully located behind the sheet workpieces; whereby when the externally threaded element is screwed deeper into the expansion structure (21) to mesh with the internal threads (24), the force-distributing bars (25) are gradually pulled backward to expand outward and are finally compressed into a fully folded state to tightly press against an inner side of the multiple layers of sheet workpieces, so that the sheet workpieces are firmly locked together.

2. The self-drilling expansion fastener (20) as claimed in claim 1, wherein the chip guard (31) includes two side covers (33), which together cover the head of the expansion structure (21); and wherein the drill (32) consists of two drill bits (34), which are forward projected from top surfaces of the two side covers (33). 3. The self-drilling expansion fastener (20) as claimed in claim 1, wherein the expansion structure (21) is integrally formed to have an internally threaded body portion (22) and a barrel body portion (23); the internal threads (24) being formed in the internally threaded body portion (22); and the force-distributing bars (25) being formed on the barrel body portion (23). 4. The self-drilling expansion fastener (20) as claimed in claim 3, wherein the barrel body portion (23) includes at least one retaining wing (27) for embedding in a peripheral wall of the drilled hole on an outermost sheet workpiece of the multiple layers of sheet workpieces, so that the self-drilling expansion fastener (20) is firmly associated with the outermost sheet workpiece. 5. The self-drilling expansion fastener (20) as claimed in claim 3, wherein the internally threaded body portion (22) is a cylindrical hollow body and the barrel body portion (23) is a hexagonal hollow body internally defining a hex bore. 6. The self-drilling expansion fastener (20) as claimed in claim 4, wherein the retaining wing (27) is formed by outward stamping a wall of the barrel body portion (23), such that the retaining wing (27) extends at an angle relative to a horizontal rear end of the barrel body portion (23). 7. The self-drilling expansion fastener (20) as claimed in claim 1, wherein the expansion structure (21) includes at least one stopper (28) formed on a rear end thereof. 8. The self-drilling expansion fastener (20) as claimed in claim 1, wherein the expansion structure (21) further includes at least one coupling device (40); and the coupling device (40) consisting of a lug portion (41) and a notch portion (42) correspondingly located opposite to the lug portion (41), such that the lug portion (41) and the notch portion (42) can be engaged with and locked to each other.

2873877

Self-drilling expansion fastener and method of forming same

Based on the following detailed description of an invention, generate the patent claims. There should be 6 claims in total. The first, independent claim is given and the remaining 5 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described with a preferred embodiment thereof and with reference to the accompanying drawings. Please refer to Figures 3 to 6. A self-drilling expansion fastener 20 according to a preferred embodiment of the present invention is integrally formed of a sheet metal material, and includes an expansion structure 21 and a drill structure 30 located at a head of the expansion structure 21. The expansion structure 21 has a front portion formed into an internally threaded body portion 22 and a rear portion formed into a barrel body portion 23. The internally threaded body portion 22 is a cylindrical hollow body and defines a plurality of internal threads 24. The barrel body portion 23 is a hexagonal hollow body and internally defines a hex bore. The barrel body portion 23 includes a plurality of laterally spaced force-distributing bars 25. Once the barrel body portion 23 is subjected to an axial pull, stress occurs at the force-distributing bars 25. In other words, the force-distributing bars 25 together form a weakening zone. In the preferred embodiment as shown in Figure 5, there are six axially extended force-distributing bars 25 being laterally equally spaced on the barrel body portion 23, such that a spacing slot 26 is formed between any two adjacent force-distributing bars 25. Further, the barrel body portion 23 includes at least one retaining wing 27. In the illustrated preferred embodiment, as shown in Figure 5, there are two retaining wings 27 formed on the barrel body portion 23 by stamping, so that these retaining wings 27 are outward protruded from a wall surface of the barrel body portion 23 and are slant at a fixed angle relative to a horizontal rear end of the barrel body portion 23. And, the barrel body portion 23 includes at least one stopper 28 formed on the rear end thereof. Again, as can be seen in Figure 5, the illustrated preferred embodiment of the present invention has two diametrically opposite stoppers 28, which are respectively upward bent from the rear end of the barrel body portion 23 to a sidewardly projected position. The drill structure 30 includes a chip guard 31 and a drill 32. As can be seen in Figure 3, the chip guard 31 includes two side covers 33, which are extended from the internally threaded body portion 22 and bent toward each other to together cover a front end of the internally threaded body portion 22. It is noted two slits 35 are formed at two lateral sides of the joint of each side cover 33 and the internally threaded body portion 22. The drill 32 consists of two drill bits 34, which are forward projected from top surfaces of the two side covers 33. The expansion structure 21 further includes at least one coupling device 40, which consists of a lug portion 41 and a notch portion 42 correspondingly located opposite to the lug portion 41, such that the lug portion 41 and the notch portion 42 can be engaged with and locked to each other. Figures 7A to 7C illustrate the steps of installing the self-drilling expansion fastener 20 on sheet workpieces. First, as shown in Figure 7A, apply a rotating force on the barrel body portion 23 of the self-drilling expansion fastener 20, so that the drill 32 is brought to drill through multiple layers of sheet workpieces, such as an attached object 50 and a supporting object 51, for the stoppers 28 to tightly press against the attached object 50. In addition to the two layers of sheet worpieces shown in the embodiment, more than two layers may be fastened by the fastener of the invention. At this point, as shown in Figure 7B, the force-distributing bars 25 are located behind the supporting object 51 and the retaining wings 27 are embedded in a peripheral wall of the drilled hole on the attached object 50, bringing the self-drilling expansion fastener 20 to firmly associate with the attached object 50 and the supporting object 51. In practical installation of the self-drilling expansion fastener 20, a matching hexagonal tool 54 can be inserted into the barrel body portion 23 to facilitate the rotation of the self-drilling expansion fastener 20, allowing the drill 32 to drill a hole on the attached object 50 and the supporting object 51. The chip guard 31 functions to prevent any chips of the workpieces 50, 51 from getting into the expansion structure 21. Thereafter, as shown in Figure 7C, screw an externally threaded element 52 into the barrel body portion 23 to fully mesh with the internal threads 24 in the internally threaded body portion 22. When the externally threaded element 52 is gradually screwed deeper into the internally threaded body portion 22, the latter is gradually pulled backward to thereby compress the force-distributing bars 25, bringing the latter to expand outward and finally be compressed into a fully folded state. The fully folded force-distributing bars 25 are now tightly pressed against an inner side of the supporting object 51, allowing the self-drilling expansion fastener 20 to firmly lock the attached object 50 to the supporting object 51. At this point, the externally threaded element 52 has a front end extended beyond the drill 32 by a predetermined length to push open the side covers 33 of the chip guard 31, so that the drill bits 34 of the drill 32 are separated from one another. In brief, the self-drilling expansion fastener 20 according to the present invention is integrally formed and has the ability of self-drilling a hole, and can therefore be manufactured with fewer components to reduce the production and installation costs thereof. The self-drilling expansion fastener 20 according to the present invention is formed of a sheet metal material through a series of punching and stamping procedures. Figures 8A to 8I sequentially illustrate the steps included in a method of the present invention for forming the self-drilling expansion fastener 20. First, as shown in Figure 8A, unnecessary portions are removed from a sheet metal raw material to obtain the sheet metal material having dimensions for forming the self-drilling expansion fastener 20; a reference line "a" is defined to determine an expansion structure zone 60 and a drill structure zone 70 on the obtained sheet metal material; and the expansion structure zone 60 is punched at a specified location to obtain at least one coupling device 61 and at a rear portion to obtain required stoppers 62. Then, as shown in Figure 8B, the expansion structure zone 60 is stamped at a specified location, which is defined as a thread forming zone 64, to obtain required threads 63. Then, as shown in Figure 8C, the expansion structure zone 60 is punched at a predetermined location, which is defined as a barrel body forming zone 66, to obtain a plurality of required force-distributing bars 65; and the drill structure zone 70 is punched at predetermined locations to obtain required side covers 71 and drill bits 72. Thereafter, as can be seen in Figure 8D, the barrel body forming zone 66 is stamped at predetermined locations to obtain required retaining wings 67, and the thread forming zone 64 is punched at predetermined locations to obtain slits 73 at joints of the side covers 71 and the thread forming zone 64. Then, as shown in Figure 8E, the stoppers 62, the side covers 71 and drill bits 72 are bent, so that the side covers 71 together form a required chip guard 74 and the drill bits 72 together form a required drill 75. As shown in Figures 8F to 8H, when the steps shown in Figures 8A to 8E are completed, the thread forming zone 64 and the barrel body forming zone 66 are subjected to a series of stamping to respectively obtain a required configuration. For example, the thread forming zone 64 is formed into a near-cylindrical hollow body and the barrel body forming zone 66 is formed into a hexagonal hollow body internally defining a hexagonal bore. Finally, as shown in Figure 8I, when the thread forming zone 64 and the barrel body forming zone 66 have been suitably shaped, the coupling devices 61 are closed to complete the self-drilling expansion fastener 20 of the present invention. By forming through a series of punching and stamping, the self-drilling expansion fastener 20 can be easily and quickly completed with largely simplified procedures, shortened working time and lowered manufacturing cost.

9. A method of integrally forming a self-drilling expansion fastener (20) from a sheet metal material through a series of punching and stamping, comprising the following steps: obtaining a sheet metal material having dimensions required for forming the self-drilling expansion fastener (20), and defining an expansion structure zone (60) and a drill structure zone (70) on the obtained sheet metal material; stamping the expansion structure zone (60) at a specified location, which is defined as a thread forming zone (64), to obtain threads having required dimensions; punching the expansion structure zone (60) at a specified location, which is defined as a barrel body forming zone (66), to obtain a plurality of force-distributing bars (65); punching the drill structure zone (70) at a predetermined location to obtain a required chip guard (74); punching the drill structure zone (70) at a predetermined location to obtain a required drill (75); and stamping the thread forming zone (64) and the barrel body forming zone (66) to obtain required configurations for these two zones.

10. The self-drilling expansion fastener forming method as claimed in claim 9, wherein the chip guard (74) includes two side covers (71) and the drill (75) includes two drill bits (72). 11. The self-drilling expansion fastener forming method as claimed in claim 9, wherein the barrel body forming zone (66) is stamped at a predetermined location to obtain at least one outward protruded retaining wing (67), and the retaining wing (67) being slant at a fixed angle relative to a horizontal rear end of the barrel body forming zone (66). 12. The self-drilling expansion fastener forming method as claimed in claim 9, wherein the thread forming zone (64) is stamped into a near-cylindrical hollow body, and the barrel body forming zone (66) is stamped into a hexagonal hollow body internally defining a hex bore. 13. The self-drilling expansion fastener forming method as claimed in claim 9, wherein the barrel body forming zone (66) is punched at a predetermined location to obtain at least one stopper (62). 14. The self-drilling expansion fastener forming method as claimed in claim 9, wherein the expansion structure zone (60) is punched at a specified location to obtain at least one coupling device (61) for coupling two longitudinal sides of the expansion structure zone (60) to each other to complete the forming of the self-drilling expansion fastener (20).

2873461

A gyratory crusher spider bushing assembly

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to figure 1, a crusher comprises a frame 100 having an upper frame 101 and a lower frame 102. A crushing head 103 is mounted upon an elongate shaft 107 having longitudinal axis 115. A first (inner) crushing shell 105 is fixably mounted on crushing head 103 and a second (outer) crushing shell 106 is fixably mounted at upper frame 101. A crushing zone 104 is formed between the opposed crushing shells 105, 106. A discharge zone 109 is positioned immediately below crushing zone 104 and is defined, in part, by lower frame 102. A drive (not shown) is coupled to main shaft 107 via a drive shaft 108 and suitable gearing 116 so as to rotate shaft 107 eccentrically about a longitudinal axis 122 of the crusher and to cause head 103 and mantle 105 to perform a gyratory pendulum movement and crush material introduced into crushing zone 104. Accordingly the longitudinal axis 115 of main shaft 107 oscillates about crusher longitudinal axis 122. An upper end region 113 of shaft 107 is maintained in an axially rotatable position by a top-end bearing assembly and a spider bushing 112 positioned intermediate between main shaft region 113 and a central boss 117 positioned about axis 122. Similarly, a bottom end region 118 of shaft 107 is supported by a bottom-end bearing assembly 119. Upper frame 101 comprises a topshell 111, mounted upon lower frame 102 (alternatively termed a bottom shell), and a spider assembly 110 that extends from topshell 111 and represents an upper portion of the crusher. The spider 110 comprises two diametrically opposed arms that extend radially outward from central boss 117. The spider arms are attached to an upper region of topshell 111 via an intermediate annular flange such that the spider arms and topshell 111 form a unitary structure and are formed integrally. Upper shaft end region 113 is protected and encased by an annular sleeve 114. Spider bushing 112 is positioned at central boss 117 to contact the radially outward facing surface 204 of sleeve 114 as sleeve 114 rotates within central boss 117. An annular wear collar 120 is mounted coaxially and radially intermediate an axially lower region of bushing 112 and shaft sleeve 114 to provide a seat for the rotating sleeve 114 that, due to the relative dimensions and positioning of wear collar 120 is prevented from contact with bushing 112. This is advantageous to obviate the requirement for replacement of the entire bushing 112 which would otherwise wear due to the rotating frictional contact with sleeve 114. Collar 120 may be attached at bushing 112 via specific attachment elements as described herein or may be thermally shrink-fitted within the bushing 112. Accordingly, in some embodiments, collar 120 may be removed and replaced at bushing 112 when worn. Alternatively, the entire assembly may be designed to be replaced follow wear of collar 120. Additionally, it is advantageous for collar 120 to comprise a different material to that of bushing 112 so as to be optimised for wear resistance. As the general size and geometry of collar 120 is significantly less than bushing 112, the increased cost of the wear resistant material is maintained to a minimum which would otherwise be prohibitive if implemented as part of the much larger bushing 112. Referring to figures 2 to 6, bushing 112 comprises a generally annular sleeve-like body that extends around axis 122 and is positioned centrally within spider boss 117. Bushing 112 comprises a radially inward facing surface 203 at an axially upper half and a corresponding radially inward facing surface 201 at an axially lower half. Inner surface 201 is stepped radially outward from axis 122 relative to inner surface 203 to create an annular shoulder 210 at the inner region of bushing 112 positioned approximately at a mid-axial region between a first axially upper end 208 and a second axially lower end 207 of bushing 112. An opposed radially outward facing surface 215 of bushing 112 is configured for contact and mating against a radially inward facing surface 216 of spider boss 117. The region between the outward facing surface 215 and inward facing surfaces 201, 203 defines the annular wall of bushing 112. An annular flange 209 projects radially outward from the first upper axial end 208 to seat bushing 112 at an annular ledge 218 formed at an upper region of central boss 117. First end 208 is defined by an axially uppermost surface 219 of flange 209. A plurality of anchorage bolts 200 extend axially through flange 209 and into ledge 218 to rotatably lock bushing 112 relative to axis 122 and central boss 117. A plurality of boreholes 211 also extend axially through flange 209 to provide a conduit for lubrication oil and the like to the region between bushing 112 and sleeve 114. As illustrated in figures 2 to 6, the axially upper radially inward facing surface 203 slopes radially inward towards axis 122 from upper end 208 towards annular shoulder 210 such that surface 203 is aligned transverse to axis 122. This provides the necessary clearance to accommodate the gyroscopic precession of the main shaft region 113 and sleeve 114 within the boss 117. The axially lower inward facing surface 201 is arranged transverse to upper surface 203 and is aligned substantially parallel to axis 122. This provides a seat to align collar 120 coaxially with axis 122. An axially lower end of bushing 112 terminates at an annular foot 206 configured to seat and positionally retain a sealing ring 121 (formed form a deformable material such as rubber or a polymer) releasably mounted at (and in particular below) the second lower axial end 207 of bushing 112. Wear collar 120 comprises a generally annular sleeve-like body having a radially inward facing surface 202 and a radially outward facing surface 205 extending axially between a first upper end 213 and a second lower end 212. A radial wall thickness of collar 120 is less than the corresponding wall thickness of bushing 112 between the opposed and respective inward and outward facing surfaces 202, 205 and 201, 215. In particular, the radial wall thickness of collar 120 is approximately equal to or less than half the corresponding wall thickness of wall bushing 112. First end 213 of collar 120 is configured to abut annular shoulder 210 to prevent upward axial movement of collar 120 beyond the annular recess 214 that is indented at the inner region of collar 120 and defined by the radially inward facing surface 201 and shoulder 210. Due to the relative radial length of shoulder 210 and the radial wall thickness of collar 120, collar 120 projects radially inward from inward facing surfaces 201, 203 of bushing 112 so as to stand internally 'proud' of bushing 112 when mounted in position as shown in figures 2 to 6. The radially inward facing surface 202 of collar 120 comprises a chamfer 500 at second end 212 as illustrated in figure 5 and 6. That is, inward facing surface 202 tapers outwardly at chamfer 500 towards the outward facing surface 205. This configuration provides a smooth transition with an annular curved region 501 of bushing 112 that extends radially inward from foot 206 at bushing second end 207. Region 501 provides an annular cavity to accommodate a part of sealing ring 121 and a volume of lubricant oil. Sealing ring 121 is further held in position and trapped axially against foot 206 by an annular rim 217 that projects radially inward at an axially lower region of central boss 117. Collar 120 is rotatably and axially locked at bushing 112 by a plurality of attachment elements formed as threaded bolts (or screws) 400. Each bolt 400 is received respectively within a threaded bore that extends axially upward from a region of bushing second end 207 and the second end 212 of collar 120. In particular, each bore is formed by cooperatively mated part cylindrical recesses 401, 402 embedded within the respective axially lower ends of collar 120 and bushing 112. Accordingly, each bolt 400 is positioned at the junction between the collar outward facing surface 205 and the bushing inward facing surface 201 at the respective lower second ends 212, 207. In this configuration, collar 120 may be conveniently attached and demounted at bushing 112 via the axially extending bolts 400 being accessible from the axially lower region of central boss 117 when shaft 107 and sleeve 114 are removed. Accordingly, each bolt 400 comprises a drive head 600 engageable by a suitable tool. According to further specific implementations, collar 120 may be attached and rotatably locked at bushing 112 via any convenient means of attachment. Such attachment arrangements may comprise tong and groove configurations in which collar 120 slides axially upward within bushing 112 and is then rotated to locate anchorage lugs extending radially from collar 120 into anchorage recesses indented on the inward facing surface of bushing 112. According to yet further specific implementations, collar 120 and bushing 112 may comprise cooperating screw threads formed at respective surfaces 205 and 201. Locking pins, bolts, rivets or flanges may then anchor collar 120 at bushing 112 with such locking elements provided at the second axially lower regions 207, 212 of the respective bushing 112 and collar 120. To reduce wear and extend the longevity of collar 120, collar 120 comprises a material different to a material of bushing 112. In particular, collar 120 comprises a metal, ceramic or polymer material having enhanced wear resistance relative to the material of bushing 112 which is typically grey iron. In one specific implementation, collar 120 comprises a bronze alloy. This is particularly advantageous to allow shrink-fitting of collar 120 at bushing 112 (to provide a secure friction-fit arrangement) optionally followed by subsequent mounting of bolts 400 within respective bores 401, 402. When assembled as illustrated in figures 1 to 6, radially inward facing surface 202 of collar 120 is positioned for mating contact against a radially outward facing surface of main shaft sleeve 114. The upper end region 113 of shaft 107 is capable of gyroscopic precession within the annular bore of the bushing assembly that is defined by the inward facing surface 203 of bushing 112 and surface 202 of collar 120. Following extended use, collar 120 may be readily demounted and replaced at bushing 112 without any wear or damage to bushing 112 due to the rotation of sleeve 114 and shaft region 113 within boss 117. The present bushing assembly is therefore advantageous to reduce the amount of material that is required to be replaced and to optimise the physical and mechanical characteristics of the selected components of the assembly suitable for wear resistance as effective wear parts. Referring to figure 5, an axial length M of bushing 112 is defined as the axial distance between the bushing first end 208 (corresponding to uppermost annular surface 219) and the bushing second end 207 and in particular a region 502 of bushing 112 that is aligned at the same axial position as the lowermost second end 212 of collar 120. Region 502 is accordingly positioned axially between the bushing first 208 and second 207 ends and axially above the foot 206. Additionally, a relative axial length C of collar 120 is defined as the axial distance between the respective collar first 213 and second 212 ends and corresponds to a total axial length of collar 120. According to the specific implementation, axial length M is greater than axial length C and in particular, length C is less than 75% (and optionally less than 60%) of length M. Accordingly, collar 120 does not extend into the axially upper region of bushing 112. Such an arrangement is advantageous to optimise the volume of the higher performance material of collar 120 within the present bushing assembly.

1. A gyratory crusher spider bushing assembly for positioning radially intermediate a topshell spider (110) and a crusher main shaft (107) configured for gyroscopic precession within a crusher, the assembly comprising: an annular main body (112) extending around an axis (122) of the assembly and having a radially outward facing surface (215) for positioning opposed to the topshell spider (110) and a radially inward facing surface (201, 203) for positioning opposed to the main shaft (107) or a sleeve (114) surrounding the main shaft (107), the main body (112) formed from a first material; the main body (112) comprising a first end (208) having a mount flange (209) extending radially outward and a second end (207) intended to be positioned lowermost within the crusher relative to the first end (208); an annular wear collar (120) positioned at the inward facing surface (201) and extending radially inward from the main body (112) to contact the main shaft (107) or the sleeve (114); the collar (120) mounted at the main body (112) to prevent independent rotation of the collar (120) about the axis (122) relative to the main body (112); characterised in that: the collar (120) comprises: a second material having a wear resistance greater than the first material; and an axial length (C) corresponding to a distance between a first end (213) and a second end (212) of the collar (120) that is less than that 75% of an axial length (M) the main body (112) corresponding to a distance between the first end (208) of the main body (112) and a region (502) of the main body (112) aligned at the same axial position as the second end (212) of the collar (120); the collar (120) positioned axially closest to the second end (207) of the main body (112) relative to the first end (208) of the main body (112).

2. The assembly as claimed in claim 1 wherein the axial length (C) of the collar (120) is less than 60% of the axial length (M) of the main body (112). 3. The assembly as claimed in claim 1 or 2 wherein the inward facing surface (201, 203) and/or the collar (120) comprises a radially extending abutment (210) to axially separate and prevent the collar (120) from moving axially towards the first end (208). 4. The assembly as claimed in claim 3 wherein the abutment (210) comprises a step configuration at the inward facing surface (201, 203) of the main body (112). 5. The assembly as claimed in claim 4 wherein the step configuration comprises a recess (214) at the inward facing surface (201, 203) extending axially from the second end (207), the recess (214) terminated at an axially upper region by an annular shoulder (210) such that the collar (120) is at least partially accommodated within the recess (214) and the first end (213) of the collar (120) abuts the annular shoulder (210). 6. The assembly as claimed in claim 5 further comprising a plurality of attachment elements (400) extending between the collar (120) and the main body (112). 7. The assembly as claimed in claim 6 wherein the attachment elements (400) are aligned coaxially with the main body (112) and/or the collar (120) and are positioned axially at or towards the second end (207) of the main body (112). 8. The assembly as claimed in claim 7 wherein the collar (120) is positioned exclusively axially within a region of the main body (112) closest to the second end (207) relative to the first end (208) such that a region of the main body (112) closest to the first end (208) is devoid of the collar (120). 9. The assembly as claimed in any preceding claim wherein the axial length (C) of the collar (120) is in the range 20 to 60% of the axial length (M) of the main body (112). 10. The assembly as claimed in any preceding claim wherein the physical or mechanical properties of second material relative to the first material comprise anyone of a combination of: a material that has a higher hardness; a softer material having reduced friction or friction coefficient; a material that has a lower surface pressure. 11. The assembly as claimed in any preceding claim wherein the second material comprises any one or a combination of the set of: a metal or metal alloy; a copper/zinc based alloy; a manganese steel; a polymer; a ceramic. 12. The assembly as claimed in any preceding claim wherein a radial thickness of the main body (112) between the inward (201) and outward (215) facing surfaces is greater than a radial thickness of the collar (120) between a radially inward (202) and a radially outward (205) facing surface of the collar (120). 13. The assembly as claimed in any preceding claim when dependant on claim 3 wherein the inward facing surface (201, 203) of the main body (112) is aligned transverse to the axis (122) of the assembly to tilt radially outward such that a radial separation distance of said inward facing surface (201, 203) at an axial position of the first end (208) of the main body (112) is more than a radial separation distance of said inward facing surface (201, 203) at an axial position at or towards the abutment (210). 14. The assembly as claimed in any preceding claim wherein the second end (212) of the collar (120) comprising a chamfer (500) to decrease a radial thickness of the collar (120) at the second end (207) between an inward (202) and an outward (205) facing surface of the collar (120). 15. A gyratory crusher comprising an assembly as claimed in any preceding claim.

2873462

Wear resistant VSI crusher distributor plate

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to figure 1, a rotor 100 of a vertical shaft impact (VSI) crusher comprises a roof in the form of an upper horizontal disc 101 having an upper wear plate 103, and a floor in the form of a lower horizontal disc 102. The lower disc 102 comprises a hub 105, which is welded centrally to a lower surface of disc 102 and is configured to be connected to a vertical shaft (not shown) for rotating rotor 100 within a main housing (not shown) of the VSI-crusher. Upper disc 101 has a central aperture 104 through which material to be crushed may be fed into rotor 100. Upper horizontal disc 101 is protected from crushable material impacting the rotor 100 from above by a top wear plate 103. Figure 2 illustrates upper disc 101 and wear plate 104 removed for illustrative purposes. Lower disc 102 is protected from wear by three lower wear plates 201. A distributor plate 200 is attached to a centre region of lower disc 102 and is configured to distribute the feed material received through aperture 104 and to protect the lower disc 102 from wear and impact damages caused by the abrasive contact with the feed material. Distributor plate 200 is modular and comprises three separate segments 205 arranged circumferentially around a central longitudinal axis 211 that extends through rotor 100 and is aligned substantially perpendicular to upper and lower discs 101, 102. Each segment 205 comprises a wear resistant insert 210 arranged at a perimeter region of distributor plate 200. Upper and lower discs 101, 102 are separated axially by a series of rotor wall sections 202 that extend vertically between discs 101, 102 and are positioned radially outside of the lower wear plates 201. Spatial gaps are provided between wall sections 202 to define outflow openings 204 through which the feed material is ejected by the centrifugal forces of the spinning rotor 100 to contact surrounding anvils (or retained material) that act to crush the material for subsequent discharge from the crusher. Referring to figures 2 and 3, each wall section 202 is terminated at a leading edge side by a wear tip holder 208 that mounts a wear resistant tip 207. Holder 208 and tip 207 are also aligned substantially vertically to extend between the upper and lower discs 101, 102. Each wall section 202 further comprises a wear tip shield 212 positioned at an opposite trailing edge of wall section 202 to extend substantially vertically between the upper and lower discs 101, 102. Accordingly, material outflow regions 204 are defined circumferentially between each wear tip 207 (and tip holder 208) and an adjacent tip shield 212. Referring to figure 3, arrow R indicates the rotational direction of the rotor 100 during operation of the VSI-crusher. During operation of the rotor 100, a bed of material 300 is created against each of the three wall section 202 and on top of each plate 201 (only one bed 300 is illustrated for clarity). Bed 300, formed from material that has been fed to the rotor 100 and has been trapped inside it, extends from a rear support plate 209 to wear tip 207 (and holder 208). Each material bed 300 acts to protect the wall section 202, the plate 201 and the wear tip 207 from wear and provides directional control of the ejected material. Arrow A describes a typical passage of material fed to rotor 100 via central aperture 104 and ejected via outflow opening 204. As illustrated in figure 3, the flow of material passing through rotor 100 travels in contact with a single distributor plate segment 205 in a generally radially outward direction from central axis 211. That is, the flow of material does not pass over the transitions between individual segments 205. More specifically, the flow A of material passes over predominantly vertex 301 formed at the junction between distributor plate edges 302, 303. Accordingly, the edges 302, 303 and vertex 301 of each segment are subjected to enhanced levels of abrasion wear relative to radially inner or other circumferential regions spaced from each vertex 301 and edges 302, 303. Accordingly, the wear resistant insert 210 is located at each distributor plate segment 205 at the region of vertex 301 and edges 302, 303. Distributor plate 200 is supported at a raised position above lower disc 102 via a mount plate (the position of which is indicated generally by reference 206) positioned immediately and directly below the distributor plate 200. The mount plate is, in turn, bolted to lower disc 102 via a locating cap screw (not shown) and locking pin and bolt set. Referring to figures 4 to 8, each distributor plate segment 205 comprises an upward facing surface 401 intended to be positioned facing towards upper disc 101 and a downward facing surface 402 for mounting against the mount plate 206. Each surface 401, 402 is defined by a pair of inner edges 406, 407 that are configured for positioning against the inner edges 406, 407 of a neighboring plate segments 205 to form the complete tessellated hexagonal shaped distributor plate 200. Surfaces 401, 402 are further defined by the radially outward facing edges 302, 303 that define a perimeter region of distributor plate 200. Each segment 205 comprises as a majority component, a main body 400. Main body 400 comprises a ductile iron alloy (alternatively turned ductile cast iron, nodular cast iron, spheroidal graphite iron, spherulitic graphite cast iron or SG iron). Main body 400 is formed as an iron alloy matrix comprising nodules of graphite and one or more nodulising elements such as magnesium for example. To provide enhanced wear resistance, cemented carbide granules 408 are embedded within the predominantly iron based main body 400 during casting to form a composite structure. Advantageously, the cemented carbide granules 408 are distributed non-uniformly through the depth of each segment 205 in a direction of axis 211 from upper surface 401 to lower surface 402. That is, granules 408 are concentrated at surface 401 so as to decrease in concentration towards surface 402. In particular, carbide granules 408 penetrate to a depth of approximately one third of the thickness of main body 400 in the axial direction from upper surface 401 to lower surface 402. The granules 408 are however distributed substantially uniformly in the plane of segment 205 substantially perpendicular to axis 211. Additionally, according to further embodiments, the granules 408 may have a higher concentration towards outer edge regions 302, 303. Furthermore, granules 408 may comprise a higher concentration within main body 400 at a region immediately surrounding wear resistant insert 210. Carbide granules 408 may comprise any form of metal carbide including by way of example titanium-carbide, zirconium-carbide, hafnium-carbide, vanadium-carbide, niobium-carbide, tantalum-carbide, chromium-carbide, molybdenum-carbide, tungsten-carbide, manganese-carbide, cobalt-carbide, nickel-carbide. As indicated, distributor plate 200 comprises three wear resistant inserts mounted at the uppermost plate surface represented in part by the upper segment surfaces 401. Each insert 210 is bonded to main body 400 during casting so as to bond and securely mount each insert 210 at each segment 205. Inserts 210 comprises a cemented tungsten carbide material that exhibits enhanced wear resistance relative to main body 400 and comprises a plate-like shape profile having a thickness (in the direction of axis 211) that is less than the thickness of main body 400. In particular, a thickness of each tile 210 is up to approximately one third of the thickness of main body 400. Insert 210 comprises an irregular heptagonal configuration in which five edges 403 are mounted and embedded internally within the main body 400 whilst two edges 404, 405 are radially outward facing away from axis 211 to be co-aligned with segment edges 302, 303 respectively. Insert 210 is further defined by an upward facing surface 409 and an opposed downward facing surface 410. Upper insert surface 409 is positioned coplanar with segment upper surface 401 so as to avoid the creation of any ridges at the upward spacing surface of distributor plate 200 that may otherwise deflect the flow A of material during rotation. This is achieved conveniently by the casting process in which insert lower surface 410 and edges 403 are bonded to the ductile iron main body 400. The inventors have observed that the bonded strength between insert 210 and main body 400 is enhanced due to the incorporation of the nodular graphite and/or carbide granules 408 within the ductile iron. This is advantageous as the centrifugal forces acting on insert 210 would otherwise facilitate detachment of the insert 210 during use. Insert 210 is specifically positioned at the region radially inside vertex 301 (and to each lateral side of vertex 301) such that upper surface 409 represents a contact region over which the majority of the feed material flows. In particular, due to its relative positioning, the majority of the material flow (A) leaves each segment 205 over and in contact with the two edges 404, 405. According to the specific implementation, a surface area of insert surface 409 relative to a surface area of segment upper surface 401 is in a range 10 to 50% and is preferably in a range 20 to 40%. The singular insert surface 409 therefore presents a significant portion of the upward facing surface 401 of each segment 205. As illustrated in figures 4 to 8, each segment 205 comprises a pair of relatively short cylindrical support feet 411 configured to seat into mount plate 206 so as to rotatably lock distributor plate 200 within rotor 100. Each segment 205 further comprises a lower wear resistant inserts 412 positioned generally at segment downward facing surface 402. Each lower insert 412 is positioned to be facing mount plate 206 and provides redundancy protection for mount plate 206, lower disc 102 and hub 105 in the event of failure (cracking, excessive wear or fracture) of main body 400 and/or upper insert 210. Lower insert 412 is also positioned at a perimeter region of distributor plate 200 such that the majority of the lower insert 412 is positioned directly below upper insert 210. Each insert 210, 412 is separated in the axial direction by an intermediate region 413 of main body 400 to provide a tertiary layer structure at the region of edges 404, 405 and vertex 301 in the direction of axis 211. The relative thicknesses in the axial direction of upper insert 210, main body region 413 and lower insert 412 are substantially equal. Accordingly, a general thickness of the upper and lower insert 210, 412 is approximately equal. Referring to figures 7 and 8, each lower insert 412 comprises a white iron alloy (alternatively term white cast iron) that typically includes a cementite phase. Unlike the upper insert 210, lower insert 412 is bonded to an underside region of main body 400 using a suitable adhesive or other chemical bonding agent. According to further specific implementations, lower insert 412 may be attached via mechanical means such as bolts, plugs, screws or pins extending axially between insert 412 and main body 400. According to the specific implementation, each lower insert 412 comprises a pair of radially outward facing edges 702, 703 configured for positioning axially below upper insert edges 404, 405. The remaining perimeter of lower insert 412 is defined by a continuous curved and/or angled inner edge 704. A recess (or groove) 800 is indented into main body 400 to extend axially inward from segment lower surface 402. A depth of recess 800 in a direction of axis 211 is slightly greater than a thickness of lower insert 412 such that a downward facing surface 700 of insert 412 is recessed relative to segment surface 402. The adhesive or bonding agent (not shown) is provided between an upper facing surface 701 of insert 412 and the segment downward facing surface 402 within recess 800. The bonding agent may also be provided between the opposed insert edges 704 and edges 801 that in part, define recess 800. Insert 412 comprises a generally ' fish-tail' shape profile so as to wedge into recess 800 and be resistant to detachment due to the centrifugal forces created by the spinning rotor 100. That is, each insert 412 comprises a pair of tail segments 706 that extend laterally outward and rearward from an insert waist region 707. Accordingly, a radially inner region of each recess 800 comprises a flange region 705 projecting inwardly within recess 800 and a flared region 708 to mate respectively with the waist 707 and tail segments 706. Accordingly, flange 705 is configured to abut each tail segment 706 so as to lock insert 412 in position within recess 800 by mechanical frictional forces. Accordingly, due to the specific choice of constituent materials for the distributor plate segments 205, upper and lower inserts 210, 412 and the relative shape, size and position of the inserts 210, 412 at the respective upper and lower surfaces 401, 402 the present distributor plate 200 is optimised for wear resistance in response to a continuous flow of material in direction A. In particular, under controlled test conditions, the present distributor plate 200 achieved a wear life of over 620 hours in contrast to a conventional distributor plate that achieved only 125 hours.

1. A distributor plate assembly (200) releasably mountable to protect a disc (102) of a rotor (100) within a vertical shaft impact crusher from material fed into the rotor (100), the assembly comprising: a main body (400) having a contact surface (401) intended to be positioned in an upward facing direction within the crusher to contact the material fed into the rotor (100); characterised in that: the main body (400) comprises: ductile iron alloy incorporating nodular graphite; and cemented carbide granules (408) embedded within the iron alloy.

2. The assembly as claimed in claim 1 further comprising a first abrasion wear resistant insert (210) positioned at the main body (400) to represent a region of the contact surface (401). 3. The assembly as claimed in claim 2 wherein at least a part of the insert (210) is positioned at a perimeter region (302, 303) of the main body (400). 4. The assembly as claimed in claim 3 wherein the insert (210) is a plate-like body and the main body (400) is formed around the plate-like body at a region of the contact surface. 5. The assembly as claimed in claim 4 wherein the insert (210) comprises a polygonal shape profile wherein at least one edge (404, 405) of the insert (210) represents a region of at least one perimeter edge of the main body (400). 6. The assembly as claimed in any one of claims 2 to 5 wherein the insert (210) comprises a cemented carbide material. 7. The assembly as claimed in any one of claims 2 to 6 further comprising a second abrasion wear resistant insert (412) positioned at a rearward surface (402) of the main body (400), the rearward surface (402) being opposite the contact surface (401) and configured to mount the plate at the disc (102) of the rotor (100). 8. The assembly as claimed in claim 7 wherein the second insert (412) is a plate-like body positioned at a perimeter region of the main body (400) to represent a region of the rearward surface (402), at least a part of the second insert (412) positioned immediately behind the first insert (412). 9. The assembly as claimed in claim 8 wherein the main body (400) comprises a recess (800) at a region of the rearward surface (402), the second insert (210) accommodated within the recess (800) at the rearward surface (402). 10. The assembly as claimed in any preceding claim wherein the carbide granules (408) comprise any one or a combination of the following metals: titanium, zirconium, hafnium, vanadium, niobium, tantalum, chromium, molybdenum, tungsten, manganese, cobalt, nickel. 11. The assembly as claimed in any preceding claim wherein the carbide granules (408) embedded in the main body (400) penetrate from the contact surface (401) towards an opposite rearward surface (402) through the main body (400) to a depth up to 50% of a total thickness of the main body (400) between the contact (401) and rearward (402) surfaces. 12. The assembly as claimed in any preceding claim wherein the main body (400) is modular and comprises a plurality of segments (205) arranged in a circumferential direction around a central axis (211) of the distributor plate assembly (200). 13. The assembly as claimed in claim 12 when dependent on any one of claims 7 to 9 wherein each segment (205) comprises the first insert (210) and the second insert (412) positioned at the respective contact (401) and rearward (402) surfaces. 14. A vertical shaft impact crusher rotor (100) comprising a distributor plate assembly (200) according to any preceding claim. 15. A vertical shaft impact crusher comprising a rotor (100) as claimed in claim 14.

2876400

Cooling element

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figures 1 a and 1 b illustrate the working principle of a Pulsating Heat Pipe (PHP). Figure 1 a illustrates a closed-loop PHP and Figure 1b illustrates an open-loop PHP. A pulsating heat pipe involves a meandering flow channel 1 having a capillary dimension, in other words a cross-section small enough for capillary forces to dominate over gravity forces. A suitable fluid can be introduced into the flow channel 10 via a filling valve 4. As a consequence, the fluid is moved by pulsations generated by pressure instabilities. The oscillations occur in a small channel loop due to the bidirectional expansion of vapour inside the channels. During operation, the liquid slugs and elongated vapour bubbles will oscillate between a cold and a hot region because of hydrodynamic instabilities caused by the rapid expansion of the bubbles confined in the small channels, and thus provide a fluid velocity almost independent of gravity. This makes pulsating heat pipes fairly insensitive to orientation, with the possibility of operating them "upside down", i.e. with an evaporator 2 on top and a condenser 3 at the bottom. An advantage of utilizing a pulsating heat pipe in a cooling element is that the cooling element can be utilized in any orientation without causing problems for fluid circulation within the cooling element. Figure 2 illustrates a first embodiment of a cooling element 10. The cooling element 1 comprises a first surface 11 for receiving an electric component 12, such as a power-semiconductor module, which may be attached to the first surface with screws, for instance. One alternative is that the cooling element 10 is a part of a motor drive, such as a frequency controller, controlling supply of electricity to an electric motor. In that case the electric component 12 may be an IGBT (Insulated Gate Bipolar Transistor) module, for instance. A second surface 13 of the cooling element is provided with fins 14 for forwarding a heat load received from the electric component 12 to surroundings via the fins. In the illustrated example the fins 14 are implemented as elongated plates like elements protruding downwards from the second surface 13 of the cooling element 10. Spacers 16 may be arranged between the fins and in contact with the second surface 13 in order to obtain gaps between the fins. An airflow 15 may be generated to pass between the fins 14 such that the fins dissipate heat into this airflow 15. In order to obtain an efficient cooling element 10, one or more of the fins are provided with a flow channel 1 for passing a fluid within each respective fin 14. Preferably each fin has a flow channel, however, in some implementations it may be sufficient to have flow channels only in a part of the fins. Preferably, in order to avoid that the flow channel 1 of each fin needs to be filled separately, the flow channels 1 of the different fins 14 may be in fluid communication with each other. Such a fluid communication may be obtained via the base plate 17 to which the electric component 12 is attached and to which the fins 14 are thermally connected. In such a solution one single filling valve 4 arranged in the first surface of the base plate 17 may be used for introducing fluid into all of the fins 14. An advantage obtained by having fluid channels in the fins 14 is that a more efficient distribution of heat load to different parts of the fins is achieved. Consequently a significant area of the fins can be efficiently utilized for dissipating heat to surroundings, as the fluid in the fluid channel 1 efficiently transfers heat between different parts of the fins 14. Figure 3 illustrates a first embodiment of a fin 14. The fins used in the embodiment of Figure 2 may be implemented as illustrated in Figure 3. The illustrated fin 14 comprises a stack of plates 21 to 23 arranged against each other. The middle plate 22 has a slit which works as the fluid channel 1 distributing fluid to different parts of the fin 14. This slit may be manufactured by punching or cutting, for instance. The two outer plates 21 and 23 are non-perforated solid plates which provide fluid tight outer walls for the fin 14 on opposite sides of the middle plate 22. The fin 14 has two openings 24 and 25 in opposite ends of the flow channel 1. The openings 24 and 25 are arranged in a side edge of the fin 14 which faces the second surface 13 of the cooling element 10. These openings facilitate a fluid communication between the fluid channel 1 of the fin 14 and other parts of the cooling element. If fluid circulation within the flow channel 1 should be obtained without the need of an external device, such as a pump, and independently of the orientation of the cooling element, the flow channel 1 may be capillary dimensioned in order to get the fins of the cooling element to work as a pulsating heat pipe. One way to determine whether or not the fluid channel has a capillary dimension is to calculate the Eötvös number, which should be below about 4. Eötvös number EÖ can be calculated as follows: [MATHS id=math0001] wherein D is the channel hydraulic diameter, g is the gravitational acceleration, ρliq is the liquid density, ρvap is the vapour density, σ is the surface tension. For refrigerant R245fa (1,1,1,3,3-Pentafluoropropane), which may be used as the fluid, a possible choice is a conduit height (= sheet thickness of the middle plate 22) of 1 mm and a conduit width (= width of slit in the middle plate 22) of 2 mm. This results in Eö = 2.2 at a fluid operating temperature of 60 °C, as shown in the table below: [TABLE 1] Figures 4 and 5 illustrate a second embodiment of a fin 14', which may be utilized in a cooling element 10 of Figure 2, for instance. The embodiment of Figures 4 and 5 is very similar to the one explained in connection with Figure 3. Therefore, the embodiment of Figures 4 and 5 will be explained mainly by pointing out the differences between these embodiments. The illustrated fin 14', may be utilized in a cooling element 10 of Figure 2, for instance. From Figure 4, which illustrates the parts of the fin 14' before assembly, it can be seen that the fin 14' comprises two middle plates 33 and 34 instead on only one middle plate in the embodiment of Figure 3. The first 33 and second 34 middle plates both comprise a plurality of separate slits 35 and 36 shaped and located in such positions that the slits 35 and 36 of the first 33 and second 34 middle plate will together form the fluid channel 1 once the plates are stacked against each other. Figure 5 illustrates the plates 32 and 33 stacked against each other. From Figure 5 it can be seen that the slits 35 and 36 of the first and second middle plate partly overlap each other such that a continuous fluid channel 1 is provided through the fin 14', similarly as in the embodiment of Figure 3. Similarly as in Figure 3, openings 24 and 25 are arranged in a side edge of the fin 14' which faces the second surface 13 of the cooling element 10. An advantage obtained with the embodiment of Figures 4 and 5 as compared to the embodiment of Figure 3, is that the middle plates 32 and 33 each consist of one single part only, which makes it easier to handle them during manufacturing, for instance. In Figure 3, the slit forming the fluid channel 1 cuts the middle plate into two separate parts, that need to be located in correct positions during manufacturing. In order to ensure that the fin 14' and the fluid channel 1 works as a pulsating heat pipe with the same fluid as explained in Figure 3, the thickness of the first 32 and second 33 middle plate may be 1 mm each. The thickness of the outer plates 21 and 23 may be 0.5 mm each, for instance. Figures 6 and 7 illustrate a second embodiment of a cooling element 40. The embodiment of Figures 6 and 7 is very similar to the one explained in connection with Figure 2. Therefore the embodiment of Figures 6 and 7 is explained mainly by pointing out the differences between these embodiments Similarly as in the embodiment of Figure 2, the fins 14 may be of the type illustrated in Figure 3 or of the type illustrated in Figures 4 and 5. In the embodiment of Figures 6 and 7, secondary fins 44 are, however, provided to extend between the illustrated fins 14. Such secondary fins 44, which increase the surface area dissipating heat into the airflow 15, may be utilized also in the embodiment of Figure 2. In the embodiment of Figures 6 and 7, the cooling element comprises a first plate 47 and a second plate 41 stacked against each other such that the first surface 11 for receiving an electric component 12 and the second surface 13 provided with fins 14 are facing opposite directions. Figure 7 illustrates the second plate 41 in more detail. The second plate working as a connector plate is provided with through holes 42 at the locations of the openings 24 and 25 of the fins 14. In Figure 7 only four fins 14 are illustrated for simplicity. As can be seen from Figure 7, the holes 42 in the second plate are such arranged and dimensioned that two fins 14 are located at each hole 42, and that one opening 24 of two adjacent fins 14 are in fluid communication via the hole 42 in question. Consequently the holes 42 provide fluid communication between the fluid channels 1 of the different fins. Due to this, the fluid channel of the different fins may be connected to a single closed loop working as a pulsating heat pipe. The first plate 47 may be implemented as a solid base plate that does not need to have any other fluid channels than possibly a bore for the filling valve 4. The first plate 47 provides a fluid tight roof on top of the second plate 42, and the second surface 13 (bottom surface in Figure 6 ) of the second plate 41 is prevented from leakage by the fins 14 and the spacer elements 16. Figure 7 illustrates that the second plate 41 is also provided with an elongated slit 43 which provides fluid communication between one respective opening of the two fins 14 which are located as far away from each other as possible. This elongated slit 43, extending completely through the second plate 41, is not necessary in all embodiments. If it is present, the result is (provided that dimensioning of the fluid channel is correct) a closed loop pulsating heat pipe, and if it is not present, the result is an open loop pulsating heat pipe. As is clear from the previous explanations, the incorporation of a pulsating heat pipe into the cooling element makes it possible to obtain a cooling element with efficient cooling capabilities and which can be used in any position necessary. Such an orientation independent cooling element can directly be used to replace an old prior art cooling element which does not include any fluid circulation in the fins, because the cooling element can be arranged in any position, also in a position where the first surface with the electric component is directed upwards and the fins are directed downwards. The production of the described cooling element can be accomplished by preparing metal plates of suitable size, by providing a solder at the locations where the parts should be attached to each other. After this the cooling element can be assembled and placed in an oven where it is heated to the melting point of the solder. Once removed from the oven, the parts attach firmly to each other while they are allowed to cool. It is to be understood that the above description and the accompanying figures are only intended to illustrate the present invention. It will be obvious to a person skilled in the art that the invention can be varied and modified without departing from the scope of the invention.

1. A cooling element (10, 40) comprising: a first surface (11) for receiving an electric component (12), a second surface (13) which is provided with fins (14, 14') for forwarding a heat load received from the electric component (12) via the first surface (11) to surroundings, characterized in that one or more of the fins (14, 14') are provided with a flow channel (1) for passing a fluid within each respective fin, the flow channel (1) having a capillary dimension and a meandering shape for providing a pulsating heat pipe.

2. The cooling element according to claim 1, wherein the flow channel (1) of the different fins (14, 14') are in fluid communication with each other. 3. The cooling element of one of claims 1 to 2, wherein the flow channel (1) of the the different fins (14, 14') are in fluid communication with each other and the cooling element comprises a common inlet (4) for introducing fluid to the fluid channel (1) of the different fins (14, 14'). 4. The cooling element of one of claims 1 to 3, wherein one of the fins (14) comprises a stack of plates, where the fluid channel (1) consists of a slit in a middle plate (22) and two outer plates (21, 23) on opposite sides of the middle plate provide fluid tight side walls of the fluid channel (1). 5. The cooling element of one of claims 1 to 4, wherein one of the fins (14') comprises a stack of plates, where the fluid channel (1) consists of a plurality of separate slits (35, 36) provided in a first (32) and second (33) middle plate such that the slits (35, 36) in the first (32) and second (33) middle plate partly overlap each other to provide a continuous fluid channel (1) through the fin (14'), and two outer plates (21, 23) on opposite sides of the first and second middle plate provide fluid tight side walls of the fluid channel (1). 6. The cooling element of one of claims 1 to 5, wherein the cooling element (40) comprises: a first plate (47) with the first surface (11) for receiving the electric component (12), and a second plate (41) with the second surface (13) which is provided with fins (14, 14'), the second plate (41) is stacked against the first plate (47) such that the first (11) and second (13) surfaces are facing opposite directions, the one or more fins (14, 14') provided with a flow channel comprises two respective openings (24, 25) in opposite ends of the respective flow channel (1), the openings (24, 25) facing the second plate (41), and the second plate (41) is provided with through holes (42) at the locations of the openings (24, 25) such that one opening (24) of two adjacent fins (14) are in fluid communication with each other via one through hole (42) provided in the second plate (41). 7. The cooling element of one of claims 1 to 5, wherein the cooling element (40) comprises: a first plate (47) with the first surface (11) for receiving the electric component (12), and a second plate (41) with the second surface (13) which is provided with fins (14, 14'), the second plate (41) is stacked against the first plate (47) such that the first (11) and second (13) surfaces are facing opposite directions, the one or more fins (14, 14') provided with a flow channel comprises two respective openings (24, 25) in opposite ends of the respective flow channel (1), the openings (24, 25) facing the second plate (41), the second plate (41) is provided with through holes (42) at the locations of the openings (24, 25) such that one opening (24) of two adjacent fins (14) are in fluid communication with each other via one through hole (42) provided in the second plate (41), and the second plate (41) is provided with an elongated slit (43) providing fluid communication between one respective opening (24) of the two fins (14, 14') which are located farthest away from each other. 8. The cooling element of one of claims 1 to 7, wherein the cooling (40) element comprises secondary fins (44) extending between the fins (14) provided on the second surface (41).

2876781

Electrical machine with improved cooling

Based on the following detailed description of an invention, generate the patent claims. There should be 12 claims in total. The first, independent claim is given and the remaining 11 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With now reference to Figure 1, it is illustrated a component for an electrical machine 1 according to the prior art. The component 1 comprises a plurality of stacked laminations 11, which are generally used to assemble stator cores or used to for forming poles mounted on the rotor. The stacked laminations 11, in order to satisfy the important need of providing a suitable cooling system therein, comprise distance means in the form of longitudinal elements, schematically represented in the figure and denoted with reference 12, which are usually welded between a pair of adjacent stacks 13a and 13b. In particular, distance means 12 is welded on a top lamination 131b of the stack 13b and on a bottom lamination 131a of the stack 13a to create a separation between the stack, thus allowing a cooling fluid to flow therein and provide heat removal. It will be appreciated that lamination stack 11 may comprise a plurality of layers of adjacent lamination stacks, in pair separated by welded distance means as explained above. The amount of stacks assembled will vary depending on the particular machine to manufacture based on the required power to be supplied. As stated above, the assembly of such component, because of the presence of welded distance means, requires great effort because the welding procedure requires time and also has to be operated properly. In fact, it is of paramount importance avoiding the movement of the welded spacers while the machine is in use, especially for the ones mounted on the rotor where important centrifugal forces are involved during operation. Figure 2 shows a planar view of the top lamination 131b as described above. The figure shows longitudinal elements 12 welded on the surface of the lamination 131b creating separation between the latter and the opposed lamination (not shown). Figure 2A shows an axial section of the longitudinal element 12. With now reference to the next Figure 3, it is shown a prospective view of a component 2 according to a first preferred embodiment of the present invention. The component 2 comprises a plurality of stacked laminations 21. In particular, the component 2 comprises a corrugated layer 22 which is interposed between a pair of adjacent stacks 23a and 23b. As clearly visible in the figure, the corrugated layer 22 provides a separation means between the stacks 23a and 23b. This way, a plurality of passageways 7 are formed between the stacks 23a and 23b for the passage of a cooling fluid, when the rotating machine is assembled and in operation. Preferably, the corrugated layer comprises a first lamination 221, positioned on top of the stack 23b, which is deformed in such a way to define on its surface first recesses 222. Preferably, first recesses 222 are in the form of longitudinal ducts, having a rectangular section. Other shapes may also be considered, like a trapezoidal one. Different process may be chosen for acquiring the first recesses 222 on the first lamination 221. An advantageous one is the forming process, in particular hydroforming. Hydroforming process allows the formation of particular shapes on ductile metals such as aluminum, brass or stainless steel by insertion of the laminate in a chamber comprising a mold and an aperture for the injection of a fluid. High pressure hydraulic pumps then inject fluid at high pressure inside the chamber which causes the laminate to expand until it matches the mold. Such process is generally used in the automotive industry. As this process is known in the art, it won't be herewith further described. With now reference to the following Figure 4, it is shown a component 3 according to a second preferred embodiment of the invention. Similarly, the component 3 comprises the plurality of stacked lamination 21 comprising a pair of adjacent lamination stacks 23a and 23b. A corrugated layer 32 is interposed there between by means of lamination 221 deformed in such a way to obtain first recesses 222. The corrugated layer 32 defines passageways 7 for the coolant fluid. The first recesses 222 are in this example in the form in longitudinal ducts, having in this embodiment a trapezoidal section. It will be appreciated that a rectangular section could be used instead. In such embodiment, the corrugated layer 32 comprises a second lamination, indicated in the figure with numeral reference 321, disposed adjacent to the first lamination and deformed as well in such a way to define on its surface a plurality of second recesses 322. Advantageously, recesses 222 and 322 have identical sections. First and second laminations 221 and 321 are disposed such that first and second recesses 222 and 322 have aligned convexities and such that each second recess 322 is at least partially hosted into a correspondent first recess 222. This configuration is particularly advantageous because it strengthens the mechanical stiffness and stability of the stacked lamination, especially in correspondence of the channels for the passage of cooling fluid. Moreover, the choice of trapezoidal section for the ducts formed on the lamination is particularly preferred as such section assures a minor mechanical stress on the material, which then guarantees a more reliable behaviour while in operation. With reference to Figure 5, it is shown a third preferred embodiment of the component according to the invention, denoted with numeral 4. Similarly, the component 4 comprises a pair of adjacent stacks 23a and 23b and a corrugated layer 42. The corrugated layer 42 comprises the first lamination 221 disposed on top of the stack 23b deformed as to define first recesses 222 having a form of longitudinal ducts (in this example having a substantially rectangular section). In this third preferred embodiment, the corrugated layer comprises a third lamination 421, in turn deformed in a way to define on its surface third recesses 422. In this example as well, first and third recesses have identical sections. However, first lamination 221 is opposite with respect to third lamination 421 and disposed such that first and third recesses 222 and 422 have opposite convexities and each first recess abuts on a correspondent third recess. This configuration is particularly advantageous because it assures a homogeneous distribution of the pressures involved in the lamination stacks during operation. It will be appreciated that also various combinations of preferred embodiments may be carried out. For example, the third embodiment may have first recesses 222 formed by a couple of laminations disposed as taught with reference to the second embodiment. Making now reference to next Figure 6, it is shown a component 5 according to a forth embodiment of the present invention. Similarly, the component 5 comprises a pair of adjacent stacks 23a and 23b and a corrugated layer 52. This embodiment differs from the preceding ones in the fact that on a first lamination 521 the recesses are in the form of a plurality of dimples, indicated in the figure with the reference number 522. Advantageously, by means of the presence of dimples passageways 7 are configured as a plurality of possible paths which the fluid can pass through. It will be appreciated that preferred features of preceding preferred embodiments are applicable mutatis mutandis to the forth embodiment. More in particular, the corrugated layer 52 may comprise a second lamination 531 opposite to the first lamination 521, the two laminations having correspondent dimples disposed with opposite convexities such that each dimple of the first lamination 521 abuts on a correspondent dimple 532, formed on second lamination 531. Furthermore, each dimple on the stack may be formed by two laminations as described, mutatis mutandis, concerning second embodiment. Advantageously, as detailed in next Figure 7, each dimple may be hollow inside and comprise an opening 5221 configured to allow passage of the cooling fluid inside the dimple. This way, the surface for the heat exchange is greatly increased, thus greatly improving the process of heat removal. With reference to the final Figure 8, it is shown a fifth last embodiment which is a combination of all the embodiments above described. In particular, Figure 8 illustrates a planar view of a corrugated layer 62 comprising a lamination 621 including a top portion having recesses in the form of a plurality of dimples, and lower portions characterized by recesses 222 in the form of longitudinal ducts. In practice the materials used and the dimensions can be chosen according to requirements and to the state of the art.

1. A component (2, 3, 4, 5, 6) for an electrical machine comprising a plurality of stacked laminations (21), the component (2, 3, 4, 5, 6) being characterized in that it comprises at least a corrugated layer (22, 32, 42, 52, 62) interposed between a pair of adjacent stacks (23a, 23b), such that said pair of adjacent stacks (23a, 23b) are spaced apart and such that a plurality of passageways (7) for a cooling fluid are formed there between.

2. The component (2, 3, 4, 5, 6) according to the preceding claim, wherein the corrugated layer (22, 32, 42, 52, 62) comprises a first lamination (221, 521, 621) deformed in such a way to define on its surface a plurality of first recesses (222, 522). 3. The component (2, 3, 4, 5, 6) according to claim 2, wherein the corrugated layer (32, 42, 52, 62) comprises a second lamination (321, 421, 531) being deformed in such a way to define on its surface a plurality of second recesses (322, 422, 532). 4. The component (3) according to the preceding claim, wherein said first and second recesses (222, 322) have aligned concavities, said second lamination (321) being disposed adjacent to said first lamination (221) such that each second recess (322) is at least partially hosted into a correspondent first recess (222). 5. The component (4, 5) according to any of claims 2 to 4, wherein said corrugated layer (42, 52) comprises a third lamination (421, 521) deformed in such a way to define on its surface a plurality of third recesses (422, 532), wherein said third and first recesses (422, 532; 222, 522) have opposite convexities, said third lamination (421, 521) being disposed opposite to said first lamination (221, 521) such that each third recess (422, 532) abuts on a correspondent first recess (222, 522). 6. The component (2, 3, 4, 6) according to any of the preceding claims, wherein said recesses (222, 322, 422) comprise longitudinal ducts (222, 322, 422). 7. The component (2, 3, 4, 6) according to the preceding claim, wherein said longitudinal ducts (222, 322, 422) have a substantially rectangular and/or trapezoidal section. 8. The component (5, 6) according to any claims 6 or 7, wherein the recesses (522, 532) comprise dimples (522, 532). 9. The component (5, 6) according to the preceding claim, where each dimple (522, 532) is hollow and comprises an opening (5221), the opening (5221) being configured to allow passage of the cooling inside said dimple (522, 532). 10. The component (2, 3, 4, 5, 6) according to any of the preceding claims, wherein said corrugated layer (22, 32, 42, 52, 62) is obtained by a forming process. 11. The component (2, 3, 4, 5, 6) according to the preceding claims, wherein the forming process is a hydroforming process. 12. An electrical machine, characterized in that it comprises a component (2, 3, 4, 5, 6) according to any of the preceding claims.

2876901

Hearing aid interconnection system

Based on the following detailed description of an invention, generate the patent claims. There should be 13 claims in total. The first, independent claim is given and the remaining 12 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The invention will become more fully understood from the detailed description given herein below. The accompanying drawings are given by way of illustration only, and thus, they are not limitative of the present invention. In the accompanying drawings: - Figure 1 a): shows a schematic cross-sectional view of a hearing aid connection system according to the invention; - Figure 1 b): shows a front view of the hearing aid connection system shown in Figure 1 a); - Figure 2 a): shows a schematic perspective view of a hearing aid connection system according to the invention; - Figure 2 b): shows a schematic cross-sectional view of the hearing aid connection system shown in Figure 2 a); - Figure 3 a): shows a schematic view of a prior art bone anchored hearing aid system including a hearing aid that is connected to a hearing aid abutment that penetrates the skin and is connected to a fixture anchored in the skull bone; - Figure 3 b): shows a schematic view of a prior art bone anchored hearing aid system similar to the one shown in Figure 3 a), where the hearing aid abutment is surrounded by swollen skin tissue; - Figure 4 a): shows a schematic view of a bone anchored hearing aid abutment surrounded by swollen skin tissue; - Figure 4 b): shows a schematic view of an extension member according to the invention mounted on a bone anchored hearing aid abutment surrounded by swollen skin tissue; - Figure 4 c): shows a schematic view of a hearing aid device attached to the bone anchored hearing aid abutment shown in Figure 4 b); - Figure 5 a): shows a schematic view of a bone anchored hearing aid abutment is surrounded by swollen skin tissue; - Figure 5 b): shows a schematic view of an extension member according to the invention mounted on a bone anchored hearing aid abutment is surrounded by swollen skin tissue; - Figure 5 c): shows a hearing aid device attached to the bone anchored hearing aid system shown in Figure 4 b); - Figure 6 a): shows a schematic view of a hearing aid interconnection system comprising a prior art bone anchored hearing aid abutment is surrounded by swollen skin tissue and - Figure 6 b): shows a schematic view of an extension member according to the invention mounted on a bone anchored hearing aid abutment is surrounded by swollen skin tissue. Referring now in detail to the drawings for the purpose of illustrating preferred embodiments of the present invention, different views of a hearing aid interconnection system 34 according to the invention are illustrated in Figure 1. Figure 1 a) shows a schematic cross-sectional view of a hearing aid interconnection system 34 aid according to the invention. The hearing aid interconnection system 34 comprises a fixture 4 having a threaded portion 6. The fixture 4 is configured to be anchored and implanted in the skull bone of a user of a hearing aid. The hearing aid interconnection system 34 comprises an abutment 8 adapted to penetrate the skin and interconnect a hearing aid to the skull bone via the implanted fixture 4. The abutment 8 comprises a through-going hole 36 configured to receive a connection screw 12 that is used to mechanically fix the fixture 4 and the abutment 8 to each other. The fixture 4 comprises a bore 14 having inner threads configured to receive the threaded portion 16 of the connection screw 12. By tightening the connection screw 12, the screw 12 is displaced along the longitudinal axis X of the abutment 8. Hereby it is possible to secure that the fixture 4 and the abutment 8 are firmly attached to each other. By the above measures the abutment will be fixed to the fixture at a fixture end thereof, and at an opposed end a hearing aid attachment end is sitting above the skin surface, and a hearing aid may be attached at surfaces thereof, which are adapted to receive the hearing aid. The hearing aid interconnection system 34 comprises an extension member 10 which when mounted provides an extension of the abutment 8 along the longitudinal axis X thereof. The extension member 10 comprises a contact surface 18 matching a corresponding contact surface 20 of the top portion of the abutment 8. The extension member 10 is screwed onto the top portion of the connection screw 12. The extension member 10 comprises a threaded bore that is adapted to receive the threaded top portion 38 of the connection screw 12. Thus the extension member 10 is detachably attached to the abutment 8. The extension member 10 is intended to add a certain length to the abutment 8. This may be a useful alternative to exchanging the abutment 8 in case of swollen skin tissue. It can be seen that the extension member 10 add a length to the abutment 8 of a distance D. Figure 1 b) illustrates a front view of the hearing aid connection system 34 shown in Figure 1 a). The hearing aid connection system 34 comprises a fixture 4 that is attached to the distal end of an abutment 8. The abutment 8 is sandwiched between the fixture 4 and an extension member 10 fixed to the proximal end of the abutment 8. The extension member 10 adds a length of distance D to the abutment 8 as indicated at Figure 1 b). The fixture 4 comprises a threaded portion 6 that is adapted to be anchored into the skull bone of a user of a hearing aid. It can be seen that the abutment 8 as well as the extension member 10 are symmetric about the longitudinal axis X of the abutment 8. The extension member 10 is a one piece part with hearing aid coupling surfaces at one part thereof and with abutment connection parts, movably connecting the extension member 10 to the head of connection screw 12, at another part thereof. Figure 2 a) illustrates a schematic perspective view of a hearing aid connection system 34 according to the invention. The hearing aid connection system 34 comprises a fixture 4 having a threaded portion 6 configured to be anchored into the skull bone of a user of a hearing aid. An abutment 8 is mechanically attached to the fixture 4 and an extension member 10 is fixed to the proximal end of the abutment 8. The extension member 10 comprises a fixed part 10' constituting the periphery of the extension member 10. The extension member 10 moreover comprises a movable part 10" that is movably mounted to the abutment 8 via a connection screw 12 (see Figure 2 b). A tool grip structure 24 adapted for engagement of a screwdriver is provided in the movable part 10" of the extension member 10. Another tool grip structure 22 is provided in the fixed part 10' of the extension member 10. The grip structure 22 is intended for providing counter torque. Figure 2 b) illustrates a schematic cross-sectional view of the hearing aid connection system 34 shown in Figure 2 a). The hearing aid connection system 34 comprises a fixture 4 having a threaded portion 6 for anchoring the fixture 4 in the skull bone of a user of a hearing aid. The hearing aid connection system 34 moreover comprises an abutment 8 that is mechanically attached to the fixture 4 by means of a centrally arranged connection screw 12. The connection screw is screwed into a centrally arranged threaded bore 14 provided in proximal and central end of the fixture 4. The connection screw 14 comprises a threaded portion 16 configured to engage in the threaded bore 14 in the fixture 4. The abutment 8 comprises a through-going hole 36 configured to receive the connection screw 12 that is used to mechanically attach the fixture 4 to the abutment 8. The extension member 10 comprises a fixed part 10' and a movable part 10" movably mounted to the abutment 8 via the connection screw. The movable part 10" comprises a threaded bore that is adapted to receive the threaded top portion 38 of the connection screw 12. A contact surface 20 provided at the proximal end of the abutment 8 bears against a corresponding contact surface 18 of the fixed part 10' of the extension member 10. Figure 3 a) illustrates a schematic view of a prior art bone anchored hearing aid system 34. The prior art bone anchored hearing aid system 34 is connected to a hearing aid abutment 8 that penetrates the skin 28 of the user of a hearing aid device 2. The hearing aid abutment 8 is connected to a fixture 4 that is anchored in the skull bone 26 of the user by means of a threaded portion 6. The hearing aid device 2 is mechanically attached to a coupling 30 that may comprise gripping jaws 30' which are adapted for a mechanical attachment to the abutment 8. Various jaw formats are available at the market, and they are not shown in further detail here. Figure 3 b) illustrates a schematic view of the bone anchored hearing aid system 34 shown in Figure 3 a). The bone anchored hearing aid system 34 comprises a hearing aid abutment 8 that is surrounded by skin tissue 28' whish has swollen due to hypotrophy or other disorder. A tissue growth like the one illustrated in Figure 3 b) typically may occur as a consequence of inflammation or infection in the skin tissue surrounding the abutment 8. Swollen scars 28' like the swollen skin tissue 28' indicated in Figure 3 b) occur when the body overproduces collagen, which causes the scar 28' to be raised above the surrounding skin 28. The swollen skin tissue 28' has risen to such a level above the surrounding skin 28 that the skin tissue 28' interferes with the coupling 30 and the sound processor (not shown) in the hearing aid device 2. Accordingly, the abutment 8 needs to be exchanged in order to make the hearing aid device 2 work properly. Figure 4 a) illustrates a schematic view of a bone anchored hearing aid abutment 8 surrounded by swollen skin tissue 28'. The skin tissue 28' is approximately twice as thick as the remaining portion of the skin 28. The abutment 8 is mechanically attached to an anchored fixture 4 provided with a threaded portion 6. The fixture 4 is anchored into the skull bone 26 of a user of a hearing aid. Figure 4 b) illustrates a schematic view of a thin extension member 10 according to the invention mounted on the bone anchored hearing aid abutment 8 shown in Figure 4 a). The extension member 10 has the same width, W, as the proximal portion of the abutment 8. Figure 4 c) illustrates a schematic view of a hearing aid device 2 mechanically attached to the bone anchored hearing aid abutment 8 shown in Figure 4 b) via a coupling 30. The coupling 30 is attached to the extension member 10 that is mechanically attached to the abutment 8. The abutment 8 is fixed to the anchored fixture 4 provided with a threaded portion 6. The fixture 4 is anchored into the skull bone 26. When the extension member 10 is attached to the abutment 8, the coupling 30 and thus the hearing aid device 2 is displaced along the longitudinal axis X of the abutment 8. Thus, a gap 32 is provided between the skin tissue 28' and the coupling 30. Hereby, the swollen or swollen skin tissue 28' will not interfere with the coupling 30 or the processor in the hearing aid device 2. Accordingly, the extension member 10 makes it possible to keep applying the hearing aid device 2 and the existing abutment 8 despite the existence of the skin tissue 28'. Figure 5 a) illustrates a schematic view of a bone anchored hearing aid abutment 8 surrounded by a swollen or swollen skin tissue 28'. The swollen skin tissue 28' in fig. 5 is thicker than the swollen skin tissue 28' shown in Figure 4. The abutment 8 is mechanically attached to an anchored fixture 4 provided with a threaded portion 6. The fixture 4 is anchored into the skull bone 26 of a user of a hearing aid. Figure 5 b) illustrates a schematic view of a thick extension member 10 according to the invention. The extension member 10 is mounted on the bone anchored hearing aid abutment 8 shown in Figure 5 a). The extension member 10 has the same width, W, as the proximal portion of the abutment 8. Figure 5 c) illustrates a schematic view of a hearing aid device 2 that is mechanically fixed to the abutment 8 shown in Figure 5 b) via a coupling 30. The coupling 30 is fixed to the extension member 10. The extension member 10 is mechanically attached to the abutment 8. The abutment 8 is fixed to the anchored fixture 4 provided with a threaded portion 6 and is anchored into the skull bone 26. Attaching the extension member 10 to the abutment 8 causes a displacement of the coupling 30. Thus, the hearing aid device 2 is moved along the longitudinal axis X of the abutment 8 and a gap 32 is established between the thickened skin tissue 28' and the coupling 30. Therefore, the thickened skin tissue 28' will not interfere with the coupling 30 or the processor in the hearing aid device 2. By using an extension member 10 according to the invention it is possible to keep applying the hearing aid device 2 and the existing abutment 8 despite the existence of thickened or swollen skin tissue 28'. The thickness of the extension member 10 may depend on the specific requirements. The thickness of the extension member 10 may by 1 mm or more, e.g. 2 mm by way of example. Figure 6 a) illustrates a schematic view of a hearing aid interconnection system 34 comprising a prior art bone anchored hearing aid abutment 8 surrounded by swollen skin tissue 28'. The thickness of the thickened skin tissue 28' exceeds the thickness of the remaining skin 28. The thickness of the thickened skin tissue 28' also exceeds the length L _1 of the abutment 8. The abutment 8 is attached to a fixture 4 provided with threads 6 and anchored to the skull bone 26 of a user of a hearing aid. The swollen or thickened skin tissue 28' surrounding the abutment 8 is in physical contact with the hearing aid device 2. Thus, there is a risk that the hearing aid device 2 will not function properly due to the presence of the swollen skin tissue 28'. In such a case the abutment 8 would be exchanged with a larger one. Replacement of an abutment 8 may require anaesthetic treatment and may introduce risk of damaging the internal thread of the external hexagon of the fixture 4. If the internal thread of the external hexagon of the fixture 4 is damaged a new surgery procedure is required in order to replace the damaged fixture 4. Figure 6 b) illustrates a schematic view of a hearing aid interconnection system 34 comprising an extension member 10 according to the invention. The extension member 10 is mounted on a bone anchored hearing aid abutment 8 that is surrounded by thickened skin tissue 28' corresponding to the one shown in Figure 6 a ). The extension member 10 is mechanically attached to the abutment 8 and the abutment 8 is fixed to an anchored fixture 4 provided with a threaded portion 6 and is anchored into the skull bone 26. When the extension member 10 is attached to the abutment 8 the coupling 30 is displaced a distance, D, along the longitudinal axis X of the abutment 8. Thus, a gap 32 is established between the thickened skin tissue 28' and the hearing aid device 2. The length of the abutment 8 and the attached extension member 10 is L _2, while the length of the abutment 8 is L _1. It can be seen that the difference between the length, L _2, of the abutment 8 with the attached extension member 10 and the length, L _1, of the abutment 8 is given by: [MATHS id=math0001] where D is the distance that the extension member 10 adds to the length of the abutment 8 along the longitudinal axis X of the abutment 8. Therefore, the thickened skin tissue 28' will not interfere with the hearing aid device 2. By using an extension member 10 according to the invention it is possible to keep using the hearing aid device 2 and the existing abutment 8 despite the existence of thickened skin tissue 28'. The thickness of the extension member 10 may depend on the specific requirements. The thickness of the extension member 10 may by 1 mm or more, e.g. 2 mm by way of example so that the distance D that the extension member 10 extends the abutment 8 along the longitudinal axis X of the abutment 8 is 1 mm or more.

1. A hearing aid interconnection system (34) comprising an abutment (8) having a fixture end and a hearing aid attachment end, where the fixture end is attachable to a bone integrated fixture (4) thereby anchoring the hearing aid interconnection system (34) to a skull bone (26), where the hearing aid attachment end of the abutment comprises hearing aid coupling surfaces adapted for engagement with a hearing aid coupling, characterised in that the hearing aid interconnection system (34) comprises an extension member (10) attachable to the abutment (8) at the hearing aid attachment end where the extension member further comprises hearing aid coupling surfaces, whereby the extension member (10) allows an extension of the length (L_1) between the fixture and the hearing aid coupling.

2. A hearing aid interconnection system (34) according to claim 1, characterised in that the extension member (10) is movably mounted to the abutment (8) via a head of a connection screw (12) which passes through a through going hole (36) in the abutment and into the fixture (4). 3. A hearing aid interconnection system (34) according to claim 1, characterised in that the hearing aid coupling surfaces of the extension member differs from the hearing aid coupling surfaces of the abutment. 4. A hearing aid interconnection system (34) according to claim 1, characterised in that the hearing aid coupling surfaces of the extension member are functionally identical to the coupling surfaces of the abutment. 5. A hearing aid interconnection system (34) according to claim 1, characterised in that a tool grip structure (24) is provided in the extension member (10). 6. A hearing aid interconnection system (34) according to claim 5, characterised in that the extension member (10) is a one-piece body with the hearing aid coupling surfaces at one part thereof and with abutment connection parts, movably connecting the extension member (10) to the head of connection screw (12), at another part thereof. 7. A hearing aid interconnection system (34) according claim 2, characterised in that the extension member (10) comprises a coupling part (10') with hearing aid coupling surfaces and a fixation part (10") movably mounted to the abutment (8) and fixating the coupling part (10') to the abutment (8) via the head of connection screw (12). 8. A hearing aid interconnection system (34) according to claim 7, characterised in that a tool grip structure (24) is provided in the movable fixation part (10") of the extension member (10). 9. A hearing aid interconnection system (34) according to one of the preceding claims, characterised in that the hearing aid coupling surfaces of the extension member (10) are arranged for being detachably gripped by gripping jaws (30') belonging to a hearing aid device (2). 10. A hearing aid interconnection system (34) according to one of the preceding claims, characterised in that the hearing aid coupling surfaces of the extension member (10) are permanently joined to a hearing aid device (2) output vibration member. 11. A hearing aid interconnection system (34) according to one of the preceding claims, characterised in that the extension member (10) has essentially the same width (W) as the top portion of the abutment (8). 12. A hearing aid interconnection system (34) according to one of the preceding claims, characterised in that the extension member (10) extends along the longitudinal axis (X) of the abutment (8) and that the extension member (10) comprises an abutment contact surface (18) which sealingly matches a corresponding contact surface (20) of the top portion of the abutment (8). 13. A hearing aid interconnection system (34) according to one of the preceding claims, characterised in that the extension member (10) extends the abutment (8) with a distance (D) which is at least 1 mm.

2876020

Backing device, axlebox, vehicle and methods for mounting and dismounting such a backing device

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a bogie 2, partly represented for simplification purpose, belonging to a railway vehicle 1. Bogie 2 comprises a frame 3, two wheelset 4 and four axleboxes 9. Only one wheelset 4 and one axlebox 9 are shown on figure 1 for simplification purpose. Wheelset 4 comprises two wheels 5 supported by an axle 6, which is hidden by frame 3 and one of the wheels 5. Axlebox 9 is mounted on the outer side of the wheel 5 and secured to frame 3. Figure 1 explains the context of the application but does not show the invention. Figure 2 shows a wheelset 4, a wheel 5, an axle 6 and suspension systems 7, together with an axlebox 10 according to the invention. Thus, axlebox 10 is different from axlebox 9 shown on figure 1. Suspension systems 7 connect axlebox 10 to the frame, not shown, of a vehicle which is also according to the invention. Axlebox 10 is mounted on axle 6 on the inner side of the wheel 5. Axlebox 10 supports axle 6, which supports wheels 5. Wheels 5, axle 6 and axlebox box 10 are centered on a central axis X10. Figures 3 to 6 show axlebox 10, which comprises a housing 20, a bearing unit 30 and a backing device 40 according to the invention. Housing 20 comprises an upper part 21 and a lower part 22. Housing 20 defines a cavity 23 receiving bearing unit 30 and a cavity 24 receiving backing device 40. Cavities 23 and 24 are centered on axis X10. Axlebox 10 comprises bolts 26 for fastening parts 21 and 22 together, once bearing unit 30 is mounted inside cavity 23. Bearing unit 30 comprises two rolling bearings 31 and 32 mounted against each other on axle 6. Bearings 31 and 32 are centered on axis X10. Each bearing 31 and 32 comprises an inner ring 33 mounted on axle 6, an outer ring 34 fitted in cavity 23 of housing 20, and rolling elements 35 mounted between inner ring 33 and outer ring 34. Alternatively, bearing unit 30 may comprise a single bearing 31 or 32, of any type adapted to the present application. Backing device 40 is mounted on axle 6 and inside cavity 24 next to bearing unit 30 to prevent movement of bearing unit 30 along axle 6. Backing device 40 has an annular shape, as shown on figure 6. In other words, backing device 40 forms a backing device for bearing unit 30. Backing device 40 comprises an inner ring 50, an outer ring 60 and tightening means 80. Rings 50 and 60 are centered on axis X10. Inner ring 50 has a cylindrical inner surface 51, a frustoconical outer surface 52 and two lateral surfaces 54 and 55. Lateral surface 55 is positioned in contact with an inner ring 33 of bearing unit 30, while lateral surface 54 is preferably positioned in contact with an abutment 6A formed on axle 6. Abutment 6A has an annular shape centered on axis X10. Diameter of abutment 6A is reduced in comparison with known wheelsets provided with a backing device. Moreover, abutment 6A is optional. Inner ring 50 also has a flange 56 extending radially to axis X10, from between outer surface 52 and lateral surface 55. Flange 56 is traversed from side to side by twelve threaded bores 58 regularly distributed around axis X10, each bore 58 extending along a direction parallel to axis X10. Outer ring 60 has a cylindrical outer surface 61, a frustoconical inner surface 62 and two lateral surfaces 64 and 65. Inner surface 62 of outer ring 60 is positioned against surface 52 of inner ring 50. Outer ring 60 is traversed from side to side, between lateral surfaces 64 and 65, by twelve cylindrical bores 68 regularly distributed around axis X10, each bore 68 extending along a direction parallel to axis X10. The tightening means 80 comprise twelve screws 81 positioned in bores 58 and 68, aligned to receive the screws 81. Each screw 81 comprises a head 82 and a body 83 having a threaded end portion 84. Head 82 is positioned against surface 64 of ring 60, body 83 extends through bore 68 and threaded portion 84 is inserted in threaded bore 58. When actuated by tightening the screws 81, the tightening means 80 press surface 62 of ring 60 against surface 52 of ring 50. Ring 50 is compressed and elastically deformed between axle 6, ring 31 of bearing unit 30 and outer ring 60. In particular, surface 51 of ring 50 is narrowed or tightened around axle 6. Thus, a rigid connection is formed between axle 6 and backing device 40. Thanks to the invention, backing device 40 can be quickly and easily mounted on the axle or dismounted from the axle. In practice, backing device 40 comprises selflocking means. More precisely, backing device 40 comprises means 52, 58, 62, 64, 68, 80 for narrowing inner surface 51 of ring 50 on axle 6. Sealing means, not shown, are preferably provided between backing device 40 and housing 20, more precisely between flange 56 and cavity 24. For example, such sealing means may comprise a rubber seal, a felt strip or any other dynamic seal adapted to the present application. The invention also concerns a method for mounting backing device 40 on axle 6 and a method for dismounting backing device 40 from axle 6. The mounting method comprises a step a) of positioning backing device 40 on axle 6, in particular next to bearing unit 30, then a step b1) of tightening the screws 81, so that inner surface 62 of ring 60 and outer surface 52 of ring 50 are pressed against each other and that inner surface 51 of ring 50 is narrowed around axle 6. The dismounting method comprises a step c1) of loosening the screws 81, so that the pressure between inner surface 62 of ring 60 and outer surface 52 of ring 50 is released and that inner surface 51 of ring 50 expands around axle 6, then a step d) of removing backing unit 10 from axle 6. Thus, backing device 40 and axlebox 10 can be quickly and easily mounted or dismounted from axle 6. Figures 7 and 8 show a second embodiment of the invention. Elements similar to the first embodiment have the same references, while elements different from the first embodiment have references augmented by 100 and are described hereafter. The mounting and dismounting methods described here-above for the first embodiment also apply to the second embodiment. In the second embodiment, bearing device 40 comprises an inner ring 150, two outer rings 160 and 170, tightening means 180 and sealing means 190. Inner ring 150 has two frustoconical outer surfaces 152 and 153. Outer rings 160 and 170 each have a frustoconical inner surface, respectively 162 and 172, which form an obtuse angle facing inner ring 150. Inner surfaces 162 and 172 are positioned against surfaces 152 and 153, respectively. The sealing means 190 comprise a labyrinth 192 defined between cavity 124 of housing 20 and outer rings 160 and 170, in order to provide dynamic sealing and avoid intrusion of external elements inside the axlebox. The tightening means 180 comprise twelve screws 181, each extending through a hole 178 formed in outer ring 170 and having a threaded portion 184 inserted in a threaded bore 168 formed in outer ring 160. When actuated by tightening the screws 181, the tightening means 180 press surface 162 against surface 152 and surface 163 against surface 153. Ring 150 is compressed and elastically deformed between axle 6, ring 31 of bearing unit 30, outer rings 160 and 170. In particular, surface 51 of ring 150 is narrowed or tightened around axle 6. Thus, a rigid connection is formed between axle 6 and backing device 40. Figure 9 shows a third embodiment of the invention. Elements similar to the first embodiment have the same references, while elements different from the first embodiment have references augmented by 200 and are described hereafter. In the third embodiment, bearing device 40 comprises an inner ring 250, an outer ring 260 and tightening means 280. Inner ring 250 comprises a cylindrical outer surface 252, while outer ring 262 comprises a cylindrical inner surface 262. The tightening means 280 comprise one or several cavities 281 formed inside inner ring 250, distributed around axis X10. For each cavity 281, the tightening means 280 also comprise a valve 282 inserted inside the inner ring 250, in fluid communication with the cavity 281. A fluid flow is represented by an arrow F1 on figure 9. When actuated by filling the cavity or cavities 281 with pressurized fluid F1, each cavity 281 is expanded, the tightening means 280 press outer surface 252 and inner surface 262 against each other and narrow inner surface 51 of inner ring 250 by elastic deformation thereof. Fluid F1 is preferably a hydraulic fluid. For the embodiment of figure 9, the mounting method comprises a step b2) of filling the cavity or cavities 281 with fluid F1, so that each cavity is expanded, that outer surface 252 and inner surface 262 are pressed against each other and that inner surface 51 of inner ring 250 is narrowed around axle 6. The dismounting method comprises a step c2) of draining fluid F1 out the cavity or cavities 281, so that each cavity 281 shrinks and retrieves its initial volume, that the pressure between inner surface 262 and outer surface 252 is released and that inner surface 51 of ring 250 expands around axle 6. Thus, backing device 40 and axlebox 10 can be quickly and easily mounted or dismounted from axle 6. Whatever the embodiment, the backing device 40 comprises: an inner ring 50, 150, 250 having an inner surface 51 and at least one outer surface 52, 152, 153, 252 ; at least one outer ring 60, 160, 170, 260 having an inner surface 62, 162, 172, 262 facing the outer surface 52, 152, 153, 252 of the inner ring 50, 150, 250 ; and tightening means 80, 180, 280 inserted inside the inner ring and/or the outer ring and which, when actuated, press the inner surface 62, 162, 172, 262 of the outer ring 60, 160, 170, 260 and the outer surface 52, 152, 153, 252 of the inner ring 50, 150, 250 against each other and narrow the inner surface 51 of the inner ring 50, 150, 250 by elastic deformation thereof. Other non-shown embodiments of axlebox 10 and/or bearing device 40 can be implemented within the scope of the invention. In particular, axlebox housing 20, bearing unit 30, inner ring 50, 150, 250, outer ring(s) 60, 160, 170, 260, tightening means 80, 180, 280 and sealing means 190 may have different configurations. In addition, technical features of the different embodiments can be, in whole or part, combined with each other. Thus, axlebox 10 and backing device 40 can be adapted to the specific requirements of the application.

1. A backing device (40), adapted to equip an axlebox (10) comprising a bearing unit (30) and supporting an axle (6), wherein the backing device (40) comprises: - an inner ring (50 ; 150 ; 250) having an inner surface (51) and at least one outer surface (52 ; 152, 153 ; 252) ; - at least one outer ring (60 ; 160, 170 ; 260) having an inner surface (62 ; 162, 172 ; 262) facing the outer surface (52 ; 152, 153 ; 252) of the inner ring (50 ; 150 ; 250) ; and - tightening means (80 ; 180 ; 280) inserted inside the inner ring (50 ; 150 ; 250) and/or the outer ring (60 ; 160, 170 ; 260) and which, when actuated, press the inner surface (62 ; 162, 172 ; 262) of the outer ring (60 ; 160, 170 ; 260) and the outer surface (52 ; 152, 153 ; 252) of the inner ring (50 ; 150 ; 250) against each other and narrow the inner surface (51) of the inner ring (50 ; 150 ; 250) by elastic deformation thereof.

2. Backing device (40) according to claim 1, wherein: - the inner ring (50 ; 150) has at least one frustoconical outer surface (52 ; 152, 153) ; - the outer ring (60 ; 160, 170) has a frustoconical inner surface (62 ; 162, 172) ; and - the tightening means (80 ; 180) are inserted inside both the inner ring (50 ; 150) and the outer ring (60 ; 160, 170) and, when actuated, press the frustoconical inner surface (62 ; 162, 172) of the outer ring (60 ; 160, 170) against the frustoconical outer surface (52 ; 152, 153) of the inner ring (50 ; 150) and narrow the inner surface (51) of the inner ring (50 ; 150) by elastic deformation thereof. 3. Backing device (40) according to claim 2, wherein the tightening means (80) comprise at least one screw (81) which extends through a hole (68) formed in a first ring among the inner ring (50) and the outer ring (60) and which has a threaded portion (84) inserted in a threaded bore (58) formed in a second ring among the inner ring (50) and the outer ring (60) ; and wherein the tightening means (180) are actuated by tightening the screw or screws (181). 4. Backing device (40) according to claim 1, wherein: - the inner ring (150) has two frustoconical outer surfaces (152, 153) ; - the backing device (40) comprises two outer rings (160, 170) each having a frustoconical inner surface (162, 172) ; and - the tightening means (180) are inserted inside the two outer rings (160, 170) and, when actuated, press the frustoconical inner surfaces (162, 172) of the outer rings (160, 170) against the frustoconical outer surfaces (152, 153) of the inner ring (150) and narrow the inner surface (51) of the inner ring (150) by elastic deformation thereof. 5. Backing device (40) according to claim 4, wherein the two frustoconical inner surfaces (162, 172) form an obtuse angle (β) facing the inner ring (150) ; wherein the tightening means (180) comprise at least one screw (181) which extends through a hole (178) formed in a first ring among the two outer rings (160, 170) and which has a threaded portion (184) inserted in a threaded bore (168) formed in a second ring among the two outer rings (160, 170) ; and wherein the tightening means (180) are actuated by tightening the screw or screws (181). 6. Backing device (40) according to claim 1, wherein the tightening means (280) comprise at least one cavity (281) formed inside the inner ring (250) and a valve (282) inserted inside the inner ring (250) in fluid communication with the cavity (281); and wherein the tightening means (280), when actuated by filling the cavity or cavities (281) with a fluid (F1), press the outer surface (252) of the inner ring (250) and the inner surface (262) of the outer ring (260) against each other and narrow the inner surface (51) of the inner ring (250) by elastic deformation thereof. 7. An axlebox (10), adapted to support an axle (6), wherein the axlebox (10) comprises a bearing unit (30) and a backing device (40) according to any one of the previous claims 1 to 6. 8. Axlebox (10) according to the previous claim 7, wherein the inner ring (50 ; 150 ; 250) of the backing device (40) has a lateral surface (55) in contact with an inner ring (33) of the bearing unit (30). 9. Axlebox (10) according to any one of the previous claims 7 or 8, wherein the inner ring (50 ; 150 ; 250) of the backing device (40) has a lateral surface (54) in contact with an abutment (6A) formed on the axle (6). 10. Axlebox (10) according to any one of the previous claims 7 to 9, comprising a housing (20) which defines a sealing labyrinth (192) with the backing device (40). 11. A vehicle (1), equipped with at least one axlebox (10) according to any one of the previous claims 7 to 10. 12. Method for mounting a backing device (40) on an axle (6), wherein the backing device (40) is according to any one of claims 1 to 6 and wherein the method comprises the following steps: a) positioning the backing device (40) on the axle (6), in particular next to the bearing unit (30) belonging to the axlebox (10) ; b) actuating the tightening means (80 ; 180 ; 280) to press the inner surface (62 ; 162, 172 ; 262) of the outer ring (60 ; 160, 170 ; 260) and the outer surface (52 ; 152, 153 ; 252) of the inner ring (50 ; 150 ; 250) against each other and to narrow the inner surface (51) of the inner ring (50 ; 150 ; 250) elastically deformed on the axle (6). 13. Method for mounting a backing device (40) on an axle (6), wherein the backing device (40) is according to any one of claims 3 or 5 and wherein the method comprises the following steps: a) positioning the backing device (40) on the axle (6) ; b1) tightening the screw or screws (81 ; 181) to press the inner surface (62 ; 162, 172) of the outer ring (60 ; 160, 170) and the outer surface (52 ; 152, 153) of the inner ring (50 ; 150 ; 250) against each other and to narrow the inner surface (51) of the inner ring (50 ; 150) elastically deformed on the axle (6). 14. Method for mounting a backing device (40) on an axle (6), wherein the backing device (40) is according to claim 6 and wherein the method comprises the following steps: a) positioning the backing device (40) on the axle (6) ; b2) filling the cavity or cavities (281) with a fluid (F1) to press the outer surface (252) of the inner ring (250) and the inner surface (262) of the outer ring (260) against each other and to narrow the inner surface (51) of the inner ring (250) elastically deformed on the axle (6). 15. Method for dismounting a backing device (40) from an axle (6), wherein the backing device (40) is according to any one of the previous claims 1 to 6 and wherein the method comprises the following steps: c) loosening the tightening means (80 ; 180 ; 280) to release the pressure between the inner surface (62 ; 162 ; 262) of the outer ring (60 ; 160 ; 260) and the outer surface (52 ; 152, 153 ; 252) of the inner ring (50 ; 150 ; 250) and to expand the inner surface (51) of the inner ring (50 ; 150 ; 250) elastically deformed around the axle (6) ; d) removing the backing device (40) from the axle (6).

2878980

Device for aligning and fastening an optical fiber coupled to an opto-electronic component

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 depicts a first not limited embodiment of a device 1 for aligning the optical axis 2 of an optical fiber 3 with the optical axis 4 of an opto-electronic component 5 and for fastening the optical fiber 3 in the resulting relative position in relation to the opto-electronic component 5. The device 1 comprises a base 6 construed and arranged to support a first framework 7. In this not limited example, the base 6 comprises a mount 8 arranged and construed to support the opto-electronic component 5. The first framework 7 is disposed onto the base 6 and comprises a bore 9 having a longitudinal axis 10 sensibly coaxial to the optical axis 4 of the opto-electronic component 5. The coaxiality between the bore axis 10 and the optical axis 4 of the opto-electronic component 5 being obtained, using of a microscope, during the positioning and fastening of the framework 7 onto the base 6. The first framework 7 may be fixed with the base 6 by welding. In a not limited embodiment, the first framework 7 is rigid, for example the material of the first framework 7 is aluminia. For example, the framework thickness T7 is 1 mm. The first framework 7 further comprises at least a tank 11 construed and arranged to contain solidifiable fastening means 12. In the not limited example illustrated in figure 1, the tank 11 is cylindrical and presents four lugs. These lugs participate to the maintaining of the solidifiable fastening means 12. The tank is not limited to this example and may presenting other shape. However, the determined shape must permit to contain and maintain the solidifiable fastening means 12. In a not limited embodiment, solidifiable fastening means 12 are formed by melted soft solder or polymerizing glue. The first framework 7 also comprises a duct 13 connected at a first end to the tank 11 and at a second end to the bore 9 so that solidifiable fastening means 12 migrate from the tank 11 to the bore 9 by capillarity action. In order to realize the capillarity action, the duct diameter is smaller than the bore diameter. For example, the duct diameter is comprised between 70 µm and 130 µm. Thus, when the optical fiber 3 is positioned into the bore 9, the position of the optical fiber 3 is adjusted in all directions 14 until the maximum transferred signal is obtained, i.e. the longitudinal axis 2 of the optical fiber 3 is aligned with the optical axis 4 of the opto-electronic component 5 to be coaxial. This alignment may be adjusted by microscope or dynamically by moving the optical fiber 3 with a micromanipulator while the opto-electronic component 5 is operating. Then, when the position of the optical fiber 3 wherein the maximum transferred signal is obtained is determined, the solidifiable fastening means 12 migrate from the tank 11 to the bore 9 by capillarity action. In a not limited embodiment, the bore 9 is cylindrical and the diameter of the bore 9 is 20 µm up 60 µm higher than the diameter of optical fiber 3. This dimension difference between the optical fiber diameter and the bore diameter allows a homogeneous repartition of the solidifying fastening means 12 around the optical fiber 3. Thus, during the migration of the fastening means 12, the position of the optical fiber 3 is not modified and the position wherein the maximum transferred signal is obtained is conserved. Even if the optical fiber 3 is slightly moved, as the fastening means 12 are not solidified yet, the position of the optical fiber 3 can be adjusted. Then, the solidifying fastening means 12 are solidified by U.V. exposure or heating. During the solidification, forces of contraction of the fastening means 12 are symmetric so that the optical fiber 3 does not move and the position is conserved. The forces are symmetric because the optical fiber 3 is 360 degree surrounded by the solidifiable fastening means 12. Thus, the optical fiber position wherein the maximum transferred signal is obtained is conserved. Figure 2 depicts a second not limited embodiment of a device 1 for aligning the optical axis 2 of an optical fiber 3 with the optical axis 4 of an opto-electronic component 5 and for fastening the optical fiber 3 in the resulting relative position in relation to the opto-electronic component 5. In this second embodiment, the base 6 comprises a first groove 15 arranged and construed to receive and position the first framework 7 so that the bore axis 10 is sensibly coaxial with the optical axis 4 of the opto-electronic component 5. The groove 15 is for example perpendicular to the optical axis 4. In order to position the first framework 7 correctly, the first framework 7 is slided into the groove 15 until that the bore axis 10 is coaxial with the optical axis 4 of the opto-electronic component. In a not limited embodiment, the first framework position is fixed by welding or gluing 16. Figure 3 depicts a third not limited embodiment of a device 1 for aligning the optical axis 2 of an optical fiber 3 with the optical axis 4 of an opto-electronic component 5 and for fastening the optical fiber 3 in the resulting relative position in relation to the opto-electronic component 5. In this third embodiment, the device 1 further comprises a second framework 17 disposed onto the base 6. The second framework 17 comprises a bore 18 having a longitudinal axis 19 sensibly coaxial with the optical axis 4 of the opto-electronic component 4. The coaxiality between the longitudinal bore axis 19 and the optical axis 4 of the opto-electronic component 5 being obtained by using of a microscope. The bore 18 is construed and arranged to receive the optical fiber 3. It could be noted that the bore diameter is 20 µm up 60 µm higher than the optical fiber 3 diameter. This feature allows do not exert a mechanical stress on the optical fiber 3. The second framework 17 is disposed onto the base 6 and may be fixed with the base 6, for example, by welding or by gluing 20. In another embodiment not illustrated, the second framework 17 comprises a slot above the bore 18. This slot may be used to place solidifiable fastening means. Then, these solidifiable fastening means migrate by gravity for surround the optical fiber 3. In another embodiment not depicted, the base 6 comprises a second groove arranged and construed to receive and position the second framework 17 so that the longitudinal bore axis19 is sensibly coaxial with the optical axis 4 of the opto-electronic component 5. The second groove is for example perpendicular to the optical axis 4. In order to position the second framework 17 correctly, the second framework 17 is slided into the second groove until that the longitudinal bore axis 19 is coaxial with the optical axis 4. In a not limited embodiment, the second framework position is fixed into the groove non depicted, by welding or gluing. In a not limited embodiment, the thickness T7 of the first framework 7 and the thickness T17 of the second framework 17 are each of them comprised between 100 µm and 300 µm, for example 127 µm. In a general manner, it could be noted that when one uses only one framework as depicted in figure 1 the framework thickness is more important than when one uses two frameworks as depicted in figure 3.Figure 4 depicts a fourth not limited embodiment of a device 1 for aligning the optical axis 2 of an optical fiber 3 with the optical axis 4 of an opto-electronic component 5 and for fastening the optical fiber 3 in the resulting relative position in relation to the opto-electronic component 5. In this embodiment, the base 6 comprises a second groove 22 and the second framework 17 is located into the second groove 22. Furthermore, the second framework 17 is fixed to the base 6, for example, by gluing 23. Besides, in this not limited embodiment, the second framework 17 comprises a tank 24 construed and arranged to contain solidifiable fastening means 25. In a not limited example, solidifiable fastening means 25 are formed by melted soft solder or polymerizing glue. The second framework 17 also comprises a duct 26 connected at a first end to the tank 24 and at a second end to the bore 18 so that solidifiable fastening means 25 migrate from the tank 24 to the bore 18 by capillarity action. In order to facilitate the capillarity action, the duct diameter is smaller than the bore diameter. For example, the duct diameter is comprised between 70 µm and 130 µm. Figure 5 depicts a fifth not limited embodiment of a device 1 for aligning optical axis 2, 2' of two optical fibers 3, 3' with the two optical axis 4, 4' of a multichannel opto-electronic component 27 and for fastening each optical fiber 3, 3' in the resulting relative position in relation to the multichannel opto-electronic component 27. In this fifth not limited embodiment, the first framework 7 comprises two bores 9 9', a unique tank 11 and two ducts 13, 13'. The first bore 9 has a longitudinal axis 10 sensibly coaxial to the first optical axis 4 of the multichannel opto-electronic component 27. The second bore 9' has a longitudinal axis 10' sensibly coaxial to the second optical axis 4' of the multichannel opto-electronic component 27. The first duct 13 is connected at a first end to the tank 11 and at a second end to the first bore 9. The second duct 13' is connected at a first end to the tank 11 and at a second end to the second bore 9'. Futhermore, the second framework 17 comprises two bores 18, 18', a unique tank 24 and two ducts 26, 26'. The first bore 18 has a longitudinal axis 19 sensibly coaxial to the first optical axis 4 of the multichannel opto-electronic component 27. The second bore 18' has a longitudinal axis 19' sensibly coaxial to the second optical axis 4' of the multichannel opto-electronic component 27. The first duct 26 is connected at a first end to the tank 24 and at a second end to the first bore 18. The second duct 26' is connected at a first end to the tank 24 and at a second end to the second bore 18'. Figure 6 depicts a sixth not limited embodiment of a device 1 for aligning four optical axis 2, 2', 2", 2'" of four optical fibers 3, 3', 3", 3'" with the four optical axis 4, 4', 4", 4'" of a multichannel opto-electronic component 27 and for fastening the four optical fibers 3, 3', 3", 3'" in the resulting relative position in relation to the multichannel opto-electronic component 27. In this sixth not limited embodiment, the first framework 7 comprises a plurality of bores 9, 9', 9", 9"', a plurality of tank 11, 11', 11 ", 11'", and a plurality of duct 13, 13', 13", 13"', each bore 9, 9', 9", 9'" having a longitudinal axis 10, 10', 10", 10"' sensibly coaxial to one of the optical axis 4, 4', 4", 4'" of the multichannel opto-electronic component 26 and each duct 13, 13', 13", 13"' being connected at a first end to a tank 11, 11', 11 ", 11 "'and at a second end to a bore 9, 9', 9", 9'". In this embodiment, the second framework 17 comprises a plurality of bores 18, 18', 18", 18"', a plurality of tank 24, 24', 24", 24"', and a plurality of duct 26, 26', 26", 26"', each bore 18, 18', 18", 18"', having a longitudinal axis 19, 19', 19", 19"' sensibly coaxial to one of the optical axis 4, 4', 4", 4'" of the multichannel opto-electronic component 27 and each duct 26, 26', 26", 26"' being connected at a first end to a tank 24, 24', 24", 24"', and at a second end to a bore 18, 18', 18", 18"'. More particularly, the first framework 7 comprises four bores 9, 9', 9", 9"', four tanks 11, 11', 11 ", 11'" and four ducts 13, 13', 13", 13"'. The first bore 9 has a longitudinal axis 10 sensibly coaxial to the first optical axis 4 of the multichannel opto-electronic component 27. The second bore 9' has a longitudinal axis 10' sensibly coaxial to the second optical axis 4' of the multichannel opto-electronic component 27. The third bore 9" has a longitudinal axis 10" sensibly coaxial to the third optical axis 4" of the multichannel opto-electronic component 27. The fourth bore 9'" has a longitudinal axis 10'" sensibly coaxial to the fourth optical axis 4'" of the multichannel opto-electronic component 27. The first duct 13 is connected at a first end to the first tank 11 and at a second end to the first bore 9. The second duct 13' is connected at a first end to the second tank 11' and at a second end to the second bore 9'. The third duct 13" is connected at a first end to the third tank 11" and at a second end to the third bore 9. The fourth duct 13"' is connected at a first end to the fourth tank 11'" and at a second end to the fourth bore 9"'. Futhermore, the second framework 17 comprises four bores 18, 18', 18", 18"', four tanks 24, 24', 24", 24'" and four ducts 26, 26', 26", 26"'. The first bore 18 has a longitudinal axis 19 sensibly coaxial to the first optical axis 4 of the multichannel opto-electronic component 27. The second bore 18' has a longitudinal axis 19' sensibly coaxial to the second optical axis 4' of the multichannel opto-electronic component 27. The third bore 18" has a longitudinal axis 19" sensibly coaxial to the third optical axis 4" of the multichannel opto-electronic component 27. The fourth bore 18"' has a longitudinal axis 19"' sensibly coaxial to the fourth optical axis 4'" of the multichannel opto-electronic component 27. The first duct 26 is connected at a first end to the first tank 24 and at a second end to the first bore 18. The second duct 26' is connected at a first end to the second tank 24' and at a second end to the second bore 18'. The third duct 26" is connected at a first end to the third tank 24" and at a second end to the third bore 18. The fourth duct 26'" is connected at a first end to the fourth tank 24"' and at a second end to the fourth bore 18"'.

1. A device (1) for aligning the optical axis (2) of an optical fiber (3) with the optical axis (4) of an opto-electronic component (5) and for fastening the optical fiber (3) in the resulting relative position in relation to the opto-electronic component (5), said device (1) comprising: - an opto-electronic component (5) comprising an optical axis (4), - a base (6) construed and arranged to support a framework, - a first framework (7) disposed onto said base (6) comprising: - a bore (9) having a longitudinal axis (10) sensibly coaxial to the optical axis (4) of the opto-electronic component (5), said bore (9) being construed and arranged to receive an optical fiber (3), - a tank (11) construed and arranged to contain solidifiable fastening means (12), and - a duct (13) connected at a first end to said tank (11) and at a second end to said bore (9) so that solidifiable fastening means (12) are capable to migrate from the tank (11) to the bore (9) by capillarity action.

2. A device (1) according to claim 1, wherein the opto-electronic component is a multichannel opto-electronic component (27), the first framework (7) comprising a plurality of bores (9, 9', 9", 9"'), a plurality of tank (11, 11', 11", 11'"), and a plurality of duct (13, 13', 13", 13"'), each bore (9, 9', 9", 9"') having a longitudinal axis (10, 10', 10", 10"') sensibly coaxial to one of the optical axis (4, 4', 4", 4"') of the multichannel opto-electronic component (27) and each duct (13, 13', 13", 13"') being connected at a first end to a tank (11, 11', 11 ", 11'") and at a second end to a bore (9, 9', 9",9"'). 3. A device (1) according to the claim 1, further comprising a second framework (17) disposed onto said base (6) comprising a bore (18) having a longitudinal axis (19) sensibly coaxial to the optical axis (4) of the opto-electronic component (5), said bore (18) being construed and arranged to receive the optical fiber (3). 4. A device (1) according to claim 2 and 3, wherein the second framework (17) disposed onto said base (6) comprises a plurality of bores (18, 18', 18", 18"'), each bore (18, 18', 18", 18"') of said second framework (17) having a longitudinal axis (19, 19', 19", 19"') sensibly coaxial to one of the optical axis (4, 4', 4", 4"') of the multichannel opto-electronic component (27). 5. A device (1) according to the claim 4, wherein the second framework (17) disposed onto said base (6) comprises: - a plurality of tank (24, 24', 24", 24"') construed and arranged to contain solidifiable fastening means (25, 25', 25", 25'"), and - a plurality of duct (26, 26', 26", 26"'), each duct (26, 26', 26", 26"') of said second framework (17) being connected at a first end to a tank (24, 24', 24", 24"') and at a second end to a bore (18, 18', 18", 18"'). 6. A device (1) according to claim 3, wherein the second framework (17) comprises: - a tank (24) construed and arranged to contain solidifiable fastening means (25), and - a duct (26) connected at a first end to said tank (24) and at a second end to said bore (18) so that solidifiable fastening means (25) are capable to migrate from the tank (24) to the bore (18) by capillarity action. 7. A device (1) according to any of the claims 3 to 6, wherein the base (6) comprises a second groove (22) arranged and construed to received and position the second framework (17). 8. A device (1) according to any of the preceding claims, wherein the base (6) comprises a first groove (15) arranged and construed to receive and position the first framework (7). 9. A device (1) according to any one of the preceding claims, wherein the bore (9, 9', 9", 9"', 18, 18', 18", 18"') is cylindrical. 10. A device (1) according to claim 9, wherein the duct diameter is smaller than the bore diameter. 11. A device (1) according to any one of the claims 9 or 10, wherein the bore diameter is 20 µm up 60 µm higher than the optical fiber diameter received. 12. A device (1) according to any one of the preceding claims, wherein the duct diameter is comprised between µm and 130 µm. 13. A device (1) according to any one of the preceding claims, wherein solidifiable fastening means (12, 12', 12", 12"', 25, 25', 25", 25"') are melted soft solder or polymerizing glue. 14. A device (1) according to any one of the preceding claims, wherein the thickness (T7, T17) of the first and/or second framework is comprised between 100 µm and 300 µm. 15. A device (1) according to any one of the preceding claims, wherein the thickness (T7, T17) of the first and/or second framework is 127 µm.

2878250

Method of operating a water-circulating household appliance

Based on the following detailed description of an invention, generate the patent claims. There should be 9 claims in total. The first, independent claim is given and the remaining 8 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Aspects of the present invention will now be described more fully. Like numbers refer to like elements throughout. Well-known functions or constructions will not necessarily be described in detail for brevity and/or clarity. Figure 1 illustrates a water-circulating household appliance 2 according to embodiments. The water-circulating household appliance 2 is illustrated in the form of a dishwasher. The water-circulating household appliance 2 comprises an electric motor 4 and a washing liquid circuit 6. The electric motor 4 may be e.g. a brushless electric motor, a synchronous electric motor, or an asynchronous electric motor. The washing liquid circuit 6 comprising a pump 8 for circulating washing liquid through the washing liquid circuit 6. The pump 8 may be a centrifugal pump. In these embodiments the washing liquid circuit 6 further comprises conduits 10, rotating arms 12 provided with nozzles, and a trough 14. The pump 8 pumps the washing liquid to the rotating arms 12, wherein the washing liquid is distributed in a washing compartment 16. In the washing compartment 16 two trays 18 are provided for holding dishes to be washed. The washing liquid distributed in the washing compartment 16 is collected in the trough 14, from where it is led back to the pump 8. The electric motor 4 is arranged to drive the pump 8. The electric motor 4 has a first direction of rotation and a second direction of rotation. The pump 8 has a primary direction of rotation corresponding to the first direction of rotation of the electric motor 4. The pump 8 has a secondary, or opposite, direction of rotation corresponding to the second direction of rotation of the electric motor 4. A portion of the washing liquid circuit 6 is arranged in thermal communication with the electric motor 4. In these embodiments a housing of the pump 8 in the washing liquid circuit 6 is arranged in thermal communication when the electric motor 4. The water-circulating household appliance 2 is arranged to perform a method according to any one of the aspects and/or embodiments discussed herein. Inter alia, for this purpose the water-circulating household appliance 2 comprises a control unit 20. The control unit 20 is arranged to control at least one washing operation of the water-circulating household appliance 2, including control of the manner in which the electric motor 4 is driven. A user of the water-circulating household appliance 2 may select a washing program in the control unit 20 via a non-shown control panel. A washing program may comprise one or more different washing operations such as pre-rinsing, washing with detergent, and after-rinsing. A heating element for heating in the washing liquid may be omitted in the water-circulating household appliance 2 since a portion of the washing liquid circuit 6 is arranged in thermal communication with the electric motor 4 and the electric motor 4 is driven in accordance with aspects and/or embodiments of the method discussed herein. The water supplied to the water-circulating household appliance 2 may be warm water thus, requiring less heating than if cold water were to be supplied. Mentioned purely as an example, circulating the washing liquid through the water-circulating household appliance 2 may require 60 - 90 W of electrical power. In an ordinary electric motor as used in a water-circulating household appliance, the power consumption may be 200-300 W or more when the electric motor is driven in accordance with aspects and/or embodiments of the method discussed herein. The excess electric power will be transformed into heat in the windings of the electric motor and thus, will be utilized to heat the washing liquid. Of course a more powerful electric motor may be used to increase the electric power consumption and thus, to increase the heat available for heating the washing liquid. Figure 2 illustrates a method of operating a water-circulating household appliance. The water-circulating household appliance comprises an electric motor and a washing liquid circuit. The washing liquid circuit comprising a pump for circulating washing liquid through the washing liquid circuit. A portion of the washing liquid circuit is arranged in thermal communication with the electric motor. The electric motor has a first direction of rotation and a second direction of rotation and is arranged to drive the pump. The pump has a primary direction of rotation corresponding to the first direction of rotation of the electric motor. The water-circulating household appliance may be a water-circulating household appliance 2 as discussed in connection with Figure 1. The method comprises a step of driving 30 the electric motor, over a time period longer than 1 minute, with a higher electrical power input than required for circulating the washing liquid through the washing liquid circuit with the pump rotating in the primary direction of rotation. The step of driving 30 the electric motor may comprise a step of rotating 32 the electric motor in the second direction of rotation to rotate the pump in a direction opposite to the primary direction of rotation. The step of driving 30 the electric motor may comprise a step of causing 34 an excessive electrical loss in the electric motor exceeding a normal electrical loss in the electric motor associated with rotating the pump in the primary direction for circulating the washing liquid through the washing liquid circuit. The step of causing 34 the excessive electrical loss may comprise a step of repeatedly starting and stopping 36 the rotation of the electric motor a number of times during each of a number of consecutive 1 minute time periods. The step of causing 34 an excessive electrical loss may comprise a step of sending 38 a DC voltage into at least one set of windings of the electric motor. The step of causing 34 an excessive electrical loss may comprise a step of sending 40 an out of phase AC voltage through at least one set of windings of the electric motor. The method may comprise a step of measuring 42 a temperature of the washing liquid. In this manner it may be decided whether the washing liquid has reached a desired temperature and the electric motor may be driven with high efficiency again. The temperature of the washing liquid may be measured directly with a temperature sensor in the washing liquid, or indirectly on the outside of e.g. a conduit or a housing of the pump. The method may comprise a step of rotating 44 the electric motor in the first direction of rotation and rotating the pump in the primary direction of rotation. In this manner the washing liquid may be circulated in the water-circulating household appliance in an energy efficient manner once the washing liquid has reached a desired temperature. As used herein, the term "comprising" or "comprises" is open-ended, and includes one or more stated features, elements, steps, components or functions but does not preclude the presence or addition of one or more other features, elements, steps, components, functions or groups thereof.

1. A method of operating a water-circulating household appliance, the water-circulating household appliance comprising an electric motor and a washing liquid circuit, the washing liquid circuit comprising a pump for circulating washing liquid through the washing liquid circuit, a portion of the washing liquid circuit being arranged in thermal communication with the electric motor, wherein the electric motor has a first direction of rotation and a second direction of rotation and is arranged to drive the pump, and wherein the pump has a primary direction of rotation corresponding to the first direction of rotation of the electric motor, characterized in that the method comprises a step of driving (30) the electric motor, over a time period longer than 1 minute, with a higher electrical power input than required for circulating the washing liquid through the washing liquid circuit with the pump rotating in the primary direction of rotation.

2. The method according to claim 1, wherein the step of driving (30) the electric motor comprises a step of rotating (32) the electric motor in the second direction of rotation to rotate the pump in a direction opposite to the primary direction of rotation. 3. The method according to claim 1 or 2, wherein the step of driving (30) the electric motor comprises a step of causing (34) an excessive electrical loss in the electric motor exceeding a normal electrical loss in the electric motor associated with rotating the pump in the primary direction for circulating the washing liquid through the washing liquid circuit. 4. The method according to claim 3, wherein the step of causing (34) the excessive electrical loss comprises a step of repeatedly starting and stopping (36) the rotation of the electric motor a number of times during each of a number of consecutive 1 minute time periods. 5. The method according to claim 3, wherein the step of causing an excessive (34) electrical loss comprises a step of sending (38) a DC voltage into at least one set of windings of the electric motor. 6. The method according to claim 3, wherein the step of causing (34) the excessive electrical loss comprises a step of sending (40) an out of phase AC voltage through at least one set of windings of the electric motor. 7. The method according to any one of the preceding claims, comprising a step of measuring (42) a temperature of the washing liquid. 8. The method according to any one of the preceding claims, comprising a step of rotating (44) the electric motor in the first direction of rotation and rotating the pump in the primary direction of rotation. 9. A water-circulating household appliance (2) comprising an electric motor (4) and a washing liquid circuit (6), the washing liquid circuit (6) comprising a pump (8) driven by the electric motor (4) and arranged to circulate washing liquid through the washing liquid circuit (6), a portion of the washing liquid circuit (6) being arranged in thermal communication with the electric motor (4),: characterized in that the water-circulating household appliance (2) is arranged to perform the method according to any one of the preceding claims.

2879476

Electric apparatus

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 illustrates a partial cross section of an electric apparatus, and Figure 2 illustrates details of the electric apparatus in Figure 1. In the following it will by way of example be assumed that the electric apparatus 1 illustrated in Figures 1 and 2 is a motor drive, such as a frequency controller, controlling supply of electricity to an electric motor. It should, however, be observed that the invention may be implemented also in other electric apparatuses. Figure 1 is a partial cross section of the apparatus, where the front walls or doors have been removed to illustrate the inner parts of the apparatus. Also a section of the top left part of the lid and of the right side wall has been left out. Two of the circuit boards have been illustrated as transparent and provided with a hatching in order to clarify the location of the circuit boards and also to show components located behind them. Figure 2 does not illustrate the housing at all, but only inner components of the electric apparatus, which ordinarily are enclosed by the housing. The electric apparatus 1 comprises a fan 2 for generating a first airflow 3 through the electric apparatus 1. In the illustrated embodiment the fan is by way of example arranged at an inlet 22 in the bottom of the housing 19, though in praxis the fan 2 may be located within the housing at a distance from the inlet 22, or at the outlet 20 of the housing 19 for generating the first air flow 3 by sucking air out of the housing 19. Still it is possible that the fan is located at a distance from the housing 19, such as in an air conduit passing air towards the inlets of the housing or passing air away from the outlets of the housing. A first cooling element 4 in contact with primary electric component 5 is arranged in the first airflow 3. The primary electric component 5 may include a power module with semiconductors that generate a significant amount of heat during use, for instance. The primary electric component 5 may be directly mounted onto a first surface 14 of the first cooling element 4 with screws, for instance. A good thermal connection should be obtained between the primary electric component 5 and the first surface 14 of the first cooling element 4. This may be obtained with a thermal interface material. Heat received via the first surface 14 of the first cooling element 4 is dissipated into the first airflow 3 via fins 6 arranged on a second surface of the cooling element, which may be an opposite surface as compared to the first surface 14. The electric apparatus 1 also comprises a component space 7 containing a secondary electric component 8. In the illustrated example it is by way of example assumed that the component space contains four capacitors. One or more walls 9 separate the component space 7 from the first cooling element 4 such that the first airflow 3 is prevented from entering the component space 7. In the illustrated example the wall 9 is a circuit board, such as a PCB (printed circuit board) which may carry a plurality of electric components which are also located in the component space 7. Additionally, a second circuit board 10 is arranged in the component space in order to facilitate electrical connections to the secondary electric component 8. As the first airflow 3 generated by the fan 2 is prevented from reaching the component space dust and dirt is also prevented from reaching the component space 8 with the first airflow 3. In order to ensure cooling for the secondary electric component 8 the apparatus 1 comprises a second cooling element 11. The second cooling element has a first end 12 in the component space and a second end 13 which is located outside of the component space 7 and in the airflow 3 from the fan 2. The first end 12 is thermally connected to the secondary component 8 for receiving heat from the secondary component and for passing heat via the second end 13 to the first airflow 3. The thermal connection between the secondary electric component 8 and the first end 12 may be accomplished by arranging these parts close enough to each other such that they touch each other. A thermal interface material (TIM) may be used between the secondary electric component 8 and the first end 12 of the second cooling element to ensure a sufficient thermal connection. In order to efficiently dissipate heat from the second cooling element 11 to the first airflow 3, the second end 13 of the second cooling element 11 is preferably provided with fins. The second cooling element 11 may be implemented as a single solid part of a suitable metal material, such as aluminum, for instance, which passes heat from the secondary electric component 8 to the first airflow 3 by conducting the heat. Alternatively, the second cooling element 11 may contain one or more fluid channels passing fluid between the first end 12 and the second end 13. Such a solution may be obtained by including a heat pipe in the second electric element, or by designing a 2-phase cooling solution with the first end 12 as an evaporator evaporating a liquid and the second end 13 as a condenser condensing the fluid back to liquid before returning it to the first end 12. It is also possible to implement the second cooling element 11 such that the first end 12 and the second end 13 are manufactured as separate parts which are thermally and mechanically connected to each other. In order to avoid that heat from the primary electric component 5 or the first cooling element 4 reaches the second end 13 of the second cooling element 11, an insulating air gap 15 is preferably arranged between the second end 13 and the first cooling element 4. Due to production reasons it may be beneficial that the first cooling element 4 is mechanically attached to the second end 13 of the second cooling element 11. However, also in such a solution, the attachment is preferably implemented in such a way that as little heat as possible can be transferred from the first cooling element 4 to the second end 13 of the second cooling element 11. Though not necessary in all embodiments, the component space 7 may be provided with an inlet 17 in a lower part and an outlet 18 in an upper part of the component space 7. Air heated within the component space 7 is thereby allowed to exit the component space via the outlet 18 while substitute air from the surroundings may enter the components space via the inlet 17 to the component space 7. Such natural convection without use of a fan will generate a second airflow 21 passing through the component space. Natural convection refers to fluid (such as air) motion which is not generated by any external source (like a pump, fan, suction device, etc.) but only by density differences in the fluid occurring due to temperature differences, as heated air is lighter than cold air. The second airflow 21 is much weaker than the first airflow 3 generated by the fan 2, and the amount of dust and dirt entering the component space 7 due to the second airflow is therefore minimal. In order to increase the amount of heat which can be dissipated from the component space 7 with the second airflow, the first end 12 of the second cooling element 11 is preferably provided with fins located in the second air flow 21. If the secondary electric component 8 is a capacitor, such as an electrolytic capacitor, this capacitor and also other capacitors in the component space 7 are preferably arranged substantially perpendicularly to the second airflow 21 in the component space 7. This makes it possible to mechanically attach the capacitors in a very rigid and stable configuration, by attaching the first ends of the capacitors to the first end 12 of the second cooling element 11 and by attaching the second ends of the capacitors to the PCB 10 providing electrical connections to the capacitors. In such a position and with small mutual gaps allowing airflow between the capacitors, the capacitors are efficiently cooled by the second airflow 21 and blocking of the second airflow due to the location of the capacitors or the location of the circuit boards can be avoided. A motor drive with a power rating of 2.2 kW (400V) suitable for use in a surrounding with a temperature of about 50 °C can in practice be manufactured to be as small as 130 x 130 x 60 mm when constructed as previously explained. In the illustrated embodiment it has by way of example been assumed that the inlets 17 and 22 to the housing are located in the bottom of the housing and that the outlets 18 and 20 from the housing are located in the upper wall or roof of the housing. However, this is naturally only by way of example. In order to obtain a housing suitable for use in outside conditions or in particularly dirty conditions, for instance, it may be necessary to arrange the inlets and outlets in some other way. One alternative is to arrange a protective cap on top of the housing to prevent water (such as condensation water or dripping water, for instance) from reaching the outlet at the roof of the housing. In that case air flowing out via the outlets does not flow straight upwards from the outlet, but instead the protective cap may direct it sideways or even downwards on the outer side of the housing before the airflow is released to the surroundings. It is to be understood that the above description and the accompanying figures are only intended to illustrate the present invention. It will be obvious to a person skilled in the art that the invention can be varied and modified without departing from the scope of the invention.

1. An electric apparatus (1), comprising: an inlet (22) and an outlet (20) for passing a first airflow generated by a fan (2) through the apparatus, a first cooling element (4) for receiving heat generated by a primary electric component (5) and for dissipating heat into the first airflow (3), a component space (7) containing a secondary electric component (8), and a housing (19) enclosing the first cooling element (4), the secondary electric component (8) and the component space (7), c h a r a c t e r i z e d i n that one or more walls (9) separate the component space (7) containing the secondary electric component (8) from the first cooling element (4) for preventing the first airflow (3) from entering the component space (7), and the apparatus (1) comprises a second cooling element (11) having a first (12) end in the component space (7), which first end (12) is thermally connected to the secondary electric component (8) for receiving heat generated by the secondary electric component (8), and a second end (13) located outside of the component space (7) for dissipating heat received from the secondary electric component (8) to the first airflow (3).

2. The electric apparatus according to claim 1, wherein a lower part of the component space (7) is provided with an inlet (17) and an upper part of the component space is provided with an outlet (18) for allowing air heated within the component space (7) to flow out via the outlet (18) and to be replaced by air from outside of the housing (19) via the inlet (17) due to natural convection without use of a fan. 3. The electric apparatus according to claim 1 or 2, wherein the first end (12) of the second cooling element (11) is provided with fins, and the second end (13) of the second cooling element (11) is provided with fins. 4. The electric apparatus according to one of claims 1 to 3, wherein the second cooling element (11) comprises a flow channel passing fluid between the first and second end of the second cooling element. 5. The electric apparatus according to one of claims 1 to 4, wherein the second cooling element (11) consists of two separate parts which are thermally connected to each other for passing heat from the first end (12) of the second cooling element to the second end (13) of the second cooling element. 6. The electric apparatus according to one of claims 1 to 5, wherein at least one of the one or more walls (9) separating the component space (7) from the first cooling element (4) consists at least partly of a circuit board. 7. The electric apparatus according to one of claims 1 to 6, wherein the secondary electric component (8) is a capacitor arranged substantially perpendicularly to a second air flow (21) flowing from the inlet (17) of the component space (7) to the outlet (18) of the component space and with a first end attached to the first end (12) of the second cooling element (11) and with a second end attached to a printed circuit board (10) in the component space (7). 8. The electric apparatus according to one of claims 1 to 7, wherein the primary electric component (5) includes one or more semiconductor components attached to the first cooling element (4). 9. The electric apparatus according to one of claims 1 to 8, wherein the first cooling element (4) is separated from the second end (13) of the second cooling element (11) by an air gap (15). 10. The electric apparatus according to one of claims 1 to 9, wherein the electric apparatus (1) is a motor drive controlling supply of electricity to an electric motor.

2878870

Self-lockable opening and closing mechanism for vacuum cabin door

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to Figures 1-4, a self-lockable opening and closing mechanism for vacuum cabin door in accordance with the present invention is shown. As illustrated, the self-lockable opening and closing mechanism for vacuum cabin door comprises: - a frame 10 being a hollow member comprising a base portion 11, two side panels 12 respectively perpendicularly connected to two opposite ends of the base portion 11 in parallel and a top panel 13 connected between respective distal ends of the two side panels 12 opposite to the base portion 11; - a driving cylinder 20 prepared in the form of a pneumatic or hydraulic cylinder and mounted at the base portion 11 within the frame 10 and adapted to reciprocate a vertically extending driving shaft 21 thereof between a received position in the base portion 11 and an extended position toward the top panel 13; - a horizontal lever 30 connected to the distal end of the driving shaft 21 at right angles; - at least one, for example, two first bars 40 each having one end thereof pivotally connected to one end of the horizontal lever 30; - at least one, for example, two rotational levers 50 each comprising a first pivot hole 51, a second pivot hole 52 and a third pivot hole 53 respectively disposed at three corners of a triangular profile thereof and having the first pivot hole 51 thereof pivotally connected to an opposite end of one respective first bar 40; - at least one, for example, two adjustment blocks 60 respectively pivotally connected to the second pivot holes 52 of the two rotational levers 50; - at least one, for example, two adjustment screws 61 rotatably mounted in the top panel 13 and respectively threaded into the two adjustment blocks 60 in a parallel manner relative to the axis of the driving shaft 21 and rotatable to adjust the distance between the respective adjustment block 60 and the top panel 13; - at least one, for example, two second bars 70 each having one end thereof pivotally connected to the third pivot hole 53 of one respective rotational lever 50; - at least one, for example, two sliding blocks 80 respectively slidably mounted one respective sliding guide means, for example, linear guideway 81 at each of the side panels 12 within the frame 10 in a parallel manner relative to axis of the driving shaft 21 and respectively pivotally connected to respective opposite ends of the second bars 70; and - at least one, for example, two valve rods 90 each having one end thereof connected to one respective sliding block 80 and an opposite end thereof connected to a vacuum cabin door 100 for moving the vacuum cabin door 100 between an open position and a close position. The aforesaid horizontal lever 30, first bars 40, rotational levers 50, adjustment blocks 60, second bars 70, sliding blocks 80 and valve rods 90 form a linkage mechanism that is drivable by the driving shaft 21 of the driving cylinder 20 to move the vacuum cabin door 100 between the open position and the close position. Further, the vacuum cabin door 100 comprises a door frame 101 and a door panel 102. The door frame 101 is connected to one side of the base portion 11 of the frame 10 opposite to the driving cylinder 20, defining therein a sliding groove 103 in parallel to the axis of the driving shaft 21 and an opening 104 cut through the sliding groove 103. The valve rods 90 are inserted through the base portion 11 and connected to the door panel 102 so that the door panel 102 is movable by the valve rods 90 between the close position to seal the opening 104 and the open position to open the opening 104. When the rotational levers 50 and the second bars 70 are in the close position, the imaginary axis A extending through the second pivot hole 52 and third pivot hole 53 of each rotational lever 50 defines with the axis B of the respective second bar 70 a contained angle θ within the range of 170°∼190°. Preferably, when the rotational levers 50 and the second bars 70 are in the close position, the imaginary axis A extending through the second pivot hole 52 and third pivot hole 53 of each rotational lever 50 is in axial alignment with the axis B of the respective second bar 70 and in parallel to the axis of the driving cylinder 20. In the present preferred embodiment, one pair of first bars 40, one pair of rotational levers 50, one pair of adjustment blocks 60, one pair of second bars 70, one pair of sliding blocks 80 and one pair of valve rods 90 are provided and bilaterally arranged in a symmetric manner relative to the axis of the driving cylinder 20. After understanding the structural details of the self-lockable opening and closing mechanism for vacuum cabin door in accordance with the present invention, the operational principle of the present invention is outlined hereinafter: As shown in Figure 4 and Figure 5, when going to move the vacuum cabin door 100 to the open position, the driving shaft 21 of the driving cylinder 20 is extended out toward the top panel 13, and the valve rods 90 moves the door panel 102 along the sliding grooves 103 toward the base portion 11 via the linking action of the horizontal lever 30, first bars 40, rotational levers 50, adjustment blocks 60, second bars 70 and sliding blocks 80, thereby moving the door panel 102 to open the opening 104. On the contrary, as shown in Figure 6 and Figure 7, when going to move the vacuum cabin door 100 to the close position, the driving shaft 21 of the driving cylinder 20 is retracted toward the inside of the base portion 11 to move the horizontal lever 30 and the first bars 40. At this time, the first pivot hole 51 of each rotational lever 50 is driven by the respective first bar 40, causing the respective rotational lever 50 to turn about the axis of the pivot point between the second pivot hole 52 of the respective rotational lever 50 and the associating adjustment block 60 and to further force the associating second bar 70 and the associating sliding block 80 along the respective sliding guide means 81 toward the base portion 11. When each sliding block 80 is being moved toward the base portion 11, the valve rods 90 are forced by the sliding blocks 80 toward the door frame 101, thereby carrying the door panel 102 to seal the opening 104. When the driving cylinder 20 is driven to close the vacuum cabin door 100, the contained angle θ defined between the imaginary axis A that extends through the second pivot hole 52 and third pivot hole 53 of each rotational lever 50 and the axis B of the respective second bar 70 is within the range of 170°∼190°. Further, when the rotational levers 50 and the second bars 70 are in the close position, the imaginary axis A extending through the second pivot hole 52 and third pivot hole 53 of each rotational lever 50 is in axial alignment with the axis B of the respective second bar 70 and in parallel to the axis of the driving cylinder 20. Thus, if the door panel 102 of the vacuum cabin door 100 is forced by a reaction force or any other factor to move in the reverse direction at this time, the reaction force will be linearly transferred through the valve rods 90, the sliding blocks 80, the second bars 70, the rotational levers 50 and the adjustment blocks 60 to the top panel 13 of the frame 10, preventing the component parts and the vacuum cabin door 100 from working and assuring positive locking of the vacuum cabin door 100. Thus, the invention does not need an extra power to keep the driving cylinder 20 in the locking position. Even the driving cylinder 20 or the related piping leaks or lacks in strength, the vacuum cabin door 100 will neither become loose nor break the vacuum effect of the vacuum cabin.

1. A self-lockable opening and closing mechanism, comprising: a frame (10) being a hollow frame formed of a base portion (11), two side panels (12) and a top panel (13); a driving cylinder (20) mounted at said base portion (11) within said frame (10), said driving cylinder (20) comprising a reciprocatable driving shaft (21); a horizontal lever (30) fixedly connected to said driving shaft (21); at least one first bar (40) each having one end thereof pivotally connected to said horizontal lever (30); at least one rotational lever (50) each comprising a first pivot hole (51), a second pivot hole (52) and a third pivot hole (53) respectively located at three corners of a triangular profile thereof, the first pivot hole (51) of each said rotational lever (50) being pivotally connected to an opposite end of one respective said first bar (40); at least one adjustment block (60) respectively pivotally connected to the second pivot hole (52) of one respective said rotational lever (50); at least one second bar (70) each having one end thereof pivotally connected to the third pivot hole (53) of one respective said rotational lever (50); at least one sliding block (80) respectively slidably mounted at one respective said side panel (12) within said frame (10) and respectively pivotally connected to an opposite end of one respective said second bar (70); a vacuum cabin door (100); and at least one valve rod (90) each having one end thereof connected to one respective said sliding block (80) and an opposite end thereof connected to said vacuum cabin door (100) for moving said vacuum cabin door (100) between an open position and a close position.

2. The self-lockable opening and closing mechanism as claimed in claim 1, wherein said two side panels (12) of said frame (10) are respectively perpendicularly connected to two opposite ends of said base portion (11) in parallel; said top panel (13) of said frame (10) is connected between respective distal ends of said two side panels (12) opposite to said base portion (11). 3. The self-lockable opening and closing mechanism as claimed in claim 2, wherein said driving shaft (21) of said driving cylinder (2) is movable between a received position in said base portion (11) and an extended position toward said top panel (13). 4. The self-lockable opening and closing mechanism as claimed in claim 1, wherein when said at least one rotational lever (50) and said at least one second bar (70) are in said close position, the imaginary axis (A) extending through the second pivot hole (52) and third pivot hole (53) of each said rotational lever (50) and the axis (B) of the respective said second bar (70) define a contained angle (θ) within the range of 170°∼190°. 5. The self-lockable opening and closing mechanism as claimed in claim 1, wherein when said at least one rotational lever (50) and said at least one second bar (70) are in said close position, the imaginary axis (A) extending through the second pivot hole (52) and third pivot hole (53) of each said rotational lever (50) and the axis (B) of the respective said second bar (70) are kept in axial alignment and in a parallel relationship with the axis of said driving cylinder (20) 6. The self-lockable opening and closing mechanism as claimed in claim 1, further comprising at least one adjustment screw (61) rotatably mounted in said top panel (13) of said frame (10) and respectively threaded into one respective said adjustment block (60) in a parallel manner relative to the axis of said driving shaft (21) and rotatable to adjust the distance between one respective said adjustment block (60) and said top panel (13) of said frame (10). 7. The self-lockable opening and closing mechanism as claimed in claim 6, wherein each said adjustment screw (61) is mounted in said top panel (13) of said frame (10) to keep the axis thereof in parallel to the axis of said driving shaft (21). 8. The self-lockable opening and closing mechanism as claimed in claim 1, further comprising a sliding guide means (81) located at each said side panel (12) and extending in a parallel manner relative to the axis of said driving shaft (21) for guiding sliding movement of one respective said sliding block (80) along one respective said side panel (12) of said frame (10). 9. The self-lockable opening and closing mechanism as claimed in claim 8, wherein said sliding guide means (81) is a linear guideway. 10. The self-lockable opening and closing mechanism as claimed in claim 1, wherein said vacuum cabin door (100) comprises a door frame (101) and a door panel (102), said door frame (101) being connected to one side of said base portion (11) of said frame (10) opposite to said driving cylinder (20), said door frame (101) defining therein a sliding groove (103) in parallel to the axis (B) of said driving shaft (21) and an opening (104) cut through said sliding groove (103); said at least one valve rod (90) is connected with said door panel (102) and reciprocatable to move said door panel (102) between said close position to seal said opening (104) and said open position to open said opening (104).

2878383

A caulk gun and a coupling device for a caulk gun

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The following description is given by way of example only to illustrate embodiments of the invention. The terminology used is for illustrative purpose only, and is not intended to limit the scope or use of the invention, unless the text clearly and explicitly requires otherwise. In the following description, reference will be made to the term "caulk" such as caulk materials, caulk tubes and caulk guns, but it should be understood that the reference is intended to encompass caulk, adhesives or anything which is suitable to be delivered in a similar manner. Figure 1 illustrates a first embodiment of a caulk gun 10 as embodied in the present invention. The caulk gun 10 is used for dispensing caulk material from a caulk tube. The caulk gun 10 includes a body 12 having a handle 14 and an actuating mechanism 16 for actuating the dispensing of the caulk material from the caulk tube. The body may also include an opening 18 configured with a screw threaded portion for receiving, for example, a caulk tube carrier 20 having a corresponding threaded end portion as shown in Figure 2. The caulk tube carrier 20 is designed for carrying a caulk tube, and can be configured with a cap 22 to seal the caulk tube after use. As shown in Figures 3 and 4, the caulk gun 10 can also be coupled with a caulk tube receiving adaptor 30 for receiving a caulk tube 32 directly, without the need of loading the caulk tube into a caulk tube carrier. Structures of the caulk tube receiving adaptor 30 will be explained in further details in the later description. The caulk gun 10 also comprises a plunger 40 having an elongated plunger rod 42 slidably connected with the body 12 of the caulk gun 10. The relevant features of the plunger 40 are shown in Figure 5, in which the housing of the body 12 of the caulk gun 10 has been removed for clarity purpose. The plunger may also include a piston (not shown) connected to the end of the plunger rod 42 for pushing the end plate of the caulk tube so as to dispense the caulk material. Figure 5 shows the plunger 40 at an initial, un-actuated position, i.e. the plunger 42 has not proceeded forward along the direction as indicated by the arrow in the figure to apply pressure onto the caulk tube (as shown by the phantom lines). When the actuating mechanism 16 is actuated, the plunger 40 will proceed to move in a direction away from the body 12 as indicated by the arrow in the figure. Specifically, the plunger rod 42 is slidably engaged with a stopping member 44, which is pivotally movable between a first position and a second position. The stopping member 44 is pivoted about a shaft 46 connected with a part of the housing (not shown) of the body 12, and its movement between the first and the second positions are biased by a spring 48. When the actuating mechanism 16 is actuated, and that the plunger 40 is moving away from the body towards the end plate of the caulk tube, the stopping member 44 is adapted to stop the movement of the plunger 40 at two predetermined distances: when the stopping member 44 is at the first position, forward movement of the plunger 40 will be prevented after the plunger 40 has been proceeding for a distance a as shown in the figure; and when the stopping member 44 is at the second position, movement of the plunger 40 will be prevented after the plunger 40 has been proceeding for a distance b as shown in the figure. Figure 5 shows the stopping member 44 at the first position. Movement of the stopping member 44 from the first position to the second position is triggered by the insertion of the caulk tube (when the adaptor 30 has been used) or the caulk tube carrier into the gun body 12, with their end portion pushes onto an arm 45 of the stopping member 44. For example, when a caulk tube is inserted at the caulk gun 10 via the adaptor 30, due to the defined length of a standard caulk tube, the stopping member 44 will not be disturbed by the end of the caulk tube and thus allowed at the first position. During operation of the caulk gun 10, the plunger 40 will continue to move towards the caulk tube so as to to apply pressure to dispense the content of the caulk material out of the caulk tube, until the plunger 40 has proceeded for the distance a, and then further movement of the plunger 40 will be prevented. For a caulk tube which is of a length longer than the standard caulk tube, the stopping member 44 will be pushed by the extra length of the tube body, and thus triggering the stopping member 44 to move from the first position to the second position. Similarly, when a caulk tube carrier is used, the extra length of the caulk tube carrier as compared to a standard caulk tube will also trigger the stoppering member 44 to move from the first position to the second position. In this case, the plunger 40 will be allowed to proceed for the longer distance b, and then further movement of the plunger 40 will be prevented. To explain further on the stopping mechanism, it is shown in Figure 6 that the stopping member 44 is slidably engaged with an elongated recess 50 of the plunger rod 42 via a micro switch 52. The micro switch 52 includes a lever 54 which will be in contact with a surface 60 of the recess 50 when the plunger is moving towards the caulk tube. The surface 60 of the recess 50 includes the first path with a distance a, which ends at a first ramp portion 56. It is this first ramp portion 56 which presses on the lever 54 to actuate the micro switch 52 and stops the movement of the plunger 40, when the stopping member 44 is at the first position α. When a caulk tube with extra length or a caulk tube carrier is used instead of a standard caulk tube, the extra length of the tube or the carrier will push the stopping member 44 to move from the first position α to the second position β, as indicated by the arrow in Figure 6 and 7. This action lifts the micro switch 52 and also the lever 54 to a higher position, so that the lever 54 can move over the first ramp portion 56 and thus the plunger 40 is allowed to continue proceeding with the forward movement for a total distance b until the lever 54 hits the second ramp portion 58, which is at an elevated position relative to the first ramp portion 56. The lever 54 is unable to move across the elevated second ramp portion 58, and thus any further movement of the plunger 40 will then be prevented and stopped at the distance b. This mechanism prevents the plunger 40 from moving continuously after it reached a fully extended position, which may cause damage to the caulk gun or the caulk tube, or expel the caulk tube or the caulk tube carrier from the caulk gun. Figures 8-10 illustrate a caulk tube receiving adaptor 70 which can be coupled to a caulk gun for receiving a caulk tube. Specifically, the adaptor 70 is for engaging part of the end portion opposing the discharge end of the caulk tube. Since the standard caulk tubes are generally configured in cylindrical shape, the adaptor 70 as embodied is also of cylindrical shape so as to accommodate the cylindrical end portion of the caulk tube. However, it can be understood that the adaptor should not be limited to cylindrical shape, but can be configured to match with the shape of the container to be received. As shown in Figures 8 and 9, the adaptor 70 can be in the form of a receptacle having a coupling member 72 adapted to releasably couple with the body 12, and a receiving member 74 adapted to releasably receive an end portion of the caulk tube. Specifically, the coupling member 72, the receiving member 74, and the opening 18 of the caulk gun are axially aligned along the longitudinal axis of the caulk tube (when received). As shown in Figure 10, the receiving member 74 comprises a releasing mechanism having a releasing collar 76 adapted to cooperate with a releasing trigger 78. Specifically, the releasing collar 76 is positioned adjacent to, and is axially aligned with the releasing trigger 78. More specifically, the releasing collar 76 is positioned between the releasing trigger 78 and the coupling member 72, and that the releasing trigger 78 is pivotally connected with the coupling member 72. The releasing trigger 78 is operable to move in a direction towards the body 12 which drives the releasing collar 76 to bias on an annular gripping portion 80. The gripping portion 80 is positioned between the releasing collar 76 and the piston 84 of the plunger 40, and includes an annular ring with a plurality of resilient teeth extending from the ring towards the ring center. Specifically, the teeth are extending from the ring towards the ring center and are pointing towards the piston 84 of the plunger 40 at an angle of less than 90°. More specifically, the gripping portion 80 can be made with metal. The teeth are adapted to engage an outer wall of the end portion of the caulk tube when the caulk tube is received at the receiving member. Particularly, when the plunger 40 is in motion to apply pressure onto the end plate of the caulk tube via the piston 84, the outer wall of the end portion of the caulk tube will be gripped tightly by the teeth of the gripping portion 80, and thus securing the caulk tube at the adaptor 70. When the releasing trigger 78 is triggered to release the caulk tube, the releasing trigger 78 will drive the adjacent releasing collar 76 to press on the gripping portion 80. The teeth of the gripping portion 80 will then be deformed by the releasing collar 76 and thus disengage the teeth from the outer wall of the caulk tube. A spring 82 is arranged between the releasing trigger 78 and the coupling member 72 to provide a biasing force on the releasing trigger 78. The adaptor 70 as embodied in the present invention can be used to substitute the conventional, horizontally elongated caulk tube holder of the traditional caulk gun, which is known to be relatively bulky and heavy for storage or transportation. In contrast to the traditional caulk gun, the adaptor 70 can be releasably coupled to the caulk gun only when needed, and thereby reducing the overall size of the caulk gun. In addition, the adaptor 70 is designed to hold the caulk tube at its end instead of supporting the tube horizontally along its length. The caulk tube can simply be inserted into the receiving member 74, and thereby minimizing the problem of the undesirable sliding of the tube within the holder of the traditional caulk gun. Furthermore, caulk tubes of various lengths can also be fitted into the caulk gun via the adaptor 70, and therefore allowing the user with a selection of caulk tubes having different volume. Furthermore, the adaptor 70 is provided with an easy-to-use releasing mechanism for a quick and simple unloading of the caulk tube after use. It should be understood that the above only illustrates and describes examples whereby the present invention may be carried out, and that modifications and/or alterations may be made thereto without departing from the spirit of the invention. It should also be understood that certain features of the invention, which are, for clarity, described in the context of separate embodiments, may also be provided in combination in a single embodiment. Conversely, various features of the invention which are, for brevity, described in the context of a single embodiment, may also be provided or separately or in any suitable sub-combination.

2. A caulk gun for dispensing caulk material, comprising: a body having a handle and an actuating mechanism; a plunger having an elongated rod slidably connected with the body, the plunger moveable by the actuating mechanism; the rod is slidably engageable with a stopping member, the stopping member is pivotally movable between a first position and a second position, wherein when the stopping member is in the first position, movement of the plunger is prevented after a first distance, and when the stopping member is at the second position, movement of the plunger is prevented after a second distance.

3. The caulk gun of claim 2, wherein the rod is configured with an elongated recess having a first ramp portion and a second ramp portion, the second ramp portion is at an elevated position relative to the first ramp portion. 4. The caulk gun of claim 2 or 3, wherein the plunger is adapted to stop at the first distance when the stopping member engages the first ramp portion, and is adapted to stop at the second distance when the stopping member engages the second ramp portion. 5. The caulk gun of any one of claims 2 to 4, wherein the second distance is longer than the first distance. 6. The caulk gun of any one of claims 2 to 5, wherein the stopping member is biased between the first and the second positions via a resilient means. 7. The caulk gun of any one of claims 2 to 6, wherein the stopping member has a contact portion slidably contacting the rod, the contact portion comprises a micro switch. 8. The caulk gun according to any one of the preceding claims, further comprising a receptacle having a coupling member adapted to releasably couple with the body, and a receiving member adapted to releasably receive an end portion of the caulk tube. 9. The caulk gun of claim 8, wherein the coupling member and the receiving member are axially aligned. 10. The caulk gun of claim 8, wherein the receiving member comprises a gripping portion having a plurality of resilient teeth for engaging an outer wall of the caulk tube. 11. The caulk gun according to any one of the preceding claims, wherein the receiving member comprises a releasing collar adapted to cooperate with a releasing trigger, the releasing trigger operable to move the releasing collar to bias on the gripping portion to deform the teeth, so as to allow disengagement of the teeth from the outer wall of the caulk tube. 12. The caulk gun according to any one of the preceding claims, wherein the releasing collar is positioned between the releasing trigger and the coupling member. 13. The caulk gun according to any one of the preceding claims, wherein the releasing trigger is pivotally connected with the coupling member. 14. The caulk gun according to any one of the preceding claims, wherein a resilient member is arranged between the releasing trigger and the coupling member to provide a biasing force on the releasing trigger. 15. The caulk gun according to any one of the preceding claims, wherein the gripping portion has an annular shape.

2881242

Continuous preform device for composite stringer

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 is an explanatory diagram showing how a stringer molding 1 made of a composite according to the present invention is applied to an aircraft fuselage 5. The stringer molding 1 is used as a structural material making up the aircraft fuselage 5 by being fixed along an inner wall surface of the aircraft fuselage 5 in an axial direction of the aircraft fuselage 5. The aircraft fuselage 5 has a three-dimensional curved surface shape, so the stringer molding 1 attached to the inner wall surface of the aircraft fuselage 5 needs to have a three-dimensional shape according to a placement location on the inner wall surface of the aircraft fuselage 5. Figure 2 shows a stringer molding 1 having a basic structure. The stringer molding has a cross section of a so-called hat shape or omega shape. The molding 1 is a long curved member having a radius of curvature R in a longitudinal direction. The radius of curvature R is not limited to a fixed radius of curvature, and may naturally be variable, changing to a radius of curvature R _1 to R _2, and so forth in a longitudinal direction. Also, the stringer molding 1 may be a long molding whose cross section at one end A is shaped to be symmetrical with respect to a vertical line V _1 and whose other end B has a torsional angle α _1 with respect to the vertical line V _1. The radius of curvature R and torsional angle α _1 vary with the installation location on the aircraft fuselage 5 where the stringer molding 1 is used. Figure 3 shows a molding 10 which has an area with a different thickness. The molding 10 shown in Figure 3 has an area 12 with an increased board thickness. The area 12 is constructed by laminating plural prepreg sheets 11a, 12a, 13a, 14a, and 15a. The sheets 11a to 15a are laminated one after another onto required locations. The cross-sectional shape of the laminated prepreg sheets may naturally be formed by laminating prepreg sheets with an identical cross section, such as prepreg sheets 11b, 12b, and 13b equal in cross-sectional shape to the molding 10 having an area with a different thickness. Figure 4 shows the molding 10 equipped with a so-called joggle portion 16 as well as a curing mold 20 shaped to form the joggle portion, where the stringer is raised along the joggle portion in locations where the inner wall surface of the aircraft fuselage is thickened. A slope corresponding to height variation of the joggle portion is normally around 20:1, and a curing mold forming device described later can do forming in such a way as to accommodate such a joggle. As described later, the present invention does forming which involves forming the molding 10 on the curing mold 20 corresponding to the product shape and sending the molding 10 to a succeeding process, namely a thermosetting (heat-curing) process, the molding 10 being provided with the area 12 different in thickness, with the joggle portion 16, and with a curvature and twist which occur in a longitudinal direction. Figure 5 is an explanatory diagram showing a configuration of a continuous preform device for a composite stringer according to the present invention. The continuous preform device for a composite stringer includes a dispenser device 200, a section preform device 300, a press/puller device 400, and a curing mold forming device 500, which are placed in a straight line from upstream to downstream. The dispenser device 200 includes a table 210 as well as a carrier film delivery roll 220 and carrier film delivery roll 230 located on an upstream side and downstream side of the table 210, respectively, and adapted to send out carrier films. The carrier film delivery roll 220 installed on the upstream side of the table 210 supplies a carrier film F _1 for a lower face of the prepreg composite while the carrier film delivery roll 230 installed on the downstream side of the table 210 supplies a carrier film F _2 for an upper face of the prepreg composite. The section preform device 300 includes a section preform shaping rollers 330 with plural shaping rollers placed above a base 310. The press/puller device 400 have a press unit 420 and a puller unit 450 on a base 410. The curing mold forming device 500 has a raisable table 520 on a base 510. The table 520 supports the curing mold 20, and plural molding guide rollers 530 are disposed above the curing mold 20. Figure 6 shows a process for setting a prepreg laminate 100 on a top face of the lower-face carrier film F _1 on the table 210 of the dispenser device 200. The prepreg laminate 100 is put on the lower-face carrier film F _1 sent out from the carrier film delivery roll 220 onto the table 210. The prepreg laminate 100 is a material produced by laying up (laminating) a necessary number of sheets of prepreg, which has been prepared by impregnating carbon fiber with epoxy resin, for example. Instead of carbon fiber, glass fiber or aramid fiber may be used as well. Also, the impregnating resin may be any thermosetting resin which cures, for example, in a temperature range of about 180 C° to 125 C°, and bismaleimide resin is used, for example. Figure 7 shows a process in which the prepreg laminate 100 from the dispenser device 200 is preformed on the section preform device 300, becoming hat-shaped or omega-shaped in cross section. The upper-face carrier film F _2 sent out by the downstream carrier film delivery roll 230 is laminated on the prepreg laminate 100 laid over the lower-face carrier film F _1. The prepreg laminate 100 sandwiched between the lower-face carrier film F _1 and upper-face carrier film F _2 is caused to pass the section preform device 300 by operation of the press/puller device 400. Using the press unit 420 disposed upstream and puller unit 450 disposed downstream, the press/puller device 400 causes the prepreg laminate 100 to pass through various devices together with the lower-face carrier film F _1 and upper-face carrier film F _2 in a manner described below. Figure 8 shows a process in which through operation of the press/puller device 400, the prepreg laminate 100 is caused to pass the section preform device 300 in order for its cross-sectional shape to be preformed and is then fed into the curing mold forming device 500. Figures 9 and 10 show a process in which the molding guide rollers 530 form the prepreg laminate 100 into a predetermined shape by pressing the prepreg laminate 100 against the curing mold 20 supported on the table 520 of the curing mold forming device 500. The press/puller device 400 stops feeding when the prepreg laminate 100 is fed completely into the curing mold forming device 500. Figure 10A shows a process in which the lower-face carrier film F _1 and upper-face carrier film F _2 are cut by a cutter 610 and cutter 620 in front of and behind the prepreg laminate 100 formed by the curing mold forming device 500 while Figure 10B shows how the lower-face carrier film F _1 and upper-face carrier film F _2 overlaid on the upper and lower faces of the prepreg laminate 100 have been cut off. Figure 11 shows a process in which the table 520 carrying the prepreg laminate 100 and curing mold 20 is lowered and separated from the molding guide roller 530. The prepreg laminate 100 formed in such a way as to conform to the shape of the curing mold pinched by the carrier films F _1 and F _2 is placed here. The table 520 carrying the prepreg laminate 100 and curing mold 20 is lowered. Figure 12 shows how the curing mold 20 with the prepreg laminate 100 mounted thereon has been removed from the table 520. Figure 13 shows a process in which the curing mold 20 with the prepreg laminate 100 overlaid integrally thereon is set on a work carrier 700. The work carrier 700 has wheels 710 for use to move to a next process and supports the curing mold 20 on a support 720. Figure 14 shows how the lower-face carrier film F _1 and upper-face carrier film F _2 covering both faces of the prepreg laminate 100 on the curing mold 20 have been removed. Figure 15 shows a process which involves covering the prepreg laminate 100 mounted on the curing mold 20 with a pressure pad 800, covering the pressure pad 800 with a bagging film 810, and sealing a periphery airtightly with a sealant 820, the curing mold 20 having the shape to be preformed. After sealing, the inside of the bagging film 810 is depressurized and thereby evacuated. As a result of this process, the prepreg laminate 100 adheres closely to the curing mold 20. Figure 16 shows a process for carrying the curing mold 20 with the evacuated prepreg laminate 100 mounted thereon into an autoclave 900 together with the work carrier 700 and curing the prepreg by heating and pressurization, to complete a molding. Figure 17A to Figure 27 show details of the devices making up the continuous preform device for the composite stringer according to the present invention. Figure 17A is a perspective view of the dispenser device 200. On the table 210, the prepreg laminate 100 is put on the lower-face carrier film F _1 delivered from the carrier film delivery roll 220. The prepreg laminate 100 is constructed by laying, one on top of another, a necessary number of sheets of prepreg differing in fiber direction. The prepreg laminate 100 may be laid up (laminated) manually by an operator or by a device called AFP (Automated Fiber Placement). The latter method is more rational in terms of labor-saving because the prepreg laminate produced by automatically laminating prepreg tape or prepreg tow of a predetermined width into a flat plate can be put on the lower-face carrier film F _1. The prepreg laminate 100 laid up on the lower-face carrier film F _1 on the table 210 is moved to a next process along with movement of the lower-face carrier film F _1, and is then delivered to a next process by being covered with the upper-face carrier film F _2 delivered from the carrier film delivery roll 230. The lower-face carrier film F _1 moving with the prepreg laminate 100 is allowed by a guide plate 240 to move along a predetermined line without weaving left and right. Figure 18 shows a prepreg laminate 110 different in planar shape from the prepreg laminate 100. The prepreg laminate 110 is provided with narrow-flanged portions and wide-flanged portions, making it possible to reduce cutting time needed to produce a predetermined stringer shape after thermosetting (curing) in a succeeding process as well as waste of prepreg material. This form of prepreg laminate 110 is also moved by being laid up on the lower-face carrier film F _1, and is then covered with the upper-face carrier film F _2. Figure 19 shows details of the section preform device 300. Plural preform shaping rollers are placed on the base 310 and heaters 340 are placed thereabove to heat the prepreg laminate. Figure 20 shows details of the preform shaping rollers 330 of the section preform device 300. The preform shaping rollers 330 according to the present embodiment are divided into eight shaping roller groups 331-338 and configured to do preforming to produce a hat-shaped cross-section. The number of sets of shaping rollers 330 is not limited to eight, and a different number of sets may be used depending on the cross-sectional shape of the stringer. When passing through the shaping roller groups 331 to 338, the prepreg laminate 100 undergoes preforming to acquire a hat-shaped cross section as shown by 100a to 100g. Figure 21 illustrates preforming done by one set of preform shaping rollers. A detailed structure of the preform shaping roller 340 will be described. The preform shaping roller 340 includes an upper roller 341 and lower roller 342 engaged vertically with each other, and opposite ends of both rollers 341 and 342 are rotatably supported by struts 343. The lower roller 342 has a convex forming die 3422 on a roller surface, and the upper roller 341 has a concave forming die 3411 in a roller surface to fit over the convex forming die 3422. The upper roller 341 is constantly biased toward the lower roller 342 by a compression spring 344. Thus, during passage of the prepreg laminate 100 and that area of the prepreg laminate 100 which differs in thickness dimension, the upper roller 341 rises by a dimension L _1 against the compression spring 344. During passage through a gap of the dimension L _1 between the upper roller 341 and lower roller 342, the prepreg laminate 100 is preformed into a hat-shaped cross section. Figures 22, 23A, and 23B are explanatory diagrams showing operation of the press unit 420 and puller unit 450 of the press/puller device 400. The press unit 420 and puller unit 450 are installed side by side. The press unit 420 includes an upper die 432 which moves up and down by means of a press cylinder 430 and a lower die 440 opposed to the upper die 432. The press cylinder may be a pneumatic cylinder or a motor-driven cylinder such as a servo motor. The puller unit 450 includes an upper presser die 462 which moves up and down by means of a press cylinder 460 and a lower presser die 470 opposed to the upper presser die 462. The press cylinder may be a pneumatic cylinder or a motor-driven cylinder such as a servo motor. The puller unit 450 has a function to reciprocate in upstream and downstream directions by means of a feed cylinder 480 and deliver the prepreg laminate 100 to a next process. The feed cylinder may be a pneumatic cylinder or a motor-driven cylinder such as a servo motor. Figure 23A is a front view of the press unit 420, where the upper die 432 moves up and down, being guided by a press die guide axis 434. Heaters 442 are placed on opposite sides of the upper die 432 and lower die 440 and the press unit 420 heats and presses prepreg laminate 100 by means of a pressing force from the press cylinder 460 and heat from the heaters 442. It is known that appropriate heating temperature is about 40°C to 50°C, for example, in the case of epoxy resin although it depends on the properties of prepreg resin. Figure 23B is a front view of the puller unit 450. The upper presser die 462 moves up and down relative to the lower presser die 470, being guided by a presser die guide axis 464. The entire puller unit 450 moves, being guided by a feed guide axis 482 which is driven by a feed cylinder 480. Parts (a) to (f) of Figure 22 show processes of the press/puller device 400. Part (a) of Figure 22 shows a pressing process. The press cylinder 430 of the press unit 420 becomes activated, pushes the upper die 432 against the lower die 440, and thereby presses the prepreg laminate 100 located between the upper and lower dies in conjunction with the heaters 442. Part (b) shows a pressing-pressure releasing process. The press cylinder 430 is deactivated and the upper die 432 is lifted. The prepreg laminate 100 is released from the grip of the upper die 432 and lower die 440 of the press unit 420. The press cylinder 460 of the puller unit 450 remains activated, holding the prepreg laminate 100. Part (c) shows a feed process. The feed cylinder 480 is activated to move the press cylinder 460 away from the press unit 420. As a result of this action, the prepreg laminate 100 is drawn out of the preform shaping rollers 330 of the section preform device 300. Part (d) shows a feed finishing process. The press cylinder 430 is activated, the upper die 432 is lowered, and the prepreg laminate 100 is gripped between the upper die 432 and lower die 440. Part (e) shows a presser releasing process. The press cylinder 460 of the puller unit 450 is deactivated and the upper presser die 462 is lifted. Part (f) shows a feeder return process. With the prepreg laminate 100 gripped by the upper die 432 and lower die 440 of the press unit 420, the feed cylinder 480 is deactivated and the entire puller unit 450 is pulled back toward the press unit 420, thereby completing one cycle. If the time required for processes shown in Parts (a) to (f) of Figure 22, i.e., for one cycle, is, for example, 5 seconds and an amount of travel of the feed cylinder per move is 15 mm, a travel distance per unit time of the prepreg laminate, i.e., molding speed, will be 10.8 meters per hour. It has been demonstrated experimentally that this level of molding speed, i.e., molding at 7.5 to 15 meters/hour is achievable. Figures 24A to 24C show configuration of an upper die 468 (elastic material) and upper die 438 (elastic material) used when there is an area with a different thickness in the middle of the prepreg laminate 100. Figures 24A and 24B show the same molding material differing in thickness. A prepreg laminate 100y has an angular projection y in a central portion. When pressure is applied with the elastic upper die 438 being interposed between the upper die 432 of the press unit 420 and the prepreg laminate 100y and with the upper die 468 being placed between the upper presser die 462 of the puller unit 450 and the prepreg laminate 100y, the upper dies 438 and 468 made of elastic material absorb forces in the directions of arrows x by elasticity. Figure 24C shows a case in which molding material varies in height such as flange thickness. When pressure is applied with similar upper dies 438 and 468 being placed on molding material 100t, height difference t is absorbed by elasticity of the elastic material. In this way, by placing an elastic material under the upper die, it is possible to deal with a material with varying thickness. Figures 25 to 27 show details of the curing mold forming device 500. The curing mold forming device 500 includes the table 520 supported by the base 510, and the curing mold 20 is mounted on the table 520 via a support 522. The table 520 is configured to be movable up and down by means of a piston 524 driven by a cylinder 526. The table 520 is pushed up to a raised position by the piston 524 and positioned by a stopper 523. The table 520 is equipped with the plural molding guide rollers 530 and the prepreg laminate 100 delivered from a preceding process (puller unit) is formed along a surface of the curing mold 20 whose mounting surface corresponds to a preformed shape. Above the base 510, the heaters 540 are disposed along the table 520 to soften the prepreg laminate 100 on the table 520 to such rigidity as to be suitable for forming, where the prepreg laminate 100 is formed so as to conform to the shape of the curing mold 20. It is known that appropriate heating temperature is about 40°C to 50°C, for example, in the case of epoxy resin although it depends on the properties of prepreg resin. Figure 26 shows a state resulting from completion of forming after the entire prepreg laminate 100 is fed into the forming die member 20 and the molding guide roller 530 forms the prepreg laminate 100 into a desired formed shape. The stopper 523 is removed, the piston 524 is compressed by operating the cylinder 526, and thereby the table 520 is pulled down together with the curing mold 20 away from the molding guide rollers 530. Figure 27 shows how the curing mold 20 with the formed prepreg laminate 100 placed thereon have been removed from the support 522 on the table 520. The curing mold 20 with the prepreg laminate 100 placed thereon is sent to a next process, being carried by the work carrier 700 described in Figure 13 and later. Figures 28A to 28C show a detailed structure of the molding guide roller 530. The molding guide roller 530 is supported turnably around a through-shaft 531 supported by a frame 532. The frame 532 is mounted on a fixed side 536 by a shaft 533 via a linear motion bearing 535. The compression spring 534 is placed between the shaft 533 and fixed side 536, constantly pressing the shaft 533 toward the foaming die member 20. Thus, the molding guide roller 530 supported by the frame 532 presses the prepreg laminate 100 against the curing mold 20 to form the prepreg laminate 100. As shown in Figure 28B, at a location where the curing mold 20 is twisted, the shaft 533 inclines by an angle α _1 in a twisting direction and the molding guide roller 530 is also inclined by a twisting angle of α _1, conforming to an attitude of the forming die member 20. Also, if the prepreg laminate 100 has an area difference in thickness dimension, the compression spring 534 compresses, raising the molding guide roller 530 by a dimension C _1 equivalent to the thickness height to deal with the difference. Figure 29 shows an example of a curing mold forming device equipped with a molding guide roller device 600. The curing mold forming device here also includes the table 520 supported by the base 510, and the curing mold 20 is mounted on the table 520 via the support 522. The table 520 is configured to be movable up and down by means of the piston 524 driven by the cylinder 526. The table 520 is pushed up to a raised position by the piston 524 and positioned by a stopper 523. Above the base 510, the heaters 540 are disposed along the table 520 as with the above example. The process of removing the curing mold 20 after completion of forming is similar to the process shown in Figure 26. The molding guide roller device 600 is supported by struts 610 erected on the base 510. Figures 30 and 31 are a front view and side view of the molding guide roller device, respectively. In upper part of the strut 610, a cross-bar 614 is supported by a fastening tool 612. Forward part of the cross-bar 614 is formed into a round bar 616. A vertical support 620 is attached to the round bar 616 via a support clamp 622. The support clamp 622 is configured to be movable in a Y-axis direction together with the first vertical support 620. The molding guide roller unit 650 is configured to be movable in a Z-axis direction when the support clamp 622 is operated. In the molding guide roller device 600, a pair of molding guide roller units 650 are attached to opposite ends of a horizontal support 630 by second vertical supports 640, the horizontal support 630 being supported on the first vertical support 620 by a slewing bearing 632. Each molding guide roller unit 650 includes two presser rollers 660 and four guide rollers 670 supported by a frame 652. Figure 32 shows motion directions of the molding guide roller units 650. The first vertical support 620 and two second vertical supports 640 can move in the Z-axis direction, which corresponds to a vertical direction. The horizontal support 630 supported by the first vertical support 620 rotates in the directions of arrows R _1, which correspond to a yaw direction. The frames 652 of the molding guide roller units 650 supported by the second vertical supports 640 rotate in the directions of arrows R _2, which correspond to a pitch direction. Figure 33 shows how the two molding guide roller units 650 apply molding pressure at different height positions in the vertical direction. The presser rollers 660 apply pressure to the curing mold 20 under their own weight acting on the presser roller 660. The pressure is applied at multiple points uniformly by four presser rollers 660, which are arranged uniformly along the curing mold 20. Figure 34 is a front view of the presser roller 660 as well as the guide rollers 670 placed on right and left sides of the presser roller 660. A support member 685 of each guide roller 670 is in threaded engagement with two threaded shafts 680 and 690. The first threaded shaft 680 has leads opposite each other, and the guide roller 670 turns in the directions of arrow R _3 with an axis 686 acting as a center of rotation when a knob 682 is turned. The second threaded shaft 690 also has leads opposite each other, and a width dimension W _1 of the guide roller 670 can be changed by turning a knob 692. Figure 35 shows how the frame 652 has inclined with respect to the second vertical supports 640 by rolling on a spherical bearing 642. The presser roller 660 and guide roller 670 can deal with inclined part of the curing mold 20. Figure 36 shows a structure in which the guide rollers 670 are supported by leaf springs 695. In the shown condition, even if a width dimension B of the curing mold 20 changes to B', the change can be followed due to the action of the spring. Figure 37 shows how the curing mold 20 is curved in a plane. Due to the facts that the shaft 620 can move in the Y-direction and that the horizontal support turns around the shaft 620 as well as due to the action of the spherical bearing 642, the presser roller 660 and guide rollers 670 follow the curving of the curing mold 20 by performing yaw motion. Thus, the present invention allows a composite stringer attached securely to an aircraft fuselage having three-dimensional curved surfaces to be continuously preformed in an efficient manner.

1. A continuous preform device for a composite stringer, the device being adapted to continuously preform a stringer made of laminated composite prepreg of a predetermined length and comprising: a dispenser device adapted to supply a prepreg laminate to a next process by sandwiching upper and lower faces of the prepreg laminate with carrier films; a section preform device adapted to form the prepreg laminate into a desired cross-sectional shape together with the carrier films; a press/puller device adapted to apply a pressing process to the prepreg laminate sandwiched between the carrier films while intermittently feeding the composite subjected to the pressing process downstream; and a curing mold forming device equipped with a forming die member and a guide roller adapted to form the incoming prepreg laminate sandwiched between the carrier films into a shape appropriate to a process preceding a curing process.

2. The continuous preform device for a composite stringer according to claim 1, wherein the dispenser device comprises a table adapted to put the prepreg laminate thereon; a reel installed at one end of the table and adapted to supply the carrier film for the lower face; a reel installed at another end of the table and adapted to supply the carrier film for the upper face; and a guide plate. 3. The continuous preform device for a composite stringer according to claim 1, wherein the section preform device comprises a plurality of preform shaping rollers and a heater adapted to form a cross-sectional shape of the prepreg laminate sandwiched between the carrier films into a hat shape or an omega shape. 4. The continuous preform device for a composite stringer according to claim 1, wherein the press/puller device comprises a press unit provided with an upper die, a lower die, and a heater; an upper presser die and a lower presser die; and a feed cylinder and a heater adapted to cause the entire press unit to reciprocate. 5. The continuous preform device for a composite stringer according to claim 1, wherein the curing mold forming device comprises a table adapted to go up and down by supporting the curing mold; a plurality of molding guide rollers adapted to press the prepreg laminate via a compression spring, the prepreg laminate being sandwiched between the carrier films and put on the curing mold; and a heater. 6. The continuous preform device for a composite stringer according to claim 1, wherein the curing mold forming device comprises a molding guide roller unit, the molding guide roller unit including two presser rollers adapted to press an upper face of a forming die member hat-shaped in cross section, and four guide rollers adapted to press a side face of the forming die member. 7. The continuous preform device for a composite stringer according to claim 6, wherein the molding guide roller unit is movable in a Y-axis direction and a Z-axis direction and turnable in a roll direction, a pitch direction, and a yaw direction, where the Y-axis direction corresponds to a horizontal direction orthogonal to a longitudinal direction of the forming die member while the Z-axis direction corresponds to a vertical direction. 8. The continuous preform device for a composite stringer according to claim 6, wherein widths and angles of the guide rollers in the molding guide roller unit are adjustable.

2881675

An air supply system

Based on the following detailed description of an invention, generate the patent claims. There should be 12 claims in total. The first, independent claim is given and the remaining 11 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described more fully hereinafter with reference to the accompanying drawings, in which currently preferred embodiments of the invention are shown. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. These embodiments are rather provided for thoroughness and completeness, and for fully conveying the scope of the invention to the skilled person. Figure 1 illustrates a clean room 1 comprising an air supply system 100 of known type. Figure 2 is a view from below of the same air supply system 100. The air supply system 100 comprises an air supply section 120 which is arranged in a ceiling 2 of the clean room 1. The air supply section 120 is arranged above an intended work area 140 of the clean room 1. The clean room 1 could be e.g. an operating theatre, a production room for clean products, or a room for handing sterile products, such as unpacking and preparation of sterile instruments before an operation. The air supply section 120 comprises a plurality of air supply membranes 122 which are arranged in an octagonal pattern. The air supply section 120 supplies clean air with a temperature being lower than the temperature of the ambient air in the room 1. Clean air is thereby supplied having a higher density than that of the ambient air. By this air density difference the supplied air sinks downwards by essentially only gravitational forces. As a result a laminar air flow 150 directed downwards from the ceiling 2 is supplied by the air supply section 120. The laminar characteristic of the air flow 150 is advantageous in that clean air is provided without the need for very high air flows. Air discharge units 160 are arranged in the clean room 1. These air discharge units 160 are located in the side wall of the clean room 1, preferably near the corners in side walls, and at a level of about 10 cm above the level of a floor 170 of the clean room 1. The air discharge units 160 are adapted to, actively or passively, guide air out from the clean room 1. Each of the air supply membranes 122 is formed by an air permeable body having an inner body and an outer body (not shown). The laminar air flow 150 is thereby provided by supplying a flow of clean air through the air supply membrane 122 in a direction from the inner body to the outer body. The inner body of the air supply membrane 122 is arranged to brake the first flow of clean air whereas the outer body is arranged to subsequently direct the first flow of clean air such that a gravitationally induced downward flow is created. [PATCIT WO2005017419A] discloses an example of how the air supply membrane 122 may be designed. The document discloses that the inner body of the air permeable body of the air supply membrane 122 consists of, or includes, porous material. The inner body is further designed to provide resistance when air is supplied there through. The inner body may have filtering properties in order to provide fewer air borne particles that exit the air supply membrane 122. The porous material may be foamed plastic with preferable open cells. The outer part of the air permeable body of the air supply membrane 122 may comprise air passages. The outer part may be non-porous and may have portions forming or defining passages or channels of uniform or substantially uniform thickness located close to each other. The channels may be rectilinear or substantially rectilinear and extend in parallel or substantially in parallel to each other. By means of design of the passages, good directional effect and generation of rectilinear air flows are provided. An air supply system 200 according to one embodiment of the present invention will now be described in detail. Figure 3 illustrates such an air supply system 200 where a first air supply section 120 and a second air supply section 230 are situated in the ceiling 2 of the clean room 1. The first air supply section 120 corresponds to the air supply section 120 of figures 1 and 2, but when describing embodiments of the invention it will be denoted "first" in order to distinguish it from the additional second air supply section 230. The first air supply section 120 discloses first air supply membranes 122, as previously described in connection to figures 1 and 2. A first flow of clean air is supplied through the air supply membranes 122 of the first air supply section 120. The second air supply section 230 comprises a second air supply membrane 232 through which a second flow of clean air is supplied. The second air supply section 230 is arranged to adjust the velocity of the second flow of clean air when entering the second air supply section 230. The velocity is adjusted to a predetermined velocity. The second air supply section 230 is also adapted to direct the second flow of clean air downwards. By combining the first flow of clean air supplied by the first air supply section 120 and the second flow of clean air supplied by the second air supply section 230, an improved clean laminar air flow 250 with regards to flow stability and uniformity is provided. In particular, it has been realized that the risk of formation of low-pressure air zones in the clean laminar air flow 250 is decreased. By low-pressure air zones is meant that the air within these zones have a lower pressure than the surrounding air. The surrounding air may be the supplied clean air and/or the ambient air in the room. The risk of entrainment of small-sized particles into the laminar flow, due to the low-pressure air zones, is thereby decreased. By the inventive system, some standardized tests, such as DIN 1946-4 qualification test for operating rooms, may be fulfilled. This test measures for example the entrainment of small-sized particles with a size up to 0.5 µm into the laminar air flow. Depending on the temperature of the clean air and the ambient air, how the air outlets are arranged etc., the predetermined velocity of the second flow of clean air may differ. For a specific air supply system configuration, the appropriate predetermined velocity may be determined by testing and/or simulating the air flow velocities and adjusting parameters of the air supply system, such as initial velocity when entering the air supply sections and/or the design of the air supply sections, until a desired air flow at e.g. a specific level is achieved. The predetermined velocity is preferably set such that an air velocity of about 0.25 m/s is obtained when the air reaches, for instance, a certain working height in the clean room 1. The working height should in this context be understood as the height, as measured from the floor 170 of the clean room 1, where the activity in need of clean air is primarily conducted. The velocity of the second flow of clean air may preferably be measured, by e.g. an air flow speed meter, at a distance of about 10 centimetres below the first air supply membrane 122 in the direction of the clean air flow 250, in order to ensure that the air velocity has the desired predetermined value. One embodiment of the second air supply section 230 will now be disclosed with reference to figure 4. Figure 4 is a view from below of the air supply system 200 disclosed in figure 3. As illustrated in figure 3, the first air supply section 120 comprises a plurality of first air supply membranes 122. In this embodiment, the air supply membranes 122 are arranged in an octagonal pattern. The first air supply section 230 is ring-shaped and surrounds the second air supply section 230. The wording ring-shaped should be construed as a ring shape formed by one or a plurality of segments providing a continuous or discontinuous ring. For symmetry reasons, the second air supply section 230 is arranged in the centre of the octagonal pattern. The flow of clean air 250 thereby becomes more homogeneous. The inventive combination of the first air supply section 120 and the second air supply section 230 provides clean air in an area, such as a work area 140, in the clean room 1. The clean air flow 250 is provided between the first and second air supply sections 120, 230 and the work area 140 in the clean room 1. The second air supply section 230 typically uses larger volumes of air than the first air supply section 120, which implies that more energy is needed to supply the clean air from the second air supply section 230. By arranging the first air supply section 120 such that it surrounds the second air supply section 230 the size of the second air supply section may be kept relatively small without reducing the area of the clean room for which clean air is supplied. In other words, clean air may be provided over a larger area of the clean room 1 in an more energy efficient manner. To provide a homogeneous and directed air flow the second air supply section 230 comprises air outlets 234 formed in the second air supply membrane 232. The air outlets 234 are formed as a honeycomb structure 236. This structure may also be referred to as having openings in a hexagonal shaped pattern or grid. The honeycomb structure 236 is a mechanically stabile structure. It should be noted that the second air supply membrane 232 may in other embodiments comprise a perforated layer in which the air outlets may be arranged in any arrangement or pattern by which a homogeneous laminar air flow 250 is provided by the air supply membrane 232. The air supply system 200 may be arranged such that the provided clean air flow 250 has an extension, as seen in a horizontal plane that covers an area having e.g. a circular, rectangular or oval shape. Other shapes are of course also feasible. In preferred embodiments, the covered area is in the interval of 0.5 - 16 m ^2. In case of a circular shape, the air supply system 200 may be arranged such that the extent of the clean air flow, as seen in a horizontal plane, covers a circular area extending with a radius of 0.5 - 2 meters, preferably 0.75-1.5 meters, as seen from the centre of the work area 140. An area extending with a radius of 0.5 - 2 meters as seen from the centre of the work area 140, yields an area of about 0.75 to 13 m ^2. An area extending with a radius of 0.75 - 1.5 meters as seen from the centre of the work area 140, yields an area of 1.7 to 7.1 m ^2. In applications where it is desired that the supplied air flow 250 covers a larger area, the first air supply section 120, as illustrated in figure 4, may comprise an additional ring-shaped section (not shown) of air supply membranes 122. The additional section may be located such that is surrounds the illustrated air supply section 120. The air supply membranes of the additional section are configured in the same manner as the air supply membranes 122 of the illustrated air supply section 120. It is realized that yet further additional sections are possible depending on the desired cover area of the supplied laminar air flow 250. According to one embodiment of the present invention the air supply system 200 is provided in a room being an operating theatre. In an operating theatre, an operating table (not illustrated) is typically arranged in the work area 140. As an alternative example, the air supply system 200 may be provided in a production room. In a production room, a production station (not illustrated) is typically located in the work area 140. The work area 140 may extend to an area surrounding e.g. the operating table or production station, in which area staff and equipment may be present. According to one embodiment of the present invention where the first air supply section 120 comprises a plurality of air supply membranes 122, air spoilers 240 are disposed between each pair of mutually adjacent first air supply membranes 122. The first air supply section 120 may thereby be arranged as a discontinuous structure surrounding the second air supply section 230. This facilitates easy assembly and exchange of the first air supply membranes 122. The presence of air spoilers 240 is advantageous as ambient air is prevented or at least hindered to be drawn into the clean air flow 250 provided by the air supply system 200. Each spoiler 240 is formed as a ridge which extends in a direction outwards from the inner area of the air supply section 120. The air spoilers 240 may due to their shape further help to minimize the increased downward velocity which may occur when clean air provided by adjacent first air supply membranes 122 meet in an uncontrolled manner. Hence, the risk of low-pressure air zones in the clean air flow 250 is further decreased. It should be noted that the laminar air flow 250 has a substantially uniform direction, in contrary to turbulent flows. However, due to disturbances in the flow path, such as persons or equipment, the direction of the laminar air flow 250 will increasingly turn outwards from the centre of the laminar air flow volume with an increasing distance from respective air supply sections 120, 230. Thus, the clean air flow 250 provided gets a funnel-shaped form in the room. The following will disclose an example of how an air supply system 300 according to an embodiment of the present invention may function. Figure 5 illustrates a cross-sectional view of the clean room 1 comprising the air supply system 300. The first air supply section 120 and the second air supply section 230 are situated in the ceiling 2 of the clean room 1. The first air supply section 120 and the second air supply section 230 are supplied with a common flow of clean air 302. The common flow of clean air 302 is in this embodiment provided by a common air flow source (not shown). The air flow source may comprise an air intake outside the room and/or a circulation device for circulating the air discharged by the air dischargers 160. By supplying the common air flow 302 to the air supply sections 120, 230, the number of components needed for the installation of the air supply device 300 is reduced. The common flow of clean air 302 is supplied using a fan 304. By providing the common flow of clean air 302, only one air flow need to be controlled in view of temperature and velocity. Thus, an efficient control system is provided. The person skilled in the art realises that the common flow of clean air 302 may be provided by other means than a fan 304. A filter element 312, comprising for example a HEPA filter, is arranged in the channel of the common flow of clean air 302. The filter element 312 cleans the throughpassing air such that the provided air flow 302 is clean. As disclosed in connection to figure 3 and figure 4, the first air supply section 120 supplies clean air with a temperature T _1 being lower than the temperature T _2 of the ambient air in the clean room 1. Clean air is thereby supplied which has a higher density than that of the ambient air. By using this air density difference and by further braking the initial velocity v _1 of the first flow of clean air as provided by the common flow of clean air 302, the supplied air sinks downwards by essentially only gravitational forces. As a result, a laminar air flow 250 directed downwards from the ceiling 2 is supplied by the first air supply section 120. The wording braking should be understood as that the initial velocity v _1 of the first flow of clean air is reduced such that the velocity of the clean air leaving the first air supply membrane 122 is essentially zero at a distance below the first air supply membrane 122. The distance is typically in the range 10 cm to 15 cm, but depends for instance on the initial velocity v _1, the temperature difference between T _1 and T _2 and the structure of the first air supply membrane 122. As an example, it is assumed that the velocity of the clean air is essentially zero at a distance of 10 cm below the first air supply membrane 122 and that the air flow 250 may be controlled to have a temperature T _1 of 1-2 °C lower than the temperature T _2 of the ambient air in the clean room 1. Under these assumptions, the laminar air flow 250 may achieve a velocity of 0.25 m/s when reaching a distance of 2 meters below the first air supply membrane 122 being situated in the ceiling. In a room having a ceiling height of about 3 meters, this is a typical working height (1 meter above the floor) used for the activities within the clean room 1. A velocity of around 0.25 m/s in the working height is advantageous since the velocity is high enough to brake the natural convection of particles deriving from persons being located in the area of the laminar air flow 250, however the velocity is still small enough to not cause any significant disturbances in form of discomfort or draught for the same persons. As disclosed above, the second air supply section 230 comprises a second air supply membrane 232 through which a second flow of clean air is supplied. The second air supply section 230 is arranged to adjust the velocity v _1 of the common flow of clean air 302, as it has when entering the second air supply section 230, to a predetermined velocity v _2. The second air supply section 230 is also adapted to direct the second flow of clean air downwards. The predetermined velocity v _2 is selected such that the clean air flow 250 has essentially the same velocity v _3 throughout a cross-section 308, as seen transverse the downward direction, of the clean air flow 250 at a specific level. According to one embodiment of the present invention the same velocity v _3 is around 0.25 m/s when reaching a distance 2 meter, being the specific level, below the second air supply member 230. The specific level may be the working height, such as a product assembly station or an operating table, for activities in the work area 140 which the clean air flow 250 covers. The working height for manual work activities, such as at a production station or at an operating table, could for example be 1 meter above the floor level. In this embodiment of the present invention the second flow of clean air has the same temperature T _1 as the first flow of clean air. This improves the laminar characteristics of the supplied clean air flow 250 in the room since differences in the density between the supplied clean air flows from the different air supply sections 120, 230 are reduced. Thus, the risk of turbulence in the air flow 250 associated with temperature, and thereby pressure differences, within the supplied clean air is mitigated. The pressure differences may otherwise lead to the presence of low or high pressure air zones within the formed clean air flow 250. The air supply system 300 further comprises a temperature controller 309. In this embodiment, the temperature controller 309 is located in the channel through which the common flow of clean air 302 is supplied to the air supply system 300. The temperature controller 309, being for example a heating radiator, a cooling radiator or a hot or cold air outlet, adjusts the temperature T _1 of the common flow of air 302 to a desired value. As exemplified above, it may be desired to adjust the temperature T _1 to 1-2 °C below the temperature T _2 of the ambient air. For this purpose, temperature sensors 310 are located in the ambient air outside the clean air flow 250. The temperature controller 309 receives the air temperature values measured by the temperature sensors 310 and adjust the temperature of the common flow of clean air 302 accordingly. The second air supply section 230 comprises a protective layer 311. The protective layer 311 cover the honeycomb structure of the air supply section 232, which thereby is protected from being damaged or becoming dirty by for instance activities performed in the clean room 1. The protective layer 311 is preferably easily exchangeable. The second air supply section 230 further comprises an inner air permeable layer 306. The inner air permeable layer 306 may consist of, or included porous material such that, by providing an even air flow resistance, the velocity of the air in the air flow is reduced. By selecting the velocity v _1 of the air flow 302 entering the air permeable layer and/or changing the resistance of the permeable layer 306, the velocity v _1 may be adjusted to a predetermined value for the air velocity v _2. The air resistance may for instance be varied by changing the porosity of the air permeable layer. The air supplied through the second air supply section 230 is moreover distributed i.e. equalized in pressure by being transported through the inner air permeable layer 306. The porous material may be foamed plastic, preferably with open cells. A method 600 for providing a clean air flow in a room is illustrated in figure 6. The method comprises supplying 602 a first flow of clean air having a lower temperature than the temperature of the ambient air in the room. The first flow of clean air is provided through a first air supply section. The method also comprises braking 604, by the first air supply section, the initial velocity of the first flow of clean air when entering the first air supply section. By the method the first flow of clean air thereafter forms a gravitationally induced downward flow. The method further comprises supplying 606 a second flow of clean air through a second air supply section. The velocity of the second flow of clean air is adjusted 608, by the second air supply section, when entering the second air supply section to a predetermined velocity. The method further comprises directing 610, by the second air supply section, the second flow of clean air downwards. The first air supply section and the second air supply section are according to the method situated in the ceiling in the room and the first air supply section at least partly surrounding the second air supply section. In one embodiment, the steps of supplying 602 the first flow of clean air and supplying the second flow of clean 604 air are performed parallel to each other. Features of the steps have been disclosed in connection to the previous figures and apply also to the method, where applicable. The person skilled in the art realizes that the present invention by no means is limited to the preferred embodiments described above. On the contrary, many modifications and variations are possible within the scope of the appended claims. For example, the second air supply section may comprise a plurality of air supply membranes. As another example, the first air supply section may only partly surround the second air supply device. This may be advantageous in some applications by that the size of the air supply system is reduced. The first air supply section may for example be shaped as a horseshoe partly surrounding the second air supply section. On the other hand, the first air supply section may in other embodiments be ring-shaped and may surround the second air supply section. The ring may have any geometrical form, for instance circular or elliptical. As yet another example, the air outlets in the one or more air supply membranes of the second air supply section may be formed in a pattern other than the honeycomb structure. The one or more air supply membranes of the second air supply section may comprise openings having any shape such as being triangular, quadratic, pentagonal etc. The openings may be arranged in order or in a random arrangement. The plurality of first air supply membranes may be arranged in a pattern such as a triangle, rectangle, hexagon, or of any shape as long as the first air supply section partly or fully surrounds the second air supply section. As an alternative to the plurality of air supply membranes of the first air supply section, the first air supply section may comprise a single air supply membrane in the form of an air supply layer or sheet. The first air supply section is not limited to comprising separately formed air supply membranes. On the contrary, the air supply section may comprise a single air supply membrane covering essentially the whole interface of the first air supply section towards the room.

1. An air supply system for providing a clean air flow (250) in a room (1), the air supply system (200, 300) comprising: a first air supply section (120) through which a first flow of clean air is supplied with a lower temperature than the temperature of the ambient air in the room (1), a second air supply section (230) through which a second flow of clean air is supplied, wherein the first air supply section (120) is arranged to brake the initial velocity (v_1) of the first flow of clean air when entering the first air supply section (120), whereby the first flow of clean air thereafter forms a gravitationally induced downward flow, wherein the second air supply section (230) is arranged to adjust the velocity (v_1) of the second flow of clean air when entering the second air supply section (230) to a predetermined velocity (v_2), and adapted to direct the second flow of clean air downwards, and wherein the first air supply section (120) and the second air supply section (230) are situated in the ceiling (2) in the room (1), the first air supply section (120) at least partly surrounding the second air supply section (230).

2. The air supply system according to claim 1, wherein the predetermined velocity (v_2) is selected such that the clean air flow (250) has essentially the same velocity (v_3) throughout a cross-section (308), as seen transverse the downward direction, of the clean air flow (250) at a specific level. 3. The air supply system according to any one of claims 1 - 2, wherein the second flow of clean air has the same temperature as the first flow of clean air. 4. The air supply system according to any one of claims 1 - 3, wherein the second air supply section (230) comprises air outlets (234) formed in an air supply membrane (232). 5. The air supply system according to claim 4, wherein the air outlets (234) in the air supply membrane (232) are formed as a honeycomb structure (236). 6. The air supply system according to any one of claims 1 - 5, wherein the first air supply section (120) comprises at least one air supply membrane (122) formed by an air permeable body having an inner body and an outer body, wherein the first flow of clean air is supplied in a direction from the inner body to the outer body. 7. The air supply system according to any one of claims 1 - 6, wherein the first air supply section (120) comprises a plurality of air supply membranes (122), and wherein air spoilers (240) are disposed between each pair of mutually adjacent air supply membranes (122) of the first air supply section (120). 8. The air supply system according to any one of claims 1 - 7, further comprising a temperature controller (309) arranged to adjust the temperature of the clean air (302) forming the first flow of clean air and/or the second flow of clean air, the adjustment being based on the temperature of the ambient air in the room (1) as measured by one or more temperature sensors (310) located in the ambient air in the room (1). 9. The air supply system according to any one of claims 1 - 8, wherein the first air supply section (120) is ring-shaped and surrounds the second air supply section (230). 10. The air supply system according to any one of claims 1 - 9, wherein the clean air flow (250) is provided between the air supply sections (120, 230) and a work area (140) in the room (1). 11. The air supply system according to any of claims 1 - 10, wherein the room (1) is an operating theatre. 12. The air supply system according to any of claims 1 - 11, wherein the first air supply section (120) and the second air supply section (230) are supplied with a common flow of clean air (302) from a common air flow source, said common flow of clean air (302) having an initial velocity (v_1) and temperature (T_1).

2881011

Cushion for chair and chair

Based on the following detailed description of an invention, generate the patent claims. There should be 7 claims in total. The first, independent claim is given and the remaining 6 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Before explaining the present invention in detail, it is to be understood that the present invention is not limited to the particular embodiments and that it can be practiced or carried out in various ways. A cushion for a chair will be explained as an embodiment of the present invention. The cushion for a chair according to the embodiment can be suitably used on a chair that includes a seating face and a backrest member. The cushion for a chair includes a cushion main body 1 and a case that covers the cushion main body 1 (not shown in the figure). As shown in Figure 1, the cushion main body 1 includes a seat member 10 that is to be mounted on a seating face of a chair and is to abut on the buttocks of a user seated, and a back-supporting member 30 that is to abut on the back of the user seated. The seat member 10 and the back-supporting member 30 are integrally formed. The cushion main body 1 is made of a resilient (shock-absorbing) member, and more specifically, a foamed resin such as a urethane foam. Since the cushion main body 1 is made of a resilient member, an angle α between the seat member 10 and the back-supporting member 30, which are integrally formed as described above, in the side view is variable. When the cushion for a chair is configured as mentioned above, the cushion main body 1 is deformed in harmony with an angle between a seating face and a backrest member of a chair, and therefore the cushion for a chair is precisely mounted on the chair. The cushion main body 1 includes, in a portion where the seat member 10 and the back-supporting member 30 are consecutively connected, a necking 1 a in which a width along the left-right direction is decreased. Therefore, the cushion main body 1 can be easily deformed in the direction along which an angle α between the seat member 10 and the back-supporting member 30 is changed. It is also possible that the seat member 10 and the back-supporting member 30 are separately formed and are subsequently joined to form the cushion main body 1. However, the back-supporting member 30 and the seat member 10 are preferably formed by integral molding. A width W1 along the left-right direction of the seat member 10 is 430 mm, and the width W1 of the seat member 10 is preferably no less than 300 mm and no greater than 550 mm. The lower limit of the width W1 is more preferably 350 mm, and still more preferably 400 mm. The upper limit of the width W1 is more preferably no greater than 500 mm, and still more preferably 450 mm. A width L1 along the front-back direction of the seat member 10 is 414 mm, and the width L1 of the seat member 10 is preferably no less than 300 mm and no greater than 550 mm. The lower limit of the width L1 is more preferably 350 mm, and still more preferably 400 mm. The upper limit of the width L1 is more preferably 500 mm, and still more preferably 450 mm. A height H1 of the back-supporting member 30 (a height from the bottom face of the seat member 10) is 366 mm, and the height H1 of the back-supporting member 30 is preferably no less than 280 mm and no greater than 500 mm. The lower limit of the height H1 is more preferably 300 mm, and still more preferably 340 mm. The upper limit of the height H1 is more preferably 450 mm, and still more preferably no greater than 400 mm. When the width W1 and the width L1 of the seat member 10 as well as the height H1 of the back-supporting member 30 fall within the above ranges, respectively, the cushion for a chair can be suitably attached to chairs for adults. In the case of a cushion for children, the width W1 and the width L1 of the seat member 10 as well as the height H1 of the back-supporting member 30 preferably fall within the following ranges, respectively. The width W1 of the seat member 10 is preferably no less than 200 mm and no greater than 450 mm. The lower limit of the width W1 is more preferably 250 mm, and still more preferably 300 mm. The upper limit of the width W1 is more preferably 400 mm, and still more preferably 350 mm. The width L1 of the seat member 10 is preferably no less than 200 mm and no greater than 450 mm. The lower limit of the width L1 is more preferably 250 mm, and still more preferably 300 mm. The upper limit of the width L1 is more preferably 400 mm, and still more preferably 350 mm. The height H1 of the back-supporting member 30 is preferably no less than 180 mm and no greater than 400 mm. The lower limit of the height H1 is more preferably 200 mm, and still more preferably 240 mm. The upper limit of the height H1 is more preferably 350 mm, and still more preferably no greater than 300 mm. The bottom face (back face) of the seat member 10 is flat. A rear face (back face) of the back-supporting member 30 is flat. Thus, when the cushion main body 1 is mounted on a chair, the bottom face of the seat member 10 is precisely mounted on a seating face of the chair in a state in which the rear face of the back-supporting member 30 abuts on a backrest member of the chair. The angle α between the seat member 10 and the back-supporting member 30 in the side view is preferably no less than 90° and no greater than 110°, and more preferably no less than 100° and no greater than 105°. When the angle α falls within the above range, the cushion main body 1 can be readily mounted precisely on an office chair. In the case of a cushion for children, the angle α is preferably about 90° (90° ± 5°). It is to be noted that the angle α between the seat member 10 and the back-supporting member 30 in the side view as referred to herein means an angle in a normal state with no external force applied to the cushion main body 1. The seat member 10 and the back-supporting member 30 each have a three-dimensionally curved surface. In the following, the shape of the surfaces of the seat member 10 and the back-supporting member 30 is described in more detail. The seat member 10 includes two ischium-facing portions 11 that have a recessed surface, and the surface of the ischium-facing portion 11 is concavely curved. The ischium-facing portion 11 has a three-dimensional curved surface such that the surface of the ischium-facing portion 11 is concavely curved in the vertical cross section along the left-right direction and is sloped upward toward the front and rear sides in the vertical cross section along the front-back direction. The ischium-facing portion 11 as referred to herein means a portion that is to abut on the ischium of the user seated, and more specifically, a vicinity of the lowest point O (the point nearest to the back face of the seat member 10) in the surface of the seat member 10 being to abut on the buttocks of the user seated (a region within 80 mm from the lowest point (i.e., a region encircled by a dashed line in Figure 3 )). In the present embodiment, a distance W2 between the respective centers O of the two ischium-facing portions 11 is 108 mm. The distance W2 between the respective centers O of the two ischium-facing portions 11 is preferably no less than 70 mm and no greater than 130 mm. The lower limit of the distance W2 between the centers O is more preferably 90 mm, and the upper limit of the distance W2 between the centers O is more preferably 120 mm. When the distance W2 between the centers O falls within the above range, in the case of a user seated being an adult, an ischium of the user seated is settled in the ischium-facing portion 11. In the case of a cushion for children, the distance W2 between the respective centers O of the two ischium-facing portions 11 is preferably no less than 70 mm and no greater than 120 mm. The lower limit of the distance W2 between the centers O is more preferably 80 mm, and the upper limit of the distance W2 between the centers O is more preferably 110 mm. It is to be noted that in the present embodiment, a thickness H2 of the seat member 10 in the center O of the ischium-facing portion 11 (a distance between the center O of the ischium-facing portion 11 and the bottom face) is 9 mm. In the present embodiment, a distance L2 from the center O of the ischium-facing portion 11 to a front edge of the cushion main body 1 is 314 mm. The distance L2 from the center O of the ischium-facing portion 11 to the front edge of the cushion main body 1 is preferably no less than 280 mm and no greater than 400 mm. The lower limit of the distance L2 is more preferably 300 mm, and the upper limit of the distance L2 is more preferably 350 mm. In the case of a cushion for children, the distance L2 from the center O of the ischium-facing portion 11 to the front edge of the cushion main body 1 is preferably no less than 230 mm and no greater than 350 mm. The lower limit of the distance L2 is more preferably 250 mm, and the upper limit of the distance L2 is more preferably 300 mm. In the vertical cross section along the front-back direction of the ischium-facing portion 11, the surface of the ischium-facing portion 11 is sloped more steeply upward on the rear side of the center O of the ischium-facing portion 11 than on the front side thereof (see Figure 6 ). Since the surface of the pair of ischium-facing portions 11 of the seat member 10 is concavely curved as mentioned above, the seat member 10 includes, between the ischium-facing portions 11 that are positioned on the rear side along the front-back direction (in the middle between the ischium-facing portions 11 along the left-right direction), an elevated portion relative to the ischium-facing portion 11 (see Figure 7 ), and the surface in the middle of the seat member 10 along the front-back direction is entirely concavely curved in the vertical cross section along the left-right direction (see Figure 8 ). The seat member 10 includes a ridge 13 provided from the middle portion thereof toward the front side along the front-back direction, and a pair of troughs 15 provided on both sides of the ridge 13. The surface of the ridge 13 and the pair of troughs 15 are continuous in the cross section along the left-right direction (see Figure 9 ). The pair of troughs 15 are arranged so that the respective ischium-facing portions 11 are positioned on an imaginary extended line toward the rear side. The surface of the trough 15 is sloped so that a distance between the lowest points of the troughs 15 in the vertical cross section along the left-right direction increases from the rear side to the front side (see Figure 2 ). Thus, the lowest point of the front edge of the trough 15 is positioned on an outer side than the position of the ischium-facing portion 11 along the left-right direction. The surface of the trough 15 is sloped upward from the ischium-facing portion 11 toward the front side, and thereafter is sloped downward toward the front side (see Figure 10 ). Therefore, even in a state in which the ischium is settled in the ischium-facing portion 11 as mentioned above, the user seated can move his or her legs easily when the user seated intends to do so. The seat member 10 includes, on the left and right edges (outside the trough 15), outer ridges 17 that are raised relative to other portions (for example, ridge 13) (see Figures 7 to 9 ). This configuration allows an outward spread of the user's legs to be minimized. In the cross section along the left-right direction of the back-supporting member 30, the back-supporting member 30 is concavely curved in the ilium upper border-facing portion and the lower ribs-facing portion. The ilium upper border-facing portion as referred to herein means a portion that is to abut on the upper border of the ilium of the user seated. In the present embodiment, the ilium upper border-facing portion means a position away from the center O of the ischium-facing portion 11 by a distance of 150 mm (L3) in the direction along which the back-supporting member 30 extends (i.e., a position at which the cross section shown in Figure 11 is taken). The distance L3 from the center O of the ischium-facing portion 11 to the center of the ilium upper border-facing portion in the direction along which the back-supporting member 30 extends is preferably no less than 120 mm and no greater than 180 mm. The lower limit of the distance L3 is preferably 140 mm, and the upper limit of the distance L3 is preferably 160 mm. In the case of a cushion for children, the distance L3 from the center O of the ischium-facing portion 11 to the center of the ilium upper border-facing portion is preferably no less than 80 mm and no greater than 120 mm. The lower limit of the distance L3 is more preferably 90 mm, and the upper limit of the distance L3 is more preferably 110 mm. The lower ribs-facing portion as referred to means a portion that is to abut on the lower ribs of the user seated. More specifically, in the present embodiment, the lower ribs-facing portion means a position away from the center O of the ischium-facing portion 11 by a distance (L4) of 250 mm in the direction along which the back-supporting member 30 extends (i.e., a position at which the cross section shown in Figure 12 is taken). It is to be noted that the distance L4 from the center O of the ischium-facing portion 11 to the lower ribs-facing portion in the direction along which the back-supporting member 30 extends is preferably no less than 220 mm and no greater than 280 mm. The lower limit of the distance L4 is preferably 240 mm, and the upper limit of the distance L3 is preferably 260 mm. In the case of a cushion for children, the distance L4 from the center O of the ischium-facing portion 11 to the lower ribs-facing portion is preferably no less than 180 mm and no greater than 240 mm. The lower limit of the distance L4 is preferably 200 mm, and the upper limit of the distance L4 is more preferably 220 mm. The surface of the portion of the seat member 10 upper than the lower ribs-facing portion (hereinafter, may be also referred to as "upper portion") is entirely concavely curved in the transverse cross section along the left-right direction and is declined rearward toward the upper part in the vertical cross section along the up-down direction (see Figure 10 ). According to such a configuration, the upper portion has a three-dimensional curved surface. The three-dimensional curved surface of the upper portion is such that a radius of curvature of the concave surface of the upper portion is larger than that of the concave surface of the lower ribs-facing portion. The surface of the seat member 10 and the back-supporting member 30 is a continuous three-dimensional curved surface such that the surface from the ischium-facing portion 11 to the ilium upper border-facing portion is entirely concaved. The rear portion of the seat member 10 from the ischium-facing portion 11 to the back-supporting member 30 (toward the back side) has a three-dimensional curved surface such that the surface of the rear portion of the seat member 10 from the ischium-facing portion 11 to the back-supporting member 30 is concavely curved in the vertical cross section along the left-right direction and is continuous from the ischium-facing portion 11 to the back-supporting member 30 in the vertical cross section along the up-down direction. A portion of the back-supporting member 30 lower than the ilium upper border-facing position (hereinafter, may be also referred to as "lower portion") has a three-dimensional curved surface such that the surface of the lower portion is concavely curved in the transverse cross section along the left-right direction and is continuous with the rear portion of the seat member 10 in the vertical cross section along the up-down direction. The cushion for a chair according to the embodiment as configured as above is used in a state in which the seat member 10 is mounted on a seating face of a chair. When a user is seated on the cushion for a chair, the ischium of the buttocks of the user seated is likely to be precisely settled in the ischium-facing portion 11 of the seat member 10, leading to less compression of the buttocks of the user seated and the stabilization of the posture of the user seated, since the seat member 10 has the three-dimensional curved surface. In addition, the buttocks of the user seated are less likely to be moved forward. In particular, since the ischium-facing portion 11 in the embodiment has such a surface shape that is sloped upward toward the front side, the forward movement of the buttocks of the user seated can be inhibited more effectively. When the ischium of the user seated is settled in the ischium-facing portion 11 in such a manner, the upper border of the ilium and the lower ribs of the user seated are precisely positioned at the ilium upper border-facing portion and the lower ribs-facing portion, respectively. Since the surface of the ilium upper border-facing portion and the lower ribs-facing portion is concavely curved in the transverse cross section along the left-right direction, and the surface of the upper portion has a three-dimensional curved surface such that the upper portion is inclined rearward toward the upper part in the vertical cross section along the up-down direction, the back of the user seated is held in such a manner that the back of the user is enfolded and supported from below by the back-supporting member 30. In particular, the back of the user seated is supported such that the ribs of the user seated are lifted upward by virtue of the surface shape of the portion upper than the lower ribs-facing portion, resulting in less feeling of compression of the chest and the like, thereby precluding possible difficulty in breathing in the user seated. In addition, the user seated can easily hold a posture with his or her head higher to have such a wider view as to help grasp the surrounding situation and communicate with others therearound. Moreover, when the posture of the user seated is held as mentioned above, the user seated can relax his or her shoulder and easily raise his or her arms, leading to ease of using both hands. Furthermore, the user can sit in a comfortable posture, as mentioned above, whereby the user can start a motion such as standing up, and for example, when the cushion for a chair according to the embodiment of the present invention is used on an office chair, the user can work smoothly during execution of a job such as an office work while maintaining his or her posture. It is to be noted that although the embodiment described above provides the aforementioned advantages based on the configuration explained above, the embodiment may be modified appropriately within the scope of the gist of the present invention. More specifically, although in the embodiment described above, a cushion for a chair suitably used principally for office chairs has been explained by way of example, the present invention is not limited thereto. The cushion for a chair according to the embodiment may be appropriately modified so as to be used for a chair for schoolchildren used in, for example, schools and the like. Although in the embodiment described above, a cushion for a chair having the cushion main body 1 covered with a case is explained by way of example, the case is not an essential constituent feature of the present invention. Even when the case is used, for example, the case may be provided with a member for attachment to a chair. Specifically, examples of the member for attachment include a string-like member for being wound around a chair, and a fabric member that is sewn on the rear face side of the back-supporting member 30 to form a bag for enveloping the backrest member, and the like. Even when the cushion for a chair according to the embodiment of the present invention includes the case and the cushion main body as mentioned above, the material for making the cushion main body is not limited to a urethane foam, and obviously, various well-known materials may be adopted. Although in the above embodiment, a cushion for a chair has been explained as an exemplary embodiment of the present invention, a configuration similar to the embodiment described above may be applied to a chair. In other words, the present invention also encompasses a chair, and a chair that includes a seat member and a back-supporting member each having a special surface shape as explained in the aforementioned embodiment is also contemplated within the scope of the present invention. Also, in the chair according to an embodiment of the present invention, it is evident that the aforementioned advantages can be exerted by employing a configuration similar to the above embodiment (including an ischium-facing portion, an ilium upper border-facing portion, a lower ribs-facing portion, an upper portion, a ridge, a trough, and the like). In addition, it is also obvious that well-known various materials can be used as a material for making the chair according to the embodiment of the present invention. As explained in the foregoing, the cushion for a chair and the chair according to the aspects of the present invention are less likely to cause compression of the buttocks of the user seated, and enable the user to maintain his or her posture precisely, whereby difficulty in breathing can be avoided. #### Industrial Applicability As described above, since the cushion for a chair and the chair according to the present invention facilitate maintenance of a user's proper posture, the cushion for a chair and the chair can be suitably used for office chairs, chairs for studying, living chairs, etc., as mentioned above, as well as seats, and the like. #### [Explanation Of The Reference Symbols] - 1: cushion main body - 1a: necking - 10: seat member - 11: ischium-facing portion - 13: ridge - 15: trough - 17: outer ridge - 30: back-supporting member - O: point - α: angle

1. A cushion for a chair comprising a seat member and a back-supporting member, wherein: the seat member is to abut on buttocks of a user seated and comprises two ischium-facing portions, a surface of each ischium-facing portion being to abut on an ischium of the user seated, each ischium-facing portion having a three-dimensional curved surface such that the surface of the ischium-facing portion is concavely curved in a vertical cross section along a left-right direction and is sloped upward toward a rear side in a vertical cross section along a front-back direction, and the back-supporting member is to abut on a back of the user seated and comprises an ilium upper border-facing portion and a lower ribs-facing portion, a surface of the ilium upper border-facing portion being to abut on an ilium of the user seated, a surface of the lower ribs-facing portion being to abut on lower ribs of the user seated, the surface of the ilium upper border-facing portion being entirely concavely curved in the transverse cross section along the left-right direction, the surface of the lower ribs-facing portion being entirely concavely curved in the transverse cross section along the left-right direction, and a portion of the back-supporting member upper than the lower ribs-facing portion having a three-dimensional curved surface such that the surface of the portion of the back-supporting member upper than the lower ribs-facing portion is entirely concavely curved in the transverse cross section along the left-right direction and is inclined rearward toward the upper part in a vertical cross section along an up-down direction.

2. The cushion for a chair according to claim 1, wherein the surface of the ischium-facing portion is sloped upward toward the front side in the vertical cross section along the front-back direction. 3. The cushion for a chair according to claim 1, wherein the seat member comprises a ridge provided at least in front of the middle portion thereof, and a pair of troughs provided on both sides of the ridge, and: the surface of the ridge and the pair of troughs being continuous in the vertical cross section along the left-right direction. 4. The cushion for a chair according to claim 1, wherein the seat member and the back-supporting member are integrally formed. 5. The cushion for a chair according to claim 4, wherein the cushion for a chair has a three-dimensional curved surface such that the surface of a rear portion of the seat member extending from the ischium-facing portion to the back-supporting member is concavely curved in the vertical cross section along the left-right direction, and is continuous from the ischium-facing portion to the back-supporting member in the vertical cross section along the front-back direction. 6. The cushion for a chair according to claim 4, wherein a portion of the back-supporting member lower than the ilium upper border-facing position has a three-dimensional curved surface such that the surface of the portion lower than the ilium upper border-facing position is concavely curved in the transverse cross section along the left-right direction and is continuous to the rear portion of the seat member in the vertical cross section along the front-back direction. 7. The cushion for a chair according to claim 4, wherein an angle between the seat member and the back-supporting member in the side view is no less than 90° and no greater than 110°.

2881007

Locking mechanism

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an exploded view of a locking mechanisme comprising a first 1 and a second part 9. The locking mechanism allows the first 1 and second 9 parts to pivot relative to each other when the locking mechanism is in a released state. This means that the locking mechanism will allow one part of a device to swing relative to another part of the same device such as e.g. the device is a table and a pair of table legs are allowed to swing relative to a table top, the device is a vehicle and a tailboard is allowed to swing relative to the vehicle, the device is a wall mounted bed and the sleeping surface e.g. including a matress is allowed to swing relative to the wall, the device is a wall or seat mounted tray or table top which is allowed to swing relative to the wall or the seat etc. Figure 2 and 3 show cut-through side views of the same embodiment as fig. 1. Figure 2 shows a cut-through side view where the cut has been made through the centre of the locking mechanism. Figure 3 shows a cut-through side view where the cut has been makde off the centre and instead shows how the fastening means for the bearing 3 fix the bearing 3 to the stationary part 2. According to the embodiment of fig. 1-3 the fastening means is constituted by four screw bolts 16. The locking mechanism comprises a stationary part 2 to which the first part 1 is fixed via a hinged connection, and a bearing 3, 3a, 3b in which the second part 9 is rotatably mounted. The stationary part 2 and the bearing 3 do not move relative to each other i.e. they are fixed relative to each other and relative to one of the device parts which the locking mechanism operates with. The stationary part 2 and the bearing is fixed to one device part and the second part either constitutes a second device part or is attached to a second device part. The bearing 3 can e.g. be provided with a cover plate 15 able to cover fastening means 16 for the bearing and making it possible to adapt the design of the locking mechanism to any desirable use or function without influencing the functionality of the locking mechanism. #### First Part The first part 1 can be constituted by a single piece of material, e.g. it can e.g. be molded from a hard polymer such as glass reinforeced nylon or steel, alternatively the first part 1 can be composed of separate pieces of material which are assembled and after assembling, the parts will be completely fixed and stationary relative to each other. If the first part 1 is composed of two or more pieces then each piece might be made of a material which is optimized in respect of weight and durability. I.e. if the locking mechanism is placed in a tray in an aeroplane it is important that each part weighs as little as possible, where as if a locking mechanism is used for e.g. holding a wall bed including a bottom and a matress which can be turned up or down, then it should be able to carry about 200 kg. Generally, the first part 1 comprises a first protruding part 1 a provided with a first contact surface 1b at one end. The protruding part 1 a extends in direction of the second part 9 and when the first part 1 is mounted in the locking mechanism and the locking mechanism is in a locked postion, the first contact surface 1 b will be in contact with the second part 9. The first protruding part 1 a should be constructed of a relatively hard and wear resistent material as it should remain relatively unaffected by the contact during the life time of the locking mechanism. When using the word "relatively" it is indicated that the use of the locking mechanism will determine how hard and wear resistent the material needs to be. The first part 1 illustrated in fig. 1 is constructed of a flat part fixed on top of a rectangular block, the flat part extends toward the second part 9 as the first protruding part 1a, and the front surface i.e. the first contact surface 1 b of the flat part is in contact with a corresponding surface of the second part 9. The contact between the first contact surface 1b and the actually prevents the second part 9 from rotating, the flat part has to be made of a material having a relatively high durability, "relatively high" means that the choice of material is influenced by the force the actual locking mechanism is subjected to. The first part 1 is also provided with a central part and the central part of the embodiment shown in fig. 1 provides an attachment position for a spring 7, the spring 7 forces the first part 1 into the locked position. Generally, the first part 1 is provided with some kind of release means which are able to provide a force big enough to overcome the force from the spring 7, the embodiment in fig. 1 is provided with a second protruding part 1c which extends in a direction opposite from the first protruding part 1a, when a relatively long handle part or release part 1d is attached to the second protruding part thereby providing a lever, it becomes easy for the user to overcome the force from the spring or spring system and release the first part 1 from the locked position. #### Hinged Connection Generally, the hinged connection allows the first part 1 to pivot around a swing axis a1 between at least two positions, a first locked position and a second released or unlocked position. In the first locked position the first part 1 is forced into a locked position by a spring 7, and in the second unlocked or released position a user overcomes the force of the spring 7 and the user forces the first part 1 into the second released position. Figure 1-3 illustrates one embodiment of a hinged connection where two pointed screws 6 with round heads forms a line which line represents the swing axis a1 (see fig. 2 ). The round heads of the pointed screws 6 face the staionary part 2 and fit into each their top recess of two screw bolts 5 which have been screwed into treads in the stationary part 2. The screw bolts 5 will normally be made of a very durable material such as steel. #### Spring Attachment Generally, the spring 7 or spring system i.e. a plurality of springs has one or more attachment points on the stationary part 2 and one or more attachment points on the first protruding part 1 a of the first part. Generally, the first part needs to have an attachment position for a spring or a spring system, but the attachment position could be at several positions, the attachment position e.g. depends on whether the spring or spring system which forces the first part into the locked position pushes or pulls. The spring 7 causes a movement of the protruding part 1a of the first part towards the circumferential surface of the second part 9 in order to keep the first protruding part 1 a in contact with the second part 9, until the force provided by the spring is exceeded by a releasing force normally provided by the user. According to the embodiment shown in fig. 1, the attachment point for the spring 7 on the first part 1 is provided by a pointed screw 11 which extends from the "lower" side of the central part of the first part 1 which is the inside of an inner surface 19 of the stationary part 2. Alternatively, the attachment point could be constituted by a tap or hook protruding from the lower surface of the first part 1, such a part could be an integrated part of the first part 1. The inner surface 19 of the stationary part 2 is the side facing the device part to which the stationary part 2 is attached. The spring 7 is illustrated as a helical metal spring which pulls in order to get from a biased to a relaxed position. One end of the helical spring 7 is attached to the free end of the pointed screw 11; the opposite end of the helical spring 7 is attached to the stationary part 2, e.g. to a (not shown) screw which is screwed into a longitudinal track 22 provided in the profile constituting the stationary part 2. The longitudinal track 22 is placed centrally and close to the inner surface 19 of the stationary part 2. When the spring 7 is placed in the position shown in fig. 1-3, the spring pulls in the direction of rotation of the first part 1, in order for the user to bring the first part 1 into an unlocked position, the user has to overcome the force provided by the spring 7 and rotate or pivot the first part 1 into an unlocked position. The first part 1 will be in an unlocked position when the first protruding part 1 a is pivoted into a position where the first protruding part 4 of the second part 9 can pass below, i.e. rotate anticlockwise in the figure, the contact surface 1b of the first protruding part 1. Alternatively, a spring or spring system can be positioned anywhere in the system where it pushes or pulls in direction of the rotation. The position of the spring 7 in the embodiment of fig. 1-3 has the advantageous that it is possible to use a physically large spring such as a helical spring without having to e.g. increase the height of the stationary part 2. #### Second Part Normally, the second part 9 shown in fig. 1 has a circular or at least partly circular perifery provided with two protruding parts, a first protruding part 4 and a second protruding part 14. The first protruding part 4 has a contact surface 4a corresponding to the first contact surface 1b of the first part 1 and the second protruding part 14 has a contact surface 14a corresponding to the third contact surface 8a of either the bearing 3a or the stationary part 2 or an independent part 8. Generally, the second part 9 is immobilised in one position when the locking mechanism is locked and when the locking mechanism is released the second part 9 can rotate or pivot between at least two positions. The contact between the first and the second contact surfaces 1 a and 4a on respectively the first part 1 and the second part 9 prevents the second part 9 from rotating or pivoting in one direction (i.e. anticlockwise according to the embodiment of fig. 1 ) when the locking mechanism is in a locked position, and the contact between the fourth and the third contact surfaces 8a and 14a on respectively the bearing 3a or the stationary part 2 or an independent part 8 and on the second part 9 prevent the second part 9 from rotating or pivoting in the opposite direction (i.e. clockwise according to the embodiment of fig. 1 ) when the locking mechanism is in a locked position. As the bearing 3 is fixed to the stationary part 2, the bearing 3 fixes the position of the second part 9 relative to both the stationary part 2 and the first part 1, and makes it impossible for the second part 9 to move away from the first part 1. Normally, friction alone will keep the second part 9 in a released or unlocked end position but the locking mechanism can be provided with means to lock the second part 9 in the released or unlocked end position and/or to lock the second part 9 in one or more intermediate positions. Whether this feature is advantagouos will depend on the actual use of the locking mechanism. According to the embodiment of fig. 1-3, the second part 9 is locked by friction in the released or unlocked position, and need therefore not be released by any release means as such; thus, the user has to overcome the frictional resistance and tentioning of the spring 7 upon bringing the second part 9 back into the locked position. #### Bottom Impact Either the bearing 3a or the stationary part 2 or an independent part held in position by the stationary part 2 or by the bearing 3a constitutes the fourth contact surface 8a facing the second part 9. The fourth contact surface 8a can be constituted e.g. by a protruding part of either the bearing 3a or the stationary part 2 extending in direction of the second part, or alternatively the fourth contact surface 8a can be provided by a separate piece e.g. a rectangular block 8 as shown in fig. 1, which is made of e.g. a hard and durable material such as steel. By making a separate piece it is possible to increase the wear resistence of the fourth contact surface without increasing the weight of the locking mechanism significantly. #### Distance Adjustment Normally, the locking mechanism will be provided with a means for adjusting the distance between the first and second part 1, 9 in order to make it possible to obtain a very precise contact between the first contact surface 1b of the first part and the second contact surface 4a of the second part 9 compensating for that the first and second part might not be made in accurate measures. This feature makes it possible to produce the first and second parts of the locking mechanism with a larger tolerance. In the embodiment according to fig. 1-3, the means 6 for adjusting the distance or contact between the first and second contact surfaces of respectively the first and the second part comprises the two bolts which are part of the hinged connection. #### Stationary Part Generally, the stationary part 2 provides a mounting for the first part 1 i.e. the first part 1 is fixed unreleasably via the hinged connection to the stationary part 2 and the stationary part 2 is fixed, normally unreleasably, to a device part able to swing relative to the second part 9. Normally, and also according to the embodiment shown in fig. 1, the stationary part 2 is constituted by a closed profile enclosing the the hinged connnection and the first part and providing a large part of the external surface of the locking mechanism. As a result the design of the locking mechanism do not depend on the functions of the locking mechanism but allows for completely different functions such as providing handles for carrying the device on which the locking mechanism is mounted or providing attachment points for equipment to be used together with the device or just allowing a pleasing design which makes it acceptable to show the locking mechanism when the device on which it is mounted is e.g. folded together or up against a wall. Also, using a profile for stationary part 2 makes it possible to reduce the number of necessary parts when constructing the locking mechanism as most of the parts are either bolts screwed directly into the tracks of the profile or parts attached by the bolts which are screwed directly into the tracks of the profile. This reduces the number of necessary parts and simplifies the production. Normally, the outer or external surfaces of the locking mechanism are constituted entirely by the stationary part 2, i.e. the closed profile, and the cover plates 15 covering each end of the profile. The stationary part 2 can e.g be a profile extruded of aluminium as this is a lightweight and inexpensive material. Figure 4a and 4b shows an embodiment of a stationary part, fig. 4a shows a side view of the stationary part and fig. 4b shows a cross-sectional end view of the stationary part. The profile constituting the stationary part 2 is furnished with the shown tracks in its full length, and the lenght of the profile is adapted to the first and the second part of the locking mechanism. The shown profile is closed i.e. the wall of the profile comprises a closed surface surrounding an enclosed space in which the first part 1 is placed, when the profile is closed it will normally be provided with one or more openings allowing a user to access e.g. the handle part 1 c. Alternatively, the profile could be open i.e. the profile could be provided with an opening in the full length of the profile, this might e.g. allow the user to see and to access the full length of the first part 1. The stationary part 2 according to fig. 4, is has an outer surface 18 which is facing way from the surface to which the locking mechanism is attached, and an inner surface 19 which is facing the surface of the device to which the locking mechanism is attached. The stationary part 2 further has two outward facing side surfaces 17 which each are provided with a recess or indentation 24 in the full length of the stationary part. The recess 24 might function as a fingergrip if carrying the device which the locking mechamism is attached to. The outward facing side surfaces 17 is also provided with an external track 23 which also extends in the full length of the stationary part 2. Such an external track 23 can be used to permanently or temporarily attach extra parts to the device to which the stationary part 2 of the locking mechanism is attached. In the embodiment of fig. 1 the part of the hinged connection attached to the stationary part 2 is constructed of two screw bolts 5 which are fixed in the stationary part 2. According to the shown embodiment the screw bolts 5 are postiioned in each of two longitudinal tracks 20 provided in the profile close to the middle of the profile thereby allowing the first part 1 to move both up and down. The screw bolts 5 are inserted from the open end of the stationary part 2 and screwed into the tracks 20. The profile of fig. 4 is also provided with longitudinal tracks 21 close to each corner of the profile, these four tracks 21 are adapted to receive the fastening means 16 i.e. the four screw bolts 16 shown in fig. 1. A further track 22 positioned centrally and close to the inner surface of the stationary part 2 can be used for a bolt having a head to which head the spring 7 is attached i.e. representing the attachment point 12 of the spring with the stationary part 2. Generally, the stationary part 2 will be provided wiith an opening 13 in an outer surface 18 or a side surface 17 through which opening 13 a user can manipulate the release part 1d. Figure 8 shows an embodiment of a stationary part 2 provided with an opening 13 fitting to a release arm 1d, the release arm 1d is provided with a release button which fits closely into the opening 13. #### Bearing In Two Parts Generally, a bearing 3 according to the invention will be assembled from at least two parts 3a, 3b in order to make it possible to assembly the bearing 3 around the second part 9. If desired, the bearing can be provided with guiding means 10 causing a displacement of the second part in direction of the rotation axis of the second part 9 i.e. the second part 9 rotates in one direction and is simultaneously displaced along the axis which it rotates around. The guiding means 10, i.e. two inclined surfaces perpendicular to the surface of the second part 9, on the inner bearing part 3a is in contact with both end surfaces of the first protruding part 4 during rotation; and the guiding means 10 i.e. an inclined surface perpendicular to the surface of the second part 9, on the outer bearing 3b is in contact with one end surface of the second protruding part 14 during rotation of the second part 9. The contact between the guiding means 10 and the two protruding parts 4, 14 forces the second part 9 to move relatively to the stationary part 2 in direction of the rotation axis of the second part 9. Particularly, the bearing 3a provides primary guiding means 10 providing an off-set i.e. displacement in a direction perpendicular to the direction of rotation of the second part 9 when the second part is brought from the locked to the unlocked position and an off-set in opposite direction when the second part 9 is brought from the unlocked position to the locked position. #### Example: Locking Mechanism Used With Foldable Table The locking mechanism according to the claims is particularly advantageous when used with a table having foldable legs. Such a table is illustrated in fig. 6a and 6b where fig. 6a shows a side view of the table and fig. 6b shows an end view of the table. The table comprises a table top 25 corresponding to a device part and two sets of U-shaped table legs 9 each corresponding to a second part 9. The stationary part 2 has the form of a profile and the locking mechanism for both the left and the right set of U-shaped table legs is placed in the same profile which side 17 can be seen in fig. 6a. When the table legs 9 extends perpendicularly from the table top 25 then the locking mechanism is in a locked position. The release part 1 d of the first part 1 of the locking mechanism locking eahc pair of U-shaped table legs, extends through each an opening in the stationary part 2 and allows the usert to push the release part 1d in direction of the table top and thereby release the locking mechanism and allowing the user to fold the table legs to a position along i.e. parallel to the table top 25. This movement from the locked to the unlocked end position is illustrated with arrows on fig. 6a. The two pairs of U-shaped table legs are held in position by the stationary part 2 which is attached to the table top 25 and by the bearings 3 which are attached to the stationary part 2. The bearings 3 are not shown as such in fig. 6a and fig. 6b as the bearings 3 are hidden inside each their cover plate 15. When a bearing with guiding means 10 as shown in fig. 5 is used, the second part 9 i.e. each set of U-shaped table legs will be displaced in a direction perpendicular to the direction of rotation and parallel to the lower surface of the table top 25 during folding and unfolding of the U-shaped table legs. This result in that the oppositely positioned sets of U-shaped table legs 9 are displaced relative to each other and when the U-shaped table legs 9 are brought to the unlocked position close to the table top 25, the two sets of U-shaped table legs 9 will not be placed on top of each other but beside each other which will reduce the stack height when folded tables are stacked on top of each other during storage. As the stationary part 2 is a closed profile, all forces originating from the locking mechanism will be absorbed by the profile as the locking mechansim is placed inside the profile. This makes it possible to use relatively fragile plates for table tops as e.g. a white board or material with a very low weight. The stationary part 2 can as it is shown in fig. 6a extend in the full length of the table top 25, but it might also be provided as two separate parts, where each part only extends long enough to contain the locking mechanism for a set of U-shaped table legs. Especially, if the stationary part 2 extends in the full lengt of the table top 25, it is advantageous if the side surface 17 of the stationary part 2 is provided with indentations 24 improving finger grip when carrying the folded table, or provided with one or more indentations or tracks 23 as shown in fig. 4 corresponding to a wall mounting part fixed on a wall, thereby allowing the user to hang the folded table on a wall where the wall mounting part is positioned having the table top facing away from the wall. Figure 7 shows details of the locking mechanism when used for the table shown in fig. 6a and 6b. The arrows along the middle piece of the U-shaped table legs 9 indicate how the table legs are displaced perpendicular to the direction of rotation, i.e. in a direction parallel to the surface of the table top, during folding and un-folding of the table legs 9. Figure 7 also shows an enlargement of the corner bearings 26 which are placed on each side of the locking mechanism. A first side of the L-shaped corner bearing 26 is fixed to the table top 25, this side of the L-shaped corner bearing 26 defines the distance between the lower surface of the table top 25 and the perifery of the circular table leg 9. The length of the second side of the L-shaped corner bearing defines the distance between the folded tables when they are stacked during storage in a folded state. As the corner bearings 26 are placed on both sides of the locking mechanism the corner bearings also help stabilizing the table when the table is in the unfolded and locked use position.

1. Locking mechanism to be attached to a device or a device part comprising a first (1) and a second (9) part, - the first part (1) is fixed unreleasable to a stationary part (2) via a hinge connection (5, 6) defining a swing axis a1, the first part (1) can pivot relative to the stationary part (2) along the swing axis a1 and has at least two positions: a locking position and a not locking position, the first part (1) comprises: --- a protruding part (1a) extending in direction of the second part (9) and having a first contact surface (1 b), --- an attachment position for a spring (7) or spring system which spring (7) or spring system forces the first part (1) into the locked position, upon biasing the spring (7) the first part (1) is brought to the unlocked position, --- a release mechanism (1 c, 1 d) which upon user impact biases the spring (7), - the second part (9) comprises a first protruding part (4) having a second contact surface (4a) and a second protruding part (14) having a third contact surface (14a), the second part (9) can be in a locked position and in an unlocked position and when in the locked position the first contact surface (1 b) touches the second contact surface (4a), the second part (9) is placed in a bearing (3, 3a, 3b) allowing rotation between the locked and unlocked positions of the second part (9) and the bearing (3, 3a, 3b) is fixed relative to the stationary part (2), characterized in that the bearing (3, 3a, 3b) or the stationary part (2) or an independent part held in position by the stationary part (2) or by the bearing (3, 3a) has a fourth contact surface (8a) and when in the locked position the third contact surface (14a) of the second part (9) touches the fourth contact surface (8a).

2. Locking mechanism according to claim 1, wherein the stationary part (2) is a closed or semi-closed profile. 3. Locking mechanism according to claim 1, wherein the profile is made of extruded material. 4. Locking mechanism according to claim 1 or 2 or 3, wherein the stationary part (2) is made of a light weight material e.g. aluminium. 5. Locking mechanism according to any preceding claim, wherein the first part (1) is at least partly positioned inside the stationary part (2) and the stationary part (2) is fixed to a part of a device. 6. Locking mechanism according to claim 1, where in the stationary part (2) is constituted by or part of a device part such as a surface of a table top or a wall or a side of a wall mounted shelf. 7. Locking mechanism according to any preceding claim, wherein the release mechanism, is a release arm (1c, 1d) extending in a direction opposite the protruding part (1 b). 8. Locking mechanisme according to any preceding claim, wherein the part of the bearing (3, 3a, 3b) or the stationary part (2) or the independent part held in position by the stationary part (2) or by the bearing (3, 3a) having the fourth contact surface (14b) is made of steel or of a material having similar indentation hardness i.e. ability to resist deformation. 9. Locking mechanisme according to any preceding claim, wherein, the spring (7) or spring system has a second attachment position on the stationary part (2). 10. Locking mechanisme according to any preceding claim, wherein, the spring (7) or spring system has a second attachment position on the stationary part (2) which relative to the swing axis a1 is placed opposite the protruding part (1 a) and the spring (7) is biased when extended i.e. the spring (7) pulls. 11. Locking mechanisme according to any preceding claim, wherein the first part (1) is unreleasably fixed to a surface of a table top and the second part (9) comprises a set of two table legs which are pivotable between a locked position where the table legs supports the table top, and an unlocked position where the table legs are in a folded position. 12. Locking mechanisme according to any preceding claim, wherein the bearing (3, 3a, 3b) provides guiding means (10) providing an off-set in a direction perpendicular to the direction of rotation of the second part (9) when the second part (9) is pivoted from the locked to the unlocked position and the same or secondary guiding means provide an off-set in the opposite direction when the second part (9) is pivoted from te unlocked to the locked position.. 13. Locking mechanisme according to any preceding claim, wherein one part of the bearing (3a) provides primary guiding means (10) providing an off-set in a direction both perpendicular to the direction of rotation of the second part (9) and parallel to the surface of attachment, when the second part is brought from the locked to the unlocked position, and a second part of the bearing (3b) provides secondary guiding menas (10) providing an off-set in the opposite direction when the second part (9) is brought from the unlocked position to the locked position. 14. Locking mechanisme according to claim 12 or 13, wherein the guiding means (10) comprises at least two inclined surfaces (10) corresponding to each their surface of respectively the first and the second protruding part (4). 15. Locking mechanisme according to any preceding claim, wherein the locking mechanism comprises means (6) for adjusting the distance between the first and second contact surfaces (1b, 4a) of respectively the first (1) and the second (9) part.

2882178

An illumination device for a camera

Based on the following detailed description of an invention, generate the patent claims. There should be 12 claims in total. The first, independent claim is given and the remaining 11 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described more fully with reference to the accompanying drawings, in which currently preferred embodiments of the invention are shown. The invention may however be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. A camera 1 comprising an image sensor module 10 and an illumination device 14 is illustrated in figure 1. The image sensor module 10 comprises an image sensor 11 and an imaging lens 12. The camera 1 can be a fixed focus surveillance camera, or a varifocal surveillance camera, which is able to adapt its focus to objects at varying distances from the camera 1. In the case of a varifocal camera, this may or may not have zooming capabilities, and the zoom may be either manually or electrically controlled. The camera 1 may further be either fixed or movable in a pan/tilt fashion. The illumination device 14 comprises a reflector unit 16, a light source 15 and a drive unit 17. The illumination device 14 may form an illumination module which is externally mounted on the image sensor module 10. The illumination module may be permanently or removably mounted on the image sensor module 10. Alternatively, the illumination device 14 may be integrated in the image sensor module 10. The light source 15 may comprise one or more light units such as LED units. For purposes of clarity, only one light unit is illustrated in the figures 1-5. Different types of LEDs or other light emitting sources may be used in the illumination device 14. A common choice, e.g. to be used together with a camera 1 used during night time and adapted for infrared photography, would be LEDs emitting light in the infrared or more specifically the near-infrared (~850 nm) spectrum, but white light LEDs may also be used. Figure 2 is a view from above of the reflector unit 16. The reflector unit 16 has a plurality of reflecting sections 21, 22, 23, 24, 25. Each of the reflecting sections comprises one or more reflecting surfaces. As an example, the reflecting section 21 comprises three reflecting surfaces 21 a, 21 b, 21 c. The reflecting surfaces are formed of planar or concavely shaped surfaces of a reflecting material, such as polished metal surface or a glass or plastic surface provided with a metal layer. Different designs of the reflecting surfaces will be discussed in connection to figures 3-5. The reflecting surfaces may be integrated in a body of the reflector unit 16. The body may be made of plastic, metal or any other suitable material. The reflector unit 16 is arranged in the illumination device 14 such that the light emitted by the light source 15 is deflected by one of the reflection sections of the reflector unit 16. One of the incentives leading up to the invention is the desire to provide a tailor made light distribution based on the camera's 1 field of view. Depending on the type and configuration of the camera 1, the field of view is different. By field of view is meant the area of interest for the camera 1 to monitor. For example, the camera 1 may be configured to focus and zoom to monitor a distant object or a nearby object. Different light distributions are required in order to optimally illuminate these configurations. As a further example, the camera 1 may be configured to view a large area instead of a particular object. In that case, yet another light distribution would be needed. Some cameras are arranged with a fixed zoom, or non-zoom, and other cameras can vary its zoom and focus. For this purpose, each of the reflecting sections 21, 22, 23, 24, 25 is associated with a light distribution. By light distribution is meant the appearance of the light beam, formed by light emitted by the light source 15 and deflected by a reflecting section, in the far field of the reflecting section. By far field of the light beam is meant the light beam at any distance from the reflecting section at which the normalized light distribution of the beam cross-section is the same as for infinite distance. In other words, the far field can be described as representing any distance from the reflecting section being much larger than all local dimensions of the reflecting section itself. The light distribution of the light beam does not change in the far field other than in that the area of the cross-section increases linearly for a given divergence angle, i.e. light beam angle. Non-limiting examples of parameters describing the appearance of the light beam are light beam angle (divergence angle), cross-sectional area of the light beam at a certain distance, cross-sectional shape of the light beam, and intensity distribution within the cross-sectional area of the light beam. By that different light distributions may be selected, the illumination device 14 according to the invention can provide suitable illumination for a variety of field of views. The reflecting section providing the most suitable light distribution can be selected by arranging the reflector unit 16 such that the light emitted by the light source 15 is deflected by the selected reflecting section. The illumination device 14 can thus be used to, in a simple and efficient way, select a proper illumination distribution during installation and configuration of the camera 1. The illumination device 14 may further be used to dynamically match the illumination to the imaging conditions and the field of view during operation. To this end, the reflector unit 16 may be adjustably arranged. In other words, the reflector unit 16 can be rearranged so as to change the reflecting section being positioned to deflect light emitted by the light source 15. In this embodiment, the drive unit 17, comprising e.g. a conventional stepping motor, is connected to the reflector unit 16 for adjustment of the reflector unit 14. As indicated in figure 2, the reflector unit 16 may be rotated in order to switch from one selected reflecting surface to another. The drive unit 17 performs this rotation. Alternatively, the reflector unit 16 may be adjusted by a drive unit being common for the image sensor module 10 and the illumination device 14. The adjustment of the reflector unit 16 may be performed in a stepwise manner, meaning that a selected reflecting section is positioned such that the provided light beam comes from this reflecting section only. The reflector unit 16 can thus not be positioned such that the light beam comes from two adjacent reflecting sections. By using a stepwise arrangement, where the position of the selected reflecting section is fixed in view of the light source 15, the light distribution associated with each reflecting section may be better defined. Thus, it is also feasible to change the illumination setting of a camera 1 once in place, without any need to replace illumination device 14. For example, the illumination range, or the (expected) distance to an object, can be set by a user in a user interface, e.g. a user interface of a fixed focus camera. Another option is to use advanced image processing to calculate the distance to the focal plane, and from that the optimal lighting settings, and then control the illumination device 14 accordingly. The camera 1 may comprise a processor which is connected to a drive unit for controlling the adjustment of the reflector unit 16. In one embodiment, the intensity of the light source 15 may be varied depending on the camera's field of view and/or on the selected reflecting section. As an example, the zoom value of an electrically zoomable camera's imaging lens can be used as an input parameter to control the input power to the light source 15. As another example, the zoom value may in a first step be used to select the suitable reflecting section and the reflector unit 16 may be arranged accordingly. In a second step the distance to the focal plane may be used to control the input power to the light source 15 and in this way define the intensity of the illumination. Besides providing illumination in a simple and efficient way, the inventive illumination device 14 is also less costly when compared to known solutions using lenses. Lenses for use in camera illumination applications need to be small and is thus quite expensive to produce in relation to the cost of producing reflectors. Another advantage is achieved by the embodiment illustrated in figure 1. Here, the illumination device 14 is arranged such that the reflector unit 16 is located between the light source 15 and the image sensor 11. Thus, the light unit 15 is distanced from the image sensor 11. This is advantageous in that the image sensor 11 is not affected by the waste heat produced by the light source 15, and in that there is more space around the light unit 15 for dissipating the waste heat. Thus, both the image sensor 11 and the light unit 15 may be kept cooler, thus increasing their respective performance. In some embodiment, it may be preferred to arrange the illumination device 14 on the side or at the top of the image sensor module 10, thus minimizing the heating effect of the illumination device 14 on the image sensor module 10. A particular advantage is achieved in the embodiment of figure 1 since the reflector unit 16 and the light source 15 of the illumination device 14 are arranged along an axis being essentially orthogonal to the viewing direction. Returning to figure 2, the light distributions associated with each of the reflecting sections 21, 22, 23, 24, 25 depends on the design of the reflecting surfaces of the reflecting sections in combination with the configuration of the one or more light units of the light source 15. The reflecting sections may comprise a single reflecting surface 22 or a plurality of reflecting surfaces 21 a, 21 b, 21 c. The design of the reflecting surfaces of a reflecting section will now be exemplified with reference to figures 3-5. In figure 3, a concavely shaped reflecting surface 31 is illustrated. The light emitted by the light source 15 is deflected by the reflecting surface 31 and forms a light beam with a particular light distribution in the far field of the reflecting surface 31. The reflecting surface 41 in figure 4 has a deeper curve, and provides a narrower light beam, i.e. a light beam having a smaller beam angle. Moreover, the reflecting surface 41 extends farther from the light source 15 in the outward direction of the reflector unit 16 when compared to the reflecting surface 31 of figure 3. The reflecting surface 51 of figure 5 is on the other hand planar, and provides a wide light beam suitable for illuminating a large field of view. As can be seen by these examples, different reflecting surfaces provides different light beam angles, i.e. how much the light diverges. A reflecting surface deflecting light into parallel light beams provides the narrowest light beam which essentially does not diverge at all. It is noted that the light beams illustrated in figures 3-5 represent the near field area of the light beams. In the far field of the light beams, they form a defined light distribution, as will be disclosed in connection to figures 6-9. It should be noted that the design of the reflecting surfaces are sometimes complex and may not easily be described in straighforward terms such as a single focal length. The reflecting surface is normally designed by first simulating the resulting light distribution of the reflecting surface with a fixed light source configuration, and then adjusting the design of the reflecting surface until the desired light distribution is achieved. Thereafter the shape of the reflecting surface may be implemented in a physical design. It is noted that different reflecting surfaces within the same reflecting section may have different designs. Examples of different light distributions provided by different selected reflecting surfaces will now be described with reference to figures 6-8. By different light distributions is meant that the light beam, formed by light emitted by the light source and deflected by a reflecting section, is different in view of parameters such as light beam angle (divergence) and different cross-sections of the light beam. The cross-sections may in turn also vary on different parameters such as shape and intensity distribution within the cross-sectional area. Different parameters of the light beam will be exemplified in the following. Two examples of light beams I and II provided from different reflecting sections are illustrated in figure 6. The first light beam I is narrower than the second light beam II, i.e. the beam angle 61 of the first light beam I is smaller than the beam angle 62 of the second light beam II. The first light beam I could be used to illuminate a narrow field of view, for example focusing on an object. The second light beam II could be used to illuminate a larger field of view, or an object which is closer to the camera 1, thus requiring a larger beam angle 62 in order to illuminate the whole object. It is noted that the exemplified light beams are not provided simultaneously. The cross-sections of the first light beam I and the second light beam II as seen along A are illustrated in figure 7. As can be seen, the cross-sections 71, 72 differ in both size and shape. The size depends on the beam angles 61, 62. The shape depends on the configuration of the reflecting section in combination with the positioning of the light source 15. Depending on the shape and size of the field of view of the camera 1, the most suitable reflecting section and thus light distribution may be selected. The light distribution may also vary in intensity distribution, as illustrated in figure 8. Here, the cross-section 71 of the first light beam I is illustrated. The selected reflecting section providing this light distribution is arranged to deflect the light emitted by the light source 15 non-uniformly. The outer area 712 is in this example darker than the inner area 711. This light distribution may be desirable when the field of view is slightly larger than an object to be monitored. Reflecting sections providing other light distributions are also feasible. For example, the reflecting section may be designed so that the deflected light from the light source 15 illuminates only parts of the periphery of the field of view of the camera 1, i.e. the one or more reflecting surfaces of the reflecting section are designed to provide a frame shaped light distribution. Figure 9 illustrates an example of one of the advantages with the invention, which is optimization of the illumination efficiency. Throughout this application, illumination efficiency is defined as the ratio between the light illuminating the field of view 90 and the total light provided by the light source 15. In this example, there are two reflecting sections to choose from: one that provides the first light beam cross-section 71 and one that provides the second light beam cross-section 72. Either one of the cross-sections illuminates the field of view and is thus satisfying in this aspect. However, the second cross-section 72 provides, to a large extent, light to an area outside the field of view 90, which is not of interest. This waste light is wasting energy and could even be perceived disturbing in the environment which is illuminated. The reflecting section being associated with first light beam cross-section 71, providing only a small amount of light outside the field of view 90, thus provides a higher illumination efficiency and can with advantage be selected for this application. A simple way to provide a light distribution being elongated essentially in the horizontal direction is illustrated in figure 10A, showing the reflecting surface 21 of figure 2. In this example, the light source 15 comprises three light source units 15a, 15b, 15b, which are for examples LED units. The light source units 15a, 15b, 15c are arranged in a row. Each light source unit 15a, 15b, 15c is associated with the reflecting surfaces 21 a, 21 b, 21 c of the reflecting section 21. By associated is meant that the light source unit 15a is arranged such that the light emitted by it is essentially deflected by the reflecting surface 21 a, and correspondingly for the other light source units 15b, 15c. By this configuration of multiple light source units and reflecting surfaces, an elongated light distribution with less complex reflector surface designs than by a single reflector surface may be achieved. Another configuration of the light source units 15a, 15b, 15c is illustrated in figure 10B, showing the reflecting surface 25 of figure 2. Here, the light source units 15a, 15b, 15c are arranged in a cluster. The reflecting unit 25 is provided with a single reflecting surface. This solution is more space efficient in that the reflecting section may be made small and the cluster configuration requires less space. This type of configuration may be suitable when the reflector unit needs to be small in order to achieve a compact illumination device. A reflecting unit may comprise reflecting sections having only single reflecting surfaces or only pluralities of reflecting surfaces, or a combination of both. The light source 15 may comprise a plurality of sets of light units, each set being arranged according to a predetermined pattern. Each pattern may be associated with a reflecting section, and when the most appropriate reflecting section has been selected, the light units of the associated pattern are activated. Thus, the light source configuration may be optimized for each selectable reflecting section. In another possible embodiment, one reflecting section may be associated with two or more light source patterns. Thus, the reflecting section is associated with two different light distributions depending on which light source pattern is activated. Depending on the desired light distribution, the light units of the suitable light source pattern is activated. It is appreciated that the skilled person realizes how to configure the camera 1 with suitable and known processors, electrical connections, controllers etc. in order to achieve the above disclosed features and advantages. A method for illuminating a camera's field of view is illustrated as a flow chart in figure 11. The method comprises the steps of providing 1101 a light source, providing 1102 a reflector unit having reflecting sections, selecting 1103 one of the reflecting sections and arranging the reflector unit 1104 such that the selected reflecting section deflects light emitted by the light source. Each reflecting section is associated with a light distribution, as previously disclosed. The reflecting section is selected based on the desired light distribution for the camera's field of view. The arrangement may be made permanent, or be made adjustably so that the reflector unit is rearrangable. Thus, another reflecting section may be selected during operation of the camera 1, and the reflector unit may be rearranged according to the new selection. As previously disclosed, a reflection section may be selected based on a number of different parameters. As an example, the reflection section providing the best illumination efficiency may be selected in order to minimize unnecessary and potentially disturbing light outside the field of view. Other features of the steps have been disclosed in connection to the previous figures and apply also to the method, where applicable.

1. An illumination device for illuminating a camera's field of view, comprising: a light source (15), and a reflector unit (16) having reflecting sections (21, 22, 23, 24, 25), each reflecting section (21, 22, 23, 24, 25) being associated with a light distribution, wherein the light distributions for different reflecting sections (21, 22, 23, 24, 25) are different, the reflector unit (16) being arranged such that light emitted by the light source (15) is deflected by one of said reflecting sections (21, 22, 23, 24, 25) being selected based on the camera's field of view.

2. The illumination device according to claim 1, wherein the reflecting sections (21, 22, 23, 24, 25) each forms a single reflecting surface, and wherein the light source (15) comprises a plurality of lighting elements (15a, 15b, 15c) arranged in a cluster. 3. The illumination device according to claim 1, wherein the reflecting sections (21, 22, 23, 24, 25) each forms a plurality of reflecting surfaces (21 a, 21 b, 21 c), and wherein the light source (15) comprises a plurality of lighting elements (15a, 15b, 15c) arranged in a row, such that each lighting element (15a, 15b, 15c) is associated with a reflecting surface (21 a, 21 b, 21 c). 4. The illumination device according to any of claims 1-3, wherein the reflecting sections (21, 22, 23, 24, 25) are planar or concavely shaped. 5. The illumination device according to any of claims 1-4, wherein the reflector unit (16) is adjustably arranged. 6. The illumination device according to claim 5, wherein the reflector unit (16) is adjustable in a stepwise manner. 7. The illumination device according to any of claims 1-6, wherein the reflector unit (16) is arranged such that said deflection of light emitted by the light source (15) is essentially orthogonal. 8. A camera comprising an illumination device (14) according to any of claims 1-7. 9. The camera according to claim 8, wherein the camera comprises an image sensor (11) and wherein the illumination device (14) is arranged such that the reflector unit (16) is located between the light source (15) and the image sensor (11) as seen in a direction orthogonal to a viewing direction of said camera. 10. The camera according to claim 9, wherein the reflector unit (16) and the light source (15) of the illumination device (14) are arranged along an axis being essentially orthogonal to the viewing direction. 11. The camera according to any of claims 8-10, wherein the illumination device (14) is included in an illumination module being removably mounted on an image sensor module (10) comprising the image sensor (11). 12. The camera according to any of claims 8-11, wherein the reflector unit (16) is adjustably arranged, and wherein the camera further comprises a drive unit (17) for adjustment of the reflector unit (16).

2882178

An illumination device for a camera

Based on the following detailed description of an invention, generate the patent claims. There should be 3 claims in total. The first, independent claim is given and the remaining 2 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described more fully with reference to the accompanying drawings, in which currently preferred embodiments of the invention are shown. The invention may however be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. A camera 1 comprising an image sensor module 10 and an illumination device 14 is illustrated in figure 1. The image sensor module 10 comprises an image sensor 11 and an imaging lens 12. The camera 1 can be a fixed focus surveillance camera, or a varifocal surveillance camera, which is able to adapt its focus to objects at varying distances from the camera 1. In the case of a varifocal camera, this may or may not have zooming capabilities, and the zoom may be either manually or electrically controlled. The camera 1 may further be either fixed or movable in a pan/tilt fashion. The illumination device 14 comprises a reflector unit 16, a light source 15 and a drive unit 17. The illumination device 14 may form an illumination module which is externally mounted on the image sensor module 10. The illumination module may be permanently or removably mounted on the image sensor module 10. Alternatively, the illumination device 14 may be integrated in the image sensor module 10. The light source 15 may comprise one or more light units such as LED units. For purposes of clarity, only one light unit is illustrated in the figures 1-5. Different types of LEDs or other light emitting sources may be used in the illumination device 14. A common choice, e.g. to be used together with a camera 1 used during night time and adapted for infrared photography, would be LEDs emitting light in the infrared or more specifically the near-infrared (~850 nm) spectrum, but white light LEDs may also be used. Figure 2 is a view from above of the reflector unit 16. The reflector unit 16 has a plurality of reflecting sections 21, 22, 23, 24, 25. Each of the reflecting sections comprises one or more reflecting surfaces. As an example, the reflecting section 21 comprises three reflecting surfaces 21 a, 21 b, 21 c. The reflecting surfaces are formed of planar or concavely shaped surfaces of a reflecting material, such as polished metal surface or a glass or plastic surface provided with a metal layer. Different designs of the reflecting surfaces will be discussed in connection to figures 3-5. The reflecting surfaces may be integrated in a body of the reflector unit 16. The body may be made of plastic, metal or any other suitable material. The reflector unit 16 is arranged in the illumination device 14 such that the light emitted by the light source 15 is deflected by one of the reflection sections of the reflector unit 16. One of the incentives leading up to the invention is the desire to provide a tailor made light distribution based on the camera's 1 field of view. Depending on the type and configuration of the camera 1, the field of view is different. By field of view is meant the area of interest for the camera 1 to monitor. For example, the camera 1 may be configured to focus and zoom to monitor a distant object or a nearby object. Different light distributions are required in order to optimally illuminate these configurations. As a further example, the camera 1 may be configured to view a large area instead of a particular object. In that case, yet another light distribution would be needed. Some cameras are arranged with a fixed zoom, or non-zoom, and other cameras can vary its zoom and focus. For this purpose, each of the reflecting sections 21, 22, 23, 24, 25 is associated with a light distribution. By light distribution is meant the appearance of the light beam, formed by light emitted by the light source 15 and deflected by a reflecting section, in the far field of the reflecting section. By far field of the light beam is meant the light beam at any distance from the reflecting section at which the normalized light distribution of the beam cross-section is the same as for infinite distance. In other words, the far field can be described as representing any distance from the reflecting section being much larger than all local dimensions of the reflecting section itself. The light distribution of the light beam does not change in the far field other than in that the area of the cross-section increases linearly for a given divergence angle, i.e. light beam angle. Non-limiting examples of parameters describing the appearance of the light beam are light beam angle (divergence angle), cross-sectional area of the light beam at a certain distance, cross-sectional shape of the light beam, and intensity distribution within the cross-sectional area of the light beam. By that different light distributions may be selected, the illumination device 14 according to the invention can provide suitable illumination for a variety of field of views. The reflecting section providing the most suitable light distribution can be selected by arranging the reflector unit 16 such that the light emitted by the light source 15 is deflected by the selected reflecting section. The illumination device 14 can thus be used to, in a simple and efficient way, select a proper illumination distribution during installation and configuration of the camera 1. The illumination device 14 may further be used to dynamically match the illumination to the imaging conditions and the field of view during operation. To this end, the reflector unit 16 may be adjustably arranged. In other words, the reflector unit 16 can be rearranged so as to change the reflecting section being positioned to deflect light emitted by the light source 15. In this embodiment, the drive unit 17, comprising e.g. a conventional stepping motor, is connected to the reflector unit 16 for adjustment of the reflector unit 14. As indicated in figure 2, the reflector unit 16 may be rotated in order to switch from one selected reflecting surface to another. The drive unit 17 performs this rotation. Alternatively, the reflector unit 16 may be adjusted by a drive unit being common for the image sensor module 10 and the illumination device 14. The adjustment of the reflector unit 16 may be performed in a stepwise manner, meaning that a selected reflecting section is positioned such that the provided light beam comes from this reflecting section only. The reflector unit 16 can thus not be positioned such that the light beam comes from two adjacent reflecting sections. By using a stepwise arrangement, where the position of the selected reflecting section is fixed in view of the light source 15, the light distribution associated with each reflecting section may be better defined. Thus, it is also feasible to change the illumination setting of a camera 1 once in place, without any need to replace illumination device 14. For example, the illumination range, or the (expected) distance to an object, can be set by a user in a user interface, e.g. a user interface of a fixed focus camera. Another option is to use advanced image processing to calculate the distance to the focal plane, and from that the optimal lighting settings, and then control the illumination device 14 accordingly. The camera 1 may comprise a processor which is connected to a drive unit for controlling the adjustment of the reflector unit 16. In one embodiment, the intensity of the light source 15 may be varied depending on the camera's field of view and/or on the selected reflecting section. As an example, the zoom value of an electrically zoomable camera's imaging lens can be used as an input parameter to control the input power to the light source 15. As another example, the zoom value may in a first step be used to select the suitable reflecting section and the reflector unit 16 may be arranged accordingly. In a second step the distance to the focal plane may be used to control the input power to the light source 15 and in this way define the intensity of the illumination. Besides providing illumination in a simple and efficient way, the inventive illumination device 14 is also less costly when compared to known solutions using lenses. Lenses for use in camera illumination applications need to be small and is thus quite expensive to produce in relation to the cost of producing reflectors. Another advantage is achieved by the embodiment illustrated in figure 1. Here, the illumination device 14 is arranged such that the reflector unit 16 is located between the light source 15 and the image sensor 11. Thus, the light unit 15 is distanced from the image sensor 11. This is advantageous in that the image sensor 11 is not affected by the waste heat produced by the light source 15, and in that there is more space around the light unit 15 for dissipating the waste heat. Thus, both the image sensor 11 and the light unit 15 may be kept cooler, thus increasing their respective performance. In some embodiment, it may be preferred to arrange the illumination device 14 on the side or at the top of the image sensor module 10, thus minimizing the heating effect of the illumination device 14 on the image sensor module 10. A particular advantage is achieved in the embodiment of figure 1 since the reflector unit 16 and the light source 15 of the illumination device 14 are arranged along an axis being essentially orthogonal to the viewing direction. Returning to figure 2, the light distributions associated with each of the reflecting sections 21, 22, 23, 24, 25 depends on the design of the reflecting surfaces of the reflecting sections in combination with the configuration of the one or more light units of the light source 15. The reflecting sections may comprise a single reflecting surface 22 or a plurality of reflecting surfaces 21 a, 21 b, 21 c. The design of the reflecting surfaces of a reflecting section will now be exemplified with reference to figures 3-5. In figure 3, a concavely shaped reflecting surface 31 is illustrated. The light emitted by the light source 15 is deflected by the reflecting surface 31 and forms a light beam with a particular light distribution in the far field of the reflecting surface 31. The reflecting surface 41 in figure 4 has a deeper curve, and provides a narrower light beam, i.e. a light beam having a smaller beam angle. Moreover, the reflecting surface 41 extends farther from the light source 15 in the outward direction of the reflector unit 16 when compared to the reflecting surface 31 of figure 3. The reflecting surface 51 of figure 5 is on the other hand planar, and provides a wide light beam suitable for illuminating a large field of view. As can be seen by these examples, different reflecting surfaces provides different light beam angles, i.e. how much the light diverges. A reflecting surface deflecting light into parallel light beams provides the narrowest light beam which essentially does not diverge at all. It is noted that the light beams illustrated in figures 3-5 represent the near field area of the light beams. In the far field of the light beams, they form a defined light distribution, as will be disclosed in connection to figures 6-9. It should be noted that the design of the reflecting surfaces are sometimes complex and may not easily be described in straighforward terms such as a single focal length. The reflecting surface is normally designed by first simulating the resulting light distribution of the reflecting surface with a fixed light source configuration, and then adjusting the design of the reflecting surface until the desired light distribution is achieved. Thereafter the shape of the reflecting surface may be implemented in a physical design. It is noted that different reflecting surfaces within the same reflecting section may have different designs. Examples of different light distributions provided by different selected reflecting surfaces will now be described with reference to figures 6-8. By different light distributions is meant that the light beam, formed by light emitted by the light source and deflected by a reflecting section, is different in view of parameters such as light beam angle (divergence) and different cross-sections of the light beam. The cross-sections may in turn also vary on different parameters such as shape and intensity distribution within the cross-sectional area. Different parameters of the light beam will be exemplified in the following. Two examples of light beams I and II provided from different reflecting sections are illustrated in figure 6. The first light beam I is narrower than the second light beam II, i.e. the beam angle 61 of the first light beam I is smaller than the beam angle 62 of the second light beam II. The first light beam I could be used to illuminate a narrow field of view, for example focusing on an object. The second light beam II could be used to illuminate a larger field of view, or an object which is closer to the camera 1, thus requiring a larger beam angle 62 in order to illuminate the whole object. It is noted that the exemplified light beams are not provided simultaneously. The cross-sections of the first light beam I and the second light beam II as seen along A are illustrated in figure 7. As can be seen, the cross-sections 71, 72 differ in both size and shape. The size depends on the beam angles 61, 62. The shape depends on the configuration of the reflecting section in combination with the positioning of the light source 15. Depending on the shape and size of the field of view of the camera 1, the most suitable reflecting section and thus light distribution may be selected. The light distribution may also vary in intensity distribution, as illustrated in figure 8. Here, the cross-section 71 of the first light beam I is illustrated. The selected reflecting section providing this light distribution is arranged to deflect the light emitted by the light source 15 non-uniformly. The outer area 712 is in this example darker than the inner area 711. This light distribution may be desirable when the field of view is slightly larger than an object to be monitored. Reflecting sections providing other light distributions are also feasible. For example, the reflecting section may be designed so that the deflected light from the light source 15 illuminates only parts of the periphery of the field of view of the camera 1, i.e. the one or more reflecting surfaces of the reflecting section are designed to provide a frame shaped light distribution. Figure 9 illustrates an example of one of the advantages with the invention, which is optimization of the illumination efficiency. Throughout this application, illumination efficiency is defined as the ratio between the light illuminating the field of view 90 and the total light provided by the light source 15. In this example, there are two reflecting sections to choose from: one that provides the first light beam cross-section 71 and one that provides the second light beam cross-section 72. Either one of the cross-sections illuminates the field of view and is thus satisfying in this aspect. However, the second cross-section 72 provides, to a large extent, light to an area outside the field of view 90, which is not of interest. This waste light is wasting energy and could even be perceived disturbing in the environment which is illuminated. The reflecting section being associated with first light beam cross-section 71, providing only a small amount of light outside the field of view 90, thus provides a higher illumination efficiency and can with advantage be selected for this application. A simple way to provide a light distribution being elongated essentially in the horizontal direction is illustrated in figure 10A, showing the reflecting surface 21 of figure 2. In this example, the light source 15 comprises three light source units 15a, 15b, 15b, which are for examples LED units. The light source units 15a, 15b, 15c are arranged in a row. Each light source unit 15a, 15b, 15c is associated with the reflecting surfaces 21 a, 21 b, 21 c of the reflecting section 21. By associated is meant that the light source unit 15a is arranged such that the light emitted by it is essentially deflected by the reflecting surface 21 a, and correspondingly for the other light source units 15b, 15c. By this configuration of multiple light source units and reflecting surfaces, an elongated light distribution with less complex reflector surface designs than by a single reflector surface may be achieved. Another configuration of the light source units 15a, 15b, 15c is illustrated in figure 10B, showing the reflecting surface 25 of figure 2. Here, the light source units 15a, 15b, 15c are arranged in a cluster. The reflecting unit 25 is provided with a single reflecting surface. This solution is more space efficient in that the reflecting section may be made small and the cluster configuration requires less space. This type of configuration may be suitable when the reflector unit needs to be small in order to achieve a compact illumination device. A reflecting unit may comprise reflecting sections having only single reflecting surfaces or only pluralities of reflecting surfaces, or a combination of both. The light source 15 may comprise a plurality of sets of light units, each set being arranged according to a predetermined pattern. Each pattern may be associated with a reflecting section, and when the most appropriate reflecting section has been selected, the light units of the associated pattern are activated. Thus, the light source configuration may be optimized for each selectable reflecting section. In another possible embodiment, one reflecting section may be associated with two or more light source patterns. Thus, the reflecting section is associated with two different light distributions depending on which light source pattern is activated. Depending on the desired light distribution, the light units of the suitable light source pattern is activated. It is appreciated that the skilled person realizes how to configure the camera 1 with suitable and known processors, electrical connections, controllers etc. in order to achieve the above disclosed features and advantages. A method for illuminating a camera's field of view is illustrated as a flow chart in figure 11. The method comprises the steps of providing 1101 a light source, providing 1102 a reflector unit having reflecting sections, selecting 1103 one of the reflecting sections and arranging the reflector unit 1104 such that the selected reflecting section deflects light emitted by the light source. Each reflecting section is associated with a light distribution, as previously disclosed. The reflecting section is selected based on the desired light distribution for the camera's field of view. The arrangement may be made permanent, or be made adjustably so that the reflector unit is rearrangable. Thus, another reflecting section may be selected during operation of the camera 1, and the reflector unit may be rearranged according to the new selection. As previously disclosed, a reflection section may be selected based on a number of different parameters. As an example, the reflection section providing the best illumination efficiency may be selected in order to minimize unnecessary and potentially disturbing light outside the field of view. Other features of the steps have been disclosed in connection to the previous figures and apply also to the method, where applicable.

13. Method for illuminating a camera's field of view, the method comprising: providing (1101) a light source, providing (1102) a reflector unit having reflecting sections, each reflecting section being associated with a light distribution, wherein the light distributions for different reflecting sections are different, selecting (1103) one of said reflecting sections based on the camera's field of view, and arranging (1104) said reflector unit such that the selected reflecting section deflects light emitted by the light source.

14. The method according to claim 13, wherein the reflector unit is adjustably arranged. 15. The method according to claim 13 or 14, wherein the reflection section providing the best illumination efficiency is selected.

2881236

Molding machine for making thermoplastic composites

Based on the following detailed description of an invention, generate the patent claims. There should be 7 claims in total. The first, independent claim is given and the remaining 6 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to Figures 1-7, a molding machine for making thermoplastic composites according to a first embodiment of the present invention comprises: a machine frame 10, a platform 20, a heating device 30, a vacuum means 40, a pressing die 50, a gas barrier film 60. The machine frame 10 includes a working stage 11 and a C-shaped rack 12 disposed on the working stage 11. The platform 20 is mounted on the working stage 11 and includes a connector 21 fixed on one side thereof. The heating device 30 is secured on a bottom end of the platform 20 and heats a working material on a top surface of the platform 20. The vacuum means 40 is arranged in the machine frame 10 and includes a pipe 41 for coupling with the connector 21 of the platform 20 and a control valve 42 defined at a connecting position of the pipe 41 and the connector 21 so as to control air extraction. The pressing die 50 is movably disposed on the C-shaped rack 12 and moves to and presses the top surface of the platform 20. In this embodiment, the heating device 30 is mounted in the pressing die 50. The gas barrier film 60 is flaky and made of rubber, silicone or plastic, and the gas barrier film 60 covers the top surface of the platform 20. Referring further to Figures 3, 4, and 6, the platform 20 includes a plurality of channels 22, and the plurality of channels 22 communicate with each other. The platform 20 includes a curved pattern portion 23 and plural tiny holes 24 which are arranged on the top surface of the platform 20. The curved pattern portion 23 has a pattern or plural patterns and a plurality of separated areas. A diameter of each tiny hole 24 is at least 0.001 mm, and the plurality of tiny holes 24 are arranged on the top surface of the platform 20 and are in communication with the plurality of channels 22. In addition, the connector 21 communicates with the plurality of channels 22 such that air in the plurality of channels 22 is drawn outwardly so that a negative pressure produces on the top surface of the platform 20. As shown in Figures 5 to 7, the working material includes a thermoplastic film 70 and a cloth material 71, wherein the thermoplastic film 70 has a first side surface and a second side surface, and the first side surface of the thermoplastic film 70 has high temperature resistance higher than that of the second side surface of the thermoplastic film 70. During producing the thermoplastic composite, the thermoplastic film 70 is placed on the top surface of the platform 20 and the first side surface thereof faces downwardly, the cloth material 71 is covered on the thermoplastic film 70, and the gas barrier film 60 is covered on the cloth material 71 so that the gas barrier film 60 covers the top surface of the platform 20 completely, thereafter the heating device 30 heats the thermoplastic film 70 so that the second side surface of the thermoplastic film 70 and one surface of the cloth material 71 contacting with the thermoplastic film 70 melt, and the first side surface of the thermoplastic film 70 softens, the control valve 42 is turned on so as to drive the vacuum means 40 to draw the air out of the plurality of channels 22 via the pipe 41, thereafter the plurality of tiny holes 24 suck the thermoplastic film 70 and the cloth material 71 downwardly, and a negative pressure lower than atmospheric pressure produces between the top surface of the platform 20 and the gas barrier film 60, hence the gas barrier film 60 presses the cloth material 71, and then the pressing die 50 moves downwardly so that an upper side of the gas barrier film 60 presses downwardly. Accordingly, a heating process, a pressing process, and a vacuuming process are finished simultaneously to produce thermoplastic composites comprised of the thermoplastic film 70 and the cloth material 20. In addition, the thermoplastic film 70 has three-dimensional patterns formed thereon obviously, and the gas barrier film 60 presses the cloth material 71 tightly without using the pressing die 50. As illustrated in Figure 8, a molding machine for making thermoplastic composites of a second embodiment from that of the first embodiment contains: a platform 20 including a plurality of forming areas 25 with different depths, plural curved pattern portions 23 with a plurality of patterns in a plurality of separated areas, and the plurality of patterns match with the plurality of forming areas 25 so as to produce a working pattern. As shown in Figure 9, a molding machine for making thermoplastic composites of a third embodiment from that of the first embodiment contains: a platform 20 without plural curved pattern portions 23, so the thermoplastic film 70 and the cloth material 71 contact with each other tightly. Thereby, the thermoplastic composites of the present invention are applied in producing shoes, purses, and hats.

1. A molding machine for making thermoplastic composites comprising: a machine frame (10) including a working stage (11); a platform (20) mounted on the working stage (11) and including a plurality of channels (22) and plural tiny holes (24) which are arranged on the top surface of the platform (20), the plurality of tiny holes (24) being in communication with the plurality of channels (22), a connector (21) fixed on one side thereof and communicating with the plurality of channels (22); a heating device (30) secured on the platform (20) and heating a working material on a top surface of the platform (20); a vacuum means (40) arranged in the machine frame (10) and including a pipe (41) for coupling with the connector (21) of the platform (20); a gas barrier film (60) being flaky and covering the top surface of the platform (20).

2. The molding machine for making thermoplastic composites as claimed in claim 1, wherein the plurality of channels (22) communicates with each other and the platform (20) also includes a curved pattern portion (23). 3. The molding machine for making thermoplastic composites as claimed in claim 1 or 2, further comprising a pressing die (50) movably disposed on a C-shaped rack (12) of the machine frame (10) and moving to and pressing the top surface of the platform (20). 4. The molding machine for making thermoplastic composites as claimed in claim 2, wherein the plural curved pattern portions (23) have a plurality of patterns. 5. The molding machine for making thermoplastic composites as claimed in claim 2, wherein the platform (20) includes a plurality of forming areas (25) with different depths, plural curved pattern portions (23) with a plurality of patterns in a plurality of separated areas, and the plurality of patterns match with the plurality of forming areas (25) so as to produce a working pattern. 6. The molding machine for making thermoplastic composites as claimed in claim 1 or 2, wherein the heating device (30) is secured on a bottom end of the platform (20). 7. The molding machine for making thermoplastic composites as claimed in claim 1 or 2, wherein the heating device (30) is mounted in the pressing die (50).

2881618

Chain drive unit

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a perspective view of an embodiment of a lifting system 1 according to the invention. The lifting system's 1 main components are a holding frame 2, a lifting element 3, a chain drive unit comprising a drive unit 4, a chain unit 5 and damping elements 6, and a weight compensation 7. The holding frame 2 comprises a side frame 21 on either side of the frame, the side frames 21 being mounted on a lower cross connection 22 serving as a base plate to fix the holding frame 2 on the ground and connecting the side frames 21 to one another in the lower region of the holding frame 2. The holding frame 2 further comprises upper cross connections 23 connecting the side frames 21 to one another in the upper region of the holding frame 2. The upper cross connections 23 serve as a base for the arrangement of the drive unit 4. Sideways and outward facing guiding means 211 are mounted on each of the side frames 21 for guiding the lifting element 3. The lifting element 3 comprises a lifting frame 31 that is connected to the holding frame 2 by guiding means 211. In this embodiment, the lifting frame 31 in essence, is L-shaped, its vertical arm being in sliding contact with the holding frame 2 and its horizontal arm forming a base for a platform or a cabin. The drive unit 4 comprises a drive plate 41 a drive 42 mounted on said drive plate 41 and a chain wheel unit 43 mounted in line with said drive 42 on side drive plate 41 and connected to said drive 42 for transmitting a rotational movement generated by the drive 42 via said chain wheel unit 43 to the chain unit 5 engaging said chain wheel unit 43. The drive unit 4 is mounted on the holding frame 2 by means of the drive plate 41. The chain unit 5, in this embodiment, as can be seen in figures 2 to 5, comprises a first chain 51 and a second chain 52 and damping elements 6, 6a. The chains in this embodiment are roller chains, comprising inner link plates 511, 521, outer link plates 512, 522, pins 513, 523 and rollers 514, 524. The longitudinal direction L is defined by the direction of the movement of the chains 51, 52 and is indicated with an arrow L in figure 2. As can be seen in figure 2, the members of the first chain 51 with respect to those of the second chain 52 are offset to each other by half a pitch P. The damping elements 6, 6a are fixed to an outer link plate 512 of the first chain 51 by a first fixation 61 and are fixed to an outer link plate 522 of the second chain 52 by a second fixation 62. Additionally, a first flap 64 adjoining the first fixation 61 abuts on an adjoining pin 513 protruding the outer link plate 522 of the first chain 51, the first fixation 61 is attached on and a second flap 65 adjoining the second fixation 62 abuts on a corresponding pin 523 of the second chain 52. The difference between a first embodiment of a damping element 6, as shown in figures 2 and 3, and a second embodiment of a damping element 6a, as shown in figures 4 and 5, is the different distance in the longitudinal direction L of the first fixation 61 to the second fixation 62. The distance of the first embodiment is half a pitch P and the one of the second embodiment is one and a half pitch P. Figures 6 and 7 show a chain wheel unit 43 of a drive unit according to the invention. The chain wheel unit 43 comprises a first sprocket 431, a second sprocket 432 and a spacer 435, all being arranged on a common rotation axle. Each of the sprocket 431, 432 comprises identical teeth 4311, 4321. The circumferential orientation of the two adjoining sprockets 431, 432 differs by half a pitch P, i.e. one tooth 4311 of the first sprocket 431 is circumferentially offset to one tooth 4321 of the second sprocket 432 by half a pitch. In this embodiment, two identical chain wheels, comprising identical sprockets 431, 432 and identical anti-twist devices 434 are being used. In this embodiment, the anti-twist device comprises individual fitting keys for each of the sprockets. Other embodiments with aligned cavities for inserting a common fitting key or other shaft to collar connections are also possible that ensure a solid rotational connection. The spacer 435 provides a means to adjust the axial distance between the first and the second sprocket. In this embodiment, the spacer 435 together with a shaft part 437 of the second sprocket 432 form an intermediate space 438 adapted to receive the damping elements. As shown in figure 7, the pitch P of a sprocket is defined as the circumferential distance between two adjoining teeth 4311, 4321. Figures 8 to 11 show the first embodiment of a damping element according to the invention in detail. However, the fixations 61, 62 on either free end of the damping element are similar or identical to the ones of the other embodiments. In essence, the damping element 6 is of a folded sheet metal design with a first fixation 61 on its one free end for the lateral fixation to the first chain 51, a second fixation 62 on its opposite free end for the lateral fixation to the second chain 52 and a force transmission unit 63 being arranged between the first and the second fixation transmitting an applied force from the first fixation 61 to the second fixation 62 and vice versa. The first fixation 61 in this embodiment is a clip with two opposing clamping jaws 611 for clamping an outer link plate 512 of the first chain 51 between the two rollers 514 being supported by said outer link plate 512 and between the two adjoining inner link plates 511 on either side of said outer link plate 512. At the free end of each of the clamping jaws 611, hooks 612 are being formed to better clench said outer link plate 512. For a better application, the hooks 612 are tapered and narrow towards their extremities. As can be seen in figure 10, the hooks 612 are realized by bending the end tip of the clamping jaws 611 by a hook angle α of more than 90 degrees in the direction of the opposite clamping jaw. From the part of the first clip 61 connecting the two adjoining clamping jaws 611 the clamping jaws 611 extend in essence perpendicular to said connecting part. A first flap 64 extends inclined from said part in the same direction from said part as the clamping jaws 611 extend from said part, forming a flap angle β. Said flap angel, in the current embodiment is around 60 degrees, however, other, smaller or larger angles are possible. The second fixation 62 is of identical design and the force transmission unit 63 in this embodiment is a leaf spring, in particular an arc-shaped leaf spring comprising a short arm 631, a long arm 632 and an arc 633 arranged in between these arms. In the depicted embodiment, the length of the short arm 631 and the long arm 632 differs by half a pitch. In other embodiments, said length differs by (2*n+1) times half a pitch, wherein n is an integer. In order to realise a pretension between the first and the second chain, the arc-shaped leaf spring 63 is bent by a pretension angle γ of less than 180 degrees. When the damping element 6 is positioned between the two adjoining chains, the two free ends of the damping element are pressed together resulting in an outward directed clamping force. In order to produce a damping element 6 as described above, a flat projection of the damping element body can be cut out of a steel sheet, representing a base plane. The clamping jaws and the adjoining flap forming a cross-like shape on either free end of said cut out body. In one step, the clamping jaws are bent in essence perpendicular to the base plane. In another step, the tips of the clamping jaws are bent inwards towards each other by a hook angle α of more than 90 degrees, in particular by 120 degrees. In another step, the flaps are bent towards the same direction as the clamping jaws by a flap angle β of around 60 degrees. The above described steps can be performed at the same time on both free ends of the damping element. In a last step, the middle section of the flat projection is bent by a pretension angle γ of less than 180 degrees, as such that the clamping jaws together with the flaps are oriented towards the outside. Figure 12 shows a third embodiment of a damping element 6b. In essence, the attachment of the damping element to the respective chain is identical to the first embodiment, i.e. the clamping jaws and the flaps. Instead of an arc-shaped leaf spring 63 connecting the first and the second connection, a magnet unit 8 is present. In use, the magnets 83 can be in contact with each other or they can be spaced apart from one another. The magnet unit 8 comprises magnet holders 82 and magnets 83. The magnet holders 82 can be formed integrally as a single piece together with the clamping jaws and the flaps or can be attached to them. The magnets 83 are attached to the magnet holders 82 or can be directly attached to the clamping jaws and flaps. In the depicted embodiment, the first fixation 61 together with a first magnet holder 82 and a first magnet 83 are identical to the second fixation 62 together with a second magnet holder 82 and a second magnet 83. Figure 13 shows a fourth embodiment of a damping element 6c. Like the third embodiment 6b, the clamping jaws and the flaps are identical to the ones of the first embodiment. In order to transmit forces from the first fixation 61 to a second fixation 62, a tension or pressure spring unit 9 is present. The tension or pressure spring unit 9 comprises spring holders 92 and springs 93. A single spring or a plurality of springs can be present. The spring holders 92 can be formed integrally as a single piece together with the clamping jaws and the flaps or can be attached to them. The springs 93 are attached to the spring holders 92 or can be directly attached to the clamping jaws and flaps. In the depicted embodiment, the first fixation 61 together with a first spring holder 92 are identical to the second fixation 62 together with a second spring holder 92. Figures 14 and 15 show a fourth embodiment of a damping element 80. The damping element 80 comprises an integrally formed housing 800, being T-shaped in essence. In the view of figure 14, in the use situation, the housing looks like a lying T. The housing 800 comprising a first leg, forming the first fixation 801, is oriented parallel to the first chain 51 in the use situation. A second leg, forming the second fixation 802, is oriented perpendicular to the first leg and arranged in the middle thereof, extending in the direction of the second chain 52 in the use situation. On the first fixation 801, in the direction that is opposite of the second fixation 802, a first pin reception 8013 is present on either free end of the first leg facing laterally towards the first chain. The first pin reception 8013 comprises a cylindrical shape and its diameter is slightly bigger than the pin 513 of the chain 51 to be received, providing some clearance between the respective pin and the corresponding side wall of the first pin reception 8013. The distance between these two first pin receptions 8013 matches the pitch of the first chain 51. Adjoining to the first pin reception 8013 and collinear with its rotational axle, a first magnet reception 8011 is formed in the first leg and is adapted to receive a magnet 803, that can be inserted from the side opposite to the first pin reception 8013. The first magnet reception 8011, in essence, comprises a cylindrical shape that widens conically from a base diameter, arranged adjacent to the first pin reception 8013, towards the direction opposite to the first pin reception 8013. The base diameter matches the diameter of a magnet to be inserted towards. The difference in diameter of the first pin reception 8013 and the first magnet reception 8011 forms a first shoulder 8012, on which the corresponding magnet 803 abuts. In the middle of the two first pin receptions 8013, in the direction of the second leg, a second magnet reception 8021 is formed and a second pin reception 8023 is formed adjacent and collinear thereto. The shape and design of the second magnet reception 8021 and the second pin reception 8013 are in essence equal to the first magnet reception 8011 respective the first pin reception 8013, being oriented towards the opposite direction. The difference in diameter of the second pin reception 8023 and the second magnet reception 8021 forms a second shoulder 8022, on which the corresponding magnet 803 abuts. In this embodiment, the second fixation 802 comprises only one second pin reception 8013. However, other embodiments with more than one second pin reception are possible, resulting in a damping element, whose shape differs from the T-shape. [REFERENCE LIST]

1. A chain drive unit (4, 5, 6, 80) for reducing chain vibrations comprising a chain wheel unit (43) with at least two sprockets (431, 432) that are arranged parallel on a common rotation axle, at least two parallel chains (51, 52) engaging these sprockets (431, 432), characterized in that at least one damping element (6, 80) connecting two adjoining chains (51, 52) and in that the circumferential orientation of two adjoining sprockets (431, 432) differs by a partial pitch (pP), and in that the damping element (6, 80) comprises a first fixation (61, 801) on its one free end for the lateral fixation to the first chain (51), a second fixation (62, 802) on its opposite free end for the lateral fixation to the second chain (52) and a force transmission unit (63, 8, 9, 800) arranged between the first and the second fixation transmitting an applied force from the first fixation (61, 801) to the second fixation (62, 802) and vice versa.

2. The chain drive unit (4, 5, 6, 80) according to claim 1, wherein the partial pitch (pP) is defined by a sprocket's pitch (P) divided by the number of sprockets. 3. The chain drive unit (4, 5, 6, 80) according to claim 1 or 2, wherein the position of the first fixation (61, 801) differs to the position of the second fixation (62, 802) in a longitudinal direction (L) of the chain's movement by the partial pitch (pP) or by (the number of sprockets*n+1) times the partial pitch (pP), wherein n is an integer. 4. The chain drive unit (4, 5, 6, 80) according to one of claims 1 to 3, wherein the force transmission unit comprises an arc-shape leaf spring (63) or a magnet (82) or a tension or pressure spring (92) or a housing (800). 5. The chain drive unit (4, 5, 6) according to one of claims 1 to 4, wherein the first fixation (61) comprises a first clip with two opposing clamping jaws (611) for clamping an outer link plate (512) of the first chain (51) and a second clip with two opposing clamping jaws (621) for clamping an outer link plate (522) of the second chain (52). 6. The chain drive unit (4, 5, 6) according to one of claims 1 to 5, wherein the damping element (6) further comprise a flap (64, 65) on its free ends adjacent to the first and second clamping jaws (611, 621) for abutting in a longitudinal direction (L) against an adjacent pin (513, 523) of the corresponding chain (51, 52). 7. The chain drive unit (4, 5, 80) according to one of claims 1 to 4, wherein the first and the second fixation (801, 802) comprise a first respective second pin reception (8013, 8023) for receiving a pin of the first respective second chain (51, 52) and a corresponding magnet (803) adjacent to the respective pin reception (8013, 8023) for attaching the respective fixation (801, 802) to the respective chain (51, 52). 8. The chain drive unit (4, 5, 6, 80) according to one of claims 1 to 7, wherein the chains (51, 52) are roller chains. 9. A lifting system (1) with a chain drive unit (4, 5, 6, 80) according to one of claims 1 to 8, wherein the lifting system (1) further comprises a holding frame (2) with guiding elements (211) arranged thereon for the guiding of a lifting element (3) arranged thereon and a weight compensation (7), wherein the lifting element (3) is connected to the weight compensation (7) by means of the chain drive unit (4, 5, 6, 80). 10. The lifting system (1) according to claim 9, wherein the chain drive unit (4, 5, 6, 80) is arranged on top of the holding frame (2).

2881618

Chain drive unit

Based on the following detailed description of an invention, generate the patent claims. There should be 3 claims in total. The first, independent claim is given and the remaining 2 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a perspective view of an embodiment of a lifting system 1 according to the invention. The lifting system's 1 main components are a holding frame 2, a lifting element 3, a chain drive unit comprising a drive unit 4, a chain unit 5 and damping elements 6, and a weight compensation 7. The holding frame 2 comprises a side frame 21 on either side of the frame, the side frames 21 being mounted on a lower cross connection 22 serving as a base plate to fix the holding frame 2 on the ground and connecting the side frames 21 to one another in the lower region of the holding frame 2. The holding frame 2 further comprises upper cross connections 23 connecting the side frames 21 to one another in the upper region of the holding frame 2. The upper cross connections 23 serve as a base for the arrangement of the drive unit 4. Sideways and outward facing guiding means 211 are mounted on each of the side frames 21 for guiding the lifting element 3. The lifting element 3 comprises a lifting frame 31 that is connected to the holding frame 2 by guiding means 211. In this embodiment, the lifting frame 31 in essence, is L-shaped, its vertical arm being in sliding contact with the holding frame 2 and its horizontal arm forming a base for a platform or a cabin. The drive unit 4 comprises a drive plate 41 a drive 42 mounted on said drive plate 41 and a chain wheel unit 43 mounted in line with said drive 42 on side drive plate 41 and connected to said drive 42 for transmitting a rotational movement generated by the drive 42 via said chain wheel unit 43 to the chain unit 5 engaging said chain wheel unit 43. The drive unit 4 is mounted on the holding frame 2 by means of the drive plate 41. The chain unit 5, in this embodiment, as can be seen in figures 2 to 5, comprises a first chain 51 and a second chain 52 and damping elements 6, 6a. The chains in this embodiment are roller chains, comprising inner link plates 511, 521, outer link plates 512, 522, pins 513, 523 and rollers 514, 524. The longitudinal direction L is defined by the direction of the movement of the chains 51, 52 and is indicated with an arrow L in figure 2. As can be seen in figure 2, the members of the first chain 51 with respect to those of the second chain 52 are offset to each other by half a pitch P. The damping elements 6, 6a are fixed to an outer link plate 512 of the first chain 51 by a first fixation 61 and are fixed to an outer link plate 522 of the second chain 52 by a second fixation 62. Additionally, a first flap 64 adjoining the first fixation 61 abuts on an adjoining pin 513 protruding the outer link plate 522 of the first chain 51, the first fixation 61 is attached on and a second flap 65 adjoining the second fixation 62 abuts on a corresponding pin 523 of the second chain 52. The difference between a first embodiment of a damping element 6, as shown in figures 2 and 3, and a second embodiment of a damping element 6a, as shown in figures 4 and 5, is the different distance in the longitudinal direction L of the first fixation 61 to the second fixation 62. The distance of the first embodiment is half a pitch P and the one of the second embodiment is one and a half pitch P. Figures 6 and 7 show a chain wheel unit 43 of a drive unit according to the invention. The chain wheel unit 43 comprises a first sprocket 431, a second sprocket 432 and a spacer 435, all being arranged on a common rotation axle. Each of the sprocket 431, 432 comprises identical teeth 4311, 4321. The circumferential orientation of the two adjoining sprockets 431, 432 differs by half a pitch P, i.e. one tooth 4311 of the first sprocket 431 is circumferentially offset to one tooth 4321 of the second sprocket 432 by half a pitch. In this embodiment, two identical chain wheels, comprising identical sprockets 431, 432 and identical anti-twist devices 434 are being used. In this embodiment, the anti-twist device comprises individual fitting keys for each of the sprockets. Other embodiments with aligned cavities for inserting a common fitting key or other shaft to collar connections are also possible that ensure a solid rotational connection. The spacer 435 provides a means to adjust the axial distance between the first and the second sprocket. In this embodiment, the spacer 435 together with a shaft part 437 of the second sprocket 432 form an intermediate space 438 adapted to receive the damping elements. As shown in figure 7, the pitch P of a sprocket is defined as the circumferential distance between two adjoining teeth 4311, 4321. Figures 8 to 11 show the first embodiment of a damping element according to the invention in detail. However, the fixations 61, 62 on either free end of the damping element are similar or identical to the ones of the other embodiments. In essence, the damping element 6 is of a folded sheet metal design with a first fixation 61 on its one free end for the lateral fixation to the first chain 51, a second fixation 62 on its opposite free end for the lateral fixation to the second chain 52 and a force transmission unit 63 being arranged between the first and the second fixation transmitting an applied force from the first fixation 61 to the second fixation 62 and vice versa. The first fixation 61 in this embodiment is a clip with two opposing clamping jaws 611 for clamping an outer link plate 512 of the first chain 51 between the two rollers 514 being supported by said outer link plate 512 and between the two adjoining inner link plates 511 on either side of said outer link plate 512. At the free end of each of the clamping jaws 611, hooks 612 are being formed to better clench said outer link plate 512. For a better application, the hooks 612 are tapered and narrow towards their extremities. As can be seen in figure 10, the hooks 612 are realized by bending the end tip of the clamping jaws 611 by a hook angle α of more than 90 degrees in the direction of the opposite clamping jaw. From the part of the first clip 61 connecting the two adjoining clamping jaws 611 the clamping jaws 611 extend in essence perpendicular to said connecting part. A first flap 64 extends inclined from said part in the same direction from said part as the clamping jaws 611 extend from said part, forming a flap angle β. Said flap angel, in the current embodiment is around 60 degrees, however, other, smaller or larger angles are possible. The second fixation 62 is of identical design and the force transmission unit 63 in this embodiment is a leaf spring, in particular an arc-shaped leaf spring comprising a short arm 631, a long arm 632 and an arc 633 arranged in between these arms. In the depicted embodiment, the length of the short arm 631 and the long arm 632 differs by half a pitch. In other embodiments, said length differs by (2*n+1) times half a pitch, wherein n is an integer. In order to realise a pretension between the first and the second chain, the arc-shaped leaf spring 63 is bent by a pretension angle γ of less than 180 degrees. When the damping element 6 is positioned between the two adjoining chains, the two free ends of the damping element are pressed together resulting in an outward directed clamping force. In order to produce a damping element 6 as described above, a flat projection of the damping element body can be cut out of a steel sheet, representing a base plane. The clamping jaws and the adjoining flap forming a cross-like shape on either free end of said cut out body. In one step, the clamping jaws are bent in essence perpendicular to the base plane. In another step, the tips of the clamping jaws are bent inwards towards each other by a hook angle α of more than 90 degrees, in particular by 120 degrees. In another step, the flaps are bent towards the same direction as the clamping jaws by a flap angle β of around 60 degrees. The above described steps can be performed at the same time on both free ends of the damping element. In a last step, the middle section of the flat projection is bent by a pretension angle γ of less than 180 degrees, as such that the clamping jaws together with the flaps are oriented towards the outside. Figure 12 shows a third embodiment of a damping element 6b. In essence, the attachment of the damping element to the respective chain is identical to the first embodiment, i.e. the clamping jaws and the flaps. Instead of an arc-shaped leaf spring 63 connecting the first and the second connection, a magnet unit 8 is present. In use, the magnets 83 can be in contact with each other or they can be spaced apart from one another. The magnet unit 8 comprises magnet holders 82 and magnets 83. The magnet holders 82 can be formed integrally as a single piece together with the clamping jaws and the flaps or can be attached to them. The magnets 83 are attached to the magnet holders 82 or can be directly attached to the clamping jaws and flaps. In the depicted embodiment, the first fixation 61 together with a first magnet holder 82 and a first magnet 83 are identical to the second fixation 62 together with a second magnet holder 82 and a second magnet 83. Figure 13 shows a fourth embodiment of a damping element 6c. Like the third embodiment 6b, the clamping jaws and the flaps are identical to the ones of the first embodiment. In order to transmit forces from the first fixation 61 to a second fixation 62, a tension or pressure spring unit 9 is present. The tension or pressure spring unit 9 comprises spring holders 92 and springs 93. A single spring or a plurality of springs can be present. The spring holders 92 can be formed integrally as a single piece together with the clamping jaws and the flaps or can be attached to them. The springs 93 are attached to the spring holders 92 or can be directly attached to the clamping jaws and flaps. In the depicted embodiment, the first fixation 61 together with a first spring holder 92 are identical to the second fixation 62 together with a second spring holder 92. Figures 14 and 15 show a fourth embodiment of a damping element 80. The damping element 80 comprises an integrally formed housing 800, being T-shaped in essence. In the view of figure 14, in the use situation, the housing looks like a lying T. The housing 800 comprising a first leg, forming the first fixation 801, is oriented parallel to the first chain 51 in the use situation. A second leg, forming the second fixation 802, is oriented perpendicular to the first leg and arranged in the middle thereof, extending in the direction of the second chain 52 in the use situation. On the first fixation 801, in the direction that is opposite of the second fixation 802, a first pin reception 8013 is present on either free end of the first leg facing laterally towards the first chain. The first pin reception 8013 comprises a cylindrical shape and its diameter is slightly bigger than the pin 513 of the chain 51 to be received, providing some clearance between the respective pin and the corresponding side wall of the first pin reception 8013. The distance between these two first pin receptions 8013 matches the pitch of the first chain 51. Adjoining to the first pin reception 8013 and collinear with its rotational axle, a first magnet reception 8011 is formed in the first leg and is adapted to receive a magnet 803, that can be inserted from the side opposite to the first pin reception 8013. The first magnet reception 8011, in essence, comprises a cylindrical shape that widens conically from a base diameter, arranged adjacent to the first pin reception 8013, towards the direction opposite to the first pin reception 8013. The base diameter matches the diameter of a magnet to be inserted towards. The difference in diameter of the first pin reception 8013 and the first magnet reception 8011 forms a first shoulder 8012, on which the corresponding magnet 803 abuts. In the middle of the two first pin receptions 8013, in the direction of the second leg, a second magnet reception 8021 is formed and a second pin reception 8023 is formed adjacent and collinear thereto. The shape and design of the second magnet reception 8021 and the second pin reception 8013 are in essence equal to the first magnet reception 8011 respective the first pin reception 8013, being oriented towards the opposite direction. The difference in diameter of the second pin reception 8023 and the second magnet reception 8021 forms a second shoulder 8022, on which the corresponding magnet 803 abuts. In this embodiment, the second fixation 802 comprises only one second pin reception 8013. However, other embodiments with more than one second pin reception are possible, resulting in a damping element, whose shape differs from the T-shape. [REFERENCE LIST]

11. A damping element (6, 80) to be used in a chain drive unit (4, 5, 6, 80), wherein the damping element (6, 80) comprises a first fixation (61, 801) on its one free end for the lateral fixation to the first chain (51), a second fixation (62, 802) on its opposite free end for the lateral fixation to the second chain (52) and a force transmission unit (63, 82, 92, 800) arranged between the first and the second fixation transmitting an applied force from the first fixation (61, 801) to the second fixation (62, 802) and vice versa.

12. The damping element (6) according to claim 11, wherein the force transmission unit comprises an arc-shape leaf spring (63) or a magnet (82) or a tension or pressure spring (92) or a housing (800). 13. The damping element (6) according to one of claims 11 or 12, wherein the first fixation (61) comprises a first clip with two opposing clamping jaws (611) for clamping an outer link plate (512) of the first chain (51) and a second clip with two opposing clamping jaws (621) for clamping an outer link plate (522) of the second chain (52).

2881618

Chain drive unit

Based on the following detailed description of an invention, generate the patent claims. There should be 2 claims in total. The first, independent claim is given and the remaining 1 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a perspective view of an embodiment of a lifting system 1 according to the invention. The lifting system's 1 main components are a holding frame 2, a lifting element 3, a chain drive unit comprising a drive unit 4, a chain unit 5 and damping elements 6, and a weight compensation 7. The holding frame 2 comprises a side frame 21 on either side of the frame, the side frames 21 being mounted on a lower cross connection 22 serving as a base plate to fix the holding frame 2 on the ground and connecting the side frames 21 to one another in the lower region of the holding frame 2. The holding frame 2 further comprises upper cross connections 23 connecting the side frames 21 to one another in the upper region of the holding frame 2. The upper cross connections 23 serve as a base for the arrangement of the drive unit 4. Sideways and outward facing guiding means 211 are mounted on each of the side frames 21 for guiding the lifting element 3. The lifting element 3 comprises a lifting frame 31 that is connected to the holding frame 2 by guiding means 211. In this embodiment, the lifting frame 31 in essence, is L-shaped, its vertical arm being in sliding contact with the holding frame 2 and its horizontal arm forming a base for a platform or a cabin. The drive unit 4 comprises a drive plate 41 a drive 42 mounted on said drive plate 41 and a chain wheel unit 43 mounted in line with said drive 42 on side drive plate 41 and connected to said drive 42 for transmitting a rotational movement generated by the drive 42 via said chain wheel unit 43 to the chain unit 5 engaging said chain wheel unit 43. The drive unit 4 is mounted on the holding frame 2 by means of the drive plate 41. The chain unit 5, in this embodiment, as can be seen in figures 2 to 5, comprises a first chain 51 and a second chain 52 and damping elements 6, 6a. The chains in this embodiment are roller chains, comprising inner link plates 511, 521, outer link plates 512, 522, pins 513, 523 and rollers 514, 524. The longitudinal direction L is defined by the direction of the movement of the chains 51, 52 and is indicated with an arrow L in figure 2. As can be seen in figure 2, the members of the first chain 51 with respect to those of the second chain 52 are offset to each other by half a pitch P. The damping elements 6, 6a are fixed to an outer link plate 512 of the first chain 51 by a first fixation 61 and are fixed to an outer link plate 522 of the second chain 52 by a second fixation 62. Additionally, a first flap 64 adjoining the first fixation 61 abuts on an adjoining pin 513 protruding the outer link plate 522 of the first chain 51, the first fixation 61 is attached on and a second flap 65 adjoining the second fixation 62 abuts on a corresponding pin 523 of the second chain 52. The difference between a first embodiment of a damping element 6, as shown in figures 2 and 3, and a second embodiment of a damping element 6a, as shown in figures 4 and 5, is the different distance in the longitudinal direction L of the first fixation 61 to the second fixation 62. The distance of the first embodiment is half a pitch P and the one of the second embodiment is one and a half pitch P. Figures 6 and 7 show a chain wheel unit 43 of a drive unit according to the invention. The chain wheel unit 43 comprises a first sprocket 431, a second sprocket 432 and a spacer 435, all being arranged on a common rotation axle. Each of the sprocket 431, 432 comprises identical teeth 4311, 4321. The circumferential orientation of the two adjoining sprockets 431, 432 differs by half a pitch P, i.e. one tooth 4311 of the first sprocket 431 is circumferentially offset to one tooth 4321 of the second sprocket 432 by half a pitch. In this embodiment, two identical chain wheels, comprising identical sprockets 431, 432 and identical anti-twist devices 434 are being used. In this embodiment, the anti-twist device comprises individual fitting keys for each of the sprockets. Other embodiments with aligned cavities for inserting a common fitting key or other shaft to collar connections are also possible that ensure a solid rotational connection. The spacer 435 provides a means to adjust the axial distance between the first and the second sprocket. In this embodiment, the spacer 435 together with a shaft part 437 of the second sprocket 432 form an intermediate space 438 adapted to receive the damping elements. As shown in figure 7, the pitch P of a sprocket is defined as the circumferential distance between two adjoining teeth 4311, 4321. Figures 8 to 11 show the first embodiment of a damping element according to the invention in detail. However, the fixations 61, 62 on either free end of the damping element are similar or identical to the ones of the other embodiments. In essence, the damping element 6 is of a folded sheet metal design with a first fixation 61 on its one free end for the lateral fixation to the first chain 51, a second fixation 62 on its opposite free end for the lateral fixation to the second chain 52 and a force transmission unit 63 being arranged between the first and the second fixation transmitting an applied force from the first fixation 61 to the second fixation 62 and vice versa. The first fixation 61 in this embodiment is a clip with two opposing clamping jaws 611 for clamping an outer link plate 512 of the first chain 51 between the two rollers 514 being supported by said outer link plate 512 and between the two adjoining inner link plates 511 on either side of said outer link plate 512. At the free end of each of the clamping jaws 611, hooks 612 are being formed to better clench said outer link plate 512. For a better application, the hooks 612 are tapered and narrow towards their extremities. As can be seen in figure 10, the hooks 612 are realized by bending the end tip of the clamping jaws 611 by a hook angle α of more than 90 degrees in the direction of the opposite clamping jaw. From the part of the first clip 61 connecting the two adjoining clamping jaws 611 the clamping jaws 611 extend in essence perpendicular to said connecting part. A first flap 64 extends inclined from said part in the same direction from said part as the clamping jaws 611 extend from said part, forming a flap angle β. Said flap angel, in the current embodiment is around 60 degrees, however, other, smaller or larger angles are possible. The second fixation 62 is of identical design and the force transmission unit 63 in this embodiment is a leaf spring, in particular an arc-shaped leaf spring comprising a short arm 631, a long arm 632 and an arc 633 arranged in between these arms. In the depicted embodiment, the length of the short arm 631 and the long arm 632 differs by half a pitch. In other embodiments, said length differs by (2*n+1) times half a pitch, wherein n is an integer. In order to realise a pretension between the first and the second chain, the arc-shaped leaf spring 63 is bent by a pretension angle γ of less than 180 degrees. When the damping element 6 is positioned between the two adjoining chains, the two free ends of the damping element are pressed together resulting in an outward directed clamping force. In order to produce a damping element 6 as described above, a flat projection of the damping element body can be cut out of a steel sheet, representing a base plane. The clamping jaws and the adjoining flap forming a cross-like shape on either free end of said cut out body. In one step, the clamping jaws are bent in essence perpendicular to the base plane. In another step, the tips of the clamping jaws are bent inwards towards each other by a hook angle α of more than 90 degrees, in particular by 120 degrees. In another step, the flaps are bent towards the same direction as the clamping jaws by a flap angle β of around 60 degrees. The above described steps can be performed at the same time on both free ends of the damping element. In a last step, the middle section of the flat projection is bent by a pretension angle γ of less than 180 degrees, as such that the clamping jaws together with the flaps are oriented towards the outside. Figure 12 shows a third embodiment of a damping element 6b. In essence, the attachment of the damping element to the respective chain is identical to the first embodiment, i.e. the clamping jaws and the flaps. Instead of an arc-shaped leaf spring 63 connecting the first and the second connection, a magnet unit 8 is present. In use, the magnets 83 can be in contact with each other or they can be spaced apart from one another. The magnet unit 8 comprises magnet holders 82 and magnets 83. The magnet holders 82 can be formed integrally as a single piece together with the clamping jaws and the flaps or can be attached to them. The magnets 83 are attached to the magnet holders 82 or can be directly attached to the clamping jaws and flaps. In the depicted embodiment, the first fixation 61 together with a first magnet holder 82 and a first magnet 83 are identical to the second fixation 62 together with a second magnet holder 82 and a second magnet 83. Figure 13 shows a fourth embodiment of a damping element 6c. Like the third embodiment 6b, the clamping jaws and the flaps are identical to the ones of the first embodiment. In order to transmit forces from the first fixation 61 to a second fixation 62, a tension or pressure spring unit 9 is present. The tension or pressure spring unit 9 comprises spring holders 92 and springs 93. A single spring or a plurality of springs can be present. The spring holders 92 can be formed integrally as a single piece together with the clamping jaws and the flaps or can be attached to them. The springs 93 are attached to the spring holders 92 or can be directly attached to the clamping jaws and flaps. In the depicted embodiment, the first fixation 61 together with a first spring holder 92 are identical to the second fixation 62 together with a second spring holder 92. Figures 14 and 15 show a fourth embodiment of a damping element 80. The damping element 80 comprises an integrally formed housing 800, being T-shaped in essence. In the view of figure 14, in the use situation, the housing looks like a lying T. The housing 800 comprising a first leg, forming the first fixation 801, is oriented parallel to the first chain 51 in the use situation. A second leg, forming the second fixation 802, is oriented perpendicular to the first leg and arranged in the middle thereof, extending in the direction of the second chain 52 in the use situation. On the first fixation 801, in the direction that is opposite of the second fixation 802, a first pin reception 8013 is present on either free end of the first leg facing laterally towards the first chain. The first pin reception 8013 comprises a cylindrical shape and its diameter is slightly bigger than the pin 513 of the chain 51 to be received, providing some clearance between the respective pin and the corresponding side wall of the first pin reception 8013. The distance between these two first pin receptions 8013 matches the pitch of the first chain 51. Adjoining to the first pin reception 8013 and collinear with its rotational axle, a first magnet reception 8011 is formed in the first leg and is adapted to receive a magnet 803, that can be inserted from the side opposite to the first pin reception 8013. The first magnet reception 8011, in essence, comprises a cylindrical shape that widens conically from a base diameter, arranged adjacent to the first pin reception 8013, towards the direction opposite to the first pin reception 8013. The base diameter matches the diameter of a magnet to be inserted towards. The difference in diameter of the first pin reception 8013 and the first magnet reception 8011 forms a first shoulder 8012, on which the corresponding magnet 803 abuts. In the middle of the two first pin receptions 8013, in the direction of the second leg, a second magnet reception 8021 is formed and a second pin reception 8023 is formed adjacent and collinear thereto. The shape and design of the second magnet reception 8021 and the second pin reception 8013 are in essence equal to the first magnet reception 8011 respective the first pin reception 8013, being oriented towards the opposite direction. The difference in diameter of the second pin reception 8023 and the second magnet reception 8021 forms a second shoulder 8022, on which the corresponding magnet 803 abuts. In this embodiment, the second fixation 802 comprises only one second pin reception 8013. However, other embodiments with more than one second pin reception are possible, resulting in a damping element, whose shape differs from the T-shape. [REFERENCE LIST]

14. Method for reducing chain vibrations within a chain drive unit (4, 5, 6, 80) comprising: providing a chain wheel unit (43) with at least two sprockets (431, 432) that are arranged parallel on a common rotation axle with a circumferential orientation of two adjoining sprockets (431, 432) differing by a partial pitch (pP), providing at least two parallel chains (51, 52) engaging the sprockets (431, 432) of the chain wheel unit (43), providing a plurality of damping elements (6, 80) having free ends with fixations (61, 62, 801, 802), attaching the fixations (61, 62, 801, 802) of the free ends of each damping element (6, 80) on opposite adjacent portions of the two parallel chains (51, 52) for connecting these two adjoining chains (51, 52), wherein a force transmission unit (63, 8, 9, 800) is arranged between the first and the second fixation transmitting an applied force from the first fixation (61, 801) to the second fixation (62, 802) and vice versa.

15. The method according to claim 14, wherein the partial pitch (pP) is defined by a sprocket's pitch (P) divided by the number of sprockets.

2881176

Cone crusher shaft position measurement sensor arrangement

Based on the following detailed description of an invention, generate the patent claims. There should be 12 claims in total. The first, independent claim is given and the remaining 11 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 illustrates a cone crusher 1 in accordance with one embodiment of the present invention. The cone crusher illustrated in Figure 1 is of the inertia cone crusher type. It will be appreciated that the present invention is applicable also to other cone crusher types. The cone crusher 1 comprises a crusher frame 2 in which the various parts of the crusher 1 are mounted. The crusher frame 2 comprises an upper frame portion 4, and a lower frame portion 6. The upper frame portion 4 has the form of a bowl and is provided with an outer thread 8 which co-operates with an inner thread 10 of the lower frame portion 6. The upper frame portion 4 supports, on the inside thereof, an outer crushing shell 12. The outer crushing shell 12 is a wear part which may be made from, for example, manganese steel. The lower frame portion 6 supports an inner crushing shell arrangement 14. The inner crushing shell arrangement 14 comprises a crushing head 16, which has the form of a cone and which supports an inner crushing shell 18, which is a wear part which may be made from, for example, a manganese steel. The crushing head 16 rests on a spherical cone crusher bearing 20. The cone crusher bearing 20 has an upper bearing surface 22 which is in bearing contact with a lower surface 24 of the crushing head 16. The bearing surface 22 of the crusher bearing 20 has an at least partly concave shape, and the lower surface 24 of the crushing head 16 has an at least partly convex shape. The cone crusher bearing 20 rests on a bearing support 26 which is mounted on an inner cylindrical portion 28 of the lower frame portion 6. The crushing head 16 is mounted on a crushing shaft 30. The crushing shaft 30 extends through the cone crusher bearing 20. Hence, the cone crusher bearing 20 forms a "collar" encircling the crushing shaft 30. At a lower end thereof, the crushing shaft 30 is encircled by a cylindrical sleeve 32. The cylindrical sleeve 32 is provided with an inner cylindrical bearing 34 making it possible for the cylindrical sleeve 32 to rotate around the crushing shaft 30. An unbalance weight 36 is mounted on one side of the cylindrical sleeve 32. At its lower end the cylindrical sleeve 32 is connected to a vertical drive shaft 38. The drive shaft 38 comprises a ball spindle 40, a pulley shaft 42, an intermediate shaft 43 connecting the ball spindle 40 to the pulley shaft 42, an upper connector 44 which connects the ball spindle 40 to the cylindrical sleeve 32, and a lower connector 46 which is arranged on the intermediate shaft 43 and which connects the ball spindle 40 to the intermediate shaft 43. The two connectors 44, 46 are connected to the ball spindle 40 in a non-rotating manner, such that rotational movement can be transferred from the pulley shaft 42 to the cylindrical sleeve 32 via the intermediate shaft 43 and the ball spindle 40. A bottom portion 48 of the lower frame portion 6 comprises a vertical cylindrical drive shaft bearing 50 in which the vertical drive shaft 38 is supported. A motor (not shown) is arranged for driving a pulley 52 which is connected to the pulley shaft 42, below the drive shaft bearing 50. Lubricant is collected at the inside of the bottom portion 48 and is returned to a lubricant pump (not shown) via a lubricant return pipe 54. The outer and inner crushing shells 12, 18 form between them a crushing chamber 56 to which material that is to be crushed is supplied. The discharge opening of the crushing chamber 56, and thereby the crushing capacity, can be adjusted by means of turning the upper frame portion 4, by means of the threads 8, 10, such that the distance between the shells 12, 18 is adjusted. When the crusher 1 is in operation the drive shaft 38 is rotated by means of the not shown motor. The rotation of the drive shaft 38 causes the sleeve 32 to rotate and as an effect of that rotation the sleeve 32 is swung outwards by means of the unbalance weight 36, displacing the unbalance weight 36 further away from the crusher central axis CC of the crusher 1, in response to the centrifugal force to which the unbalance weight 36 is exposed. Such displacement of the unbalance weight 36 and of the cylindrical sleeve 32 to which the unbalance weight 36 is attached is allowed thanks to the ball spindle 40 and thanks to the fact that the sleeve 32 may slide somewhat, thanks to the cylindrical bearing 34, in the vertical direction along the crushing shaft 30. The combined rotation and swinging of the cylindrical sleeve 32 with unbalance weight 36 mounted thereon causes an inclination of the crushing shaft 30, and makes the crushing shaft 30 gyrate, such that material is crushed between the outer and inner crushing shells 12, 18 forming between them the crushing chamber 56. During operation of the crusher 1 it is important to know the manner in which the crushing shaft 30 moves to be able to properly control the operation of the crusher 1. The movement of the crushing shaft 30 will be influenced by, among other things, the amount and the properties of the material forwarded to the crushing chamber 56, the distribution of the material around the crushing chamber 56, the rpm at which the drive shaft 38 rotates the cylindrical sleeve 32, and the existence of any pieces of uncrushable material in the crushing chamber 56. To this end a cone crusher shaft position measurement sensor arrangement 58 is arranged at a bottom 60 of the lower frame portion 6. The sensor arrangement 58 comprises a target means 62 arranged to move in a horizontal direction in concordance with the movement of the upper connector 44. Since the upper connector 44 is connected to the cylindrical sleeve 32, which in turn is connected, via cylindrical bearing 34, to the crushing shaft 30, the target means 62 will move in a horizontal plane in concordance with the movement of the crushing shaft 30. The sensor arrangement 58 further comprises at least one first sensor element 64. The first sensor element 64 is arranged for detecting the horizontal position of the target means 62 in a manner which will be described in more detail hereinafter. The sensor arrangement 58 comprises a sensor table 66. The sensor table 66 supports in a sliding manner the target means 62 such that the target means 62 can move in the horizontal direction. Furthermore, the sensor table 66 also provides a support for the first sensor element 64. The sensor table 66 is mounted to the lower frame portion 6 by means of table supporting legs 68. A target means connector 70 is mounted to the upper connector 44 to transfer the movement of the upper connector 44 to the target means 62. Figure 2 illustrates the sensor arrangement 58 in more detail, and when the crusher 1 is in operation. When the crusher 1 is in operation the drive shaft 38 rotates the sleeve 32, and the unbalance weight 36 shown in Figure 1 will swing the cylindrical sleeve 32, and thereby the crushing shaft 30, to the side. Thereby, a shaft central axis SC, which is the central axis of the crushing shaft 30, will deviate from the crusher central axis CC. Hence, there will be an angle α between the shaft central axis SC and the crusher central axis CC. This angle α will provide crucial information about the operation of the crusher and is measured by means of the sensor arrangement 58. The target means 62 comprises a circular target disc 72, which is preferably made from a non-conductive material, such as a polymer material, and a circular metallic sensor target 74 extending around the circular target disc 72. The sensor table 66 comprises a lower table plate 76 and an upper table cover 78 that may, in accordance with one embodiment, be formed from non-conductive materials, for example polymer materials. The lower table plate 76 and the upper table cover 78 form between them a sensor table space 80 in which the target disc 72 may move, sliding on the lower table plate 76. The sensor table space 80 limits the vertical movements of the target disc 72, preferably to such a degree that the target disc 72 can move less than +/- 5 mm, more preferably less than +/- 2 mm, in the vertical direction. The sensor table space 80 has a horizontal width which is larger than the diameter of the target disc 72, to account for the fact that the target disc 72 is swung to the side upon operation of the crusher. The crusher central axis CC and the shaft central axis SC intersect in a pivot point PVP. The vertical position of the pivot point PVP, and thereby a vertical distance HP between the pivot point PVP and the lower side of the metallic target 74, is set by the geometry, i.e. the radius, of the spherical cone crusher bearing 20 that supports the crushing head 16 and the crushing shaft 30, as illustrated in Figure 1. Thereby, by determining the horizontal position of the metallic target 74 in relation to the crusher central axis CC it becomes possible to calculate, based on such horizontal position and the known vertical distance HP, the angle α between the shaft central axis SC and the crusher central axis CC. The first sensor element 64 is arranged in a sensor space 82 formed in the lower table plate 76. The sensor space 82 extends under the sensor table space 80 to enable the first sensor element 64 to sense a present position of the metallic sensor target 74 of the target disc 72. The first sensor element 64 comprises an elongate horizontal sensing array 84 which extends in a horizontal direction and towards the crusher central axis CC. In this embodiment the first sensor element 64 comprises an inductive position sensor. Such an inductive position sensor generates an inductive field which shifts along a sensitive surface and detects a metallic sensor target in the detection range of the inductive field. The inductive sensor comprises several coils arranged in a coil array. Hence, in this embodiment the horizontal sensing array 84 comprises a coil array. The inductive sensor 64 calculates the current position of the sensor target 74 and provides output as, for example, a distance-proportional analog signal. The inductive sensing field extends along the horizontal length of the horizontal sensing array 84. The first sensor element 64 is thus able to detect the horizontal position along the horizontal sensing array 84 of the metallic sensor target 74 without any physical contact therewith. The sensor output is received by a control unit (not shown) connected to the first sensor element 64. During operation of the sensor arrangement 58, the first sensor element 64 emits an alternating electro-magnetic sensing field along the sensing array 84. When the metallic sensor target 74 enters the sensing field eddy currents are induced in the target 74 which reduces the signal amplitude of the first sensor element 64 and triggers a change of state at the sensor element 64 output received by the control unit. In this embodiment an inductive sensor called PMI-F110 commercially available from Pepperl+Fuchs GmbH, Mannheim, DE, was used. This type of inductive sensor comprises coils arranged in a coil array. Figures 3a and 3b illustrate the sensor arrangement 58 in more detail. As shown in Figure 3a the horizontal sensing array 84 of the first sensor element 64 may typically have a horizontal length SHL, as seen in parallel to the radius of the target disc 72, which is in the range of 50 to 500 mm. The metallic sensor target 74 may have a horizontal width THW which is in the range of, for example, 2 to 25 mm. The horizontal width THW of the metallic sensor target 74 is adapted to the type of first sensor element 64 that is utilized. In accordance with one example, the horizontal width THW of the metallic sensor target 74 may be 11 mm. The first sensor element 64 is arranged in the lower table plate 76 in such a position that the metallic sensor target 74 will be located above the horizontal sensing array 84 in the movement of the circular target disc 72. The horizontal sensing array 84 of the first sensor element 64 may detect the present horizontal position of the metallic sensor target 74 with a high accuracy. In accordance with one embodiment, the circular target disc 72 is made from an isolating material, such as a plastic material, in order not to interfere with the desired electrical interference between the sensor target 74 and the horizontal sensing array 84 of the first sensor element 64. The circular target disc 72 may be provided with target disc openings 86. The target disc openings 86 reduce the weight of the target disc 72. Furthermore, the target disc openings 86 provides for lubricating fluid, such as lubricating oil, splashing from the spherical cone crusher bearing 20 illustrated in Figure 1 to flow through the target disc 72, via the target disc openings 86, and further to the sensor table space 80. The lubricating fluid may, in the sensor table space 80, provide for lubrication of a horizontal sliding surface 88 of the lower table plate 76, over which the target disc 72 slides in the horizontal plane. Additionally, the upper table cover 78 may be provided with table cover openings 90, through which lubricating fluid may also flow to the sensor table space 80 for further improved lubrication. The target means connector 70 has a ball-joint type outer surface 92 which is in contact with a cylindrical inner periphery 94 of the target disc 72. Thereby, the swinging movement of the crushing shaft 30, to which the target means connector 70 is connected via the upper connector 44 and the cylindrical sleeve 32, as shown in Figure 1, is translated into a horizontal movement of the target disc 72. The horizontal movement of the target disc 72 is measured by the first sensor element 64 as the elongate horizontal sensing array 84 thereof detects the present horizontal position of the metallic sensor target 74. Based on the known geometry of the crusher 1 the measured present horizontal position of the metallic sensor target 74 can be recalculated into the present angle α between the shaft central axis SC and the crusher central axis CC, illustrated in Figure 2. For example, an outwardly horizontal movement of 70 mm of the metallic sensor target 74, compared to the position at a stopped crusher, as detected by the first sensor element 64 may be recalculated into an angle α of 2° between the shaft central axis SC and the crusher central axis CC. An electrical wire, schematically indicated as 85 in Figure 3a, may transmit electrical signals from the first sensor element 64 to a calculating device, such as a process computer, schematically indicated as 87 in Figure 3a, that recalculates the measured horizontal position to the angle α. Thereby, the first sensor element 64 provides for determining, via the measured horizontal position of the sensor target 74 of the target disc 72, the present angle α. Based on this information the operation of the crusher 1 can be controlled. Figure 3b illustrates the sensor arrangement 58 as seen from the top thereof. In accordance with one embodiment the sensor arrangement may comprise the first sensor element 64 and additionally also a second sensor element 96. The second sensor element 96 may typically be of the same design as the first sensor element 64 and may, as such, be of the type PMI-F110 commercially available from Pepperl+Fuchs GmbH, Mannheim, DE. The second sensor element 96 has an elongate horizontal sensing array 98 which is of a similar size and design as the horizontal sensing array 84. Looking in the horizontal plane, the horizontal sensing array 98 of the second sensor element 96 extends towards the crusher central axis CC at an angle β of, for example, 90° to the horizontal sensing array 84 of the first sensor element 64. By measuring the position of the metallic sensor target 74 by a first sensor element 64 and a second sensor element 96, that have different positions, it is possible to determine the position of the crushing shaft 30 in X-Y coordinates. This is particularly beneficial when the supply of material to the crushing chamber 56, shown in Figure 1, is uneven. Uneven supply of material to the crushing chamber 56 tends to make the crushing shaft 30 to swing at a higher angle in some directions, and at lower angle in other directions. By measuring the position of the crushing shaft 30 by means of the first and second sensor elements 64, 96 it becomes possible to determine where around the crushing chamber 56 the maximum and minimum angle α occurs, and to take steps to minimize the difference between the maximum and minimum angle α. Furthermore, if the difference between maximum and minimum angle is large this may be an indication that there is uncrushable objects in the crushing chamber 56. Hence, a large difference between maximum and minimum angle may be a trigger for stopping the crusher to remove the uncrushable object. Figure 4 illustrates one example of results obtained by using the sensor arrangement 58. The measurement "Sensor 1" illustrates a measurement signal obtained from the first sensor element 64 measuring the horizontal position of the metallic sensor target 74 located on the target disc 72. The measurement "Sensor 2" illustrates a measurement signal obtained from the second sensor element 96 measuring the horizontal position of the metallic sensor target 74 located on the target disc 72. As can be seen the measurement signals "Sensor 1" and "Sensor 2" are both close to sinusshaped, and the two signals are displaced in relation to each other, due to the angle β between the two sensor elements 64, 96. The curve "Angle min" illustrates the minimum angle α between the shaft central axis SC and the crusher central axis CC during a turn of the drive shaft 38 as determined from the measured horizontal positions, and the curve "Angle max" illustrates the maximum angle α between the shaft central axis SC and the crusher central axis CC during a turn of the drive shaft 38 as determined from the measured horizontal positions. Finally, the curve "Angle avg" illustrates the average angle α between the shaft central axis SC and the crusher central axis CC during a turn of the drive shaft 38 as determined from the measured horizontal positions. Figure 5 illustrates, schematically, how a current position of the crushing shaft 30 can be determined during operation of the gyratory crusher 1 shown in Figure 1. In Figure 5 it is shown, schematically and in a top view, how the metallic sensor target 74 moves inside the sensor table space 80. The present position of the metallic target 74 is measured simultaneously by means of the first sensor element 64 and the second sensor element 96, that are located at an angle β of 90°to each other, as seen in the horizontal plane. The centre MCP of the metallic target 74 is currently, due to the outward swinging of the unbalance weight 36 shown in Figure 1, located a horizontal distance OFS from the crusher central axis CC. Since the metallic target 74 is arranged on the circular target disc 72, as shown in, for example, Figure 2, which moves in concordance with the movement of the crushing shaft 30, the horizontal distance OFS can be used, together with the known vertical distance HP from the metallic target 74 to the pivot point PVP, shown in Figure 2, for calculation of the present angle α between the shaft central axis SC and the crusher central axis CC. The horizontal distance OFS can be calculated based on the distance D1 from the crusher central axis CC to the metallic target 74 as measured by the first sensor element 64, the distance D2 from the crusher central axis CC to the metallic target 74 as measured by the second sensor element 96, and the radius r of the metallic target 74. The following equation can be used: [MATHS id=math0001] Hereinbefore it has been described that the cone crusher shaft position measurement sensor arrangement 58 comprises a first sensor element 64, and optionally also a second sensor element 96. It will be appreciated that the sensor arrangement 58 may also comprise further sensor elements. The reason for using further sensor elements could be to further increase the accuracy of measuring the position of the crushing shaft, and/or to have one or more sensor elements as back-up, in case of failure of one sensor element. To summarize, a cone crusher shaft position measurement sensor arrangement (58) is arranged for measuring a position of a crushing shaft (30) of a cone crusher (1) of the type comprising an inner crushing shell (18), which is supported by a crushing head (16) mounted on the crushing shaft (30), and an outer crushing shell (12) which is supported on a crusher frame (2). The sensor arrangement (58) comprises a target means (62) adapted to be connected to the crushing shaft (30) and to move in a horizontal plane in concordance with the movement of the crushing shaft (30). The target means (62) comprises a sensor target (74).The sensor arrangement (58) further comprises at least one first sensor element (64) for sensing the horizontal position of the sensor target (74).

1. A cone crusher shaft position measurement sensor arrangement for measuring a position of a crushing shaft (30) of a cone crusher (1) of the type comprising an inner crushing shell (18), which is supported by a crushing head (16) mounted on the crushing shaft (30), and an outer crushing shell (12) which is supported on a crusher frame (2), characterised in the cone crusher shaft position measurement sensor arrangement (58) comprising a target means (62) adapted to be connected to the crushing shaft (30) and to move in a horizontal plane in concordance with the movement of the crushing shaft (30), the target means (62) comprising a sensor target (74), the sensor arrangement (58) further comprising at least one first sensor element (64) for sensing the horizontal position of the sensor target (74).

2. A sensor arrangement according to claim 1, wherein the target means (62) comprises a circular target disc (72). 3. A sensor arrangement according to any of the preceding claims, wherein the sensor target comprises a circular sensor target (74) extending around the target means (62). 4. A sensor arrangement according to any of the preceding claims, wherein the at least one first sensor element (64) comprises a horizontal sensing array (84) which extends in a horizontal direction and is arranged for sensing a horizontal position of the sensor target (74). 5. A sensor arrangement according to any of the preceding claims, wherein the sensor arrangement (58) comprises a sensor table (66) having a horizontal sliding surface (88) over which the target means (62) may slide in the horizontal plane. 6. A sensor arrangement according to any of the preceding claims, wherein the at least one first sensor element (64) comprises an inductive sensor. 7. A sensor arrangement according to any of the preceding claims, wherein the sensor arrangement comprises at least the first sensor element (64) and additionally a second sensor element (96), wherein the first and second sensor elements (64, 96) are arranged for sensing the horizontal position of the sensor target (74) in at least two different positions in the horizontal plane. 8. A sensor arrangement according to claim 7, wherein the first sensor element (64) and the second sensor element (96) each comprises a horizontal sensing array (84, 98) extending towards a crusher central axis (CC), wherein there is a horizontal angle β of at least 10°, more preferably an angle β of 20° to 160°, between the respective horizontal sensing arrays (84, 98). 9. A sensor arrangement according to any of the preceding claims, further comprising a calculating device (87) arranged for recalculating a horizontal position of the sensor target (74) measured by the at least one first sensor element (64) into an angle α between the crusher central axis (CC) and the shaft central axis (SC) of the crushing shaft (30). 10. A sensor arrangement according to any of the preceding claims, further comprising a target means connector (70) arranged to transfer the swinging movement of the crushing shaft (30) into a horizontal movement of the target means (62). 11. A cone crusher comprising an inner crushing shell (18), which is supported by a crushing head (16) mounted on a crushing shaft (30), and an outer crushing shell (12) which is supported on a crusher frame (2), characterised in the cone crusher comprising a cone crusher shaft position measurement sensor arrangement (58) according to any of the preceding claims. 12. A cone crusher according to claim 11, wherein the cone crusher is an inertia cone crusher (1) comprising a cylindrical sleeve (32) encircling the crushing shaft (30) and an unbalance weight (36) mounted on one side of the cylindrical sleeve (32).

2881176

Cone crusher shaft position measurement sensor arrangement

Based on the following detailed description of an invention, generate the patent claims. There should be 3 claims in total. The first, independent claim is given and the remaining 2 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 illustrates a cone crusher 1 in accordance with one embodiment of the present invention. The cone crusher illustrated in Figure 1 is of the inertia cone crusher type. It will be appreciated that the present invention is applicable also to other cone crusher types. The cone crusher 1 comprises a crusher frame 2 in which the various parts of the crusher 1 are mounted. The crusher frame 2 comprises an upper frame portion 4, and a lower frame portion 6. The upper frame portion 4 has the form of a bowl and is provided with an outer thread 8 which co-operates with an inner thread 10 of the lower frame portion 6. The upper frame portion 4 supports, on the inside thereof, an outer crushing shell 12. The outer crushing shell 12 is a wear part which may be made from, for example, manganese steel. The lower frame portion 6 supports an inner crushing shell arrangement 14. The inner crushing shell arrangement 14 comprises a crushing head 16, which has the form of a cone and which supports an inner crushing shell 18, which is a wear part which may be made from, for example, a manganese steel. The crushing head 16 rests on a spherical cone crusher bearing 20. The cone crusher bearing 20 has an upper bearing surface 22 which is in bearing contact with a lower surface 24 of the crushing head 16. The bearing surface 22 of the crusher bearing 20 has an at least partly concave shape, and the lower surface 24 of the crushing head 16 has an at least partly convex shape. The cone crusher bearing 20 rests on a bearing support 26 which is mounted on an inner cylindrical portion 28 of the lower frame portion 6. The crushing head 16 is mounted on a crushing shaft 30. The crushing shaft 30 extends through the cone crusher bearing 20. Hence, the cone crusher bearing 20 forms a "collar" encircling the crushing shaft 30. At a lower end thereof, the crushing shaft 30 is encircled by a cylindrical sleeve 32. The cylindrical sleeve 32 is provided with an inner cylindrical bearing 34 making it possible for the cylindrical sleeve 32 to rotate around the crushing shaft 30. An unbalance weight 36 is mounted on one side of the cylindrical sleeve 32. At its lower end the cylindrical sleeve 32 is connected to a vertical drive shaft 38. The drive shaft 38 comprises a ball spindle 40, a pulley shaft 42, an intermediate shaft 43 connecting the ball spindle 40 to the pulley shaft 42, an upper connector 44 which connects the ball spindle 40 to the cylindrical sleeve 32, and a lower connector 46 which is arranged on the intermediate shaft 43 and which connects the ball spindle 40 to the intermediate shaft 43. The two connectors 44, 46 are connected to the ball spindle 40 in a non-rotating manner, such that rotational movement can be transferred from the pulley shaft 42 to the cylindrical sleeve 32 via the intermediate shaft 43 and the ball spindle 40. A bottom portion 48 of the lower frame portion 6 comprises a vertical cylindrical drive shaft bearing 50 in which the vertical drive shaft 38 is supported. A motor (not shown) is arranged for driving a pulley 52 which is connected to the pulley shaft 42, below the drive shaft bearing 50. Lubricant is collected at the inside of the bottom portion 48 and is returned to a lubricant pump (not shown) via a lubricant return pipe 54. The outer and inner crushing shells 12, 18 form between them a crushing chamber 56 to which material that is to be crushed is supplied. The discharge opening of the crushing chamber 56, and thereby the crushing capacity, can be adjusted by means of turning the upper frame portion 4, by means of the threads 8, 10, such that the distance between the shells 12, 18 is adjusted. When the crusher 1 is in operation the drive shaft 38 is rotated by means of the not shown motor. The rotation of the drive shaft 38 causes the sleeve 32 to rotate and as an effect of that rotation the sleeve 32 is swung outwards by means of the unbalance weight 36, displacing the unbalance weight 36 further away from the crusher central axis CC of the crusher 1, in response to the centrifugal force to which the unbalance weight 36 is exposed. Such displacement of the unbalance weight 36 and of the cylindrical sleeve 32 to which the unbalance weight 36 is attached is allowed thanks to the ball spindle 40 and thanks to the fact that the sleeve 32 may slide somewhat, thanks to the cylindrical bearing 34, in the vertical direction along the crushing shaft 30. The combined rotation and swinging of the cylindrical sleeve 32 with unbalance weight 36 mounted thereon causes an inclination of the crushing shaft 30, and makes the crushing shaft 30 gyrate, such that material is crushed between the outer and inner crushing shells 12, 18 forming between them the crushing chamber 56. During operation of the crusher 1 it is important to know the manner in which the crushing shaft 30 moves to be able to properly control the operation of the crusher 1. The movement of the crushing shaft 30 will be influenced by, among other things, the amount and the properties of the material forwarded to the crushing chamber 56, the distribution of the material around the crushing chamber 56, the rpm at which the drive shaft 38 rotates the cylindrical sleeve 32, and the existence of any pieces of uncrushable material in the crushing chamber 56. To this end a cone crusher shaft position measurement sensor arrangement 58 is arranged at a bottom 60 of the lower frame portion 6. The sensor arrangement 58 comprises a target means 62 arranged to move in a horizontal direction in concordance with the movement of the upper connector 44. Since the upper connector 44 is connected to the cylindrical sleeve 32, which in turn is connected, via cylindrical bearing 34, to the crushing shaft 30, the target means 62 will move in a horizontal plane in concordance with the movement of the crushing shaft 30. The sensor arrangement 58 further comprises at least one first sensor element 64. The first sensor element 64 is arranged for detecting the horizontal position of the target means 62 in a manner which will be described in more detail hereinafter. The sensor arrangement 58 comprises a sensor table 66. The sensor table 66 supports in a sliding manner the target means 62 such that the target means 62 can move in the horizontal direction. Furthermore, the sensor table 66 also provides a support for the first sensor element 64. The sensor table 66 is mounted to the lower frame portion 6 by means of table supporting legs 68. A target means connector 70 is mounted to the upper connector 44 to transfer the movement of the upper connector 44 to the target means 62. Figure 2 illustrates the sensor arrangement 58 in more detail, and when the crusher 1 is in operation. When the crusher 1 is in operation the drive shaft 38 rotates the sleeve 32, and the unbalance weight 36 shown in Figure 1 will swing the cylindrical sleeve 32, and thereby the crushing shaft 30, to the side. Thereby, a shaft central axis SC, which is the central axis of the crushing shaft 30, will deviate from the crusher central axis CC. Hence, there will be an angle α between the shaft central axis SC and the crusher central axis CC. This angle α will provide crucial information about the operation of the crusher and is measured by means of the sensor arrangement 58. The target means 62 comprises a circular target disc 72, which is preferably made from a non-conductive material, such as a polymer material, and a circular metallic sensor target 74 extending around the circular target disc 72. The sensor table 66 comprises a lower table plate 76 and an upper table cover 78 that may, in accordance with one embodiment, be formed from non-conductive materials, for example polymer materials. The lower table plate 76 and the upper table cover 78 form between them a sensor table space 80 in which the target disc 72 may move, sliding on the lower table plate 76. The sensor table space 80 limits the vertical movements of the target disc 72, preferably to such a degree that the target disc 72 can move less than +/- 5 mm, more preferably less than +/- 2 mm, in the vertical direction. The sensor table space 80 has a horizontal width which is larger than the diameter of the target disc 72, to account for the fact that the target disc 72 is swung to the side upon operation of the crusher. The crusher central axis CC and the shaft central axis SC intersect in a pivot point PVP. The vertical position of the pivot point PVP, and thereby a vertical distance HP between the pivot point PVP and the lower side of the metallic target 74, is set by the geometry, i.e. the radius, of the spherical cone crusher bearing 20 that supports the crushing head 16 and the crushing shaft 30, as illustrated in Figure 1. Thereby, by determining the horizontal position of the metallic target 74 in relation to the crusher central axis CC it becomes possible to calculate, based on such horizontal position and the known vertical distance HP, the angle α between the shaft central axis SC and the crusher central axis CC. The first sensor element 64 is arranged in a sensor space 82 formed in the lower table plate 76. The sensor space 82 extends under the sensor table space 80 to enable the first sensor element 64 to sense a present position of the metallic sensor target 74 of the target disc 72. The first sensor element 64 comprises an elongate horizontal sensing array 84 which extends in a horizontal direction and towards the crusher central axis CC. In this embodiment the first sensor element 64 comprises an inductive position sensor. Such an inductive position sensor generates an inductive field which shifts along a sensitive surface and detects a metallic sensor target in the detection range of the inductive field. The inductive sensor comprises several coils arranged in a coil array. Hence, in this embodiment the horizontal sensing array 84 comprises a coil array. The inductive sensor 64 calculates the current position of the sensor target 74 and provides output as, for example, a distance-proportional analog signal. The inductive sensing field extends along the horizontal length of the horizontal sensing array 84. The first sensor element 64 is thus able to detect the horizontal position along the horizontal sensing array 84 of the metallic sensor target 74 without any physical contact therewith. The sensor output is received by a control unit (not shown) connected to the first sensor element 64. During operation of the sensor arrangement 58, the first sensor element 64 emits an alternating electro-magnetic sensing field along the sensing array 84. When the metallic sensor target 74 enters the sensing field eddy currents are induced in the target 74 which reduces the signal amplitude of the first sensor element 64 and triggers a change of state at the sensor element 64 output received by the control unit. In this embodiment an inductive sensor called PMI-F110 commercially available from Pepperl+Fuchs GmbH, Mannheim, DE, was used. This type of inductive sensor comprises coils arranged in a coil array. Figures 3a and 3b illustrate the sensor arrangement 58 in more detail. As shown in Figure 3a the horizontal sensing array 84 of the first sensor element 64 may typically have a horizontal length SHL, as seen in parallel to the radius of the target disc 72, which is in the range of 50 to 500 mm. The metallic sensor target 74 may have a horizontal width THW which is in the range of, for example, 2 to 25 mm. The horizontal width THW of the metallic sensor target 74 is adapted to the type of first sensor element 64 that is utilized. In accordance with one example, the horizontal width THW of the metallic sensor target 74 may be 11 mm. The first sensor element 64 is arranged in the lower table plate 76 in such a position that the metallic sensor target 74 will be located above the horizontal sensing array 84 in the movement of the circular target disc 72. The horizontal sensing array 84 of the first sensor element 64 may detect the present horizontal position of the metallic sensor target 74 with a high accuracy. In accordance with one embodiment, the circular target disc 72 is made from an isolating material, such as a plastic material, in order not to interfere with the desired electrical interference between the sensor target 74 and the horizontal sensing array 84 of the first sensor element 64. The circular target disc 72 may be provided with target disc openings 86. The target disc openings 86 reduce the weight of the target disc 72. Furthermore, the target disc openings 86 provides for lubricating fluid, such as lubricating oil, splashing from the spherical cone crusher bearing 20 illustrated in Figure 1 to flow through the target disc 72, via the target disc openings 86, and further to the sensor table space 80. The lubricating fluid may, in the sensor table space 80, provide for lubrication of a horizontal sliding surface 88 of the lower table plate 76, over which the target disc 72 slides in the horizontal plane. Additionally, the upper table cover 78 may be provided with table cover openings 90, through which lubricating fluid may also flow to the sensor table space 80 for further improved lubrication. The target means connector 70 has a ball-joint type outer surface 92 which is in contact with a cylindrical inner periphery 94 of the target disc 72. Thereby, the swinging movement of the crushing shaft 30, to which the target means connector 70 is connected via the upper connector 44 and the cylindrical sleeve 32, as shown in Figure 1, is translated into a horizontal movement of the target disc 72. The horizontal movement of the target disc 72 is measured by the first sensor element 64 as the elongate horizontal sensing array 84 thereof detects the present horizontal position of the metallic sensor target 74. Based on the known geometry of the crusher 1 the measured present horizontal position of the metallic sensor target 74 can be recalculated into the present angle α between the shaft central axis SC and the crusher central axis CC, illustrated in Figure 2. For example, an outwardly horizontal movement of 70 mm of the metallic sensor target 74, compared to the position at a stopped crusher, as detected by the first sensor element 64 may be recalculated into an angle α of 2° between the shaft central axis SC and the crusher central axis CC. An electrical wire, schematically indicated as 85 in Figure 3a, may transmit electrical signals from the first sensor element 64 to a calculating device, such as a process computer, schematically indicated as 87 in Figure 3a, that recalculates the measured horizontal position to the angle α. Thereby, the first sensor element 64 provides for determining, via the measured horizontal position of the sensor target 74 of the target disc 72, the present angle α. Based on this information the operation of the crusher 1 can be controlled. Figure 3b illustrates the sensor arrangement 58 as seen from the top thereof. In accordance with one embodiment the sensor arrangement may comprise the first sensor element 64 and additionally also a second sensor element 96. The second sensor element 96 may typically be of the same design as the first sensor element 64 and may, as such, be of the type PMI-F110 commercially available from Pepperl+Fuchs GmbH, Mannheim, DE. The second sensor element 96 has an elongate horizontal sensing array 98 which is of a similar size and design as the horizontal sensing array 84. Looking in the horizontal plane, the horizontal sensing array 98 of the second sensor element 96 extends towards the crusher central axis CC at an angle β of, for example, 90° to the horizontal sensing array 84 of the first sensor element 64. By measuring the position of the metallic sensor target 74 by a first sensor element 64 and a second sensor element 96, that have different positions, it is possible to determine the position of the crushing shaft 30 in X-Y coordinates. This is particularly beneficial when the supply of material to the crushing chamber 56, shown in Figure 1, is uneven. Uneven supply of material to the crushing chamber 56 tends to make the crushing shaft 30 to swing at a higher angle in some directions, and at lower angle in other directions. By measuring the position of the crushing shaft 30 by means of the first and second sensor elements 64, 96 it becomes possible to determine where around the crushing chamber 56 the maximum and minimum angle α occurs, and to take steps to minimize the difference between the maximum and minimum angle α. Furthermore, if the difference between maximum and minimum angle is large this may be an indication that there is uncrushable objects in the crushing chamber 56. Hence, a large difference between maximum and minimum angle may be a trigger for stopping the crusher to remove the uncrushable object. Figure 4 illustrates one example of results obtained by using the sensor arrangement 58. The measurement "Sensor 1" illustrates a measurement signal obtained from the first sensor element 64 measuring the horizontal position of the metallic sensor target 74 located on the target disc 72. The measurement "Sensor 2" illustrates a measurement signal obtained from the second sensor element 96 measuring the horizontal position of the metallic sensor target 74 located on the target disc 72. As can be seen the measurement signals "Sensor 1" and "Sensor 2" are both close to sinusshaped, and the two signals are displaced in relation to each other, due to the angle β between the two sensor elements 64, 96. The curve "Angle min" illustrates the minimum angle α between the shaft central axis SC and the crusher central axis CC during a turn of the drive shaft 38 as determined from the measured horizontal positions, and the curve "Angle max" illustrates the maximum angle α between the shaft central axis SC and the crusher central axis CC during a turn of the drive shaft 38 as determined from the measured horizontal positions. Finally, the curve "Angle avg" illustrates the average angle α between the shaft central axis SC and the crusher central axis CC during a turn of the drive shaft 38 as determined from the measured horizontal positions. Figure 5 illustrates, schematically, how a current position of the crushing shaft 30 can be determined during operation of the gyratory crusher 1 shown in Figure 1. In Figure 5 it is shown, schematically and in a top view, how the metallic sensor target 74 moves inside the sensor table space 80. The present position of the metallic target 74 is measured simultaneously by means of the first sensor element 64 and the second sensor element 96, that are located at an angle β of 90°to each other, as seen in the horizontal plane. The centre MCP of the metallic target 74 is currently, due to the outward swinging of the unbalance weight 36 shown in Figure 1, located a horizontal distance OFS from the crusher central axis CC. Since the metallic target 74 is arranged on the circular target disc 72, as shown in, for example, Figure 2, which moves in concordance with the movement of the crushing shaft 30, the horizontal distance OFS can be used, together with the known vertical distance HP from the metallic target 74 to the pivot point PVP, shown in Figure 2, for calculation of the present angle α between the shaft central axis SC and the crusher central axis CC. The horizontal distance OFS can be calculated based on the distance D1 from the crusher central axis CC to the metallic target 74 as measured by the first sensor element 64, the distance D2 from the crusher central axis CC to the metallic target 74 as measured by the second sensor element 96, and the radius r of the metallic target 74. The following equation can be used: [MATHS id=math0001] Hereinbefore it has been described that the cone crusher shaft position measurement sensor arrangement 58 comprises a first sensor element 64, and optionally also a second sensor element 96. It will be appreciated that the sensor arrangement 58 may also comprise further sensor elements. The reason for using further sensor elements could be to further increase the accuracy of measuring the position of the crushing shaft, and/or to have one or more sensor elements as back-up, in case of failure of one sensor element. To summarize, a cone crusher shaft position measurement sensor arrangement (58) is arranged for measuring a position of a crushing shaft (30) of a cone crusher (1) of the type comprising an inner crushing shell (18), which is supported by a crushing head (16) mounted on the crushing shaft (30), and an outer crushing shell (12) which is supported on a crusher frame (2). The sensor arrangement (58) comprises a target means (62) adapted to be connected to the crushing shaft (30) and to move in a horizontal plane in concordance with the movement of the crushing shaft (30). The target means (62) comprises a sensor target (74).The sensor arrangement (58) further comprises at least one first sensor element (64) for sensing the horizontal position of the sensor target (74).

13. A method of measuring a position of a crushing shaft of a cone crusher of the type comprising an inner crushing shell (18), which is supported by a crushing head (16) mounted on the crushing shaft (30), and an outer crushing shell (12) which is supported on a crusher frame (2), characterised in connecting a target means (62) to the crushing shaft (30), moving the target means (62) in a horizontal plane in concordance with the movement of the crushing shaft (30), and sensing the horizontal position of the target means (62) by at least one first sensor element (64).

14. A method according to claim 13, further comprising recalculating a horizontal position of the target means (62) measured by the at least one first sensor element (64) into an angle α between the crusher central axis (CC) and the shaft central axis (SC) of the crushing shaft (30). 15. A method according to any one of claims 13-14, further comprising measuring the horizontal position of the target means (62) by at least a first and a second sensor element (64, 96) in two different positions in the horizontal plane.

2881201

Cutting insert

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to Figures 1-2, a disposable carving blade 10 comprises a central hole 11 defined at a central position thereof, a first central line 15 passing through the central position thereof, a right cutting rim 12 formed on a first peripheral side thereof and a left cutting rim 13 formed on a second peripheral side thereof, wherein the right cutting rim 12 is connected with the left cutting rim 13 to form a V-shaped portion, the V-shaped portion includes a cutting edge 14 defined on a distal end thereof. The disposable carving blade 10 also comprises another right cutting rim 12 arranged on a third peripheral side thereof symmetrical and parallel to the right cutting rim 12 on the first peripheral side of the disposable carving blade 10 and comprises another left cutting rim 13 arranged on a fourth peripheral side thereof symmetrical and parallel to the left cutting rim 13 on the second peripheral side of the disposable carving blade 10. A distance between the two left cutting rims 13 is a first rim spacing value L1, and a distance between the two right cutting rims 12 is a second rim spacing value L2. An intersection point of the right cutting rim 12 on the first peripheral side of the disposable carving blade 10 and the left cutting rim 13 on the second peripheral side of the disposable carving blade 10 is adjacent to the first central line 15, and a distance between the intersection point and the first central line 15 is a first eccentric value e, a width radius Y is defined between a distal end of the cutting edge 14 and the first central line 15, and the first eccentric value e is set based on using requirement. Since a length of each right cutting rim 12 is not symmetrical to that of each left cutting rim 13, and the intersection point is not located at the first central line 15 (i.e., is adjacent to the first central line 15), the first rim spacing value L1 defined between the two left cutting rims 13 is different from the second rim spacing value L2 defined between the two right cutting rims 12. In more detail, the disposable carving blade 10 is substantially formed in a parallelogram shape, and when the intersection point of the right cutting rim 12 on the first peripheral side of the disposable carving blade 10 and the left cutting rim 13 on the second peripheral side of the disposable carving blade 10 is located beside the right side of the first central line 15, the length of the right cutting rim 12 is shorter than that of the left cutting rim 13. That is, the second rim spacing value L2 defined between the two right cutting rims 12 is larger than the first rim spacing value L1 defined between the two left cutting rims, and when a difference between the first rim spacing value L1 and the second rim spacing value L2 changes, the first eccentric value e changes accordingly. Referring to Figures 3 and 4, a cutter arbor 20 includes a holder 21 on a distal end thereof and a second central line 200 defined thereon. The holder 21 has a screw orifice 211 formed at a central position thereof, wherein the second central line 200 of the cutter arbor 20 passes through a central point of the screw orifice 211 of the holder 21, i.e., the holder 21 is not eccentric relative to the cutter arbor 20. The central hole 11 of the disposable carving blade 10 corresponds in shape to the screw orifice 211 of the holder 21 so that the disposable carving blade 10 is locked in the screw orifice 211 of the holder 21. Thereby, the first eccentric value e is produced by merely arranging the right cutting rim 12 asymmetrically to the left cutting rim 13 of the disposable carving blade 10, and when a length of each right cutting rim 12 and that of each left cutting rim 13 are changed, the first eccentric value e is also changed. In an embodiment, as shown in Figures 5 and 6, the first eccentric value e of the disposable carving blade 10 is 0.01 mm, the width radius Y is 0.05 mm, and a width of a slot cut by the disposable carving blade 10 is 0.1 mm, wherein the disposable carving blade 10 is locked on the holder 21 of the cutter arbor 20. In this embodiment, the second central line 200 of the cutter arbor 20 passes through the central point of the screw orifice 211 of the holder 21, i.e., the holder 21 is not eccentric relative to the cutter arbor 20. It is noted that the left cutting rim 13 on the second peripheral side of the disposable carving blade 10 does not extend to the right side of the second central line 200, such that the left cutting rim 13 cannot interfere a cutting process. It is preferable that when the cutting edge 14 becomes dull, the disposable carving blade 10 is rotated upside down to cut a workpiece by ways of another cutting edge 14. In addition, a new disposable carving blade 10 is used to replace the dull disposable carving blade 10. In another embodiment, as illustrated in Figures 7 and 8, the first eccentric value e of the disposable carving blade 10 is 0.02 mm, the width radius Y is 0.1 mm, and a width of a slot cut by the disposable carving blade 10 is 0.2 mm, wherein the disposable carving blade 10 is locked on the holder 21 of the cutter arbor 20. In this embodiment, the second central line 200 of the cutter arbor 20 passes through the central point of the screw orifice 211 of the holder 21, i.e., the holder 21 is not eccentric relative to the cutter arbor 20. It is noted that the left cutting rim 13 on the second peripheral side of the disposable carving blade 10 does not extend to the right side of the second central line 200, such that the left cutting rim 13 cannot interfere the cutting process. Preferably, when the cutting edge 14 becomes dull, the disposable carving blade 10 is rotated upside down to cut the workpiece by ways of another cutting edge 14. Moreover, a new disposable carving blade 10 is applied to replace the dull disposable carving blade 10. In further embodiment, referring to Figures 9 and 10, the first eccentric value e of the disposable carving blade 10 is 0.03 mm, the width radius Y is 0.15 mm, and a width of a slot cut by the disposable carving blade 10 is 0.3 mm, wherein the disposable carving blade 10 is locked on the holder 21 of the cutter arbor 20. In this embodiment, the second central line 200 of the cutter arbor 20 passes through the central point of the screw orifice 211 of the holder 21, i.e., the holder 21 is not eccentric relative to the cutter arbor 20. It is noted that the left cutting rim 13 on the second peripheral side of the disposable carving blade 10 does not extend to the right side of the second central line 200, such that the left cutting rim 13 cannot interfere the cutting process. It is preferable that when the cutting edge 14 becomes dull, the disposable carving blade 10 is rotated upside down to cut a workpiece by ways of another cutting edge 14. Furthermore, a new disposable carving blade 10 is served to replace the dull disposable carving blade 10. Accordingly, as the first eccentric value e is directly defined on the disposable carving blade 10, the user can change the width radius Y as well as the first eccentric value e by merely selecting a desired disposable carving blade 10 without replacing the cutter arbor 20, such that the assembly between the cutter arbor 20 and the disposable carving blade 10 is facilitated. Preferably, the disposable carving blade 10 is manufactured by means of powder metallurgy, so the first eccentric value e is formed directly without being ground, thereby lowering production cost and improving manufacturing accuracy. Moreover, referring to Figures 11 and 12, the disposable carving blade 10 can also cooperate with another holder 21 which includes a third central line 2110 passing through the central position of the screw orifice 211, and a second eccentric value E is defined between the third central line 2110 and the second central line 200 of the cutter arbor 20. The second eccentric value E is set according to using requirement so as to increase the width radius Y. In other words, the width radius Y can be changed by merely replacing the cutter arbor 20 without replacing the disposable carving blade 10. Accordingly, by using the disposable carving blade 10 and the cutter arbor 20 of the present invention, the user can merely replace the disposable carving blade 10 or the cutter arbor 20 to achieve various slot widths, thereby saving using cost and avoiding assembling the cutter arbor 20 and the disposable carving blade 10 in different specification.

1. A disposable carving blade (10) comprising: a central hole (11) defined at a central position thereof, a first central line (15) passing through the central position thereof, a right cutting rim (12) formed on a first peripheral side thereof and a left cutting rim (13) formed on a second peripheral side thereof, characterized in that the right cutting rim (12) is connected with the left cutting rim (13) to form a V-shaped portion, the V-shaped portion includes a cutting edge (14) defined on a distal end thereof, and an intersection point of the right cutting rim (12) on the first peripheral side of the disposable carving blade and the left cutting (13) rim on the second peripheral side of the disposable carving blade (10) is adjacent to the first central line (15), and a distance between the intersection point and the first central line (15) is a first eccentric value (e).

2. The disposable carving blade as claimed in claim 1, wherein a length of the right cutting rim (12) is not symmetrical to that of the left cutting rim (13). 3. The disposable carving blade as claimed in claim 2, further comprising another right cutting rim (12) arranged on a third peripheral side thereof symmetrical and parallel to the right cutting rim (12) on the first peripheral side of the disposable carving blade and comprising another left cutting rim (13) arranged on a fourth peripheral side thereof symmetrical and parallel to the left cutting rim (13) on the second peripheral side of the disposable carving blade, wherein a distance between the two left cutting rims (13) is a first rim spacing value (L1), and a distance between the two right cutting rims (12) is a second rim spacing value (L2). 4. The disposable carving blade as claimed in claim 3, wherein the intersection point is located beside a right side of the first central line (15), and the first rim spacing value (L1) defined between the two left cutting rims (13) is less than the second rim spacing value (L2) defined between the two right cutting rims (12). 5. The disposable carving blade as claimed in claim 3, wherein the intersection point is located beside a left side of the first central line (15), and the second rim spacing value (L2) defined between the two right cutting rims (12) is less than the first rim spacing value (L1) defined between the two left cutting rims (13).

2883667

Device for gripping vessels

Based on the following detailed description of an invention, generate the patent claims. There should be 13 claims in total. The first, independent claim is given and the remaining 12 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In the following, an exemplary device 1 for gripping vessels 2 according to the invention is explained. As schematically illustrated in Figure 1, the device 1 can, e.g., be part of a system (instrument) for processing samples (not further detailed), generally referred to at reference numeral 100, such as an analytical system (instrument) for processing samples by one or more analytical methods such as, but not limited to, photometric methods, involving the use of vessels, such as, but not limited to cuvettes. The device 1 for gripping vessels 2 comprises a stationary mount 3 having a bottom plate 4, a top plate 5 and a vertical beam 6, with the beam 6 being fixed to the bottom plate 4 and the top plate 5 being fixed to the beam 6. The device 1 further comprises an elongate vertical support 7 having a longitudinal axis 8 which is rotatably fixed to the mount 3. Stated more particularly, the vertical support 7 is rotatably fixed to both the bottom plate 4 and the top plate 5 by means of rotational bearings (not further detailed) so as to be rotatable around the longitudinal axis 8. A rotating mechanism 9 is coupled to the support 7 for rotating the support 7 around the longitudinal axis 8. Specifically, the rotating mechanism 9 is configured as a belt drive comprising an electric motor 10 for driving a belt 11. As illustrated, in one embodiment, the belt 11 is wound around a driving wheel 12 fixed in rotation to the support 7 so that the support 7 can be rotated together with the wheel 12 which is rotated by the motor-driven belt 11. The device 1 comprises a gripper 13 provided with two gripping jaws 15, 15' for gripping a vessel 2. As can best be seen in Figure 3, each vessel 2 comprises a bottom-closed body 32 open on the top for receiving liquid. The body 32 comprises side walls 33 provided with a flange 34 projecting perpendicularly from the side walls 33 and being integrally formed therewith. As illustrated, the upper gripping jaw 15' and the flange 34 are provided with two pairs of engagement elements, each of which consisting of a projection 35 and a depression 36. Specifically, in one embodiment, as illustrated, the flange 34 has two depressions 36 and the upper gripping jaw 15' has two projections 35 for engagement with the depressions 36. Accordingly, the reliability of gripping and holding a vessel 2 can be improved so as to reduce the risk of a failure. The gripper 13 is fixed to the support 7 in a manner to be translatable along the longitudinal axis 8. Specifically, in one embodiment, the support 7 is provided with a gripper guide 14 extending along the longitudinal axis 8 of the support 7 in vertical direction for guiding the gripper 13. Accordingly, the gripper 13 can be translated along the gripper guide 14. A translating mechanism 37 is coupled to the gripper 13 for translating the gripper 13 along the gripper guide 14. Specifically, the translating mechanism 37 is configured as belt drive comprising an electric motor 10' for driving a belt 11'. The belt 11' is wound around a driving wheel 12' that is coupled to another belt 11'' fixed in translation to the gripper 13. Accordingly, the gripper 13 can be translated along the gripper guide 14 by driving the belt 11" by rotating the wheel 12', with the latter one being rotated by the motor-driven belt 11'. Accordingly, the gripper 13 can be rotated by driving the wheel 12 and can be translated by driving the wheel 12'. Since the electric motors 10, 10' can be independently controlled with respect to each other, the gripper 13 can be rotated or translated or can have a combined translational/rotational movement. As can, e.g., be seen in Figure 1, the device 1 further comprises a lower reference element 16 and two upper reference elements 17, 17', each of which being shaped as a ring segment covering a range of segment angles, e.g. between 45° and 180°. It, however, is to be understood that any other range of segment angles can be envisaged according to the specific demands of the user. Specifically, the reference elements 16, 17, 17' are fixed to the mount 3 so as to be stationary with respect to the support 7 and gripper 13, respectively. Each reference element 16, 17, 17' defines a stop position 38, 39, 39' for a vertical movement (translation) of the gripper 13, with the lower reference element 16 defining a lower stop position 38 and the two upper reference elements 17, 17' defining two upper stop positions 39, 39' so that the device 1 has stop positions in two different heights (positions of the longitudinal axis 8). The gripping jaws 15, 15' are passively biasable towards each other to close the gripper 13 for holding a vessel 2 between the stop positions as defined by the reference elements 16, 17, 17' and are actively biasable away from each other to open the gripper 13 by pushing the gripper 13 against a reference element 16, 17, 17' in a stop position 38, 39, 39'. The gripper 13 can be pushed against one reference element 16, 17, 17' by translating and/or rotating the gripper 13. Due to the vertical orientation of the support 7, the upper reference elements 17, 17' are in a higher position than the lower reference element 16, with the upper reference elements 17, 17' being on opposite sides of the support 7. Specifically, the stop position 38 of the lower reference element 16 can, e.g., be located in correspondence to a picking position 103 of the system 100 for picking-up separated vessels 2 provided by an automated separator 101 for separating vessels 2 supplied in bulk form and providing separated vessels 2 at the picking position 103. Thus, the stop positions 39, 39' of the upper reference elements 17, 17' can be located in correspondence to an analytical compartment 102 of the system 100 for releasing or gripping vessels 2, e.g., for analyzing samples. Due to the arrangement of the upper reference elements 17, 17', vessels 2 can also be released on opposite sides of the support 7. One stop position of the upper reference elements 17, 17' can, e.g., be used for releasing vessels 2 into a waste compartment (not illustrated) of the system 100 or into a second analytical compartment. Each of the reference elements 16, 17, 17' has an upper guiding face 40 for guiding the gripper 13. In one embodiment, the guiding face 40 is configured as sliding face for sliding engagement with the gripper 13. Accordingly, the gripper 13 can be kept open in case of rotating the gripper 13 around the rotational axis 8. As a result, vessels 2 can be taken up or released in a broad range of angles of a stop position 38, 39, 39'. Specifically, as can be seen in Figure 2, the gripper base 19 is provided with a contact wheel 42 for rolling on the guiding face 40 by rotating the gripper 13 around the mount 3. Accordingly, a friction between the gripper 13 and a reference element 16, 17, 17' can advantageously be reduced. With particular reference to Figures 3 and 5 to 8, the gripper 13 comprises a gripper head 18 and a gripper base 19. Specifically, the gripper head 18 is translatably fixed to the support 7 guidable (guided) by the gripper guide 14. Accordingly, the gripper head 18 can be translated along the gripper guide 14 by driving the translating mechanism 37 as above-described. The gripper head 19 is movably fixed to the gripper base 18 in a manner to be movable relative to the gripper base 18 against the resilient force of resilient members 20, 20' by pushing the gripper base 19 against a reference element 16, 17, 17'. Specifically, the gripper base 19 comprises two gripper legs 21, 21', each of which being provided with one gripping jaw 15, 15' at an end portion thereof. As illustrated, in one embodiment, the gripper legs 21, 21', e.g., are configured as a lower gripper leg 21 provided with the lower gripping jaw 15 and an upper gripper leg 21' provided with the upper gripping jaw 15' so that the flange 34 of a vessel 2 in an up-right position can readily be gripped. As can best be seen in Figures 7 and 8, the gripper base 19 further comprises a leg support 22, e.g. configured as a (e.g. vertical) plate-like member for fixing of the gripper legs 21, 21' in a manner that the gripper legs 21, 21' are movable (moved) together with the leg support 22, with the gripping jaws 15, 15' being movable towards and away from each other. A first resilient element 20, such as but not limited to a compression spring, is arranged between the leg support 22 and a push element 23 which is also a component of the gripper base 19. The push element 23 can be used to push the gripper base 19 against a reference element 16, 17, 17' in a stop position 38, 39, 39'. At the distant end of the leg support 22 relative to the gripping jaws 15, 15', the leg support 22 is connected to an elongate guiding link 24, such as but not limited to a connecting rod, which on one side is fixed to the push element 23 and on the other side is provided with a base guiding element 25, such as but not limited to a guiding roller, guidable (guided) by a base guide 26 provided by the gripper head 18. Specifically, as illustrated, the base guide 26 can, e.g., be configured as a linear recess extending inclined with respect to the longitudinal axis 8. Accordingly, in case the push element 23 is pushed against a reference element 16, 17, 17' by translating the gripper 13 (i.e. gripper head 18), the gripper head 18 can be moved relative to the gripper base 19, with the gripping jaws 15, 15' being drawn away guided by the base guide 26 so as to have a component of movement perpendicular to the longitudinal axis 8. Since the gripper legs 21, 21' are fixed to the leg support 22, the gripper legs 21, 21' can be moved together with the leg support 22. A second resilient element 20', such as but not limited to a compression spring, is arranged between the gripper head 18 and the gripper base 19 so as to increase the resilient force when pushing the push element 23 against a reference element 16, 17, 17'. Accordingly, the gripper base 19 (and the gripper legs 21, 21') can be pushed back (reverse movement) by the resilient force of the second resilient force 20' in a position of the gripping jaws 15, 15' other than a stop position 38, 39, 39'. As illustrated, the gripper head 18 further comprises two jaw guiding elements 29 arranged on both sides of the gripping legs 21, 21'. The jaw guiding elements 29 can, e.g., be configured as plates which, e.g., are vertically arranged in parallel arrangement with the leg support 22. Each of the jaw guiding elements 29 is provided with two jaw guides 30, 30' arranged above/below of each other in correspondence to the gripper legs 21, 21' for guiding of the gripper legs 21, 21' and gripping jaws 15, 15', respectively. As illustrated, in one embodiment, each jaw guide 30, 30' is configured as a recess or through-hole formed by the jaw guiding element 29, with a leg nose 31 (see Figure 2 ) projecting from each of the gripper legs 21, 21' being inserted in the jaw guide 30, 30' for guiding of the gripper leg 21, 21'. Accordingly, the gripper legs 21, 21' can be moved relative to the jaw guiding elements 29 when moving the gripper head 18 relative to the gripper base 19, e.g., by pushing the gripper base 19 against a reference element 16, 17, 17' in a stop position 38, 39, 39'. As illustrated, the jaw guides 30, 30' of each of the jaw guiding elements 29 are shaped in a manner to move the gripping jaws 15, 15' away from each other by pushing the gripper base 19 against a reference element 16, 17, 17' or to move the gripping jaws 15, 15' towards each other in gripper positions other than the stop positions 38, 39, 39'. Accordingly, by pushing the gripper base 19 and push element 23, respectively, against a reference element 16, 17, 17', the gripper legs 21, 21' can be moved backwards to have a component of movement perpendicular to the longitudinal axis 8 so as to move the gripping jaws 15, 15' away from each other. Furthermore, the gripper legs 21, 21' can be moved forwards (in the reverse direction) by the resilient force of the resilient element 21' so as to move the gripping jaws 15, 15' towards each other. The forward and backward movement of the gripping jaws 15, 15' can advantageously be used for gripping or releasing a vessel 2. As illustrated in Figure 1, the device 1 for gripping vessels 2 can be part of a system 100 for analyzing samples, comprising a separator 101 for separating vessels 2 supplied in bulk form and providing single vessels 2 to a picking position 103 and at least one analytical compartment 102 for analyzing samples with the vessels 2. Specifically, the picking position 103 can be located in correspondence to the stop position 38 of, e.g., the lower reference element 16 so as to pick up separated vessels 2 by the gripper 13 by pushing the gripper 13 against the lower reference element 16. Accordingly, the stop position 39, 39' of one of the upper reference elements 17, 17' can be located in correspondence to the analytical compartment 102 so as to release the gripped vessel 2 for using in analyzing samples. Particularly, one of the stop positions 39, 39' of the upper reference elements 17, 17' can be used to release a gripped vessel 2 into a waste compartment. For taking up and releasing a vessel 2, the gripper 13 is moved to a first stop position 38, 39, 39' as defined by one of the reference elements 16, 17, 17' (e.g. the lower reference element 16). The gripper 13 then is opened by translating the gripper 13 and pushing the push element 23 against a first reference element 16, 17, 17'. The gripper 13 then is reclosed by translating the gripper 13 away from the first reference element 16, 17, 17' so as to grip the vessel 2. This is followed by moving the gripper 13 to a second stop position 38, 39, 39' as defined by a second reference element 16, 17, 17' (e.g. one of the upper reference elements 17, 17') and opening the gripper 13 by pushing the push element 23 against the second reference element 16, 17, 17' for releasing the vessel 2. Figure 9 illustrates the gripper 13 in an open condition in which the gripping jaws 15, 15' are distanced with respect to each other. A major advantage is given by the fact, that the gripper 13 (i.e. the gripper base 19) keeps contact with a reference element 16, 17, 17' while opening or closing the gripping jaws 15, 15'. Stated more particularly, in a stop position 38, 39, 39' in which the gripper base 19 is in contact with a reference element 16, 17, 17', the gripper head 18 can be moved relative to the gripper base 19 in order to open or close the gripping jaws 15, 15', while keeping the gripper base 19 in permanent contact with the reference element 16, 17, 17'. Accordingly, the position of the gripper base 19 relative to the longitudinal axis 8 remains unchanged when opening or closing the gripping jaws 15, 15'. As a result, a vessel 2 can reliably be gripped or released. At a same stop position 38, 39, 39', a range of rotational positions of the gripper 13 around the longitudinal axis 8 is accessible for taking up or releasing vessels 2. Specifically, the reference element 16, 17, 17' shaped as a ring segment can be used to keep the gripper 13 in an open position while moving the gripper base 19 along the ring segment. As a result, the gripping jaws 15, 15' can be moved sideways in an open position to a position where a vessel 2 is located, followed by a translation of the gripper head 18 relative to the gripper base 19 so as to close the gripping jaws 15, 15' and grip the vessel 2. By the reverse operation, the vessel 2 can be released. The device 1 of the invention has many advantages over the prior art. A major advantage is given by the fact that the gripping jaws 15, 15' can be operated without a motor and a need to move cables. Instead, the gripping jaws 15, 15' can readily be operated by pushing (e.g. translating) the gripper base 19 against a reference element 16, 17, 17' for opening the gripper 13 and using the resilient force of at least one resilient element 20' for closing the gripper 13 in gripper positions different from the stop positions 38, 39, 39'. Moreover, the device 1 is highly compact in design resulting in a comparably small foot-print, and is simple and robust in construction so as to be suitable for long-term maintenance-free usage. Samples can be processed in a highly cost-efficient manner.

1. A device (1) for gripping vessels (2), comprising: a stationary mount (3), an elongate support (7) having a longitudinal axis (8), coupled to the mount (3) in a manner to be rotatable relative to the mount (3) around the longitudinal axis (8), a rotating mechanism (9), adapted for rotating the support (7), a gripper (13), coupled to the support (7) in a manner to be translatable relative to the support (7) along the longitudinal axis (8), wherein the gripper (13) is provided with gripping jaws (15, 15') for gripping a vessel (2), a translating mechanism (37), adapted for translating the gripper (13), a first actuator (20) for driving the rotating mechanism (9) and a second actuator (20') for driving the translating mechanism (37), at least two reference elements (16, 17', 17'), fixed to the mount (3) in at least two different stop positions (38, 39, 39'), wherein the gripping jaws (15, 15') are passively biasable towards each other for holding a vessel (2) at positions other than the at least two stop positions (38, 39, 39') and wherein the gripping jaws (15, 15') are actively biasable away from each other by pushing the gripper (13) against a reference element (16, 17', 17') in one of the stop positions (38, 39, 39').

2. The device (1) according to claim 1, wherein the gripper (13) comprises: a gripper head (18), coupled to the support (7) in a manner to be translatable with respect to the support (7) along the longitudinal axis (8), a gripper base (19) provided with the gripping jaws (15, 15'), with the gripper head (18) being coupled to the gripper base (18) in a manner to be movable relative to the gripper base (19) against the resilient force of at least one resilient member (20, 20') by pushing the gripper base (19) against a reference element (16, 17', 17') in a stop position (38, 39, 39'), wherein the gripping jaws (15, 15') are coupled to the gripper head (18) in a manner to be moved away from each other by pushing the gripper base (19) against a reference element (16, 17', 17') and to be moved towards each other in positions other than the stop positions (38, 39, 39'). 3. The device (1) according to claim 2, wherein the gripper head (18) is coupled to the gripper base (19) in a manner to be movable relative to the gripper base (19) having a component of movement perpendicular to the longitudinal axis (8) of the support (7). 4. The device (1) according to claim 3, wherein the gripper head (18) is provided with a base guide (26) for guiding the gripper base (19), with the base guide (26) being inclined with respect to the longitudinal axis (8) of the support (7). 5. The device (1) according to any one of the preceding claims 2 to 4, wherein the gripper head (18) is provided with at least one jaw guide (30) coupled to a gripping jaw (15, 15') for guiding the gripping jaw (15, 15'), with the jaw guide (30) being shaped in a manner to move the gripping jaws (15, 15') away from each other by pushing the gripper base (19) against a reference element (16, 17', 17') and to move the gripping jaws (15, 15') towards each other in positions other than the stop positions (38, 39, 39'). 6. The device (1) according any one of the preceding claims 1 to 5, wherein the support (7) is provided with a gripper guide (14) extending along the longitudinal axis (8) for guiding the gripper (13). 7. The device (1) according to any one of the preceding claims 1 to 6, wherein at least one reference element (16, 17', 17') is shaped as a ring segment. 8. The device (1) to any one of the preceding claims 1 to 7, wherein at least one reference element (16, 17', 17') comprises a guiding face (40) for guiding the gripper (13) along the guiding face (40) by rotating the gripper (13) around the longitudinal axis (8) of the support (7). 9. The device (1) according to claim 8, wherein the gripper (13) comprises at least one contact wheel (42) for rolling on the guiding face (40) of a reference element (16, 17', 17') by rotating the gripper (13) around the longitudinal axis (8) of the support (7). 10. The device (1) according to any one of the preceding claims 1 to 9, wherein the translating mechanism (37) and/or the rotating mechanism (9) is configured as a belt drive. 11. The device (1) according to any one of the preceding claims 1 to 10, wherein at least one gripping jaw (15') comprises at least one engagement element (35, 36) for engagement with a corresponding engagement element of a vessel (2). 12. A system (100) for analyzing samples, comprising: a separator (101) for separating vessels (2) supplied in bulk form and providing separated vessels (2) to a picking position (103);: at least one analytical compartment (102)for analyzing samples with the vessels (2);: a device (1) for gripping vessels (2) according to any one of the preceding claims 1 to 11 for transferring vessels (2) from the picking position (103) located in correspondence to a first stop position (38) to the at least one analytical compartment (102) located in correspondence to at least one second stop position (39). 13. The system (100) according to claim 12, wherein the device (1) for gripping vessels (2) comprises a third stop position (39') for releasing vessels into a waste compartment or a second analytical compartment.

2883667

Device for gripping vessels

Based on the following detailed description of an invention, generate the patent claims. There should be 2 claims in total. The first, independent claim is given and the remaining 1 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In the following, an exemplary device 1 for gripping vessels 2 according to the invention is explained. As schematically illustrated in Figure 1, the device 1 can, e.g., be part of a system (instrument) for processing samples (not further detailed), generally referred to at reference numeral 100, such as an analytical system (instrument) for processing samples by one or more analytical methods such as, but not limited to, photometric methods, involving the use of vessels, such as, but not limited to cuvettes. The device 1 for gripping vessels 2 comprises a stationary mount 3 having a bottom plate 4, a top plate 5 and a vertical beam 6, with the beam 6 being fixed to the bottom plate 4 and the top plate 5 being fixed to the beam 6. The device 1 further comprises an elongate vertical support 7 having a longitudinal axis 8 which is rotatably fixed to the mount 3. Stated more particularly, the vertical support 7 is rotatably fixed to both the bottom plate 4 and the top plate 5 by means of rotational bearings (not further detailed) so as to be rotatable around the longitudinal axis 8. A rotating mechanism 9 is coupled to the support 7 for rotating the support 7 around the longitudinal axis 8. Specifically, the rotating mechanism 9 is configured as a belt drive comprising an electric motor 10 for driving a belt 11. As illustrated, in one embodiment, the belt 11 is wound around a driving wheel 12 fixed in rotation to the support 7 so that the support 7 can be rotated together with the wheel 12 which is rotated by the motor-driven belt 11. The device 1 comprises a gripper 13 provided with two gripping jaws 15, 15' for gripping a vessel 2. As can best be seen in Figure 3, each vessel 2 comprises a bottom-closed body 32 open on the top for receiving liquid. The body 32 comprises side walls 33 provided with a flange 34 projecting perpendicularly from the side walls 33 and being integrally formed therewith. As illustrated, the upper gripping jaw 15' and the flange 34 are provided with two pairs of engagement elements, each of which consisting of a projection 35 and a depression 36. Specifically, in one embodiment, as illustrated, the flange 34 has two depressions 36 and the upper gripping jaw 15' has two projections 35 for engagement with the depressions 36. Accordingly, the reliability of gripping and holding a vessel 2 can be improved so as to reduce the risk of a failure. The gripper 13 is fixed to the support 7 in a manner to be translatable along the longitudinal axis 8. Specifically, in one embodiment, the support 7 is provided with a gripper guide 14 extending along the longitudinal axis 8 of the support 7 in vertical direction for guiding the gripper 13. Accordingly, the gripper 13 can be translated along the gripper guide 14. A translating mechanism 37 is coupled to the gripper 13 for translating the gripper 13 along the gripper guide 14. Specifically, the translating mechanism 37 is configured as belt drive comprising an electric motor 10' for driving a belt 11'. The belt 11' is wound around a driving wheel 12' that is coupled to another belt 11'' fixed in translation to the gripper 13. Accordingly, the gripper 13 can be translated along the gripper guide 14 by driving the belt 11" by rotating the wheel 12', with the latter one being rotated by the motor-driven belt 11'. Accordingly, the gripper 13 can be rotated by driving the wheel 12 and can be translated by driving the wheel 12'. Since the electric motors 10, 10' can be independently controlled with respect to each other, the gripper 13 can be rotated or translated or can have a combined translational/rotational movement. As can, e.g., be seen in Figure 1, the device 1 further comprises a lower reference element 16 and two upper reference elements 17, 17', each of which being shaped as a ring segment covering a range of segment angles, e.g. between 45° and 180°. It, however, is to be understood that any other range of segment angles can be envisaged according to the specific demands of the user. Specifically, the reference elements 16, 17, 17' are fixed to the mount 3 so as to be stationary with respect to the support 7 and gripper 13, respectively. Each reference element 16, 17, 17' defines a stop position 38, 39, 39' for a vertical movement (translation) of the gripper 13, with the lower reference element 16 defining a lower stop position 38 and the two upper reference elements 17, 17' defining two upper stop positions 39, 39' so that the device 1 has stop positions in two different heights (positions of the longitudinal axis 8). The gripping jaws 15, 15' are passively biasable towards each other to close the gripper 13 for holding a vessel 2 between the stop positions as defined by the reference elements 16, 17, 17' and are actively biasable away from each other to open the gripper 13 by pushing the gripper 13 against a reference element 16, 17, 17' in a stop position 38, 39, 39'. The gripper 13 can be pushed against one reference element 16, 17, 17' by translating and/or rotating the gripper 13. Due to the vertical orientation of the support 7, the upper reference elements 17, 17' are in a higher position than the lower reference element 16, with the upper reference elements 17, 17' being on opposite sides of the support 7. Specifically, the stop position 38 of the lower reference element 16 can, e.g., be located in correspondence to a picking position 103 of the system 100 for picking-up separated vessels 2 provided by an automated separator 101 for separating vessels 2 supplied in bulk form and providing separated vessels 2 at the picking position 103. Thus, the stop positions 39, 39' of the upper reference elements 17, 17' can be located in correspondence to an analytical compartment 102 of the system 100 for releasing or gripping vessels 2, e.g., for analyzing samples. Due to the arrangement of the upper reference elements 17, 17', vessels 2 can also be released on opposite sides of the support 7. One stop position of the upper reference elements 17, 17' can, e.g., be used for releasing vessels 2 into a waste compartment (not illustrated) of the system 100 or into a second analytical compartment. Each of the reference elements 16, 17, 17' has an upper guiding face 40 for guiding the gripper 13. In one embodiment, the guiding face 40 is configured as sliding face for sliding engagement with the gripper 13. Accordingly, the gripper 13 can be kept open in case of rotating the gripper 13 around the rotational axis 8. As a result, vessels 2 can be taken up or released in a broad range of angles of a stop position 38, 39, 39'. Specifically, as can be seen in Figure 2, the gripper base 19 is provided with a contact wheel 42 for rolling on the guiding face 40 by rotating the gripper 13 around the mount 3. Accordingly, a friction between the gripper 13 and a reference element 16, 17, 17' can advantageously be reduced. With particular reference to Figures 3 and 5 to 8, the gripper 13 comprises a gripper head 18 and a gripper base 19. Specifically, the gripper head 18 is translatably fixed to the support 7 guidable (guided) by the gripper guide 14. Accordingly, the gripper head 18 can be translated along the gripper guide 14 by driving the translating mechanism 37 as above-described. The gripper head 19 is movably fixed to the gripper base 18 in a manner to be movable relative to the gripper base 18 against the resilient force of resilient members 20, 20' by pushing the gripper base 19 against a reference element 16, 17, 17'. Specifically, the gripper base 19 comprises two gripper legs 21, 21', each of which being provided with one gripping jaw 15, 15' at an end portion thereof. As illustrated, in one embodiment, the gripper legs 21, 21', e.g., are configured as a lower gripper leg 21 provided with the lower gripping jaw 15 and an upper gripper leg 21' provided with the upper gripping jaw 15' so that the flange 34 of a vessel 2 in an up-right position can readily be gripped. As can best be seen in Figures 7 and 8, the gripper base 19 further comprises a leg support 22, e.g. configured as a (e.g. vertical) plate-like member for fixing of the gripper legs 21, 21' in a manner that the gripper legs 21, 21' are movable (moved) together with the leg support 22, with the gripping jaws 15, 15' being movable towards and away from each other. A first resilient element 20, such as but not limited to a compression spring, is arranged between the leg support 22 and a push element 23 which is also a component of the gripper base 19. The push element 23 can be used to push the gripper base 19 against a reference element 16, 17, 17' in a stop position 38, 39, 39'. At the distant end of the leg support 22 relative to the gripping jaws 15, 15', the leg support 22 is connected to an elongate guiding link 24, such as but not limited to a connecting rod, which on one side is fixed to the push element 23 and on the other side is provided with a base guiding element 25, such as but not limited to a guiding roller, guidable (guided) by a base guide 26 provided by the gripper head 18. Specifically, as illustrated, the base guide 26 can, e.g., be configured as a linear recess extending inclined with respect to the longitudinal axis 8. Accordingly, in case the push element 23 is pushed against a reference element 16, 17, 17' by translating the gripper 13 (i.e. gripper head 18), the gripper head 18 can be moved relative to the gripper base 19, with the gripping jaws 15, 15' being drawn away guided by the base guide 26 so as to have a component of movement perpendicular to the longitudinal axis 8. Since the gripper legs 21, 21' are fixed to the leg support 22, the gripper legs 21, 21' can be moved together with the leg support 22. A second resilient element 20', such as but not limited to a compression spring, is arranged between the gripper head 18 and the gripper base 19 so as to increase the resilient force when pushing the push element 23 against a reference element 16, 17, 17'. Accordingly, the gripper base 19 (and the gripper legs 21, 21') can be pushed back (reverse movement) by the resilient force of the second resilient force 20' in a position of the gripping jaws 15, 15' other than a stop position 38, 39, 39'. As illustrated, the gripper head 18 further comprises two jaw guiding elements 29 arranged on both sides of the gripping legs 21, 21'. The jaw guiding elements 29 can, e.g., be configured as plates which, e.g., are vertically arranged in parallel arrangement with the leg support 22. Each of the jaw guiding elements 29 is provided with two jaw guides 30, 30' arranged above/below of each other in correspondence to the gripper legs 21, 21' for guiding of the gripper legs 21, 21' and gripping jaws 15, 15', respectively. As illustrated, in one embodiment, each jaw guide 30, 30' is configured as a recess or through-hole formed by the jaw guiding element 29, with a leg nose 31 (see Figure 2 ) projecting from each of the gripper legs 21, 21' being inserted in the jaw guide 30, 30' for guiding of the gripper leg 21, 21'. Accordingly, the gripper legs 21, 21' can be moved relative to the jaw guiding elements 29 when moving the gripper head 18 relative to the gripper base 19, e.g., by pushing the gripper base 19 against a reference element 16, 17, 17' in a stop position 38, 39, 39'. As illustrated, the jaw guides 30, 30' of each of the jaw guiding elements 29 are shaped in a manner to move the gripping jaws 15, 15' away from each other by pushing the gripper base 19 against a reference element 16, 17, 17' or to move the gripping jaws 15, 15' towards each other in gripper positions other than the stop positions 38, 39, 39'. Accordingly, by pushing the gripper base 19 and push element 23, respectively, against a reference element 16, 17, 17', the gripper legs 21, 21' can be moved backwards to have a component of movement perpendicular to the longitudinal axis 8 so as to move the gripping jaws 15, 15' away from each other. Furthermore, the gripper legs 21, 21' can be moved forwards (in the reverse direction) by the resilient force of the resilient element 21' so as to move the gripping jaws 15, 15' towards each other. The forward and backward movement of the gripping jaws 15, 15' can advantageously be used for gripping or releasing a vessel 2. As illustrated in Figure 1, the device 1 for gripping vessels 2 can be part of a system 100 for analyzing samples, comprising a separator 101 for separating vessels 2 supplied in bulk form and providing single vessels 2 to a picking position 103 and at least one analytical compartment 102 for analyzing samples with the vessels 2. Specifically, the picking position 103 can be located in correspondence to the stop position 38 of, e.g., the lower reference element 16 so as to pick up separated vessels 2 by the gripper 13 by pushing the gripper 13 against the lower reference element 16. Accordingly, the stop position 39, 39' of one of the upper reference elements 17, 17' can be located in correspondence to the analytical compartment 102 so as to release the gripped vessel 2 for using in analyzing samples. Particularly, one of the stop positions 39, 39' of the upper reference elements 17, 17' can be used to release a gripped vessel 2 into a waste compartment. For taking up and releasing a vessel 2, the gripper 13 is moved to a first stop position 38, 39, 39' as defined by one of the reference elements 16, 17, 17' (e.g. the lower reference element 16). The gripper 13 then is opened by translating the gripper 13 and pushing the push element 23 against a first reference element 16, 17, 17'. The gripper 13 then is reclosed by translating the gripper 13 away from the first reference element 16, 17, 17' so as to grip the vessel 2. This is followed by moving the gripper 13 to a second stop position 38, 39, 39' as defined by a second reference element 16, 17, 17' (e.g. one of the upper reference elements 17, 17') and opening the gripper 13 by pushing the push element 23 against the second reference element 16, 17, 17' for releasing the vessel 2. Figure 9 illustrates the gripper 13 in an open condition in which the gripping jaws 15, 15' are distanced with respect to each other. A major advantage is given by the fact, that the gripper 13 (i.e. the gripper base 19) keeps contact with a reference element 16, 17, 17' while opening or closing the gripping jaws 15, 15'. Stated more particularly, in a stop position 38, 39, 39' in which the gripper base 19 is in contact with a reference element 16, 17, 17', the gripper head 18 can be moved relative to the gripper base 19 in order to open or close the gripping jaws 15, 15', while keeping the gripper base 19 in permanent contact with the reference element 16, 17, 17'. Accordingly, the position of the gripper base 19 relative to the longitudinal axis 8 remains unchanged when opening or closing the gripping jaws 15, 15'. As a result, a vessel 2 can reliably be gripped or released. At a same stop position 38, 39, 39', a range of rotational positions of the gripper 13 around the longitudinal axis 8 is accessible for taking up or releasing vessels 2. Specifically, the reference element 16, 17, 17' shaped as a ring segment can be used to keep the gripper 13 in an open position while moving the gripper base 19 along the ring segment. As a result, the gripping jaws 15, 15' can be moved sideways in an open position to a position where a vessel 2 is located, followed by a translation of the gripper head 18 relative to the gripper base 19 so as to close the gripping jaws 15, 15' and grip the vessel 2. By the reverse operation, the vessel 2 can be released. The device 1 of the invention has many advantages over the prior art. A major advantage is given by the fact that the gripping jaws 15, 15' can be operated without a motor and a need to move cables. Instead, the gripping jaws 15, 15' can readily be operated by pushing (e.g. translating) the gripper base 19 against a reference element 16, 17, 17' for opening the gripper 13 and using the resilient force of at least one resilient element 20' for closing the gripper 13 in gripper positions different from the stop positions 38, 39, 39'. Moreover, the device 1 is highly compact in design resulting in a comparably small foot-print, and is simple and robust in construction so as to be suitable for long-term maintenance-free usage. Samples can be processed in a highly cost-efficient manner.

14. A process for gripping vessels (2), comprising the following steps of: moving a gripper (13) provided with gripping jaws (15, 15') passively biased towards each other to a first stop position (38) ; opening the gripper (13) by pushing the gripper (13) against a first reference element (16) for up-taking a vessel (2), reclosing the gripper (13) by moving the gripper (13) away from the first reference element (16) so as to grip a vessel (2), moving the gripper (13) to a second stop position (39) opening the gripper (13) by pushing the gripper (13) against a second reference element (17) for releasing the vessel (2).

15. The process according to claim 14, wherein moving of the gripper (13) comprises translating and/or rotating the gripper (13).

2883819

A mobile stockpiling conveyor

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to the drawings, there is shown a mobile stockpiling conveyor according to the invention indicated generally by the reference numeral 1. The mobile stockpiling conveyor 1 has a mobile chassis 2 mounted in this case on tracks 3 forming primary mobile support elements. A conveyor 4 is mounted on the chassis 2 by a telescopic support strut 5 and an associated link arm 6. A pivot mount 7 pivotally supports an infeed end of the conveyor 4 when in use. In accordance with the invention, secondary mobile support elements, in this case auxiliary wheels 8 are mounted on the chassis 2. During normal manoeuvring of the chassis 2 these auxiliary wheels 8 are supported in a raised inoperative stored position on the chassis 2 and the chassis 2 is driven about on the tracks 3 in the usual way. However, for stockpiling the auxiliary wheels 8 can be lowered into an operative ground-engaging position as shown in the drawings, raising the tracks 3 clear of the ground. Thus, by driving the auxiliary wheels 8 when they are in the lowered position, the chassis 2 can be moved laterally to swing the conveyor 4 laterally through an arc about the pivot mount 7 to build up a series of stockpiles of material. In more detail, the secondary mobile support elements comprise a pair of wheel sets 10, 11, each of which is mounted on an associated pivot arm 12, 13 and each having a pair of the wheels 8. Each pivot arm 12, 13 is pivotally mounted by a pivot pin 14 at its inner end to a mounting bracket 15 on the chassis 2. A ram 16, 17 extends between the mounting bracket 15 and each arm 12, 13 and is operable to raise and lower the arm 12, 13 on the chassis 2. Pivot pins 18 connect each end of each ram 16, 17 to the mounting bracket 15 and the associated arms 12, 13. An hydraulic motor 19 mounted on one of the wheel sets 10, 11 is operable to drive the associated wheels 8 on the arm 12, 13. The rotational axis of each set 10,11 of wheels 8 is substantially parallel to a longitudinal axis of the conveyor 4 for lateral movement of the conveyor.4. The conveyor 4 comprises a number of folding sections. The conveyor 4 is supported on the chassis 2 by the telescopic support strut 5 and the associated fixed length link arm 6 which are adjustable to allow correct positioning of the conveyor 4. The support strut 5 is telescopically adjustable, having lower elements 20, 21 which are slidably received within complementary upper elements 23, 24. Rams 25, 26 are operable to extend and retract the support strut 5. A lower end of the support strut 5 is mounted by pivot pins 27, 28 on the chassis 2 and an upper end of the support strut 5 is mounted by pivot pins 29 to associated mounting brackets 30 on an underside of the conveyor 4. The link arm 6 is pivotally mounted by pivot pins 32 at an inner end on the chassis 2 and pivotally mounted at an outer end by pivot pins 34 to associated mounting brackets 35 on an underside of the conveyor 4. A telescopic pivot adjusting link 36 is mounted below the link arm 6 and has an inner end pivotally mounted on the chassis 2 by pivot pins 37 and an outer end mounted by pivot pins 38 to mounting brackets 39 on an underside of the link arm 6. Rams 40 are operable to extend and retract telescopic inner 41 and outer 42 portions of the link 36. The pivot mount 7 has a ground engaging base 50 carrying a swivel joint 51. The swivel joint 51 is connected by fixed length rods 52 to an outer end of the link arm 6, said rods 52 being pivotally connected to the link arm 6 and to the swivel joint 51. Also, a telescopic arm 54 extends between the swivel joint 51 and an outer end of the pivot adjusting link 36 and is pivotally connected to both the swivel joint 51 and the pivot adjusting link 36. A ram 56 is operable to telescopically adjust inner 57 and outer 58 portions of the pivot adjusting link 54. The conveyor 4 comprises an infeed section 60, an intermediate section 61 and a discharge section 62. Each of the infeed section 60 and the discharge section 62 are foldable inwardly over the intermediate section 61 by means of rams 63, 64 at hinge joints 65, 66 between the conveyor sections 60, 61, 62. The intermediate conveyor section 61 is movable on the chassis 2 by means of the telescopic support strut 5 and the associated link arm 6 between a lowered stored position seated on a rest 68 on the chassis 2 and a raised operative position above the chassis 2 as shown in the drawings. A loading infeed hopper 69 is provided at the infeed section 60 of the conveyor 4. In use, the mobile stockpiling conveyor 1 when in the fully folded position is readily easily manoeuvred on the tracks 3 into a desired stockpiling position. The auxiliary wheels 8 can then be lowered to provide improved stability as they extend outwardly of the tracks 3. By extending the telescopic strut 5 and the associated link arm 6 the conveyor 4 is raised into the desired operative position. With the conveyor sections 60.61,62 unfolded into the operative position shown in the drawings, the telescopic strut 5 and the associated link arm 6 can be adjusted to position the infeed section 60 and discharge section 62 of the conveyor 4 as required. The pivot mount 7 is lowered to engage the ground to provide stability at the infeed end of the conveyor 4 and to allow subsequent pivoting by means of the swivel joint 51 and operation of the auxiliary wheels 8 to swing the conveyor 4 between different stockpiling position as required.

1. A mobile stockpiling conveyor (1), including: a chassis (2) mounted on primary mobile support elements (3), a conveyor (4) mounted on the chassis (2), a pivot mount (7) for pivotally supporting an infeed end of the conveyor (4), characterised in that there is provided secondary mobile support elements (8) which are movable between a raised disengaged position on the chassis (2) and a lowered ground-engaging operating position in which the primary mobile support elements (3) are lifted clear of the ground.

2. The mobile stockpiling conveyor (1) as claimed in claim 1 wherein each secondary mobile support element (8) is rotatable about an axis of rotation which is substantially parallel to a longitudinal axis of the conveyor (4) when in the operating position for lateral movement of the conveyor (4). 3. The mobile stockpiling conveyor (1) as claimed in claim 1, wherein each secondary mobile support element (8) is rotatable about an axis of rotation which passes through a pivot axis of the pivot mount (7) when in the operating position. 4. The mobile stockpiling conveyor (1) as claimed in any one of the preceding claims, wherein the secondary mobile support elements (8) are mounted on a pivot arm (12, 13) on the chassis (2) for pivoting between a raised disengaged position and a lowered operating position, with actuating means (16, 17) which is operable to raise and lower the pivot arm (12, 13). 5. The mobile stockpiling conveyor (1) as claimed in claim 4 wherein each pivot arm (12, 13) has an inner end and an outer end, said inner end being pivotally mounted on the chassis (2) and at least one wheel (8) being mounted at the outer end of the arm (12, 13), an actuating ram (16, 17) being mounted between the arm (12, 13) and chassis (2) which is operable to raise and lower the pivot arm (12, 13). 6. The mobile stockpiling conveyor (1) as claimed in claim 4 or claim 5 wherein each pivot arm (12, 13) is mounted on an upstanding mounting bracket (15) on the chassis (2), the inner end of the pivot arm being pivotally mounted (14) at a lower end of the mounting bracket (15) and the ram (16, 17) extending between upper end of the mounting bracket (15) and a pivot mount (18) intermediate the inner end and an outer end of the pivot arm (12, 13). 7. The mobile stockpiling conveyor (1) as claimed in claim 5 or claim 6 wherein at least one of said wheels (8) is driven by an hydraulic motor (19). 8. The mobile stockpiling conveyor (1) as claimed in any preceding claim wherein the conveyor (4) is mounted on the chassis (2) by a telescopic support strut (5) and an associated fixed length link arm (6) which extend outwardly at opposite sides of the chassis (2), both (5, 6) extending between the chassis (2) and the conveyor (4) and being pivotally connected to both the chassis (2) and the conveyor (4). 9. The mobile stockpiling conveyor (1) as claimed in claim 8 wherein a telescopic pivot adjusting link (36) extends between the chassis (2) and the link arm (6), being telescopically adjustable to pivot the link arm (6) on the chassis (2). 10. The mobile stockpiling conveyor (1) as claimed in any preceding claim wherein the pivot mount (7) has a ground-engaging base (50) with a swivel joint (51) mounted thereon, said swivel joint (51) connected by fixed length rods (52) to an outer end of the link arm (6) and being pivotally connected to the link arm (6) and the swivel joint (51), and a telescopic arm (54) extending between the swivel joint (51) and an outer end of the pivot adjusting link (36) and being pivotally connected to the swivel joint (51) and the pivot adjusting link (36). 11. The mobile stockpiling conveyor (1) as claimed in any preceding claim wherein the conveyor (4) comprises a plurality of folding sections (60, 61, 62). 12. The mobile stockpiling conveyor (1) as claimed in claim 11 wherein the conveyor (4) comprises an infeed section (60), an intermediate section (61) and a discharge section (62), each of the infeed section (60) and the discharge section (62) being hingedly connected to the intermediate section (61) and foldable inwardly over the intermediate section (61). 13. The mobile stockpiling conveyor (1) as claimed in claim 12 wherein the intermediate conveyor section (61) is movable on the chassis (2) by means of the telescopic support strut (5) and the associated link arm (6) between a lowered stored position seated on a rest (68) on the chassis (2) and a raised operative position above the chassis (2). 14. The mobile stockpiling conveyor (1) as claimed in any one of claims 8 to 13 wherein an outer end of the telescopic support strut (5) is pivotally connected adjacent a discharge end of the intermediate section (61) of the conveyor (4) and an outer end of the link arm (6) is pivotally connected adjacent an infeed end of the intermediate section (61) of the conveyor (4). 15. The mobile stockpiling conveyor (1) as claimed in any one of claims 12 to 14, wherein conveyor folding rams (63, 64) extend between the intermediate section (61) and each of the infeed section (60) and the discharge section (62) of the conveyor (4) for folding the infeed section (60) and the discharge section (62) on the intermediate section (61).

2883640

Cutting tool with replaceable abutment members and toolholder and cutting insert therefor

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figures 1 -3 show a cutting tool 21 according to an aspect of the present invention. The cutting tool 21 comprises a cutting insert 23 mounted to a toolholder 25. As seen, for example, in Figures 1 and 3, the toolholder 25 comprises a bottom abutment surface 27 and a projection 29 extending upwardly from the bottom abutment surface. The projection 29 includes an internally threaded opening 31 (e.g., Figures 1 and 4 ). The internally threaded opening 31 has a central axis C1 that is offset from a central axis C3 of the projection 29 in a first direction D1 (from C3 to C1) as seen in Figures 6 and 7. The toolholder 25 further comprises a clamping screw 33 having external threads 35 for mating with internal threads of the internally threaded opening 31 and a head 37 having a bottom clamping surface 39 shaped as a truncated cone ( Figures 1 and 3 ). As seen, for example, with reference to Figures 6 and 7, when the bottom clamping surface 39 of the head 37 contacts a correspondingly shaped insert clamping surface 41 on the cutting insert 23, the insert is urged in (or substantially in) the first direction D1 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert 23. While the insert 23 will ordinarily be moved in the first direction D1 when the clamping screw is tightened, the insert may not necessarily be moved in exactly the same direction as the first direction, such as if the insert contacts an abutment surface as in the embodiment shown in Figures 8 and 9 and moves at an angle to the first direction over at least some portion of its movement. The central axis C1 of the internally threaded opening 31 is the same as the central axis of the screw 33 when the screw is screwed into the internally threaded opening. The toolholder 25 further comprises at least two abutment members 43 extending from a side wall 45 of the projection 29 in radial directions. At least abutment points on the abutment members 43 are closer to the central axis C3 of the projection 29 than to the central axis C1 of the internally threaded opening 31 when measured in a plane perpendicular to the axes C1 and C3. Typically, the entire abutment member 43 is closer to the central axis C3 of the projection 29 than to the central axis C1 of the internally threaded opening. This is, for example, typically the case when the abutment members are in the form of circularly cylindrical pins as shown in, for example, Figures 1, 6, and 7. Abutment points on the abutment members 43 are defined as the forwardmost points on the abutment members facing the first direction D1. The abutment points on the abutment members contact corresponding supporting points of recess supporting surfaces 61 ( Figures 5-7 ). The projection 29 is typically but not necessarily generally circularly cylindrical, and an internal cylindrical wall 47 of the insert 23 is also typically but not necessarily generally circularly cylindrical. The internal cylindrical wall 47 of the insert 23 includes recesses 49 for receiving the abutment members 43. Providing generally circularly cylindrical shapes to the projection 29 and the internal cylindrical wall 47 of the insert 23 can facilitate indexing of the insert relative to the toolholder 25, although the insert may be indexed even if the shapes of the projection and internal cylindrical wall are not circular. The shapes may be "generally" circularly cylindrical in the sense that the abutment members 43 or the recesses 49 are spaced around the surfaces and prevent them from being perfectly circularly cylindrical. As seen in Figures 1 and 3-7, the abutment members 43 can comprise circularly cylindrical pins, although the abutment members may be provided in a variety of suitable forms, such as by being machined together with the projection 29 or secured to the projection by means such as brazing. Providing the abutment members 43 as circularly cylindrical pins permits the abutment members to be easily mounted in holes 51 ( Figures 1, 3, and 4 ) formed in the bottom abutment surface 27 and recesses 53 formed in the projection and, in the event of damage to the abutment members, removed from the holes and recesses. The circularly cylindrical shape of the abutment members 43 is also ordinarily relatively simple to manufacture. Use of easily removable abutment members 43 facilitates replacement of the abutment members in the event of damage which is not possible with conventional abutment surfaces that form surfaces of walls of pockets machined into blocks of material that form the toolholder. Recesses 53 in the projection 29 for the abutment members 43 in the form of replaceable pins will typically, but do not necessarily, extend parallel to the central axis C3 of the projection and perpendicular to the bottom abutment surface 27. The cutting insert 23 comprises a bottom supporting surface 55 for supporting the insert against the bottom abutment surface 27, a top surface 57, and a through hole 59 for receiving the projection 29. The through hole 59 extends from the bottom supporting surface 55 to the top surface 57. The through hole 59 comprises the internal, cylindrical wall portion 47 and an inverted truncated conical insert clamping surface 41 between the cylindrical wall and the top surface 57. As seen, for example, in Figures 1, 3, and 5-7, the through hole 59 comprises a plurality of recesses 49 having recess supporting surfaces 61 ( Figures 5-7 ) in the cylindrical wall 47 arranged to receive the abutment members 29 so that the abutment members abut against the recess supporting surfaces 61 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert 23 and moves the insert in the first direction D1 through the distance moved illustrated in Figure 7. The recesses 49 can extend to the insert clamping surface 41 and the bottom clamping surface 39 of the head 37 of the clamping screw 33 is preferably of sufficient size to cover all of the recesses to minimize the possibility of any chips from a workpiece falling into the recesses. A corner 63 is formed at an intersection of the top surface 57 and a side wall 65 of the insert 23. All or part of the corner 63 forms a plurality of different cutting edges when the insert 23 is indexed relative to the toolholder 25. The insert 23 can have a plurality of cutting edges as seen in Figure 1 (showing nine discrete straight-edge corner portions that can form parts of up to nine separate cutting edges) or the cutting edges may be formed as portions of, for example, an insert having a circular shape when viewed along a central axis C2 of the through hole 59 of the insert. The insert 23 comprises at least two recesses 49 for receiving the abutment members 43 and, more typically, at least three recesses 49 spaced such that the insert can be indexed relative to the at least two abutment members 43 on the toolholder 25 to at least two different positions to expose two or more different portions of the cutting edge. Each cutting edge corresponds to a respective pair of recesses 49 in which the abutment members 43 are received when the particular cutting edge is in a working position relative to the toolholder 25. In the embodiment shown in FIG 5, for example, there are nine elongated (and straight) portions of the corner 63 and nine transition portions disposed between respective pairs of the elongated portions. The elongated portions each have a corresponding recess 49 directed toward the elongated portion of the corner, typically centered along a line extending from the central axis C2 of the through hole 59 and bisecting the elongated portion of the corner. As seen in the illustrative insert 23 shown in, e.g., Figures 1 and 5, an insert may have nine recesses 49 spaced at angles AR of 40 degrees around the central axis C2 of the through hole 59 and can be indexed to up to nine different positions relative to the two abutment members 43 on the projection 29. At least when the abutment members 43 have radiused external surfaces, as when they are formed from circular pins, the recesses 49 are typically formed as radiused surfaces and, even if the entire recess 49 is not formed as a radiused surface, at least the recess supporting surfaces 61 are typically formed as radiused surfaces. The radii of the recesses 49 and/or the recess supporting surfaces 61 is at least as large as and, typically, slightly larger than the radii of the abutment members 43 to permit the abutment members to be received in the recesses. The recesses 49 seen in the embodiment shown in Figure 5 are in the form of generally circular arcs of about 180 degrees. The arcs may be smaller than 180 degrees, however, typically not less than about 90 degrees. The recesses 49 and the non-recessed portion of the internal cylindrical wall 47 together preferably define a cylinder. Longitudinal axes of the recesses 49 and the longitudinal axis of the internal cylindrical wall 47, i.e., the axis C2 of the insert through hole 59 are preferably perpendicular to a plane of the bottom surface 57 and, typically, to a plane of the top surface 55 of the insert 23. When the internal cylindrical wall 47 is generally circularly cylindrical, the radius of the internal cylindrical wall is typically between about 3-10 times as large as the radii of the recesses 49 and/or the recess supporting surfaces 61 and, more preferably, between 5-7 times as large. When the internal cylindrical wall 47 is generally circularly cylindrical, the material of the internal cylindrical wall defining spaces between the recesses 49 typically defines an arc of a circle. The size of the arc of the circle depends upon the size and number of the recesses 49 relative to the size of the internal cylindrical wall 47. In an insert 23 as shown in Figure 5 that has nine recesses 49 that are approximately 1/6 the size of the diameter of the generally circularly cylindrical internal cylindrical wall 47, the material of the internal cylindrical wall between the recesses defines an arc of a circle that is about 20 degrees. The nine recesses 49, likewise, extend over arcs of the circle of the generally circularly cylindrical internal cylindrical wall 47 that are about 20 degrees. Thus, while not necessarily true of all embodiments of the insert 23, the arc of the circle between each recess is roughly equal to or greater than the arc of the circle across each of the recesses 49. As seen in the illustrative toolholder 25 shown in, e.g., Figures 1 and 4, the abutment members 43 are typically spaced at an angle AA around the central axis C3 of the projection 29 that is slightly less than an angle between the two recesses 49 of the insert 23 in which the abutment members 43 are to be received. For example, in the case of the abutment members 43 shown in the cutting tool 21 of Figure 1 for use with the insert 23 having nine recesses 49 spaced at 40 degrees around the insert opening axis C2, the abutment members might be at an angle of 79 degrees around the central axis C3 of the projection 29 as they are intended to be received in recesses 49 in the insert that are spaced at 80 degrees around the insert opening axis. By arranging the abutment members 43 so that they define a slightly smaller angle about the central axis C3 of the projection than the angle that the recesses 49 in which they are to be received define about the insert opening axis C2, when the insert 23 is moved in the first direction D1 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert, i.e., moved from the position shown in Figure 6 to the position shown in Figure 7, the radiused surfaces of the abutment members 43 will tend to contact the recesses 49 on parts of the recesses that are closest to each other as seen in Figure 7. This will tend to minimize any tendency of the insert to move relative to toolholder during a cutting operation. The abutment members 43 may be but need not be received in consecutive ones of the recesses 49. Arranging the abutment members 43 so that they are received in non-consecutive ones of the recesses 49 can help to provide good, evenly spaced support for the insert 23 on the toolholder 25. Where the toolholder 25 has two abutment members 43, it may, but need not, further comprise one or more additional side surfaces 67 and 69, that define non-zero angles with respect to the bottom abutment surface 27 and with respect to each other. Because the side surfaces 67 and/or 69 can ordinarily be entirely omitted, this provides substantially greater design flexibility for the toolholder 25. If side surfaces 67 and/or 69 are provided, part or all of the side wall 65 of the insert 23 may comprise one (particularly in the case of a circular insert) or a plurality of side insert surfaces which are moved toward but do not contact the side surfaces 67 and 69 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert 23 and moves the insert in the first direction D1. To avoid overdetermination, the side insert surfaces will ordinarily not contact the side surfaces 67 and 69 at all, however, there may be some contact in some designs when cutting forces urge the insert 23 in the first direction D1. The abutment members 43 will contact the recess supporting surfaces 61 in the recesses 49 before the side surfaces 67 and 69 and the side insert surfaces come into contact. In this way, the brunt of the forces on the insert 23 during a cutting operation will be borne by the abutment members 43 rather than the side surfaces 67 and 69, which can be useful if the abutment members 43 are in a form such that they can be easily replaced. As is seen in Figures 6 and 7, in the cutting tool 21, no part of the insert 23 contacts side insert abutment surfaces 67 and 69 in the pocket. Moreover, because the abutment members 43 function as replacements for traditional side abutment surfaces and can be located relatively close to the working cutting edges as compared to side abutment surfaces, this can reduce the effect of size variations in the insert. For example, in a conventional insert, the position of the cutting edge relative to the toolholder is dependent upon the distances from the points at which the side insert supporting surfaces contact the side abutment surfaces to the cutting edge whereas, in an insert as described herein, the position of the cutting edge relative to the toolholder is dependent upon the much shorter distances from the points at which the abutment members 43 contact the recess supporting surfaces 61 to the cutting edge. A variation in insert size will have less impact on the location of the cutting edge in a cutting tool according to aspects of the present invention than in a conventional cutting tool. As can be appreciated from, for example, in Figure 3, the abutment members 43 can contact the recess supporting surfaces 61 close to the top surface 57 of the insert, near the point of contact between the clamping surfaces 39 and 41 of the clamping screw 33 and the insert 23. This feature can facilitate support of the insert 23 relative to the toolholder 25 and the projection 29, particularly as compared to other "bottom support" style inserts that involve projections that only extend a minimal distance above a bottom abutment surface of the toolholder. Moreover, this feature can facilitate avoidance of any tendency of an insert to climb up a bottom support-style projection that might occur as the result of cutting forces on the insert when side surfaces of the projection are sloped or of minimal height. The top and bottom surfaces 57 and 55 of the insert 23 may be identical, and the through hole 59 may comprise a second inverted truncated conical insert clamping surface 73 ( Figure 3 ) between the cylindrical wall 47 and the bottom surface 55. By such a structure, an insert 23 that is indexable by being reversible, i.e., capable of being flipped over to permit use of cutting edges at a corner 75 defined by the intersection of the side wall 65 of the insert with the bottom surface 55, can be provided. A cutting tool 21' according to another embodiment is shown in Figures 8 and 9 and includes a toolholder 25' that comprises a single abutment member 43' and an insert abutment surface 67' that defines a non-zero angle with respect to the bottom abutment surface 27'. The insert 23' comprises at least one and, more typically, a plurality of side supporting surfaces 71'. One of the side supporting surfaces 71' is moved toward the side abutment surface 67' when the clamping screw 33' is tightened relative to the toolholder 25' and the insert 23' and moves the insert in the first direction D1. In this way, three points of contact are obtained between: 1 - the insert 23' and the bottom abutment surface 27'; 2 - the insert 23' and the abutment member 43'; and 3 - the insert 23' and the insert abutment surface 67'. The toolholder 25' shown in Figures 8 and 9 may have all of the features of the toolholder 25 shown in Figures 1-4 and 6-7, except that the toolholder shown in Figures 8 and 9 includes the insert abutment surface 67' in order to provide three points of contact with the insert 23'. The axis C1 of the internally threaded opening 31' in the projection 29' is typically located so that the first direction D1' is generally in a direction of a line defined by the point of contact between the insert 23' and the insert abutment surface 67' and the point of contact between the insert 23' and the abutment member 43. The insert 23' for the toolholder 25' shown in Figures 8 and 9 may be identical to the insert 23 used in the embodiment shown in Figures 1-7, however, the insert for the toolholder shown in Figures 8 and 9 need only include one recess 61' and, to be indexable, only needs two recesses, whereas the insert in the embodiment shown in Figures 1-7 requires at least two recesses 61 and, to be indexable, requires at least three recesses. In the present application, the use of terms such as "including" is open-ended and is intended to have the same meaning as terms such as "comprising" and not preclude the presence of other structure, material, or acts. Similarly, though the use of terms such as "can" or "may" is intended to be open-ended and to reflect that structure, material, or acts are not necessary, the failure to use such terms is not intended to reflect that structure, material, or acts are essential. To the extent that structure, material, or acts are presently considered to be essential, they are identified as such.

1. A toolholder (25; 25') comprising: a bottom abutment surface (27; 27');: a projection (29; 29') extending upwardly from the bottom abutment surface (27; 27'), the projection (29; 29') including an internally threaded opening (31; 31'), the internally threaded opening (31; 31') having a central axis (C1; C1') that is offset from a central axis (C3; C3') of the projection (29; 29') in a first direction (D1; D1'); and: a clamping screw (33; 33') having external threads (35; 35') for mating with internal threads of the internally threaded opening (31; 31') and a head (37) having a bottom clamping surface (39; 39') shaped as a truncated cone for contacting an insert clamping surface (41;41') and urging an insert (23; 23') in substantially the first direction (D1; D1') when the clamping screw (33; 33') is tightened relative to the toolholder (25; 25') and the insert (23; 23'),: characterized in that the toolholder (25; 25') comprises at least one abutment member (43; 43') extending from a side wall (45; 45') of the projection (29; 29') in a radial direction, each abutment member having an abutment point, at least the abutment point of the at least one abutment member (43; 43') being closer to the central axis (C3; C3') of the projection (29; 29') than to the central axis (C1; C1') of the internally threaded opening (31; 31').

2. The toolholder (21; 21') according to claim 1, characterized in that the projection (29; 29') is generally circularly cylindrical. 3. The toolholder (21; 21') according to any of claims 1-2, characterized in that each of the at least one abutment members (43; 43') comprises a circularly cylindrical pin. 4. The toolholder (21; 21') according to claim 3, characterized in that each pin is partially disposed in a respective recesses (53) in the projection (29; 29') that extends parallel to the central axis (C3; C3') of the projection (29; 29'). 5. A cutting tool (21; 21'), comprising a toolholder (25; 25') according to any of claims 1-5, and the cutting insert (23; 23') attachable to the toolholder (25; 25'), the insert (23; 23') comprising a bottom supporting surface (55, 55') for supporting the insert (23; 23') against the bottom abutment surface (27; 27'), a top surface (57; 57'), and a through hole (59) for receiving the projection (29; 29') extending from the bottom supporting surface (55; 55') to the top surface (57; 57'), the through hole (59) comprising an internal, cylindrical wall portion (47; 47') and an inverted truncated conical insert clamping surface (41; 41') between the cylindrical wall (47, 47') and the top surface (57; 57'), characterized in that the through hole (59) comprises a plurality of recesses (49; 49') having recess supporting surfaces (61; 61') in the cylindrical wall (47; 47') arranged to receive the at least one abutment member (43; 43') so that the abutment point of each abutment member (43; 43') of the at least one abutment member abuts against a corresponding one of the recess supporting surfaces (61; 61') when the clamping screw (33; 33') is tightened relative to the toolholder (25; 25') and the insert (23; 23') and moves the insert (23; 23') in the first direction (D1; D1'). 6. The cutting tool (21; 21') according to claim 5, characterized in that the insert (23; 23') comprises at least two recesses (49). 7. The cutting tool (21; 21') according to any of claims 5-6, characterized in that at the recess supporting surface(s) (61; 61') is/are radiused surface(s). 8. The cutting tool (21; 21') according to any of claims 5-7, characterized in that the insert (23; 23') comprises a plurality of cutting edges, each cutting edge corresponding to a respective recess (61; 61'). 9. The cutting tool (21') according to any of claims 1-8, characterized in that the toolholder comprises an insert abutment surface (67') that defines a non-zero angle with respect to the bottom abutment surface (27'), and in that the insert (23') comprises at least one side supporting surfaces (71'), one of the at least one side supporting surfaces (71') being moved toward the side abutment surface (67') when the clamping screw (33') is tightened relative to the toolholder (25') and the insert (23') and moves the insert (23') in the first direction (D1'). 10. The cutting tool (21) according to any of claims 1-8, characterized in that the toolholder (25) comprises two abutment members (43) extending from the side wall (45) of the projection in radial directions, the abutment members (43) each being closer to the central axis (C3) of the projection (29) than to the central axis (C1) of the internally threaded opening (31).

2883640

Cutting tool with replaceable abutment members and toolholder and cutting insert therefor

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figures 1 -3 show a cutting tool 21 according to an aspect of the present invention. The cutting tool 21 comprises a cutting insert 23 mounted to a toolholder 25. As seen, for example, in Figures 1 and 3, the toolholder 25 comprises a bottom abutment surface 27 and a projection 29 extending upwardly from the bottom abutment surface. The projection 29 includes an internally threaded opening 31 (e.g., Figures 1 and 4 ). The internally threaded opening 31 has a central axis C1 that is offset from a central axis C3 of the projection 29 in a first direction D1 (from C3 to C1) as seen in Figures 6 and 7. The toolholder 25 further comprises a clamping screw 33 having external threads 35 for mating with internal threads of the internally threaded opening 31 and a head 37 having a bottom clamping surface 39 shaped as a truncated cone ( Figures 1 and 3 ). As seen, for example, with reference to Figures 6 and 7, when the bottom clamping surface 39 of the head 37 contacts a correspondingly shaped insert clamping surface 41 on the cutting insert 23, the insert is urged in (or substantially in) the first direction D1 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert 23. While the insert 23 will ordinarily be moved in the first direction D1 when the clamping screw is tightened, the insert may not necessarily be moved in exactly the same direction as the first direction, such as if the insert contacts an abutment surface as in the embodiment shown in Figures 8 and 9 and moves at an angle to the first direction over at least some portion of its movement. The central axis C1 of the internally threaded opening 31 is the same as the central axis of the screw 33 when the screw is screwed into the internally threaded opening. The toolholder 25 further comprises at least two abutment members 43 extending from a side wall 45 of the projection 29 in radial directions. At least abutment points on the abutment members 43 are closer to the central axis C3 of the projection 29 than to the central axis C1 of the internally threaded opening 31 when measured in a plane perpendicular to the axes C1 and C3. Typically, the entire abutment member 43 is closer to the central axis C3 of the projection 29 than to the central axis C1 of the internally threaded opening. This is, for example, typically the case when the abutment members are in the form of circularly cylindrical pins as shown in, for example, Figures 1, 6, and 7. Abutment points on the abutment members 43 are defined as the forwardmost points on the abutment members facing the first direction D1. The abutment points on the abutment members contact corresponding supporting points of recess supporting surfaces 61 ( Figures 5-7 ). The projection 29 is typically but not necessarily generally circularly cylindrical, and an internal cylindrical wall 47 of the insert 23 is also typically but not necessarily generally circularly cylindrical. The internal cylindrical wall 47 of the insert 23 includes recesses 49 for receiving the abutment members 43. Providing generally circularly cylindrical shapes to the projection 29 and the internal cylindrical wall 47 of the insert 23 can facilitate indexing of the insert relative to the toolholder 25, although the insert may be indexed even if the shapes of the projection and internal cylindrical wall are not circular. The shapes may be "generally" circularly cylindrical in the sense that the abutment members 43 or the recesses 49 are spaced around the surfaces and prevent them from being perfectly circularly cylindrical. As seen in Figures 1 and 3-7, the abutment members 43 can comprise circularly cylindrical pins, although the abutment members may be provided in a variety of suitable forms, such as by being machined together with the projection 29 or secured to the projection by means such as brazing. Providing the abutment members 43 as circularly cylindrical pins permits the abutment members to be easily mounted in holes 51 ( Figures 1, 3, and 4 ) formed in the bottom abutment surface 27 and recesses 53 formed in the projection and, in the event of damage to the abutment members, removed from the holes and recesses. The circularly cylindrical shape of the abutment members 43 is also ordinarily relatively simple to manufacture. Use of easily removable abutment members 43 facilitates replacement of the abutment members in the event of damage which is not possible with conventional abutment surfaces that form surfaces of walls of pockets machined into blocks of material that form the toolholder. Recesses 53 in the projection 29 for the abutment members 43 in the form of replaceable pins will typically, but do not necessarily, extend parallel to the central axis C3 of the projection and perpendicular to the bottom abutment surface 27. The cutting insert 23 comprises a bottom supporting surface 55 for supporting the insert against the bottom abutment surface 27, a top surface 57, and a through hole 59 for receiving the projection 29. The through hole 59 extends from the bottom supporting surface 55 to the top surface 57. The through hole 59 comprises the internal, cylindrical wall portion 47 and an inverted truncated conical insert clamping surface 41 between the cylindrical wall and the top surface 57. As seen, for example, in Figures 1, 3, and 5-7, the through hole 59 comprises a plurality of recesses 49 having recess supporting surfaces 61 ( Figures 5-7 ) in the cylindrical wall 47 arranged to receive the abutment members 29 so that the abutment members abut against the recess supporting surfaces 61 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert 23 and moves the insert in the first direction D1 through the distance moved illustrated in Figure 7. The recesses 49 can extend to the insert clamping surface 41 and the bottom clamping surface 39 of the head 37 of the clamping screw 33 is preferably of sufficient size to cover all of the recesses to minimize the possibility of any chips from a workpiece falling into the recesses. A corner 63 is formed at an intersection of the top surface 57 and a side wall 65 of the insert 23. All or part of the corner 63 forms a plurality of different cutting edges when the insert 23 is indexed relative to the toolholder 25. The insert 23 can have a plurality of cutting edges as seen in Figure 1 (showing nine discrete straight-edge corner portions that can form parts of up to nine separate cutting edges) or the cutting edges may be formed as portions of, for example, an insert having a circular shape when viewed along a central axis C2 of the through hole 59 of the insert. The insert 23 comprises at least two recesses 49 for receiving the abutment members 43 and, more typically, at least three recesses 49 spaced such that the insert can be indexed relative to the at least two abutment members 43 on the toolholder 25 to at least two different positions to expose two or more different portions of the cutting edge. Each cutting edge corresponds to a respective pair of recesses 49 in which the abutment members 43 are received when the particular cutting edge is in a working position relative to the toolholder 25. In the embodiment shown in FIG 5, for example, there are nine elongated (and straight) portions of the corner 63 and nine transition portions disposed between respective pairs of the elongated portions. The elongated portions each have a corresponding recess 49 directed toward the elongated portion of the corner, typically centered along a line extending from the central axis C2 of the through hole 59 and bisecting the elongated portion of the corner. As seen in the illustrative insert 23 shown in, e.g., Figures 1 and 5, an insert may have nine recesses 49 spaced at angles AR of 40 degrees around the central axis C2 of the through hole 59 and can be indexed to up to nine different positions relative to the two abutment members 43 on the projection 29. At least when the abutment members 43 have radiused external surfaces, as when they are formed from circular pins, the recesses 49 are typically formed as radiused surfaces and, even if the entire recess 49 is not formed as a radiused surface, at least the recess supporting surfaces 61 are typically formed as radiused surfaces. The radii of the recesses 49 and/or the recess supporting surfaces 61 is at least as large as and, typically, slightly larger than the radii of the abutment members 43 to permit the abutment members to be received in the recesses. The recesses 49 seen in the embodiment shown in Figure 5 are in the form of generally circular arcs of about 180 degrees. The arcs may be smaller than 180 degrees, however, typically not less than about 90 degrees. The recesses 49 and the non-recessed portion of the internal cylindrical wall 47 together preferably define a cylinder. Longitudinal axes of the recesses 49 and the longitudinal axis of the internal cylindrical wall 47, i.e., the axis C2 of the insert through hole 59 are preferably perpendicular to a plane of the bottom surface 57 and, typically, to a plane of the top surface 55 of the insert 23. When the internal cylindrical wall 47 is generally circularly cylindrical, the radius of the internal cylindrical wall is typically between about 3-10 times as large as the radii of the recesses 49 and/or the recess supporting surfaces 61 and, more preferably, between 5-7 times as large. When the internal cylindrical wall 47 is generally circularly cylindrical, the material of the internal cylindrical wall defining spaces between the recesses 49 typically defines an arc of a circle. The size of the arc of the circle depends upon the size and number of the recesses 49 relative to the size of the internal cylindrical wall 47. In an insert 23 as shown in Figure 5 that has nine recesses 49 that are approximately 1/6 the size of the diameter of the generally circularly cylindrical internal cylindrical wall 47, the material of the internal cylindrical wall between the recesses defines an arc of a circle that is about 20 degrees. The nine recesses 49, likewise, extend over arcs of the circle of the generally circularly cylindrical internal cylindrical wall 47 that are about 20 degrees. Thus, while not necessarily true of all embodiments of the insert 23, the arc of the circle between each recess is roughly equal to or greater than the arc of the circle across each of the recesses 49. As seen in the illustrative toolholder 25 shown in, e.g., Figures 1 and 4, the abutment members 43 are typically spaced at an angle AA around the central axis C3 of the projection 29 that is slightly less than an angle between the two recesses 49 of the insert 23 in which the abutment members 43 are to be received. For example, in the case of the abutment members 43 shown in the cutting tool 21 of Figure 1 for use with the insert 23 having nine recesses 49 spaced at 40 degrees around the insert opening axis C2, the abutment members might be at an angle of 79 degrees around the central axis C3 of the projection 29 as they are intended to be received in recesses 49 in the insert that are spaced at 80 degrees around the insert opening axis. By arranging the abutment members 43 so that they define a slightly smaller angle about the central axis C3 of the projection than the angle that the recesses 49 in which they are to be received define about the insert opening axis C2, when the insert 23 is moved in the first direction D1 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert, i.e., moved from the position shown in Figure 6 to the position shown in Figure 7, the radiused surfaces of the abutment members 43 will tend to contact the recesses 49 on parts of the recesses that are closest to each other as seen in Figure 7. This will tend to minimize any tendency of the insert to move relative to toolholder during a cutting operation. The abutment members 43 may be but need not be received in consecutive ones of the recesses 49. Arranging the abutment members 43 so that they are received in non-consecutive ones of the recesses 49 can help to provide good, evenly spaced support for the insert 23 on the toolholder 25. Where the toolholder 25 has two abutment members 43, it may, but need not, further comprise one or more additional side surfaces 67 and 69, that define non-zero angles with respect to the bottom abutment surface 27 and with respect to each other. Because the side surfaces 67 and/or 69 can ordinarily be entirely omitted, this provides substantially greater design flexibility for the toolholder 25. If side surfaces 67 and/or 69 are provided, part or all of the side wall 65 of the insert 23 may comprise one (particularly in the case of a circular insert) or a plurality of side insert surfaces which are moved toward but do not contact the side surfaces 67 and 69 when the clamping screw 33 is tightened relative to the toolholder 25 and the insert 23 and moves the insert in the first direction D1. To avoid overdetermination, the side insert surfaces will ordinarily not contact the side surfaces 67 and 69 at all, however, there may be some contact in some designs when cutting forces urge the insert 23 in the first direction D1. The abutment members 43 will contact the recess supporting surfaces 61 in the recesses 49 before the side surfaces 67 and 69 and the side insert surfaces come into contact. In this way, the brunt of the forces on the insert 23 during a cutting operation will be borne by the abutment members 43 rather than the side surfaces 67 and 69, which can be useful if the abutment members 43 are in a form such that they can be easily replaced. As is seen in Figures 6 and 7, in the cutting tool 21, no part of the insert 23 contacts side insert abutment surfaces 67 and 69 in the pocket. Moreover, because the abutment members 43 function as replacements for traditional side abutment surfaces and can be located relatively close to the working cutting edges as compared to side abutment surfaces, this can reduce the effect of size variations in the insert. For example, in a conventional insert, the position of the cutting edge relative to the toolholder is dependent upon the distances from the points at which the side insert supporting surfaces contact the side abutment surfaces to the cutting edge whereas, in an insert as described herein, the position of the cutting edge relative to the toolholder is dependent upon the much shorter distances from the points at which the abutment members 43 contact the recess supporting surfaces 61 to the cutting edge. A variation in insert size will have less impact on the location of the cutting edge in a cutting tool according to aspects of the present invention than in a conventional cutting tool. As can be appreciated from, for example, in Figure 3, the abutment members 43 can contact the recess supporting surfaces 61 close to the top surface 57 of the insert, near the point of contact between the clamping surfaces 39 and 41 of the clamping screw 33 and the insert 23. This feature can facilitate support of the insert 23 relative to the toolholder 25 and the projection 29, particularly as compared to other "bottom support" style inserts that involve projections that only extend a minimal distance above a bottom abutment surface of the toolholder. Moreover, this feature can facilitate avoidance of any tendency of an insert to climb up a bottom support-style projection that might occur as the result of cutting forces on the insert when side surfaces of the projection are sloped or of minimal height. The top and bottom surfaces 57 and 55 of the insert 23 may be identical, and the through hole 59 may comprise a second inverted truncated conical insert clamping surface 73 ( Figure 3 ) between the cylindrical wall 47 and the bottom surface 55. By such a structure, an insert 23 that is indexable by being reversible, i.e., capable of being flipped over to permit use of cutting edges at a corner 75 defined by the intersection of the side wall 65 of the insert with the bottom surface 55, can be provided. A cutting tool 21' according to another embodiment is shown in Figures 8 and 9 and includes a toolholder 25' that comprises a single abutment member 43' and an insert abutment surface 67' that defines a non-zero angle with respect to the bottom abutment surface 27'. The insert 23' comprises at least one and, more typically, a plurality of side supporting surfaces 71'. One of the side supporting surfaces 71' is moved toward the side abutment surface 67' when the clamping screw 33' is tightened relative to the toolholder 25' and the insert 23' and moves the insert in the first direction D1. In this way, three points of contact are obtained between: 1 - the insert 23' and the bottom abutment surface 27'; 2 - the insert 23' and the abutment member 43'; and 3 - the insert 23' and the insert abutment surface 67'. The toolholder 25' shown in Figures 8 and 9 may have all of the features of the toolholder 25 shown in Figures 1-4 and 6-7, except that the toolholder shown in Figures 8 and 9 includes the insert abutment surface 67' in order to provide three points of contact with the insert 23'. The axis C1 of the internally threaded opening 31' in the projection 29' is typically located so that the first direction D1' is generally in a direction of a line defined by the point of contact between the insert 23' and the insert abutment surface 67' and the point of contact between the insert 23' and the abutment member 43. The insert 23' for the toolholder 25' shown in Figures 8 and 9 may be identical to the insert 23 used in the embodiment shown in Figures 1-7, however, the insert for the toolholder shown in Figures 8 and 9 need only include one recess 61' and, to be indexable, only needs two recesses, whereas the insert in the embodiment shown in Figures 1-7 requires at least two recesses 61 and, to be indexable, requires at least three recesses. In the present application, the use of terms such as "including" is open-ended and is intended to have the same meaning as terms such as "comprising" and not preclude the presence of other structure, material, or acts. Similarly, though the use of terms such as "can" or "may" is intended to be open-ended and to reflect that structure, material, or acts are not necessary, the failure to use such terms is not intended to reflect that structure, material, or acts are essential. To the extent that structure, material, or acts are presently considered to be essential, they are identified as such.

11. A cutting insert (23; 23'), comprising: a bottom surface (55; 55'), a top surface (57; 57'), and a through hole (59) extending from the bottom surface (55; 55') to the top surface (57; 57'), the through hole (59) comprising an internal, cylindrical wall portion (47; 47') and an inverted truncated conical insert clamping surface (41; 41') between the cylindrical wall (47; 47') and the top surface (57; 57'), characterized in that the through hole (59) comprises a plurality of recesses (49; 49') having recess supporting surfaces (61; 61') in the cylindrical wall (47; 47').

12. The cutting insert (23; 23') according to claim 11, characterized in that the cylindrical wall (47; 47') is generally circularly cylindrical. 13. The cutting insert (23; 23') according to any of claims 11-12, characterized in that at least the recess supporting surfaces (61; 61') are radiused surfaces. 14. The cutting insert (23; 23') according to any of claims 11-13, characterized in that the insert (23; 23') comprises a plurality of cutting edges, each cutting edge corresponding to a respective pair of recesses (49; 49'). 15. The cutting insert (23; 23') according to any of claims 11-14, characterized in that the top and bottom surfaces (55; 55' and 57; 57') are identical, the through hole (59) comprises a second inverted truncated conical insert clamping surface between the cylindrical wall (47; 47') and the bottom surface (55; 55'), and the insert (23; 23') is reversible. 16. The cutting insert (23; 23') according to any of claims 11-15, characterized in that the corner (63; 63') comprises a plurality of discrete elongated portions and a plurality of discrete transition portions, each transition portion being disposed between a respective pair of elongated portions, each elongated portion having a corresponding recess (49; 49') directed toward the elongated portion and centered along a line extending from the central axis (C2; C2') of the through hole (59; 59') and bisecting the elongated portion. 17. The cutting insert (23; 23') according to any of claims 11-16, characterized in that material of the cylindrical wall (47; 47') defining spaces between the recesses (49; 49') defines an arc of a circle, the recesses (49; 49') extend over arcs of the circle of the cylindrical wall (47; 47') that are about 20 degrees, and arcs of the circle between each recess (49; 49') are equal to or greater than arcs of the circle across each of the recesses (49; 49). 18. The cutting insert (23; 23') according to any of claims 11-17, characterized in that the recesses (49; 49') extend to the clamping surface (41; 41').

2884219

Automatic shooting ribbon dispenser

Based on the following detailed description of an invention, generate the patent claims. There should be 6 claims in total. The first, independent claim is given and the remaining 5 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to Figures 1 and 2, the ribbon dispenser of the present invention comprises a body 1, a front cover 2, a cylinder 3, a trigger 4, a striking unit 5 and a revolving unit 6, wherein the body 1 is a hollow body composed of a right case 11 and a left case 12. The front cover 2 is pivotally connected to the front end of the body 1. The front cover 2 has a hole 21 which communicates with the interior of the body 21. The cylinder 3 is rotatably located in the body 1 and located behind the rear end of the front cover 2, so that the cylinder 3 can be installed into the body 1 or removed from the body 1 via the front end of the body 1. The trigger 4 is pivotally connected to the body 1 and located outside of the body 1. The trigger 4 has a pivot 41 which is pivotally connected between the right and left cases 11, 12 so that when the trigger 4 is pivoted, the trigger 4 is pivoted about the pivot 41. The striking unit 5 is located in the body 1 and located behind the cylinder 3 so as to introduce air into the chambers 32 via the inlets 33. The revolving unit 6 is located in the body 1 and connected to the cylinder 3 so as to revolve the cylinder 3. As shown in Figures 3 and 4, the cylinder 3 has an engaging slot 31 on the rear end thereof and comprises multiple chambers 32 in which ribbons (not shown) are received. The chambers 32 are arranged radially about the center of the cylinder 3. Each chamber 32 has an opening located behind the rear end of the front cover 2 as shown in Figure 2. An inlet 33 is defined through the rear end of each chamber 32 so that the ribbons are ejected from the hole 21 of the body 1 as shown in Figure 1. The shape of the engaging slot 31 can be triangular slot, polygon slot, oval slot or any known slot. As shown in Figures 2 and 5, the trigger 4 has a driving portion 42 on the rear end thereof so as to drive the striking unit 5. The striking unit 5 comprises a tube 51, a piston 52, a compression spring 53, an arm 54, a link 55 and a pawl 56. The tube 51 is located behind the rear end of the cylinder 3 and has an outlet 512 defined in the front end thereof and the outlet 512 is located corresponding to the cylinder 3. The piston 62 is located in the tube 51 and has at least one piston ring 522 mounted thereto which is in contact with an inside of the tube 51 so as to provide better air-tightness. The compression spring 53 is located on the rear end of the piston 52 so as to push the piston 532 toward the cylinder 3. The front end of the compression spring 53 is located adjacent to the rear end of the cylinder 52 and the rear end of the compression spring 53 is located adjacent to two stops 13 of the body 1. The front end of the arm 54 is pivotally connected to the rear end of the piston 52 and the rear end of the arm 54 is pivotally connected to the front end of the link 55. As shown in Figures 2, 5 and 6, the pawl 56 is pivotally connected to the body 1 by a pin 57, and the rear end of the link 55 is pivotally connected to the pawl 56 by the pin 57. The pawl 56 has a first surface 562 formed on the top thereof. The pawl 56 has a tip 564 which extends to a rotation area of the driving portion 42 and located above the driving member 42 so that the driving member 42 is able to push the pawl 56 which pivots the link 55 toward the rear end of the body 1. The link 55 has a second surface 552 which is rested on the first surface 562 so that the pawl 56 pivots the link 55 about the pin 57 and toward the rear end of the body 1. A torsion spring 58 has two legs 582 which are connected between the link 55 and the pawl 56, such that the link 55 and the pawl 56 can return to their initial positions. As shown in Figures 2 and 7, a stud 43 protrudes from one side of the trigger 4 so as to drive the revolving unit 6. The stud 43 is located between the pivot 41 and the body 1. The revolving unit 6 has a rod 61, an extension spring 62, a revolving member 63 and a shaft 64. The rod 61 has two protrusions 612 respectively extending from one side thereof. The body 1 has a restriction slot 112 defined in the right case 11 as shown in Figure 10 and the two protrusions 612 are located within the restriction slot 112. The rod 61 extends through a guide slot 614 which has a first end extending toward a top of the body 1 and a second end of the guide slot 614 extends toward the bottom of the body 1. The stud 43 is pivotally located in the guide slot 614 so as to move the rod 61 toward the cylinder 3 when the trigger 4 is pulled. As shown in Figure 10, a push member 616 extends from the other one side of the rod 61 which pivots the revolving member 63. The push member 616 has a first inclined face 6162 and a second inclined face 6164 respectively formed on front and rear end thereof. The front end of the extension spring 62 is hooked to the rear end of the rod 61. The rear end of the extension spring 62 is connected to the inside of the body 1 so as to move the rod 61 toward the rear end of the body 1. The revolving member 63 is located behind the cylinder 3 and the front end of the revolving member 63 is connected to the shaft 64 which is engaged with the engaging slot 31 of the cylinder 3 as shown in Figure 4, so that the revolving member 63 and the cylinder 3 are co-rotated with each other. A shown in Figure 8, the revolving member 63 has multiple first guide members 632 and multiple second guide members 634 on outside thereof. The number of each of the first and second guide members 632, 634 is the same as the number of the chambers 32 of the cylinder 3. The first guide members 632 are located adjacent to the first end of the revolving member 63, the first end of the revolving member 63 is located remote from the cylinder 3. The second guide members 634 are located adjacent to a second end of the revolving member 63, the second end of the revolving member 63 is located close to the cylinder 3. A first notch 633 is defined between any two adjacent first guide members 632. A second notch 633 is defined between any two adjacent second guide members 634. The first guide members 632 are located corresponding to the second notches 635, the second guide members 634 are located corresponding to the first notches 633. Each of the first guide members 632 has a first curved face 6322 on one side thereof, the first curved face 6322 is located to face the opening of the second notch 635. Each of the second guide members 634 has a second curved face 6342 on one side thereof, the second curved face 6342 is located to face an opening of the first notch 633. The push member 616 is moved back and forth between the first and second notches 633, 635 to revolve the revolving member 63. The rod 61 revolves the revolving member 63 by the push member 616. When the user pulls the trigger 4 which is pivoted about the pivot 41 counter clockwise. The driving portion 42 pushes the tip 564 and the pawl 56 is pivoted clockwise about the pin 57. Because the second surface 552 is rested on the first surface 562, the pawl 56 pivots the link 55 clockwise about the pin 57 and toward the rear end of the body 1. The piston 52 is pulled by the arm 54 to suck air into the room between the piston 52 and the outlet 512. The piston 52 compresses the compression spring 53. When the tip 564 is rotated clockwise with the pawl 56 and removes from the rotation area of the driving portion 42, driving portion 42 is separated from the tip 564, so that the pawl 56 is not pushed by the driving portion 42. The compression spring 53 provides a force to move the piston 52 forward, the air in the tube 51 is pushed from the outlet 512 and enters into the chamber 32 via the inlet 33, therefore, the ribbons in the chamber 32 are ejected from the hole 21 of the body 1. The forward movement of the piston 53 makes the arm 54, the link 55 and the pawl 45 to move back to their initial positions. Besides the ejection of the ribbons by pulling the trigger 4, the pulling of the trigger 4 also moves the stud 43 to move the rod 61 forward and the extension spring 62 is extended. After the ribbons are ejected, user releases the trigger 4 the extension spring 62 pulls the rod 61 to move backward to its initial position. When the rod 61 moves backward, the trigger 4 is pivoted clockwise about the pivot 41 to its initial position. When the trigger 4 is pivoted clockwise, the driving portion 42 touches the tip 564 and the pawl 56 is pivoted counter clockwise about the pin 57. Because the pawl 56 is pivotally connected to the link 55 by the pin 57, and the can only drive the link 55 toward the rear end of the body 1 in one direction, so that the pawl 56 cannot drive the link 55, the arm 54 and the piston 52 when the pawl 56 is pivoted counter clockwise. The pawl 56 is rotated relative to the link 55 so as to activate the torsion spring 58. When the tip 564 and the pawl 56 are both pivoted counter clockwise, and the tip 564 is removed from the rotation area of the driving portion 42, the driving portion 42 is separated from the tip 564, so that the pawl 56 is not pushed by the driving portion 42. The torsion spring 58 provides a force to pivot the pawl 56 clockwise back to its initial position. When the user pulls the trigger 4 and the rod 61 moves forward, the push member 616 is moved forward from the first notch 633. When the first inclined face 6162 contacts the second guide member 634 located corresponding to the first notch 633, because the shape of the first inclined face 6162 and the second curved face 6342 of the second guide member 634, the push member 616 is guided by the second curved face 6342 and enters into the second notch 635. The push member 616 pushes the second curved face 6342 laterally so that the revolving member 63 is revolved to rotate the cylinder 3. One of the inlet 33 of the cylinder 3 is located corresponding to the outlet 512 of the tube 51, so that air is introduced into the chamber 32 to eject the ribbons in the chamber 32 out from the hole 21 of the body 1. When the user releases the trigger 4 and the rod 61 moves backward, the push member 616 is moved backward from the second notch 635. When the second inclined face 6164 contacts the first guide member 632 located corresponding to the second notch 635, because the shape of the second inclined face 6164 and the first curved face 6322 of the first guide member 632, the push member 616 is guided by the first curved face 6322 and enters into the first notch 633. The push member 616 pushes the first curved face 6322 laterally so that the revolving member 63 is revolved to rotate the cylinder 3. The outlet 512 of the tube 51 is located between two adjacent inlets 33 of the cylinder 3. The user pulls and releases the trigger 4 to activate the striking unit 5 and revolves the revolving unit 6 to eject the ribbons, the action to the trigger 4 can be operated consecutively to eject the ribbons in the chambers 32 of the cylinder 3 consecutively without any extra action needed. After all of the ribbons in the chambers 32 are ejected, the user can open the front cover 2 to replace a new cylinder 3 and the ribbon dispenser can be used again within short period of time. While we have shown and described the embodiment in accordance with the present invention, it should be clear to those skilled in the art that further embodiments may be made without departing from the scope of the present invention.

1. A ribbon dispenser comprising: a body being a hollow body; a front cover pivotally connected to a front end of the body and having a hole which communicates with an interior of the body; a cylinder rotatably located in the body and located behind a rear end of the front cover, the cylinder having multiple chambers in which ribbons are received, the chambers being arranged radially about a center of the cylinder, an opening of each chamber located behind the rear end of the front cover, an inlet defined through a rear end of each chamber; a striking unit located in the body and located behind the cylinder so as to introduce air into the chambers via the inlets; a revolving unit located in the body and connected to the cylinder so as to revolve the cylinder, and a trigger pivotally connected to the body and located outside of the body, the trigger having a driving portion on a rear end thereof so as to drive the striking unit, a stud protruding from a side of the trigger so as to drive the revolving unit.

2. The dispenser as claimed in claim 1, wherein the striking unit comprises a tube, a piston, a compression spring, an arm, a link and a pawl, the tube is located behind the rear end of the cylinder and has an outlet defined in a front end thereof, the piston is located in the tube and the compression spring is located on a rear end of the piston so as to push the piston toward the cylinder, a front end of the arm is pivotally connected to the rear end of the piston and a rear end of the arm is pivotally connected to a front end of the link, a rear end of the link is pivotally connected to the pawl which is pivotally connected to the body, the pawl has a tip which extends to a rotation area of the driving portion and located above the driving member so that the driving member is able to push the pawl which pivots the link toward a rear end of the body, a torsion spring is connected between the link and the pawl, the revolving unit has a rod, an extension spring, a revolving member and a shaft, the rod has two protrusions respectively extending from one side thereof, the body has a restriction slot defined therein and the two protrusions are located within the restriction slot, the rod extends through a guide slot which has a first end extending toward a top of the body and a second end of the guide slot extending toward a bottom of the body, the stud is pivotally located in the guide slot so as to move the rod toward the cylinder, a push member extends from the other one side of the rod which pivots the revolving member, the push member has a first inclined face and a second inclined face respectively formed on front and rear end thereof, a front end of the extension spring is connected to a rear end of the rod, a rear end of the extension spring is connected to an inside of the body so as to move the rod toward the rear end of the body, the revolving member is located behind the cylinder and the revolving member is connected to the shaft which is connected to the cylinder so that the revolving member and the cylinder are co-rotated with each other, the revolving member has multiple first guide members and multiple second guide members on outside thereof, the first guide members are located adjacent to a first end of the revolving member, the first end of the revolving member is located remote from the cylinder, the second guide members are located adjacent to a second end of the revolving member, the second end of the revolving member is located close to the cylinder, a first notch is defined between any two adjacent first guide members, a second notch is defined between any two adjacent second guide members, the first guide members are located corresponding to the second notches, the second guide members are located corresponding to the first notches, each of the first guide members has a first curved face on one side thereof, the first curved face is located to face an opening of the second notch, each of the second guide members has a second curved face on one side thereof, the second curved face is located to face an opening of the first notch, the push member is moved back and forth between the first and second notches to revolve the revolving member. 3. The dispenser as claimed in claim 2, wherein the cylinder has an engaging slot on the rear end thereof and the shaft is engaged with the engaging slot so that the revolving member drives the shaft to revolve the cylinder. 4. The dispenser as claimed in claim 2, wherein the piston has at least one piston ring mounted thereto which is in contact with an inside of the tube. 5. The dispenser as claimed in claim 2, wherein a front end of the compression spring is located adjacent to the rear end of the cylinder and a rear end of the compression spring is located adjacent to two stops of the body. 6. The dispenser as claimed in claim 2, wherein the pawl has a first surface formed on a top thereof and the link has a second surface which is rested on the first surface so that the pawl pivots the link toward the rear end of the body.

2884212

Method for producing a plate heat exchanger and plate heat exchanger

Based on the following detailed description of an invention, generate the patent claims. There should be 7 claims in total. The first, independent claim is given and the remaining 6 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figs 1 and 2 disclose a plate heat exchanger 1 comprising a plate package 2 having heat exchanger plates 3 which are provided beside each other. The plate package 2 is provided between two end plates 4 and 5 which may form a frame plate and a pressure plate, respectively. The end plates 4 and 5 are pressed against the plate package 2 and against each other by means of tie bolts 6 which extend through the end plates 4 and 5. The tie bolts 6 comprise threads and the plate package 2 may thus be compressed by screwing nuts 7 on the tie bolts 6 in a manner known per se. In the embodiment disclosed, four tie bolts 6 are indicated. It is to be noted that the number of tie bolts 6 may vary and be different in different applications. The plate heat exchanger 1 comprises according to the embodiments described also a first inlet port 8 and a first outlet port 9 for a first medium, and a second inlet port 10 and a second outlet port 11 for a second medium. The inlet and outlet ports 8-11 extend in the embodiments disclosed through one of the end plates 4 and the plate package 2. The ports 8-11 may be arranged in many different ways and also through the second end plate 5. The heat exchanger plates 3 may be manufactured in a compression- moulded metal sheet, carbon steel, stainless steel, or any other material which is suitable for the intended application. Each heat exchanger plate 3 comprises a heat transfer area 12 and an edge area 13, which extends around and outside the heat transfer area 12. The heat transfer area 12 is in the embodiment disclosed substantially centrally located on the heat exchanger plate 3, and in a known manner provided with a corrugation 14 of ridges and valleys. The corrugation 14 is obtained through compression-moulding of the metal sheet. In the embodiment disclosed, the corrugation 14 has merely been indicated schematically as extending obliquely over the heat transfer area 12. It is to be noted that the corrugation 14 also may comprise significantly more complicated extensions of the ridges and valleys, for instance along the fishbone pattern known per se. Also heat exchanger plates 3 having a substantially plane heat transfer area may be used within the scope of this invention. Each heat exchanger plate 3 also comprises a number of portholes 15, in the embodiment disclosed four portholes 15, which extend through the heat exchanger plate 3 and are located inside and in the proximity of the edge area 13. The portholes 15 are located in the proximity a respective corner of the heat exchanger plate 3 and are substantially concentric with the above mentioned inlet and outlet ports 8-11 of the plate heat exchanger 1. The heat exchanger plates 3 are provided in such a manner in the plate package 2 that first plate interspaces 16, which communicate with the first inlet port 8 and the first outlet port 9, and second plate interspaces 17, which communicate with the second inlet port 10 and the second outlet port 11, are formed, see figs. 1 and 6. The first and second plate interspaces 16 and 17 are provided in an alternating order in the plate package 2. Such a separation of the plate interspaces 16, 17 may be achieved by means of one or several gaskets 18, which extend in the gasket grooves 19 which are formed during the compression-moulding of the heat exchanger plates 3. The gasket groove 19 of each heat exchanger plate 3 extends, as can be seen in fig. 3, around the heat transfer area 15 and around each of the portholes 15. At each heat exchanger plate 3 a gasket 18 is, in the embodiments disclosed, provided before the mounting of the plate heat exchanger 1. The gasket 18 extends in a part of the gasket groove 19 in such a way that the gasket 18 encloses the heat transfer area 12 and two of the portholes 15 and also each of the two remaining portholes 15. The gasket 18 thus forms three separate areas which are delimited from each other by means of the gasket 18. It is to be noted that the gasket 18 does not necessarily need to be shaped as one single gasket 18 but may also consist of several different gaskets. During the mounting, every second heat exchanger plate 3 may be rotated 180°, for instance around a central normal axis or round a central longitudinal axis. Thereafter the heat exchanger plates 3 are compressed so that the desired first and second plate interspaces are obtained. In the plate package 2, the first medium may be introduced through the first inlet port 8, through the first plate interspaces 16 and out through the first outlet port 9. The second medium may be introduced through the second inlet port 10, through the second plate interspaces 17 and out through the second outlet port 11. The two media may for instance be conveyed in a counter current flow, as indicated in figs. 2 and 3, or in parallel flow in relation to each other. In the embodiments described, the portholes 15 have a cylindrical or substantially circular shape. The portholes 15 may however also have any other suitable regular or irregular shape, for instance an oval shape or a polygonal shape, for instance a triangular, a square, a pentagonal etc. shape suitably with somewhat rounded corners. The heat exchanger plate 3 may be used in various plate heat exchanger applications and include fewer or more than the portholes 15 disclosed. Furthermore, the invention is applicable to plate heat exchangers without portholes 15, wherein the inlet members and the outlet members may connect to different sides of the plate package. According to the invention a plate for a plate heat exchanger as described above is coated with a tantalum containing compound preferably metal tantalum, tantalum oxide and/or tantalum nitride, which is applied on the surfaces of the heat exchanger plates 3 to be in contact with highly corrosive fluid. In a preferred embodiment the tantalum containing compound is metal tantalum and/or tantalum oxide, preferably metal tantalum. If the tantalum coating is made of metal tantalum the uppermost part of the coating is oxidized and thus is tantalum oxide. The coating may according to the invention preferably be applied by means of Chemical Vapor Deposition (CVD). A basic CVD process may consist of the following steps: 1) a predefined mix of reactant gases and diluent inert gases are introduced at a specified flow rate into the reaction chamber; 2) the gas species move to the substrate; 3) the reactants get adsorbed on the surface of the substrate; 4) the reactants undergo chemical reactions with the substrate to form the film; and 5) the gaseous by-products of the reactions are desorbed and evacuated from the reaction chamber. According to the present invention the tantalum containing coating applied onto the surfaces in at least one of the flow sides designated for being used for highly corrosive fluids has preferably a film thickness of about 1-125 µm, preferably 1-50 µm, more preferably 10-40 µm and even more preferably 15-25 µm. Thermo-chemical surface treatments of iron and steel by means of nitrogen or carbon carrying gases are known processes, called nitriding or carburizing, respectively. Nitrocarburizing is a process in which a gas carrying both carbon and nitrogen is used. These processes are traditionally applied to improve the hardness and wear resistance of iron and low alloyed steel articles. The steel article is exposed to a carbon and/or nitrogen carrying gas at an elevated temperature for a period of time, whereby the gas decomposes and carbon and/or nitrogen atoms diffuse through the steel surface into the steel material. The outermost material close to the surface is transformed into a layer with improved hardness, and the thickness of this layer depends on the treatment temperature, the treatment time and the composition of the gas mixture. According to the present invention the plates 3, after the coating by a tantalum containing compound, are treated in a nitrogen containing gas atmosphere at a temperature of approximately 800 - 1200°C, preferably 850- 950°C, and most preferably at a temperature 900°C, for about an hour. The nitrogen containing gas may be chosen from nitrides, especially amides such as urea, acetamide and formamide Before the treatment the hardness of the tantalum containing layer was measured to approximately 300 HV by means of e g a hardnessmeter. After the nitrogen containing gas treatment, the surface hardness of the tantalum containing layer was measured to approximately 1500 HV. The hardness of the tantalum containing layer at a distance of approximately 2 µm from the surface was measured to a value of approximately 600 HV. According to the invention the hardness of the plates is preferably > 1000 HV. By the method of the invention a corrosion resistant plate heat exchanger is achieved which is cheaper to manufacture and has a longer life time than previously known tantalum coated plate heat exchangers. Due to the hardening of the tantalum containing coating, the abrasion resistance and the wear resistance of the coating is increased, which is especially valuable in the contact points between the plates.

1. Method for producing a plate heat exchanger (1) comprising a plurality of heat exchanger plates (3), wherein the heat exchanger plates (3) are provided adjacent each other and form a plate package (2) with first plate interspaces (16) for a first medium and second plate interspaces (17) for a second medium, wherein each of the heat exchanger plates comprises: portholes (15) which form ports (8, 9, 10, 11) extending through the plate package (2),: a heat transfer area (12),: an edge area (13) extending outside the heat transfer area (12) and the ports (8, 9, 10, 11),: a gasket groove (19) extending in the edge area (13) outside the heat transfer area (12) and the ports (8, 9, 10, 11),: and wherein a gasket (18) is provided in the gasket groove (19) for tight abutment against an adjacent plate (3) in the plate heat exchanger (1), the heat exchanger plates (3) being at least partly coated with a tantalum containing coating, characterized in that: the plates (3) are treated by nitrides at a temperature of 800 - 1200°C in order to increase the hardness and wear resistance of the tantalum surface.

2. Method for producing a plate heat exchanger according to claim 1, characterized in that the plates (3) are treated by nitrides at a temperature of 850 - 950°C, preferably at a temperature of 900°C. 3. Method for producing a plate heat exchanger according to claim 1 or 2, characterized in that the nitrides are chosen from amides such as urea, acetamide and formamide. 4. Method for producing a plate heat exchanger according to any one of claims 1-3, characterized in that the coating has a surface hardness of > 600 HV. 5. Method for producing a plate heat exchanger according claim 1 or 2, characterized in that the coating has a surface hardness of > 1000 HV. 6. A plate for a plate heat exchanger produced according to the method of any one of claims 1-5. 7. A plate heat exchanger produced according to the method of any one of claims 1-5.

2883731

Disconnector for hybrid vehicle

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Hereinafter, examples of embodiments of the invention will be described in detail with reference to the accompanying drawings such that they can easily be made and used by those skilled in the art. Advantages and features of the present invention and methods of accomplishing the same may be understood more readily by reference to the following detailed description of preferred embodiments and the accompanying drawings. However, the following descriptions of such embodiments are intended primarily for illustrating the principles and exemplary constructions of the present invention, and the present invention is not specifically limited to these exemplary embodiments. Thus, one skilled in the art can appreciate or recognize that various modifications, substitutions and equivalents thereof can be made thereto without departing from the spirit and scope of the present invention. In addition, it should be understood that the terms and words used in the specification and the appended claims should not be construed as limited to general and dictionary meanings, but interpreted based on the meanings and concepts corresponding to technical aspects of the present invention on the basis of the principle that the inventor is allowed to define terms appropriately for the best explanation for the invention. For the sake of convenience, an orientation is set on the basis of illustration of figures. Figure 1 is a perspective view illustrating an assembled state of a disconnector for a hybrid vehicle according to an embodiment of the present invention, Figure 2 is a front view of the disconnector for a hybrid vehicle shown in Figure 1, Figure 3 is a cross-sectional view taken along the line A-A of Figure 2, Figure 4 is a cross-sectional view taken along the line B-B of Figure 2, illustrating a case of interrupting power, and Figure 5 is a cross-sectional view taken along the line B-B of Figure 2, illustrating a case of transmitting power. As shown in Figures 1 to 5, the disconnector for a hybrid vehicle according to an embodiment of the present invention includes an upper housing 1 connected to a reducer A, an input shaft 3 installed inside the upper housing 1 and transmitting rotary power of the reducer A, bearings 9 and 10 installed between the upper housing 1 and the input shaft 3, a hub 4 disposed under the input shaft 3, a sleeve 5 having an inner circumferential surface spline-coupled to outer circumferential surfaces of the input shaft 3 and the hub 4 to then be shifted to transmit or interrupt the rotary power of the input shaft 3 to the hub 4, a shift fork 6 coupled to an outer circumferential surface of the sleeve 5 and shifting the sleeve 5, a first spring 12 installed between the upper housing 1 and the shift fork 6, a lower case 2 connected to a lower portion of the upper housing 1, a constant velocity joint B connected to the hub 4 through the inside of the lower case 2, a needle roller 11 installed between the lower case 2 and the constant velocity joint B, an actuator 8 coupled to the inside of the lower case 2 and pushing out the shift fork 6, and a linear sensor 15 sensing a transfer distance of the shift fork 6. The actuator 8 includes a motor 81 generating rotary power, a lead screw 82 converting a rotary motion of the motor 81 into a linear motion, a cover 84 mounted at a front end of the lead screw 82, a second spring 83 installed between the lead screw 82 and the cover 84, and a position sensor 85 installed to be spaced apart from one side of the lead screw 82. A reversible motor is used as the motor 81. Figure 6 is a perspective view of a shift fork of the disconnector for a hybrid vehicle shown in Figure 1 and Figure 7 is a cross-sectional view taken along the line C-C of Figure 6. As shown in Figure 6, in the disconnector for a hybrid vehicle according to an embodiment of the present invention, the shift fork 6 has an inclined surface 61 formed at a region positioned to correspond to the linear sensor 15. The aforementioned disconnector for a hybrid vehicle according to an embodiment of the present invention operates as follows. If power is applied to the actuator 8 to transfer rotary power from the reducer A to the constant velocity joint B, the rotary power is generated from the motor 81 and the lead screw 82 converts a rotary motion of a rotary shaft of the motor 81 into a linear motion to transfer the linear motion to the cover 84. Here, a transfer completion position of the lead screw 82 is sensed by the position sensor 85. If the lead screw 82 pushes the cover 84, the cover 84 lifts the shift fork 6 while exhibiting a buffering action derived from an elastic force of the second spring 83. Accordingly, the shift fork 6 shifts the sleeve 5 coupled to the hub 4 toward the input shaft 3, thereby commonly coupling the sleeve 5 to the hub 4 and the input shaft 3. Here, the linear sensor 15 is installed at a region corresponding to the inclined surface 61 of the shift fork 6 to measure a transfer distance of the shift fork 6, thereby accurately controlling the transfer distance of the shift fork 6. If the shift fork 6 shifts the sleeve 5 toward the input shaft 3 in such a manner, the input shaft 3 and the hub 4 separated from each other by the sleeve 5 are coupled to each other, thereby transmitting the rotary power of the reducer A transmitted through the input shaft 3 to the hub 4 to be combined with the rotary power of the constant velocity joint B. If the motor 81 of the actuator 8 is rotated in the opposite direction to interrupt transmission of the rotary power from the reducer A to the constant velocity joint B, the lead screw 82 returns to its original position. Here, the transfer completion position of the lead screw 82 is sensed by the position sensor 85. If the lead screw 82 returns to its original position, the shift fork 6 is pushed out by a restoring force of the first spring 12 installed between the upper housing 1 and the shift fork 6, thereby shifting the sleeve 5 commonly coupled to the hub 4 and the input shaft 3 to separate the hub 4 and the input shaft 3 from each other. Here, the transfer distance of the shift fork 6 is measured by the linear sensor 15 installed at the region positioned to correspond to the inclined surface 61 of the shift fork 6, so that a controller(not shown) can accurately control the transfer distance of the shift fork 6. If the shift fork 6 shifts the sleeve 5 commonly coupled to the hub 4 and the input shaft 3 in the above-described a manner, the input shaft 3 and the hub 4 are separated from each other by the sleeve 5. Accordingly, the rotary power of the reducer A transmitted through the input shaft 3 is not transmitted to the hub 4, so that the constant velocity joint B does not rotate.

1. A disconnector for a hybrid vehicle, comprising: an upper housing connected to a reducer; an input shaft installed inside the upper housing and transmitting rotary power of the reducer; bearings installed between the upper housing and the input shaft; a hub disposed under the input shaft; a sleeve having an inner circumferential surface spline-coupled to outer circumferential surfaces of the input shaft and the hub to then be shifted to transmit or interrupt the rotary power of the input shaft to the hub; a shift fork coupled to an outer circumferential surface of the sleeve and shifting the sleeve; a first spring installed between the upper housing and the shift fork; a lower case connected to a lower portion of the upper housing; a constant velocity joint connected to the hub through the inside of the lower case; a needle roller installed between the lower case and the constant velocity joint; an actuator coupled to the inside of the lower case and pushing out the shift fork; and a linear sensor sensing a transfer distance of the shift fork.

2. The disconnector of claim 1, wherein the actuator comprises: a motor generating rotary power; a lead screw converting a rotary motion into a linear motion; a cover mounted at a front end of the lead screw; a second spring installed between the lead screw and the cover; and a position sensor installed to be spaced apart from one side of the lead screw. 3. The disconnector of claim 2, further comprising a controller controlling a motor of the actuator of the motor according to the transfer distance of the shift fork measured by the linear sensor. 4. The disconnector of claim 2 or 3, wherein the motor is a reversible motor. 5. The disconnector of claim 1, wherein the shift fork has an inclined surface formed at a region positioned to correspond to the linear sensor.

2832680

Machine for applying threaded caps to containers

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to figure 1, numeral 10 indicates a machine for applying threaded caps to containers C, such as bottles or the like. The machine 10 comprises a central column 12 rotatable about a vertical axis A. The central column 12 carries a turret 14 equipped with a plurality of means for gripping the containers C. The means for gripping the containers C are known per se and can be of various types depending on the type of containers C. In general, the gripping means of the bottles must ensure a radial and axial retention of the bottle and must also have an anti-rotation element which prevents rotation of the bottle about its vertical axis. In the illustrated example, the turret 14 is equipped with an external guide 20 and fork elements 22 configured to receive respective necks of the containers C, and equipped with respective anti-rotation elements. It is intended that the system represented in the figures is only an example of a possible gripping means and that the invention is applicable to any other system for gripping the containers C. As illustrated in greater detail in Figures 2 and 3, the containers C are provided with an external thread 16 configured for receiving a threaded cap. At the base of the thread 16 of the containers C a radially projecting rim 18 is formed. With reference to Figure 1, the machine 10 comprises a plurality of screwing heads 24. Each screwing head 24 is located above a respective gripping means of the containers C. Each screwing head 24 comprises a spindle 26 carrying a cap-gripping member 28 at its lower end. Each screwing head 24 has a respective electric motor 30 which imparts a rotational movement to the spindle 26 about a respective longitudinal axis B. The cap-gripping member 28 is equipped with a rotational movement about the axis B and a translational movement in the direction of the axis B. The rotational movement and the translational movement are synchronized with each other, so that during operation the caps held by the gripping members 28 are equipped with a screwing movement. The linear movement in the direction of the axis B of the cap-gripping member 28 can be obtained by means of a mechanical or electronic cam. The structure and operation of the screwing heads 24 are known per se and do not require a more detailed description as they are beyond the scope of the present invention. The maximum torque applied to the cap-gripping member 28 is limited by the current supplied to the motor 30. With reference to Figures 2 and 3, the cap-gripping member 28 of each screwing head 24 has a frusto-conical seat 32 configured for receiving and retaining a respective cap 34. The cap 34 has a respective internal thread 36 which is designed to couple with the external thread 16 of the respective container C. The machine 10 according to the present invention comprises a vision system 38 which is used for detecting the angular position of the threads 16 of the containers C and the angular position of the threads 36 of the caps 34. More precisely, the vision system 38 is used to detect the angular position of the start points of the threads 16 and 36. The vision system 38 can comprise a first viewing device 40 ( Figure 2 ) for detecting the angular position of the start point of the external thread 16 of a container C, and a second vision device 42 ( Figure 3 ) for detecting the angular position of the start point of the internal thread 36 of a cap 34 held by the gripping member 28. Each vision device 40, 42 can be associated with a respective illuminator 44, 46 arranged to illuminate the respective area of vision. As illustrated in Figures 2 and 3, the vision devices 40, 42 and the respective illuminators 44 and 46 may be arranged outside of the turret 14. Alternatively, the vision devices 40, 42 can be axially aligned with the caps 34 and containers C. The vision system 38 is in a fixed position and detects images of the threads 16, 36 of the containers C and the caps 34 which, from time to time, pass in front of the vision system 38. The images recorded by the vision system 28 are sent to an electronic control unit schematically indicated with numeral 48 in Figure 1. The electronic control unit 48 has an algorithm that analyses the images detected by the vision devices 40, 42 and determines the angular position with respect to a reference system of the start point of the external thread 16 of the container C and the start point of the internal thread 36 of the corresponding cap 34. The electronic control unit 48 is configured to control the electric motors 30 of the screwing heads 24 in order to make an adjustment of the angular position of the caps 34 according to the information on the detected angular position of the threads 16, 36. The adjustment of the angular position of the caps 34 consists in a rotation about the axis B of the gripping members 28. This adjustment can be carried out before applying the caps 34 to the respective containers C. Alternatively, the adjustment of the angular position of the caps can be carried out after the caps 34 have been placed on the threads 16 of the respective containers C. In this case, an angular stroke equal to the sum of the screwing angle of the caps and the displacement angle between the thread of the cap and the thread of the container is applied to each cap 34 The purpose of the adjustment movement is to arrange the caps 34 with respect to the containers C so that the threads 36 of the caps 34 are in a preset angular position with respect to the threads 16 of the respective containers C. Starting from the position in which the caps 34 are juxtaposed to the containers C with the threads 36, 16 in a predetermined angular position, the motors 30 apply an angular rotation about the axis B, with a predetermined amplitude, to the respective gripping members 28. In this way, the screwing stroke of the caps 34 is determined on the basis of a geometric criterion rather than as a function of the screwing torque. This allows a greater precision of screwing to be obtained and the avoidance of defects in the closing of the containers due to an excessive or insufficient closing torque. In parallel to the control of the motors 30 on the basis of a predetermined screwing stroke, the electronic control unit 48 can also carry out a detection of the screwing torque applied to the caps 34 by any known method for torque detection. The electronic control unit 48 may be programmed to vary the screwing stroke with respect to the established preset value in case the measured closing torque is insufficient or excessive. The vision system 38 is able to recognize the threads 36 of caps with different sizes, different colours and different numbers of thread elements (from 1 to n elements). The vision system 38 is also able to recognize interruptions of the threads and the thread sectors with zero slope. The vision system 38 is also able to detect the thread of transparent glass or plastic containers.

1. Machine for applying threaded caps to containers, comprising: - gripping means (20, 22) configured for holding respective containers (C), - at least one screwing head (24) including a gripping member (28) configured for holding a respective cap (34), - at least one electric motor (30) associated with said screwing head (24) and configured to control a rotational movement of said gripping member (28) about a longitudinal axis (B), wherein said gripping member (28) is equipped with a translational movement along said longitudinal axis (B) synchronized with the rotational movement so that during operation, said gripping member (28) moves along a screwing path, characterized in that it comprises: - at least one vision system (38) configured for detecting images of the threads (16) of the containers (C) and the caps (34) held by said gripping member (28), and - an electronic control unit (48) configured to process the images of said threads (16, 36) and to determine the angular position of the start point of the thread (16) of the containers (C) and the angular position of the start point of the thread (36) of the caps (34) and for controlling an adjustment of the angular position of the caps (34) so as to carry out the screwing of the caps (34) onto the respective containers (C) with the respective threads (16, 36) arranged in a preset relative position.

2. Machine according to claim 1, characterized in that it comprises a first vision device (40) for detecting images of the threads (16) of the containers (C) and a second vision device (42) for detecting images of the threads (36) of the caps (34). 3. Machine according to claim 2, characterized in that said vision devices (40, 42) are associated with respective illuminators (44, 46) arranged to illuminate the respective vision zones of said vision devices (40, 42) 4. Machine according to claim 1, characterized in that: said electronic control unit (48) is configured to process the images detected by said vision device in order to determine the angular position of the start point of the thread (16) of a container (C) and the angular position of the start point of the thread (36) of a respective cap (34) with respect to a common reference system. 5. Machine according to claim 1, characterized in that said electronic control unit (48) is also configured to control said electric motor (30) of said screwing head (24) according to the information on the screwing torque.

2887501

Manufacturing a generator rotor

Based on the following detailed description of an invention, generate the patent claims. There should be 13 claims in total. The first, independent claim is given and the remaining 12 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The illustration in the drawings is in schematic form. It is noted that in different figures, similar or identical elements are provided with the same reference signs or with reference signs, which are different from the corresponding reference signs only within the first digit. Figure 1 illustrates a schematic perspective view of an arrangement 100 for manufacturing an outer rotor for an electrical generator according to an embodiment of the present invention in a state where already some permanent magnets 101 are releasably attached to the arrangement for manufacturing an outer rotor. The arrangement for manufacturing an outer rotor comprises a circular auxiliary structure 103 to which plural magnets are releasably attachable so that in Figure 1 not visible radially inner surfaces of the magnets 101 are aligned to comply with an intended inner diameter of the rotor corresponding to two times an intended inner radius r0, as is illustrated in Figure 1. The annular (in particular cylindrical) auxiliary structure 103 comprises rods and bars 105 which are connected with each other (for example using screws, adhesives or the like) in order to form a frame onto which a smooth or stepped outer surface 107 is formed which provides contact surface for the plural magnets 101 such as to allow releasably attachment of the plural magnets to the auxiliary structure radially outer surface 107. The auxiliary structure radially outer surface 107 has in the embodiment illustrated in Figure 1 a cylindrical shape without any recesses. In other embodiments, such as in embodiments illustrated in Figures 2, 3, 4 and 5, the auxiliary structure radially outer surface 107 may comprise recesses in which the plural magnets may be accompanied. The auxiliary structure 103 is supported by a support structure 109 comprising a base 111 and bars 113, 115. In particular, the support structure 109 holds the auxiliary structure 103 using an axis 117 corresponding to an axis of the outer rotor to be manufactured using the auxiliary structure 103. By the bars or rods 105, a fixture support structure is assembled supporting the auxiliary structure radially outer surface 107 to which the plural magnets 101 may releasably be attached. In Figure 1, only a portion of the magnets intended to be attached to the auxiliary structure 103 are illustrated. When manufacturing the outer rotor, all permanent magnets 101 intended to be comprised in the to be manufactured rotor may then be releasably attached to the auxiliary structure radially outer surface 107 of the auxiliary structure 103. In Figure 1, furthermore a radial direction 118 (also denoted as r) and a circumferential direction 119 (also denoted by the angle θ) as well as an axial direction 117 (corresponding to the rotor axis and perpendicular to the radial direction 117 and perpendicular to the circumferential direction 119) are indicated. Figure 2 schematically illustrates a cross-sectional (cut perpendicular to the axial direction) view (viewed in the axial direction 217) of a portion of an arrangement 200 for manufacturing an outer rotor of a generator according to an embodiment of the present invention. The arrangement 200 comprises an annular auxiliary structure 203 comprising an auxiliary structure radially outer surface 207. For the sake of clarity, the fixture structure including bars and rods is not illustrated in Figure 2 but supports the radially outer surface 207 of the auxiliary structure 203. As an example, two permanent magnets 201 are illustrated in Figure 2 being releasably attached to the auxiliary structure 203. In particular, for this purpose, the auxiliary structure radially outer surface 207 comprises recesses 221 at circumferential positions where permanent magnets are to be releasably attached. Thereby, the radius r1' of the auxiliary structure reaching from the central point 216 (through which the rotor axis or auxiliary structure axis runs) to the auxiliary structure radially outer surface 207 of the recesses 221 is smaller than the radius r2 of the auxiliary structure 203 extending from the central point 216 to the auxiliary structure radially outer surface 207 between adjacent magnets 201. In the illustration of Figure 2, bonding material has not been illustrated, as the illustration of Figure 2 is focused on the geometry of the auxiliary structure 203 and the manner of placement of the permanent magnets 201. However, when the auxiliary structure 203 is used in a manufacturing process to manufacture an outer rotor, bonding material will be applied at least in contact with radially outer surfaces 223 of the permanent magnets 201 and circumferentially between the permanent magnets 201. Furthermore, bonding material may also be applied on radially inner surfaces 225 of the magnets 201 and partially also on side surfaces 227 of the permanent magnets 201, as will be described in further detail with reference to Figures 2, 4 and 5. As can be taken from Figure 2, the radially outer surfaces 223 of the magnets 201 are at a greater radial position (i.e. r3) than the auxiliary structure radially outer surface (being positioned at the radius r2) circumferentially between the adjacent magnets 201. Furthermore, as can be taken from Figure 2, the radially inner surfaces 225 of the magnets 201 are at a smaller radial position (i.e. positioned at radius r1) than the auxiliary structure radially outer surface circumferentially between adjacent magnets (positioned at radius r2). Thereby, the magnets 201 may firmly but releasably hold within the recesses 221 during the manufacturing process, in order to position the magnets 201 for an intended radius of the rotor which may be the radius r1 (or a radius slightly smaller than r1 since additional bonding material may be applied onto the radially inner surfaces 225 of the magnets 201, such that an intended radius r0 or r1' of the rotor may result after completion of the manufacturing method). The circumferential direction 219 and the radial direction 218 is also illustrated in Figure 2. Figure 3 schematically illustrates a cross-sectional view (viewed along the axial direction 317) of an arrangement 300 for manufacturing an outer rotor according to an embodiment of the present invention. In a recess 321 of the auxiliary structure outer surface 307, a permanent magnet 301 is accompanied. The axial direction 317, the radial direction 318 and also the circumferential direction 319 are indicated in Figure 3. The arrangement 300 is illustrated in a stage during manufacturing an outer rotor. Thereby, the arrangement 300 for manufacturing the outer rotor may be prepared to hold the magnets 301 during the manufacturing process in a precise circular circumferential position with a precise inner diameter (for example the diameter r1 illustrated in Figure 2 ) as prescribed for the rotor. Further, the arrangement 300 is in the embodiment illustrated in Figure 3 suitable to hold vacuum bags and fiber material while building and casting the rotor. Before placing the permanent magnet into the recess 321, first an inner sheet 329 is placed within the recess 321 on the auxiliary structure radially outer surface 307 and also on this auxiliary structure radially outer surface 307 in circumferential regions where no permanent magnets 301 are to be placed. On the inner sheet 329 then one or more layers of fiber material 331 are placed to cover the inner sheet 329. The inner sheet 329 may serve as a portion of a vacuum bag on the outer surface 307 of the auxiliary structure or arrangement 300 for manufacturing a rotor. The fiber material or fiber layers 321 may establish one or more inner layers of fiber material or inner sheet 329 of said inner vacuum bag. Thereby, the fiber material 331 may be positioned for example by laying out fiber mats on the outer surface 307 (on top of the inner sheet 329) or by filament winding. After having placed the inner sheet 329 and the radially inner fiber material 331 on top of the inner sheet 329, the permanent magnets 301 may be placed on the radially inner fiber material 331 (i.e. fiber material which is placed at least on the radially inner surfaces 325 of the permanent magnets 301). Thereby, the permanent magnets 301 are placed on the radially inner fiber material 331 in their correct or intended positions relative to the arrangement 300 (in particular the auxiliary structure radially outer surface 307) and relative to their desired positions for the completed outer rotor. Thereby, the magnets 301 may be magnetized or demagnetized. After having placed the magnets 301 in their for the completed outer rotor intended positions, one or more layers of radially outer fiber material 333 is placed on the radially outer surfaces 323 of the magnets 301 and potentially partially also on portions of the side surfaces 327 of the magnets 301. Thereby, the radially outer fiber material 333 may for example be positioned by laying out fiber mats on the radially outer surface 323 or by filament winding. As a next step in the manufacturing process, an outer sheet 335 (serving as a portion of the vacuum bag) is placed on top of the radially outer fiber material 333 to build up the construction. In particular, the outer sheet 335 may then be joined with the inner sheet 329 to form a bag. Before placing the outer sheet 335, the fiber materials, i.e. the radially outer fiber material 333 and also the radially inner fiber material 331 may at least in part have been soaked or wetted or applied with resin. In other embodiments, the resin is applied after the bag comprising the inner sheet 329 and the outer sheet 335 has been (e.g. partially) closed. According to other embodiments, resin may be applied while the bag is still open. After having applied the resin 337 in particular illustrated in a region beside a side surface 327 of the magnet 301, the bag is then closed, in order to contain the magnets 301, the radially inner fiber material 331, the radially outer fiber material 333 and the resin 337 therein. Afterwards, the inside of the bag is evacuated, in order to perform a VARTM process for casting the rotor. Although not explicitly illustrated in Figure 3, the resin material 337 is also contained on or soaking the fiber materials 331 and 333. In a circumferential region where a permanent magnet 301 is not to be placed, extended radially inner fiber material 339 joins with extended radially outer fiber material 341 which forms an extension of the radially outer fiber material 333. Further, the extended radially inner fiber material 329 forms an extension of the radially inner fiber material 331. The manufacturing method and manufacturing arrangement may be new in that a similar wind turbine generator construction and method of manufacturing may not be known from the prior art. Embodiments of the present invention may be advantageous in that fixtures and thereby rotors may be constructed to a relatively large diameter, such as up to 10 m diameter without the limitation of rolling equipment conventionally required for manufacturing. Furthermore, embodiments of the present invention may be advantageous in that the manufacturing the rotor and establishing the magnets may be done in a single process step. This may be both time- and cost-effective. Furthermore, embodiments of the present invention may be advantageous in that the manufactured rotor may require little or may not require post-processing after casting. Furthermore, by a particular selection of the fiber material type to be used (uni-directional, bi-axial, carbon, glass fiber, Kevlar, etc.), the rotor may be designed to accommodate or to satisfy the various physical requirements set up for the rotor, such as load in the different directions, torsional loads, generation of noise, stiffness, weight, etc. Furthermore, embodiments of the present invention may be advantageous in that they may minimize bearing current related to the capacitive coupling between rotor and stator and even further with lightning currents flowing from hub to stator via capacitive coupling from rotor to stator. These advantages may be achieved by using an electrically nonconductive material for constructing the rotor. When completed the outer rotor 302 is manufactured. Figures 4 and 5 schematically illustrate cross-sectional views along the axial direction of a portion of other arrangements 400 and 500, respectively for manufacturing an outer rotor for a generator according to embodiments of the present invention. It should be noted that elements similar in structure and/or function to other elements illustrated in other figures are denoted with the same reference sign differing only in the first digit. The embodiment illustrated in Figure 4 differs from the embodiment of the arrangement 300 illustrated in Figure 3 in that the inner sheet 329 illustrated in Figure 3 is not present in the embodiment illustrated in Figure 4. A bag is, in the arrangement 400 illustrated in Figure 4, formed by the outer sheet 435 and the support structure radially outer surface 407 which forms a resin tight barrier and which may therefore form an inner bonding material retaining structure instead of the inner sheet 329. Apart from this difference, the embodiment corresponds to the embodiment illustrated in Figure 3. During a manufacturing process thereby, the step of placing an inner sheet onto the auxiliary structure radially outer surface 407 may be avoided. Instead, the radially inner fiber material 431 is directly placed onto the auxiliary structure radially outer surface 407 of the auxiliary structure 403 and is then soaked or provided with resin material 437. After placing the magnet 401 into the recess 425, after placing radially outer fiber material 433 on the outer surface 423 of the permanent magnet 401 and after placing the outer sheet 435 on top of the radially outer fiber material 433 and also applying resin 437, the bag formed by the auxiliary structure radially outer surface 407 and the outer sheet 435 may be evacuated and the resin may allowed to crosslink. The arrangement 500 for manufacturing an outer rotor illustrated in Figure 5 is similar to the arrangement 400 illustrated in Figure 4 except that the auxiliary structure 503 additionally comprises recesses or channels 543 between adjacent magnets and other channels 545 at circumferential positions where permanent magnets are to be placed, wherein the recesses or channels 543, 545 are formed by repressions on the auxiliary structure radially outer surface 507. The channels 543, 545 lead to a vacuum pump which may be adapted to evacuate the bag in order to remove residual air and to thus improve the joining and connection structure which eventually forms the outer rotor. The auxiliary structure radially outer surfaces 407, 507 illustrated in Figures 4 and 5 may be coated or pretreated (e.g. with a coating) or may comprise material (e.g. Teflon) in order to reduce sticking of the bonding material (in particular resin) to the auxiliary structure radially outer surfaces 407, 507. Permanent magnets may have previously be encapsulated in stainless steel.

1. Method for manufacturing an outer rotor (102) for an electrical generator; the method comprising: releasably attaching plural magnets (101) at an annular auxiliary structure (103) so that radially inner surfaces (225) of the magnets (201) are aligned to comply with an intended inner diameter (2*r0) of the rotor (102); applying a bonding material (331,333,337) at least in contact with radially outer surfaces (323) of the magnets (201,301) and circumferentially between magnets (201,301), in order to fix the aligned magnets (201,301) in place.

2. Method according to claim 1, wherein the bonding material (331,333,337) is applied such as to surround the radially outer surfaces (223,323) and the radially inner surfaces (225,325) of the magnets (201,301). 3. Method according to claim 1 or 2, wherein the bonding material (331,333,337) comprises composite material including a resin (337) and fiber material (331,333), in particular glass fiber and/or carbon fiber material. 4. Method according to one of claims 1 to 3, wherein a radial position (r3) of the radially outer surfaces (223) of the magnets (201) are greater than a radial position (r2) of an auxiliary structure radially outer surface circumferentially between adjacent magnets (201). 5. Method according to one of claims 1 to 4, wherein a radial position (r1) of the radially inner surfaces (225) of the magnets (201) are smaller than a radial position (r2) of the auxiliary structure radially outer surface (207) circumferentially between adjacent magnets. 6. Method according to one of claims 1 to 5,: wherein the fiber material (331,333) is applied between the auxiliary structure radially outer surface (307) and the radially inner surfaces (325) of the magnets (301) as radially inner fiber material (331),: wherein the fiber material is applied on the radially outer surfaces (323) of the magnets (301) as radially outer fiber material (333). 7. Method according to one of claim 6,: wherein the radially outer fiber material extends in a circumferential direction beyond the outer surface (323) of the magnets as extended radially outer fiber material (341),: wherein the radially inner fiber material extends in the circumferential direction beyond the radially inner surfaces (325) of the magnets as extended radially inner fiber material (339),: wherein the extended radially outer fiber material (341) and the extended radially inner fiber material (339) are stacked on top of each other circumferentially between adjacent magnets (301). 8. Method according to one of claims 6 or 7,: wherein applying the bonding material comprises: soaking the radially outer fiber material (333), the radially inner fiber material (331) and the extended radially outer fiber material (341) stacked with the extended radially inner fiber material (339) with resin (337), the method in particular further comprising: crosslinking the resin (337) for solidification. 9. Method according to one of claims 1 or 8,: wherein as an outer bonding material retaining structure an outer sheet (335) is arranged on the radially outer surfaces (323) of the magnets (301), in particular on the radially outer fiber material. 10. Method according to one of claim 9,: wherein as an inner bonding material retaining structure an inner sheet (329) is arranged between the radially inner fiber material (331) and the auxiliary structure radially outer surface (307). 11. Method according to one of claim 9,: wherein the auxiliary structure radially outer surface (307) is tight for the bonding material, to form an inner bonding material retaining structure,: wherein the auxiliary structure radially outer surface in particular comprises with adhering reducing material, in particular Teflon. 12. Method according to one of claim 1, wherein the auxiliary structure outer surface (507) comprises recesses or channels (543, 545) where vacuum can be applied. 13. Method according to one of claims 10 to 12, wherein applying a bonding material comprises: partially tightly joining the inner bonding material retaining structure (329) and outer bonding material retaining structure (335) to form a bag; filling an inside of the bag with resin (337); completely tightly joining the inner bonding material retaining structure and outer bonding material retaining structure to close the bag; and evacuating the inside of the bag, in particular using the recesses or channels, the method in particular further comprising: removing the auxiliary structure (103,203,303), in particular collapsing the auxiliary structure using a hydraulic mechanism.

2887499

Stator insulation for cold magnets

Based on the following detailed description of an invention, generate the patent claims. There should be 9 claims in total. The first, independent claim is given and the remaining 8 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The illustration in the drawings is in schematic form. It is noted that in different figures, similar or identical elements are provided with the same reference signs. Figure 1 shows a section of a generator 100 for a wind turbine, in particular a direct drive wind turbine. The generator 100 comprises a rotor assembly 102 which is rotatable around a rotary axis 106 and a stationary stator assembly 101, wherein the rotor assembly 102 and the stator assembly 101 are arranged with respect to each other such that a gap 108 exists between the rotor assembly 102 and the stator assembly 101, so that the rotor assembly 102 is rotatable with respect to the stator assembly 101. The stator assembly 101 has a surface 107 facing the gap 108 and the rotor assembly 102. The stator assembly 101 comprises a thermal insulation layer 104 applied onto the surface 107 for reducing an exchange of thermal energy between the rotor assembly 102 and the stator assembly 101. The stator assembly 101 comprises stator windings 105 and the rotor assembly 102 comprises magnets 103, in particular permanent magnet elements. The surface 107 of the stator assembly 101 is the surface which is in magnetic interaction with the respective part of the rotor assembly 102. Specifically, the magnetic interaction is generated between the surface 107 of the stator assembly and the respective part of the rotor assembly 102. According to the exemplary embodiment shown in Figure 1, the rotor assembly 102 is an external rotor assembly such that (e.g. at least the part of the rotor assembly 102 which provides the magnetic field linkage of) the rotor assembly 102 surrounds at least partially the surface 107 of the stator assembly 101. Hence, the surface 107 of the stator assembly 101 forms a radially outer surface of the stator assembly 101. The thermal insulation layer 104 is capable of impeding at least partially a heat transfer from the rotor assembly 102 to the stator assembly 101, and vice versa. In particular, the permanent magnets 103 installed at the rotor assembly 102 can be protected by the thermal insulation layer 104 from heat being generated by stator windings 105 of the stator assembly 101 and by stator iron core. Thereby, the heat transfer from the heat generating stator coils/windings 105 to the magnets 103 of the rotor assembly 102 can be based on thermal radiation and thermal convection. Hence, the thermal insulation layer 104 at the surface 107 of the stator assembly 101 has the advantage that during an operation the magnets 103 can be kept comparatively cool because the heat from the stator assembly 101 is insulated by the thermal insulation layer 104. By keeping the temperature of the permanent magnet material of the magnets 103 comparatively cool even in extreme operational ranges, the risk of an unwanted demagnetization of the magnet component can be effectively reduced. Furthermore, also the overall magnetic performance of the magnets 103 and, as a consequence, also the performance of the whole electromechanical generator 100 can be increased by keeping the temperature of the permanent magnet material comparatively cool. By the approach of the present invention, the thermal insulation layer 104 is arranged at the surface 107 of the stator assembly 101. The surface 107 of the stator assembly 101 is generally a homogeneous and smooth surface in comparison to a surface of the rotor assembly 102. The surface of the rotor assembly 102 comprises generally a plurality of recesses into which the permanent magnets 103 are arranged. Furthermore, the permanent magnets 103 protrude from the rotor surface into the gap 108 such that an uneven surface of the rotor assembly 102 is given. Hence, it is more complex and hence more expensive to apply the thermal insulation layer 104 to a surface of the rotor assembly 102. The thermal insulation layer 104 is e.g. glued to the surface 107 of the stator assembly 101. The stator assembly 101 comprises at least one cooling duct 109 which comprises an opening at the surface 107 of the stator assembly 101. The thermal insulation layer 104 comprises respective holes (see Fig, 2 ), in particular a punched holes, which are formed such that a cooling fluid (e.g. cooling air) can flow between the cooling duct 109 and the gap 108. The stator assembly 101 comprises a plurality of stator segments as shown in Figure 1 being arranged one after another along a circumferential direction with respect to the rotary axis 106. Figure 2 shows a more detailed view of a section of the thermal insulation layer 104. The thermal insulation layer 104 comprises at least one hole, in particular a punched hole, which is formed such that a cooling fluid (e.g. cooling air) can flow between the cooling duct 109 and the gap 108. Hence, the cooling air may flow from the gap 108 into the cooling duct 109 and hence out of the gap 108. Alternatively, the cooling air may flow out of the cooling duct 109 into the gap 108. The thermal insulation layer 104 may be adapted to the location of the opening of the cooling duct 109 at the surface 107, such that the thermal insulation layer 104 does not cover the cooling fluid opening of the cooling duct 109.

1. Generator (100) for a wind turbine, in particular a direct drive wind turbine, the generator (100) comprising: a rotor assembly (102) which is rotatable around a rotary axis (106), and: a stator assembly (101),: wherein the rotor assembly (102) and the stator assembly (101) are arranged with respect to each other such that a gap (108) exists between the rotor assembly (102) and the stator assembly (101), so that the rotor assembly (102) is rotatable with respect to the stator assembly (101),: wherein the stator assembly (101) has a surface (107) facing the gap (108) and the rotor assembly (102),: wherein the stator assembly (101) comprises a thermal insulation layer (104) applied onto the surface (107) for reducing an exchange of thermal energy between the rotor assembly (102) and the stator assembly (101).

2. Generator (100) according to claim 1,: wherein the insulation layer comprises an aerogel material. 3. Generator (100) according to claim 1 or 2,: wherein the thermal insulation layer (104) is glued to the surface (107) of the stator assembly (101). 4. Generator (100) according to one of the claims 1 to 3,: wherein the stator assembly (101) comprises at least one cooling duct (109) which comprises an opening at the surface (107),: wherein the thermal insulation layer (104) comprises at least one hole, in particular a punched hole, which is formed such that a cooling fluid is flowable between the cooling duct and the gap (108). 5. Generator (100) according to one of the claims 1 to 4,: wherein the stator assembly (101) comprises a plurality of stator segments being arranged one after another along a circumferential direction with respect to the rotary axis (106). 6. Generator (100) according to one of the claims 1 to 5,: wherein the rotor assembly (102) is an external rotor assembly such that the rotor assembly (102) surrounds the surface (107) of the stator assembly (101). 7. Generator (100) according to one of the claims 1 to 5,: wherein the rotor assembly (102) is an internal rotor assembly such that the surface (107) of the stator assembly (101) surrounds the rotor assembly (102). 8. Generator (100) according to one of the claims 1 to 7, wherein the stator assembly (101) comprises stator windings (105), and: wherein the rotor assembly (102) comprises magnets (103), in particular permanent magnets. 9. Wind turbine, in particular a direct drive wind turbine, the wind turbine comprising,: a generator (100) according to one of the claims 1 to 8.

2886998

Attachment means, gasket arrangement, heat exchanger plate and assembly

Based on the following detailed description of an invention, generate the patent claims. There should be 7 claims in total. The first, independent claim is given and the remaining 6 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to Figures 1, 2 and 3, an assembly 2 comprising a heat exchanger plate 4 and a gasket arrangement 6, is shown. Figure 2 shows an enlargement of a part of the assembly enclosed by the dashed rectangle A in Figure 1, and Figure 3 shows an enlargement of a part of the assembly enclosed by the dashed rectangle B in Figure 2. The heat exchanger plate 4, of which a first side 8 is visible in the figures, is an essentially rectangular sheet of stainless steel provided with a number of port holes 10, 12, 14 and 16, and pressed with specific patterns within different areas of the heat exchanger plate (illustrated partly in Figure 2 ). The heat exchanger plate 4 comprises a gasket groove 18 extending along an outer plate periphery 20 to enclose the port holes 10, 12, 14 and 16, and completely along two inner plate peripheries 22 and 24 defining two of the port holes 10 and 14, respectively, to separately enclose these. Further, the gaskets groove 18 extends twice "diagonally" across the heat exchanger plate so as to further enclose the port holes 10 and 14. The heat exchanger plate 4 further comprises a first and a second length edge portion 26 and 28, respectively, extending between the gasket groove 18 and a first and a second length edge 30 and 32, respectively, of the heat exchanger plate 4. The edge portions 26 and 28 are corrugated so as to comprise alternately arranged ridges 34 and valleys 36 ( Figures 2 and 3 ). The ridges 34 are closed towards the gasket groove 18 and arranged to provide gasket support. With reference to the orthogonal system of coordinates in Figure 1, the ridges 34 and valleys 36 illustrated in Figures 2 and 3 has a length extension in an x-direction, a width extension in an y-direction and a height/depth extension in a z-direction, while the part of the gasket groove 18 illustrated in Figures 2 and 3 has a length extension in the y-direction, a width extension in the x-direction and a thickness extension in the z-direction. As is clear from the figures, the ridges 34, just like the valleys 36, have a width varying along a length of the ridges and valleys, respectively, i.e. along the x-direction. More particularly, each of the ridges 34 has a first portion 38 with a first varying width wr1 and a second portion 40 with a second varying width wr2. The first portion is closer to the gasket groove 18 than the second portion and the first portion is wider than the second portion, i.e. wr1 > wr2. Each of the ridges 34 comprises a third portion 42, here composed of the first and second portions 38 and 40, which is tapered such that the width of the third portion is gradually increasing towards the gasket groove 18. Further, each of the valleys 36 has a first portion 44 with a first varying width wv1 and a second portion 46 with a second varying width wv2. The first portion is closer to the gasket groove 18 than the second portion and the second portion is wider than the first portion, i.e. wv2 > wv1. Each of the valleys 36 comprises a third portion 48, here composed of the first and second portions 44 and 46, which is tapered such that the width of the third portion is gradually decreasing towards the gasket groove 18. The gasket arrangement 6 comprises a rubber gasket 50 and a number of essentially similar rubber attachment means 52 integrally formed with the gasket, one of these attachment means being illustrated in more detail in Figures 4 and 5a - 5d. The attachment means 52 comprises a first connection member 54, a second connection member 56 and a bridge 58. The first and second connection members are essentially similar and they have a length just exceeding a width (extension in x-direction with reference to Figure 1 ) of the first and second length edge portions 26 and 28. A first part, more particularly a first end 60, of the first connection member 54 is connected to the gasket 50. Similarly, a first part, more particularly a first end 62, of the second connection member 56 is connected to the gasket 50. A second part, more particularly a second end 64, of the first connection member 54 is connected to the bridge 58. Similarly, a second part, more particularly a second end 66, of the second connection member 56 is connected to the bridge 58. The first and second connection members are separated from, and essentially parallel to, each other, and they project essentially perpendicularly from the gasket. As seen in Figure 5a, the bridge has a length extension in the y-direction, a width extension in the x-direction and a thickness extension in the z-direction, while the first and second connection members have a length extension in the x-direction, a width extension in the y-direction and a thickness extension in the z-direction. The bridge 58 extends essentially parallel to the gasket 50. It has a center portion 68 that is wider than the rest of the bridge and an upper surface 70 of the center portion is provided with a friction increasing structure in the form of an elongate projection 72 extending essentially parallel to the gasket, i.e. along the y-direction. This is to facilitate application of the gasket arrangement in connection with which the attachment means is grabbed by the bridge 58. The wider center portion also increases the rigidity of the bridge and thus the complete attachment means. The attachment means 52 further comprises a finger 74 arranged between the first and second connection members 54 and 56. A connection part, more particularly a first end 76, of the finger 74 is connected to the bridge 58 while a second end 78 of the finger is free. The finger projects essentially perpendicularly from the bridge towards the gasket 50. Thus, the finger 74 has a length extension in the x-direction, a width extension in the y-direction and a thickness extension in the z-direction. As is clear from the figures, the finger 74 has a width varying along a length of the finger, i.e. along the x-direction. More particularly, a first portion 80 of the finger has a first varying width wf1 while a second portion 82 of the finger has a second varying width wf2. The first portion is closer to the bridge 58 than the second portion and the second portion is wider than the first portion, i.e. wf2 > wf1. Further, a third portion 84 of the finger 74, comprising the first and second portions 80 and 82 and a portion extending there between, is tapered such that the width of the third portion is gradually decreasing along the length of the finger in a direction towards the bridge 58, i.e. a -x-direction, which is opposite the x-direction. A gasketed plate heat exchanger constructed in accordance with the present invention comprises a compressed stack of heat exchanger plates 4, each two heat exchanger plates being separated by a gasket arrangement 6. In connection with assembly of the plate heat exchanger, each heat exchanger plate 4 is provided with a gasket arrangement, wherein the gasket 50 is arranged in the gasket groove 18 on the first side 8 of the heat exchanger plate and the attachment means 52 are arranged in engagement with the first and the second length edge portion 26 and 28, respectively, of the heat exchanger plate 4. More particularly, each of the attachment means 52 is so fastened to the heat exchanger plate 4 that the first and the second connection members 54 and 56, respectively, are arranged on the first side 8 of the heat exchanger plate 4, in a respective one of two neighboring valleys 36 of the edge portions 26 and 28. Further, the finger 74 is arranged on a second side (not shown), which is opposite to the first side 8, of the heat exchanger plate 4, in the ridge 34 arranged between the above mentioned neighboring valleys. Arranged like that, the first and second connection members and the finger together squeeze the heat exchanger plate 4 to attach the gasket 50 in the groove 18 thereof. This is illustrated in Figure 2. As is clear from the figures the ridge 34 and the finger 74 are so dimensioned that the finger occupies essentially the entire ridge resulting in a firm engagement between the heat exchanger plate 4 and the attachment means 52. Further, because of the widths of the ridge and the finger varying in the above described way, the attachment means is "locked" to the heat exchanger plate. More particularly, the attachment means is prevented from moving in relation to the heat exchanger plate in a direction parallel to an extension plane of the heat exchanger plate, i.e. the finger is prevented from sliding out of engagement with the ridge which could happen with some prior art attachment means. As is illustrated in Figure 5b, the finger 74 is tapered so as to be thicker at its first end 76 than at its free second end 78. Thereby, when the attachment means is applied onto the heat exchanger plate, the finger may follow the heat exchanger plate more closely and thus engage stronger therewith. Further, the free second end 78 of the finger 74 is slightly chamfered at a surface 86 arranged to face away from the heat exchanger plate 4 when the gasket arrangement 6 is applied thereon. A purpose of the chamfering is to give the attachment means a less sprawling impression when fixed to the heat exchanger plate 4 since the finger 74 may not engage, depending on its stiffness and exact shape, with the second side of the heat exchanger plate along its entire extension. Another purpose of this chamfering is to make the finger less prone to engagement with an underlying external structure in connection with application of the attachment means onto the heat exchanger plate. Another feature of the attachment means 52 is that the bridge 58 is thicker, and thus more rigid, than the finger 74 which facilitates application of the attachment means onto the heat exchanger plate. As is most clearly illustrated in Figure 5c, the gasket 50 is, at its connection to the first and second connection members 54 and 56, thinner than the first and second connection members are at their respective second ends 64 and 66, respectively. In order not to extend beyond the gasket, with the risk of affecting its sealing capacity when pressed against another heat exchanger plate, the first and second connection members are tapered such as to be less thick at their respective first ends 60 and 62 where they join the gasket 50. Figure 6 illustrate an alternative gasket arrangement 88 adapted for engagement with the heat exchanger plate 4. The gasket arrangement 88 is in many ways similar to the gasket arrangement 6, and the same reference numerals have been used for parts of the two gasket arrangements that are similar. These similar parts will not be described again. The gasket arrangement 88 comprises a number of essentially similar rubber attachment means 90 integrally formed with the gasket, one of these attachment means being illustrated in more detail in Figures 6. The attachment means 90 comprises a first connection member 92, a second connection member 94 and a bridge 96. As is clear from Figure 6, the connection members 92 and 94 each have a width varying along a length of the connection members, i.e. along the x-direction. More particularly, a respective first portion 98 of the connection members has a first varying width wc1 while a respective second portion 100 of the connection members has a second varying width wc2. The first portion is closer to the bridge 96 than the second portion and the first portion is wider than the second portion, i.e. wc1 > wc2. Further, a respective third portion 102 of the connection members 92 and 94, comprising the first and second portions 98 and 100 and a portion extending there between, is tapered such that the width of the third portion is gradually decreasing along the length of the connection members in a direction from the bridge 96, the x-direction. As a result thereof, as is illustrated in Figure 6, also the bridge 96, as well as the complete attachment means 90, is tapered, i.e. has a varying width, a width extension being parallel to a length direction of the bridge, i.e. the y-direction. The above described embodiments of the present invention should only be seen as examples. A person skilled in the art realizes that the embodiments discussed can be varied in a number of ways without deviating from the inventive conception. As an example, the above described gasket arrangements comprise a plurality of attachment means distributed along an outside of the gasket so as to engage with the first and second length edges of the heat exchanger plate. Naturally, one or more of the attachment means could also/instead be arranged to engage with a first and/or a second transverse edge and/or a port hole edge of the heat exchanger plate. The present invention can be used in connection with alternative gasket designs, for example a gasket arranged to enclose the port holes once only, whereby the gasket could be essentially rectangular, or a ring gasket arranged to enclose one of the port holes only. The attachment means need not comprise one finger only like above but could comprise any number of fingers, some or all having varying widths. In case of the attachment means comprising a plurality of fingers, the fingers could be arranged to engage alternately with the first and second sides of the heat exchanger plate. Accordingly, one or more fingers, with or without a varying width, could be arranged for engagement with a respective one of the valleys of the heat exchanger plate. Further, a finger arranged to engage with a valley, i.e. the first side, of the heat exchanger plate need not have a free second end but could instead have a second end arranged to engage with the gasket. The gasket and the attachment means must not be integrally formed but could be two separate but connectable parts. Further, the gasket and attachment means need not be made of rubber but can be made of any suitable material. Further, the gasket and attachment means need not be of the same material. The first and second connection members of the above attachment means extend from the bridge to the gasket but they could instead extend beyond the bridge and/or the gasket. Similarly, the finger could extend beyond the bridge and/or the gasket. The assemblies according to the above embodiments are such that the gasket groove and the valleys of the length edge portions essentially are in the same plane. Naturally, alternative embodiments are possible where the gasket groove and the valleys are in different planes. The finger and connection members as well as the bridge of the attachment means could be formed in an alternative way than above described. For example, the finger and/or the connection members need not extend parallel to each other and/or perpendicularly to the bridge. Also, the bridge need not extend essentially parallel to the gasket. Further, the finger and/or the connections elements need not be tapered in the z-direction and/or chamfered. Also, the finger may have a constant width along a part/parts of its length. The above described attachment means 90 comprises connection members 92 and 94 having a varying width in that an outside of the connection members extend non-perpendicularly to the gasket 50 which gives also the attachment means 90 a varying width. Alternatively, an inside of the connection members could instead extend non-perpendicularly to the gasket 50 whereby the attachment means 90 could have an essentially constant width. Further, both an inside and an outside of the connection members could extend non-perpendicularly to the gasket 50. The ridges and valleys of the heat exchanger plate above are all similar but this is not a requirement. Alternatively, only the ridges and/or the valleys arranged for engagement with an attachment means could have a varying width, or only the ridges and/or the valleys arranged for engagement with the fingers of the attachment means could have a varying width, while the rest of the ridges and/or the valleys could have an essentially constant width. The friction increasing structure of the bridge need not be formed as an elongate projection but can be formed in other ways, for example as a ribbed or rough surface portion. Further, the surface provided with this friction increasing structure need not be the upper surface of the bridge but could be another surface thereof. The present invention could be used in connection with other types of heat exchanger plates than the above described one. Such other plate types could be made of other materials than stainless steel, be provided with a gasket groove of an alternative design or no gasket groove at all, be provided with another pattern, another port hole design or another number of port holes than four. Finally, the present invention could be used in connection with other types of plate heat exchangers than purely gasketed ones, e.g. plate heat exchangers comprising permanently joined heat exchanger plates. It should be stressed that the attributes first, second, third, etc. is used herein just to distinguish between species of the same kind and not to express any kind of mutual order between the species. It should be stressed that a description of details not relevant to the present invention has been omitted and that the figures are just schematic and not drawn according to scale. It should also be said that some of the figures have been more simplified than others. Therefore, some components may be illustrated in one figure but left out on another figure. The present invention could be combined with the invention described in applicant's copending European patent application titled "HEAT TRANSFER PLATE AND PLATE HEAT EXCHANGER" filed on the same day as the present European patent application, and the invention described in applicant's copending patent application [PATCIT EP13153167A].

1. An attachment means (52, 90) arranged to engage with an edge portion (26, 28) of a heat exchanger plate (4) for fastening a gasket (50) to a first side (8) of the heat exchanger plate, comprising a first connection member (54, 92), a second connection member (56, 94) and a bridge (58, 96), a first part (60) of the first connection member being arranged to engage with the gasket, a second part (64) of the first connection member engaging with the bridge, a first part (62) of the second connection member being arranged to engage with the gasket and a second part (66) of the second connection member engaging with the bridge, further comprising a finger (74) arranged between the first and second connection members, a connection part (76) of the finger engaging which the bridge, the finger being arranged to extend from the bridge towards the gasket, characterized in that the finger has a width that is varying along a length of the finger, a width extension of the finger being parallel to a length extension of the bridge.

2. An attachment means (52, 90) according to claim 1, wherein the finger (74) has a first portion (80) with a first width (wf1) and a second portion (82) with a second width (wf2), the first portion being arranged closer to the bridge (58, 96) than the second portion, and the first width being smaller than the second width. 3. An attachment means (52, 90) according to any of the preceding claims, wherein a third portion (84) of the finger (74) is tapered along the length of the finger in a direction towards the bridge (58, 96). 4. An attachment means (90) according to any of the preceding claims, wherein at least one of the first and second connection members (92, 94) has a width that is varying along a length of said at least one of the first and second connection members, a width extension of said at least one of the first and second connection members being parallel to the length extension of the bridge (96). 5. An attachment means (90) according to any of the preceding claims having a varying width, a width extension of the attachment means being parallel to the length extension of the bridge (96). 6. An attachment means (52, 90) according to any of the preceding claims, wherein each of the first and second connection members (54, 92, 56, 94) is arranged to engage with the first side (8) of the heat exchanger plate (4) while the finger (74) is arranged to engage with a second opposite side of the heat exchanger plate. 7. A gasket arrangement (6, 88) comprising a gasket (50) and an attachment means (52, 90) according to any of claims 1-6.

2886998

Attachment means, gasket arrangement, heat exchanger plate and assembly

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to Figures 1, 2 and 3, an assembly 2 comprising a heat exchanger plate 4 and a gasket arrangement 6, is shown. Figure 2 shows an enlargement of a part of the assembly enclosed by the dashed rectangle A in Figure 1, and Figure 3 shows an enlargement of a part of the assembly enclosed by the dashed rectangle B in Figure 2. The heat exchanger plate 4, of which a first side 8 is visible in the figures, is an essentially rectangular sheet of stainless steel provided with a number of port holes 10, 12, 14 and 16, and pressed with specific patterns within different areas of the heat exchanger plate (illustrated partly in Figure 2 ). The heat exchanger plate 4 comprises a gasket groove 18 extending along an outer plate periphery 20 to enclose the port holes 10, 12, 14 and 16, and completely along two inner plate peripheries 22 and 24 defining two of the port holes 10 and 14, respectively, to separately enclose these. Further, the gaskets groove 18 extends twice "diagonally" across the heat exchanger plate so as to further enclose the port holes 10 and 14. The heat exchanger plate 4 further comprises a first and a second length edge portion 26 and 28, respectively, extending between the gasket groove 18 and a first and a second length edge 30 and 32, respectively, of the heat exchanger plate 4. The edge portions 26 and 28 are corrugated so as to comprise alternately arranged ridges 34 and valleys 36 ( Figures 2 and 3 ). The ridges 34 are closed towards the gasket groove 18 and arranged to provide gasket support. With reference to the orthogonal system of coordinates in Figure 1, the ridges 34 and valleys 36 illustrated in Figures 2 and 3 has a length extension in an x-direction, a width extension in an y-direction and a height/depth extension in a z-direction, while the part of the gasket groove 18 illustrated in Figures 2 and 3 has a length extension in the y-direction, a width extension in the x-direction and a thickness extension in the z-direction. As is clear from the figures, the ridges 34, just like the valleys 36, have a width varying along a length of the ridges and valleys, respectively, i.e. along the x-direction. More particularly, each of the ridges 34 has a first portion 38 with a first varying width wr1 and a second portion 40 with a second varying width wr2. The first portion is closer to the gasket groove 18 than the second portion and the first portion is wider than the second portion, i.e. wr1 > wr2. Each of the ridges 34 comprises a third portion 42, here composed of the first and second portions 38 and 40, which is tapered such that the width of the third portion is gradually increasing towards the gasket groove 18. Further, each of the valleys 36 has a first portion 44 with a first varying width wv1 and a second portion 46 with a second varying width wv2. The first portion is closer to the gasket groove 18 than the second portion and the second portion is wider than the first portion, i.e. wv2 > wv1. Each of the valleys 36 comprises a third portion 48, here composed of the first and second portions 44 and 46, which is tapered such that the width of the third portion is gradually decreasing towards the gasket groove 18. The gasket arrangement 6 comprises a rubber gasket 50 and a number of essentially similar rubber attachment means 52 integrally formed with the gasket, one of these attachment means being illustrated in more detail in Figures 4 and 5a - 5d. The attachment means 52 comprises a first connection member 54, a second connection member 56 and a bridge 58. The first and second connection members are essentially similar and they have a length just exceeding a width (extension in x-direction with reference to Figure 1 ) of the first and second length edge portions 26 and 28. A first part, more particularly a first end 60, of the first connection member 54 is connected to the gasket 50. Similarly, a first part, more particularly a first end 62, of the second connection member 56 is connected to the gasket 50. A second part, more particularly a second end 64, of the first connection member 54 is connected to the bridge 58. Similarly, a second part, more particularly a second end 66, of the second connection member 56 is connected to the bridge 58. The first and second connection members are separated from, and essentially parallel to, each other, and they project essentially perpendicularly from the gasket. As seen in Figure 5a, the bridge has a length extension in the y-direction, a width extension in the x-direction and a thickness extension in the z-direction, while the first and second connection members have a length extension in the x-direction, a width extension in the y-direction and a thickness extension in the z-direction. The bridge 58 extends essentially parallel to the gasket 50. It has a center portion 68 that is wider than the rest of the bridge and an upper surface 70 of the center portion is provided with a friction increasing structure in the form of an elongate projection 72 extending essentially parallel to the gasket, i.e. along the y-direction. This is to facilitate application of the gasket arrangement in connection with which the attachment means is grabbed by the bridge 58. The wider center portion also increases the rigidity of the bridge and thus the complete attachment means. The attachment means 52 further comprises a finger 74 arranged between the first and second connection members 54 and 56. A connection part, more particularly a first end 76, of the finger 74 is connected to the bridge 58 while a second end 78 of the finger is free. The finger projects essentially perpendicularly from the bridge towards the gasket 50. Thus, the finger 74 has a length extension in the x-direction, a width extension in the y-direction and a thickness extension in the z-direction. As is clear from the figures, the finger 74 has a width varying along a length of the finger, i.e. along the x-direction. More particularly, a first portion 80 of the finger has a first varying width wf1 while a second portion 82 of the finger has a second varying width wf2. The first portion is closer to the bridge 58 than the second portion and the second portion is wider than the first portion, i.e. wf2 > wf1. Further, a third portion 84 of the finger 74, comprising the first and second portions 80 and 82 and a portion extending there between, is tapered such that the width of the third portion is gradually decreasing along the length of the finger in a direction towards the bridge 58, i.e. a -x-direction, which is opposite the x-direction. A gasketed plate heat exchanger constructed in accordance with the present invention comprises a compressed stack of heat exchanger plates 4, each two heat exchanger plates being separated by a gasket arrangement 6. In connection with assembly of the plate heat exchanger, each heat exchanger plate 4 is provided with a gasket arrangement, wherein the gasket 50 is arranged in the gasket groove 18 on the first side 8 of the heat exchanger plate and the attachment means 52 are arranged in engagement with the first and the second length edge portion 26 and 28, respectively, of the heat exchanger plate 4. More particularly, each of the attachment means 52 is so fastened to the heat exchanger plate 4 that the first and the second connection members 54 and 56, respectively, are arranged on the first side 8 of the heat exchanger plate 4, in a respective one of two neighboring valleys 36 of the edge portions 26 and 28. Further, the finger 74 is arranged on a second side (not shown), which is opposite to the first side 8, of the heat exchanger plate 4, in the ridge 34 arranged between the above mentioned neighboring valleys. Arranged like that, the first and second connection members and the finger together squeeze the heat exchanger plate 4 to attach the gasket 50 in the groove 18 thereof. This is illustrated in Figure 2. As is clear from the figures the ridge 34 and the finger 74 are so dimensioned that the finger occupies essentially the entire ridge resulting in a firm engagement between the heat exchanger plate 4 and the attachment means 52. Further, because of the widths of the ridge and the finger varying in the above described way, the attachment means is "locked" to the heat exchanger plate. More particularly, the attachment means is prevented from moving in relation to the heat exchanger plate in a direction parallel to an extension plane of the heat exchanger plate, i.e. the finger is prevented from sliding out of engagement with the ridge which could happen with some prior art attachment means. As is illustrated in Figure 5b, the finger 74 is tapered so as to be thicker at its first end 76 than at its free second end 78. Thereby, when the attachment means is applied onto the heat exchanger plate, the finger may follow the heat exchanger plate more closely and thus engage stronger therewith. Further, the free second end 78 of the finger 74 is slightly chamfered at a surface 86 arranged to face away from the heat exchanger plate 4 when the gasket arrangement 6 is applied thereon. A purpose of the chamfering is to give the attachment means a less sprawling impression when fixed to the heat exchanger plate 4 since the finger 74 may not engage, depending on its stiffness and exact shape, with the second side of the heat exchanger plate along its entire extension. Another purpose of this chamfering is to make the finger less prone to engagement with an underlying external structure in connection with application of the attachment means onto the heat exchanger plate. Another feature of the attachment means 52 is that the bridge 58 is thicker, and thus more rigid, than the finger 74 which facilitates application of the attachment means onto the heat exchanger plate. As is most clearly illustrated in Figure 5c, the gasket 50 is, at its connection to the first and second connection members 54 and 56, thinner than the first and second connection members are at their respective second ends 64 and 66, respectively. In order not to extend beyond the gasket, with the risk of affecting its sealing capacity when pressed against another heat exchanger plate, the first and second connection members are tapered such as to be less thick at their respective first ends 60 and 62 where they join the gasket 50. Figure 6 illustrate an alternative gasket arrangement 88 adapted for engagement with the heat exchanger plate 4. The gasket arrangement 88 is in many ways similar to the gasket arrangement 6, and the same reference numerals have been used for parts of the two gasket arrangements that are similar. These similar parts will not be described again. The gasket arrangement 88 comprises a number of essentially similar rubber attachment means 90 integrally formed with the gasket, one of these attachment means being illustrated in more detail in Figures 6. The attachment means 90 comprises a first connection member 92, a second connection member 94 and a bridge 96. As is clear from Figure 6, the connection members 92 and 94 each have a width varying along a length of the connection members, i.e. along the x-direction. More particularly, a respective first portion 98 of the connection members has a first varying width wc1 while a respective second portion 100 of the connection members has a second varying width wc2. The first portion is closer to the bridge 96 than the second portion and the first portion is wider than the second portion, i.e. wc1 > wc2. Further, a respective third portion 102 of the connection members 92 and 94, comprising the first and second portions 98 and 100 and a portion extending there between, is tapered such that the width of the third portion is gradually decreasing along the length of the connection members in a direction from the bridge 96, the x-direction. As a result thereof, as is illustrated in Figure 6, also the bridge 96, as well as the complete attachment means 90, is tapered, i.e. has a varying width, a width extension being parallel to a length direction of the bridge, i.e. the y-direction. The above described embodiments of the present invention should only be seen as examples. A person skilled in the art realizes that the embodiments discussed can be varied in a number of ways without deviating from the inventive conception. As an example, the above described gasket arrangements comprise a plurality of attachment means distributed along an outside of the gasket so as to engage with the first and second length edges of the heat exchanger plate. Naturally, one or more of the attachment means could also/instead be arranged to engage with a first and/or a second transverse edge and/or a port hole edge of the heat exchanger plate. The present invention can be used in connection with alternative gasket designs, for example a gasket arranged to enclose the port holes once only, whereby the gasket could be essentially rectangular, or a ring gasket arranged to enclose one of the port holes only. The attachment means need not comprise one finger only like above but could comprise any number of fingers, some or all having varying widths. In case of the attachment means comprising a plurality of fingers, the fingers could be arranged to engage alternately with the first and second sides of the heat exchanger plate. Accordingly, one or more fingers, with or without a varying width, could be arranged for engagement with a respective one of the valleys of the heat exchanger plate. Further, a finger arranged to engage with a valley, i.e. the first side, of the heat exchanger plate need not have a free second end but could instead have a second end arranged to engage with the gasket. The gasket and the attachment means must not be integrally formed but could be two separate but connectable parts. Further, the gasket and attachment means need not be made of rubber but can be made of any suitable material. Further, the gasket and attachment means need not be of the same material. The first and second connection members of the above attachment means extend from the bridge to the gasket but they could instead extend beyond the bridge and/or the gasket. Similarly, the finger could extend beyond the bridge and/or the gasket. The assemblies according to the above embodiments are such that the gasket groove and the valleys of the length edge portions essentially are in the same plane. Naturally, alternative embodiments are possible where the gasket groove and the valleys are in different planes. The finger and connection members as well as the bridge of the attachment means could be formed in an alternative way than above described. For example, the finger and/or the connection members need not extend parallel to each other and/or perpendicularly to the bridge. Also, the bridge need not extend essentially parallel to the gasket. Further, the finger and/or the connections elements need not be tapered in the z-direction and/or chamfered. Also, the finger may have a constant width along a part/parts of its length. The above described attachment means 90 comprises connection members 92 and 94 having a varying width in that an outside of the connection members extend non-perpendicularly to the gasket 50 which gives also the attachment means 90 a varying width. Alternatively, an inside of the connection members could instead extend non-perpendicularly to the gasket 50 whereby the attachment means 90 could have an essentially constant width. Further, both an inside and an outside of the connection members could extend non-perpendicularly to the gasket 50. The ridges and valleys of the heat exchanger plate above are all similar but this is not a requirement. Alternatively, only the ridges and/or the valleys arranged for engagement with an attachment means could have a varying width, or only the ridges and/or the valleys arranged for engagement with the fingers of the attachment means could have a varying width, while the rest of the ridges and/or the valleys could have an essentially constant width. The friction increasing structure of the bridge need not be formed as an elongate projection but can be formed in other ways, for example as a ribbed or rough surface portion. Further, the surface provided with this friction increasing structure need not be the upper surface of the bridge but could be another surface thereof. The present invention could be used in connection with other types of heat exchanger plates than the above described one. Such other plate types could be made of other materials than stainless steel, be provided with a gasket groove of an alternative design or no gasket groove at all, be provided with another pattern, another port hole design or another number of port holes than four. Finally, the present invention could be used in connection with other types of plate heat exchangers than purely gasketed ones, e.g. plate heat exchangers comprising permanently joined heat exchanger plates. It should be stressed that the attributes first, second, third, etc. is used herein just to distinguish between species of the same kind and not to express any kind of mutual order between the species. It should be stressed that a description of details not relevant to the present invention has been omitted and that the figures are just schematic and not drawn according to scale. It should also be said that some of the figures have been more simplified than others. Therefore, some components may be illustrated in one figure but left out on another figure. The present invention could be combined with the invention described in applicant's copending European patent application titled "HEAT TRANSFER PLATE AND PLATE HEAT EXCHANGER" filed on the same day as the present European patent application, and the invention described in applicant's copending patent application [PATCIT EP13153167A].

8. A heat exchanger plate (4) comprising, on a first side (8) thereof, a gasket groove (18) extending along an edge (30, 32) of the heat exchanger plate (4), an edge portion (26, 28) of the heat exchanger plate extending between the edge and the gasket groove and being corrugated so as to comprise alternately arranged ridges (34) and valleys (36) as seen from the first side, the edge portion being arranged to engage with an attachment means (52, 90) for fastening a gasket (50) in the gasket groove, a width extension of the ridges and valleys being parallel to a length extension of the gasket groove, characterized in that at least one of the ridges and valleys has a width that is varying along a length of said at least one of the ridges and valleys, a first portion (38) of said at least one of the ridges and valleys having a first width (wr1) and a second portion (40) of said at least one of the ridges and valleys having a second width (wr2), the first portion being arranged closer to the gasket groove than the second portion, and the first width being larger than the second width.

9. A heat exchanger plate (4) according to claim 8, wherein said at least one of the ridges and valleys (34, 36) is closed towards the gasket groove (18). 10. A heat exchanger plate (4) according to any of claims 8-9, wherein a third portion (42) of said at least one of the ridges and valleys (34, 36) is tapered along the length of said at least one of the ridges and valleys in a direction from the gasket groove (18). 11. A heat exchanger plate (4) according to any of claims 8-10, wherein said at least one of the ridges and valleys is one of the ridges (34) and wherein at least one of the valleys (36) has a width that is varying along a length of said at least one of the valleys. 12. An assembly (2) comprising a heat exchanger plate (4) according to any of claims 8-11 and a gasket arrangement according to claim 7.

2886452

Flow body, method for manufacturing a flow body and aircraft having such a flow body

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a flow body according to the invention in form of a vertical tailplane 2 having an air sucking nose component 4. The vertical tailplane 2 provides a directional stability around the vertical axis, i.e. the z-axis in an aircraft-fixed coordinate system, reduces aerodynamic side slip and allows to control the aircraft's yaw movement by a rudder 6 movably arranged at a trailing edge 8 of the vertical tailplane 2. The vertical tailplane 2 is fully exposed to an airflow caused by the motion of the aircraft, such that the drag of the vertical tailplane 2 should be decreased to a minimum. As the overall dimensions of the vertical tailplane 2 mainly depend on the stabilizing function and the required structural stability, the drag cannot be reduced through decreasing the size of the vertical tailplane 2. As explained further above, a significant drag reduction may be achieved through selectively sucking air from a boundary flow layer of a nose region of the vertical tailplane 2, such that the flow is as laminar as possible. Therefore, the air sucking nose component 4 is at least partially gas permeable through a microperforation. The air sucking nose component 4 is couplable with an air sucking line 10, a fan 12 and/or any other device that is able to provide a clearly lower pressure than the dynamic pressure in the boundary layer of the air sucking nose component 4. This may be also be accomplished through passive means, such as through exploiting a gas flow along an opening which experiences a suction force due to the Bernoulli effect. As shown in further figures 2a and 2b, a flow body according to the invention may be created having a combination of a self-contained metal structure with a reduced spanwise extension and a composite structure connected thereto, altogether leading to a low weight and reduced manufacturing costs. More particularly, Figure 2a shows the flow body in form of the vertical tailplane 2 with the air sucking nose component 4 in a lateral view. Here, a sectional plane 14 is indicated by the letter A. The sectional view onto this sectional plane 14 is shown in Figure 2b. Here, the general setup of the flow body is shown in detail. The flow body 2 comprises a microperforated suction skin 16, which is curved in a way that a leading edge 18 is created, wherein a small region around the leading edge 18 will be named "nose region" in the following. The suction skin 16 furthermore comprises two opposing ends 20 and 22 facing away from the leading edge 18. In the following, an upper end 20 (in the drawing plane) will be named "first end", while a lower end 22 will be named "second end 22". From the first end 20, a first interior sidewall 24 extends into the direction of the leading edge 18, wherein the distance between the first interior sidewall 24 and the suction skin 16 constantly increases. In a clear distance to the leading edge 18, the first interior sidewall 24 ends. The same way, a second interior sidewall 26 extends from the second end 22 of the suction skin into the direction of the leading edge 18. The two interior sidewalls 24 and 26 are connected by a second spar member 28 having a perforation 105, which second spar member 28 is arranged vertically relative to an extension direction 30 of the profile chord of the flow body 2. Further, the first end 20 and the second end 22 are connected through a first spar member 32. The intermediate space between the second spar member 28 and the suction skin 16 is closed through stringers 34. Consequently, four closed sections within the suction skin 16 are created. The space between the first inner wall 24 and the suction skin 16, closed by a spanwise stringer 34, is named first suction chamber 36. At the opposite side, a second suction chamber 38 is created between the second interior sidewall 26 and the suction skin 16. Between the nose region and the second spar member 28, closed by auxiliary spars 34, a third suction chamber 40 is created. Enclosed by the first, the second and the third suction chamber 36, 38 and 40 and the second spar 32, a suction duct 42 is created. The suction chambers 36, 38 and 40 are coupled with the central duct 42 through interior perforations 44 having a diameter or opening dimensions, which clearly increase the opening diameters of microperforation in the suction skin 16. Hence, through applying a suction pressure at the central duct 42, air is sucked over the three suction chambers 36, 38 and 40 through the microporous opening in the suction skin 16 into the suction duct 42. In a region at the first end 20 and the second end 22, the suction skin 16 comprises inwardly directed indentations 46 and 48, which allow receiving of connection regions 50 and 52 of composite sidewall members 54 and 56. The composite sidewall members 54 and 56 further extend the air sucking nose component 4 and may allow a connection on a front spar 58 of the flow body / vertical tailplane 2. The part extending from the nose region to the first spar member 32 is made from a metallic material, and preferably is completely self-contained. Hence, for the purpose of saving weight, the sidewall members 54 and 56 are preferably made from a sandwich structure. The use of stringers, spars or other stiffening elements thereby concentrate on the metallic part, resulting in a reduction of the overall weight. Preferably, the first spar member 32 is fastened to the suction skin 16 in a region that also includes the first end 20 and the second end 22, such that the connections to the composite sidewall members 54 and 56 may be combined with the connection to the front spar 32. Fastening material may thereby be reduced. Figure 3a shows a possible detail of a joint in the region around the first end 20. Here, the indentation 46 is created through the use of an angular sheet metal, which may be welded to the remaining part of the suction skin 16, e.g. through diffusion welding. The indentation 46 may comprise a receiving surface 60, which is milled with a precision-milling method to provide exact measures. The connection region 50 of the first composite sidewall member 54 may comprise a jointed stay bolt 62, which may preferably be integrated into the composite material of the first sidewall member 54, e.g. between two subsequent fiber, metal or plastic layers. The bolt 62 comprises a large contact surface, which allows to easily integrate it into the composite sidewall member 54 during the manufacturing process. The contact surface may be disk- or stripe-shaped. The bolt 62 may extend through a first hole 64 created in the indentation/receiving surface 60, extend through a second hole 66 of the first interior sidewall 24 and, furthermore, extend through a third hole 68 of the second spar 32. Afterwards, a nut 70 is screwed onto the bolt 62. Consequently, through fastening the nut 70, all of the components are fastened together. It goes without saying, that an appropriate amount of sealing material should be applied before fastening the nut 70 as well as providing the three boreholes 64, 66 and 68 together at once and debur the boreholes 64, 66 and 68. A connection of the composite sidewalls 54 and 56 to the front spar 58 may be accomplished through a bolt 72 integrated into the sidewall member 54, e.g. in a cone-shaped borehole 74, for creating an even, plane surface. The composite sidewall member 54 may further comprise an indentation 76, which allows to provide a sealing lip 78 onto the composite sidewall 54 and the bolt 72. The sealing lip may be glued to this composition. The front spar 58 of the vertical tailplane 2 may then be fastened to the composite sidewall member 54 through a nut 80, which is fastened onto the bolt 72. In an alternative embodiment or additionally to the use of bolts 72, fastening elements 82 having a flexible element 84 with an undercut 86 may be used for clamping/clicking/ratching the composite sidewall member 54 onto the front spar 58. Figure 4 shows the air sucking nose component 4 of the flow body according to the invention in an isometric view. Here, the leading edge 18, the first end 20 and the second end 22 limit the metallic structure, while composite sidewalls 54 and 56 follow on. In a partial sectional view, the first interior sidewall 24 with a number of perforations 44 is demonstrated. These inner perforations 44 comprise a diameter clearly exceeding the diameter of the microporous suction skin 16. Figure 5 shows another exemplary embodiment of a flow body 88. Here, the suction skin 16 is equipped with a plurality of ribs 90, which are distanced to each other and extend between the first spar member 32 and the leading edge 18 of the suction skin 16. In this exemplary embodiment, the ribs 90 are brazed to the suction skin 16. As clearly visible from Figure 6, only outer ribs 92 and 94 extend completely to the nose region 18, while all intermediate ribs 90 located between the outer ribs 92 and 94 leave a gap, i.e. a certain distance, to the nose region 18. Exemplarily, outer rib 92 comprises a flange 93 for connecting the suction duct 98 to a suction line. Each of the ribs 90 has a central cut-out 96, which allows to lead a tubular suction duct 98 through the flow body 88. The space between the first spar member 32 and a nose region around the leading edge 18 constitutes a suction chamber, from which air is drawn off through the tubular suction duct 98. For this purpose, the tubular suction duct 98 has a second perforation with boreholes having a diameter, which clearly exceeds the diameter of boreholes of the first perforation in the suction skin 16. The tubular suction duct 98 has at least one scoop, hood or protrusion 100, which connects to a central cut-out 96 of a rib 90 in order to support the tubular suction duct 98. The ribs 90 preferebly extend vertical to the suction skin (16), while end ribs preferebly extend parallel to the direction of flight, i.e. parallel to the direction of air flowing onto the flow body. Figure 7 shows a still further exemplary embodiment of a flow body 102 which differs from the flow body 88 of Figure 5 through the lack of the tubular suction duct. However, due to the use of a second spar member in front of the ribs 90, an interior suction duct 109 is constituted by the first spar member 32, the second spar member 104 and the suction skin 16 therebetween. Fig 8 shows, just like Figure 6, that the outer ribs 92 and 94 completely extend to the leading edge 18, while all intermediate ribs 90 located between the outer ribs 92 and 94 leave a gap, i.e. a certain distance, to the leading edge 18. All ribs 90 have a central cut-out 96, which allows to suck of air through all perforation holes along the leading edge 18. It goes without saying that the second spar member 104 comprises a second perforation 105 for allowing air to pass through it. Finally Figure 9 demonstrates a pressure distribution along the profile of the flow body, e.g. the vertical tailplane. As usual, a pressure coefficient c _p, which is the difference between local static pressure and freestream static pressure, nondimensionalized by the freestream dynamic pressure, is shown over the non.dimensionalized relative length of the chord (c) of the flow body (x/c), wherein cp is plotted upside down, i.e. negative (suction) c _p values are higher in the plot than positive c _p values. The suction takes place preferably at the first 10% of the length of the chord of the vertical tailplane. Due to the shape of the vertical tailplane, a first suction peak 106 is created, which is followed by a local maximum 108 of the pressure distribution, i.e. a small region in the plot of Figure 9 where the plot is clearly pushed to the x-axis. While the solid curve 110 shows a pressure distribution of an exemplarily chosen vertical tailplane according to the prior art, the dashed lines having the suction peak 106 and the local maximum demonstrates the changes in the pressure distribution due to a feasible redesign.

1. A flow body (2, 88, 102) comprising: - a curved suction skin (16) having a first perforation, a leading edge (18) and two skin sections extending therefrom, wherein each skin section has an outer end (20, 22) facing away from the leading edge (18), - an interior suction duct (42, 98, 109) having a second perforation (44, 105) and extending through an inside of the curved suction skin (16) in a distance from the leading edge (18), and - two sidewall members (54, 56), connected to the outer ends (20, 22) of the skin sections, wherein the sidewall members (54, 56) are made of a composite material, wherein the curved suction skin (16) comprises a profiled contour shape, which determines a pressure distribution over at least one of the two skin sections when air flows over the curved suction skin (16),: wherein the pressure distribution comprises a stagnation point, a suction peak and a local pressure maximum downstream of the suction peak and upstream a trailing edge of the flow body,: wherein the first perforation extends from the stagnation point to the local pressure maximum.

2. The flow body (2, 88, 102) of claim 1, wherein the first perforation extends from the stagnation point along the curved suction skin (16) up to 8%-15% of a chord length and in particular 10% of the chord length of the flow body (2, 88, 102). 3. The flow body (2, 88, 102) of claim 1 or 2, wherein the sidewall members (54, 56) are made of a sandwich material having at least one core layer enclosed between cover layers. 4. The flow body (2, 88, 102) of any of the previous claims, wherein the interior suction duct (42, 98, 109) is created by an interior wall arrangement fixed to an inside of the curved suction skin (16), the interior wall arrangement comprising: - a first interior sidewall (24) connected to the first end (20) of the suction skin (16), - a second interior sidewall (26) connected to the second end (22) of the suction skin (16), - a first spar member (32) connected to the first and second interior sidewalls (24, 26) at the first and second ends (20, 22) of the suction skin (16), - a second spar member (28) connected to the first and second interior sidewalls (24, 26) at an end opposite to the first and second ends (20, 22) of the suction skin (16), such that a closed, quadrilateral cross-sectional suction duct surface is created by the first spar member (32), the first interior sidewall (24), the second spar member (28) and the second interior sidewall member (26), wherein the quadrilateral cross-sectional suction duct surface extends at a distance along the leading edge (18). 5. The flow body (2, 88, 102) of claim 4,: further comprising at least one stringer (34) arranged between at least one of the first interior sidewall (24), the second interior sidewall (26) and the suction skin (16),: wherein the at least one stringer (34) extends along the leading edge (18) in a distance thereto. 6. The flow body (2, 88, 102) of claim 4 or 5,: wherein the extension of the at least one stringer (34) is interrupted along the leading edge (18). 7. The flow body (2, 88, 102) of one of claims 1 to 3,: further comprising a plurality of ribs (90) at a distance to each other and arranged along the inside of the suction skin (16),: wherein the ribs (90) each comprise a cutout (96), and: wherein the suction duct (98) is tubular, has a second perforation (105) and extends through the cutouts (96) of the ribs (90). 8. The flow body (2, 88, 102) of one of claims 1 to 3,: further comprising a plurality of ribs (90) at a distance to each other and arranged along the inside of the suction skin (16), a first spar member (32) and a second spar member (104): wherein the suction duct is created between the suction skin (16), the first spar member (32) and the second spar member (104).

2886452

Flow body, method for manufacturing a flow body and aircraft having such a flow body

Based on the following detailed description of an invention, generate the patent claims. There should be 6 claims in total. The first, independent claim is given and the remaining 5 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a flow body according to the invention in form of a vertical tailplane 2 having an air sucking nose component 4. The vertical tailplane 2 provides a directional stability around the vertical axis, i.e. the z-axis in an aircraft-fixed coordinate system, reduces aerodynamic side slip and allows to control the aircraft's yaw movement by a rudder 6 movably arranged at a trailing edge 8 of the vertical tailplane 2. The vertical tailplane 2 is fully exposed to an airflow caused by the motion of the aircraft, such that the drag of the vertical tailplane 2 should be decreased to a minimum. As the overall dimensions of the vertical tailplane 2 mainly depend on the stabilizing function and the required structural stability, the drag cannot be reduced through decreasing the size of the vertical tailplane 2. As explained further above, a significant drag reduction may be achieved through selectively sucking air from a boundary flow layer of a nose region of the vertical tailplane 2, such that the flow is as laminar as possible. Therefore, the air sucking nose component 4 is at least partially gas permeable through a microperforation. The air sucking nose component 4 is couplable with an air sucking line 10, a fan 12 and/or any other device that is able to provide a clearly lower pressure than the dynamic pressure in the boundary layer of the air sucking nose component 4. This may be also be accomplished through passive means, such as through exploiting a gas flow along an opening which experiences a suction force due to the Bernoulli effect. As shown in further figures 2a and 2b, a flow body according to the invention may be created having a combination of a self-contained metal structure with a reduced spanwise extension and a composite structure connected thereto, altogether leading to a low weight and reduced manufacturing costs. More particularly, Figure 2a shows the flow body in form of the vertical tailplane 2 with the air sucking nose component 4 in a lateral view. Here, a sectional plane 14 is indicated by the letter A. The sectional view onto this sectional plane 14 is shown in Figure 2b. Here, the general setup of the flow body is shown in detail. The flow body 2 comprises a microperforated suction skin 16, which is curved in a way that a leading edge 18 is created, wherein a small region around the leading edge 18 will be named "nose region" in the following. The suction skin 16 furthermore comprises two opposing ends 20 and 22 facing away from the leading edge 18. In the following, an upper end 20 (in the drawing plane) will be named "first end", while a lower end 22 will be named "second end 22". From the first end 20, a first interior sidewall 24 extends into the direction of the leading edge 18, wherein the distance between the first interior sidewall 24 and the suction skin 16 constantly increases. In a clear distance to the leading edge 18, the first interior sidewall 24 ends. The same way, a second interior sidewall 26 extends from the second end 22 of the suction skin into the direction of the leading edge 18. The two interior sidewalls 24 and 26 are connected by a second spar member 28 having a perforation 105, which second spar member 28 is arranged vertically relative to an extension direction 30 of the profile chord of the flow body 2. Further, the first end 20 and the second end 22 are connected through a first spar member 32. The intermediate space between the second spar member 28 and the suction skin 16 is closed through stringers 34. Consequently, four closed sections within the suction skin 16 are created. The space between the first inner wall 24 and the suction skin 16, closed by a spanwise stringer 34, is named first suction chamber 36. At the opposite side, a second suction chamber 38 is created between the second interior sidewall 26 and the suction skin 16. Between the nose region and the second spar member 28, closed by auxiliary spars 34, a third suction chamber 40 is created. Enclosed by the first, the second and the third suction chamber 36, 38 and 40 and the second spar 32, a suction duct 42 is created. The suction chambers 36, 38 and 40 are coupled with the central duct 42 through interior perforations 44 having a diameter or opening dimensions, which clearly increase the opening diameters of microperforation in the suction skin 16. Hence, through applying a suction pressure at the central duct 42, air is sucked over the three suction chambers 36, 38 and 40 through the microporous opening in the suction skin 16 into the suction duct 42. In a region at the first end 20 and the second end 22, the suction skin 16 comprises inwardly directed indentations 46 and 48, which allow receiving of connection regions 50 and 52 of composite sidewall members 54 and 56. The composite sidewall members 54 and 56 further extend the air sucking nose component 4 and may allow a connection on a front spar 58 of the flow body / vertical tailplane 2. The part extending from the nose region to the first spar member 32 is made from a metallic material, and preferably is completely self-contained. Hence, for the purpose of saving weight, the sidewall members 54 and 56 are preferably made from a sandwich structure. The use of stringers, spars or other stiffening elements thereby concentrate on the metallic part, resulting in a reduction of the overall weight. Preferably, the first spar member 32 is fastened to the suction skin 16 in a region that also includes the first end 20 and the second end 22, such that the connections to the composite sidewall members 54 and 56 may be combined with the connection to the front spar 32. Fastening material may thereby be reduced. Figure 3a shows a possible detail of a joint in the region around the first end 20. Here, the indentation 46 is created through the use of an angular sheet metal, which may be welded to the remaining part of the suction skin 16, e.g. through diffusion welding. The indentation 46 may comprise a receiving surface 60, which is milled with a precision-milling method to provide exact measures. The connection region 50 of the first composite sidewall member 54 may comprise a jointed stay bolt 62, which may preferably be integrated into the composite material of the first sidewall member 54, e.g. between two subsequent fiber, metal or plastic layers. The bolt 62 comprises a large contact surface, which allows to easily integrate it into the composite sidewall member 54 during the manufacturing process. The contact surface may be disk- or stripe-shaped. The bolt 62 may extend through a first hole 64 created in the indentation/receiving surface 60, extend through a second hole 66 of the first interior sidewall 24 and, furthermore, extend through a third hole 68 of the second spar 32. Afterwards, a nut 70 is screwed onto the bolt 62. Consequently, through fastening the nut 70, all of the components are fastened together. It goes without saying, that an appropriate amount of sealing material should be applied before fastening the nut 70 as well as providing the three boreholes 64, 66 and 68 together at once and debur the boreholes 64, 66 and 68. A connection of the composite sidewalls 54 and 56 to the front spar 58 may be accomplished through a bolt 72 integrated into the sidewall member 54, e.g. in a cone-shaped borehole 74, for creating an even, plane surface. The composite sidewall member 54 may further comprise an indentation 76, which allows to provide a sealing lip 78 onto the composite sidewall 54 and the bolt 72. The sealing lip may be glued to this composition. The front spar 58 of the vertical tailplane 2 may then be fastened to the composite sidewall member 54 through a nut 80, which is fastened onto the bolt 72. In an alternative embodiment or additionally to the use of bolts 72, fastening elements 82 having a flexible element 84 with an undercut 86 may be used for clamping/clicking/ratching the composite sidewall member 54 onto the front spar 58. Figure 4 shows the air sucking nose component 4 of the flow body according to the invention in an isometric view. Here, the leading edge 18, the first end 20 and the second end 22 limit the metallic structure, while composite sidewalls 54 and 56 follow on. In a partial sectional view, the first interior sidewall 24 with a number of perforations 44 is demonstrated. These inner perforations 44 comprise a diameter clearly exceeding the diameter of the microporous suction skin 16. Figure 5 shows another exemplary embodiment of a flow body 88. Here, the suction skin 16 is equipped with a plurality of ribs 90, which are distanced to each other and extend between the first spar member 32 and the leading edge 18 of the suction skin 16. In this exemplary embodiment, the ribs 90 are brazed to the suction skin 16. As clearly visible from Figure 6, only outer ribs 92 and 94 extend completely to the nose region 18, while all intermediate ribs 90 located between the outer ribs 92 and 94 leave a gap, i.e. a certain distance, to the nose region 18. Exemplarily, outer rib 92 comprises a flange 93 for connecting the suction duct 98 to a suction line. Each of the ribs 90 has a central cut-out 96, which allows to lead a tubular suction duct 98 through the flow body 88. The space between the first spar member 32 and a nose region around the leading edge 18 constitutes a suction chamber, from which air is drawn off through the tubular suction duct 98. For this purpose, the tubular suction duct 98 has a second perforation with boreholes having a diameter, which clearly exceeds the diameter of boreholes of the first perforation in the suction skin 16. The tubular suction duct 98 has at least one scoop, hood or protrusion 100, which connects to a central cut-out 96 of a rib 90 in order to support the tubular suction duct 98. The ribs 90 preferebly extend vertical to the suction skin (16), while end ribs preferebly extend parallel to the direction of flight, i.e. parallel to the direction of air flowing onto the flow body. Figure 7 shows a still further exemplary embodiment of a flow body 102 which differs from the flow body 88 of Figure 5 through the lack of the tubular suction duct. However, due to the use of a second spar member in front of the ribs 90, an interior suction duct 109 is constituted by the first spar member 32, the second spar member 104 and the suction skin 16 therebetween. Fig 8 shows, just like Figure 6, that the outer ribs 92 and 94 completely extend to the leading edge 18, while all intermediate ribs 90 located between the outer ribs 92 and 94 leave a gap, i.e. a certain distance, to the leading edge 18. All ribs 90 have a central cut-out 96, which allows to suck of air through all perforation holes along the leading edge 18. It goes without saying that the second spar member 104 comprises a second perforation 105 for allowing air to pass through it. Finally Figure 9 demonstrates a pressure distribution along the profile of the flow body, e.g. the vertical tailplane. As usual, a pressure coefficient c _p, which is the difference between local static pressure and freestream static pressure, nondimensionalized by the freestream dynamic pressure, is shown over the non.dimensionalized relative length of the chord (c) of the flow body (x/c), wherein cp is plotted upside down, i.e. negative (suction) c _p values are higher in the plot than positive c _p values. The suction takes place preferably at the first 10% of the length of the chord of the vertical tailplane. Due to the shape of the vertical tailplane, a first suction peak 106 is created, which is followed by a local maximum 108 of the pressure distribution, i.e. a small region in the plot of Figure 9 where the plot is clearly pushed to the x-axis. While the solid curve 110 shows a pressure distribution of an exemplarily chosen vertical tailplane according to the prior art, the dashed lines having the suction peak 106 and the local maximum demonstrates the changes in the pressure distribution due to a feasible redesign.

9. Method for manufacturing a flow body (2, 88, 102), comprising: - forming a suction skin (16) to a profiled contour shape having a leading edge (18) and two skin sections extending therefrom, wherein each skin section has an outer end (20, 22) facing away from the leading edge (18), such that the profiled contour shape of the suction skin (16) determines a pressure distribution over at least one of the two skin sections when air flows over the curved suction skin (16), which pressure distribution comprises a stagnation point, a suction peak and a local pressure maximum downstream of the suction peak and upstream of a trailing edge of the flow body, - creating a first perforation extending from the stagnation point to the local pressure maximum, - providing an interior suction duct (42, 98, 109) having a second perforation (44, 105) and extending through an inside of the curved suction skin (16) in a distance from the leading edge (18), and - connecting two sidewall members (54, 56) to the outer ends (20, 22) of the skin sections, wherein the sidewall members (54, 56) are made of a composite material.

10. The method of claim 9, wherein creating the first perforation comprises creating first perforation holes from the stagnation point along the curved suction skin (16) up to 8%-15% of a chord length and in particular 10% of the chord length of the flow body (2, 88, 102). 11. The method of claim 9 or 10, wherein forming the curved suction skin (16) comprises a Super Plastic Forming (SPF) process of a titanium workpiece. 12. The method of claim 11, wherein forming the curved suction skin (16) comprises integrating a plurality of stiffening components at the inside of the suction skin through the SPF process. 13. The method of one of claims 9 to 12, further comprising brazing ribs (90) to the inside of the suction skin (16). 14. Aircraft having at least one flow body (2, 88, 102) of one of the claims 1 to 8.

2886453

Boundary layer control system and aircraft having such a boundary layer control system

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an overview of a tailplane having a vertical tailplane 2, two horizontal tailplanes 4, which are arranged vertical to each other at a tail 6 of an aircraft. Downstream of the vertical tailplane 2 and the horizontal tailplanes 4, a tail cone 8 is present. The tailplanes 2 and 4 comprise nose sections 10 as boundary layer control components, which are perforated and allow to move air through the nose sections 10, i.e. sucking of air or blowing of air. By sucking of air through the nose sections 10, a laminar flow control is enabled, since the boundary flow layer will be stabilised, preferably during cruise flight. The aerodynamic drag of the tailplanes 2 and 4 is thereby clearly decreased. According to the this exemplary embodiment, a suction chamber 12 is arranged in a root region of one of the horizontal tailplanes 4, which is couplable to the nose sections 10 through ducts 14 and 16. Duct 16 exemplarily extends along a front spar of the horizontal tailplane 4, such that the necessary distance to an air control device is minimized. The duct 16 may comprise gimbals for compensating trim movements of the horizontal tailplane and extends into the suction chamber 12. The function of the suction chamber 12 is explained further below. In Figure 2, an underside of the horizontal tailplanes 4 is visible. The suction chamber 12 comprises an skin section, which is shown as an outer surface 18 comprising a outflow opening 20, which extends to the surrounding of the aircraft. It is apparent, that the direction of the outflow opening 20 is extending angularly to the expected flow. Due to the Bernoulli effect a suction force at the outflow opening 20 is created in case the aircraft moves relative to air. As the suction chamber 12 is couplable to the nose sections 10 of the tailplanes 2 and 4, a passive suction of air may be accomplished. Resultantly, the laminarization may be accomplished without any active element. In Figure 3, an air control device 22 is shown, which is couplable to the above-mentioned ducts 14 for the horizontal tailplanes 4 and 16 for the vertical tailplane 2. Further, a pressurized air line in the form of an APU bleed air line 24 is present, which extends from the air control device 22 into the tail cone 8, where an APU may be present (not depicted in Figure 3 ). Further, an air injector 26 is present, which extends into a connection line 28 and has an inlet 30 for ambient air 32. A bleed air valve (not shown) may allow to let bleed air flow into the connection line 28. Further downstream, the supply ducts 14 and 16 are couplable by means of a control valve 36 to the pressurized air line 24. The control valve 36 may comprise three or more distinct flow control positions, indicated with a), b) and c). In case bleed air shall flow into the vertical tailplane 2, the flow control position a) shall be used. In case bleed air shall flow into the horizontal tailplanes 4, the flow control position b) shall be used. However, another flow control position may be feasible to provide both the horizontal and vertical tailplanes with bleed air for purging the boundary layer control components at the same time, if a sufficient pressure and flow rate is available. In case suction of air shall be accomplished, the flow control position c) may be feasible, in which ducts 14 and 16 are connected to each other. As the duct 16 runs through the nose region of the horizontal tailplanes 4, it may cross the suction chamber 12 and be directly coupled with the outflow opening 20, such that the suction force acts along the whole duct 16. By simply connecting duct 14 to duct 16, the suction force also acts on the boundary layer control component of the vertical tailplane 2. In case bleed air flows from the bleed air duct 24 to the connection line 28, ambient air is sucked into the connection line 28 through the air injector 26, which is closable through an injector valve 34. Further, it will then flow to the supply ducts 14 and 16, depending on the flow control position of the control valve 36. A flow restrictor 38 as a flow resistance means upstream of the air injector 26 reduces the pressure of the bleed air entering the connection line 28. Altogether, the volume flow rate downstream the air injector 26 is clearly increased, which reduces the required bleed air volume flow rate. Further, due to the clearly lower temperature of the ambient air compared to bleed air, the temperature of the air reaching the supply ducts 14 and 16 are decreased. Through a control logic, or just through receiving a signal, purging the nose sections 10 may be accomplished through introducing bleed air. In this operational case, the opening 20, which is connected to the supply ducts 14 and 16, should be closed through a cover 40 (see option I in Figure 5 ). Figure 4 shows a possible installation position in the tail 6 of the aircraft. For the purpose of better visibility, the vertical and horizontal tailplanes 2, 4 are removed in this view. In Figure 5, a detailed view of the suction chamber 12 is provided. Here, the opening 20 is closable by a cover 40, which is shown in a first state I (closed) and in a second state II (open). Depending on the opening state, a suction force is present at the opening 20, which leads to a suction on the nose sections 10 of the tailplanes 2, 4 for the laminarization of the flow. Coupling the suction chamber 12 and the outflow opening 20 is accomplished through a port 41, which extends into the interior of the tailplane root region. Figure 6 shows the air sucking chamber 12 in a lateral view (view B as indicated in Figure 5 ), in which a hollow chamber 42 is indicated, into which air is sucked from the connected nose sections 10. Still further, Figure 6 shows an exemplary embodiment of a perforated nose region 44 and a leading edge suction duct 46. Figure 7 exemplarily shows a vertical tailplane 2 in a sectional view with a central duct 48 constituted in a self-contained structure 50, wherein a flange 52 is connectable to the supply duct 16. Exemplarily, one-way valves 51 and 53 provide for a routing of the airflow depending on their direction, i.e. for purging the airflow should be applied more to the nose edge (region 10a), while sucking of air may take place in a slight distance thereto (region 10b). Figure 8 demonstrates that the pressure in the air suction chamber 42 is clearly lower than the effective suction pressure in the exemplary central duct 48 and directly at the nose section 10. Hence, the flow resistance should be optimized in order to maintain a sufficient suction of air at the nose sections 10. Figure 9 shows another exemplary embodiment with an opening 54 arranged in front of a horizontal tailplane 4 in a skin section 55 of the aircraft. Again, due to the Bernoulli effect, a suction force is created at the opening 54 in case it is open. Detail C shows a scoop 56, which is rotatably arranged in the opening 54. With this rotatable scoop 56, the opening 54 may either act as a ram air opening or as a suction opening. How this is accomplished is further shown in Figures 10a-10e with an air control device 57, wherein the direction of flow in Figures 10a-10d runs from the right to the left (as indicated by an arrow), which is opposite the direction of flight. Figure 10a shows the movably supported body, i.e. a rotatably supported scoop 56, which is movably around a rotational axis 64 and may change its position in a guide 59, which is in fluid communication with the opening 54, in a first position. Here, a suction opening 60 faces downstream the skin section 55, i.e. towards the tail cone 8. Hence, in the viewing direction of Figure 10a, the surrounding airflow around the aircraft passes from the right to the left over the scoop 56. Hence, a suction force is created in the suction opening 60. By connecting a connection or suction duct 62, which is in fluid communication with opening 54, to the ducts 14 and 16, a suction of air through the nose sections 10 to the opening 54 is accomplished. As explained above, the scoop 56 is rotatably supported on a rotational axis 64, wherein the rotational axis 64 may be situated in a center of a hollow ring or sphere, which corresponds to the shape of the scoop 56. Preferably, the scoop 56 may be rotated around 90°. If the scoop 56 comprises a shape of a segment of a hollow disk or a hollow ring, a ram air opening 66 may be brought to a position facing upstream, as shown in Figure 10c. The suction opening 60 is hidden inside the suction duct 62 and is not exposed to the ambient anymore. In the position in Figure 10c, scoop 56 acts as a ram air inlet. As demonstrated, the rotational axis 64 is inwards directed from the outer surface 55, such that one of the suction opening 60 and the ram air opening 66 may always be sealed. Also, the scoop 56 may be a quarter segment of a hollow sphere-shaped body. The guide 59 should then be a section of a (half) sphere. In order to eliminate active components for moving the scoop 56 between the two positions, Figures 10b and 10d show a shape memory alloy spring arrangement 68. This arrangement 68 exemplarily comprises a first spring 70 and a second spring 72, which are mechanically connected in a series connection. In a connecting region 74, which may be a joint, a rotatably supported lever 76 is coupled with the shape memory alloy spring arrangement 68. If the joint 74 moves in a lateral direction, the lever 76 rotates around the rotational axis 64 and thereby rotates the scoop 56. The rotation may be accomplished through the design characteristics of the first spring 70 and the second spring 72. For example, the first spring 70 is a tensioning spring, which urges into an original shape when it reaches a first transition temperature immanent to the first spring 70 due to its material composition. Further, the second spring 72 may be a pressing spring, which purges into its original shape when it reaches a second transition temperature. In Figure 10b, the second spring 72 has reached its original immanent shape, which leads to a compression of the first spring 70, which is outside the first transition temperature associated with the first spring 70. This may exemplarily be the case during a cruise flight, when the second transition temperature equals a typical maximum temperature at a cruise flight altitude. In lower altitudes, the first spring may reach its first transition temperature limit, such that the scoop 56 moves into the opposite direction. This enables a precise and reliable control of the scoop 56 completely independent of active elements. For providing a purging function, a fan or compressor 70, which is shown in Figure 9, is necessary, as the ram air pressure may not be able to overcome the pressure at the nose sections 10 induced by the impinging flow. Finally, Figure 11 shows the air injector 26 in a larger size. Here, connection line 28 comprises a snorkel 78 reaching from an outside of the connection line 28 and outside a fuselage of the aircraft to its inside. By air flowing through the flow restrictor 38 over the snorkel 78, air 32 is sucked into the connection line. Thus, the volume flow rate is increased and the temperature is decreased.

1. A boundary layer control system for an aircraft, comprising: - an outflow opening (20, 60) arrangeable in a skin section (18, 55) of the aircraft, which outflow opening (20, 60) provides a suction force when air flows along the skin section (18, 55), - at least one duct (14, 16) couplable with the outflow opening (20, 60) and coupled to a boundary layer control component (10) having perforations, - a pressurized air source, and - an air control device (22),: wherein the air control device (22) is configured to selectively couple the at least one duct (14, 16) with one of: - the pressurized air source for purging the perforations of the boundary layer control component (10) and - the outflow opening (20,60) for inducing a suction of air through the perforations into the boundary layer control component (10).

2. The boundary layer control system of claim 1,: wherein the air control device (22) comprises at least one valve (36) for selectively coupling the at least one duct (14, 16) with the pressurized air source or the outflow opening (20, 60). 3. The boundary layer control system of claim 1 or 2,: wherein the pressurized air source is a pressurized air line (24), which is connectable to a bleed air port of the aircraft. 4. The boundary layer control system of claim 3,: wherein the bleed air port is associated with an auxiliary power unit arranged in a tail region (6) of the aircraft. 5. The boundary layer control system of claim 3 or 4,: wherein the pressurized air line (24) is in fluid communication with at least one flow resistance means (38) for reducing the pressure of the pressurized air delivered by the pressurized air line (24). 6. The boundary layer control system of any of the claims 3 to 5,: further comprising an air injector (26) having an outlet arranged in or downstream the pressurized air line (24) and an air inlet (32) couplable with a source of ambient air. 7. The boundary layer control system of claim 6,: wherein the air inlet (32) is arrangeable at an outer surface of the aircraft. 8. The boundary layer control system of any of the previous claims,: wherein the outflow opening (20, 60) is arranged in a suction chamber (12) and wherein the at least one duct (14, 16) is couplable with the outflow opening (20, 60) over the suction chamber (12). 9. The boundary layer control system of claim 8,: wherein the suction chamber (12) is a part of a root portion of a horizontal tailplane (4). 10. The boundary layer control system of claim 1,: wherein the air control device (22) comprises an arrangement of at least one shape memory alloy spring (70, 72) and a movable body (56),: wherein the arrangement is adapted for blocking the outflow opening (20, 60), when the at least one shape memory alloy spring (70, 72) is exposed to a first transition temperature and to unblock the outflow opening (20, 60), when the at least one shape memory alloy spring (70, 72) is exposed to a second transition temperature. 11. The boundary layer control system of claim 10,: wherein the arrangement of shape memory alloy springs (70, 72) comprises two shape memory alloy springs (70, 72) in a serial connection,: wherein a first spring (70) is a tensioning spring and a second spring (72) is a pressing spring,: wherein the first spring (70) and the second spring (72) comprise different transition temperatures. 12. The boundary layer control system of claim 10 or 11,: wherein the movable body (56) is a scoop having a suction opening (60) and a ram air opening (66),: wherein a plane of the suction opening (60) and a plane of the ram air opening (66) intersect at an angle larger than 45° and smaller than 180°,: wherein the body (56) is rotatably mounted in an opening (54) in the skin section and couplable with a connection point of the arrangement of shape memory alloy springs (70, 72),: wherein depending on the temperature either the suction opening (60) or the ram air opening (66) extends out of the opening (54) and faces in one of two opposed directions. 13. The boundary layer control system of one of any of the previous claims,: further comprising a fan couplable to the at least one duct (14, 16) for increasing the pressure of pressurized air for purging the boundary layer control component (10). 14. An aircraft having a boundary layer control system of one of claims 1 to 13. 15. The aircraft of claim 14, further comprising a tailplane arrangement, wherein the boundary layer control component (10) is arranged on a leading edge of at least one tailplane of the tailplane arrangement.

2886741

Fender, its use, method for its manufacture and method for protecting a surface

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1a-b illustrate the collision between a moving object 2, such as a shopping cart or a car, and a wall 4 provided with a strip-shaped rubber fender 6 extending horizontally along the wall 4. In the situation of Figure 1 a, the object 2 approaches the wall 4 from an impact direction, i.e., the impact direction is opposite to the object's motion illustrated by an arrow A. In the illustrated exemplary situation, the impact direction lies in the horizontal plane and forms an acute angle with the longitudinal direction of the fender 6. Figure 1 b illustrates the moment of impact between the object 2 and the fender 6. The impact force C acting on the object 2 at the engagement between the object 2 and the fender 6 may be decomposed into a component N normal to the wall; a frictional component F parallel to the wall; and a torque T about a vertical axis, which will urge the object to turn anticlockwise as seen from above. On collision, the torque T will strive to turn the object 2 anticlockwise, and thereby press the front end of the object 2 towards the wall 4. This effect will even further increase the impact force. In this manner, the fender 6 may in fact attract, rather than deflect, the object, causing the impact to be more severe, to the object 2 as well as to the wall 4, than it would have been without a fender. Moreover, a previously controlled, linear motion of the object maintained by e.g. a driver may due to the collision become out of control, e.g. causing uncontrolled rotation. By way of example, a person pushing a shopping cart 2, and accidentally running into the rubber fender 6 at an oblique angle, may lose control of the cart 2. On the other hand, a certain amount of friction between the object 2 and the fender 6 is desired; it may, for example, assist in stopping a shopping cart 2 that is already out of control, or that has accidentally been set in motion. Figure 2 illustrates a strip-shaped fender 10 for protecting a surface, such as the wall 4 of Figs 1 a-b, from shocks from an impact direction having a component normal to the surface. The fender 10 is formed as a strip, the cross-section of which is essentially identical along the length of the fender 10. A solid rubber body 12 of the fender 10 comprises a resilient bladder 14, i.e. a tubular portion enclosing an air-filled space 16 extending along the length of the fender 10, and a mounting foot 18 for attaching the fender 10 to a mating, elongate groove (not shown). The bladder 14 is closed as seen in cross-section. An outer portion of the bladder 14 is provided with a low-friction slide strip 20, which has a low-friction slide surface 22 facing away from the mounting foot 18. The bladder's 14 outer surface is exposed along two strip-shaped bladder surface portions 24a, 24b, which extend on either side of the low-friction slide strip 20. The rubber of the body 12 has been selected to provide a normal to high level of friction, whereas the material of the slide strip 20 has been selected to provide a relatively low level of friction. Typically, the slide strip 20 may be formed by e.g. a thermoplastic, a low-friction rubber, or a flocked-fibre layer. As the body 12 is formed by a rubber selected to provide a higher level of friction than the low-friction slide strip, the exposed bladder surface portions 24a-b thereby form impact-absorption surfaces for frictionally engaging with, and thereby decelerating, an object impacting the fender 10. The fender's outer surface facing away from the mounting foot 18 is formed by the slide surface 22 and the two impact-absorption surfaces 24a-b. The low-friction slide surface 22 forms the outermost extremity of the fender 10 in a direction normal to the surface to be protected, and the two adjoining higher-friction impact-absorption surfaces 24a-b are retractedly arranged behind the outermost extremity of, the low-friction slide surface 22. The low-friction slide surface 22 covers about 30% of the total outer surface of the bladder, and the two impact-absorption surfaces 24a-b cover the remaining about 70%. Figs 3a-b illustrate the collision between a blunt object 2 and the fender 10. In the situation of Figure 3a, the object 2 approaches the wall 4 from an impact direction, its direction of motion being illustrated by an arrow A. The first fender portion to engage with the object 2 will be the outermost extremity 26 of the slide surface 22. On impact, the object 2 will gradually depress, and resiliently de-form, the fender 10 to an extent determined by the level of the impact force. If the impact force exceeds a limit force, the fender 10 will be sufficiently depressed to allow the object 2 to engage with the higher-friction impact-absorption surfaces 24a-b, thereby having arrived at the situation illustrated in Figure 3b. Assuming that the object 2 strikes the fender 10 at an acute angle with the fender's longitudinal direction, the friction in the engagement between the object 2 and the higher-friction impact-absorption surfaces 24a-b will now decelerate the object's 10 motion along the fender 10. The function of the fender 10 may be better understood by referring again to the situation of Figure 1 b, but assuming that the fender 6 has been replaced by the fender 10 described with reference to Figs 2-3. Upon impact, the low-friction slide surface 22 will be the first to engage with the object 2. When the surface-normal component of the impact force acting on the fender 10 (opposite, and identical in magnitude, to the normal force N acting on the object 2) exceeds the limit force, the impact force is sufficient to bring the object 2 into engagement with the higher-friction impact-absorption surfaces 24a-b, i.e. the fender 10 will have been locally depressed into the shape illustrated in Figure 3b. When having reached this position, the higher-friction impact-absorption surfaces 24a-b will start to decelerate the object's 10 motion along the fender 10. However, before having reached this position, the normal force N exerted by the fender 10 on the object 2 will have already applied a significant clockwise torque on the object, thereby counteracting the anticlockwise torque induced by the friction along the fender's longitudinal direction. Stated more briefly, the fender 10 will engage with, and decelerate, the object 2 without so strongly urging the object 2 to turn towards the wall 4. Thereby, the effect that the impact might become more severe than it would have been without a fender may be avoided, and control of the object's 2 continued motion after the impact may easier be maintained. The situation described above relates to an impact force exceeding the limit force. In the event that the impact force does not exceed the limit force, the object 2 will merely slide against the fender's 10 slide surface 22, and its motion will therefore not be significantly deflected or impaired. A typical limit force of a fender 10 may, by way of example, correspond to a line load, which is applied along a line perpendicular to the fender's 10 longitudinal direction and directed towards the fender 10 from an impact direction normal to the surface 4 to be protected, of between 40 N/dm and 4000 N/dm. A limit force in the lower part of the range may, e.g., be suited for absorbing the shock of a shopping cart impacting the wall of a self-service store, whereas a limit force in the upper part of the range may be suited for absorbing shocks of large vehicles or the like. Thanks to the low-friction slide surface 22, the fender 10 will be exposed to relatively moderate longitudinal as well as transversal stress, which will prolong its service life. The fender 10 may be manufactured by extruding the body 12 from a relatively higher-friction rubber material, and extruding the slide strip 20 as a layer of relatively lower-friction polymer, such as any suitable plastic or lower-friction rubber material, onto the body 12. The body 12 and slide strip 20 may also be co-extruded in a single extrusion step. The friction of rubber materials may be adjusted in many different ways. By way of example, it may be adjusted by using various rubber composition additives well known to those skilled in the art, such as polytetrafluoroethylene; by applying friction-increasing or friction-reducing substances, such as talcum powder, to the rubber surface; or by adjusting the hardness of the rubber. Figure 4 illustrates a second embodiment of a fender. The fender 110 is functionally equivalent to the fender 10 described with reference to Figs 2-3. However, the fender 110 differs from the fender 10 in that the fender's 110 body 112 is made of a low-friction rubber, and the outermost extremity of the resilient bladder 114 is bare, defining a low-friction slide surface 122 extending along the length of the fender 110. Two relatively higher-friction rubber strips 123a, 123b, extending along the length of the fender 110, form impact-absorption surfaces 224a, 224b for engaging with, and decelerating, an impacting object once the impact force has exceeded a limit force. Figure 5 illustrates a third embodiment of a fender. The fender 210 comprises two bladders 214a-b located on either side of a central bladder 214c. The three bladders 214a-c form, together with three arrow-shaped feet 218a-c for attaching the fender 210 to mating grooves in a surface to be protected, an integral rubber body 212. A slide strip 220, having an outer low-friction slide surface 222, covers the outer surface of the central bladder 214c. The adjoining bladders 214a-b are bare, exposing the relatively higher-friction rubber material of the body 212 to form a pair of impact-absorbing surfaces 224a-b. The slide surface 222 of the central bladder 214c forms the outermost extremity of the fender in a direction normal to the surface to be protected, whereas the impact-absorption surfaces 224a-b of the adjoining bladders 214a-b are retractedly arranged behind the outermost extremity of the low-friction slide surface 222. Thereby, a blunt object striking the fender from an impact direction normal to the surface to be protected will first engage the low-friction slide surface 222 of the central bladder 214c, and thereafter, if the impact force exceeds a limit force, engage with the relatively higher-friction impact-absorption surfaces 224a-b. Figure 6 illustrates a fourth embodiment of a fender. The fender 310 comprises a solid, relatively high-friction rubber body 312 with a recess 315 extending along the length of the body 312. The recess 315 defines, together with a strip-shaped sheet 320 of relatively low-friction rubber bridging the recess 315 and extending along the length of the fender 310, a closed bladder 314. The sheet 320 of relatively low-friction rubber bulges out from the recess 315, to form a low-friction slide surface 322 at the outermost extremity of the fender 310 in a direction normal to the surface 4 to be protected. Relatively higher-friction impact-absorption surfaces 324a-b are retracted behind the outermost extremity of the slide surface 322, so as not to be the first surfaces to engage with any blunt object impacting the fender from an direction normal to the surface 4 to be protected. The fender 310 does not have a foot; instead, it may be e.g. screwed or glued onto the surface 4 to be protected. Figs 7a-b illustrate the collision between an object and a fifth embodiment of a fender. The fender 410 differs from the fenders 10, 110, 210, 310 described hereinbefore in that the fender 410 does not comprise a bladder. However, the function of the fender 410 is similar to those previously described. A blunt object 2 approaching a surface 4 to be protected will first engage with a strip-shaped low-friction slide portion 420 of the fender, and thereafter, if the impact force of the object 2 exceeds a limit force, depress or deflect the low-friction slide portion 420 ( Figure 7b ), such that the object engages with higher-friction impact-absorption portions 424a-b of the fender, which portions 424a-b are retractedly arranged behind the outermost extremity of the surface 422 of the low-friction slide portion 420 when the fender is unloaded ( Figure 7a ). The fenders 10, 110, 210, 320, 410 described hereinbefore are particularly well suited for protecting against impacts of blunt objects moving in a plane parallel to the normal of the surface to be protected, and having a velocity a substantial component of which is directed along the longitudinal direction of the fender. To concretize and exemplify, the fenders are well suited for extending horizontally on vertical walls, for protecting against objects moving in the horizontal plane. Particular applications may comprise, e.g., protecting the walls of industrial buildings, research laboratories, parking garages, self-service stores, hospitals and loading platforms against impacting objects rolling on wheels, and protecting pier constructions against boats approaching horizontally along a water surface.

1. A strip-shaped fender for mounting on a surface to be protected from shocks from an impact direction, the fender (10; 110; 210; 310) being characterized in comprising: a resilient bladder (14; 114; 214c; 314) extending along the length of the fender (10; 110; 210; 310);: a strip-shaped low-friction slide surface (22; 122; 222; 322) extending along the resilient bladder (14; 114; 214c; 314), the slide surface (22; 122; 222; 322) forming the outermost extremity (26) of the fender (10; 110; 210; 310) in the impact direction, so as to be the first fender (10; 110; 210; 310) portion to engage with any blunt object (2) impacting the fender (10; 110; 210; 310) from the impact direction; and: a strip-shaped higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b) extending along the length of the fender (10; 110; 210; 310), said higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b) being retractedly arranged behind the outermost extremity (26) of the low-friction slide surface (22; 122; 222; 322) so as not to be the first fender portion to engage with any blunt object (2) impacting the fender (10; 110; 210; 310) from the impact direction,: the bladder (14; 114; 214c; 314) being configured to, when an impact force of a blunt object (2) striking the bladder (14; 114; 214c; 314) from the impact direction exceeds a limit force, resiliently yield, such that the blunt object (2) engages the higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b) of the fender (10; 110; 210; 310).

2. The strip-shaped fender according to claim 1, further comprising a mounting foot (18; 218a-c) for attaching the fender (10; 210) to a mating groove of the surface (4) to be protected from shocks. 3. The strip-shaped fender according to any of the previous claims, wherein said higher-friction impact-absorption surface is formed by a strip-shaped portion (24a-b; 124a-b) of the bladder (14; 114) adjoining the low-friction slide surface (22; 122). 4. The strip-shaped fender according to claim 3, wherein the low-friction slide surface (22) covers less than about 40% of a total outer surface of the bladder (14). 5. The strip-shaped fender according to any of the claims 1-2, wherein said higher-friction impact-absorption surface is formed by the outer surface (224a-b) of a second resilient bladder (214a-b) extending along the length of the fender (210). 6. The strip-shaped fender according to any of the previous claims, further comprising a second strip-shaped higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b), wherein said higher-friction impact-absorption surfaces (24a-b; 124a-b; 224a-b; 324a-b) extend along either side of the low-friction slide surface (22; 122; 222; 322). 7. The strip-shaped fender according to any of the previous claims, wherein the limit force corresponds to a line load, applied along a line perpendicular to the fender's longitudinal direction, exerting a force of 40 N/dm from an impact direction normal to the surface (4) to be protected. 8. The strip-shaped fender according to any of the previous claims, wherein said low-friction slide surface (22; 122; 222; 322) is formed by a flocked fibre surface. 9. The strip-shaped fender according to any of the previous claims, wherein said low-friction slide surface (22; 122; 222; 322) is made by rubber or plastic. 10. The strip-shaped fender according to any of the previous claims, wherein said higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b) is formed by rubber.

2886741

Fender, its use, method for its manufacture and method for protecting a surface

Based on the following detailed description of an invention, generate the patent claims. There should be 3 claims in total. The first, independent claim is given and the remaining 2 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1a-b illustrate the collision between a moving object 2, such as a shopping cart or a car, and a wall 4 provided with a strip-shaped rubber fender 6 extending horizontally along the wall 4. In the situation of Figure 1 a, the object 2 approaches the wall 4 from an impact direction, i.e., the impact direction is opposite to the object's motion illustrated by an arrow A. In the illustrated exemplary situation, the impact direction lies in the horizontal plane and forms an acute angle with the longitudinal direction of the fender 6. Figure 1 b illustrates the moment of impact between the object 2 and the fender 6. The impact force C acting on the object 2 at the engagement between the object 2 and the fender 6 may be decomposed into a component N normal to the wall; a frictional component F parallel to the wall; and a torque T about a vertical axis, which will urge the object to turn anticlockwise as seen from above. On collision, the torque T will strive to turn the object 2 anticlockwise, and thereby press the front end of the object 2 towards the wall 4. This effect will even further increase the impact force. In this manner, the fender 6 may in fact attract, rather than deflect, the object, causing the impact to be more severe, to the object 2 as well as to the wall 4, than it would have been without a fender. Moreover, a previously controlled, linear motion of the object maintained by e.g. a driver may due to the collision become out of control, e.g. causing uncontrolled rotation. By way of example, a person pushing a shopping cart 2, and accidentally running into the rubber fender 6 at an oblique angle, may lose control of the cart 2. On the other hand, a certain amount of friction between the object 2 and the fender 6 is desired; it may, for example, assist in stopping a shopping cart 2 that is already out of control, or that has accidentally been set in motion. Figure 2 illustrates a strip-shaped fender 10 for protecting a surface, such as the wall 4 of Figs 1 a-b, from shocks from an impact direction having a component normal to the surface. The fender 10 is formed as a strip, the cross-section of which is essentially identical along the length of the fender 10. A solid rubber body 12 of the fender 10 comprises a resilient bladder 14, i.e. a tubular portion enclosing an air-filled space 16 extending along the length of the fender 10, and a mounting foot 18 for attaching the fender 10 to a mating, elongate groove (not shown). The bladder 14 is closed as seen in cross-section. An outer portion of the bladder 14 is provided with a low-friction slide strip 20, which has a low-friction slide surface 22 facing away from the mounting foot 18. The bladder's 14 outer surface is exposed along two strip-shaped bladder surface portions 24a, 24b, which extend on either side of the low-friction slide strip 20. The rubber of the body 12 has been selected to provide a normal to high level of friction, whereas the material of the slide strip 20 has been selected to provide a relatively low level of friction. Typically, the slide strip 20 may be formed by e.g. a thermoplastic, a low-friction rubber, or a flocked-fibre layer. As the body 12 is formed by a rubber selected to provide a higher level of friction than the low-friction slide strip, the exposed bladder surface portions 24a-b thereby form impact-absorption surfaces for frictionally engaging with, and thereby decelerating, an object impacting the fender 10. The fender's outer surface facing away from the mounting foot 18 is formed by the slide surface 22 and the two impact-absorption surfaces 24a-b. The low-friction slide surface 22 forms the outermost extremity of the fender 10 in a direction normal to the surface to be protected, and the two adjoining higher-friction impact-absorption surfaces 24a-b are retractedly arranged behind the outermost extremity of, the low-friction slide surface 22. The low-friction slide surface 22 covers about 30% of the total outer surface of the bladder, and the two impact-absorption surfaces 24a-b cover the remaining about 70%. Figs 3a-b illustrate the collision between a blunt object 2 and the fender 10. In the situation of Figure 3a, the object 2 approaches the wall 4 from an impact direction, its direction of motion being illustrated by an arrow A. The first fender portion to engage with the object 2 will be the outermost extremity 26 of the slide surface 22. On impact, the object 2 will gradually depress, and resiliently de-form, the fender 10 to an extent determined by the level of the impact force. If the impact force exceeds a limit force, the fender 10 will be sufficiently depressed to allow the object 2 to engage with the higher-friction impact-absorption surfaces 24a-b, thereby having arrived at the situation illustrated in Figure 3b. Assuming that the object 2 strikes the fender 10 at an acute angle with the fender's longitudinal direction, the friction in the engagement between the object 2 and the higher-friction impact-absorption surfaces 24a-b will now decelerate the object's 10 motion along the fender 10. The function of the fender 10 may be better understood by referring again to the situation of Figure 1 b, but assuming that the fender 6 has been replaced by the fender 10 described with reference to Figs 2-3. Upon impact, the low-friction slide surface 22 will be the first to engage with the object 2. When the surface-normal component of the impact force acting on the fender 10 (opposite, and identical in magnitude, to the normal force N acting on the object 2) exceeds the limit force, the impact force is sufficient to bring the object 2 into engagement with the higher-friction impact-absorption surfaces 24a-b, i.e. the fender 10 will have been locally depressed into the shape illustrated in Figure 3b. When having reached this position, the higher-friction impact-absorption surfaces 24a-b will start to decelerate the object's 10 motion along the fender 10. However, before having reached this position, the normal force N exerted by the fender 10 on the object 2 will have already applied a significant clockwise torque on the object, thereby counteracting the anticlockwise torque induced by the friction along the fender's longitudinal direction. Stated more briefly, the fender 10 will engage with, and decelerate, the object 2 without so strongly urging the object 2 to turn towards the wall 4. Thereby, the effect that the impact might become more severe than it would have been without a fender may be avoided, and control of the object's 2 continued motion after the impact may easier be maintained. The situation described above relates to an impact force exceeding the limit force. In the event that the impact force does not exceed the limit force, the object 2 will merely slide against the fender's 10 slide surface 22, and its motion will therefore not be significantly deflected or impaired. A typical limit force of a fender 10 may, by way of example, correspond to a line load, which is applied along a line perpendicular to the fender's 10 longitudinal direction and directed towards the fender 10 from an impact direction normal to the surface 4 to be protected, of between 40 N/dm and 4000 N/dm. A limit force in the lower part of the range may, e.g., be suited for absorbing the shock of a shopping cart impacting the wall of a self-service store, whereas a limit force in the upper part of the range may be suited for absorbing shocks of large vehicles or the like. Thanks to the low-friction slide surface 22, the fender 10 will be exposed to relatively moderate longitudinal as well as transversal stress, which will prolong its service life. The fender 10 may be manufactured by extruding the body 12 from a relatively higher-friction rubber material, and extruding the slide strip 20 as a layer of relatively lower-friction polymer, such as any suitable plastic or lower-friction rubber material, onto the body 12. The body 12 and slide strip 20 may also be co-extruded in a single extrusion step. The friction of rubber materials may be adjusted in many different ways. By way of example, it may be adjusted by using various rubber composition additives well known to those skilled in the art, such as polytetrafluoroethylene; by applying friction-increasing or friction-reducing substances, such as talcum powder, to the rubber surface; or by adjusting the hardness of the rubber. Figure 4 illustrates a second embodiment of a fender. The fender 110 is functionally equivalent to the fender 10 described with reference to Figs 2-3. However, the fender 110 differs from the fender 10 in that the fender's 110 body 112 is made of a low-friction rubber, and the outermost extremity of the resilient bladder 114 is bare, defining a low-friction slide surface 122 extending along the length of the fender 110. Two relatively higher-friction rubber strips 123a, 123b, extending along the length of the fender 110, form impact-absorption surfaces 224a, 224b for engaging with, and decelerating, an impacting object once the impact force has exceeded a limit force. Figure 5 illustrates a third embodiment of a fender. The fender 210 comprises two bladders 214a-b located on either side of a central bladder 214c. The three bladders 214a-c form, together with three arrow-shaped feet 218a-c for attaching the fender 210 to mating grooves in a surface to be protected, an integral rubber body 212. A slide strip 220, having an outer low-friction slide surface 222, covers the outer surface of the central bladder 214c. The adjoining bladders 214a-b are bare, exposing the relatively higher-friction rubber material of the body 212 to form a pair of impact-absorbing surfaces 224a-b. The slide surface 222 of the central bladder 214c forms the outermost extremity of the fender in a direction normal to the surface to be protected, whereas the impact-absorption surfaces 224a-b of the adjoining bladders 214a-b are retractedly arranged behind the outermost extremity of the low-friction slide surface 222. Thereby, a blunt object striking the fender from an impact direction normal to the surface to be protected will first engage the low-friction slide surface 222 of the central bladder 214c, and thereafter, if the impact force exceeds a limit force, engage with the relatively higher-friction impact-absorption surfaces 224a-b. Figure 6 illustrates a fourth embodiment of a fender. The fender 310 comprises a solid, relatively high-friction rubber body 312 with a recess 315 extending along the length of the body 312. The recess 315 defines, together with a strip-shaped sheet 320 of relatively low-friction rubber bridging the recess 315 and extending along the length of the fender 310, a closed bladder 314. The sheet 320 of relatively low-friction rubber bulges out from the recess 315, to form a low-friction slide surface 322 at the outermost extremity of the fender 310 in a direction normal to the surface 4 to be protected. Relatively higher-friction impact-absorption surfaces 324a-b are retracted behind the outermost extremity of the slide surface 322, so as not to be the first surfaces to engage with any blunt object impacting the fender from an direction normal to the surface 4 to be protected. The fender 310 does not have a foot; instead, it may be e.g. screwed or glued onto the surface 4 to be protected. Figs 7a-b illustrate the collision between an object and a fifth embodiment of a fender. The fender 410 differs from the fenders 10, 110, 210, 310 described hereinbefore in that the fender 410 does not comprise a bladder. However, the function of the fender 410 is similar to those previously described. A blunt object 2 approaching a surface 4 to be protected will first engage with a strip-shaped low-friction slide portion 420 of the fender, and thereafter, if the impact force of the object 2 exceeds a limit force, depress or deflect the low-friction slide portion 420 ( Figure 7b ), such that the object engages with higher-friction impact-absorption portions 424a-b of the fender, which portions 424a-b are retractedly arranged behind the outermost extremity of the surface 422 of the low-friction slide portion 420 when the fender is unloaded ( Figure 7a ). The fenders 10, 110, 210, 320, 410 described hereinbefore are particularly well suited for protecting against impacts of blunt objects moving in a plane parallel to the normal of the surface to be protected, and having a velocity a substantial component of which is directed along the longitudinal direction of the fender. To concretize and exemplify, the fenders are well suited for extending horizontally on vertical walls, for protecting against objects moving in the horizontal plane. Particular applications may comprise, e.g., protecting the walls of industrial buildings, research laboratories, parking garages, self-service stores, hospitals and loading platforms against impacting objects rolling on wheels, and protecting pier constructions against boats approaching horizontally along a water surface.

11. Use of a fender for protecting an essentially vertical surface (4) from shocks from an impact direction, the fender (10; 110; 210; 310; 410) comprising: a low-friction slide surface (22; 122; 222; 322; 422) forming the outermost extremity (26) of the fender (10; 110; 210; 310; 410) in the impact direction, so as to be the first fender portion to engage with any blunt object (2) impacting the fender (10; 110; 210; 310; 410) from the impact direction; and: a higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b; 424a-b) retractedly arranged behind the outermost extremity (26) of the low-friction slide surface (22; 122; 222; 322; 422) so as not to be the first fender portion to engage with any blunt object (2) impacting the fender (10; 110; 210; 310; 410) from the impact direction,: the low-friction slide surface (22; 122; 222; 322; 422) being configured to, when an impact force of a blunt object (2) striking the fender (10; 110; 210; 310; 410) from the impact direction exceeds a limit force, resiliently yield, such that the blunt object (2) engages the higher-friction impact-absorption surface (24a-b; 124a-b; 224a-b; 324a-b; 424a-b), the fender (10; 110; 210; 310; 410) being, when in use, mounted onto the essentially vertical surface (4) so as to protect against shocks from an object (2) moving in the horizontal plane and striking the fender (10; 110; 210; 310) from an impact direction forming an oblique angle with the essentially vertical surface to be protected.

12. Use of a fender according to claim 11 for protecting the wall of an industrial building or laboratory against impacting machines or vehicles; protecting the wall of a parking garage against impacting cars; protecting the wall of a self-service store against impacting shopping carts; protecting the wall of a hospital against impacting hospital beds; protecting a loading platform against impacting trucks; or protecting a pier construction against impacting boats. 13. Use of a fender according to any of the claims 11-12, wherein the fender (10; 110; 210; 310) is a strip-shaped fender according to any of the claims 1-10, the fender's (10; 110; 210; 310) longitudinal direction extending mainly in the horizontal direction.

2887637

Image collector device having a sealed sensor space, and method of sealing a sensor space in an image collector device

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In Figure 1 an image collector device 1 is shown. In this embodiment, the image collector device is a camera 1, having a lens 2 arranged in a lens holder 3. Further, the camera 1 has a circuit board 4 on which a sensor 5 is arranged. The circuit board is screwed onto the lens holder 3. A sensor space 6 is formed between the lens 2 and the circuit board 4. Thus, the sensor 5 is arranged in the sensor space 6. A sealing device 7 is arranged between the circuit board 4 and the lens 2. An additional seal in the form of an O-ring 8 is arranged around the lens outside the lens holder 3. The sealing device 7 may be seen more clearly in Figure 4, showing the sealing device 7 separately. The sealing device 7 has a first end 9 and a second end 10. A circumferential wall 11 extends between the first end 9 and the second end 10. In the embodiments shown, the circumferential wall 11 is pleated and may be referred to as bellows-shaped. At the first end 9, the sealing device 7 has an end wall 12, in which an opening 13 is formed. In this embodiment, the entire sealing device is flexible, but at least an end wall portion 14 surrounding the opening 13 should be flexible. The sealing device 7 is flexible enough to be compressible to fit in the sensor space, as will be discussed further below, and provides sufficient resilience to spring back when compressed, thus allowing a tight seal against the circuit board 4 and the lens holder 3, respectively. The sealing device may be moulded from silicone, by moulding processes such as injection moulding or compression moulding. The silicone may be hardened or otherwise treated such that it does not emit gasses once the sealing device 7 has been installed in the camera 1. Such gasses could else be harmful to the sensor 5. In the embodiment shown, the sealing device 7 has a generally square cross-sectional shape with rounded corners. The opening 13 is circular to fit around a circular cross-section of the lens 2. With reference to Figure 2, and to the closer detail view in Figure 3, the arrangement of the sealing device 7 for sealing the sensor space 6 will be described further. In the embodiment shown, the lens 2 has an outer thread 15, and the lens holder 3 has an inner thread 16. The lens 2 may hereby be threadedly engaged in the lens holder 3. When mounting the camera components, the sealing device 7 is placed inside the lens holder 3 with the first end 9 facing the threaded part of the lens holder, where the lens 2 is to be inserted, and with the second end 10 facing the opposite part of the lens holder 3, where the circuit board 4 is to be attached. The end wall 12 of the sealing device 7 is placed in contact with an abutment shoulder 17 of the lens holder 3. Then, the lens 2 is screwed into the lens holder 3. When the inner end 18 of the lens 2 has passed the abutment shoulder 17, the lens 2 also starts to be inserted into the opening 13 in the end wall 12 of the sealing device 7. When the outer thread 15 of the lens reaches the opening 13, the lens 2 starts to be threaded into the opening. When the lens 2 has been screwed into the lens holder 3 to a desired depth, the end wall portion 14 surrounding the opening 13 is caught between two adjacent flanks 19, 20 of the outer thread. Particles possibly sticking on the thread 15 are pushed away by the end wall portion 14 surrounding the opening 13, and are hence prevented from entering the sensor space. The flexibility of the end wall portion 14 surrounding the opening 13 enables a good seal against the lens 2. The generally square cross-sectional shape of the sealing device 7 in combination with a similarly square cross-sectional shape of the inside of the lens holder beyond the abutment shoulder 17 makes it possible to prevent the sealing device 7 from rotating. The sealing device 7 may in this manner also be prevented from twisting. The circuit board 4 with the sensor is then screwed onto the lens holder 3, with the sensor 5 placed such that it becomes surrounded by the circumferential wall 11. If extended to its full length, the sealing device 7 would be longer than the distance between the abutment shoulder 17 and the circuit board. Therefore, when the circuit board 4 is attached to the lens holder 3, the sealing device 7 is compressed between the abutment shoulder 17 of the lens holder 3 and the circuit board 4. Because of the resilience of the circumferential wall 11 a tight seal of the sensor space 6 may be achieved. The desired resilience may be achieved by a suitable combination of a resilient and flexible material and an appropriate shape of the circumferential wall 11. The resilience should be such that the sealing device 7 may be compressed to fit in the sensor space 6 and such that it springs back to extend the whole length of the sensor space, and to abut tightly against the circuit board 4 and the lens holder 3. When the sealing device 7 is compressed between the circuit board 4 and the abutment shoulder an axial seal of the sensor space is achieved. Further, the arrangement of the flexible end wall portion 14 surrounding the opening 13 between two adjacent flanks 19, 20 of the outer thread 15 of the lens ensures a radial seal. It will be appreciated that a person skilled in the art can modify the above described embodiments in many ways and still use the advantages of the invention as shown in the embodiments above. As an example, the lens holder need not be of the type shown on the drawings, where the circuit board is attached directly to the lens holder. Instead, the lens could be screwed into a shorter lens holder and then be inserted into a housing to which the circuit board is attached. In such case, the end wall of the sealing device could be placed in abutment with a suitable wall portion or abutment shoulder of the housing. The lens holder need not necessarily be threaded, but could be slidingly inserted in the lens holder. The sealing device may be made from silicone or from another elastomeric material such as polyurethane or other thermoplastic elastomer. The material may be treated in order to prevent it from emitting gasses that could be harmful to the sensor. For instance, in the case of silicone, the material may be double-hardened. The sealing device may be made from just one material or could be made from a combination of materials. For instance, the sealing device may be made from metallic end portions, with a flexible circumferential end portion arranged there between, and with a flexible end wall arranged at the first end. Further, the sealing device could be made from mainly an elastomeric material with a relatively low hardness, and with a harder reinforcing ring arranged or embedded at each end. The material of the circumferential wall may be chosen such that it is impermeable to dust and other particles, to moisture, and to light, thus protecting the sensor space, and the sensor arranged therein, from these potentially harmful factors. The opening in the end wall may have a diameter that is slightly smaller than the minor diameter of the threaded portion of the lens, such that the flexibility of the end wall portion surrounding the opening ensures a tight fit around the lens. The circumferential wall of the sealing device could have other shapes, apart from the bellows shape shown in the exemplifying figures. For instance, the circumferential wall could be made with straight, fairly non-flexible wall portions between highly flexible wall portions or beads. Further, the sealing device could have another cross-sectional shape, such as circular. If the cross-sectional shape is polygonal, the corners may make it possible to prevent the sealing device from rotating or twisting when a lens is screwed into the opening in the end wall if the walls of the lens holder or housing have corresponding surfaces against which the corners may abut. The sealing device may be made by moulding, e.g., injection moulding or compression moulding. In the embodiment shown, the sealing device is simply compressed between the lens holder and the circuit board. In some instances it may be desirable to fix one or both ends of the sealing device to the lens holder and circuit board, respectively, by glue or other fixing means. In the description above, reference has been made to the image collector device as a camera. The camera may be a camera employing visible light or IR light. Further, the camera may be a thermal camera. Still further, the image collector device may be of other types, such as an IR detector.

1. An image collector device comprising: a sensor (5) arranged on a circuit board (4),: a lens (2), and: a lens holder (3),: said lens (2) being mounted in said lens holder (3),: wherein a sensor space (6), in which said sensor (5) is arranged, is formed between said lens (2) and said circuit board (4),: saidimage collector device (1) further comprising a sealing device (7) comprising a first end (9), a second end (10), a resilient circumferential wall portion (11) extending between said first and second ends (9, 10), and an end wall (12) arranged at said first end (9), an opening (13) being formed in said end wall (12), wherein an end wall portion (14) surrounding said opening (13) is flexible, wherein said sealing device (7) is arranged in said sensor space (6), said circumferential wall portion (11) of said sealing device (7) being arranged around said sensor (5) and sealing said sensor space (6),: wherein said circumferential wall portion (11) is compressed in a direction along said sensor space (6) between said lens (2) and said circuit board (4), and: wherein said opening (13) in said end wall (12)sealingly encloses said lens (2).

2. The image collector device according to claim 1, wherein said lens (2) comprises an outer thread (15), and said lens holder (3) comprises an inner thread (16), said lens (2) being threadedly engaged in said lens holder (3), and wherein said end wall portion (14) surrounding said opening (13) is arranged between two adjacent flanks (19, 20) of said outer thread (15). 3. The image collector device according to claim 1 or 2, wherein said lens (2) at least in a portion enclosed by said opening (13) in said end wall has a circular cross-sectional shape, and wherein said opening (13) in said end wall (12) is circular. 4. The image collector device according to any one of the preceding claims, wherein said circumferential wall portion (11) is pleated. 5. The image collector according to any one of the preceding claims, wherein said circumferential wall portion (11) is shaped as a bellows. 6. The image collector device according to any one of the preceding claims, wherein said circumferential wall portion (11) has a generally rectangular cross-sectional shape. 7. The image collector device according to any one of the preceding claims, wherein said sealing device (7) comprises an elastomeric material. 8. The image collector device according to any one of the preceding claims, wherein said sealing device (7) is moulded from an elastomeric material. 9. The image collector device according to any one of the preceding claims, wherein said elastomeric material comprises silicone rubber. 10. The image collector device according to any one of the preceding claims, wherein said sealing device (7) is arranged to seal said sensor space (6) against particles and light.

2887637

Image collector device having a sealed sensor space, and method of sealing a sensor space in an image collector device

Based on the following detailed description of an invention, generate the patent claims. There should be 2 claims in total. The first, independent claim is given and the remaining 1 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In Figure 1 an image collector device 1 is shown. In this embodiment, the image collector device is a camera 1, having a lens 2 arranged in a lens holder 3. Further, the camera 1 has a circuit board 4 on which a sensor 5 is arranged. The circuit board is screwed onto the lens holder 3. A sensor space 6 is formed between the lens 2 and the circuit board 4. Thus, the sensor 5 is arranged in the sensor space 6. A sealing device 7 is arranged between the circuit board 4 and the lens 2. An additional seal in the form of an O-ring 8 is arranged around the lens outside the lens holder 3. The sealing device 7 may be seen more clearly in Figure 4, showing the sealing device 7 separately. The sealing device 7 has a first end 9 and a second end 10. A circumferential wall 11 extends between the first end 9 and the second end 10. In the embodiments shown, the circumferential wall 11 is pleated and may be referred to as bellows-shaped. At the first end 9, the sealing device 7 has an end wall 12, in which an opening 13 is formed. In this embodiment, the entire sealing device is flexible, but at least an end wall portion 14 surrounding the opening 13 should be flexible. The sealing device 7 is flexible enough to be compressible to fit in the sensor space, as will be discussed further below, and provides sufficient resilience to spring back when compressed, thus allowing a tight seal against the circuit board 4 and the lens holder 3, respectively. The sealing device may be moulded from silicone, by moulding processes such as injection moulding or compression moulding. The silicone may be hardened or otherwise treated such that it does not emit gasses once the sealing device 7 has been installed in the camera 1. Such gasses could else be harmful to the sensor 5. In the embodiment shown, the sealing device 7 has a generally square cross-sectional shape with rounded corners. The opening 13 is circular to fit around a circular cross-section of the lens 2. With reference to Figure 2, and to the closer detail view in Figure 3, the arrangement of the sealing device 7 for sealing the sensor space 6 will be described further. In the embodiment shown, the lens 2 has an outer thread 15, and the lens holder 3 has an inner thread 16. The lens 2 may hereby be threadedly engaged in the lens holder 3. When mounting the camera components, the sealing device 7 is placed inside the lens holder 3 with the first end 9 facing the threaded part of the lens holder, where the lens 2 is to be inserted, and with the second end 10 facing the opposite part of the lens holder 3, where the circuit board 4 is to be attached. The end wall 12 of the sealing device 7 is placed in contact with an abutment shoulder 17 of the lens holder 3. Then, the lens 2 is screwed into the lens holder 3. When the inner end 18 of the lens 2 has passed the abutment shoulder 17, the lens 2 also starts to be inserted into the opening 13 in the end wall 12 of the sealing device 7. When the outer thread 15 of the lens reaches the opening 13, the lens 2 starts to be threaded into the opening. When the lens 2 has been screwed into the lens holder 3 to a desired depth, the end wall portion 14 surrounding the opening 13 is caught between two adjacent flanks 19, 20 of the outer thread. Particles possibly sticking on the thread 15 are pushed away by the end wall portion 14 surrounding the opening 13, and are hence prevented from entering the sensor space. The flexibility of the end wall portion 14 surrounding the opening 13 enables a good seal against the lens 2. The generally square cross-sectional shape of the sealing device 7 in combination with a similarly square cross-sectional shape of the inside of the lens holder beyond the abutment shoulder 17 makes it possible to prevent the sealing device 7 from rotating. The sealing device 7 may in this manner also be prevented from twisting. The circuit board 4 with the sensor is then screwed onto the lens holder 3, with the sensor 5 placed such that it becomes surrounded by the circumferential wall 11. If extended to its full length, the sealing device 7 would be longer than the distance between the abutment shoulder 17 and the circuit board. Therefore, when the circuit board 4 is attached to the lens holder 3, the sealing device 7 is compressed between the abutment shoulder 17 of the lens holder 3 and the circuit board 4. Because of the resilience of the circumferential wall 11 a tight seal of the sensor space 6 may be achieved. The desired resilience may be achieved by a suitable combination of a resilient and flexible material and an appropriate shape of the circumferential wall 11. The resilience should be such that the sealing device 7 may be compressed to fit in the sensor space 6 and such that it springs back to extend the whole length of the sensor space, and to abut tightly against the circuit board 4 and the lens holder 3. When the sealing device 7 is compressed between the circuit board 4 and the abutment shoulder an axial seal of the sensor space is achieved. Further, the arrangement of the flexible end wall portion 14 surrounding the opening 13 between two adjacent flanks 19, 20 of the outer thread 15 of the lens ensures a radial seal. It will be appreciated that a person skilled in the art can modify the above described embodiments in many ways and still use the advantages of the invention as shown in the embodiments above. As an example, the lens holder need not be of the type shown on the drawings, where the circuit board is attached directly to the lens holder. Instead, the lens could be screwed into a shorter lens holder and then be inserted into a housing to which the circuit board is attached. In such case, the end wall of the sealing device could be placed in abutment with a suitable wall portion or abutment shoulder of the housing. The lens holder need not necessarily be threaded, but could be slidingly inserted in the lens holder. The sealing device may be made from silicone or from another elastomeric material such as polyurethane or other thermoplastic elastomer. The material may be treated in order to prevent it from emitting gasses that could be harmful to the sensor. For instance, in the case of silicone, the material may be double-hardened. The sealing device may be made from just one material or could be made from a combination of materials. For instance, the sealing device may be made from metallic end portions, with a flexible circumferential end portion arranged there between, and with a flexible end wall arranged at the first end. Further, the sealing device could be made from mainly an elastomeric material with a relatively low hardness, and with a harder reinforcing ring arranged or embedded at each end. The material of the circumferential wall may be chosen such that it is impermeable to dust and other particles, to moisture, and to light, thus protecting the sensor space, and the sensor arranged therein, from these potentially harmful factors. The opening in the end wall may have a diameter that is slightly smaller than the minor diameter of the threaded portion of the lens, such that the flexibility of the end wall portion surrounding the opening ensures a tight fit around the lens. The circumferential wall of the sealing device could have other shapes, apart from the bellows shape shown in the exemplifying figures. For instance, the circumferential wall could be made with straight, fairly non-flexible wall portions between highly flexible wall portions or beads. Further, the sealing device could have another cross-sectional shape, such as circular. If the cross-sectional shape is polygonal, the corners may make it possible to prevent the sealing device from rotating or twisting when a lens is screwed into the opening in the end wall if the walls of the lens holder or housing have corresponding surfaces against which the corners may abut. The sealing device may be made by moulding, e.g., injection moulding or compression moulding. In the embodiment shown, the sealing device is simply compressed between the lens holder and the circuit board. In some instances it may be desirable to fix one or both ends of the sealing device to the lens holder and circuit board, respectively, by glue or other fixing means. In the description above, reference has been made to the image collector device as a camera. The camera may be a camera employing visible light or IR light. Further, the camera may be a thermal camera. Still further, the image collector device may be of other types, such as an IR detector.

11. A method of sealing a sensor space in an image collector device (1), said sensor space (6) being defined between a lens (2) arranged in a lens holder (3), and a circuit board (4) on which a sensor (5) is arranged, said method comprising the steps of: arranging a sealing device (7) between said lens (2) and said circuit board (4), said sealing device (7) having a first end (9), a second end (10), a resilient circumferential wall (11 extending between said first and second ends (9, 10), and an end wall (12) at said first end (9), said end wall (12) having an opening (13), an end wall portion (14) surrounding said opening (13) being flexible,: arranging said opening (13) in said end wall (12) around said lens (2) such that it sealingly encloses said lens (2),: arranging said circumferential wall (11) around said sensor (5), and compressing said sealing device (7) between said lens holder (3) and said circuit board (4), such that said circumferential wall (11) flexes, pressing said first end (9) against said lens holder (3), and pressing said second end (10) against said circuit board (4), thereby sealing said sensor space (6).

12. The method according to claim 11, further comprising the steps of threadedly engaging said lens (2) in said lens holder (3), and arranging said end wall portion (14) surrounding said opening (13) between two adjacent flanks (19, 20) of an outer thread (15) of said lens (2), thereby forming a radial seal around said lens (2).

2886797

A hollow cooled gas turbine rotor blade or guide vane, wherein the cooling cavities comprise pins interconnected with ribs

Based on the following detailed description of an invention, generate the patent claims. There should be 11 claims in total. The first, independent claim is given and the remaining 10 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

In connection with Figure 1, a cooling channel 100a is provided in a rotor blade or guide vane (in the following, for simplicity, is spoken by a rotor blade) of the gas turbine to send a cooling medium 130 therein. The inner wall of the flow cooling path 100 is covered with the heat exchange walls 110a and 111 a in which the pins (see Figure 2 ) are provided towards the inner side of the cooling channel 100a. The structure of the heat exchange walls 110a and 111 a can be the same as the structure of any other cooling path 101 a, 102a. When the gas turbine is operated, a high temperature gas 120 is blown towards the rotor blade, and the rotor blade is rotated around a rotation shaft (not shown). The cooling medium 130 is supplied from the base portion of the rotor blade into the cooling channel 100a. The cooling medium 130 takes away the heat from the rotor blade and is discharged to a path 131 through which the high temperature gas 120 flows. The heat exchange walls 110a, 111 a are provided on the inner wall of the cooling channel 100a to efficiently transfer the heat of the rotor blade to the cooling medium 130. Since the rotor blade is efficiently cooled by the heat exchange along the channels 100a, 101 a, 102a, it is preferably used in the gas turbine in which the higher temperature gas 120 is used. Or, the flow rate of the cooling medium 130 is little as compared with the gas turbine to which the temperature of the combustion gas 120 is equal. Figure 2 shows a cross section of the cooling channel 100 in the region of the trailing edge of the rotor vane or guide vane comprising pins 200 and ribs 300. Rib height h is adapted to pin height, wherein rib height is adapted to certain fraction of pin height. Rib width w at the bottom 201 (see Figure 4 ) is adapted to castability requirement, wherein the width should be larger than 60% of the height. When the height of the rib is low, turbulence generated by to top portion of the rib reaches the base wall 110 and bottom wall 111 plate surfaces to promote heat exchange. The wall 110 and 111 correspond to the pressure side and suction side of the rotor blade or guide vane. This embodiment is effective in case the pin has a low thermal conductivity. The reason of this result is because the base plate of the channel can be cooled more efficiently by cooling the surface of the base plate directly rather than cooling the side face of the pin of the low thermal conductivity. When the diameter of round rib is small, the projection area in the direction of the cooling air flow decreases so that the pressure loss can be suppressed. The pins 200 are radially or quasi-radially spaced along the channel 100 with respect to the flow direction of cooling medium 130 and extend laterally between the flowed surfaces 110, 111. Each of the pins 200 is transversely disposed to the flow direction of the cooling fluid along the trailing edge of the rotor or guide vane. In this way, each of the pins 200 provides an obstruction in the flow exiting of the flowed channel 100. Each of the pins 200 is circular in cross section and equal in radial dimension. It should be apparent that a mixture of pins of various shapes and sizes may be used. Figure 3 shows a plan view of the pins 200 and ribs 300 structure along the cooling channel 100 resp. 100a (see Figure 1 ). The rib 300 is disposed along the cooling channel 100 between the spins configuration forming an alveolar or quasi-alveolar structure. This structure of the ribs defines an interruption in each of the cooled channels 100. The interruptions permit cross-flow within cooling channel 100. The cross-flow ensures that, in the event that one of the first portions of cooled channels becomes blocked, cooling fluid will continue to be distributed over the adjacent extent of the channel space. The cross-flow through the interruption provides a means to backfill each of the second plurality of subchannels (see Figure 1 ) which is downstream of a blocked first sub-channel of the airfoil. In addition, each of the pins 200 provides an obstruction within the channel which encourages cross flow between channels and facilitates distribution of cooling flow to the whole extension of the channel. Where the cooling channel 100 is sufficiently narrow, ribs 300 are not required anymore. The higher flow velocity provides enough heat transfer coefficient. Figure 4 shows a section of a trapezoidal rib 300a enclosing the width w and height h configuration. Figure 5 shows a section of a rib between two pins with an inclined surface 300b. According to Figure 6, the flow of the hot gases 130 is shown by an arrow (see Figure 3 ), whereby the direction of flow is also predetermined. According to Figure 6, a vortex generator 300c essentially comprises three triangular surfaces around which flow occurs. These are a top surface 310 and two side surfaces 311 and 313. In their longitudinal extent, these surfaces run at certain angles in the direction of flow. The side walls of the vortex generators 300c, which preferably consist of right-angled triangles, are fixed, preferably gastight, with their longitudinal sides to the channel or duct wall 110. They are orientated in such a way that they form a face at their narrow sides while enclosing an acute or arrow angle α. The face is embodied as a sharp connecting edge 316 and is perpendicular to every duct wall 110 with which the side surfaces are flush. The two side surfaces 311, 313 enclosing the arrow angle α are symmetrical in form, size and orientation and they are arranged on both sides of a symmetry axis 317 which is equi-directional to the duct axis. With a very narrow edge 315 running transversely to the duct through which flow occurs, the top surface 310 bears against the same duct wall 110 as the side surfaces 311, 313. Its longitudinally directed edges 312, 314 are flush with the longitudinally directed edges of the side surfaces 311, 313 projecting into the flow duct. The top surface 310 runs at a setting angle γ to the duct wall 110, the longitudinal edges 312, 314 of which form a point 318 together with the connecting edge 316. The vortex generator 300c can of course also be provided with a base surface with which it is fastened to the duct wall 110 in a suitable manner. However, such a base surface is in no way connected with the mode of operation of the element. The mode of operation of the vortex generator 300c is as follows: when flow occurs around the edges 312 and 314, the main flow is converted into a pair of oppositely directed vortices, as shown schematically in the figures. The vortex axes lie in the axis of the main flow. The swirl number and the location of the vortex breakdown, provided the latter is intended, are determined by corresponding selection of the setting angle γ and the arrow angle α. The vortex intensity and the swirl number increase as the angles increase, and the location of the swirl breakdown is displaced upstream right into the region of the vortex generator 300c itself. Depending on the operational use, these two angles α and γ are predetermined by design conditions and by the process itself. This vortex generator need only be adapted in respect of length, width and height. In Figure 6, the connecting edge 316 of the two side surfaces 311, 313 forms the downstream edge of the vortex generator 300c. The edge 315 of the top surface 310 running transversely to the duct through which flow occurs is therefore the edge acted upon first by the duct flow. #### List Of References Numerous - 100: Flow cooling path, channel - 100a: Channel for cooling fluid within a rotor blade or guide vane - 101a: Channel for cooling fluid within a rotor blade or guide vane - 102a: Channel for cooling fluid within a rotor blade or guide vane - 110: Pressure side, flowed surface - 111: Suction side, flowed surface - 120: Turbine working gas - 130: Cooling medium or fluid - 131: Discharge of cooling fluid - 200: Pins - 300: Ribs - 300a: Rib with a trapezoidal form - 300b: Rib with an inclined surface - 300c: Rib with a vortex generator function - 310: Top surface - 311: Side surface - 312: Longitudinally directed edge - 313: Side surface - 314: Longitudinally directed edge - 315: Transversally directed edge - 316: Connecting edge - 317: Symmetry axis - 318: Converging point - α: Arrow angle - γ: Setting angle - w: Width of the rib - h: Height of the rib

1. A rotor blade or guide vane airfoil for a gas turbine engine having a longitudinal axis and a source of cooling fluid, the airfoil having a pressure wall, a suction wall, a leading edge, a trailing edge and at least one cooling fluid flow passage, wherein the cooling fluid flow passage is in fluid communication with the source of cooling fluid and providing means for directing cooling fluid at least to the trailing edge, wherein the cooling fluid flow passage including: one or more axially extending walls, each of the walls extending laterally between the pressure wall and suction wall (110, 111), one or more of walls being spaced within the cooling fluid flow path such that adjacent pairs of walls define a channel between the pressure wall and suction wall, the spacing between the adjacent walls comprising in flow direction of the cooling fluid a structure of regularly or irregularly disposed pins (200) and ribs (300), wherein the pins holistic or approximately cover the axial height of the fluid flow passage, the ribs have a deeper level with respect to being actively connected pins, and the ribs establish a bridge-like connection between each of adjacent pins.

2. The rotor blade or guide vane according to claim 1, characterized in that at least one cooling flow passage between adjacent pairs of walls being radially or quasi-radially spaced within the rotor blade or guide vane compared to the longitudinal axis of the gas turbine, wherein the cooling flow passage comprising in flow direction of the cooling fluid a structure of regularly or irregularly disposed pins and ribs, the pins holistic or approximately cover the width of the cooling flow passage, the ribs have a deeper level with respect to being actively connected pins, and the ribs establish a bridge-like connection between each of adjacent pins. 3. The rotor blade or guide vane airfoil according to claim 1 or 2, characterized in that the ribs establish a bridge-like connection between each of two adjacent pins. 4. The rotor blade or guide vane airfoil according to claim 1 or 2, characterized in that the rib-related bridge-like connection between each adjacent ribs extends along at least one portion of the length of the channel in flow direction of the cooling fluid. 5. The rotor blade or guide vane airfoil according to claim 4, characterized in that the rib-related bridge-like connection between each adjacent ribs extends only along the first flow-applied portion of the length of the channel in flow direction of the cooling fluid. 6. The rotor blade or guide vane airfoil according to claim 1 or 2, characterized in that the rib having a square or rectangular or trapezoidal cross-section. 7. The rotor blade or guide vane airfoil according to claim 6, characterized in that the leading face of the rib with respect to the flow direction of the cooling fluid comprising an inclined or tapered surface. 8. The rotor blade or guide vane airfoil according to claim 1 or 2, characterized in that the trapezoidal cross-section having a top width (w) that is larger than 60% of the height (h). 9. The rotor blade or guide vane airfoil according to claim 1 or 2, characterized in that the rib between each two adjacent spins consists of at least one vortex generator having a three triangular surfaces. 10. The rotor blade or guide vane airfoil according to one of claims 1 to 9, characterized in that the pin span-wise pitch is decreased where the channel height and the pin cross section gets smaller. 11. The rotor blade or guide vane airfoil according to one of claims 1 to 10, characterized in that the span-wise pitch of the pin with a larger cross-section is equal or corresponds to a multiple of the span-wise pitch of the downstream situated pins with a smaller cross-section.

2886824

Improved turbocompound scheme, in particular in the field of industrial vehicles

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

According to figure 1 a combustion engine E, for example Diesel type, has an intake manifold In and an exhaust manifold Ex. A turbocharger unit T-C defines a first supercharging stage, having the first turbine T operatively connected immediately downstream of the exhaust manifold. The compressor C, driven by the first turbine T, sucks fresh air from the ambient, compresses it, while the intercooler unit CAC cools the compressed air before entering into the intake manifold In. An EGR system and a wastegate valve WG can be implemented. In addition, the turbine T can be variable geometry type. A second turbine PT is arranged downstream said first turbine T along the exhaust line, according the flow of the exhaust gasses. Also the power turbine can be variable geometry type. Such second turbine, is hereinafter called as power turbine, being coupled with the engine crankshaft K through a clutch CL and gears G for adapting the power turbine speed with the engine speed. A first electric motor/generator EM1 is operatively coupled with the first supercharging stage. For example, the rotor of the electric motor/generator EM1 can have two opposite accessible ends, one of them axially connected with the shaft of the first turbine T and the other with the shaft of the compressor C. The power turbine is stably operatively paired with a second electric motor/generator EM2. Both the electric motor/generators EM1 and EM2 are electrically connected between each other via suitable power electronics PE, namely inverters/rectifiers and the like, and their functioning is controlled by control means CTRL. Said control means CTRL can also control the operation of the clutch CL. Preferably, at high engine speeds and loads the first electric motor/generator EM1 works as a generator for reducing the engine boost and thus the compressor speed, thus the electric energy produced by EM1 is addressed to the second electric motor/generator EM2, that cooperates - as a motor - with the power turbine in helping the engine, thus the fuel supply can be reduced. In particular the control means can be adapted to reduce automatically the fuel supplied - with respect to a corresponding position of the accelerator pedal - on the basis of the mechanical power provided by the second electric motor/generator EM2. Preferably, at low engine speed and loads, and during load steps in fired mode, when the engine needs more boost from the compressor, the second electric motor/generator works as a generator, being coupled with the crank train, while the electric energy produced by it is addressed to the first electric motor/generator, that cooperates - as a motor - with the first turbine in driving the compressor. Preferably at low and moderate engine speeds in engine brake mode, similarly as above, when the engine needs more boost from the compressor, the second electric motor/generator works as a generator, being coupled with the crank train, while the electric energy produced by it is addressed to the first electric motor/generator, that cooperates - as a motor - with the first turbine in driving the compressor. Preferably at high engine speeds in engine brake mode, the power turbine is decoupled from the crank train by opening the respective clutch. To avoid the power turbine over speeding, the second electric motor/generator works as a generator, i.e. braking the power turbine, while the electric energy produced by it is addressed to the first electric motor/generator that cooperates - as a motor - with the first turbine in driving the compressor. Thanks to the present invention, the electric energy in this system is produced and consumed without storing it. This implies a faster electric energy transfer and a better efficiency. Amounts of power needed or supplied by external devices however can be transferred to/from loads/storage means/generators. According to another embodiment of the present invention, the motor/generators can completely replace the well known alternator driven by the classical belt. Thus, the energy stored in the classical lead battery to restart the combustion engine and for powering the onboard auxiliary services can be supplied by said motor/generators. Similarly, according to another embodiment of the present invention, the second motor/generator can completely replace the well known electric starting motor by rendering the classical geared starter motor obsolete. Thus, not only the fuel consumption is reduced, but also the load response and engine brake capability of the engine system are improved. According to a preferred embodiment of the invention, a flap can be arranged downstream of said power turbine PT along said exhaust line. During engine braking operation, namely when the fuel supply is cut and the engine is motored by the vehicle inertia, the flap can be closed in order to develop a backpressure, which increases the pumping work of the combustion engine and thus the engine braking effect. The control of the electric motor/generators and optionally of the clutch, is carried out by control means that can be integrated within the engine control unit ECU or in another specific control unit. This invention can be implemented advantageously in a computer program comprising program code means for performing one or more steps of such method, when such program is run on a computer. For this reason the patent shall also cover such computer program and the computer-readable medium that comprises a recorded message, such computer-readable medium comprising the program code means for performing one or more steps of such method, when such program is run on a computer. Many changes, modifications, variations and other uses and applications of the subject invention will become apparent to those skilled in the art after considering the specification and the accompanying drawings which disclose preferred embodiments thereof. All such changes, modifications, variations and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by this invention. Further implementation details will not be described, as the man skilled in the art is able to carry out the invention starting from the teaching of the above description.

1. Improved turbocompound system, in particular in the field of industrial vehicles, comprising a combustion engine (E) having - a crankshaft (K), - a first turbocharger system, wherein a first turbine (T) drives a fresh air compressor (C), - a power turbine (PT) arranged downstream of said first turbine (T), operatively coupled with said crankshaft (K) through a clutch,: wherein a first electric motor/generator (EM1) is stably coupled with said turbocharger system (T, C), a second electric motor/generator (EM2) is stably coupled with said power turbine (PT), the first and second electric motor/generators (EM1, EM2) being electrically interconnected, and wherein control means (CTRL) are adapted to control said electric motor/generators (EM1, EM2) as motor or generator and adapted to control one in an opposite way with respect to the other, so that the electric energy produced by one is consumed by the other and vice versa.

2. Turbocompound system according to claim 1, wherein said control means (CTRL) are adapted to control said electric motor/generators (EM1, EM2) according to said opposite way, in fired condition and/or in motored and engine brake conditions, in transient and/or in stationary operations of the engine system. 3. Turbocompound system according to claims 1 or 2, wherein said control means (CTRL) are able - to check a condition where it is required to increase the compressor (C) speed and: when said condition is verified said control means are adapted - to control said first electric motor/generator (EM1) to work as a motor and said second electric motor/generator (EM2) to work as a generator and - to command the closing of said clutch (CL). 4. Turbocharger according to claim 3, wherein said control means (CTRL) are adapted to perform said steps when at least one of the following further conditions are verified: - the combustion engine is fired or - the combustion engine is motored or in low or moderate speed of braking condition. 5. Turbocompound system according to any of the previous claims 2 - 4, wherein said control means (CTRL) are able to check the following conditions: - the combustion engine is fired and it is required to decrease the compressor (C) speed and: when said conditions are verified said control means are adapted to control said first electric motor/generator (EM1) to work as a generator and said second electric motor/generator (EM2) to work as a motor and to command a closing of said clutch in order to supplement the crankshaft (K). 6. Turbocompound system according to any of the previous claims 2 - 4, wherein said control means (CTRL) are able to check the following conditions: - high engine speed during engine braking and: when said conditions are verified said control means are adapted to command the opening of said clutch and to control said second electric motor/generator (EM2) to work as a generator by liming the power turbine speed and to control said first electric motor/generator (EM1) to work as a motor to increase the compressor speed, in order to increase the engine braking torque. 7. Turbocompound system according to claim 5, wherein, said control means (CTRL) are adapted to reduce automatically the fuel supplied - with respect to a corresponding position of an accelerator pedal - on the basis of a mechanical power provided by said second electric motor/generator (EM2). 8. Industrial vehicle comprising a turbocompound scheme, according to any of the previous claims from 1 to 7.

2886824

Improved turbocompound scheme, in particular in the field of industrial vehicles

Based on the following detailed description of an invention, generate the patent claims. There should be 9 claims in total. The first, independent claim is given and the remaining 8 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

According to figure 1 a combustion engine E, for example Diesel type, has an intake manifold In and an exhaust manifold Ex. A turbocharger unit T-C defines a first supercharging stage, having the first turbine T operatively connected immediately downstream of the exhaust manifold. The compressor C, driven by the first turbine T, sucks fresh air from the ambient, compresses it, while the intercooler unit CAC cools the compressed air before entering into the intake manifold In. An EGR system and a wastegate valve WG can be implemented. In addition, the turbine T can be variable geometry type. A second turbine PT is arranged downstream said first turbine T along the exhaust line, according the flow of the exhaust gasses. Also the power turbine can be variable geometry type. Such second turbine, is hereinafter called as power turbine, being coupled with the engine crankshaft K through a clutch CL and gears G for adapting the power turbine speed with the engine speed. A first electric motor/generator EM1 is operatively coupled with the first supercharging stage. For example, the rotor of the electric motor/generator EM1 can have two opposite accessible ends, one of them axially connected with the shaft of the first turbine T and the other with the shaft of the compressor C. The power turbine is stably operatively paired with a second electric motor/generator EM2. Both the electric motor/generators EM1 and EM2 are electrically connected between each other via suitable power electronics PE, namely inverters/rectifiers and the like, and their functioning is controlled by control means CTRL. Said control means CTRL can also control the operation of the clutch CL. Preferably, at high engine speeds and loads the first electric motor/generator EM1 works as a generator for reducing the engine boost and thus the compressor speed, thus the electric energy produced by EM1 is addressed to the second electric motor/generator EM2, that cooperates - as a motor - with the power turbine in helping the engine, thus the fuel supply can be reduced. In particular the control means can be adapted to reduce automatically the fuel supplied - with respect to a corresponding position of the accelerator pedal - on the basis of the mechanical power provided by the second electric motor/generator EM2. Preferably, at low engine speed and loads, and during load steps in fired mode, when the engine needs more boost from the compressor, the second electric motor/generator works as a generator, being coupled with the crank train, while the electric energy produced by it is addressed to the first electric motor/generator, that cooperates - as a motor - with the first turbine in driving the compressor. Preferably at low and moderate engine speeds in engine brake mode, similarly as above, when the engine needs more boost from the compressor, the second electric motor/generator works as a generator, being coupled with the crank train, while the electric energy produced by it is addressed to the first electric motor/generator, that cooperates - as a motor - with the first turbine in driving the compressor. Preferably at high engine speeds in engine brake mode, the power turbine is decoupled from the crank train by opening the respective clutch. To avoid the power turbine over speeding, the second electric motor/generator works as a generator, i.e. braking the power turbine, while the electric energy produced by it is addressed to the first electric motor/generator that cooperates - as a motor - with the first turbine in driving the compressor. Thanks to the present invention, the electric energy in this system is produced and consumed without storing it. This implies a faster electric energy transfer and a better efficiency. Amounts of power needed or supplied by external devices however can be transferred to/from loads/storage means/generators. According to another embodiment of the present invention, the motor/generators can completely replace the well known alternator driven by the classical belt. Thus, the energy stored in the classical lead battery to restart the combustion engine and for powering the onboard auxiliary services can be supplied by said motor/generators. Similarly, according to another embodiment of the present invention, the second motor/generator can completely replace the well known electric starting motor by rendering the classical geared starter motor obsolete. Thus, not only the fuel consumption is reduced, but also the load response and engine brake capability of the engine system are improved. According to a preferred embodiment of the invention, a flap can be arranged downstream of said power turbine PT along said exhaust line. During engine braking operation, namely when the fuel supply is cut and the engine is motored by the vehicle inertia, the flap can be closed in order to develop a backpressure, which increases the pumping work of the combustion engine and thus the engine braking effect. The control of the electric motor/generators and optionally of the clutch, is carried out by control means that can be integrated within the engine control unit ECU or in another specific control unit. This invention can be implemented advantageously in a computer program comprising program code means for performing one or more steps of such method, when such program is run on a computer. For this reason the patent shall also cover such computer program and the computer-readable medium that comprises a recorded message, such computer-readable medium comprising the program code means for performing one or more steps of such method, when such program is run on a computer. Many changes, modifications, variations and other uses and applications of the subject invention will become apparent to those skilled in the art after considering the specification and the accompanying drawings which disclose preferred embodiments thereof. All such changes, modifications, variations and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by this invention. Further implementation details will not be described, as the man skilled in the art is able to carry out the invention starting from the teaching of the above description.

9. Method of controlling a turbocompound system, in particular in the field of industrial vehicles, the turbocompound system comprising a combustion engine (E) having a crankshaft (K), a first turbocharger system, wherein a first turbine (T) drives a fresh air compressor (C), a power turbine (PT) arranged downstream of said first turbine (T), stably coupled with said crankshaft (K) through a clutch, wherein a first electric motor/generator (EM1) is stably coupled with said turbocharger system (T, C), a second electric motor/generator (EM2) is operatively coupled with said power turbine (PT), the first and second electric motor/generators (EM1, EM2) being electrically interconnected, and wherein control means (CTRL) are adapted to control said electric motor/generators (EM1, EM2) as motor or generator, the method comprising the procedure of controlling one of said electric motor/generators (EM1, EM2) in an opposite way with respect the other, so that the electric energy produced by one is consumed by the other and vice versa.

10. Method according to claim 9, wherein said procedure to control said electric motor/generators (EM1, EM2) according to said opposite way, is performed in fired condition and/or in motored and engine brake conditions, in transient and/or in stationary operations of the engine system. 11. Method according to claims 9 or 10, wherein said procedure comprising - checking a condition where it is required to increase the compressor (C) speed and: when said condition is verified the procedure comprises - controlling said first electric motor/generator (EM1) to work as a motor and said second electric motor/generator (EM2) to work as a generator and - commanding a closing of said clutch. 12. Method according to claim 11, wherein said steps are carried out when at least one of the following further conditions are verified: - the combustion engine is fired or - the combustion engine is motored or in low and moderate speed of braking condition. 13. Method according to any of the previous claims 10 - 12, further comprising the checking of the following conditions: - the combustion engine is fired and it is required to decrease the compressor (C) speed and: when said conditions are verified the procedure comprises the controlling of said first electric motor/generator (EM1) to work as a generator and said second electric motor/generator (EM2) to work as a motor and the commanding of a closing of said clutch in order to supplement the crankshaft (K). 14. Method according to any of the previous claims 10 - 12, further comprising the checking of the following conditions: - high engine speed during engine braking and: when said conditions are verified the procedure comprises commanding of the opening of said clutch and the controlling said second electric motor/generator (EM2) to work as a generator by liming the power turbine speed and the controlling said first electric motor/generator (EM1) to work as a motor to increase the compressor speed, in order to increase the engine braking torque. 15. Method according to claim 14, further comprising the step of reducing automatically the fuel supplied - with respect to a corresponding position of an accelerator pedal - on the basis of a mechanical power provided by said second electric motor/generator (EM2). 16. Computer program comprising computer program code means adapted to perform all the steps of any claim from 9 to 15, when said program is run on a computer. 17. A computer readable medium having a program recorded thereon, said computer readable medium comprising computer program code means adapted to perform all the steps of any claim from 9 to 15, when said program is run on a computer.

2886825

Improved turbocompound system, in particular in the field of industrial vehicles

Based on the following detailed description of an invention, generate the patent claims. There should be 9 claims in total. The first, independent claim is given and the remaining 8 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

According to figure 1 a combustion engine E, for example Diesel type, has an intake manifold In and an exhaust manifold Ex. A turbocharger unit T, C defines a first supercharging stage (optional), having the first turbine T operatively connected immediately downstream of the exhaust manifold Ex. The compressor C, driven by the first turbine T, sucks fresh air from the ambient, compresses it, while the intercooler unit CAC cools the compressed air before entering into the intake manifold In. An EGR system and a wastegate valve WG can be implemented. In addition, the turbine T can be variable geometry type. A second turbine PT is arranged on the exhaust gas line IL, downstream said first turbine T, if present, according the flow of the exhaust gasses. Also the power turbine can be variable geometry type. Such second turbine, is hereinafter called as power turbine, being coupled with the engine crankshaft K through a clutch CL and gears G for adapting the power turbine speed with the engine speed. The power turbine is stably paired with an electric motor EM. The electric motor is electrically connected with the external electric system of the engine or vehicle that contain means for storing electric energy ESM that could be of any type. For example, said storage means ESM can be the usual lead battery used for restarting the combustion engine and for assuring the operating of the onboard auxiliary services and/or traction batteries (lithium, supercapacitors or the like), specifically adopted in the field of the electric and hybrid vehicles. Control means CTRL control the operation of the clutch and of the electric machine EM via the power electronics PE, namely an inverter or the like. In particular, the control means are adapted - to command the opening of said clutch, namely the disconnection of the power turbine from the crankshaft, when the combustion engine speed exceeds a predefined value in engine brake mode and motored mode; - to control then said electric motor/generator to limit turbine speed by generating electric energy to be stored within the storage means ESM,in order to extract as much work as possible from the drivetrain, for storage as electric power in the batteries. In case the vehicle is not provided of traction batteries, a suitable resistance can be implemented for dissipating an exceeding amount of electric energy that cannot be stored within the lead batteries. In a following phase, the engine speed falls under said predefined value, thus the clutch is closed. If the vehicle is provided with traction batteries, during a following acceleration phase, the electric motor/generator is controlled in order to work as a motor by cooperating with the power turbine for helping the crankshaft and by exploiting the electric energy previously stored within said storage means ESM. The engine speed is usually detected through a speed sensor. Thanks to the present invention, the electric energy is produced without subtracting mechanical energy by the combustion engine, through a really compact scheme, and, above all, through a few changes with respect to a known turbocompound system. Thus, not only the fuel consumption is reduced, but also the load response and engine brake capability of the engine system is improved. According to a preferred embodiment of the present invention, said clutch is hydrodynamic type. Therefore, the opening of the clutch is carried out by cutting the hydrodynamic oil of the clutch. According to another embodiment of the invention said electric motor/generator EM replaces completely the well known engine alternator. In other words, the vehicle implementing the present turbocompound system does not have another electric generator. In such a case, the EM is controlled in order to work as generator, by offering a variable load, not only when the power turbine is disconnected from the crankshaft, but also during other conditions, for example when the engine has a constant speed and/or during decelerating phases. According to another embodiment of the invention said electric motor/generator EM replaces completely the well known engine starter. In other words, the vehicle implementing the present turbocompound system does not have another electric starter. In such a case, the EM is controlled in order to work as a combustion engine starter, powered by the batteries, with the clutch closed to start the engine. According to a preferred embodiment of the invention, a flap can be arranged downstream of said power turbine PT along said exhaust line. During engine braking operation, namely when the fuel supply is cut and the engine is motored by the vehicle inertia, the flap can be closed in order to develop a backpressure, which increases the pumping job of the combustion engine and thus the engine braking effect. According to another preferred embodiment of the invention, the power turbine has a variable and controllable geometry and the flap is not present. During engine braking operation, the power turbine is controlled in order to close the scroll, by reducing its outflow section, thus generating a high backpressure. The electric motor/generator is controlled in order to work as generator, by offering a suitable load to the power turbine. In particular, the generator EM is controlled in order to maintain the power turbine speed under a second predetermined speed while the clutch is open. The control of the electric motor/generator and of the clutch and of the power turbine, in case the latter has a controllable variable geometry, is carried out by control means that can be integrated within the engine control unit ECU or in another specific control unit. This invention can be implemented advantageously in a computer program comprising program code means for performing one or more steps of such method, when such program is run on a computer. For this reason the patent shall also cover such computer program and the computer-readable medium that comprises a recorded message, such computer-readable medium comprising the program code means for performing one or more steps of such method, when such program is run on a computer. Many changes, modifications, variations and other uses and applications of the subject invention will become apparent to those skilled in the art after considering the specification and the accompanying drawings which disclose preferred embodiments thereof. All such changes, modifications, variations and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by this invention. Further implementation details will not be described, as the man skilled in the art is able to carry out the invention starting from the teaching of the above description.

1. Improved turbocompound system, in particular in the field of industrial vehicles, comprising a combustion engine (E) having - a crankshaft (K), - an exhaust gas line (EL), - a power turbine (PT) arranged on said exhaust gas line (EL), operatively coupled with said crankshaft (K) through a clutch (CL), - means for detecting the combustion engine speed, - control means (CTRL) for controlling said clutch,: Wherein an electric motor/generator is operatively coupled with a shaft of said power turbine (PT) and electric storage means (ESM) are coupled with said electric motor/generator to store electric energy produced by said electric motor/generator and wherein, when the combustion engine speed exceeds a predefined value, said control means are adapted - to command the opening of said clutch and - to control said electric motor/generator in order to offer a suitable mechanical load to said power turbine, by producing said electric energy.

2. Turbocompound system according to claim 1, wherein said control means (CTRL) are adapted to command the closing of said clutch when the combustion engine speed falls under said predefined value. 3. Turbocompound system according to claims 1 or 2, wherein said predefined engine speed value can be change according to a fired or motored or engine brake condition. 4. Turbocompound system according to one of the claims 1 - 3, wherein said control means (CTRL) are adapted to control said motor/generator in order to work as a motor during an accelerating phase of the engine, by cooperating with the power turbine for helping the crankshaft (K). 5. Turbocompound system according to any of the previous claims 1 - 4, wherein said electric motor/generator (EM) replaces completely an engine alternator, so that said control means (CTRL) control said electric motor/generator (EM) in order to work as generator, by offering a variable load, also when the engine has a constant and/or decreasing speed. 6. Turbocompound system according to any of the previous claims 1 - 5, wherein said electric motor/generator (EM) replaces completely an engine starter, so that said control means (CTRL) are adapted to control said electric motor/generator (EM) in order to work as a combustion engine starter, whereas the clutch is closed. 7. Turbocompound system according to any of the previous claims 1 - 5, wherein said power turbine has a variable controllable geometry and wherein said control means are adapted to control said geometry. 8. Turbocompound system according to claim 6, wherein, during engine braking operation, said control means are adapted to control the closing of said geometry in order to reduce its outflow section, and to control the electric motor/generator (EM) in order to work as generator, by offering a suitable load to the power turbine. 9. Industrial vehicle comprising a turbocompound system, according to any of the previous claims from 1 to 8.

2886825

Improved turbocompound system, in particular in the field of industrial vehicles

Based on the following detailed description of an invention, generate the patent claims. There should be 8 claims in total. The first, independent claim is given and the remaining 7 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

According to figure 1 a combustion engine E, for example Diesel type, has an intake manifold In and an exhaust manifold Ex. A turbocharger unit T, C defines a first supercharging stage (optional), having the first turbine T operatively connected immediately downstream of the exhaust manifold Ex. The compressor C, driven by the first turbine T, sucks fresh air from the ambient, compresses it, while the intercooler unit CAC cools the compressed air before entering into the intake manifold In. An EGR system and a wastegate valve WG can be implemented. In addition, the turbine T can be variable geometry type. A second turbine PT is arranged on the exhaust gas line IL, downstream said first turbine T, if present, according the flow of the exhaust gasses. Also the power turbine can be variable geometry type. Such second turbine, is hereinafter called as power turbine, being coupled with the engine crankshaft K through a clutch CL and gears G for adapting the power turbine speed with the engine speed. The power turbine is stably paired with an electric motor EM. The electric motor is electrically connected with the external electric system of the engine or vehicle that contain means for storing electric energy ESM that could be of any type. For example, said storage means ESM can be the usual lead battery used for restarting the combustion engine and for assuring the operating of the onboard auxiliary services and/or traction batteries (lithium, supercapacitors or the like), specifically adopted in the field of the electric and hybrid vehicles. Control means CTRL control the operation of the clutch and of the electric machine EM via the power electronics PE, namely an inverter or the like. In particular, the control means are adapted - to command the opening of said clutch, namely the disconnection of the power turbine from the crankshaft, when the combustion engine speed exceeds a predefined value in engine brake mode and motored mode; - to control then said electric motor/generator to limit turbine speed by generating electric energy to be stored within the storage means ESM,in order to extract as much work as possible from the drivetrain, for storage as electric power in the batteries. In case the vehicle is not provided of traction batteries, a suitable resistance can be implemented for dissipating an exceeding amount of electric energy that cannot be stored within the lead batteries. In a following phase, the engine speed falls under said predefined value, thus the clutch is closed. If the vehicle is provided with traction batteries, during a following acceleration phase, the electric motor/generator is controlled in order to work as a motor by cooperating with the power turbine for helping the crankshaft and by exploiting the electric energy previously stored within said storage means ESM. The engine speed is usually detected through a speed sensor. Thanks to the present invention, the electric energy is produced without subtracting mechanical energy by the combustion engine, through a really compact scheme, and, above all, through a few changes with respect to a known turbocompound system. Thus, not only the fuel consumption is reduced, but also the load response and engine brake capability of the engine system is improved. According to a preferred embodiment of the present invention, said clutch is hydrodynamic type. Therefore, the opening of the clutch is carried out by cutting the hydrodynamic oil of the clutch. According to another embodiment of the invention said electric motor/generator EM replaces completely the well known engine alternator. In other words, the vehicle implementing the present turbocompound system does not have another electric generator. In such a case, the EM is controlled in order to work as generator, by offering a variable load, not only when the power turbine is disconnected from the crankshaft, but also during other conditions, for example when the engine has a constant speed and/or during decelerating phases. According to another embodiment of the invention said electric motor/generator EM replaces completely the well known engine starter. In other words, the vehicle implementing the present turbocompound system does not have another electric starter. In such a case, the EM is controlled in order to work as a combustion engine starter, powered by the batteries, with the clutch closed to start the engine. According to a preferred embodiment of the invention, a flap can be arranged downstream of said power turbine PT along said exhaust line. During engine braking operation, namely when the fuel supply is cut and the engine is motored by the vehicle inertia, the flap can be closed in order to develop a backpressure, which increases the pumping job of the combustion engine and thus the engine braking effect. According to another preferred embodiment of the invention, the power turbine has a variable and controllable geometry and the flap is not present. During engine braking operation, the power turbine is controlled in order to close the scroll, by reducing its outflow section, thus generating a high backpressure. The electric motor/generator is controlled in order to work as generator, by offering a suitable load to the power turbine. In particular, the generator EM is controlled in order to maintain the power turbine speed under a second predetermined speed while the clutch is open. The control of the electric motor/generator and of the clutch and of the power turbine, in case the latter has a controllable variable geometry, is carried out by control means that can be integrated within the engine control unit ECU or in another specific control unit. This invention can be implemented advantageously in a computer program comprising program code means for performing one or more steps of such method, when such program is run on a computer. For this reason the patent shall also cover such computer program and the computer-readable medium that comprises a recorded message, such computer-readable medium comprising the program code means for performing one or more steps of such method, when such program is run on a computer. Many changes, modifications, variations and other uses and applications of the subject invention will become apparent to those skilled in the art after considering the specification and the accompanying drawings which disclose preferred embodiments thereof. All such changes, modifications, variations and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by this invention. Further implementation details will not be described, as the man skilled in the art is able to carry out the invention starting from the teaching of the above description.

10. Method of controlling a turbocompound system, in particular in the field of industrial vehicles, the turbocompound system comprising a combustion engine (E) having - a crankshaft (K), - an exhaust gas line (EL), - a power turbine (PT) arranged on said exhaust gas line (EL), operatively coupled with said crankshaft (K) through a clutch - means for detecting the combustion engine speed, - control means (CTRL) for controlling said clutch, - an electric motor/generator operatively coupled with a shaft of said power turbine (PT) and - electric storage means (ESM) coupled with said electric motor/generator to store electric energy produced by said electric motor/generator,: the method comprising the all the following steps - checking the combustion engine speed exceeds a predefined value, then - commanding the opening of said clutch and - controlling said electric motor/generator in order to offer a suitable mechanical load to said power turbine, by producing said electric energy.

11. Method according to claim 10, further comprising the step of closing said clutch when the combustion engine speed falls under said predefined value. 12. Method according to claims 10 or 11, wherein said predefined engine speed value can be change according to a fired or motored or engine brake condition. 13. Method according to any of the previous claims 10 - 12, wherein said electric motor/generator (EM) replaces completely an engine alternator, so that said electric motor/generator (EM) in controlled in order to work as generator, by offering a variable load, also when the engine has a constant and/or decreasing speed. 14. Method according to any of the previous claims 10 - 13, wherein said electric motor/generator (EM) replaces completely an engine starter, so that said electric motor/generator (EM) is controlled in order to work as a combustion engine starter, whereas the clutch is closed. 15. Method according to any of the previous claims 10 - 14, wherein said power turbine has a variable controllable geometry and the method further comprises the step of controlling said geometry by closing said geometry in order to reduce its outflow section, and controlling the electric motor/generator (EM) in order to work as generator, by offering a suitable load to the power turbine. 16. Computer program comprising computer program code means adapted to perform all the steps of any claim from 10 to 15, when said program is run on a computer. 17. A computer readable medium having a program recorded thereon, said computer readable medium comprising computer program code means adapted to perform all the steps of any claim from 10 to 15, when said program is run on a computer.

2886826

A turbocompound assembly, in particular in the field of industrial vehicles

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The assembly CL, according to figures 1 and 2, comprises a cylindrical body B1, defining a development axis X and an corresponding axial symmetry.: Within the body B1 is arranged a differential arrangement, wherein the pinion of the power turbine PT defines a sun gear S meshing into two or more planet gears P, which in turn mesh into a ring gear IG coupled with the engine crankshaft.: The ring gear, according to figure 2 and 3 is integral part with the body B1. Preferably, said ring gear is internally arranged as a meridian of the body B1. Therefore, the power turbine shaft S lies on said symmetry axis X and his pinion engages simultaneously two or more gears P that, in turn, engage said inner annular gear IG. Thus, said two or more gears define planet gears, radial arranged with respect to the sun S. A carrier (not shown in figures 1 - 3 ) maintains planet gears P angularly equally spaced.: Within the body, preferably, is also arranged a hydrodynamic clutch HCL, thus the ring gear IG is coupled with the engine crankshaft through said hydrodynamic clutch HCL.: The hydrodynamic clutch HCL comprises a first C1 and a second component B2 rotatably joined between each another according the development axis X, the latter defining a symmetry axis for the differential assembly.: The first component C1 is fixed with the interior of said body B1, while the second component B2 is fixed with the shaft SH, that is suitable to be coupled with the engine crankshaft.: The shaft SH is provided with an annular gear, operatively paired with the crank train G, optional, for cooperating in adapting the power turbine speed with the crank shaft speed. Therefore, the second portion B2 is designed to be stably connected with the crankshaft K, through the crank train G if present.: The shaft S of the power turbine can comprise a bearing. According to a preferred embodiment of the invention, said bearing is integrated within said support B5. Or, alternatively, the body itself defines a bearing for the power turbine shaft. According to another preferred embodiment of the invention, disclosed on figure 4, the support B5 not only supports the power turbine shaft bearing B51, but also defines a carrier B52 for the planets P as well as for the bearing B53 for the input side of the hydrodynamic coupling respectively for the ring gear that is integrated in that coupling..: Thus, a single body can comprise not only the Epicyclic assembly and the hydrodynamic coupling, but also the power turbine shaft bearing. The power turbine support B5 is operatively fixed, while the body B1 (not shown in figure 4 ) rotates motored by the Epicyclic assembly. The second component B2 of the clutch, instead is fixed with the body B1 and the first component C1 according to its oil pressure as in any known hydrodynamic coupling.: On figure 4 is shown the support B5 having an annular shape with a coaxial bearing B51 for the power turbine shaft S, and eccentric bearings B52 for the planet gears P, parallel with the power turbine shaft S.: The support B5, preferably, protrudes through the free space between the planets P, by interpenetrating with the portion B1/C1 of the assembly defining another rotatable interface with it, in particular another annular/coaxial bearing B53.: Being the first component C1 of the hydrodynamic coupling integral and fixed with the body B1, said rotatable interface can be obtained directly on the free face of the first component of the hydrodynamic clutch.: Although, in figure 4 is not shown the shaft SH, it is fixed with the portion B2 as shown in figure 3. Advantageously, one single body encloses a differential device, a hydrodynamic clutch and a power turbine bearing.: Preferably, the single body B1 has a cylindrical shape, both internally and externally defining said axial symmetry X and has a further annular outer gear OG suitable to be paired with a power source or a load EM2 as shown on figure 5. #### Implementation Example According to figure 5 a combustion engine E, for example Diesel type, has an intake manifold In and an exhaust manifold Ex. A turbocharger unit T, C defines a first supercharging stage (optional), having the first turbine T operatively connected immediately downstream of the exhaust manifold Ex. The compressor C, driven by the first turbine T, sucks fresh air from the ambient, compresses it, while the intercooler unit CAC cools the compressed air before entering into the intake manifold In. An EGR system and a waste gate valve WG can be implemented. In addition, the power turbine can be a variable geometry type. A power turbine PT is arranged on the exhaust gas line IL, downstream said first turbine T, if present, according the flow of the exhaust gasses.: Such power turbine is coupled with the engine crankshaft K through the turbocompound assembly disclosed above.: It follows that the power turbine is stably paired with an electric motor EM. The electric motor is electrically connected with means for storing electric energy ESM that could be of any type.: Control means CTRL control the operation of the clutch and of the electric motor EM. Many changes, modifications, variations and other uses and applications of the subject invention will become apparent to those skilled in the art after considering the specification and the accompanying drawings which disclose preferred embodiments thereof. All such changes, modifications, variations and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by this invention. Further implementation details will not be described, as the man skilled in the art is able to carry out the invention starting from the teaching of the above description.

1. A turbocompound assembly, in particular in the field of industrial vehicles comprising a power turbine (PT) paired with the engine crankshaft, wherein said paring is carried out through said assembly, the assembly comprising - a differential arrangement, wherein the pinion of said power turbine defines a sun gear (S) meshing into two or more planet gears (P), which in turn mesh into a ring gear (IG) coupled with the engine crankshaft and - a hydrodynamic clutch (CL) so that said ring gear (IG) is coupled with the engine crankshaft through said hydrodynamic clutch (HCL) and - a body (B1) encloses said hydrodynamic clutch (HCL) and said ring gear (IG) is integral with said body (B1).

2. Assembly according to claim 1, wherein said hydrodynamic clutch (HCL) comprises a first (C1) and a second (B2) components rotatably joined between each another according an axis (X), the latter defining a symmetry axis for the differential assembly and wherein said first component is stably fixed with said body (B1) and said second component is integral with a shaft (SH) suitable to be coupled with the engine crankshaft. 3. Assembly according to claim 2, further comprising a power turbine shaft support (B5), wherein said ring gear (IG), said power turbine shaft support (B5), a carrier of said planet gears are all seated in said single body (B1). 4. Assembly according to claim 3, wherein said power turbine shaft support (B5) defines said planet gear carrier. 5. Assembly according to claim 3 or 4, wherein said single body (B1) has a cylindrical shape, both internally and externally defining said axial symmetry (X). 6. Assembly according to any of the previous claims, wherein said differential arrangement has a further annular outer gear (OG) suitable to be paired with power source or load (EM). 7. Turbocompound system having a power turbine (PT), driven by the exhaust gasses of a combustion engine (E), paired with a crank train (G) through a turbocompound assembly according to any of the previous claims 1 - 8. 8. Turbocompound system according to claim 7, further comprising an electric motor/generator (EM) or an expander, geared with the power turbine (PT) trough said annular outer gear (OG). 9. Turbocompound system according to claims 7 or 8, comprising a combustion engine (E) having - a crankshaft (K), - a first turbocharger system, wherein a first turbine (T) drives a fresh air compressor (C), - a power turbine (PT) arranged downstream of said first turbine (T), operatively coupled with said crankshaft (K) through said hydrodynamic clutch (CL) and said crank train (G). 10. Industrial vehicle comprising a turbocompound system, according to any of the previous claims from 7 to 9.

2886994

Plate heat exchanger with mounting flange

Based on the following detailed description of an invention, generate the patent claims. There should be 21 claims in total. The first, independent claim is given and the remaining 20 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Embodiments of the present invention relate to configurations of a mounting structure on a plate heat exchanger. Corresponding elements are designated by the same reference numerals. Figs 1-2 disclose an embodiment of a plate heat exchanger 1 according to the invention. The plate heat exchanger 1 comprises a plurality of plates which are stacked one on top of the other to form a plate package 2. The plate package 2 may be of any conventional design. Generally the plate package 2 comprises a plurality of heat exchanger plates 3 with corrugated heat transfer portions that define flow passages (internal channels) for a first and second fluid between the heat exchanger plates 3 such that heat is transferred through the heat transfer portions from one fluid to the other. The heat exchanger plates 3 may be single-walled or double-walled. The heat exchanger plates 3 are only schematically indicated in Figure 1, since they are well-known to the person skilled in the art and their configuration is not essential for the present invention. The plate package 2 has the general shape of a rectangular cuboid, albeit with rounded corners. Other shapes are conceivable. Generally, the plate package 2 defines a surrounding external wall 4 which extends in a height or axial direction A between a top axial end and a bottom axial end. The wall 4 has a given perimeter or contour at its bottom axial end. In the illustrated example, the wall 4 has essentially the same contour along its extent in the axial direction A. The bottom axial end of the plate package 2 comprises or is provided with an essentially planar end surface 5 ( Figure 2 ), which may but need not conform to the contour of the wall 4 at the bottom axial end. The end surface 5 extends in a lateral plane. Generally, the plate package 2, and the end surface 5, extends between two longitudinal ends in a longitudinal direction L and between two transverse ends in a transverse direction T ( Figure 2 ). Although not shown on the drawings, the heat transfer plates 3 have in their corner portions through-openings, which form inlet channels and outlet channels in communication with the flow passages for the first fluid and the second fluid. These inlet and outlet channels open in the end surface 5 of the plate package 2 to define separate portholes for inlet and outlet of the first and second fluids, respectively. In the illustrated example, the end surface 5 has four portholes 6 ( Figure 2 ). The plate package 2 is permanently connected to two identical (in this example) mounting plates 7, which are arranged on a respective end portion of the end surface 5. The mounting plates 7 are thereby separated in the longitudinal direction L, leaving a space free of material beneath the center portion of the plate package 2. Compared to using a single mounting plate that extends beneath the entire plate package 2, the illustrated configuration saves weight and material of the heat exchanger 1, and thereby also cost. Each mounting plate 7 has two through-holes 8 which are mated with a respective pair of the portholes 6 of the plate package 2 to define inlet and outlet ports of the heat exchanger 1. The mounting plates 7 are configured for attaching the heat exchanger 1 to an external suspension structure (not shown) such that the inlet and outlet ports mate with corresponding supply ports for the first and second medium on the external structure. Optionally, one or more seals (not shown) may be provided in the interface between the mounting plate 7 and the external structure. Each mounting plate 7 defines a mounting flange 9 that projects from the wall 4 and extends around the longitudinal end of the plate package 2. Bores 10 are provided in the mounting flange 9 as a means for fastening the heat exchanger 1 to the external structure. Threaded fasteners or bolts, for example, may be introduced into the bores 10 for engagement with corresponding bores in the external structure. The plate package 2 and the mounting plates 7 are made of metal, such as stainless steel or aluminum. All the plates in the heat exchanger 1 are permanently connected to each other, preferably through melting of a metallic material, such as brazing, welding or a combination of brazing and welding. The plates in the plate package 2 may alternatively be permanently connected by gluing. The mounting plates 7 are dimensioned, with respect to material, thickness and extent in the longitudinal and transverse directions, so as to have an adequate strength and stiffness to the static load that is applied to the mounting plates 7 when fastened on the external structure. The static load, which tends to deform the mounting plates 7, may originate from a combination of the weight of the heat exchanger 1, internal pressure applied by the media in the heat exchanger 1 and transferred to the mounting plates 7, and compression forces applied to the mounting plates 7, e.g. at the above-mentioned seals, via the fasteners and the bores 10. This static load tend to deform the mounting plates 7. As seen in Figs 1-2, the mounting plates 7 are generally designed to have a significant thickness. As a non-limiting example, the thickness may be 15-40 mm. The bottom of the plate package 2, on the other hand, is normally made of much thinner material. If the heat exchanger 1 is installed in an environment where vibrations are transferred to the mounting plate 7 via the external structure, the heat exchanger 1 also needs to be designed to account for the mechanical stresses caused by the cyclic loading of the vibrations, i.e. cyclic stresses. For example, such vibrations occur for heat exchangers that are mounted in vehicles, such as cars, trucks and ships. In one non-limiting example, the heat exchanger 1 is an oil cooler for an engine. When cyclic stresses are applied to a material, even though the stresses do not cause plastic deformation, the material may fail due to fatigue especially in local regions with high stress concentration. The use of stiff thick mounting plates 7 connected to a plate package 2 with a relatively thin bottom is likely to lead to high concentrations of cyclic stress at the interface between the mounting plates 7 and the plate package 2, and possibly also within the plate package 2. Embodiments of the present invention are designed to counteract stress concentration that may lead to fatigue failure. To this end, the mounting plates 7 are generally designed with a reduced thickness of the mounting plate 7 in selected intersection regions 11, which are located at and around the point where the perimeter of the mounting plate 7 intersects with the perimeter of the wall 4 of the plate package 2, as seen in plan view ( Figure 2 ). As used herein, the "perimeter" designates the outer contour. The perimeter of the mounting plate 7, as seen in the normal direction to the end surface 5, is also denoted "peripheral edge" herein. Specifically, each intersection region 11 includes the intersection point and spans an area where the mounting plate 7 overlaps and is attached to the plate package 2. The heat exchanger 1 in Figs 1-2 has four intersection regions 11, which are approximately indicated by dashed lines in Figure 2. The intersection regions 11 typically extend about 5-20 mm from the intersection point in the plane of the mounting plate 7. By thinning the mounting plate 7 in the intersection regions 11, a locally increased flexibility is achieved in each such region 11 without significantly impairing the stiffness of the mounting plate 7 as a whole. The flexibility results in a favorable load transfer in the interface between the mounting plate 7 and the plate package 2. Figs 3A, 3B and 4 illustrate a mounting plate 7 in more detail. The mounting plate 7 has a generally elongated shape with rounded corner portions, as seen in plan view. The mounting plate 7 has essentially planar top and bottom surfaces 12, 13, where the top surface 12 forms an engagement surface to be permanently connected to the end surface 5 on the plate package 2, and the bottom surface 13 forms an engagement surface to be applied and fixed to the external supporting structure. The through-holes 8 and bores 10 are formed to extend between the top and bottom surfaces 12, 13. At the perimeter of the mounting plate 7, the top and bottom surfaces are connected by a peripheral edge surface 14. The edge surface 14 is essentially planar and right-angled to the top and bottom surfaces 12, 13 except for two elongated recesses or cuts 15 that are formed at two corner portions of the mounting plate 7. The recesses 15 result in a local and gradual reduction of the thickness of the mounting plate 7 towards its perimeter at the corner portions. As seen in Figure 2, the recesses 15 are provided on the mounting plate 7 such that they overlap with the wall 4 that defines the perimeter of the plate package 2. In other words, the recesses 15 are arranged to locally increase the flexibility of the mounting plate 7 in a respective intersection region 11. In the illustrated embodiment, the respective recess 15 is elongated and extends across the entire rounded corner portion of the mounting plate 7. The recess 15 extends essentially parallel to the top surface 12 and defines a linear cut line or border line 16 on the bottom surface 13, as shown in Figure 4. The cut line 16 defines an angle α to the transverse direction T of the plate package 2. The present Applicant has found that both the extent of the recess 15 and the angle α may be optimized to achieve a desired distribution of stress in the interface between the mounting plate 7 and the plate package 2. Specifically, it may be advantageous for the recess 15 to extend outside the perimeter of the plate package 2, i.e. into the mounting flange 9 ( Figure 1 ). Furthermore, it may be advantageous for the angle α to exceed 0°. It is currently believed that the distribution of stress is improved with increasing angle α, up an angle of 90°. However, the angle may be limited by other design considerations, and in practice the angle α may be at least 1°, at least 5°, or at least 10°. It should be noted that the placement of the bores 10 may be fixed if they are to be matched with corresponding bores, bolts, pins or other fasteners on the external structure. In such a situation, it may be necessary to design the mounting plate 7 with an increased width b in the longitudinal L direction so as to be able to accommodate a recess 15 with a given extent and angle while leaving sufficient material between the recess 15 and the nearest bore 10. As shown in Figure 4, the recess 15 is angled to leave a distance d in the plane of the mounting plate 7 between the cut line 16 and the center of nearest bore 10. It should be noted that the recess 15 need not define a linear cut line 16 with the bottom surface 13. Figs 9A-9B illustrate part of a heat exchanger with a smaller recess 15 in the mounting plate 7. The recess 15 defines a curved cut line 16 on the bottom surface 13 and extends only about halfway across the corner portion of the mounting plate 7. The angle α is defined with respect to the intersection point (marked by a black dot) between the surrounding wall 4 and the cut line 16, as seen from the bottom of the heat exchanger. In Figure 9B, the surrounding wall 4 is partly hidden behind the mounting plate 7 and the location of the wall 4 is indicated by a dashed line. The angle α is defined as the angle, in the plane of the mounting plate 7, between the transverse direction T and the tangent of the cut line 16 at the intersection point. As noted above, this angle α is a design parameter that may be set to exceed 0°, and preferably to be at least 1°, 5° or 10°. This definition and choice of the angle α is applicable to all embodiments shown herein. Figs 9C-9D illustrate a variant in which the recess 15 defines a cut line 16 with a linear center portion bounded by curved end parts. The linear center portion causes the recess to extend further beneath the plate package 2. Figs 9E-9F illustrate another implementation in which the mounting plate 7 has smaller width (cf. b in Figure 4 ). Compared to the mounting plate 7 in Figs 9A-9D, there is less material around the nearest bore 10, and the recess 15 cannot extend into the corner portion. The recess 15 defines a cut line 16 with a linear portion that extends beneath the plate package 2 and a curved end portion in the mounting flange 9. Although all illustrated examples involve recesses 15 that extend into the mounting flange 9, it may be possible to achieve a sufficient stress distribution by confining the recesses 15 entirely within the perimeter of the wall 4. It is also conceivable for the recesses 15 to be much longer so as to extend not only in the mounting flange 9 but also further beneath plate package 2. The two recesses 15 may even meet beneath the plate package 2. One embodiment of this type is shown in Figure 9G. However, a recess 15 that extends significantly beneath plate package 2 may reduce the strength of the mounting plate 7 without significantly contributing to a more uniform distribution of stress. The mounting plate 7 may be initially manufactured with a coherent edge surface 14, e.g. planar and right-angled as shown in Figs 3A-3B, and the recesses 15 may be provided by locally removing a respective portion around the shoulder between the bottom surface 13 and the edge surface 14. The recesses 15 may be formed by machining, e.g. milling, grinding, boring or drilling. Reverting to Figure 4, the respective recess 15 is formed with a cross-section that is generally tapered towards the perimeter of the mounting plate 7. Figure 5, which is taken along the line A1-A1 in Figure 4, shows the cross-section of the mounting plate 7 at the location of the recess 15. As seen, the recess 15 defines a transition 20 from a major thickness t1 of the mounting plate 7 to a minor thickness t2 at the peripheral edge. The transition 20 is generally concave and has curved inner corner portion. In this example, the inner corner portion is surrounded by essentially straight portions. The inner corner portion is formed as a circular curve with a predefined radius R. Calculations indicate that the ratio of the radius R to the major thickness t1 may be in the range of about 0.2 -1.0 to achieve desirable results. The cross-section in Figure 5 is taken at right angles to the cut line 16. For ease of manufacture and/or estimation of the stress distribution (below), the cross-section at right angles to the cut line 16 may (but need not) be the same along the recess 15, i.e. along the cut line 16. This is applicable to all examples of recesses shown herein, and thus Figure 5 may also illustrate the cross-section along line C in Figure 9B, Figure 9D and Figure 9F. The heat exchanger 1 in Figure 1 comprises some additional features that may serve to improve stability and durability. Figure 6A shows the juncture between the mounting plate 7 and the plate package 2 in greater detail and is taken within the dashed rectangle 6A in Figure 1. In this example, a sealing plate 21 is connected to the stack of heat exchanger plates to define a bottom surface of the plate package 2. The sealing plate 21, as shown in Figure 7, is generally planar and has through-holes 22 at its corners to be mated with corresponding through-holes in the heat exchanger plates 3. The perimeter of the sealing plate 21 is bent upwards to form a surrounding flange 23 which adapted to abut on and be fixed to a corresponding flange of an overlying heat exchanger plate, as is known in the art. Thus, the perimeter of the sealing plate 21 generally conforms to the perimeter of the surrounding wall 4, although the surrounding flange 21 may project slightly beyond the perimeter of the surrounding wall 4 as defined by the heat exchanger plates. In certain embodiments, the mounting plates 7 may be directly attached to the sealing plate 21. In such embodiments, the sealing plate 21 is an end plate that defines the end surface 5. However, in the illustrated embodiment, an additional plate 24 is attached intermediate the sealing plate 21 and the mounting plate 7 for the purpose of reinforcing the bottom surface of the plate package 2. Thus, the end surface 5 is defined by this additional reinforcement or supporting plate 24. The use of such a reinforcement plate 24 may be advantageous when the working pressure of one or both of the media conveyed through the heat exchanger 1 is high or when the working pressure for one or both of the media varies over time. The reinforcement plate 24, which is shown in greater detail in Figure 8, has a uniform thickness and defines through-holes 25 which are matched to the portholes in the plate package 2. The perimeter of the reinforcement plate 24 may be essentially level with the perimeter of the sealing plate 21 or the perimeter of the wall 4 of the plate package 2. However, in the illustrated example, the reinforcement plate 24 is adapted to locally project from the perimeter of the wall 4 and thus from the perimeter of the sealing plate 21. Specifically, the reinforcement plate 24 is provided with cutouts 26 that are located to extend in the longitudinal direction between the intersection regions 11 on a respective transverse side of the plate package 2 so as to be essentially level with the axial wall 4. Thereby, the longitudinal end points of the cutouts 26 define a respective transition 27 to a projecting tab portion 28, where the transitions 27 are located to overlap the perimeter of the mounting plate 7 in proximity to the intersection regions 11 and are shaped to be non-perpendicular to the perimeter of the mounting plate 7 at the overlap, as seen in a direction towards the bottom of the heat exchanger 1. This configuration of the reinforcement plate 24 will locally decrease the stress in the reinforcement plate 24 next to the intersection regions 11. The transitions 27 may e.g. form a bevel or a curve from the cutout 26 to the tab 28. In the illustrated example, see Figure 6A, the tab portions 28 protrude from the plate package 2 to essentially co-extend with and abut against a respective mounting plate 7. This has been found to result in a favorable distribution of stress between the mounting plate 7, the reinforcement plate 24 and the sealing plate 21 especially at the corners of the plate package 2. It will also increase the strength of the joint between the reinforcement plate 24 and the mounting plate 7 due to the increased contact area between them. In an alternative implementation, not shown, the reinforcement plate 24 projects from the plate package 2 around its entire perimeter except for small notches that are located in the proximity of the intersection regions 11 to provide transitions 27 that are appropriately shaped to be non-perpendicular to the perimeter of the mounting plate 7. The design of the mounting plate 7, and the reinforcement plate 24 if present, may be optimized based on the general principles outlined above, by simulating the distribution of stress in the heat exchanger structure. Such simulations may serve to adapt one or more of the thickness t1 of the mounting plates 7, the width b of the mounting plates 7, the cross-section of the recess 15, the extent of the recess 15, and the angle α of the recess 15. The simulations may be based on any known technique for numerical approximations of stress, such as the finite element method, the finite difference method, and the boundary element method. A simulation of the stress distribution within the structure in Figure 6A, for one specific vibration load condition, indicates that stresses are well-distributed without any significant peaks in the interface between the mounting plate 7 and the reinforcement plate 24, along arrow L1, with a maximum stress value of about 65 N/mm ^2 (MPa). The simulation also indicates a corresponding magnitude and distribution of stress in the interface between the reinforcement plate 24 and the sealing plate 21, along arrow L2. For comparison, the stress distribution has also been simulated, for the same vibration load condition, within a heat exchanger provided with a mounting plate 7 without any recesses in the intersection regions. This heat exchanger 1 is shown in bottom plan view in Figure 6B. As seen, the respective mounting plate 7 has a uniform thickness throughout its extent, also where the perimeter of the mounting plate 7 intersects the perimeter of the wall 4 of the plate package 2. In this example, the reinforcement plate 24 has the same extension as the sealing plate 21. Figure 6C is an enlarged perspective view of the intersection region. The simulation indicated a significant stress concentration at the juncture of the mounting plate 7 and the reinforcement plate 24, with a maximum stress value of about 310 N/mm ^2 in region L3. For example, the cross-section of the recesses 15 may deviate from the one shown in Figure 5. One alternative cross-section is shown in Figure 10A, where the recess 15 is formed as a bevel 30 that extends linearly from the bottom surface 13 to the top surface 12, to produce a pointed peripheral edge. In Figure 10B, the cross-section is formed as a bevel 30 that extends linearly from the bottom surface 13 to a location inward of the peripheral edge to produce a distal lip 31 of uniform thickness. In Figure 10C, the recess is formed as a sequence of multiple steps 32 towards the peripheral edge. Although not shown in Figure 10C, each step 32 may be provided with a rounded inner corner portion, similar to the cross-section in Figure 5. As used herein, "top", "bottom", "vertical", "horizontal", etc merely refer to directions in the drawings and does not imply any particular positioning of the heat exchanger 1. Nor does this terminology imply that the mounting plates 7 need to be arranged on any particular end of the plate package 2. Reverting to Figure 1, the mounting plates may alternatively be arranged on the top axial end of the plate package 2 and may be permanently connected either to a sealing plate or to a reinforcement plate overlying the sealing plate. Furthermore, the mounting plates 7 may be arranged on an end of the plate package 2 that lacks portholes or on which each or at least one porthole 6 is located intermediate the mounting plates 7.

1. A plate heat exchanger, comprising: a plurality of heat exchanger plates (3) which are stacked and permanently connected to form a plate package (2) that defines first and second fluid paths for a first medium and a second medium, respectively, separated by said heat exchanger plates (3), said plate package (2) defining a surrounding external wall (4) that extends in an axial direction (A) between first and second axial ends, an end plate (21; 24) permanently connected to one of the first and second axial ends so as to provide an end surface (5) that extends between first and second longitudinal ends in a lateral plane which is orthogonal to the axial direction (A), and two mounting plates (7) permanently connected to a respective surface portion of the end surface (5) at the first longitudinal end and the second longitudinal end, respectively, such that the mounting plates (7) are spaced from each other in a longitudinal direction (L) on the end surface (5), wherein the respective mounting plate (7) comprises opposing flat engagement surfaces (12, 13) and a peripheral edge that forms a perimeter of the mounting plate (7), wherein the respective mounting plate (7) is arranged with one of its engagement surfaces (12, 13) permanently connected to the end surface (5), wherein the peripheral edge partially extends beyond the outer periphery of the end surface (5), so as to define a mounting flange (9), and partially extends across the end surface (5) in contact with the same, and wherein the mounting plate (7) has a decreasing thickness towards the peripheral edge in predefined intersection regions (11), which are located where the peripheral edge intersects with the perimeter of the surrounding external wall (4) as seen in a normal direction to the end surface (5).

2. The plate heat exchanger of claim 1, wherein the respective intersection region (11) has a predefined cross-sectional shape which connects the engagement surfaces (12, 13) by reducing the thickness of the mounting plate (7) from a first thickness (t1), given by the distance between the engagement surfaces (12, 13), to a second thickness (t2) at the peripheral edge. 3. The plate heat exchanger of claim 2, wherein the cross-sectional shape comprises a portion with continuously decreasing thickness towards the peripheral edge. 4. The plate heat exchanger of claim 2 or 3, wherein the cross-sectional shape comprises a concave portion. 5. The plate heat exchanger of claim 2, 3 or 4, wherein the cross-sectional shape comprises a corner portion having a radius (R). 6. The plate heat exchanger of claim 5, wherein the ratio between the radius (R) and the first thickness (t1) is in the range of about 0.2-1. 7. The plate heat exchanger of any one of claims 2-6, wherein the cross-sectional shape comprises at least one of a bevel (30) and a plurality of steps (32). 8. The plate heat exchanger of any preceding claim, wherein the decreasing thickness is formed by recesses (15) in the respective mounting plate (7), wherein the respective recess (15) is formed to extend within each of the predefined intersection regions (11) between the engagement surface (13) that faces away from the end surface (5) and the peripheral edge, as seen in the normal direction to the end surface (5). 9. The plate heat exchanger of claim 8, wherein the respective recess (15) extends along the peripheral edge, as seen in the normal direction to the end surface (5). 10. The plate heat exchanger of claim 9, wherein the mounting plate (7), intermediate the recesses (15) along the peripheral edge, comprises a peripheral edge surface (14) which joins and is essentially perpendicular to the opposing engagement surfaces (12, 13), and wherein the recesses (15) are located along a shoulder between the engagement surface (13) that faces away from the end surface (5) and the peripheral edge surface (14). 11. The plate heat exchanger of claim 8, 9 or 10, wherein the respective recess (15) defines a border line (16) to the engagement surface (13) that faces away from the end surface (5), said border line (16) defining an intersection point with the perimeter of the surrounding external wall (4), as seen in the normal direction to the end surface (5), wherein the tangent of the border line (16) at the intersection point defines an angle α that exceeds 0°, and preferably is at least 1°, 5° or 10°, to a transverse direction (T), which is orthogonal to the longitudinal direction (L), in the plane of the mounting plate (7). 12. The plate heat exchanger of claim 11, wherein the recess (15) has essentially the same cross-sectional shape, as seen at right angles to the border line (16), along the border line (16). 13. The plate heat exchanger of claim 11 or 12, wherein the border line (16) comprises an essentially straight line that defines said tangent. 14. The plate heat exchanger of claim 11, 12 or 13, wherein the border line (16) is an essentially straight line. 15. The plate heat exchanger of any one of claims 8-14, wherein the respective recess (15) extends from the intersection region (11) into the mounting flange (9). 16. The plate heat exchanger of any preceding claim, wherein the end plate (21) is a sealing plate which is permanently and sealingly connected to one of the heat exchanger plates (3) at one of said first and second axial ends. 17. The plate heat exchanger of any one of claims 1-15, wherein the end plate (24) is a reinforcement plate (24) which is permanently connected to a sealing plate (21) on the plate package (2), wherein the end plate (24) has at least two supporting flanges (28) that extend beyond the perimeter of the surrounding external wall (4) so as to abut on the mounting flange (9) defined by the respective mounting plate (7). 18. The plate heat exchanger of claim 17, wherein the end plate (24) comprises, along its perimeter and as seen in the normal direction of the end surface (5), concave or beveled surfaces (27) adjacent to the supporting flanges (28), wherein the concave or beveled surfaces (27) are located to overlap the peripheral edge of the respective mounting plate (7) in the proximity of the intersection regions (11), and wherein the respective concave or beveled surface (27) is non-perpendicular to the peripheral edge at the overlap, as seen in the normal direction to the end surface (5). 19. The plate heat exchanger of any preceding claim, wherein at least one of the mounting plates (7) defines at least one through hole (8) that extends between the engagement surfaces (12, 13) and is aligned with a corresponding through hole (22; 25) defined in the end plate (21; 24) and an internal channel defined in the plate package (2), so as to form an inlet or an outlet for the first or the second medium. 20. The plate heat exchanger of any preceding claim, wherein the mounting flange (9) comprises a plurality of mounting holes (10) adapted to receive bolts or pins for fastening the plate heat exchanger. 21. The plate heat exchanger of any preceding claim, wherein the heat exchanger plates (3) are permanently joined to each other through melting of metallic material.

2886995

Plate heat exchanger with mounting flange

Based on the following detailed description of an invention, generate the patent claims. There should be 19 claims in total. The first, independent claim is given and the remaining 18 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Embodiments of the present invention relate to configurations of a mounting structure on a plate heat exchanger. Corresponding elements are designated by the same reference numerals. Figs 1-3 disclose an embodiment of a plate heat exchanger 1 according to the invention. The plate heat exchanger 1 comprises a plurality of plates which are stacked one on top of the other to form a plate package 2. The plate package 2 may be of any conventional design. Generally the plate package 2 comprises a plurality of heat exchanger plates 3 with corrugated heat transfer portions that define flow passages (internal channels) for a first and second fluid between the heat exchanger plates 3 such that heat is transferred through the heat transfer portions from one fluid to the other. The heat exchanger plates 3 may be single-walled or double-walled. The heat exchanger plates 3 are only schematically indicated in Figure 1, since they are well-known to the person skilled in the art and their configuration is not essential for the present invention. The plate package 2 has the general shape of a rectangular cuboid, albeit with rounded corners. Other shapes are conceivable. Generally, the plate package 2 defines a surrounding external wall 4 which extends in a height or axial direction A between a top axial end and a bottom axial end. The wall 4 has a given perimeter or contour at its bottom axial end. In the illustrated example, the wall 4 has essentially the same contour along its extent in the axial direction A. The bottom axial end of the plate package 2 comprises or is provided with an essentially planar end surface 5 ( Figs 2-3 ), which may but need not conform to the contour of the wall 4 at the bottom axial end. The end surface 5 extends in a lateral plane. Generally, the plate package 2, and the end surface 5, extends between two longitudinal ends in a longitudinal direction L and between two transverse ends in a transverse direction T ( Figure 2 ). Although not shown on the drawings, the heat transfer plates 3 have in their corner portions through-openings, which form inlet channels and outlet channels in communication with the flow passages for the first fluid and the second fluid. These inlet and outlet channels open in the end surface 5 of the plate package 2 to define separate portholes for inlet and outlet of the first and second fluids, respectively. In the illustrated example, the end surface 5 has four portholes 6 ( Figure 2 ). The plate package 2 is permanently connected to two identical (in this example) mounting plates 7, which are arranged on a respective end portion of the end surface 5. The mounting plates 7 are thereby separated in the longitudinal direction L, leaving a space free of material beneath the center portion of the plate package 2. Compared to using a single mounting plate that extends beneath the entire plate package 2, the illustrated configuration saves weight and material of the heat exchanger 1, and thereby also cost. Each mounting plate 7 has two through-holes 8 which are mated with a respective pair of the portholes 6 of the plate package 2 to define inlet and outlet ports of the heat exchanger 1. The mounting plates 7 are configured for attaching the heat exchanger 1 to an external suspension structure (not shown) such that the inlet and outlet ports mate with corresponding supply ports for the first and second medium on the external structure. Optionally, one or more seals (not shown) may be provided in the interface between the mounting plate 7 and the external structure. Each mounting plate 7 defines a mounting flange 9 that projects from the wall 4 and extends around the longitudinal end of the plate package 2. Bores 10 are provided in the mounting flange 9 as a means for fastening the heat exchanger 1 to the external structure. Threaded fasteners or bolts, for example, may be introduced into the bores 10 for engagement with corresponding bores in the external structure. The plate package 2 and the mounting plates 7 are made of metal, such as stainless steel or aluminum. All the plates in the heat exchanger 1 are permanently connected to each other, preferably through melting of a metallic material, such as brazing, welding or a combination of brazing and welding. The plates in the plate package 2 may alternatively be permanently connected by gluing. The mounting plates 7 are dimensioned, with respect to material, thickness and extent in the longitudinal and transverse directions, so as to have an adequate strength and stiffness to the static load that is applied to the mounting plates 7 when fastened on the external structure. The static load, which tends to deform the mounting plates 7, may originate from a combination of the weight of the heat exchanger 1, internal pressure applied by the media in the heat exchanger 1 and transferred to the mounting plates 7, and compression forces applied to the mounting plates 7, e.g. at the above-mentioned seals, via the fasteners and the bores 10. This static load tend to deform the mounting plates 7. As seen in Figs 1-3, the mounting plates 7 are generally designed to have a significant thickness. As a non-limiting example, the thickness may be 15-40 mm. The bottom of the plate package 2, on the other hand, is normally made of much thinner material. If the heat exchanger 1 is installed in an environment where vibrations are transferred to the mounting plate 7 via the external structure, the heat exchanger 1 also needs to be designed to account for the mechanical stresses caused by the cyclic loading of the vibrations, i.e. cyclic stresses. For example, such vibrations occur for heat exchangers that are mounted in vehicles, such as cars, trucks and ships. In one non-limiting example, the heat exchanger 1 is an oil cooler for an engine. When cyclic stresses are applied to a material, even though the stresses do not cause plastic deformation, the material may fail due to fatigue especially in local regions with high stress concentration. The use of stiff thick mounting plates 7 connected to a plate package 2 with a relatively thin bottom is likely to lead to high concentrations of cyclic stress at the interface between the mounting plates 7 and the plate package 2, and possibly also within the plate package 2. Embodiments of the present invention are designed to counteract stress concentration that may lead to fatigue failure. To this end, the mounting plates 7 have dedicated slots or notches 15 in the edge portion of the respective mounting plate 7. The slots 15 are arranged to extend below the end surface 5 so as to intersect the surrounding wall 4 of the plate package 2, as seen in the normal direction to the end surface 5. In the embodiment in Figs 1-3, the slots 15 are arranged with their opening at selected intersection points 11 which are formed between the perimeter of the mounting plate 7 and the perimeter of the wall 4 of the plate package 2. As used herein, the "perimeter" designates the outer contour as seen in plan view. In Figure 2, the intersection points 11 are indicated by black dots. By providing the intersecting slots 15 in the edge surface 14, a locally increased flexibility is achieved in a region around each such intersection point 11 without significantly impairing the stiffness and stability of the mounting plate 7 as a whole. The flexibility results in a favorable load transfer in the interface between the mounting plate 7 and the plate package 2. Figs 5A-5B illustrate a mounting plate 7 in more detail. The mounting plate 7 has a generally elongated shape with rounded corner portions, as seen in plan view. The mounting plate 7 has essentially planar top and bottom surfaces 12, 13, where the top surface 12 forms an engagement surface to be permanently connected to the end surface 5 on the plate package 2, and the bottom surface 13 forms an engagement surface to be applied and fixed to the external supporting structure. The through-holes 8 and bores 10 are formed to extend between the top and bottom surfaces 12, 13. At the perimeter of the mounting plate 7, the top and bottom surfaces are connected by a peripheral edge surface 14. The edge surface 14 is essentially planar and right-angled to the top and bottom surfaces 12, 13 and forms the above-mentioned edge portion. In plan view, the corner portions of the mounting plate 7 are connected by essentially straight contour lines, and the contour line of the edge surface 14 that extends across the plate package 2 ( Figure 2 ) is designed to intersect the wall 4 at approximately right angles. This design is selected to minimize the width of the mounting plates 7 in the longitudinal direction L ( Figure 2 ). Other designs are conceivable. In the illustrated example, the slots 15 are located along the straight contour line that extends across the plate package 2. Figure 3B shows the juncture between the mounting plate 7 and the plate package 2 in greater detail, in a perspective from below, and is taken within the dashed rectangle 3B in Figure 3A. It is seen that the slot 15 defines an elongated opening in the edge surface 14. The opening has a width w in the peripheral direction of the edge surface 14 and a height h in the thickness direction of the mounting plate 7 (equal to the axial direction A, Figure 1 ). In Figure 3B, the mounting plate 7 is mounted to the end surface 5 of the plate package 1 such that the opening of the slot 15 intersects the wall 4. In this particular example, further structures are located in the interface between the plate package 2 and the mounting plate 7. These structures are by formed a sealing plate 21 and an reinforcement plate 24, which are described below with reference to Figs 7-8. As seen in Figure 3B, the elongated opening of the slot 15 is spaced from and generally parallel to the top surface 12, and thus to the end surface 5. The slot 15 is located close to the top surface 12, so as to form a thinned lip of material between the slot 15 and the top surface 12. This lip is at least partly attached to the end surface 5 and provides a locally increased flexibility for the mounting plate 7 in the region of the intersection point. By arranging the slot 15 parallel to the top surface 12, the lip has a uniform thickness along the width w of the slot 15 which may enable a more uniform distribution of stress. It is currently believed that the width w and height h of the respective slot 15 are of lesser importance for the stress distribution and can be selected within relatively broad limits. The width and height may rather be selected to facilitate manufacture while ensuring that the mounting plate 7 has an adequate overall stiffness and strength. In one example, the height h is about 5%-50% of the total thickness of the mounting plate 7, but it may fall outside this range. Depending on implementation, the width w may be at least 2 mm, at least 5 mm or at least 10 mm. To further illustrate the configuration of the slot 15, Figure 4A shows a cross-section in the longitudinal direction L, taken along the line A1-A1 in Figure 2, and Figure 4B is a partial plan view of the mounting plate 7 at the location of the slot 15. The slot 15 forms a blind hole, which is defined by a bottom wall 16 and two side walls 17, 18 which extend from the bottom wall 16 to the opening in the edge surface 14. Figs 4A-4B illustrate a number of design parameters that may be adapted, in addition to the width w and the height h, to counteract stress concentration. One such design parameter is the distance t1 between the slot 15 and the top surface 12, and thus the thickness of the above-mentioned lip. The distance t1 is preferably small, e.g. about 3 mm or smaller, and preferably less than about 2 mm or even less than about 1 mm. The slot 15 has a maximum depth d in the longitudinal direction L, i.e. between the bottom wall 16 and the opening in the edge surface 14. This depth d may depend on the shape of the bottom wall. In one example, the slot 15 has the same depth d along its width w. However, in the illustrated example, as seen in Figure 4B, the bottom wall 16 follows the arc of a circle with a radius R1, as seen in a plane parallel to the end surface 5. The radius R1 is defined with respect to a center line C, which is spaced from the edge surface 14. This configuration of the bottom wall 16 may facilitate the manufacture of the slot 15. Furthermore, the bottom wall 16 has a curved shape in cross-section transverse to the extent of the slot 15, i.e. in a plane perpendicular to the end surface 5 ( Figure 4A ). Thereby, the bottom wall 16 forms a trough with smooth transitions to the side walls 17, 18. Such a shape of the bottom wall 16 may further counteract stress concentration. In Figure 4A, the curvature of the bottom wall 16 is given by a radius R2. In Figure 4A, the side walls 17, 18 extend essentially parallel to the top and bottom surfaces 12, 13 and thereby connect essentially at right angles to the edge surface 14 at the opening of the slot 15. Such a configuration may be preferred to simplify manufacture. However, an alternative configuration that may reduce the stress concentration further is shown in Figure 4C. Here, the side wall 17 facing the top surface 12, i.e. the side wall 17 that defines the thinned lip, is inclined to the top surface 12. Thereby, the side wall 17 meets the edge surface 14 at an angle α that exceeds 0°. The angle α is defined with respect to the plane of the top surface 12. In the illustrated example, the side wall 17 is flat and thus has a linear extent from the bottom wall 16 to the opening. If the side wall 17 instead is non-flat, e.g. curved, the angle α is given by the direction (tangent) of the side wall 17 at the opening, i.e. at the location where the side wall 17 meets the edge surface 14. In certain implementations, the angle α may be larger than 2°, 5° or 10° to achieve adequate stress distribution. The angle α is preferably less than about 45°. This definition and choice of the angle α is applicable to all embodiments shown herein. It should be noted that the slot 15 preferably has the same cross-sectional shape along its extent, i.e. along the width w in Figure 3B. The mounting plate 7 may be initially manufactured with a coherent edge surface 14, e.g. planar and right-angled as shown in the drawings, and the slots 15 may be provided by locally removing material from mounting plate 7 at the edge surface 14. The slots 15 may be formed by machining, e.g. milling, grinding, boring or drilling. For example, the slot 15 in Figs 4A-4B may be formed by a milling cutter located to rotate around the center line C. The heat exchanger 1 in Figure 1 comprises some additional features that may serve to improve stability and durability. Figure 6A shows the juncture between the mounting plate 7 and the plate package 2 in greater detail and is taken within the dashed rectangle 6A in Figure 1. In this example, a sealing plate 21 is connected to the stack of heat exchanger plates to define a bottom surface of the plate package 2. The sealing plate 21, as shown in Figure 7, is generally planar and has through-holes 22 at its corners to be mated with corresponding through-holes in the heat exchanger plates 3. The perimeter of the sealing plate 21 is bent upwards to form a surrounding flange 23 which adapted to abut on and be fixed to a corresponding flange of an overlying heat exchanger plate, as is known in the art. Thus, the perimeter of the sealing plate 21 generally conforms to the perimeter of the surrounding wall 4, although the surrounding flange 21 may project slightly beyond the perimeter of the surrounding wall 4 as defined by the heat exchanger plates. In certain embodiments, the mounting plates 7 may be directly attached to the sealing plate 21. In such embodiments, the sealing plate 21 is an end plate that defines the end surface 5. However, in the illustrated embodiment, an additional plate 24 is attached intermediate the sealing plate 21 and the mounting plate 7 for the purpose of reinforcing the bottom surface of the plate package 2. Thus, the end surface 5 is defined by this additional reinforcement or supporting plate 24. The use of such a reinforcement plate 24 may be advantageous when the working pressure of one or both of the media conveyed through the heat exchanger 1 is high or when the working pressure for one or both of the media varies over time. The reinforcement plate 24, which is shown in greater detail in Figure 8, has a uniform thickness and defines through-holes 25 which are matched to the portholes in the plate package 2. The perimeter of the reinforcement plate 24 may be essentially level with the perimeter of the sealing plate 21 or the perimeter of the wall 4 of the plate package 2. However, in the illustrated example, the reinforcement plate 24 is adapted to locally project from the perimeter of the wall 4, and thus from the perimeter of the sealing plate 21. Specifically, the reinforcement plate 24 is provided with cutouts 26 that are located to extend in the longitudinal direction between the intersection points 11 on a respective transverse side of the plate package 2 so as to be essentially level with the axial wall 4. Thereby, the longitudinal end points of the cutouts 26 define a respective transition 27 to a projecting tab portion 28, where the transitions 27 are located to overlap the perimeter of the mounting plate 7 in proximity to the intersection points 11 and are shaped to be non-perpendicular to the perimeter of the mounting plate 7 at the overlap, as seen in a direction towards the bottom of the heat exchanger 1. This configuration of the reinforcement plate 24 will locally decrease the stress in the reinforcement plate 24 at the intersection points 11. The transitions 27 may e.g. form a bevel or a curve from the cutout 26 to the tab 28. In the illustrated example, see Figure 6A, the tab portions 28 protrude from the plate package 2 to essentially co-extend with and abut against a respective mounting plate 7. This has been found to result in a favorable distribution of stress between the mounting plate 7, the reinforcement plate 24 and the sealing plate 21 especially at the corners of the plate package 2. It will also increase the strength of the joint between the reinforcement plate 24 and the mounting plate 7 due to the increased contact area between them. In an alternative implementation, not shown, the reinforcement plate 24 projects from the plate package 2 around its entire perimeter except for small notches that are located in the proximity of the intersection points 11 to provide transitions 27 that are appropriately shaped to be non-perpendicular to the perimeter of the mounting plate 7. The design of the mounting plate 7, and the reinforcement plate 24 if present, may be optimized based on the general principles outlined above, by simulating the distribution of stress in the heat exchanger structure. Such simulations may serve to adapt one or more of the thickness and width of the mounting plates 7, the width w and the height h of the slots 15, the depth d of the slots 17, the thickness t1 of the attachment lip formed by the slot 15, as well as further parameters related to the internal shape of the slot 15, such as the above-mentioned parameters R1, R2 and α. The simulations may be based on any known technique for numerical approximation of stress, such as the finite element method, the finite difference method, and the boundary element method. A simulation of the stress distribution within the structure in Figure 6A, for one specific vibration load condition, indicates that stresses are well-distributed without any significant peaks in the interface between the reinforcement plate 24 and the sealing plate 21. For this particular simulation, the maximum stress levels are distributed along arrow L1, at which the stress values are approximately 100 N/mm ^2 (MPa). The simulation also indicates that stresses are equally well-distributed in the interface between the mounting plate 7 and the reinforcement plate 24, with maximum stress levels of approximately 80-90 N/mm ^2 being distributed along arrow L2 in Figure 6B, which is a reproduction of Figure 3B. For comparison, the stress distribution has also been simulated, for the same vibration load condition, within a heat exchanger provided with a mounting plate 7 without slots in the edge surface 14, as shown in the enlarged perspective view in Figure 6C. In this example, the reinforcement plate 24 has the same extension as the sealing plate 21. The simulation indicated a significant stress concentration at the juncture of the mounting plate 7 and the reinforcement plate 24, with a maximum stress value of about 310 N/mm ^2 in region L3. While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiments, it is to be understood that the invention is not to be limited to the disclosed embodiments, but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and the scope of the appended claims. For example, the edge surface 14 may have any shape and angle to the top and bottom surfaces 12, 13 of the mounting plate 7. It should be noted that the openings of the slots 15 need not exactly overlap the intersection points 11, as seen in the normal direction to the end surface 5. For example, if the edge surface 14 is non-perpendicular to the top and bottom engagement surfaces 12,13, the openings of the slots 15 may be separated from perimeter of the respective mounting plate 7 as seen in said normal direction, and thus from the intersection points 11 (which are given by the perimeter of the respective mounting plate 7). In other words, when projected onto the lateral plane of the heat exchanger 1, the slots 15 may be spaced from the perimeter of the respective mounting plate 7. Although all illustrated examples involve slots 15 that extend on both sides of their respective intersections with the surrounding wall 4, it may be possible to achieve a sufficient stress distribution by confining the slots 15 within the perimeter of the wall 4, or by confining the slots to the mounting flange 9 that projects from the wall 4, as long as the slots 15 extend to intersect the perimeter of the surrounding wall 4. It is also conceivable to provide the heat exchanger with mounting plates 7 having much wider slots 15 than those shown in Figs 1-5. Figure 9A illustrates a mounting plate 7 with a slot 15 that extends from the nearest corner portion of the mounting plate 7 to a location further towards the center of the plate package 2 compared to the embodiment in Figure 3B. It is also conceivable to provide the mounting plate 7 with a single slot 15 long enough to intersect the surrounding wall 4 at both transverse sides of the plate package 2. Figure 9B shows such a mounting plate 7, in which a coherent slot 15 is formed to extend along the entire edge surface 14 that faces the other mounting plate 7. As used herein, "top", "bottom", "vertical", "horizontal", etc merely refer to directions in the drawings and does not imply any particular positioning of the heat exchanger 1. Nor does this terminology imply that the mounting plates 7 need to be arranged on any particular end of the plate package 2. Reverting to Figure 1, the mounting plates may alternatively be arranged on the top axial end of the plate package 2 and may be permanently connected either to a sealing plate or to a reinforcement plate overlying the sealing plate. Furthermore, the mounting plates 7 may be arranged on an end of the plate package 2 that lacks portholes or on which each or at least one porthole 6 is located intermediate the mounting plates 7.

1. A plate heat exchanger, comprising: a plurality of heat exchanger plates (3) which are stacked and permanently connected to form a plate package (2) that defines first and second fluid paths for a first medium and a second medium, respectively, separated by said heat exchanger plates (3), said plate package (2) defining a surrounding external wall (4) that extends in an axial direction (A) between first and second axial ends, an end plate (21; 24) permanently connected to one of the first and second axial ends so as to provide an end surface (5) that extends between first and second longitudinal ends in a lateral plane which is orthogonal to the axial direction (A), and two mounting plates (7) permanently connected to a respective surface portion of the end surface (5) at the first longitudinal end and the second longitudinal end, respectively, such that the mounting plates (7) are spaced from each other in a longitudinal direction (L) on the end surface (5), wherein the respective mounting plate (7) comprises opposing flat engagement surfaces (12, 13) connected by an edge portion (14) that extends along the perimeter of the mounting plate (7), wherein the respective mounting plate (7) is arranged with one of its engagement surfaces (12, 13) permanently connected to the end surface (5), such that the perimeter of the mounting plate (7) partially extends beyond the outer periphery of the end surface (5), so as to define a mounting flange (9), and partially extends across the end surface (5) in contact with the same, and wherein at least one slot (15) is formed in the edge portion (14) of the respective mounting plate (7) to intersect the perimeter of the surrounding external wall (4) as seen in a normal direction to the end surface (5).

2. The plate heat exchanger of claim 1, wherein the edge portion comprises an edge surface (14) that extends between the engagement surfaces (12, 13), the at least one slot (15) being formed in the edge surface (14). 3. The plate heat exchanger of claim 2, wherein the edge surface (14) is essentially flat, and preferably perpendicular to the engagement surfaces (12, 13). 4. The plate heat exchanger of any preceding claim, wherein the at least one slot (15) extends essentially parallel to the end surface (5). 5. The plate heat exchanger of any preceding claim, wherein the at least one slot (15) is located in proximity of and spaced from the engagement surface (12, 13) that faces the end surface (5). 6. The plate heat exchanger of claim 5, wherein the at least one slot (15) is spaced from the engagement surface (12, 13) that faces the end surface (5) by a material thickness (t1) of less than about 3 mm, preferably less than about 1 mm or about 2 mm. 7. The plate heat exchanger of any preceding claim, wherein the at least one slot (15) is configured to form a blind-hole that defines an elongated opening in the edge portion (14), said blind-hole (15) having a bottom wall (16) and first and second side walls (17, 18), the first and second side walls (17, 18) being spaced from each other in the axial direction (A) and extending from the bottom wall (16) to the elongated opening in the edge portion (14). 8. The plate heat exchanger of claim 7, wherein the bottom wall (16) comprises a curved portion. 9. The plate heat exchanger of claim 8, wherein the curved portion is defined by a radius (R2). 10. The plate heat exchanger of any one of claims 7-9, wherein the first side wall (17), which is located closer to the end surface (5) than the second side wall (18), connects to the edge portion (14) at the elongated opening so as to define an angle α to the lateral plane, wherein 0°<α ≤45°, and preferably 0°<α ≤45°, as seen in a cross-section perpendicular to the lateral plane. 11. The plate heat exchanger of claim 10, wherein the first side wall (17) defines a straight line from the elongated opening to the bottom wall (16), as seen in the cross-section perpendicular to the lateral plane. 12. The plate heat exchanger of any one of claims 7-11, wherein the bottom wall (16) defines an arc of a circle as seen in a cross-section parallel to the lateral plane. 13. The plate heat exchanger of any preceding claim, wherein the at least one slot comprises a coherent slot (15) that at least spans the end surface (5) in the transverse direction (T) so as to intersect the perimeter of the surrounding external wall (4) at two opposing sides of the plate package (2), as seen in the normal direction to the end surface (5). 14. The plate heat exchanger of any preceding claim, wherein the end plate (21) is a sealing plate which is permanently and sealingly connected to one of the heat exchanger plates (3) at one of said first and second axial ends. 15. The plate heat exchanger of any one of claims 1-13, wherein the end plate (24) is a reinforcement plate (24) which is permanently connected to a sealing plate (21) on the plate package (2), wherein the end plate (24) has at least two supporting flanges (28) that extend beyond the perimeter of the surrounding external wall (4) so as to abut on the mounting flange (9) defined by the respective mounting plate (7). 16. The plate heat exchanger of claim 15, wherein the end plate (24) comprises, along its perimeter and as seen in the normal direction of the end surface (5), concave or beveled surfaces (27) adjacent to the supporting flanges (28), wherein the concave or beveled surfaces (27) are located to overlap the perimeter of the respective mounting plate (7) at intersection points (11) where the perimeter of the respective mounting plate (7) intersects the perimeter of the surrounding external wall (4), and wherein the respective concave or beveled surface (27) is non-perpendicular to the perimeter of the mounting plate (7) at the overlap, as seen in the normal direction to the end surface (5). 17. The plate heat exchanger of any preceding claim, wherein at least one of the mounting plates (7) defines at least one through hole (8) that extends between the engagement surfaces (12, 13) and is aligned with a corresponding through hole (22; 25) defined in the end plate (21; 24) and an internal channel defined in the plate package (2), so as to form an inlet or an outlet for the first or the second medium. 18. The plate heat exchanger of any preceding claim, wherein the mounting flange (9) comprises a plurality of mounting holes (10) adapted to receive bolts or pins for fastening the plate heat exchanger. 19. The plate heat exchanger of any preceding claim, wherein the heat exchanger plates (3) are permanently joined to each other through melting of metallic material.

2886232

Cutting inserts with cross-holes and green bodies and methods for making such cutting inserts and green bodies

Based on the following detailed description of an invention, generate the patent claims. There should be 13 claims in total. The first, independent claim is given and the remaining 12 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figures 4A-4I show a green body 21 for a cross-hole, compacted cutting insert according to an aspect of the present invention. The particular green body 21 illustrated will form a double-sided cutting insert, meaning the presence of chip breaker geometries on two sides of the cutting insert, and the present invention shall be primarily described in connection with such a double-sided green body/insert, however, it will be appreciated that the present invention is also applicable to single-sided, three-sided and four-sided inserts. The green body 21 is typically formed from a compactable material such as tungsten carbide powder, or cermet powder, that is subsequently sintered to form a blank being subject to different finishing operations, such as grinding and coating, to form the cutting insert. During sintering, the green body shrinks to a smaller size and, if shrinkage is uniform, as is typically desired, the resulting blank will be the same shape as the green body, except smaller. It will thus be understood that the illustration of the green body 21 will also constitute an illustration of the cutting insert that results from the sintering of the green body and the finishing treatment of the blank after sintering. The green body comprises a first side 23, a second side 25, and a side surface 27 extending between the first side and the second side entirely around the first side and the second side. The first and second sides 23 and 25 may be identical but need not be, and the side surface may be cylindrical or substantially cylindrical, but need not be. The green body 21 is illustrated as having a side surface 27 that is perpendicular to planes of the first side 23 and the second side 25, however, the green body may have planes of a first side 23 and a second side 25 that forms an angle, usually up to about +/- 30 degrees, with planes of the side surface 27. It will be appreciated, of course, that the first and second sides will not necessarily be planar and may have a variety of shapes, including chipbreakers, such that a "plane" of the first and second sides may be an imaginary reference plane. The green body 21 comprises a "quadrilateral-shaped" cross-hole 29 extending through the green body from a first location 31 on the side surface 27 to a second location 33 on the side surface on an opposite side of the green body from the first location. A "quadrilateral-shaped" cross-hole is defined as and intended to encompass a variety of similar cross-hole shapes adapted to facilitate an improved density distribution of compacted material in a green body and including cross-holes with shapes similar to quadrilaterals, cross-holes in the form of orthogonal quadrilaterals (e.g., squares), and non-orthogonal quadrilaterals (e.g., rhombuses, kites), although sides may be curved to the extent that the curvature does not interfere with the function of the quadrilateral shape as described herein, and corners need not be sharp and may be curved. In a presently preferred embodiment, the cross-hole will have a rhombus shape. The quadrilateral may have a major axis and a minor axis between most distant opposite corners and closes opposite corners, respectively. What shall be referred to here as the major axis will typically be parallel to an axis extending from the first side 23 to the second side 25 of the green body 21, and the minor axis will typically be within +/- 30 degrees of perpendicular to the major axis. The major axis is considered to extend substantially in a direction of pressing of the insert (illustrated by arrows in Figure 6B ). The length of the minor axis will typically be from about 0.2x (times) the length of the major axis to about 2x the length of the major axis. While corners at the ends of the major and minor axes may have no radii, they will ordinarily have at least small radii. Radii of corners at the ends of the major axis will typically be smaller than radii of corners at the ends of the minor axis. By having no radii or small radii of corners at the ends of the major axis the mechanism causing build-up of the density above and below the cross hole pin upon compaction of the compactable material is believed to be deactivated, and thereby the variation in density in the green body is reduced. Of course, other radii can be selected, if desired. Provision of the quadrilateral-shaped cross-hole 29 facilitates providing a green body with a substantially uniform density between the first side 23 and the second side 25 and over the height of the side surface 27. A uniform density distribution is desirable in green bodies to minimize shape distortions during sintering. The cross-hole 29 has a quadrilateral shape with first and second points 35 and 37 ( Figure 4E ) of the quadrilateral closest to the first and second sides 23 and 25 of the green body, respectively, and third and fourth points 39 and 41 ( Figure 4E ) of the quadrilateral between the first and second points. A distance D1 ( Figure 4E ) between the first and second points 35 and 37 is ordinarily greater than a distance D2 ( Figure 4E ) between the third and fourth points 39 and 41. The side surface 27 ordinarily has at least two, opposing, portions 43 and 45 that may be flat or curved, and the first location 31 and the second location 33 are disposed on the two portions. The green body 21 shown in Figures 4A-4I includes two additional, minor flat or substantially flat portions 47 and 49 between the portions 43 and 45, however, it will be appreciated that any of the portions 43-49 may be curved, may comprise a series of angled surfaces, may have recesses and protrusions, and/or need not include any flat or planar portions. In the quadrilateral-shaped cross-hole 29, the third and fourth points 39 and 41 of the quadrilateral are typically disposed mid-way between the first and second sides 23 and 25 of the green body 21. The first and second points 35 and 37 of the quadrilateral are typically disposed at equal distances from the first and second sides 23 and 25, respectively. In figure 4 radii of corners at the ends of the major axis, i.e. at the first and second points 35 and 37, are smaller than radii of corners at the ends of the minor axis. i.e. at third and fourth points 39 and 41. The cross-hole 29 can comprise generally circular countersunk portions 51 and 53 centered at the first location and the second location of the type that are typically used in conventional cutting inserts. The outer diameters D3 ( Figure 4E ) of circles defined by the countersunk portions 51 and 53 are typically greater than the distance D2 between the third and fourth points 39 and 41 of the quadrilateral 29, but less than the distance D1 between the first and second points 35 and 37. As in conventional, elliptical or circular holes, the slightly elliptical or circular countersunk portions 51 and 53 can each include a substantially cylindrical portion 51' and 53' extending to the side surface 27 and an inner portion 51" and 53" that defines a non-zero angle with the substantially cylindrical portion and with the side surface adjacent the cross-hole. The angled inner portions 51" and 53" typically function as clamping surfaces for a head of a bolt or screw (not shown) that is used to clamp the insert formed from the green body 21 to a toolholder (not shown). It will be appreciated, however, that it is not necessary that the cross-hole 29 include countersunk portions or that the insert formed from the green body 21 be of the type that is clamped by means of a bolt or screw. The insert may be clamped by a clamping arm or wedge arrangement, for example, and the cross-hole 29 may not play any role in clamping of the insert. The cross-hole 29 may have the same shape through the entire thickness of the insert which, in addition to reducing density variations in the green body, can reduce the amount of material used to form the insert. The first side 23 and the second side 25 are typically formed by compaction by, typically, first and second punches (e.g., 127 and 129 in Figures 6A-6B ) and are typically non-planar and have shapes that are the inverse of non-planar surfaces of the first and second punches. Ordinarily, peripheral edges 55 and 57 of the first side 23 and the second side 25 intersect with the side surface 27 and define respective edges that form cutting edges after sintering of the green body. While the first and second sides 23 and 25 may be flat, typically, central regions 59 and 61 of the first and second sides disposed inward of the peripheral edges 55 and 57 have a specially shaped geometry such that overlying portions of the central regions are closer to each other (D4) than at least some overlying portions of the peripheral edges of the first and second sides (D5) as the result of compaction of the material forming the green body between the two opposing punches having appropriately shaped, inverse geometries (e.g., punches 127 and 129 in Figures 6A-6B ). The expression "overlying portions" is intended to refer to portions of the green body at the first and second side and at the side surface adjacent the first and second side that are disposed vertically above one another in the view seen in Figure 6B. It will be appreciated that the insert may be formed in other ways than described above, such as by pressing a compactable material in a die with one fixed surface opposing a movable punch. Planes of the first side 23 and the second side 25 are illustrated as being substantially perpendicular to the side surface 27 and to the pressing direction of the punches 127 and 129 (illustrated by arrows in Figure 6B ), however, it will be appreciated that the planes of the first side and the second side may be inclined relative to the side surface and/or to the pressing direction of the punches. A density of the green body 21 with the quadrilateral-shaped cross-hole is ordinarily substantially uniform between the first side and the second side. Substantially uniform is defined for purposes of the description of the density of the green body as merely meaning more uniform than will typically be achieved in an insert having a circular cross-hole. While not wishing to be bound by theory, considering, first, only compaction caused by providing a quadrilateral-shaped cross-hole 29, as seen in Figures 4A-4I, assuming no friction between compactable material for forming the green body 21 and die tool parts, because more material has to be moved aside to form the cross-hole in the region adjacent the third and fourth points 39 and 41 of the quadrilateral and extending across the width of the green body, compaction of the material is maximum in that region and decreases in a direction toward the first and second points 35 and 37. This is illustrated in Figure 7B by more closely spaced lines L (in a manner similar to the manner by which a contour map illustrates differing degrees of steepness) toward the third and fourth points 39 and 41. At the same time, in case of friction, compaction of the material for forming a green body by opposing punches results in an increased density of the material closest to the first and second sides 23 and 25 and decreasing toward the region mid-way between the first and second sides, illustrated in Figure 7A by more closely spaced lines L closest to the first and second sides 23 and 25 (showing the prior art compaction gradient in a green body of the type shown in Figure 1C that would have been formed by a press tool as shown in Figures 1A and 1B ). As a consequence of the differing compaction gradients or regions, the relatively increased compaction in the region mid-way between the first and second sides 23 and 25 resulting from frictionless formation of the cross-hole 29, as illustrated in Figure 7B, is offset by the relatively decreased compaction in a mid-way region, as shown in Figure 7A, resulting from forming the green body 21 by the opposing punches. Likewise, the relatively increased compaction of the green body 21 in the regions toward the first and second sides 23 and 25 as the result of forming the green body by the opposing punches is offset by the relatively decreased compaction of those regions resulting from frictionless formation of the quadrilateral-shaped cross-hole. Preferably, a density of the green body 21 adjacent the third and fourth points 39 and 41 of the quadrilateral is substantially equal to a density of the green body adjacent the first and second sides 23 and 25. Following compaction of the green body 21, the green body is typically sintered to form a blank having the shape of the green body, albeit smaller because of shrinkage. Because the green body 21 can be formed to have a substantially uniform density, the green body is expected to shrink uniformly during sintering so that accuracy of the shape of the blank can be improved without the need for subsequent processing, or at least with the need for less subsequent processing than is typical in a similar blank having an elliptical or circular cross-hole. A method of making the green body 21 for forming the cutting insert is illustrated in Figures 6A-6B. In the method, two opposing quadrilateral shaped cross-hole pins 121' and 121" (a representative pin 121 is seen in greater detail in Figures 5A-5F ) are positioned in a die 123 so that ends 125' and 125" of the pins contact each other. Material for forming a green body 21 of the cutting insert is introduced into the die in which the two opposing pins 121' and 121" are disposed. The material is compacted between first and second punches 127 and 129 and around the pins 121' and 121" to form a green body 21 as seen in Figures 4A-4I. The green body 21 comprises a first side 23, a second side 25, a side surface 27 extending between the first side and the second sides entirely around the first side and the second side, and a quadrilateral-shaped cross-hole 29 defined by the pins and extending through the green body from a first location 31 on the side surface to a second location 33 on the side surface on an opposite side of the green body from the first location. The pin 121 shown in Figures 5A-5F will ordinarily be the same pin that is used for the pins 121' and 121" shown in Figures 6A-6B. The pin 121 includes a quadrilateral-shaped end 125 and a quadrilateral-shaped cylindrical portion 131 extending from the end to an angled portion 133 that has the inverse shape of the angled inner portion 51" and 53" of the cross-hole. The angled portion 133 transitions to a slightly elliptically or circularly cylindrical portion 135. The quadrilateral-shaped cylindrical portion 131 and the elliptically or circularly cylindrical portion 135 typically transition to a slightly larger quadrilateral-shaped cylindrical portion 131' and a slightly larger elliptically or circularly cylindrical portion 135' at a distance from the end 125 that is one half of the depth of the cross-hole 29 to be formed by the pin 121. The larger quadrilateral-shaped cylindrical portion 131' and larger elliptically or circularly cylindrical portion 135' are sized to minimize the possibility of compactable material for forming the green body being pressed between walls of the cylindrical hole in the die and the larger quadrilateral-shaped cylindrical portion and larger circularly cylindrical portion. While not wishing to be bound by theory, by changing the geometry of the cross hole pin from a conventional slightly elliptical shape into such a quadrilateral shape, it is believed that the mechanism causing the build-up of the density above and below the cross hole pin upon compaction of the compactable material is deactivated. The final result is a green body with a substantially uniform density distribution. Figure 7A shows the typical density distribution that occurs as the result of compaction of the compactable material between opposing punches, similar to the distribution shown in Figure 1C except, instead of showing the variation in compression as a series of regions of different compression, variation in compression is reflected by the closeness of horizontal lines L. Figure 7B shows the density distribution of the green body as it is believed to result where a quadrilateral shaped cross hole pin is used, while assuming that no friction exists between the compactable material and the die walls and between the compactable material and the quadrilateral shaped cross hole pin. It is believed that a relatively low density exists in the top/bottom region, a relatively high density in the middle region, and a medium density in the region between the top/bottom region and the middle region. In addition, Figure 7B shows no build-up of density above the sharp tip of the quadrilateral shaped cross hole pin. It is believed that a sufficiently sharp tip will not be "flat" enough to stop the powder from flowing toward the left or right of the cross-hole pin. In case of no friction, the relative density at a specific point is directly proportionally to the space between the quadrilateral shaped cross hole pin and die wall at that specific point. Figure 7C shows the final density distribution of a green body with quadrilateral shaped cross hole that is the result of compaction between opposing punches as shown in Figure 7A including friction, and frictionless compaction around a quadrilateral-shaped cross-hole pin. The density distribution is uniform because it is assumed that the friction effects on the density distribution of Figure 7A are inversely proportional to the density distribution effects of the frictionless quadrilateral shape cross hole compaction as shown in Figure 7B. Thus, when compacting the material in the die, the material closest to the punches 127 and 129 at the first and second sides 23 and 25 of the green body 21 is compacted more by the punches and due to friction between the die walls and the compactable material than the material mid-way between the first and second sides as seen in Figure 7A. However, the presence of the pins 121' and 121" results in compactable material flowing to the left and right of the first and second points 35 and 37 of the quadrilateral and, at a horizontally widest part of the quadrilateral-shaped cross-hole 29 (assuming the punches 127 and 129 are moving in a vertical direction) by the first and fourth points 39 and 41 of the quadrilateral, being compacted more than material at the horizontally narrowest part of the quadrilateral, i.e., by the first and second points 35 and 37, and more than material above and below the quadrilateral. Thus, compaction increases toward the vertical center of the green body as a result of compaction around the pins 121' and 121" while also increasing in a direction toward the first and second sides 23 and 25 of the green body away from the vertical center of the green body as a result of compaction by the first and second punches 127 and 129. These two offsetting compaction effects tend to reduce variation in density in the green body 21 between the first and second sides 23 and 25. In the present application, the use of terms such as "including" is open-ended and is intended to have the same meaning as terms such as "comprising" and not preclude the presence of other structure, material, or acts. Similarly, though the use of terms such as "can" or "may" is intended to be open-ended and to reflect that structure, material, or acts are not necessary, the failure to use such terms is not intended to reflect that structure, material, or acts are essential. To the extent that structure, material, or acts are presently considered to be essential, they are identified as such.

1. A green body (21) for a cross-hole, compacted cutting insert, comprising: a first side (23), a second side (25), and a side surface (27) extending between the first side (23) and the second side (25) entirely around the first side (23) and the second side (25), characterized in that the green body (21) comprises a quadrilateral-shaped cross-hole (29) extending through the green body (21) from a first location (31) on the side surface (27) to a second location (33) on the side surface (27) on an opposite side of the green body (21) from the first location (31), and the quadrilateral-shaped cross-hole (29) has first and second points (35 and 37) of the cross-hole (29) closest to the first and second sides (23 and 25) of the green body (21), respectively, and third and fourth points (39 and 41) of the cross-hole (29) between the first and second points (35 and 37).

2. The green body (21) for a cross-hole, compacted cutting insert as set forth in claim 1, wherein a distance (D1) between the first and second points (35 and 37) is greater than a distance (D2) between the third and fourth points (39 and 41). 3. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-2, wherein the side surface (27) is a substantially cylindrical surface. 4. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-3, wherein the side surface (27) has at least two, opposing, portions (43 and 45), and in that the first location (31) and the second location (33) are disposed on the two portions (43 and 45). 5. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-4, wherein the first side (23) and the second side (25) are non-planar. 6. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-5, wherein peripheral edges (55 and 57) of the first side (23) and the second side (25) intersect with the side surface (27) and define an edge. 7. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-6, wherein a density of the green body (21) is substantially uniform between the first side (23) and the second side (25). 8. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-7, wherein the cross-hole (29) has a quadrilateral shape with first and second points (35 and 37) of the cross-hole (29) closest to the first and second sides (23 and 25) of the green body (21), respectively, and third and fourth points (39 and 41) of the cross-hole (29) between the first and second points (35 and 37), wherein a density of the green body (21) adjacent the third and fourth points (39 and 41) of the cross-hole (29) is substantially equal to a density of the green body (21) adjacent the first and second sides (23 and 25). 9. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-8, wherein the third and fourth points (39 and 41) of the cross-hole (29) are disposed mid-way between the first and second sides (23 and 25) of the green body (21). 10. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-9, wherein the first and second points (35 and 37) of the cross-hole (29) are disposed at equal distances from the first and second sides (23 and 25), respectively. 11. The green body (21) for a cross-hole, compacted cutting insert as set forth in any of claims 1-10, wherein the cross-hole (29) comprises generally circular countersunk portions (51 and 53) centered at the first location (31) and the second location (33). 12. The green body (21) for a cross-hole, compacted cutting insert as set forth in claim 11, wherein the circular countersunk portions (51 and 53) each includes a substantially cylindrical portion (51' and 53') extending to the side surface (27) and an inner portion (51" and 53") that defines a non-zero angle with the substantially cylindrical portion (51' and 53') and with the side surface (27) adjacent the cross-hole (29). 13. A cutting insert made from the green body (21) for a cross-hole compacted cutting insert as set forth in any of claims 1-12.

2886228

Chuck

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Referring to the Figures 1-5, a first embodiment of a chuck according to the invention will now be described. The chuck comprises a general rotation symmetric chuck body 1 of a generally homogenous metal material which is rotatable around a rotation axis 2. The chuck body is in one end formed with an attachment portion 3, which in the embodiments shown herein is in form of a tapered, non-circular shaft of a commonly known type which is adapted to be secured to a not shown mating motor-driven spindle of a working machine. In the opposite end the chuck body is provided with a circular cylindrical chuck bore 4, which is adapted to receive and clamp a shank 5 of a machining tool 6. A shank of a machining tool in form of a shank end mill is shown inserted into the chuck bore of the various drawings. The chuck is of the kind which clamps the tool shank by means of a hydraulic pressure. For this purpose, the chuck is provided with a hydraulic clamping element in form of a rather thin-walled clamping collet 7 inserted into the chuck bore, as is best seen in Figures 4a-b. In a way known per se, the collet is at least in its ends connected to the chuck body 1 in a fluid- and gastight fashion, e.g. by soldering. The intermediate portion of the collet between its ends is disengaged from the chuck body and fluid channels 8 for the hydraulic fluid are arranged in the area between the collet 7 and the chuck body 1 into which pressurized hydraulic fluid may be fed through a hydraulic supply channel 9 from a not shown pressure generating means, which for example can be formed as a hydraulic piston being controllable by means of a screw or the like which are positioned inside of a hole 10 in the chuck body 1 as is shown e.g. in Figures 1 and 6. When pressurized hydraulic fluid is forced into the space between the collet 7 and the chuck body 1, the collet will tend to deflect inwards and accordingly clamp around the tool shank 5. According to the invention, the chuck is provided with an attachment member, which is positionable in a mounting portion 11 located at an inner end of the chuck bore 4. In a first embodiment of the invention, illustrated in Figures 1-5, the attachment member is generally formed as a sleeve 12 having a generally circular cross section. The envelope surface of the sleeve is formed with splines 13 having grooves and ridges in the axial direction. The mounting portion 11 has a generally circular cross section and is formed with splines 14 having grooves and ridges in the axial direction around its circumference which mates with the splines 13 of the sleeve 12 such that the sleeve can be inserted with snug fit within the mounting portion 11. Accordingly, when the sleeve 12 is positioned within the mounting portion it will be prevented from rotation but will be displaceable in the axial direction. Preferably, the grooves of the splines on the circumference of the mounting portion may have a part-circular shape in cross section. With grooves shaped in this way they can easily be machined by means of a shank end mill which is beneficial because of the limited space at the end of the chuck bore. Accordingly, it is also preferred that also the ridges of the splines at the attachment member have a part-circular shape in cross section. In the first embodiment, the machining tool 6 in form of a shank end mill, is attachable to the sleeve shaped attachment member 12 by means of a conical shaped male thread 15 formed in the end of the tool shank 5 which can be threaded into a mating conical female thread in the outer end of the sleeve. This is best illustrated in Figures 3 and 5. When the tool 6 is threaded into engagement with the attachment member 12, the tool will be prevented from being pulled apart in the axial direction from the attachment member and will also be prevented from being rotated in one direction in relation to the attachment member. The attachment member 12 is in its turn attachable to the chuck body 1 by means of a double-threaded regulating screw 16, as shown in Figure 3, having a right-hand thread 17 in one end portion, which end is also formed with a suitably engagement formation, e.g. in form of an Allen aperture 18, for engagement and rotation by means of a tool, e.g. an Allen key 19. The other end portion of the regulating screw is formed with a left-hand thread 20. The right-hand thread 17 can be threaded into a matching right-hand female thread in a hole 21 inside the chuck body at the inner end of the mounting portion for the attachment member, whereas the left-hand thread 20 can be threaded into a mating left-hand female thread in a hole 43 at the inner end of the attachment member 12. With a chuck as described above, the tool 6 can be securely mounted in the chuck bore on the one hand by means of a clamping force from the hydraulic pressure acting on the tool shank 5 from the deflectable collet 7, and on the other hand be prevented from being pulled out in the axial direction as well as being rotated in one direction by means of the threaded connection between the tool shank 5 and the attachment member 12, which in its turn is prevented from being rotated in relation to the chuck body 1 by means of the splines connection 13, 14 between the attachment member 12 and the mounting portion 11 of the chuck body, as well as being prevented from being pulled out from the chuck body by means of the double-threaded regulating screw 16 interconnecting the attachment member 12 and the chuck body 1. Furthermore, by means of the chuck, the projecting length of the tool 6 from the chuck body 1 can readily be regulated, such as is schematically illustrated in Figures 4a and 4b. More precisely, before clamping the tool shank 5 by applying a hydraulic pressure on the clamping collet 7, the projecting length can be regulated by rotating the regulating screw 16 by means of a tool, e.g. an Allen key 19, from the inner end of the chuck body. By rotating the Allen key in the direction as illustrated in Figure 4a, the attachment member 12 can, due to the splines connection 13, 14, be drawn further into the mounting portion 11 of the chuck body, which will also draw the machining tool 6 further into the chuck bore 4. When, on the other hand, the Allen key 19 is rotated in the opposite direction, as illustrated in Figure 4b, the attachment member 12 will be displaced outwards from the mounting portion 11 and the machining tool 6 will also be displaced outwards in relation to the chuck bore. When the correct projecting length of the machining tool has been obtained, a hydraulic pressure is applied to the clamping collet 7, which accordingly will clamp around the tool shank 5. A second embodiment of the inventive chuck, as illustrated in the Figures 6-13, has a similar outer appearance as the first embodiment which can be seen from Figure 6. Accordingly, also this chuck comprises a general rotation symmetric chuck body 1 of a generally homogenous metal material which is rotatable around a rotation axis 2. The chuck body is in one end formed with an attachment portion 3, which in the embodiments shown herein is in form of a tapered, non-circular shaft of a commonly known type which is adapted to be secured to a not shown mating motor-driven spindle of a working machine. In the opposite end the chuck body is provided with a circular cylindrical chuck bore 4, which is adapted to receive and clamp a shank 5 of a machining tool 6. A shank of a machining tool in form of a shank end mill is shown inserted into the chuck bore of the various drawings. Also this chuck is of the kind which clamps the tool shank by means of a hydraulic pressure. For this purpose, the chuck is provided with a hydraulic clamping element in form of a rather thin-walled clamping collet 7 inserted into the chuck bore, as is best seen in Figures 9a and 9b. The clamping collet is identical with and functions in the same way as the clamping collet described in relation to the first embodiment. However, the chuck according to this embodiment differs from the first embodiment in that the attachment member, the regulating mechanism of the attachment member and the connection between the tool shank and the attachment member are differently designed. Here, the attachment member has the overall shape of a yoke 22 having two yoke shanks 23', 23" projecting inward in the axial direction from a cylindrical base part 24 having a circular cross section and which in an outer end is provided with a female bayonet coupling part 25 mating with a male bayonet coupling part 26 in an inner end of the tool shank 5. The bayonet coupling 25, 26 is illustrated in more detail in Figure 11, which is a cross section along the line XI-XI in Figure 10 which shows the attachment member 22 and the machining tool 6 in an assembled state. As evident from Figure 11 in combination with Figures 9a and 9b, the male bayonet coupling part 26 of the tool is formed with a shank portion 27 having a circular cross section closest to the tool shank, and an inner head portion 28 having a somewhat "triangular" shape. The female bayonet coupling part 25 has a somewhat "triangular" inlet opening closest to the outer end of the attachment member 22, through which the triangular head 28 of the male bayonet coupling part 26 may pass. Inward from the triangular inlet opening, the female bayonet coupling part 25 is formed with recesses 30 in the areas between the apexes 31 of the triangular inlet opening, such that when the triangular head 28 of the male bayonet coupling part 26 has passed the triangular inlet opening of the female bayonet coupling part, the male and female bayonet coupling parts can engage with each other by a further minor rotation of the tool shank 5 in relation to the attachment member 22 to the position as illustrated in Figure 11. In this position the apexes 32 of the triangular head 28 of the male bayonet coupling part 26 will be locked in the recesses 30 against pull-out in the axial direction as well as against rotation in one direction. As is evident from Figure 12, the chuck is also provided with a spring 33 in the inner end of the female bayonet coupling part 25 acting to press the male bayonet coupling part 26 and accordingly also the machining tool 6 in an axial direction outwards. With reference to the Figures 7, 8, 9a, 9b, 12 and 13 follows hereinafter a description of the pull out and rotary preventing means for the attachment member 22 as well as of the mechanism for regulating the axial projecting length of the machining tool 6 from the chuck. As is evident from the drawings, two locking rods 34', 34" are accommodated in a hole 35 transverse to the axial direction of the chuck and are extended through the space between the yoke shanks 23', 23" and are partly overlapping each other. The locking rods are adjustably telescoping interconnected by means of a regulating rod 36 having one right-hand thread 37 and one left-hand thread 38. The regulating rod is extended through and in threaded engagement with a hole 39 in each of the locking rods, such that when rotating the regulating rod 36 in one direction by means of a suitable tool, such as by e.g. an Allen key 19 in engagement with an Allen aperture 40 in one of the ends of the regulating rod, the locking rods 34', 34" will be displaced in a direction apart from each other, and when rotating the regulating rod in the other direction, the locking rods will be displaced in a direction towards each other. Moreover, the yoke shanks 23', 23" are in the inner surfaces facing each other, provided with diagonally oppositely directed grooves 41, and the locking rods are provided with guide surfaces which, in the assembled state of the mechanism, are facing in opposite directions and are provided with diagonally oppositely directed ridges 42. In the assembled state of the mechanism, the diagonally oppositely directed grooves 41 of the yoke shanks and the diagonally oppositely directed ridges 42 of the locking rods are in engagement with each other such that pull out of the attachment member in the axial direction, and hence also the machining tool, is prevented. Since the attachment member 22 is formed as a yoke and the locking rods extends through intermediate space between the two yoke shanks, the attachment member will also be prevented from rotation in both directions. In Figures 9a and 9b is illustrated the procedure for regulating the projecting length of the machining tool 6 from the chuck. When rotating the regulating rod 36 in one direction by means of an Allen key 19, as is illustrated in Figure 9a, the locking rods 34', 34" will be synchronously displaced in a direction towards each other. Accordingly, the engagement between the diagonally oppositely directed ridges 42 of the locking rods and the diagonally oppositely directed grooves 41 of the yoke shanks 23', 23" will cause a retraction of the attachment member 22, and hence also the machining tool 6, into the chuck. When, on the other hand, the regulating rod 36 is rotated in the opposite direction, as is illustrated in Figure 9b, the attachment member and the machining tool will be synchronously displaced in a direction outward from the chuck. The synchronously displacement of the locking rods is advantageous since due to that the dynamic balance of the chuck will be maintained regardless of the projecting length of the machining tool. It is also advantageous to be able to regulate the projecting length of the machining tool from a direction transverse to the rotary axis of the chuck, since then it is possible to regulate the projecting length while the chuck is mounted in the machine. With a chuck according to the first embodiment it is necessary to first remove the chuck from the machine before performing the regulating.

1. A rotatable chuck for clamping a shank portion (5) of a rotatably operating machining tool (6), comprising a rotatable chuck body (1) provided with a cylindrical bore (4) being concentric with a rotation axis (2) of the rotatable chuck body, wherein circumferential surfaces of a clamping portion (7) of the bore are adapted to apply a clamping force around the circumference of the shank portion of the tool when it is mounted in the chuck to fixate the tool in a well-defined position in the chuck, and wherein the chuck also is provided with auxiliary pull out preventing means, for preventing inadvertent pull out of the tool in the axial direction of the bore during machining operation, as well as auxiliary rotary preventing means for preventing inadvertent rotation in at least one direction in relation to the chuck during machining operation, c h a r a c t e r i z e d in that the auxiliary pull out and rotary preventing means comprises an attachment member (12, 22) being positionable in an inner portion of the bore (4) and being attachable to the shank portion (5) to be clamped, such that the tool (6) and the attachment member will be prevented from being pulled apart in the axial direction as well as be prevented from being rotated in at least one direction in relation to each other, wherein the rotatable chuck body (1) also comprises an axial pull out preventing means as well as a rotary preventing means in at least one direction, arranged to engage with the attachment member.

2. The chuck according to claim 1, wherein the axial position of the attachment member is continuously adjustably displaceable and lockable in different positons within the chuck body. 3. The chuck according to claim 1 or 2, wherein the attachment member is sleeve shaped and is on an envelope surface formed with splines, having grooves and ridges in the axial direction, which are adapted to engage with mating splines at a mounting portion of the chuck body. 4. The chuck according to any of the preceding claims, wherein the attachment member is provided with a threaded hole in its inner end and the chuck body is provided with a threaded hole inward of the mounting portion, such that the attachment member is attachable to the chuck body by means of a screw. 5. The chuck according to claim 4, wherein the screw is a regulating screw which can be utilized to regulate an axial position of the attachment member inside the chuck body and a projecting length of the machining tool from the chuck body. 6. The chuck according to claim 4 or 5, wherein the regulating screw is formed with one right-hand thread and one left-hand thread. 7. The chuck according to any of the claims 1-3, wherein the attachment member is formed as a yoke having two yoke shanks projecting in the axial direction. 8. The chuck according to claim 7, wherein the pull out and rotation preventing means comprises a locking rod which is accommodated in a hole in the chuck body transverse to the axial direction, and extends through the space between the yoke shanks. 9. The chuck according to claim 7, wherein the pull out and rotation preventing means comprises two locking rods, which are accommodated in a hole in the chuck body transverse to the axial direction, and extend through the space between the yoke shanks, wherein the locking rods are adjustably telescoping interconnected by means of a regulating rod. 10. The chuck according to claim 9, wherein the locking rods are provided with engagement formations which are adapted to engage with mating engagement formations provided on the yoke shanks. 11. The chuck according to claim 10, wherein the engagement formations provided on the locking rods and the yoke shanks are formed as diagonally oppositely directed grooves and ridges. 12. The chuck according to any of the preceding claims, wherein the attachment member is provided with a male or female thread in its outer end which is adapted to engage with a mating thread at the inner end of the tool shank. 13. The chuck according to claim 12, wherein the thread is conical shaped. 14. The chuck according to any of the claims 1-11, wherein the attachment member is provided with a male or female bayonet coupling part, which is adapted to engage with a mating bayonet coupling part at the inner end of the tool shank. 15. The chuck according to claim 14, wherein the bayonet coupling part is provided with a spring adapted to apply a force acting in an axial outward direction on the tool shank.

2887111

Lens holder

Based on the following detailed description of an invention, generate the patent claims. There should be 5 claims in total. The first, independent claim is given and the remaining 4 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described more fully hereinafter with reference to the accompanying drawings, in which certain embodiments of the invention are shown. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided by way of example so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like numbers refer to like elements throughout. Figure 1 is an exploded perspective view of an embodiment of the inventive arrangement for attaching a lens to a lens holder. The arrangement 100 comprises a lens holder 200 and a fixing part 300. In some embodiments the arrangement 100 also comprises a lens 400, and a PCB (printed circuit board) 140 having an image sensor 145. In a further embodiment the arrangement also comprises an insulating component 150. The insulating component 150 protects the image sensor 145 and the lens 400 from, e.g., dust. Figure 2 is a perspective view of an embodiment of the inventive lens holder for attaching a lens. The lens holder 200 comprises a compressible retainer 210. The compressible retainer 210 has a plurality of projections 220. The plurality of projections 220 are arranged at distances from each other. In one embodiment, the distances between the plurality of projections 220 are equally long. In another embodiment, the distances between the plurality of projections 220 have different lengths. In one embodiment, the plurality of projections 220 each have a protrusion 230 protruding in a direction parallel with the radius of curvature of the compressible retainer 210. When attaching a lens to the lens holder, an attachment portion 410 (see, Figure 4 ) of the lens 400 is inserted into the compressible retainer 210. The compressible retainer 210 can be compressed by means of a clamping force. The clamping force can be a predetermined clamping force. A pressure regulator, other types of pneumatic tools, or any kind of mechanics may be used in order to provide a predetermined clamping force. When the compressible retainer 210 is compressed, a radius of curvature of the compressible retainer 210 is reduced. When the compressible retainer 210 is compressed, the plurality of projections 220 are pressed towards each other and/or inwards toward a center of the lens holder 200 in a direction parallel with the radius of curvature of the compressible retainer 210. More specifically, the plurality of projections 220 are pressed towards the attachment portion 410 of the lens 400 to be attached to the lens holder 200. In the embodiment having protrusions 230, the protrusions 230 are pressed towards the attachment portion 410. The lens holder can, e.g., be made of plastic. The plastic can, e.g., include polycarbonate and/or glass fiber. Figure 3 is a perspective view of an embodiment of the inventive fixing part. The fixing part 300 has a pressing part 310 and a fixing arc 320. The pressing part 310 has two legs 312. The legs 312 are each connected to the ends of the fixing arc 320. Furthermore, the pressing part 310 has an intermediate portion 314, the intermediate portion 314 having a concavity 315. The fixing arc 320 is arranged to fit around a compressible retainer, e.g., the compressible retainer 210. If the pressing part 310 is pressed, more specifically if the legs 312 are pressed, a radius of curvature of the fixing arc 320 is reduced such that the compressible retainer 210 is compressed. The fixing part can be made of metal, e.g., stainless steel. The fixing part can be manufactured by, e.g., bending a strip and welding its ends together or by cutting an appropriately shaped tube. The fixing part can, e.g., have a width in the range of 0,5 mm-3 cm. In one embodiment, the fixing part has a width of 5 mm. The fixing part 700 can have a plurality of pressing parts 710. This is illustrated in Figure 8 which is a perspective view of an embodiment of the inventive fixing part. The fixing part 700 has a plurality of pressing parts 710 and the fixing arc has a plurality of arc portions 712. The pressing parts 710 are at their ends connected to the arc portions 720. If the pressing parts are pressed 710, the radius of curvature r3 of the fixing arc is reduced. The legs 712 correspond to the legs 312 and the intermediate 714 portion having a concavity 715 corresponds to the intermediate 314 portion having a concavity 315. Herein, when referring to fixing arc 320 it is also, where applicable, referred to the fixing arc having the fixing arc portions 720. Figure 4 is a perspective view of a lens 400. The lens comprises an attachment portion 410. The lens can, e.g., be a wide-angle lens. The lens can be any kind of lens system with an attachment part. Figure 5 is a perspective view of an embodiment of the inventive arrangement comprising the fixing part 300 of Figure 3, the lens holder 200 of Figure 2, and the image sensor 145 of Figure 1. The fixing arc 320 is arranged around the compressible retainer 210. The image sensor 145 is attached to the lens holder 200 or is ready to be attached to the lens holder 200. The image sensor can, e.g., be attached to the lens holder by gluing. Figure 6 is a perspective view of a cross-section of the embodiment of Figure 5. Also visible here is the insulating component 150 of Figure 1. Figure 7 is a perspective view of an embodiment of the inventive arrangement. The arrangement 100 in Figure 7 corresponds to the 100 arrangement of Figure 1 and comprises a lens 400, a fixing part 300, a lens holder 200 and an image sensor 145. The arrangement 100 is in Figure 7 in a calibration mode. The calibration mode comprises the attachment portion 410 being arranged in the compressible retainer 210, the fixing part being 300 arranged around the compressible retainer 210, and the fixing part 200 being open. In the calibration mode, the lens 400 and its attachment portion 410 is free to move. The position of the lens 400 in relation to the lens holder 200 can be adjusted by, e.g., rotating the lens 400 or the lens holder 200, or by moving the lens 400 and/or the lens holder 200 towards or away from each other. The distance between the lens 400 and the image sensor 145 is sometimes referred to as the flange back distance. By adjusting the flange back distance, a desirable focus can be obtained throughout the whole zooming range of the lens 400. In one embodiment, the step of moving the attachment portion comprises moving the attachment portion until a depth of field of the camera formed by the lens and the image sensor is maximized. The arrangement 100 can be in a fixed mode, as is illustrated by Figure 7b in combination with Figure 7 and Figure 7a. Figure 7a is a perspective view of an embodiment of the inventive fixing part drawn out from the arrangement of Figure 7. Figure 7b is a perspective view of the inventive fixing part of Figure 7a. The fixing part in Figure 7b is closed. The fixed mode comprises the fixing part 300 being closed which comprises the fixing part 300 having a smaller radius of curvature than when open, such that the compressible retainer 210 of the lens holder 200 is compressed around the attachment portion 410, thereby attaching the lens 400 to the lens holder 200. In the fixed mode, the attachment portion 210 and the lens holder 200 are not free to move in relation to each other. In the following, an embodiment of the inventive method for attaching a lens to a lens holder will be presented with reference to Figures 1-8. A fixing arc 320 of a fixing part 300 is arranged around a compressible retainer 210 of a lens holder 200. An attachment portion 410 of the lens 400 is inserted into the compressible retainer 210. A radius of curvature of the fixing arc 320 is reduced, such that the compressible retainer 210 of the lens holder 20 is compressed around the attachment portion 410, thereby attaching the lens 400 to the lens holder 200. The pressing part 310 of the fixing part 300 is pressed such that the radius of curvature of the fixing arc 320 is reduced. If the fixing part has a plurality of pressing parts and the fixing arc has a plurality of arc portions, then the pressing parts are pressed such that the radius of curvature of the fixing arc is reduced. The pressing of the pressing part can be performed by means of a predetermined force. A pressure regulator may be used or other types of pneumatic tools, in order to provide a predetermined pressing force. Before the step of reducing the radius of curvature of the fixing arc, an image sensor may be attached to the lens holder. Then, the attachment portion may be moved until a desirable distance between the attachment portion and the image sensor is obtained. As an alternative, the lens is attached to the lens holder before the image sensor being attached to the lens holder. The attachment portion is for instance inserted into the lens holder as far as it gets. The radius of curvature of the fixing arc is reduced such that the compressible retainer of the lens holder is compressed around the attachment portion thereby attaching the lens to the lens holder. After that the image sensor is attached to the lens holder. The focus can then be adjusted using a focus mechanism of the lens. Image based adjustment system (IBAS) can be used for calculating the current focus value of the lens. It is to be noted that all embodiments and features described in this application are applicable on all aspects of the invention.

1. Method for attaching a lens (400) to a lens holder (200), comprising: arranging a fixing arc (320) of a fixing part (300) around a compressible retainer (210) of the lens holder (200), inserting an attachment portion (410) of the lens (400) into the compressible retainer (210), and reducing a radius of curvature (r2) of the fixing arc (320), such that the compressible retainer (210) of the lens holder (200) is compressed around the attachment portion (410), thereby attaching the lens (400) to the lens holder (200).

2. Method according to claim 1, further comprising: the fixing part (300) having a pressing part (312), the pressing part (312) being at its ends connected to the fixing arc (320), and the step of reducing further comprising: pressing the pressing part (312) thus reducing the radius of curvature (r2) of the fixing arc (320). 3. Method according to claim 1,: the fixing part (700) having a plurality of pressing parts (712), and the fixing arc having a plurality of arc portions (720),: the pressing parts (712) being at their ends connected to the arc portions (720), and the step of reducing further comprising: pressing the pressing parts (712) thus reducing the radius of curvature (r3) of the fixing arc. 4. Method according to any one of claims 1-3, the step of pressing further comprising: pressing by means of a predetermined force. 5. Method according to any one of claims 1-4, comprising, before the step of reducing: attaching an image sensor (145) to the lens holder (200), moving the attachment portion (410) until a desirable distance between the attachment portion (410) and the image sensor (145) is obtained, and/or moving the attachment portion (410) until a desirable rotational angle of the lens (400) is obtained.

2887111

Lens holder

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will now be described more fully hereinafter with reference to the accompanying drawings, in which certain embodiments of the invention are shown. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided by way of example so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like numbers refer to like elements throughout. Figure 1 is an exploded perspective view of an embodiment of the inventive arrangement for attaching a lens to a lens holder. The arrangement 100 comprises a lens holder 200 and a fixing part 300. In some embodiments the arrangement 100 also comprises a lens 400, and a PCB (printed circuit board) 140 having an image sensor 145. In a further embodiment the arrangement also comprises an insulating component 150. The insulating component 150 protects the image sensor 145 and the lens 400 from, e.g., dust. Figure 2 is a perspective view of an embodiment of the inventive lens holder for attaching a lens. The lens holder 200 comprises a compressible retainer 210. The compressible retainer 210 has a plurality of projections 220. The plurality of projections 220 are arranged at distances from each other. In one embodiment, the distances between the plurality of projections 220 are equally long. In another embodiment, the distances between the plurality of projections 220 have different lengths. In one embodiment, the plurality of projections 220 each have a protrusion 230 protruding in a direction parallel with the radius of curvature of the compressible retainer 210. When attaching a lens to the lens holder, an attachment portion 410 (see, Figure 4 ) of the lens 400 is inserted into the compressible retainer 210. The compressible retainer 210 can be compressed by means of a clamping force. The clamping force can be a predetermined clamping force. A pressure regulator, other types of pneumatic tools, or any kind of mechanics may be used in order to provide a predetermined clamping force. When the compressible retainer 210 is compressed, a radius of curvature of the compressible retainer 210 is reduced. When the compressible retainer 210 is compressed, the plurality of projections 220 are pressed towards each other and/or inwards toward a center of the lens holder 200 in a direction parallel with the radius of curvature of the compressible retainer 210. More specifically, the plurality of projections 220 are pressed towards the attachment portion 410 of the lens 400 to be attached to the lens holder 200. In the embodiment having protrusions 230, the protrusions 230 are pressed towards the attachment portion 410. The lens holder can, e.g., be made of plastic. The plastic can, e.g., include polycarbonate and/or glass fiber. Figure 3 is a perspective view of an embodiment of the inventive fixing part. The fixing part 300 has a pressing part 310 and a fixing arc 320. The pressing part 310 has two legs 312. The legs 312 are each connected to the ends of the fixing arc 320. Furthermore, the pressing part 310 has an intermediate portion 314, the intermediate portion 314 having a concavity 315. The fixing arc 320 is arranged to fit around a compressible retainer, e.g., the compressible retainer 210. If the pressing part 310 is pressed, more specifically if the legs 312 are pressed, a radius of curvature of the fixing arc 320 is reduced such that the compressible retainer 210 is compressed. The fixing part can be made of metal, e.g., stainless steel. The fixing part can be manufactured by, e.g., bending a strip and welding its ends together or by cutting an appropriately shaped tube. The fixing part can, e.g., have a width in the range of 0,5 mm-3 cm. In one embodiment, the fixing part has a width of 5 mm. The fixing part 700 can have a plurality of pressing parts 710. This is illustrated in Figure 8 which is a perspective view of an embodiment of the inventive fixing part. The fixing part 700 has a plurality of pressing parts 710 and the fixing arc has a plurality of arc portions 712. The pressing parts 710 are at their ends connected to the arc portions 720. If the pressing parts are pressed 710, the radius of curvature r3 of the fixing arc is reduced. The legs 712 correspond to the legs 312 and the intermediate 714 portion having a concavity 715 corresponds to the intermediate 314 portion having a concavity 315. Herein, when referring to fixing arc 320 it is also, where applicable, referred to the fixing arc having the fixing arc portions 720. Figure 4 is a perspective view of a lens 400. The lens comprises an attachment portion 410. The lens can, e.g., be a wide-angle lens. The lens can be any kind of lens system with an attachment part. Figure 5 is a perspective view of an embodiment of the inventive arrangement comprising the fixing part 300 of Figure 3, the lens holder 200 of Figure 2, and the image sensor 145 of Figure 1. The fixing arc 320 is arranged around the compressible retainer 210. The image sensor 145 is attached to the lens holder 200 or is ready to be attached to the lens holder 200. The image sensor can, e.g., be attached to the lens holder by gluing. Figure 6 is a perspective view of a cross-section of the embodiment of Figure 5. Also visible here is the insulating component 150 of Figure 1. Figure 7 is a perspective view of an embodiment of the inventive arrangement. The arrangement 100 in Figure 7 corresponds to the 100 arrangement of Figure 1 and comprises a lens 400, a fixing part 300, a lens holder 200 and an image sensor 145. The arrangement 100 is in Figure 7 in a calibration mode. The calibration mode comprises the attachment portion 410 being arranged in the compressible retainer 210, the fixing part being 300 arranged around the compressible retainer 210, and the fixing part 200 being open. In the calibration mode, the lens 400 and its attachment portion 410 is free to move. The position of the lens 400 in relation to the lens holder 200 can be adjusted by, e.g., rotating the lens 400 or the lens holder 200, or by moving the lens 400 and/or the lens holder 200 towards or away from each other. The distance between the lens 400 and the image sensor 145 is sometimes referred to as the flange back distance. By adjusting the flange back distance, a desirable focus can be obtained throughout the whole zooming range of the lens 400. In one embodiment, the step of moving the attachment portion comprises moving the attachment portion until a depth of field of the camera formed by the lens and the image sensor is maximized. The arrangement 100 can be in a fixed mode, as is illustrated by Figure 7b in combination with Figure 7 and Figure 7a. Figure 7a is a perspective view of an embodiment of the inventive fixing part drawn out from the arrangement of Figure 7. Figure 7b is a perspective view of the inventive fixing part of Figure 7a. The fixing part in Figure 7b is closed. The fixed mode comprises the fixing part 300 being closed which comprises the fixing part 300 having a smaller radius of curvature than when open, such that the compressible retainer 210 of the lens holder 200 is compressed around the attachment portion 410, thereby attaching the lens 400 to the lens holder 200. In the fixed mode, the attachment portion 210 and the lens holder 200 are not free to move in relation to each other. In the following, an embodiment of the inventive method for attaching a lens to a lens holder will be presented with reference to Figures 1-8. A fixing arc 320 of a fixing part 300 is arranged around a compressible retainer 210 of a lens holder 200. An attachment portion 410 of the lens 400 is inserted into the compressible retainer 210. A radius of curvature of the fixing arc 320 is reduced, such that the compressible retainer 210 of the lens holder 20 is compressed around the attachment portion 410, thereby attaching the lens 400 to the lens holder 200. The pressing part 310 of the fixing part 300 is pressed such that the radius of curvature of the fixing arc 320 is reduced. If the fixing part has a plurality of pressing parts and the fixing arc has a plurality of arc portions, then the pressing parts are pressed such that the radius of curvature of the fixing arc is reduced. The pressing of the pressing part can be performed by means of a predetermined force. A pressure regulator may be used or other types of pneumatic tools, in order to provide a predetermined pressing force. Before the step of reducing the radius of curvature of the fixing arc, an image sensor may be attached to the lens holder. Then, the attachment portion may be moved until a desirable distance between the attachment portion and the image sensor is obtained. As an alternative, the lens is attached to the lens holder before the image sensor being attached to the lens holder. The attachment portion is for instance inserted into the lens holder as far as it gets. The radius of curvature of the fixing arc is reduced such that the compressible retainer of the lens holder is compressed around the attachment portion thereby attaching the lens to the lens holder. After that the image sensor is attached to the lens holder. The focus can then be adjusted using a focus mechanism of the lens. Image based adjustment system (IBAS) can be used for calculating the current focus value of the lens. It is to be noted that all embodiments and features described in this application are applicable on all aspects of the invention.

6. Lens holder (200) for attaching a lens (400) comprising: a compressible retainer (210) arranged to receive an attachment portion (410) of the lens (400), the compressible retainer (210) being arranged to be compressed such that a radius of curvature (r1) of the compressible retainer (210) is reduced, thereby attaching the lens (400) to the lens holder (200).

7. Lens holder (200) according to claim 6, the compressible retainer (210) being arranged to be compressed by means of a clamping force. 8. Lens holder (200) according to claim 6 or 7, the compressible retainer (210) comprising a plurality of projections (220) spaced apart. 9. Lens holder (200) according to claim 8, the plurality of projections (220) each having a protrusion (230) protruding in a direction parallel with the radius of curvature (r1) of the compressible retainer (210). 10. Arrangement (100) for attaching a lens (400) to a lens holder (200), comprising: the lens holder (200) according to any one of claims 6-9, a fixing part (300) having a pressing part (310) and a fixing arc (320), the pressing part being (310) at its ends connected to the fixing arc (320), the fixing arc (320) being arranged to fit around the compressible retainer (210) and, if the pressing part (310) is pressed, a radius of curvature (r2) of the fixing arc (320) is arranged to be reduced such that the compressible retainer (210) is compressed. 11. Arrangement (100) according to claim 10, the pressing part (310) having two legs (312), each connected to the ends of the fixing arc (320), and an intermediate portion (314), the intermediate portion (314) having a concavity (315). 12. Arrangement (100) according to any one of claims 10-11, the fixing part being (300) made of metal. 13. Arrangement (100) according to any one of claims 10-12, the arrangement (100) having a fixed mode comprising: the fixing part (300) being closed which comprises the fixing arc (320) having a smaller radius of curvature (r2) than when the fixing part (300) is open, such that the compressible retainer (210) of the lens holder (200) is compressed around the attachment portion (410) thereby attaching the lens (400) to the lens holder (200). 14. Arrangement (100) according to any one of claims 10-13, the arrangement (100) having a calibration mode comprising: the attachment portion (410) being arranged in the compressible retainer (210), the fixing arc (320) being arranged around the compressible retainer (210), and the fixing (300) part being open. 15. Arrangement (100) according to any one of claims 10-14,: the fixing part (700) having a plurality of pressing parts (712), and the fixing arc having a plurality of arc portions (720),: the pressing parts (712) being at their ends connected to the arc portions (720),: if the pressing parts (712) are pressed, the radius of curvature (r3) of the fixing arc is arranged to be reduced.

2886300

Method of manufacturing a liner, liner, and appliance

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to Figure 1, a sheet 2 is shown which has been extruded in extrusion direction 4, which is a first step or procedure of the manufacturing method according to the present invention. The extrusion process can be performed by an extruding apparatus as known from the art. The extruded sheet 2 comprises a rectangular form or shape having a side lengths which lie between 1,5 - 2,5 m in the present preferred embodiment. The sheet 2 is displayed in Figure 2 after structural features such as ribs 14 and ribs 16 have been formed in a forming step. The forming step can further involve low deep drawing forming, which can be conducted by a conventional process known from the art such as vacuum forming, hot sheet forming etc. The forming step can in preferred embodiments be conducted by thermoforming or other suitable methods and is only an optional step in the described method. With reference to Figure 3, sheet 2 is shown after it has gone through a perimeter trimming operation in which in the regions of each of its four corners 6, a substantially rectangular piece was cut off, resulting in a pre-shaped sheet 2 for the forthcoming operations. The cut-off rectangular pieces in the present embodiment are all of the same size and - taken into account mirror symmetry - identical in shape. The perimeter trimming step as described in connection with Figure 3 has a distinct advantage over techniques known form the art: the usual step of deep thermoforming sheet 2 displayed in Figure 1 involving high stretching of the sheet 2 to obtain the shape of the liner shown in Figure 5 can be avoided. This way, the forming step(s) can directly follow the extrusion step, with the intermediate step of pre-shaping sheet 2. The necessity to perform large stretching operation of conventional methods limits the choice of materials for the liner: for large stretching operations, the material has to allow this procedure without getting corrupt in its consistency and constitution, which is usually only the case if an amorphous material is chosen. In the method according to the invention, since the large stretching operations are not necessary, also semi-crystalline materials such as polypropylene can be employed. In another forming step, which can also be combined with at least one of the previous forming steps, hinges 10 are formed. In Figure 4, the sheet 2 is shown after a plurality of hinges 10 or folding lines has been formed. For this forming step, various methods known form the art can be employed. In the present embodiment, the forming station is a thermoforming station. Further referring to Figure 3, subsequently, sheet 2 is processed to provide holes, especially for use in connection with accessories, and other structural features. As an example, an outlet for the cooling system has been formed by cutting or punching a circular hole 22 into the sheet 2. Another hole 22 with a rectangular shape has also been cut into the sheet 2 which is designed as a fixation point of a control box for the refrigerator. Hinges 10 are formed by appropriate tools, for instance heated coining heads. A preferred embodiment of the hinges will be described in connection with Figure 7. The forming steps according to Figure 2, 3 and 4 can be performed in the order shown or in any other order which leads to an effective production cycle. All or a selection of these forming steps can also be performed simultaneously. Up to this stage, sheet 2 has stayed flat. The next method step involves a folding operation to obtain the liner which in the present embodiment is a cabinet liner. Sheet 2 is folded along hinges 10 in such a way that peripheral rectangular parts 26, 28, 30, 32 are folded by an angle of 90° around the respective hinges 10 which connect them to a central part 34 of sheet 2. By this folding operation, adjacent edges and folding lines of neighboring peripheral parts 26, 28, 30, 32 are moved next to each other two by two into a parallel position. This way, edges 40 and 42, edges 44 and 46, edges 48 and 50, and edges 52 and 54 are aligned next to each other. The peripheral parts 26 and 30 comprise, respectively, two flanges 36. Peripheral parts 26, 28, 30, 32 comprise border elements 56 which are folded by 90° around the respective hinges to form a frame which can serve both as a blocking element as well as a covering element when inserting the liner into the housing of a refrigerating appliance. If necessary, the edges of the sheet 2 to be joined this way can be shaped by milling to allow a seamless joining. The folding operation leads to the cabinet liner 60 displayed in Figure 5. With respect to Figure 6, the folding procedure results in the cabinet liner 60 with folded edges 64, 66, 68, 70 which can optionally be joined by adhesive tape and/or undergo hedge sealing. The flanges 36 have been folded by 90° and rest and/or are attached to adjacent peripheral parts 28, 30, 32, 34. After the folding step, in a foaming step the cabinet liner 60 is put into a foaming tool and foamed, after which it is ready to be deployed in a household appliance, especially a refrigeration appliance or refrigerator. An advantageous embodiment of a hinge 10 is illustrated in Figure 7 in a side view of sheet 2. The hinge 10 comprises a first recess 80 and a second recess 84 on opposite sides of sheet 2. First recess 80 comprises a segment 88 which is basically geometrically shaped like a segment of a circle, the circle having a radius larger than a depth c of the recess 80 oriented in a direction 90 along the depth of sheet 2 and perpendicular to its surfaces. Segment 88 on both sides is connected to lines 92, 94 being parallel to direction 90, thus being perpendicular to a first and second surface of sheet 2. Second recess 84 likewise comprises a segment 106 basically being a segment of a circle which on both sides is connected to lines 110, 112 running parallel to lines 92, 94 of the first recess 80 and parallel to direction 90. The corresponding radius R of circular segment 106 is in the present embodiment 0,80 mm and smaller than the one related to segment 88, while the depth in direction 90 of the second recess 84 is approximately six times larger than the depth of the first recess. Depth c of first recess 80 is 0,15 mm as shown in the embodiment. A depth d which corresponds to the minimum distances of both recesses 80, 84, if oriented in direction 90, is between 0,2 mm and 0,4 mm. A width e of both recesses 80, 84 is 1,5 mm. Bend arrows 116, 118 indicate the folding directions of parts 120, 122 which are separated by the hinge 10 between them. After the folding operation, parts 120 and 122 will be substantially perpendicular to each other. The design of the hinges 10 is not limited to the hinge design described and can in other preferred embodiments be designed differently, as long as it allows a sufficient folding of its adjacent parts. For instance, it can be designed with triangular recesses in the sheet or any other recesses which leads a folding line and therefore to a deformable or bendable part of the sheet. With respect to Figure 8, in a frontal perspective view, part of a refrigeration appliance 130 is shown with a cabinet liner 60, which is fit into and attached to a housing 134. In particular, the liner 60 is enclosed in an outer shell of the cabinet, and defines one or more internal compartments for food storage. Between the outer shell and the liner, an insulation layer is provided.

1. Method for manufacturing a liner (60) comprising the steps of a) extruding a sheet (2), b) perimeter trimming said sheet (2), and c) folding said sheet (2) and joining adjacent edges (40, 42, 44, 46, 48, 50, 52, 54)

2. Method according to claim 1, whereby said sheet (2) is made of material comprising semi-crystalline polymers. 3. Method according to claim 1, whereby said sheet (2) is designed as a compact, alveolar or twin-wall sheet (2). 4. Method according to one of the claim 1 to 3, whereby said sheet (2) has a rectangular shape and perimeter trimming is performed by cutting off a substantially rectangular shape in each corner (6) of said sheet (2). 5. Method according to claim 3, whereby said cut-off rectangular shapes are identical in shape. 6. Method according to one of claims 1 to 5, comprising a forming step of forming at least one hinge (10) in said sheet (2). 7. Method according to one of the claims 1 to 6, comprising a forming step of forming at least one structure into said sheet (2), said structure comprising a protrusion or intrusion of said sheet (2). 8. Method according to one of claims 1 to 7, comprising a step of cutting at least one hole (22) into said sheet (2). 9. Method according to one of the claims 1 to 8, comprising a sealing step in which edges of parts (26, 28, 30, 32) of said sheet (2) which are adjacent to each other after folding are sealed together. 10. Liner (60), characterized in that it is obtained by a method according to claims 1 to 9. 11. Liner (60) according to claim 10 with four adjacent hinges (10) allowing the folding of said sheet (2) into a box-shaped structure. 12. Liner (60) according to claim 10 or 11 comprising at least one hinge (10) which comprises a sheet region of reduced thickness with a first recess (80) and a second recess (84) on opposite sides of the sheet (2), the respective recess (80, 84) being essentially shaped as a segment of a circle (88, 106) with transitions to two parallel lines (92, 94, 110, 112). 13. Liner (60) according to claim 12, whereby the minimum distance between said recesses (80, 84) is between 0,2 mm and 0,4 mm. 14. Liner (60) according to claims 12 or 13, whereby the depth of said first recess (80) is considerably smaller than the depth of said second recess (84). 15. Appliance (130) with a liner (60) according to one of claims 10 to 14.

2821571

Locking mechanism, opening system and motor vehicle

Based on the following detailed description of an invention, generate the patent claims. There should be 11 claims in total. The first, independent claim is given and the remaining 10 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

With reference to figures 1 to 4, an opening system 100 carrying out the invention will now be described. In the described example, the opening system 100 is a trunk opening system for a motor vehicle (not depicted). Furthermore, the directions (front-back, up-down, left-right) correspond to the usual directions of the motor vehicle. With reference to figure 1, the opening system 100 comprises a frame 102, for example the body-in-white of the motor vehicle. The opening system 100 further comprises a panel 104 intended to move with respect to the frame 102 to selectively take an open position and a closed position. In the described example, the panel 104 is a trunk panel intended to selectively cover and give access to the trunk (not depicted) of the motor vehicle. The opening system 100 further comprises a locking mechanism 106 for selectively blocking the panel 104 in its closed position and letting the panel 104 be opened. In the described example, the locking mechanism 106 is located frontward with respect to the panel 104. In the described example, the locking mechanism 106 first comprises a blocking unit intended to selectively take a blocking configuration in which the blocking unit blocks the panel 104 in its closed position, and an unblocking configuration in which the blocking unit lets the panel 104 be opened. In the described example, the blocking unit is a latch 108, for example, a mechanical latch, an electro-mechanical latch or a magnetic latch. The latch 108 comprises a base 110 fixed to the frame 102, and a casing 112 fixed to the panel 104 in a manner not depicted on figure 1. The latch 108 further comprises a bolt 114 mounted on the casing 112 in a movable way, so as to selectively take an engaged position and a disengaged position. In the engaged position, if the casing 112 is against the base 110, the bolt 114 engages the casing 112 in order to attach the casing 112 to the base 110, and thus maintain the panel 104 in its closed position. In the disengaged position, the bolt 114 is disengaged from the base 112 in order to allow separation of the casing 112 from the base 110, and thus opening of the panel 104. The locking mechanism 106 further comprises a blocking unit actuation system 116. In the described example, because the blocking unit is a latch, the system 116 will from now on be called latch actuation system 116. In the described example, the latch actuation system 116 is intended to be activated by a user in order to make the latch 108 let the panel 104 be opened. The latch actuation system 116 first comprises a lever 118 intended to rotate around a left-right axis A1 between a blocking position (which is the position depicted on figure 1 ) and an unblocking position, in order to put the latch 108 in respectively its blocking configuration and unblocking configuration. The lever 118 comprises an upper arm 120 extending above the axis A1 and a lower arm 122 extending below the axis A1. The lever 118 further comprises a weight 124 fixed to the lower arm 122. The latch actuation system 116 further comprises a rod 126 connecting the lever 118 to the bolt 114. The rod 126 is intended to move the bolt 114 of the latch 108 between its engaged position and its disengaged position when the lever 118 respectively moves between its blocking position and its unblocking position. The latch actuation system 116 further comprises a housing 128 fixed to the panel 104 and projecting frontward from the panel 104. The housing 128 is cylindrical and extends around a front-back axis A2. The latch actuation system 116 further comprises a lever actuation device 130 partially contained into the housing 128, and intended to move along the axis A2 between a back position and a front position. The lever actuation device 130 first comprises a pushbutton 132 passing through the panel 104 and projecting backward from the panel 104, behind the housing 128. The pushbutton 132 is intended to be pushed frontward, for instance by a user wanting to open the panel 104, so as to push the lever actuation device 130 from its back position to its front position. The lever actuation device 130 further comprises a restoration means (not depicted), such as a restoration spring, for moving the lever actuation device 130 from its back position to its front position. The lever actuation device 130 further comprises a link element 134 providing a link with the lever 118. The link element 134 first comprises a pushing portion 136 intended to push the upper arm 120 of the lever 118 frontward so as to rotate the lever 118 from its unblocking position to its blocking position when the lever actuation device 130 moves from its back position to its front position. The link element 134 further comprises a return portion 138 intended to be pushed by the upper arm 120 of the lever 118 when the lever 118 rotates from its blocking position to its unblocking position, so as to move the lever actuation device 130 from its back position to its front position. In the described example, the return portion 138 is fixed to the pushing portion 136. The link element 134 is furthermore intended to move between a coupled position in which the pushing portion 136 is able to push the lever 118 and an uncoupled position in which the pushing portion 136 is unable to push the lever 118, so that pushing the pushbutton 132 does not activate the lever 118. In the described example, the link element 134 is intended to rotate with respect to the housing 128 around the axis A2 for moving between its coupled position and its uncoupled position. Preferably, the link element 134 is bistable between its coupled and uncoupled position. The lever actuation device 130 further comprises a coupling system 140 intended to move the link element 134 between its coupled position and its uncoupled position. In the described example, the coupling system 140 is activated by use of a key and is therefore provided with a key insertion slot 142 located for example in the center of the pushbutton 132. It should be noted that the return portion 138 is intended to be pushed by the upper arm 120 of the lever 118, whatever the position of the link element 134 - coupled or uncoupled - may be. With reference to figure 2, the link element 134 will now be described in greater detail. The link element 134 first comprises a disk-shaped base 202 centered on the axis A2. The link element 134 further comprises a circumferential wall 204 projecting frontward from the disk-shaped base 202. The circumferential wall 204 is provided with a longitudinal slot 206 and a circumferential slot 208. The circumferential slot 208 joins the longitudinal slot 206 at a front end of the latter. The return element 138 is formed by the portion of the circumferential wall 204 extending frontward with respect to the circumferential slot 208. Furthermore, the portion of the circumferential wall 204 extending backward with respect to the circumferential slot 208 forms a stop 210 intended to push the lever 118, as it will be explained below. With reference to figures 3 and 4, the lever 118 further comprises a pin 302 projecting from the upper arm 120 of the lever 118 and extending in the circumferential slot 206 when the link element 134 is in the coupled position, and in the longitudinal slot 208 when the link element 134 is in the uncoupled position. The lever 118 further comprises a restoration means 304 intended to restore the lever 118 from its unblocking position to its blocking position. In the described example the restoration means 304 is a restoration spring. Operation of the opening system 100 will now be explained. The link element 134 is first assumed to be in its coupled position while the panel 104 is closed and blocked in this closed position by the latch 108. Because the link element 134 is in its coupled position, the pin 302 of the lever 118 is located in the circumferential slot 208 of the link element 134 and aligned with the stop 210 of the link element 134 with respect to the front-back direction. When an user activates the lever actuation device 130 by pushing the pushbutton 132, the lever actuation device 130 moves from its back position to its front position. Because the pin 302 is aligned with the stop 210, the stop 210 pushes the upper arm 120 of the lever 118 frontward so as to move the lever 118 from its blocking position to its unblocking position. In turn, the rod 126 moves the bolt 114 of the latch 118 from its engaged position to its disengaged position, allowing opening of the panel 104. When the user releases the pushbutton 132, the restoration means 304 restores the lever 118 to its blocking position. During this restoration movement, the pin 302 pushed the link element 134 backward to make the lever actuation device 130 move from its front position to its back position. At the same time, the rod 126 moves the bolt 114 of the latch 108 from its disengaged position to its engaged position. If the casing 112 is against the base 110, the latch 108 blocks the panel 104 in its closed position. In case of a collision from the front, the inertia of the lever actuation device 130 tends to make the lever actuation device 130 move from its back position toward its front position. The stop 210 pushes the pin 302 of the lever 118, so that the lever 118 tends to move from its blocking position toward its unblocking position, which poses a danger of opening of the panel 104. At the same time, the inertia of the lower arm 122 and the weight 124 of the lever 118 tends to make the lower arm 122 move frontward, so that the lever 118 tends to move from its unblocking position toward its blocking position. The mass of the weight 124 is chosen so that, when the locking mechanism 106 is accelerating along the axis A1, for instance as a result of a front or back collision, the upper arm 120 of the lever 118 and the lever actuation device 130 produce a first torque on the lever 118 around the axis A1, while the lower arm 122 of the lever 118 and the weight 124 of the lever 118 produce a second torque on the lever 118 around the axis A1, the first and second torques having opposite signs and equal absolute values, plus or minus 10%. With such a mass for the weight 124, the inertia of the lower arm 122 and the weight 124 of the lever 118 compensates the inertia of the lever actuation device 130, and prevents the lever 118 from reaching its unblocking position. Opening of the panel 104 is therefore prevented. In case of a collision from the back, the inertia of the lower arm 122 and the weight 124 of the lever 118, tends to make the lower arm 122 move backward, so that the lever 118 tends to move from its blocking position toward its unblocking position, which poses a danger of opening of the panel 104. At the same time, the inertia of the lever actuation device 130 tends to make the lever actuation device 130 move backward and drag along the upper arm 120 of the lever by means of the return portion 138. The inertia of lever actuation device 130 compensates the inertia of the lower arm 122 and weight 124 and prevents the lever 118 from reaching its unblocking position. Opening of the panel 104 is therefore prevented. When the user activates the coupling system 140, the link element 134 moves from its coupled position to its uncoupled position. As a results, the pin 302 of the lever 118 travels into the circumferential slot 208 and reaches the front end of the longitudinal slot 210, so that the stop 210 is shifted from the pin 302 and is unable to push the pin 302 frontward, and thus also to move the lever 118 from its blocking position to its unblocking position. Pushing the pushbutton 132 does not open the panel 104 anymore. In case of a collision from the front, the inertia of the lever actuation device 130 tends to make the lever actuation device 130 move from its back position toward its front position. However, because the link element 134 is not coupled to the lever 118, the movement of the lever actuation device 130 toward the front does not make the lever 118 move toward its unblocking position, so that the panel 104 stays blocked by the latch 108. In case of a collision from the back, the inertia of the lower arm 122 and the weight 124 of the lever 118, tends to make the lower arm 122 move backward, so that the lever 118 tends to move from its blocking position toward its unblocking position, which poses a danger of opening of the panel 104. At the same time, the inertia of the lever actuation device 130 tends to make the lever actuation device 130 move backward and drag along the upper arm 120 of the lever by means of the return portion 138, which is still located in front of the pin 302. The inertia of lever actuation device 130 compensates the inertia of the lower arm 122 and weight 124 and prevents the lever 118 from reaching its unblocking position. Opening of the panel 104 is therefore prevented. When the user activates again the coupling system 140, the link element 134 moves back from its uncoupled position to its coupled position.

1. Locking mechanism (106) for a panel (104) comprising: - a blocking unit (108) intended to selectively take a blocking configuration in which the blocking system blocks the panel (104) in a closed position, and an unblocking configuration in which the blocking system (108) lets the panel (104) be opened, - a blocking unit actuation system (116) comprising: - a lever (118) intended to rotate around a first axis (A1) between a blocking position and an unblocking position, in order to put the blocking unit (108) in respectively the blocking configuration and the unblocking configuration, the lever (118) comprising an upper arm (120) extending above the first axis (A1), a lower arm (122) extending below the first axis (A1), and a weight (124) fixed to the lower arm (122), and - a lever actuation device (130) intended to move between a back position and a front position, the lever actuation device (130) comprising a link element (134) providing a link with the lever (118), the link element (134) comprising a pushing portion (136) intended to push the upper arm (120) of the lever (118) frontward so as to rotate the lever (118) from its unblocking position to its blocking position when the lever actuation device (130) moves from its back position to its front position, characterized in that the link element (134) further comprises a restoring portion (138) intended to be pushed by the upper arm (120) of the lever (118) when the lever (118) rotates from its blocking position toward its unblocking position, so as to move the lever actuation device (130) toward its front position.

2. Locking mechanism (106) according to anyone of claims 1,: wherein the link element (134) is furthermore intended to move between a coupled position in which the pushing portion (136) is able to push the upper arm (120) of the lever (118) and an uncoupled position in which the pushing portion (136) is unable to push the lever (118),: wherein the lever actuation device (130) further comprises a coupling system (140) intended to move the link element (134) between its coupled position and its uncoupled position, and: and wherein the restoring element (138) is intended to be pushed by the upper arm (120) of the lever (118) when the lever (118) rotates from its blocking position to its unblocking position, so as to move the lever actuation device (130) from its back position to its front position, whatever the position of the link element (134) - coupled or uncoupled - may be. 3. Locking mechanism (106) according to claim 1 or 2, wherein the lever actuation device (130) is intended move along a second axis (A2). 4. Locking mechanism (106) according to claims 2 and 3, wherein the link element (134) is intended to rotate around the second axis (A2) in order to move between its coupled position and its uncoupled position. 5. Locking mechanism (106) according to claim 4,: wherein the link element (134) comprises a base (202) and a wall (204) circumferential with respect to the second axis (A2) and projecting frontward from the base (202), wherein the circumferential wall (204) is provided with a longitudinal slot (206) and a circumferential slot (208), the circumferential slot (208) joining the longitudinal slot (206),: wherein the return element (138) is formed by the portion of the circumferential wall (204) extending frontward with respect to the circumferential slot (208), and: wherein the lever comprises a pin (302) projecting from the upper arm (120) of the lever (118) and extending in the circumferential slot (206) when the link element (134) is in the coupled position, and in the longitudinal slot (208) when the link element (134) is in the uncoupled position. 6. Locking mechanism (106) according to anyone of claims 2 to 5, wherein the link element (134) is bistable between its coupled position and its uncoupled position. 7. Locking mechanism (106) according to anyone of claims 1 to 6, wherein the weight (124) has a mass chosen so that, when the locking mechanism (106) is accelerating along the first axis (A1), the upper arm (120) of the lever (118) and the lever actuation device (130) produce a first torque on the lever (118) around the first axis (A1), while the lower arm (122) and the weight (124) of the lever (118) produce a second torque on the lever (118) around the first axis (A1), the first and second torques having opposite signs and equal absolute values, plus or minus 10%. 8. Locking mechanism (106) according to anyone of claims 1 to 7, wherein the blocking unit (108) is a latch. 9. Locking mechanism (106) according to anyone of claims 1 to 8, wherein the lever actuation device (130) further comprises a pushbutton (132) intended to be pushed frontward so as to push the lever actuation device (130) front its back position to its front position. 10. Opening system (100) comprising a panel (104) and a locking mechanism (106) for the panel (104), according to anyone of claims 1 to 9. 11. Motor vehicle comprising an opening system (100) according to claim 10, wherein the panel (104) is a trunk panel.

2832521

Pipe connection arrangement

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a pipe coupling arrangement 10 according to the invention between two pipes 11, 12 of an air circuit of a motor vehicle engine. This arrangement is particularly suited when a connection between pipes, which are made of chemically incompatible materials, is required. The coupling of the pipes 11, 12 is achieved by molding over one end of the first pipe (or substrate pipe) 11, an end of the second pipe 12. In this example, the substrate pipe 11 is made of rubber, such as Polyacrylate rubber, and the overmolded pipe 12 is made of thermoplastic, such as Polypropylene. As will be described in more detail below, the ends of pipes 11, 12 are mated by molding the pipe 12 (or the pipe end) in a mold already containing the pipe 11 end, the pipe 11 having been manufactured beforehand by any suitable means. The shape of the end of each pipe 11, 12 is chosen so as to create an efficient mechanical anchoring of both pipes 11, 12, even if they are made of chemically incompatible materials. Referring now to Figure 2, the substrate pipe 11 comprises a tubular body 111 (which is shown partially) ended by a circular flange 112. The internal diameter 119B of the hollow tubular body 111 is inferior to the internal diameter 119A of the hollow flange 112. The shape of the flange 112 is not limited to the one illustrated in Figure 2. Indeed, in some embodiments, the flange 112 may have a cylinder shape. In other embodiments, it may have a different shape, for example a conical or spherical shape, or it may have a hexagonal cross section. In the embodiment presented in figure 2, the flange 112 extends radially from the axial outer surface 118 of the pipe body 111 and forms an annular enlarged part of the pipe body 111. The flange surface comprises a first radial outer surface 113 (extending radially from the outer surface 118), prolonged by an axial outer surface 114, a second radial outer surface 115, an axial inner surface 116 and a radial inner surface 117. The radial inner surface 117 is prolonged by the axial inner surface 110 of the pipe body 111. Figure 3 presents a mold 30 adapted for obtaining a pipe connection arrangement according to an exemplary embodiment of the invention, by molding the pipe 12 over the end of the substrate pipe 11 of figures 1 and 2. As illustrated in the sectional view of Figure 3, the injection mold 30 has a circular cavity 310, which creates the volume for obtaining the overmolded pipe 12. The cavity 310 comprises three parts, i.e. two lateral cavities (a left part 312 and a right part 316) separated by a wider central cavity 314. The left cavity 312 and the central cavity 314, as shown figure 4, are adapted to receive the flanged end of the substrate pipe 11. The diameter of the left cavity 312 is substantially equal to the outer diameter of the pipe body 111. The flange 112 of the substrate pipe 11 and part of the pipe body 111 are received in the central cavity 314, which has a larger diameter than the two lateral cavities 312, 316. Depending on the desired shape of the overmolded pipe 12, the central cavity 314 and the lateral cavity 316 may have different diameters and various shapes. Referring now to Figure 4, the end of substrate pipe 11 is first fitted inside the cavity 310 and a rigid tubular core 40 is then inserted in the cavity 310. More precisely, an end of the core 40 is placed inside the end of substrate pipe 11, the external diameter of the core 40 being substantially equal to the internal diameter 119B of the pipe tubular body 111. Each of those operations can be performed, depending upon the embodiments, either manually, either with a robot hand. Once the substrate pipe 11 is fitted inside the cavity 310, there remains a free space 420 around the flange 112 and the core 40. In particular, the flange 112 and a part 450 of the body 111 are pushed far enough into the cavity 310 in order to create a gap 430 between the cavity wall 440 and the first radial outer surface 113 of the flange 112. The free space 420 finally extends between the walls of the cavity 310 and the first radial outer surface 113, the axial outer surface 114, the second radial outer surface 115, the axial inner surface 116 and the radial inner surface 117 of the flange 112. As the flange 112 has an inner diameter 119A larger than the inner diameter 119B of the body 111, and as a consequence larger than the external diameter of the core 40, the free space 420 also extends between the flange 112 and the core 40 (more precisely, according to figure 2, between the axial inner surface 116 of the flange 112 and the core 40). As illustrated in Figure 5, the pipe 12 is then molded over the end of the rubber pipe 11 and around the core 40 by the injection of molten thermoplastic 120 in the free space 420. Thus, the coupling of the pipes 11, 12 is formed by the effect of overmolding, i.e. by surrounding the flange 112 of the substrate pipe 11 with molten plastic 120. The molten plastic 120 forming the second pipe 12 thus encapsulates (i.e. encloses or surrounds on all sides) the flanged end of the substrate pipe 11. More precisely, because of the specific shape of the free space 420 that surrounds the flange 112 of the substrate pipe 11 before the injection step, the flange 112 is caught up (or flooded) in the overmolded material 120 after the injection step. As shown in Figure 5, the overmolded material 120, and thus the end 121 of pipe 12, surrounds the first radial outer surface 113, the axial outer surface 114, the second radial outer surface 115, the axial inner surface 116 and the radial inner surface 117 of the flange 112. The overmolded material 120 when solidifying grips onto these surfaces of the flange 112. As shown in Figure 6, the two pipes 11, 12 (once removed from the mold 30) are then mechanically attached to each other, in a tight manner, and in communication with each other so as to convey any type of fluid. The way the flange 112 of the substrate pipe 11 is encapsulated within the end 121 of the overmolded pipe 12 (the flange 112 being "sandwiched" radially and axially by the overmolded pipe) ensures proper fastening and sealing of the rubber pipe 11 and the thermoplastic pipe 12. It is to be noted that the inner diameter 119B of pipe 11 is equal to the inner diameter 122 of pipe 12. The solution of the invention is advantageously applicable for joining pipes or other members intended for conveying fluids (gases, vapors or liquids). It is advantageously applicable in the automobile industry, in an internal combustion engine of a motor vehicle for instance. The present invention eliminates the additional step according to the prior art solution of adding a screw clamp on the rubber pipe, and provides a pipe coupling arrangement which results in reduced labor, materials and costs. The overmolding technique described previously allows the introduction of adhesive between the outer surface of the substrate pipe 11 and the surrounding overmolded material 120 so as to provide tightness of the connection when the pipes 11, 12 are used to convey liquids for instance.

1. Pipe connection arrangement (10), comprising a first pipe (11) having a flange (112) on one end and a second pipe (12) having an end (121) molded over said flange (112), characterized in that said molded end (121) of said second pipe (12) encapsulates said flange (112) of said first pipe (11).

2. Pipe connection arrangement according to claim 1, characterized in that the inner diameter (119A) of said flange (112) is superior to the inner diameter (119B) of said first pipe (11). 3. Pipe connection arrangement according to claim 2, characterized in that said molded end (121) of said second pipe (12) covers the outer and inner surfaces (113, 114, 115, 116, 117) of said flange (112). 4. Pipe connection arrangement according to claim 1, characterized in that the inner diameter (122) of said second pipe (12) is equal to the inner diameter (119B) of said first pipe (11). 5. Pipe connection arrangement according to any one of claims 1 to 4, characterized in that the materials of the first and second pipes (11, 12) are chemically incompatible. 6. Pipe connection arrangement according to claim 5, characterized in that said first pipe (11) is in rubber and said second pipe (12) is made of thermoplastic. 7. Pipe connection arrangement according to claim 6, characterized in that said first pipe (11) is in polyacrylate rubber. 8. Pipe connection arrangement according to claim 6 or 7, characterized in that said second pipe (12) is in polypropylene. 9. Pipe connection arrangement, according to any of claims 1 to 8 characterized in that it also comprises thickness means located on a frontier between said first pipe (11) and said molded end of said second pipe (12). 10. Method for joining two pipes (11, 12) to a pipe connection arrangement according to any one of the previous claims by a second pipe (12) overmolded over the end of a first pipe (11), wherein an injection mold (30) has a cavity (310) which creates the volume for obtaining the overmolded pipe (12).

2832984

Flange connection

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

A detailed description of an exemplary embodiment of the invention follows with reference to the figures provided. Figure 1. shows a detachable flat flange connection between two parts of an air intake system of a motor vehicle. In this particular example, the outlet pipe 10 of a turbo compressor or turbo charger of an internal combustion engine is ended by a flange 11, which is fitted to a flange 21 located on an end section of a thermoplastic duct 20. The material of the outlet pipe 10 is metal, the flange 21 being in thermoplastics. The abutting faces of the flanges 11, 21 are flat. As illustrated in Figures 2 and 3, the flange 11 of outlet pipe 10 comprises two symmetrically disposed threaded through-holes 12, 13 and the flange 21 of thermoplastic duct 20 comprises two symmetrically disposed through-holes 22, 23 for a screw or bolt connection to flange 11. The tight connecting assembly connecting end to end the thermoplastic duct 20 to the outlet pipe 10 comprises a radial sealing gasket 40 fitted in the flange 21. It further comprises a metallic flange 50 and a sheet gasket 60 which are fitted between the flanges 11, 21 before the axial tightening screws 32, 33 are fitted in corresponding through-holes 12, 13 and 22, 23 in order to fasten the flanges 11 and 21, and thus the thermoplastic duct 20 to the metal outlet pipe 10. It is to be noted that for reasons of clarity, screws 32, 33 are not represented in Figures 3 and 4. The radial sealing gasket 40 is, in this example, an O-ring or a toric joint of a material which is elastic (an elastomeric material preferably) and resistant against the medium, i.e. air, conducted through the flow channels 14, 24. The radial sealing gasket 40 is fitted in an internal circular housing, or support, 25 of the plastic flange 21, i.e. it is accommodated inside the flange 21. The housing 25 is configured so as to support therein the gasket 40 and surrounds the channel 24 in which the medium flows. As illustrated in Figure 3, a metallic flange 50 of symmetrical circular shape comprises a circular opening 54 for passage of flowable medium and two ears from which extend tubular pins 55, 56. Through-holes 52, 53 are defined in tubular pins 55, 56 respectively. The diameter of the tubular pins 55, 56 is chosen so that they fit inside the through-holes 22, 23 of plastic flange 21 when the metallic flange 50 is abutted against the flat face of the plastic flange 21. The pins 55, 56 are used to replace the usual metallic bushing needed to keep the tightening torque, and avoid unscrewing due to plastic (21) creeping. The circular opening 54 of the metallic flange 50 is surrounded by a curved skirt 57, which extends in the same direction as the tubular pins 55, 56. When the metallic flange 50 is abutted against the flat face of the plastic flange 21, the skirt 57 maintains the sealing gasket 40 in position inside the housing 25 of the flange 21, ensuring radial sealing of the tight connecting assembly of the invention. The skirt 57 of metallic flange 50 and the housing 25 of flange 21 define a groove or channel in which the sealing gasket 40 is compressed ensuring sealing (as illustrated by reference number 70 in Figure 2 ) between the metallic flange 50 and the thermoplastic duct 20. The steel sheet or flat gasket 60 is of circular shape and comprises a circular opening 64 for passage of flowable medium. It further comprises ears in which are disposed through-holes 62, 63, and three fastening or retaining clips or brackets 65, 66, 67 extending in a direction perpendicular to the surface of the sheet gasket 60. The fastening clips 65, 66, 67 are arranged to removably fasten the sheet gasket 60 on the flange 21 of the duct 20, the metallic flange 50 being placed between the flange 21 and the sheet gasket 60. It is to be noted that the sheet gasket 60 comprises one or more lips or projections (two projections 68 in this example) on the surface 69 that are designed to be urged against the flat face of flange 11 of outlet pipe 10. These projections 68 ensure axial sealing of the tight connecting assembly of the invention (the sealing between the metallic flange 50 and the pipe 10 is illustrated by reference number 71 in Figure 2 ). Once the sheet gasket 60 is mounted on the plastic flange 21 (as illustrated in Figure 4 ) urging the metallic flange 50 against the flat face of the plastic flange 21, screws 32, 33 are inserted in the holes 22, 23 of duct 20, then through holes 52, 53 and 62, 63 of the metallic flange 50 and sheet gasket 60 respectively. The extremity of screws 32, 33 is retained in threaded holes 12, 13 of the classic flange 11 of outlet pipe 10 to form a mechanical connection between abutted flanges 11, 21 of opposed pipe 10 and duct 20. The plastic part 20 is retained by the head of each screw 32, 33. In summary, the tight connecting assembly of the present invention implements two sealing areas. The compressed inner sealing gasket 40 allows radial sealing between metallic flange 50 and channel 24 of plastic part 20. The metallic outer sheet gasket 60 ensures axial sealing between the parts 10, 20 in which the medium flows and the metallic flange 50. Mechanical assembly of the metallic pipe 10 and of the plastic duct 20 is ensured by the metallic flange 50, and tightness of the connection is ensured by the sealing gasket 40 (radial tightness) and the metallic sheet gasket 60 (axial tightness). Because the flange 50 is in metal, it is not much subject to deformation (less than plastic in any case). Thus, contrary to the classical flat flange connection, tightness is not directly linked to the mechanical assembly device. A further advantage of the invention is that the use of a radial gasket allows a decoupling of the flat flange connection. Indeed, even if the plastic part, i.e. plastic duct 20, happens to be deformed because of creeping, temperature and/or pressure for instance, the assembly offers good protection against leakage. Another advantage is that the solution of the invention is compatible with current and standard flange design. Such a connection is also easy to assemble and quickly detachable, In an alternative embodiment, the metallic flange 50 is provided with the sealing projections ensuring axial tightness of the flange connection so that the latter does not require the use of the sheet gasket 60. It is to be noted that the sealing gasket 40 may be mounted (or be part of) on the outside periphery of skirt 57 before assembly of the connection. Each of the flanges 11, 21 may be located on one end of a straight or bent (elbow type) segment of any part of an engine, e.g. an internal combustion engine, of a motor vehicle. The flange 50 is in metal or any other heat-resistant material such as a ceramic or graphite material. The sheet gasket 60 may be in steel or any other heat-resistant material such as a ceramic or graphite material. The medium flowing inside the duct 20 and pipe 10 could be combustion air, compressed by the turbo charger running to the charge air cooler, the intake manifold or the combustion chamber or exhaust gas leaving the engine.

1. A flange connection between a first duct (20) and a second duct (10) of an engine, comprising a first flange (21) located on one end of said first duct (20), a second flange (11) located on one end of said second duct (10) and connecting means (32, 33) for axially tightening the first and second abutting flanges (11, 21), characterized in that the flange connection comprises first sealing means (40) for radially sealing said flange connection and interface means (50, 60) configured to be mounted on said first flange (21) and to come into contact with the abutting face of said second flange (11), said interface means (50, 60) comprising second sealing means (60) for radially sealing said flange connection.

2. A flange connection according to claim 1, characterized in that said first flange (21) is in plastics e.g. thermoplastic material and said second flange (11) is in a heat-resistant material, e.g. cast iron. 3. A flange connection according to claim 3, characterized in that said interface means (50, 60) are at least partly in a heat-resistant material, e.g. metal. 4. A flange connection according to any of claims 1 to 3, characterized in that said interface means comprises a third flange (50). 5. A flange connection according to claim 4, characterized in that said third flange (50) carries said first sealing means (40). 6. A flange connection according to claim 4 or 5, characterized in that said interface means comprises a sheet gasket (60) configured to be mounted between said third flange (50) and said second flange (11). 7. A flange connection according to claim 4 or 5, characterized in that said third flange (50) carries said second sealing means (60). 8. A flange connection according to claim 6, characterized in that said sheet gasket (60) carries said second sealing means (60). 9. A flange connection according to any of claims 1 to 8, characterized in that said second sealing means (60) comprise one or more circular projections configured to come into contact with the abutting surface of said second flange (11). 10. A flange connection according to any of claims 1 to 9, characterized in that said first flange (2-1) comprises a housing (25) surrounding the flow channel (24) of said first duct (20) for accommodating said first sealing means (40). 11. A flange connection according to any of claims 1 to 10, characterized in that said first sealing means (40) comprise an annular seal. 12. A flange connection according to any of claims 4 to 11, characterized in that said third flange (50) comprises maintaining means (57) defining with said housing (25) a groove for said first sealing means (40). 13. A flange connection according to any of claims 6 to 12, characterized in that said sheet gasket (60) comprises retaining means configured to removably fasten said sheet gasket (60) on said first flange (21). 14. A flange connection according to claim 13, characterized in that said retaining means comprise several brackets designed to snap said sheet gasket (60) on said first flange (21). 15. A flange connection according to any of claims 1 to 14, characterized in that the first duct (20) and a second duct (10) are ducts of a combustion engine guiding air downstream from a compressor or air charger.

2843224

Charge air duct for an internal combustion engine

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

A detailed description of several exemplary embodiments of the invention follows with reference to the figures provided. In the different embodiments described below, the charge air duct is located between the outlet of the charge air cooler and the intake manifold plenum of a combustion engine provided with a one-stage or two-stage turbocharger. In such a combustion engine, intake air is directed in an air filter delivering clean air to a compressor of a turbocharger. The compressed air leaving the turbocharger is directed via a first charge air duct (which is not the subject matter of the invention) through a charge air cooler. The charge air cooler is used to reduce the temperature (and thus increase the density) of the compressed air before the cooled air reaches the air inlet side of the intake manifold plenum via a second charge air duct (which is the subject matter of the invention). It is to be noted that the charge air duct of the invention is not a runner of an intake manifold of an internal combustion engine (it is known that the intake manifold of such an engine comprises an air plenum feeding different cylinders via a respective runner). The charge air duct of the invention comprises a first short duct (also called main duct) and a second long duct (also called bypass duct). The charge air is routed into one or the other of these ducts using a control device. In other words, the air is fed through the main duct or the bypass duct depending on the position of the control device. Thus, the active charge air duct of the invention is of variable length and, unlike conventional charge air ducts of fixed length, it can be easily adapted to different engine operating situations. Advantageously, the charge air routing is adapted to various engine operating conditions using a single control device. In the embodiments described hereinafter, the arrows are schematic representations of the charge air flow through the short and long ducts. Figures 1A to 1C show the charge air duct according to a first embodiment of the invention. The charge air duct 100 comprises a body (or housing) 101 in which a cylindrical hollow tube (or central part) 109 is fitted. The inner part of the tube 109 defines a main duct 102. The main duct 102 has an air inlet 103, into which the charge air flows, and an air outlet 104 in which a control device (or switching means) 105 is positioned. As mentioned before, the air fed in the air inlet 103 is compressed by a turbocharger of the combustion engine and cooled by the charge air cooler. The air flowing through the air outlet 104 is directed in the intake manifold plenum and different combustion chambers of the engine. The air inlet and outlet 103, 104 have a circular cross-section in this example. Figure 1C is a detailed view of Figure 1A showing the control device 105 in its closed position. The control device, or valve, 105 comprises a disc shaped flap 1052 mounted on a shaft 1051, which is secured at both ends to the wall of the main duct 102. The shaft 1051, and thus the control device 105, can be rotated by way of an actuator (not shown) around an axis 106, which is perpendicular to the longitudinal axis 107 of the main duct 102. A swirl or helical lip (or fin, or helix) 1091 is arranged on the outer surface of the tube 109. The swirl fin 1091 extends in the space defined between the main duct 102 and the housing 101, this space being sealed at both ends (in particular by a cover 112 at the air inlet end). The helix 1091 forms several turns over a complete revolution around the axis 207, and its outer periphery is in contact with the inner surface of the housing 101, thus defining a long swirl duct 108. The long duct 108 is arranged (formed) around the main short duct 102 and is separated from the main duct 102 by a dividing wall. The slope of the helix 1091 is here of the order of 10° relative to a horizontal plane but may vary depending on the desired long duct length. A first radial opening or passage 110 is provided in the main duct 102 in the region of the air inlet 103. A second radial opening 211 is provided in the main duct 102 in the region of the air outlet 104. The radial opening 111 is located between the control device 105 and the air outlet 104. Depending on a rotational position of the shaft 1051, the flap 1052 of the control device 105 is capable of opening and closing the air passage delimited by the inner surface of the main duct 102. Preferably, the flap 1052 switches between two states (i.e. on or off) only. The flap 1052 can be part of a progressive valve in an alternative embodiment. The flap 1052 can be an hinge flap or any other type of valve. The disc shaped flap 1052 has an outer diameter, which is slightly smaller than the inner diameter of main duct 102, which is of a cylindrical shape. When the shaft 1051 is rotated to a position at which the flap 1052 is perpendicular to the longitudinal axis 107 of the main duct 102, the main duct 102 is fully closed by the flap 1052. Although it is not illustrated, the flap 1052 is designed so as to prevent leakage of the charge air when closed. In a preferred embodiment, a seal ring assembly is provided at an outer periphery of the disc flap 1052, so as to seal any gap existing between the inner peripheral surface of the main duct 102 and the outer periphery of the flap 1052. When the engine operates at low speed range, the flap 1052 is closed (i.e. it is in the long duct position) as shown in Figure 1A. Charge air is directed in the long duct 108. As illustrated by the arrows, the charge air flow enters the short duct 102 in the axial direction via the air inlet 103 and exits through the first radial opening 110 into the long duct 108 (it is thus redirected by approximately 90°). Once it has circulated in the long duct 108, swirling around the main duct 102, the charge air flow enters the short duct 102 through the second radial opening 111 and exits the short duct 102 in the axial direction via the air outlet 104. When the engine operates at high speed range, the control device 105 is moved into its opened position (or short duct position), as shown in Figure 2B, and the charge air flows directly through the main duct 102 from the air inlet 103 to the air outlet 104. Due to the fact that control device 105 does not close the first and second radial openings 110, 111 when in its opened position, a portion of the inlet air can possibly flow within the long duct 108. Thus, air feeding in the intake manifold plenum is increased when the control device 105 is in its opened position, since the control device does not close the long duct 108 in that opened position. In one embodiment, the control device 105 is connected to an actuator to allow selectable positioning depending from at least one input. Such an input can be a measured engine speed, and/or a measured charge air pressure, and/or a turbocharger/compressor performance for instance. Such an actuator can be an electromechanical or pneumatic actuator driven by an electronic control device that includes software. A sensor for monitoring the position of the control device 105 can be provided. In another embodiment, the control device 105 is self-actuated. In short, in the high engine speed range (above 1500 rpm for instance), in which the turbocharger compresses (i.e. increases the pressure) the supplied air in an effective manner, the flap 1052 is opened so as to route the charge air in the short (main) duct 102. In the low engine speed range, in which the action of the turbocharger is minimal or non-existent, the position of the flap 1052 is switched. The flap 1052 closes the main duct 102 so as to route the air in the bypass (long) duct 108. The volumetric efficiency is thus increased in the low engine speed range, where usually the effect of the turbocharger is unsatisfactory, without degrading the volumetric efficiency in the high engine speed range. Indeed, charge air pressure losses are decreased in the high engine speed range, thus increasing the supply of air (and volumetric efficiency) in this range and improving engine power. Also, higher torque at low speed reduces the engine operating speed (i.e. it enables engine downspeeding), thus reducing fuel consumption, and/or improving dynamic behaviour of the vehicle (less time to torque and faster acceleration). The main short duct 102 is 600 mm long for instance and has a diameter (cross section) superior to 50 mm (equal to 57 mm for instance), the long duct 108 being 1400 mm long for instance and its diameter being inferior to 30 mm preferably (equal to 28 mm for instance). Thus, the flow cross section of the long duct 108 is smaller than the flow cross section of the main duct 102. The length and cross section of the charge air duct 100 is thus adjusted based on engine speed, in this example. In other words, the charge air duct 100 is configured to switch between two modes, i.e. a long route and a short route. It is to be noted that the charge air duct 100 is manufactured using an injection molding process. The charge air duct 100 is assembled by inserting the cylindrical tube 109 on which the swirl fin 1091 is formed inside the housing 101, and by securing the cover 112 at one end of the housing 101. Figures 7A to 7F show several possible ways of ensuring the sealing of the swirl lip 1091 (and thus the long duct 108) against the inner wall of the housing 101. In the example of Figure 7A, the long duct sealing is carried out by adjustment of the lip 1091 against the inner surface of the housing 101 so that the outer periphery of the lip 109 is in contact with the inner surface of the housing 101. Such an adjustment suppresses, or minimizes, the gap between the free end of the lip 1091 and the housing 101. In the alternative example of Figure 7B, long duct sealing is carried out radially by using the flexibility of the swirl lip 1091 and by bending it against the inner surface of the housing 101. In this figure 7B, the bottom view shows the lip 1091 in its free state before assembly (i.e. before insertion of the tube 109 in the housing 101) and the top view shows the same lip 1091 in the assembled state in which it is bended and in contact with the inner surface of the housing 101. In the example of Figure 7C, long duct sealing is carried out axially by using the flexibility of the swirl lip 1091. The swirl lip 1091 is bent against the inner surface of the housing 101 where it is retained in a bended state by a notch 1011 configured on the inner surface of the housing 101. In this figure 7C, the bottom view shows the lip 1091 in its free state before assembly and the top view shows the lip 1091 in the assembled state once bended and in contact with the notch surface 1011. In the example of Figure 7D, long duct sealing is obtained by providing a swirling overmolded seal 1012 on the inner surface of the housing 101 against which the bended lip 1091 is in contact. In this figure 7D, the bottom view shows the lip 1091 in its free state before assembly and the top view shows the lip 1091 in the assembled state once bended and in contact with the seal 1012. In the example of Figure 7E, long duct sealing is obtained by providing a seal 1092 at the free end of the lip 1091 (such a seal 1092 may be overmolded on the lip 1091), the seal 1092 being designed to come into contact against the inner surface of the housing 201 once the lip 2091 is bended. In this figure 7E, the bottom view shows the lip 1091 in its free state before assembly and the top view shows the lip 1091 in the assembled state once bended. In the example of Figure 7F, long duct sealing is obtained by providing a welded sheet 1013 on the inner surface of the housing 101. The welded sheet 1013 may cover a part or the entire inner surface of the housing 101. It is to be noted that sealing can be maximized by providing a welded sheet 1013 or an overmolded seal 1012 on the inner surface of the housing 101 combined with an overmolded seal 1092 at the free end of the lip 1091 for instance. It is also to be noted that the sealing arrangements described in relation to figures 7A to 7E may also be applied to the charge air ducts described in the embodiments of figures 2A-2B and figures 4A-4C. Figures 5A to 5C show an alternative embodiment of a charge air duct 500. Components in these figures corresponding to those in Figures 1A to 1C have reference numerals which are 400 or 4000 higher. The charge air duct 500 in this embodiment comprises a long duct 508 designed as a swirl duct and arranged around a main short duct 502, which is bended. It is to be noted that the long duct 508 is blow molded on and around the short duct 502. In figure 5A, the flap 5052 is closed so that charge air is directed as illustrated by the arrows from the inlet port 503 into the long duct 508 via the radial opening 510. As illustrated in Figure 5C, which is a detail view of Figure 5A, air flowing into the long duct 508 is directed towards the outlet port 504 via the radial opening 511. The radial opening 511 is located between the control device 505 and the air outlet 504. In figure 5B, the flap 5052 is opened so that charge air is directed as illustrated by the arrows from the inlet port 503 to the outlet port 504 via the short duct 502. Figures 6A to 6C show another alternative embodiment of a charge air duct 600 in which the long duct 608 is also blow molded on and around the short duct 602. Components in these figures corresponding to those in Figures 1A to 1C have reference numerals which are 500 or 5000 higher. It is to be noted that the main duct 602 is straight in this embodiment. In figure 6A, the flap 6052 is closed so that charge air is directed as illustrated by the arrows from the inlet port 603 into the long duct 608 via the radial opening 610. As illustrated in Figure 6C, which is a detail view of Figure 6A, air flowing into the long duct 608 is directed towards the outlet port 604 via the radial opening 611. The radial opening 611 is located between the control device 605 and the air outlet 604. In figure 6B, the flap 6052 is opened (this is shown in Figure 6D which is a top view of the charge air duct 600 of Figure 6B ) so that charge air is directed as illustrated by the arrows from the inlet port 603 to the outlet port 604 via the short duct 602. Figures 2A and 2B show the charge air duct 200 according to another embodiment of the invention in which the longitudinal axis 2071 of the long duct 208 is substantially parallel to the longitudinal axis 2072 of the short duct 202. Thus, unlike the previous embodiments, the long duct 208 in this embodiment does not swirl around the short duct 202. Components in these figures corresponding to those in Figures 1A to 1C have reference numerals which are 100 or 1000 higher. The housing 201 of the charge air duct 200 comprises a first hollow cylindrical part 2011 defining the short duct 202 and a second juxtaposed hollow cylindrical part 2012. A rotating flap 2052 is located inside the short duct 202. A tube 209 carrying a swirling lip 2091 is inserted inside the second cylindrical part 2012 (which is closed by a cover 212), thus defining the long duct 208. When the flap 2052 is closed ( figure 2A ), charge air from the air inlet 203 is directed in the long duct 208 via a radial air opening 210. Charge air is then directed towards the air outlet 204 via a radial air opening 211. When the flap 2052 is opened ( figure 2B ), charge air flows in the short duct 202. Figures 3A and 3B show the charge air duct 300 according to another embodiment in which the longitudinal axis of the long duct 308 is substantially parallel to the longitudinal axis of the short duct 302. Components in these figures corresponding to those in Figures 1A to 1C have reference numerals which are 200 or 2000 higher. In this embodiment, the housing 301 of the charge air duct 300 comprises a first hollow cylindrical part 3011 defining the short duct 302 and a second juxtaposed hollow cylindrical part 3012. A rotating flap 3052 is located inside the short duct 302. An insert 309 carrying several bends 3093 is inserted inside the second cylindrical part 3012 (which is closed by a cover 312), thus defining the long duct 308. When the flap 3052 is closed ( figure 3A ), charge air from the air inlet 303 is directed in the long duct 308 via a radial air opening 310. Air is redirected by 180°, the sequence of redirection or bends forming a "S". Charge air is then directed towards the air outlet 304 via a radial air opening 311. When flap 3052 is opened ( figure 3B ), charge air flows in the short duct 302. With reference to Figures 4A to 4C, it is shown a charge air duct 400 according to another embodiment of the invention. Components in these figures corresponding to those in Figures 1A to 1C have reference numerals which are 300 or 3000 higher. The housing 401 in this embodiment has a general "T" shape and comprises a first hollow cylindrical part 4011 whose longitudinal axis 4071 is perpendicular to the longitudinal axis 4072 of a second hollow cylindrical part 4012. A rotating flap 4052 is located within the short duct 402 formed by the hollow cylindrical part 4011. A tube, or central part, 409 carrying a double helix 4091 is inserted inside the second cylindrical part 4012 (which is closed by a cover 412), thus defining the long duct 408. Each of the helix forming the double helix 4091 forms several turns, clockwise or anticlockwise, over a complete revolution around the axis 4072. The outer periphery of each helix is in contact with the inner surface of the housing 401, thus defining a long swirl duct 408. The long duct 408 comprises a first duct portion 4081 which is in communication with a second duct portion 4082 near the bottom end of the second hollow cylindrical part 4012. When the flap 4052 is closed ( figure 4A ), charge air from the air inlet 403 is directed in the long duct 408 via a radial air opening 410. First, air is spiralling down within the first duct portion 4081, and then is spiralling up within the second duct portion 4082 ( Figure 4C is a section view along the axis A-A of the charge air duct 400 of Figure 4A ). Charge air is then directed towards the air outlet 404 via a radial air opening 411. When flap 4052 is opened ( figure 4B ), charge air flows in the short duct 402. Figures 8 and 9 show two possible ways of connecting a charge air duct according to an embodiment of the invention with an intake manifold of a combustion engine. The charge air duct 800 shown in Figure 8 comprises a short duct 802 and a long duct 808 spiralling around the short duct 802. The on/off flap 8052 is positioned so as to close the short duct 802. The charge air flow entering the air inlet 803 is thus directed in the long duct 808 and flows out of the air outlet 8111 into the plenum of the intake manifold 850. Although not illustrated, when the on/off flap 8052 opens the short duct 802, air flows out of the air outlet 8110 into the plenum of the intake manifold 850 (there is a single radial air opening 810 between the short duct 802 and the long duct 808). The charge air duct 800 comprises a throttle valve 8053 located in the air outlet 8111. The throttle valve 8053 can be an on/off valve or a progressive valve. Thus, in this embodiment, the on/off flap 8052 and the throttle valve 8053 are integrated in the charge air duct 800, which is secured to the intake manifold 850. The direct connection of the charge air duct 800 on the plenum of the intake manifold 850 is advantageous in that it eliminates the need to use a dosing device in the intake manifold. Such an on/off flap and a throttle valve can also be integrated in the charge air duct 400 for instance (the throttle valve would be located in the air outlet 411 in that case). The throttle valve 8053 allows the dosing of charge air from the long duct 808 into the plenum of the intake manifold 850. In figure 9, the on/off flap 8052 and the throttle valve 8053 are not integrated in the charge air duct 800, but in an intermediate housing 960 which is secured at one end to the charge air duct 900 and at the other end to the intake manifold 950. In other words, the on/off flap 8052 and the throttle valve 8053 form an added system to the charge air duct 900. Components in these figures corresponding to those in Figure 8 have reference numerals which are 100 or 1000 higher. Figure 10 show one possible way of connecting the charge air duct 400 according to the embodiment described in relation to figures 4A to 4C with an intake manifold 850 of a combustion engine. As mentioned previously, the charge air duct 400 comprises a rotating flap 4052 located within the short duct 402 formed by the hollow cylindrical part 4011. A tube, or central part, 409 carrying a double helix 4091 defines the long duct 408. In this embodiment, the charge air duct 400 further comprises a throttle valve 4053 located in the air opening 411. The throttle valve 4053 can be an on/off valve or a progressive valve. In other words, the on/off flap 4052 and the throttle valve 4053 are integrated in the charge air duct 400. The throttle valve 4053 allows the dosing of charge air from the long duct 408 into the plenum of the intake manifold 850. In all of the embodiments described, the charge air duct is made of plastics. Such a charge air duct is thus cost-effective to produce and is of relative low weight. In an alternative, the charge air duct can be manufactured in aluminum. The charge air duct of the invention is also easy to assemble and compact. As mentioned previously, the charge air duct of the invention can be easily adapted to different operating situations of the engine, whether in the low speed range or in the high speed range. The charge air duct of the invention improves the dynamic behavior of the vehicle providing more torque at low engine speed, and needing less time to torque. It reduces fuel consumption and CO _2 emissions. The solution of the invention can be applied to all types of turbocharged engines. The above embodiments are to be understood as illustrative examples of the invention. Further embodiments of the invention are envisaged.

1. A charge air duct (100) for delivering charge air to an intake manifold of an internal combustion engine, said charge air duct (100) comprising a housing (101) with at least one charge air inlet (103) and at least one charge air outlet (104),: characterized in that said charge air duct (100) comprises control means (105) arranged in the housing (101) to influence the charge air flow, the charge air being guided from the inlet (103) to the outlet (104) via a first duct (102) in a first position of the control means (105) and from the inlet (103) to the outlet (104) via a second duct (108) in a second position of the control means (105),: and in that said first duct (102) and said second duct (108) are of different geometry.

2. A charge air duct (100) according to claim 1, characterized in that the length of said second duct (108) is greater than the length of said first duct (102). 3. A charge air duct (100) according to claim 2, characterized in that the cross-section of said first duct (102) is greater than the cross-section of said second duct (108). 4. A charge air duct (100) according to any one of claims 1 to 3, characterized in that the control means (105) close said first duct (102) in said second position and open said first duct (102) in said first position without closing said second duct (108). 5. A charge air duct (100) according to any one of claims 1 to 4, characterized in that the control means (105) comprise a first valve (1052) rotatable about an axis (106) extending along a diameter of said first duct (102). 6. A charge air duct (100) according to any one of claims 1 to 5, characterized in that said second duct (108) is swirling around said first duct (102). 7. A charge air duct (100) according to any one of claims 1 to 6, characterized in that said first duct (102) and said second duct (108) have the same longitudinal axis (107). 8. A charge air duct (100) according to any one of claims 1 to 5, characterized in that the longitudinal axis (2071) of said first duct (202) and the longitudinal axis (2072) of said second duct are substantially parallel (208). 9. A charge air duct (100) according to claim 1 to 8, characterized in that said second duct (108) is a helical duct comprising a helical fin (1091) arranged on the outer wall of a central part (109). 10. A charge air duct (100) according to any one of claims 1 to 5, characterized in that the longitudinal axis (4071) of said first duct (402) and the longitudinal axis (4072) of said second duct (408) are substantially orthogonal. 11. A charge air duct (100) according to claim 10, characterized in that said second duct (408) comprises a first clockwise helical duct portion (4081) in communication with a second anti-clockwise helical duct portion (4082), each duct portion (4081, 4082) comprising a helical fin arranged on the outer wall of a central part (409). 12. A charge air duct (100) according to any one of claims 9 to 11, characterized in that said at least one helical fin (1091) is in contact with the inner surface of said housing (101). 13. A charge air duct (100) according to claim 12, characterized in that said inner surface (101) and/or said at least one helical fin (1091) comprise(s) sealing means. 14. A charge air duct (100) according to any one of claims 1 to 5, characterized in that said second duct (308) comprise several bends (3093) designed to redirect the charge air flow by an angle comprised between 90° and 180°. 15. A charge air duct (100) according to any one of claims 1 to 14, characterized in that it comprises a second valve (8053) located in said second duct (808).

2873851

Aerating system for hydraulic turbine

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows an installation for the conversion of energy according to the present invention. This installation comprises a hydraulic turbine 31 that, in Figure 1, is a Francis turbine. The rotating part of the hydraulic turbine 31 is a runner 10, in this Figure 1, of the Francis type. This runner 10 rotates around a vertical axis 202, driving the rotation of a drive shaft 204. The drive shaft 204 is linked to a generator 206 for producing electricity. However, it is also possible to use the mechanical energy produced for driving another device. The water is stored upstream in a water reservoir not shown in Figure 1. Water is then then provided into the hydraulic turbine 31 via a pressure pipe 22 having a drop height defined by the difference in elevation between the water reservoir and the hydraulic turbine 31. The pressure pipe 22 ends into a cover 24 which surrounds the runner 10 and allows distributing water substantially uniformly around the vertical axis 202 within the runner 10. More specifically, the water flows between the runner blades 2 that are arranged between a crown 2022 and a band 2020 in the runner 10. Each of these blades 2 comprises a leading edge 2080 against which the water comes from the cover 24 and a trailing edge 2082 from which water escapes into a draft tube 26. The blades 2 have an asymmetric profile with a lower surface 2084 and an upper surface 2086. The direction of flow of water through the hydraulic turbine 31 is shown in Figure 1, by arrows E. The present invention relates to an aerating system 100 in the runner 10 of a hydraulic turbine. The aerating system 100 of the invention comprises a plurality of hydrofoils 12 located in the inter-blade canals 11 of the water passage of the hydraulic turbine, these inter-blade canals 11 being used for the air admission in the water flow, thus increasing the dissolved oxygen level contained in the water circulating through the hydraulic turbine. The aerating system 100 of the invention is shown in Figures 1 to 6. The hydrofoils 12 of the aerating system 100 of the invention are located inside the inter-blades canals 11 of the runner 10. Each hydrofoil 12 is connected to the pressure side 101 or to the blade suction side 102 or to both sides 101 and 102, of the inter-blade canals 11. According to the invention, it is necessary that at least one of the blades 2 of the runner 10 that is in contact with the hydrofoil 12 comprises an aerating canal 20 to deliver air to the hydrofoil 12. This canal 20 can either connect an air inlet at the runner crown or the runner band to the hydrofoil. The profile of the hydrofoil 12 of the invention is non-axis symmetrical. The hydrofoil 12 can be made from two plates 13 and 14 with a free passage in between, or can be made from one plate having aerating canals inside to allow air admission at the hydrofoil 12 trailing edge or at one of its sides. The hydrofoil 12 is located inside the inter-blades canal 11 where the water flow conditions best optimize the natural air admission and dissolved oxygen enhancement, for the turbine operating point. It is possible to use one or several hydrofoils 12 in a turbine runner 10. It is possible to use the same hydraulic profile for all the hydrofoils 12 or several different hydraulic profiles. It is possible to locate all the hydrofoils 12 at the same elevation inside the inter-blades canal 11 or at different elevations depending of the expected characteristics. It is possible to use one or several hydrofoils 12 at different elevation in a same inter-blades canal 11. All these characteristics configure the different embodiments of the system of the invention. Preferably, the chord of the hydrofoil is longer on the side where it connects to the aerating canal 20 and its length decreases through the inter-blade canal 11 in order to minimize friction losses. The proposed solution according to the invention results in a distributed aerating system 100 that can be located exactly where the air admission is the most efficient for the considered operating condition of the hydraulic turbine. The outlet of the runner 10 is an appropriate location that allows good mixing between air and water; furthermore, the air admission system efficiency increases when the water pressure at the injection location is low. The pressure at the runner outlet varies in azimuth from the blades suction side 102 to the pressure side 101 and in the meridian view from the band side to the crown side. The proposed aerating system 100 is the only one that allows air admission in the inter-blades canals 11, from any optimized location on the suction side 102 to any optimized location on the pressure side 101. The proposed design is an appropriate solution which satisfies the dissolved oxygen enhancement market demands at present. It mainly concerns Francis turbines but it could also be considered for Propeller turbines.

1. Aerating system (100) for the runner (10) of a hydraulic turbine, the runner (10) comprising a plurality of blades (2), such that inter-blade canals (11) are configured between each pair of blades (2) for the admission of air in the water flow circulating through the hydraulic turbine, characterized in that the aerating system (100) comprises at least one hydrofoil (12) located in the inter-blade canal (11) of the runner (10) contacting the pair of blades (2) configuring the inter-blade canal (11) where the hydrofoil (12) is located, such that the hydrofoil (12) has a non-axis symmetrical profile, and such that at least one of the blades (2) in contact with the hydrofoil (12) comprises an aerating canal (20) delivering air to the hydrofoil (12).

2. Aerating system (100) according to claim 1 characterized in that the aerating canal (20) is delivering air from the runner crown to the hydrofoil (12). 3. Aerating system (100) according to claim 1 characterized in that the aerating canal (20) is delivering air from the runner band to the hydrofoil (12). 4. Aerating system (100) according to any of claims 1-3 characterized in that it comprises an electronic device controlling the air flow through the aerating system (100). 5. Aerating system (100) according to any of the previous claims characterized in that the hydrofoil (12) is connected to the pressure side (101) of the inter-blade canal (11). 6. Aerating system (100) according to any of claims 1-4 characterized in that the hydrofoil (12) is connected to the suction side (102) of the inter-blade canal (11). 7. Aerating system (100) according to any of claims 1-4 characterized in that the hydrofoil (12) is connected to the pressure side (101) and to the suction side (102) of the inter-blade canal (11). 8. Aerating system (100) according to any of the previous claims, characterized in that the hydrofoil (12) comprises two plates (13, 14) and a free passage in between to allow the admission of air. 9. Aerating system (100) according to any of claims 1-7, characterized in that the hydrofoil (12) comprises one plate and also comprises a plurality of aerating canals inside to allow the admission of air. 10. Aerating system (100) according to any of the previous claims, characterized in that it comprises a plurality of hydrofoils (12), each one having a different hydraulic profile. 11. Aerating system (100) according to any of claims 1-9, characterized in that it comprises a plurality of hydrofoils (12), all of them having the same hydraulic profile. 12. Aerating system (100) according to any of the previous claims, characterized in that it comprises a plurality of hydrofoils (12), all of them located at the same elevation in the inter-blade canals (11), with respect to the runner (10). 13. Aerating system (100) according to any of claims 1-11, characterized in that it comprises a plurality of hydrofoils (12), all of them located at different elevations in the inter-blade canals (11), with respect to the runner (10). 14. Aerating system (100) according to any of claims 1-11, characterized in that it comprises a plurality of hydrofoils (12), all of them located at different elevations with respect to the runner (10), in one single and the same inter-blade canal (11). 15. Hydraulic turbine comprising an aerating system (100) according to any of claims 1-14.

2881679

Electric heater

Based on the following detailed description of an invention, generate the patent claims. There should be 10 claims in total. The first, independent claim is given and the remaining 9 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The invention is explained in detail below by means of an exemplary embodiment and with reference to the drawings, in which; - Figure1: shows a circuit board with a multitude of contact areas that are electrically connected to a power supply, whereby two heating elements are shown next to the circuit board, whereby each heating element shows one connector clip through which the heating elements can be connected to the circuit board, and - Figure 2: shows the embodiment of figure 1, whereby the connector clips of the heating elements are connected to the circuit board by means of the connector clips. #### Preferred Embodiments Of The Invention Figure 1 shows an electric heater 1 with one circuit board 2 and two heating elements 4. Each heating element 4 possesses a multitude of heat transmitting fins 5 and at least one PTC-heating element (not shown in figure 1 ). Each heating element 4 further shows a connector clip 6, which can be used to connect the heating element 4 to the circuit board 2. The circuit board 2 possesses a multitude of contact areas 3. These contact areas 3 are connected to a power supply that is not shown in figure 1. The connection between the contact areas 3 and the power supply can be realized by conducting paths and power switches on the circuit board 2. The circuit board 2 can be a printed circuit board as it is widely known in the state of the art. The contact areas 3 are located near to one of the edges of the circuit board so that they can easily be covered by the connector clips 6 of the heating elements 4. To cover the contact areas 3 with the connecter clips 6, the connector clips 6 can be plugged over the edge of the circuit board 2 in a way that one of the flexible extensions 7 slips over the circuit board 2 and the other flexible extension 7 slips under the circuit board 2. The flexible extensions 7 in figure 1 are arched. The tips of the flexible extensions 7 point away from each other. This design of the connector clip 6 makes it easier to slip the connector clip 6 over the circuit board 2. The deflection of the flexible extensions 7, which is caused by the circuit board 2 as it has a height that is bigger than the smallest distance between the flexible extensions 7 of one connector clip 6, creates a force that is directed at the circuit board 2 and that creates a contact pressure between the flexible extensions 7 and the circuit board 2. This contact pressure helps to avoid relative movement between the circuit board 2 and the connector clip 6 and thus stabilizes the connection. Each connector clip 6 can be attached to the circuit board 2 in a way that only one contact area 3 is covered by one connector clip 6. This makes it possible to create a specified electrical connection between one certain contact area 3 and one connector clip 6. As the circuit board 2 is preferably either is a control unit or is connected to a control unit it is possible to activate or deactivate the heating elements 4 individually. The circuit board 2 can possess contact areas 3 on the upper side, as shown in figure 1, and on the lower side. Depending on the conducting paths on the circuit board 2 the contact area/areas 3, that are connected with one specific connector clip 6, can be connected to one pole of a power supply or to two poles (one contact area relative to one connector relative to one pole). Especially if the contact areas 3 are connected to two different poles of a power supply it is easy to create a closed electric circuit that contains the power supply, the conducting paths, the contact areas 3, the connector clip 6, the heating element 4 and the PTC-heating elements, which are arranged alongside the heating element 4 (not shown in figure 1 ). Through a closed electric circuit a PTC-heating element can be operated in a way that heat is produced. In a still further refinement the heating elements or more specific the PTC-heating elements can be connected to a power supply by further additional means, such as cables or conductive bridge elements. To plug the connector clips 6 to the circuit board 2 the heating elements 4 must be moved in a direction, which is indicated by the arrow that is marked with the reference number 8. Figure 2 shows the embodiment of figure 1, whereby the heating elements 4 are connected to the circuit board 2. The connection is created by a lateral movement of the heating elements 4 along the direction 8 of figure 1, The connector clips 6 are slipped over the right edge of the circuit board 2. The connector clips 6 embrace the circuit board 2 with the flexible extensions 7. The deflected flexible extensions 7 create a force, which results in a contact pressure between the flexible extensions 7 and the circuit board 2. In an alternative embodiment a multitude of heating elements 4 can be applied to the circuit board. A preferred embodiment has one heating element 4 attached to each contact area 3. An electric heater can possess a multitude of circuit boards, which can be connected to each other by additional wiring or a circuit board with a multitude of busbars, which are connected to the negative pole and/or the positive pole of a power supply and can be plugged into those connector clips. The system can be arranged within a frame or a housing. It is preferred if the circuit board 2 is covered with an insulation against humidity and/or mechanical stress and/or electric short-circuits. Such means are not shown in the figures 1 and 2. In another preferred embodiment the circuit board and/or the connector clips are encased in a waterproof housing. Preferably the whole circuit board and especially the area where the electrical connection between the heating elements and the circuit board is created is encased in the housing. This helps to prevent short-circuits and damage due to corrosion. Such a housing is not shown in the figures 1 and 2. While the invention has been shown in the figures 1 and 2 in one preferred embodiment, it will be clear to those skilled in the arts to which it pertains that a variety of modifications and changes can be made thereto without departing from the scope of the invention.

1. Electric heater (1) for an automobile vehicle, with at least one heating element (4) and with at least one circuit board (2), whereby the circuit board (2) possesses at least one contact area (3) through which an electrical connection between a heating element (4) and a power supply can be realized, whereas the heating element (4) possesses at least one PTC-heating element, characterized in that the heating element can be clipped to the circuit board (2) by the means of a connector clip (6), whereby the connector clip (6) possesses two flexible extensions (7), which are arranged opposed to each other,

2. Electric heater (1) as claimed in claim 1, characterized in that the distance between the two flexible extensions (7) is smaller than the height of the plate-shaped circuit board (2) in the zone of the contact area (3). 3. Electric heater (1) as claimed in one or more of the previous claims, characterized in that the connector clip (6) forms a U-shaped cross-section, which forms a receiving area, whereby the circuit board (2) can be inserted into the receiving area. 4. Electric heater (1) as claimed in claim 3, characterized in that a force is created by the insertion of the circuit board (2) into the receiving area of the connector clip (6), whereby the force creates contact pressure between the contact area (3) and the flexible extensions (7). 5. Electric heater (1) as claimed in one or more of the previous claim, characterized in that at least one of the flexible extensions (7) is electrically conductive. 6. Electric heater (1) as claimed in one or more of the previous claims, characterized in that the PTC-heating element is electrically connectable to the contact area (3) by the heating element (4) and/or the connector clip (6). 7. Electric heater (1) as claimed in one or more of the previous claims, characterized in that the contact area (3) and/or the circuit board (2) and/or the connector clip (6) is covered by an electrical insulation and/or an insulation against fluid leakage and/or an insulation against mechanical stress. 8. Electric heater (1) as claimed in one or more of the previous claims, characterized in that the circuit board (2) and/or the contact area (3) of the circuit board (2) is electrically connected to at least one pole of a power supply. 9. Electric heater (1) as claimed in one or more of the previous claims, characterized in that the circuit board (2) is encased in a housing partially or in full extent. 10. Electric heater (1) as claimed in one or more of the previous claims, characterized in that the heating element (4) is a planar body which extensions in two of the three spatial directions are larger than the extension in the third spatial direction, whereby the PTC-heating element is connected to one side of the heating element (4) and one or more fins (5) are connected to the opposed side of the heating element (4).

2829756

Auxiliary bearing of the ball bearing type for a magnetically suspended rotor system

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will be described in connection with preferred embodiments which are given by way of examples. Figure 1 shows an example of a portion of an auxiliary bearing of the ball bearing type according to a first example of the invention. Such auxiliary bearing may be used with a conventional active radial magnetic bearing as defined in connection with Figure 7. Figure 1 shows an example of an auxiliary bearing 118 of the ball-bearing type comprising a pair of rolling elements 103, 113, each set of rolling elements 103, 113 being between a stator cage 101, 111 and a rotor cage 102, 112. In this embodiment he rotor cage 102, 112 is integral with a rotor member 104, 114 rotating around an axis X-X' 106 or X"-X"' 116 respectively, whereas a clearance E2 is defined between the stator cage 101, 111 and a stationary stator member 105, 115 respectively. The clearance E2 may be for example between 0.2 and 0.3 millimeter and is smaller than the air gap of the associated radial magnetic bearing (not shown), which may be for example between 0.4 and 0.6 millimeter. Usually the clearance of the auxiliary bearing is about half the air gap of the magnetic bearing. It may be noted that in the embodiment of Figure 1, the clearance E2 is defined between an annular surface 124 constituted by the outer surface of the stator cage 101, 111 and the stationary stator member 105, 115, whereas the annular surface 123 constituted by the outer surface of the rotor cage 102, 112 is integral with the rotating shaft 104, 114. However, the invention similarly applies to an embodiment where the clearance E2 is defined between an annular surface 123 constituted by the outer surface of the rotor cage 102, 112 and the rotating shaft 104, 114, whereas the annular surface 124 constituted by the outer surface of the stator cage 101, 111 is integral with the stationary stator member 105, 115. According to the invention, an offset is created between the first and second ball bearings constituting the auxiliary bearing 118. The assembly of Figure 1 is thus constructed in such a way that a radial misalignment Δ is voluntarily created between the axis X-X' 106 and the axis X"-X"' 116 and more generally between the first ball bearing comprising rolling elements 103 and the second ball bearing comprising rolling elements 113. In the embodiment of Figure 1, the radial misalignment Δ is generated mainly by geometrical means, i.e. there is an offset in the bearing housing seats of the first and second ball bearings. However the offset and radial misalignment may be further created by applying (in the direction of arrows 150 and 160) specific loads which are different for both ball bearings. These loads may be generated for example by radial or axial springs having different stiffnesses or having different preloading conditions. Figure 2 shows an example of a portion of an auxiliary bearing of the ball bearing type according to a second example of the invention. Such auxiliary bearing may be used with a conventional active radial magnetic bearing as defined in connection with Figure 7. Figure 2 shows an example of an auxiliary bearing 218 of the ball-bearing type comprising a pair of rolling elements 203, 213, each set of rolling elements 203, 213 being between a stator cage 201, 211 and a rotor cage 202, 212. The rotor cage 202, 212 is integral with a rotor member 204, 214 rotating around an axis X-X' 206, whereas a clearance E2 is defined between the stator cage 201, 211 and a stationary stator member 205, 215 respectively. The clearance E2 may be for example between 0.2 and 0.3 millimeter and is smaller than the air gap of the associated radial magnetic bearing (not shown), which may be for example between 0.4 and 0.6 millimeter. Usually the clearance of the auxiliary bearing is about half the air gap of the magnetic bearing. It may be noted that in the embodiment of Figure 2, the clearance E2 is defined between an annular surface 224 constituted by the outer surface of the stator cage 201, 211 and the stationary stator member 205, 215, whereas the annular surface 223 constituted by the outer surface of the rotor cage 202, 212 is integral with the rotating shaft 204, 214. However, the invention similarly applies to an embodiment where the clearance E2 is defined between an annular surface 223 constituted by the outer surface of the rotor cage 202, 212 and the rotating shaft 204, 214, whereas the annular surface 224 constituted by the outer surface of the stator cage 201, 211 is integral with the stationary stator member 205, 215. According to the invention, an offset is created between the first and second ball bearings constituting the auxiliary bearing 218. The assembly of Figure 2 is thus constructed in such a way that an angular misalignment α is voluntarily created between the first ball bearing comprising rolling elements 103 and the second ball bearing comprising rolling elements 113. In the embodiment of Figure 2, the angular misalignment α is generated mainly by geometrical means, i.e. there is an offset in the bearing housing seats of the first and second ball bearings. For example as shown in Figure 2, the second ball bearing with rolling elements 213 is mounted substantially perpendicularly to the axis X-X' 206, whereas the first ball bearing with rolling elements 203 is inclined by an angle α. Typically the angle α may be comprised between about 5 and 30 degrees, but other values are possible according to the needs. The offset and angular misalignment may be further created by applying (in the direction of arrows 250 and 260) specific loads which are different for both ball bearings. These loads may be generated for example by radial or axial springs having different stiffnesses or having different preloading conditions. In the same auxiliary bearing it is also possible to combine a radial misalignment Δ as shown in Figure 1 and an angular misalignment α as shown in Figure 2. Some additional means may be used to generate an offset between two ball bearings used in the same auxiliary bearing. Thus a non-uniform circumferential axial preload may be applied on each ball bearing in the direction of the arrows 150, 160 of Figure1 or in the direction of the arrows 250, 260 of Figure2. The circumference variation of axial preload will induce a variation of the angular contact between the balls 103, 113; 203, 213 and the corresponding races. When the shaft is rotating, in one revolution thanks to the angular contact variation, the balls 103, 113; 203, 213 will accelerate and decelerate, thus producing a "traffic jam effect" which will increase significantly the ball bearing resistive torque. It may be noted that due to the soft way of applying axial and radial preload on the ball bearings, a geometrical offset may be obtained as defined here-above with respect to Figures 1 and 2. For example the bolting torque of each of a plurality of spring shims located around the circumference of the first and second ball bearings may be chosen to be non-uniform and therefore it is possible to purposely generate an offset in axial loading. Figure 3 illustrates another example of additional means used to create an offset in the ball bearings of an auxiliary bearing. The embodiment of Figure 3 is substantially similar to the embodiment of Figure 1 and the same elements have the same reference numerals and will not be described again. In the embodiment of Figure3, a radial spring washer 144A is inserted between the rotor cage 102 and the rotor member 104. Similarly a radial spring washer 144B is inserted between the rotor cage 112 and the rotor member 104. The radial spring washers 144A, 144B are annular wavy radial spring washers which may have the shape of corrugated steel strips 144 as illustrated in Figures 4 and 5 before receiving an annular shape. The thickness a of the strip, the pitch p of the corrugations, the height h of the corrugations and the width L of the strip 144 contribute to define the stiffness of the spring constituted by such a corrugated strip 144 when it is put in annular shape to constitute a radial spring washer 144A, 144B interposed between a rotor cage 102, 112 and a rotary member 104, 114. The corrugated steel strips 144, which are also named "Borelly springs", may be manufactured and used as described in French patent [PATCIT FR2614375]. According to the invention, the radial spring washers 144A, 144B are designed to have a different stiffness around a circumference and also to have different stiffnesses for each of the ball bearings constituting an auxiliary bearing. In the embodiment illustrated in Figure 3, radial spring washers are inserted between rotor cages 102, 112 and a rotary member 104, 114, whereas a clearance E2 is created between stator cages 101, 111 and a stationary stator member 105, 115. However it is also possible to create a clearance E2 between rotor cages 102, 112 and the rotary member 104, 114 and to interpose the radial spring washers 144A, 144B between stator cages 101, 111 and the stationary member 105, 115. The embodiment of Figure 3 may also be combined with the embodiment of Figure 2, i.e. radial spring washers 144A, 144B may also be inserted between the rotor cages 202, 212 and the rotary member 204, 214 in an embodiment creating an angular misalignment or alternatively radial spring washers 144A, 144B may also be inserted between the stator cages 201, 211 and the stationary stator member 205, 215 in an embodiment creating an angular misalignment if a clearance is created between the rotor cages 202, 212 and the rotary member 204, 214. The invention enables to increase significantly and in a controlled manner the starting torque of a set of ball bearings assembled in a cartridge used for the purpose of securing the landing of the rotor for a machine levitated on active magnetic bearings. The starting torque will be adjusted to be higher than the aerotorque generated by aerodynamic effects. It is to be noted that loads applied on the ball bearings set during landing are significantly higher than ball bearing preload which may therefore be qualified as "soft" preload. The features of the present invention thus enable to improve the starting torque of an auxiliary bearing without significantly modifying the ball bearing behavior during landing. The auxiliary bearing according to the invention may be used for different applications, for example in the automotive industry (with bearings of relatively small size), e.g. for small turbo-compressors or in oil and gas industry (with bearings of a larger size), e.g. for motor compressors.

1. An assembly comprising a rotating shaft (104, 114; 204, 214) supported with respect to a stationary housing (105, 115; 205, 215) by at least one active magnetic bearing presenting a mean radial air gap and at least one auxiliary bearing (118; 218) comprising first and second coaxially arranged annular surfaces (124, 123), one (124) of said first and second coaxially arranged annular surfaces (124, 123) defining a clearance (E2) with one of said stationary housing (105, 115; 205, 215) and said rotating shaft (104, 114; 204, 214), said clearance (E2) being less than said mean radial air gap, and the other (123) of said first and second coaxially arranged annular surfaces (124, 123) being integral with the other one of said stationary housing (105, 115; 205, 215) and said rotating shaft (104, 114; 204, 214), characterized in that the auxiliary bearing (118; 218) comprises a first ball bearing and a second ball bearing having a misalignment with respect to each other.

2. The assembly according to claim 1, wherein said misalignment is a radial misalignment. 3. The assembly according to claim 1, wherein said misalignment is an angular misalignment. 4. The assembly according to claim 1 or claim 2, wherein said radial misalignment is broader than said clearance (E2). 5. The assembly according to claim 1 or claim 3, wherein said angular misalignment is comprised between 5 and 30 degrees. 6. The assembly according to any one of claims 1 to 5, wherein said misalignment is both a radial misalignment and an angular misalignment. 7. The assembly according to any one of claims 1 to 6, wherein said misalignment is obtained exclusively by a geometrical offset between said first and second ball bearings. 8. The assembly according to any one of claims 1 to 7, wherein said misalignment is obtained at least partly by application of a differential load on said first and second ball bearings. 9. The assembly according to any one of claims 1 to 6, wherein said misalignment is obtained by application of a load through axial or radial springs having different stiffnesses or different preloading conditions. 10. The assembly according to any one of claims 1 to 6, wherein said misalignment is obtained through application of a non-uniform circumferential axial preload on the first and second ball bearings. 11. The assembly according to any one of claims 1 to 6, wherein said misalignment is obtained at least partly by the insertion of a first and a second annular wavy radial spring washers (144A, 144B) between said other (123) of said first and second coaxially arranged annular surfaces (124, 123) of said first and second ball bearings respectively and said other one of said stationary housing (105, 115; 205, 215) and said rotating shaft (104, 114; 204, 214), said first annular wavy spring washer (144A) having a different stiffness from said second annular wavy spring washer (144B). 12. The assembly according to claim 11, wherein said first and second annular wavy spring washers (144A, 144B) further each have different stiffnesses around circumferences of the respective first and second ball bearings. 13. The assembly according to any one of claims 1 to 12, wherein said mean radial air gap is between 0.2 and 0.5 mm and said clearance (E2) is between 0.15 and 0.3 mm. 14. A radial magnetic bearing device, characterized in that it comprises an assembly according to any one of claims 1 to 13.

2854258

Permanent magnet rotor shaft assembly and method

Based on the following detailed description of an invention, generate the patent claims. There should be 11 claims in total. The first, independent claim is given and the remaining 10 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will be described in connection with preferred embodiments which are given by way of examples. A typical arrangement of a first embodiment of the invention is illustrated in Figure 1 which shows a permanent rotor shaft assembly 100 for an electrical machine, more specifically for high speed applications which can reach tip speeds up to 300 m/s. The assembly 100 comprises a permanent magnet cylindrical core 101 having a longitudinal axis X-X'. The cylindrical core 101 is axially compressed by first and second end shafts 102A, 102B and is radially compressed by a sleeve 104 made of a non-magnetic high strength metal. The set of elements 101, 102A and 102B forms the overall rotor shaft. According to the invention one (102A) of the first and second end shafts 102A, 102B comprises, in its portion facing the cylindrical core 101, a central shoulder head 103A which cooperates with a mating central recess 106A made in a central portion of a front face of the cylindrical core 101. The shoulder head 103A insures the concentricity of the elements 101 and 102A during the assembly process and provides support for the cylindrical magnet core 101, whilst introducing additional stiffness to the set of assembled elements 101, 102A and 102B once the mounting process is achieved. The permanent magnet cylindrical core 101 comprises rare earth magnets such as NdFeBr or Sm2Co17. The sleeve 104 is made of a non-magnetic high strength metal which may be advantageously chosen among Inconel, Hastelloy, Ti-6%Al-6%V-2%Sn, Ti-2.5%Cu. The magnetization direction of the magnet 101 may be radial, diametral or constituted by a Halbach magnetization. The polarity of the magnets of the core 101 can be 2 poles or 4 poles. The central shoulder head 103A is inserted in the mating central recess by tight fit assembly, slip joint assembly or glued assembly. The first and second end shafts 102A, 102B and the sleeve 104 are fixed on the permanent magnet cylindrical core 101 by welding, adhesive or heat shrinking. The sleeve 104 constitutes a hoop which radially compresses the permanent magnet cylindrical core 101 and the first and second end shafts 102A, 102B. The first and second end shafts 102A, 102B axially compress the permanent magnet cylindrical core 101. According to a specific embodiment, the first and second end shafts 102A, 102B further comprise cylindrical tracks 105A, 105B for mechanical bearings. The reference numerals 105A, 105B may also alternatively represent cylindrical stack iron laminations for magnetic bearings. Such cylindrical stack iron laminations may be made on the first and second end shafts 102A, 102B as an alternative for cylindrical tracks for mechanical bearings, but the first and second end shafts 102A, 102B may also comprise simultaneously in a not shown embodiment a combination of both cylindrical tracks for mechanical bearings (such as auxiliary bearings associated with magnetic bearings) and cylindrical stack iron laminations for magnetic bearings. The tracks for mechanical bearings and/or the stack iron laminations for magnetic bearings may be located on a stepped portion 122A, 122B of the first and second end shafts 102A, 102B. Actually the elements 105A, 105B may be located at different levels (different area or different shoulder) of the end shafts according to the needs. Figs 2 and 3 illustrate a second embodiment of the invention which relates to a permanent rotor shaft assembly 200 for an electrical machine, more specifically for high speed applications which can reach tip speeds up to 300 m/s. The permanent rotor shaft assembly 200 comprises a permanent magnet cylindrical core 201 having a longitudinal axis X-X'. The cylindrical core 201 is axially compressed by first and second end shafts 202A, 202B and is radially compressed by a sleeve 204 made of a non-magnetic high strength metal. The set of elements 201, 202A and 202B forms the overall rotor shaft in a manner similar to the overall rotor shaft of the assembly 100 of the first embodiment. However in the permanent rotor shaft assembly 200 according to the second embodiment of Figs 2 and 3, a central shoulder head 203A, 203B is provided in each of the first and second end shafts 202A, 202B, in its portion facing the cylindrical core 201, a mating central recess 206A, 206B is provided in each of the central portions of the front faces of the cylindrical core 201, and the central shoulder heads 203A, 203B are respectively mounted in the mating central recesses 206A, 206B. Such arrangement of the second embodiment is otherwise similar to the first embodiment and the same materials, assembly means and optional features such as the additional tracks or stack iron laminations 105A, 105B of Figure 1 may also be applied to the embodiment of Figure 2. The assembly 200 of Figure 2 nevertheless constitutes a best mode of implementation of the invention and ensures an easy concentric alignment of the elements 202A, 201, 202B, whilst inserting the sleeve 204 and confers an enhanced stiffness on the set of elements once assembled. The invention further relates to a method for making a permanent rotor shaft assembly 100 or 200 for an electrical machine, comprising the steps of: - forming a permanent magnet cylindrical core 101 respectively 201 having a longitudinal axis X-X', - bonding a first end shaft 102A respectively 202A onto one end of the permanent magnet cylindrical core 101 respectively 201, - bonding a second end shaft 102B respectively 202B onto the other end of the permanent magnet cylindrical core 101 respectively 201, - installing a sleeve 104 respectively 204 made of a non-magnetic high strength metal in interference fit fashion around the permanent magnet cylindrical core 101 respectively 201 and the portions of the first and second end shafts 102A, 102B respectively 202A, 202B adjacent to the permanent magnet cylindrical core 101 respectively 201, so that the cylindrical core 101 respectively 201 be axially compressed by the first and second end shafts 102A, 102B respectively 202A, 202B and be radially compressed by the sleeve 104 respectively 204. More specifically, the method according to the invention further comprises the steps of: - providing at least one central shoulder head 103A respectively 203A, 203B in the first and second end shafts 102A, 102B respectively 202A, 202B, in its portion facing the cylindrical core 101 respectively 201, - providing in a central portion of a front face of the cylindrical core 101 respectively 201, at least one mating central recess 106A respectively 206A, 206B, which is adapted to cooperate with the at least one central shoulder head 103A respectively 203A, 203B, and - mounting the at least one central shoulder head 103A respectively 203A, 203B in the at least one mating central recess 106A respectively 206A, 206B, before inserting the sleeve 104 respectively 204 made of a non-magnetic high strength metal in interference fit fashion around the permanent magnet cylindrical core 101 respectively 201 and the portions of the first and second end shafts 102A, 102B respectively 202A, 202B adjacent to the permanent magnet cylindrical core 101 respectively 201. In the preferred embodiment illustrated in Figs 2 and 3, a central shoulder head 203A, 203B is provided in each of the first and second end shafts 202A, 202B, in its portion facing the cylindrical core 201, a mating central recess 206A, 206B is provided in each of the central portions of the front faces of the cylindrical core 201, and the central shoulder heads 203A, 203B are respectively mounted in the mating central recesses 206A, 206B, before inserting the sleeve 204 made of a non-magnetic high strength metal in interference fit fashion around the permanent magnet cylindrical core 201 and the portions of the first and second end shafts 202A, 202B adjacent to the permanent magnet cylindrical core 201. The central shoulder head 103A, 203A or 203B is inserted in a corresponding mating central recess 106A, 206A or 206B preferably by tight fit assembly, slip joint assembly or glued assembly. The first and second end shafts 102A, 102B respectively 202A, 202B and the sleeve 104 respectively 204 are preferably fixed to the permanent magnet cylindrical core 101 respectively 201 by welding, adhesive or heat shrinking. Generally speaking, the invention provides a simplification in the manufacturing process, increases performance and reduces cost.

1. A permanent rotor shaft assembly for an electrical machine, comprising a permanent magnet cylindrical core (101; 201) having a longitudinal axis, said cylindrical core (101; 201) being axially compressed by first and second end shafts (102A, 102B; 202A, 202B) and being radially compressed by a sleeve (104; 204) made of a non-magnetic high strength metal, characterized in that at least one (102A; 202A, 202B) of said first and second end shafts (102A, 102B; 202A, 202B) comprises, in its portion facing said cylindrical core (101; 201), a central shoulder head (103A; 203A, 203B) which cooperates with a mating central recess (106A; 206A, 206B) made in a central portion of a front face of said cylindrical core (101; 201).

2. The permanent rotor shaft assembly according to claim 1, wherein said permanent magnet cylindrical core (101; 201) comprises rare earth magnets made of NdFeBr or Sm2Co17. 3. The permanent rotor shaft assembly according to claim 1 or claim 2, wherein said sleeve (104; 204) is made of a non-magnetic high strength metal chosen among Inconel, Hastelloy, Ti-6%Al-6%V-2%Sn, Ti-2.5%Cu. 4. The permanent rotor shaft assembly according to any one of claims 1 to 3, wherein said central shoulder head (103A; 203A, 203B) is inserted in said mating central recess (106A; 206A, 206B) by tight fit assembly, slip joint assembly or glued assembly. 5. The permanent rotor shaft assembly according to any one of claims 1 to 4, wherein said first and second end shafts (102A, 102B; 202A, 202B) and said sleeve (104; 204) are fixed on said permanent magnet cylindrical core (101; 201) by welding, adhesive or heat shrinking. 6. The permanent rotor shaft assembly according to any one of claims 1 to 5, wherein said first and second end shafts (102A, 102B; 202A, 202B) further comprise cylindrical tracks (105A, 105B) for mechanical bearings. 7. The permanent rotor shaft assembly according to any one of claims 1 to 6, wherein said first and second end shafts (102A, 102B; 202A, 202B) further comprise cylindrical stack iron laminations (105A, 105B) for magnetic bearings. 8. The permanent rotor shaft assembly according to claim 6, wherein said cylindrical tracks (105A, 105B) for mechanical bearings are located on a stepped portion (122A, 122B) of said first and second end shafts (102A, 102B; 202A, 202B). 9. The permanent rotor shaft assembly according to claim 7, wherein said cylindrical stack iron laminations (105A, 105B) for magnetic bearings are located on a stepped portion (122A, 122B) of said first and second end shafts (102A, 102B; 202A, 202B). 10. The permanent rotor shaft assembly according to any one of claims 1 to 9, wherein a central shoulder head (203A, 203B) is provided in each of said first and second end shafts (202A, 202B), in its portion facing said cylindrical core (201), a mating central recess (206A, 206B) is provided in each of the central portions of the front faces of said cylindrical core (201), and said central shoulder heads (203A, 203B) are respectively mounted in said mating central recesses (206A, 206B). 11. A rotary high speed electrical machine having tip speeds up to 300 m/s, characterized in that it comprises a permanent rotor shaft assembly according to any one of claims 1 to 10.

2854258

Permanent magnet rotor shaft assembly and method

Based on the following detailed description of an invention, generate the patent claims. There should be 4 claims in total. The first, independent claim is given and the remaining 3 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will be described in connection with preferred embodiments which are given by way of examples. A typical arrangement of a first embodiment of the invention is illustrated in Figure 1 which shows a permanent rotor shaft assembly 100 for an electrical machine, more specifically for high speed applications which can reach tip speeds up to 300 m/s. The assembly 100 comprises a permanent magnet cylindrical core 101 having a longitudinal axis X-X'. The cylindrical core 101 is axially compressed by first and second end shafts 102A, 102B and is radially compressed by a sleeve 104 made of a non-magnetic high strength metal. The set of elements 101, 102A and 102B forms the overall rotor shaft. According to the invention one (102A) of the first and second end shafts 102A, 102B comprises, in its portion facing the cylindrical core 101, a central shoulder head 103A which cooperates with a mating central recess 106A made in a central portion of a front face of the cylindrical core 101. The shoulder head 103A insures the concentricity of the elements 101 and 102A during the assembly process and provides support for the cylindrical magnet core 101, whilst introducing additional stiffness to the set of assembled elements 101, 102A and 102B once the mounting process is achieved. The permanent magnet cylindrical core 101 comprises rare earth magnets such as NdFeBr or Sm2Co17. The sleeve 104 is made of a non-magnetic high strength metal which may be advantageously chosen among Inconel, Hastelloy, Ti-6%Al-6%V-2%Sn, Ti-2.5%Cu. The magnetization direction of the magnet 101 may be radial, diametral or constituted by a Halbach magnetization. The polarity of the magnets of the core 101 can be 2 poles or 4 poles. The central shoulder head 103A is inserted in the mating central recess by tight fit assembly, slip joint assembly or glued assembly. The first and second end shafts 102A, 102B and the sleeve 104 are fixed on the permanent magnet cylindrical core 101 by welding, adhesive or heat shrinking. The sleeve 104 constitutes a hoop which radially compresses the permanent magnet cylindrical core 101 and the first and second end shafts 102A, 102B. The first and second end shafts 102A, 102B axially compress the permanent magnet cylindrical core 101. According to a specific embodiment, the first and second end shafts 102A, 102B further comprise cylindrical tracks 105A, 105B for mechanical bearings. The reference numerals 105A, 105B may also alternatively represent cylindrical stack iron laminations for magnetic bearings. Such cylindrical stack iron laminations may be made on the first and second end shafts 102A, 102B as an alternative for cylindrical tracks for mechanical bearings, but the first and second end shafts 102A, 102B may also comprise simultaneously in a not shown embodiment a combination of both cylindrical tracks for mechanical bearings (such as auxiliary bearings associated with magnetic bearings) and cylindrical stack iron laminations for magnetic bearings. The tracks for mechanical bearings and/or the stack iron laminations for magnetic bearings may be located on a stepped portion 122A, 122B of the first and second end shafts 102A, 102B. Actually the elements 105A, 105B may be located at different levels (different area or different shoulder) of the end shafts according to the needs. Figs 2 and 3 illustrate a second embodiment of the invention which relates to a permanent rotor shaft assembly 200 for an electrical machine, more specifically for high speed applications which can reach tip speeds up to 300 m/s. The permanent rotor shaft assembly 200 comprises a permanent magnet cylindrical core 201 having a longitudinal axis X-X'. The cylindrical core 201 is axially compressed by first and second end shafts 202A, 202B and is radially compressed by a sleeve 204 made of a non-magnetic high strength metal. The set of elements 201, 202A and 202B forms the overall rotor shaft in a manner similar to the overall rotor shaft of the assembly 100 of the first embodiment. However in the permanent rotor shaft assembly 200 according to the second embodiment of Figs 2 and 3, a central shoulder head 203A, 203B is provided in each of the first and second end shafts 202A, 202B, in its portion facing the cylindrical core 201, a mating central recess 206A, 206B is provided in each of the central portions of the front faces of the cylindrical core 201, and the central shoulder heads 203A, 203B are respectively mounted in the mating central recesses 206A, 206B. Such arrangement of the second embodiment is otherwise similar to the first embodiment and the same materials, assembly means and optional features such as the additional tracks or stack iron laminations 105A, 105B of Figure 1 may also be applied to the embodiment of Figure 2. The assembly 200 of Figure 2 nevertheless constitutes a best mode of implementation of the invention and ensures an easy concentric alignment of the elements 202A, 201, 202B, whilst inserting the sleeve 204 and confers an enhanced stiffness on the set of elements once assembled. The invention further relates to a method for making a permanent rotor shaft assembly 100 or 200 for an electrical machine, comprising the steps of: - forming a permanent magnet cylindrical core 101 respectively 201 having a longitudinal axis X-X', - bonding a first end shaft 102A respectively 202A onto one end of the permanent magnet cylindrical core 101 respectively 201, - bonding a second end shaft 102B respectively 202B onto the other end of the permanent magnet cylindrical core 101 respectively 201, - installing a sleeve 104 respectively 204 made of a non-magnetic high strength metal in interference fit fashion around the permanent magnet cylindrical core 101 respectively 201 and the portions of the first and second end shafts 102A, 102B respectively 202A, 202B adjacent to the permanent magnet cylindrical core 101 respectively 201, so that the cylindrical core 101 respectively 201 be axially compressed by the first and second end shafts 102A, 102B respectively 202A, 202B and be radially compressed by the sleeve 104 respectively 204. More specifically, the method according to the invention further comprises the steps of: - providing at least one central shoulder head 103A respectively 203A, 203B in the first and second end shafts 102A, 102B respectively 202A, 202B, in its portion facing the cylindrical core 101 respectively 201, - providing in a central portion of a front face of the cylindrical core 101 respectively 201, at least one mating central recess 106A respectively 206A, 206B, which is adapted to cooperate with the at least one central shoulder head 103A respectively 203A, 203B, and - mounting the at least one central shoulder head 103A respectively 203A, 203B in the at least one mating central recess 106A respectively 206A, 206B, before inserting the sleeve 104 respectively 204 made of a non-magnetic high strength metal in interference fit fashion around the permanent magnet cylindrical core 101 respectively 201 and the portions of the first and second end shafts 102A, 102B respectively 202A, 202B adjacent to the permanent magnet cylindrical core 101 respectively 201. In the preferred embodiment illustrated in Figs 2 and 3, a central shoulder head 203A, 203B is provided in each of the first and second end shafts 202A, 202B, in its portion facing the cylindrical core 201, a mating central recess 206A, 206B is provided in each of the central portions of the front faces of the cylindrical core 201, and the central shoulder heads 203A, 203B are respectively mounted in the mating central recesses 206A, 206B, before inserting the sleeve 204 made of a non-magnetic high strength metal in interference fit fashion around the permanent magnet cylindrical core 201 and the portions of the first and second end shafts 202A, 202B adjacent to the permanent magnet cylindrical core 201. The central shoulder head 103A, 203A or 203B is inserted in a corresponding mating central recess 106A, 206A or 206B preferably by tight fit assembly, slip joint assembly or glued assembly. The first and second end shafts 102A, 102B respectively 202A, 202B and the sleeve 104 respectively 204 are preferably fixed to the permanent magnet cylindrical core 101 respectively 201 by welding, adhesive or heat shrinking. Generally speaking, the invention provides a simplification in the manufacturing process, increases performance and reduces cost.

12. A method for making a permanent rotor shaft assembly for an electrical machine, comprising the steps of: forming a permanent magnet cylindrical core (101; 201) having a longitudinal axis, bonding a first end shaft (102A; 202A) onto one end of said permanent magnet cylindrical core (101; 201), bonding a second end shaft (102B; 202B) onto the other end of said permanent magnet cylindrical core (101; 201), installing a sleeve (104; 204) made of a non-magnetic high strength metal in interference fit fashion around said permanent magnet cylindrical core (101; 201) and the portions of said first and second end shafts (102A, 102B; 202A, 202B) adjacent to said permanent magnet cylindrical core (101; 201), so that said cylindrical core (101; 201) be axially compressed by said first and second end shafts (102A, 102B; 202A, 202B) and be radially compressed by said sleeve (104; 204), characterized in that it further comprises the steps of: providing at least one central shoulder head (103A; 203A, 203B) in said first and second end shafts (102A, 102B; 202A, 202B), in its portion facing said cylindrical core (101; 201), providing in a central portion of a front face of said cylindrical core (101; 201), at least one mating central recess (106A; 206A, 206B), which is adapted to cooperate with said at least one central shoulder head (103A; 203A, 203B), and mounting said at least one central shoulder head (103A; 203A, 203B) in said at least one mating central recess (106A; 206A, 206B), before inserting said sleeve (104; 204) made of a non-magnetic high strength metal in interference fit fashion around said permanent magnet cylindrical core (101; 201) and the portions of said first and second end shafts (102A, 102B; 202A, 202B) adjacent to said permanent magnet cylindrical core (101; 201).

13. The method according to claim 12, wherein a central shoulder head (203A, 203B) is provided in each of said first and second end shafts (202A, 202B), in its portion facing said cylindrical core (201), a mating central recess (206A, 206B) is provided in each of the central portions of the front faces of said cylindrical core (201), and said central shoulder heads (203A, 203B) are respectively mounted in said mating central recesses (206A, 206B), before inserting said sleeve (204) made of a non-magnetic high strength metal in interference fit fashion around said permanent magnet cylindrical core (201) and the portions of said first and second end shafts (202A, 202B) adjacent to said permanent magnet cylindrical core (201). 14. The method according to claim 12 or claim 13, wherein said central shoulder head (203A, 203B) is inserted in a mating central recess (206A, 206B) by tight fit assembly, slip joint assembly or glued assembly. 15. The method according to any one of claims 12 to 14, wherein said first and second end shafts (102A, 102B; 202A, 202B) and said sleeve (104; 204) are fixed to said permanent magnet cylindrical core (101; 201) by welding, adhesive or heat shrinking.

2863079

Radial magnetic bearing and method of manufacture

Based on the following detailed description of an invention, generate the patent claims. There should be 14 claims in total. The first, independent claim is given and the remaining 13 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will be described in connection with preferred embodiments which are given by way of examples. A typical arrangement of a first embodiment of the invention is illustrated in Figure 1 which shows a quadrant of a radial magnetic bearing according to the invention, comprising an inner rotor 101 having an axis of rotation and including a central shaft 110 having an outer periphery. A ferromagnetic armature 111 which may be made of a stack of high quality magnetic laminations, such as stainless ferromagnetic iron, ferritic steel or silicon iron, is mounted on the outer periphery of the shaft 110. An outer stator 102 comprises a plurality of electromagnets including poles 121 made of ferromagnetic or stainless ferromagnetic material which project radially inwardly towards the rotor 101, whilst leaving air-gaps (e) between end faces of the poles 121 and the ferromagnetic armature 111, and coils 122 wound around the poles 121. A first end face of a pole 121 is thus opposite the ferromagnetic armature of the rotor 101 and defines the air-gap e. Another end of a pole 121 is extended through an outer portion 123 which is secured to a supporting member 127. Each pole 121 and its corresponding outer portion 123 are included in an angularly segmented module 120A or 120B comprising a stack of laminations made of ferromagnetic material. The outer portion 123 defines shoulders 125 with respect to the corresponding pole 121, thus providing free spaces on each side of the pole 121. The outer portion 123 of a segmented module 120A or 120B contacts outer portions 123 of neighboring segmented modules 120A or 120B essentially without air-gap and without insulating separation. However in practice an air-gap of very small value, such as for example an air-gap of 0.1 mm, may be tolerated between the outer portions 123 of two neighboring segmented modules. The outer portions 123 of all segmented modules 120A, 120B are assembled by clamping rings 127, 128. The coils 122 which are located in free spaces around the poles 121 are mounted in a string. As shown in Figure 1, each outer portion 123 of each segmented module 120A, 120B advantageously comprises rounded outer corners 126. Such rounded corners remove magnetic singularities and facilitate the assembly of the segmented modules 120A, 120B. Figure2 shows the magnetic flux lines in an embodiment such as the embodiment described in connection with Figure 1. As shown in Figures 1 to 8, each outer portion 123 of each segmented module 120A, 120B or 120 comprises a central hole 124 provided in the stack of laminations for mounting purposes. An example of mounting method of the radial bearing of Figure 1 will be described in connection with Figures 6 to 8. A first clamping ring 127 has a plurality of holes 134 designed to be registered with the central holes 124 of the segmented modules 120, 120A, 120B and a second clamping ring 128 has a plurality of guides 129 such as studs or spindles designed for receiving the central holes of the segmented modules 120, 120A, 120B and the plurality of holes 134 of the first clamping ring 127. Thus a method for making a radial magnetic bearing according to the invention essentially comprises the steps of: - forming a plurality of angularly segmented modules 120, 120A, 120B, each comprising a pole 121 and an outer portion 123 made of a stack of laminations made of ferromagnetic material, the outer portion 123 defining shoulders 125 with respect to the pole 121, - forming first and second clamping rings 127, 128, - forming a plurality of coils 122 connected in a string, the number of coils 122 being equal to the number of poles 121, - arranging the angularly segmented modules 120, 120A, 120B in such a manner that each outer portion 123 contacts outer portions 123 of neighboring segmented modules 120, 120A, 120B essentially without air-gap and without insulating separation, free spaces being defined between the poles 121 of adjacent segmented modules 120, 120A, 120B, - assembling the angularly segmented modules 120, 120A, 120B together with the first and second clamping rings 127, 128, and - inserting the plurality of coils 122 interconnected in a string in the free spaces around the plurality of poles 121 of the segmented modules 120, 120A, 120B. As already mentioned, in practice an air-gap of very small value, such as for example an air-gap of 0.1 mm, may be tolerated between the outer portions 123 of two neighboring segmented modules 120, 120A, 120B. More specifically, the step of assembling the angularly segmented modules 120, 120A, 120B comprises inserting a plurality of guides 129 of the second clamping ring 128 into central holes 124 of the segmented modules 120, 120A, 120B and a plurality of holes 134 of the first clamping ring 127. Generally speaking, the shape and size of the angularly segmented modules 120, 120A, 120B are chosen to optimize the radial load capacity whilst enabling serial production. Due to the provision of wound segmented modules 120, 120A, 120B, it is possible to define the right shape aiming at obtaining optimum carrying capacity, while easily integrating the coils in this type of magnetic bearing module and therefore allowing for serial production. Moreover since the mounting of the coils 122 is achieved through a string of coils, the number of interconnections is reduced. Finally, the provision of first and second clamping rings 127, 128 with the cooperation of holes and studs or other guiding means enables to precisely assemble the segmented modules in adjacent contacting positions, without any insulating separation or air-gap. The segmented modules 120, 120A, 120B and clamping rings 127, 128 are radially and axially locked in a final step of assembly. The system of angularly segmented modules according to the invention is applicable to all types of radial active magnetic bearings and all types of magnetic materials. A specific example of coils 122 and of modules 120 comprising stacked laminations for forming a pole 121 and an outer portion 123, together with a central hole 124 and rounded corners 126 being formed in the outer portion 123 is illustrated in Figure 7. According to a specific embodiment, all angularly segmented modules 120 have the same shape and size, thus facilitating the manufacturing process (see e.g. Figure 8 ). However, it is also possible that the angularly segmented modules 120A, 120B have the same radial size but have different sizes in a peripheral direction of the angularly segmented modules 120A, 120B. Different types of modules of different shapes could thus be integrated in the stator 102 of a radial magnetic bearing to optimize the load capacity. For example it is possible to design two types of segmented modules 120A, 120B, as illustrated in Figs 1 to 5. In the embodiments of Figs 1 to 5, the poles 121 comprise a first set of pairs of angularly segmented modules 120A having poles 121 of reduced width, which e.g. may be arranged along orthogonal directions X'-X and Y'-Y and a second set of angularly segmented modules 120B having poles 121 of larger width, which are interposed between the pairs of poles 121 of reduced width of the first set of angularly segmented modules 120A. For example, the number of pairs of poles 121 of reduced width of the first set of angularly segmented modules 120A may be equal to four, whereas the number of the poles 121 of larger width of the second set of angularly segmented modules 120B, which are interposed between the pairs of poles 121 of reduced width, may be equal to 1 (see fig. 5 ), 2 (see Figures 1 to 3 ) or 3 (see Figure 4 ). Thus according to specific embodiments of the invention the total number of angularly segmented modules 120, 120A, 120B and of the corresponding poles 121 may be equal to 12, 16 or 20, but other numbers of segmented modules 120 or 120A, 120B are possible. Generally speaking, the invention provides a simplification in the manufacturing process, increases performance and reduces cost. The following non limiting list of advantages is linked with the implementation of the invention: - Optimization of the radial load capacity of the order of 30% with respect to a standard design; - Decrease of the length by 30% to 40% for the same load capacity of a conventional version of radial magnetic bearing; - Drastic reduction of the number of interconnections and failures due to the winding in rosary ( i.e. arrangement of a string of coils), thus also leading to a cost reduction; - Ease of assembly and disassembly of the radial magnetic bearing comprising a stator with wound modules; - Adaptation to all magnetic materials; - Adaptation to all models and types of radial magnetic bearings; - Ability to automate the assembly of coils and modules; - Possibility of assembling the modules by tight rings or shrunk can; - Possibility of easily integrating additional sensors such as thermal sensors.

1. A radial magnetic bearing, comprising an inner rotor (101) having an axis of rotation and including a central shaft (110) having an outer periphery and a ferromagnetic armature (111) mounted on said shaft (110) on said outer periphery; and an outer stator (102) comprising a plurality of electromagnets including poles (121) made of ferromagnetic or stainless ferromagnetic material which project radially inwardly towards said rotor (101), whilst leaving air-gaps (e) between end faces of said poles (121) and said ferromagnetic armature (111), and coils (122) wound around said poles (121), said poles (121) being extended through outer portions (123) which are attached to a supporting member (127), characterized in that each pole (121) and said corresponding outer portion (123) are included in an angularly segmented module (120, 120A, 120B) comprising a stack of laminations made of ferromagnetic or stainless ferromagnetic material, said outer portion (123) defining shoulders (125) with respect to said pole (121), said outer portion (123) contacting outer portions (123) of neighboring segmented modules (120, 120A, 120B) and the outer portions (123) of all segmented modules (120, 120A, 120B) being assembled by clamping rings (127, 128), whereas said coils (122) located in free spaces around said poles (121) are mounted in a string.

2. The radial magnetic bearing according to claim 1, wherein each outer portion (123) of each segmented module (120, 120A, 120B) comprises rounded outer corners (126). 3. The radial magnetic bearing according to claim 1 or claim 2, wherein each outer portion (123) of each segmented module (120, 120A, 120B) comprises a central hole (124) provided in the stack of laminations for mounting purposes. 4. The radial magnetic bearing according to claim 3, wherein said clamping rings comprise a first clamping ring (127) having a plurality of holes (134) designed to be registered with said central holes (124) of said segmented modules (120, 120A, 120B) and a second clamping ring (128) having a plurality of guides (129) designed for receiving said central holes (124) of said segmented modules (120, 120A, 120B) and said plurality of holes (134) of said first clamping ring (127). 5. The radial magnetic bearing according to any one of claims 1 to 4, wherein said angularly segmented modules (120) all have the same shape. 6. The radial magnetic bearing according to any one of claims 1 to 4, wherein said angularly segmented modules (120A, 120B) have the same radial size but have different sizes in a peripheral direction of the angularly segmented modules (120A, 120B). 7. The radial magnetic bearing according to any one of claims 1 to 4, wherein said poles (121) of said angularly segmented modules comprise a first number of pairs of poles (121) of reduced width of a first set of angularly segmented modules (120A) and a second number of poles (121) of larger width of a second set of angularly segmented modules (120B) which are interposed between said pairs of poles (120A) of reduced width. 8. The radial magnetic bearing according to any one of claims 1 to 7, wherein the number of said angularly segmented modules (120, 120A, 120B) and of the corresponding poles (121) is equal to 12, 16 or 20. 9. The radial magnetic bearing according to claim 7, wherein the number of pairs of poles (121) of reduced width of said first set of angularly segmented modules (120A) is equal to four and the number of the poles (121) of larger width of said second set of angularly segmented modules (120B) which are interposed between said pairs of poles (121) of reduced width is equal to 1, 2 or 3. 10. The radial magnetic bearing according to any one of claims 1 to 9, wherein said ferromagnetic armature (111) of said inner rotor (101) is made of a stack of high quality magnetic laminations. 11. A method for making a radial magnetic bearing according to claim 1, comprising the steps of: forming a plurality of angularly segmented modules (120, 120A, 120B) each comprising a pole (121) and an outer portion (123) made of a stack of laminations made of ferromagnetic or stainless ferromagnetic material, said outer portion (123) defining shoulders (125) with respect to said pole (121), forming first and second clamping rings (127, 128), forming a plurality of coils (122) connected in a string, the number of said coils (122) being equal to the number of said poles (121), arranging said angularly segmented modules (120, 120A, 120B) in such a manner that each said outer portion (123) contacts outer portions (123) of neighboring segmented modules (120, 120A, 120B), free spaces being defined between the poles (121) of adjacent segmented modules (120, 120A, 120B), assembling said angularly segmented modules (120, 120A, 120B) together with said first and second clamping rings (127, 128), and inserting said plurality of coils (122) interconnected in a string in said free spaces around said plurality of poles (121) of said segmented modules (120, 120A, 120B). 12. The method according to claim 11, wherein said step of assembling said angularly segmented modules (120, 120A, 120B) comprises inserting a plurality of guides (129) of said second clamping ring (128) into central holes (124) of said segmented modules (120, 120A, 120B) and a plurality of holes (134) of said first clamping ring (127). 13. The method according to claim 11 or claim 12, wherein the shape and size of the angularly segmented modules (120A, 120B) are chosen to optimize the radial load capacity and to enable serial production. 14. The method according to any one of claims 11 to 13, wherein the poles (121) comprise a first number of pairs of poles (120A) of reduced width and a second number of poles (120B) of larger width which are interposed between said pairs of poles (120A) of reduced width.

2879278

Versatile cooling housing for an electrical motor

Based on the following detailed description of an invention, generate the patent claims. There should be 4 claims in total. The first, independent claim is given and the remaining 3 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 is a longitudinal section view schematically illustrating one embodiment of an electrical device such as a motor having an outer housing which allows liquid cooling according to the invention. Basically, an electrical motor 10 comprises a rotatable shaft 12 a part of which forms a rotor 14 having at least a magnetic portion surrounded by a stator 16. The rotatable shaft is supported at each end by bearings 18A, 18B, for example rolling bearing as illustrated or magnetic bearings. The stator is disposed within an outer housing 20 of the motor and comprises a laminated magnetic stack 16A surrounded by a windings 16B and disposed along a periphery of the rotor to define an annular air gap therebetween. More particularly, the laminated magnetic stack abuts against a central portion of the outer housing 20 which also extends on either side to enclose the other components of the motor. Furthermore, transverse walls 22A, 22B close the outer housing on each side of the rotatable shaft and also form internal supports for the bearings. According to the invention, the outer housing 20 which has an interior surface 20A configured in its central portion to interface with the laminated magnetic stack 16A of the electrical motor comprises in said central portion an exterior surface 20B having not constant cooling fins 24. More particularly, the cooling fins have alternatively high and small height, all the high cooling fins having a same height and all the small cooling fins having the same height. A cover plate 26 is affixed to the outer housing 20 by fixing means 28 such as bolts or screws and seals 30 are fitted between the cover plate and the outer housing for isolating the liquid cool-ing. By resting on the higher cooling fins, the cover plate creates a cooling path (as illustrated by the arrows) between higher and smaller cooling fins from an inlet hole 26A (receiving the liquid cooling from an inlet manifold not shown) to an outlet hole 26B (delivering the liquid cooling to an outlet manifold not shown), all pierced in the cover plate. For creating this cooling path, alternatively higher and smaller cooling fins on the inlet manifold are in opposition on the outlet manifold. The outer housing with its cooling fins is preferably realised by sand casting (it means that the internal cooling system is leak free and the surface roughness is well adapted for heat exchanges). The operation of an electrical motor is known and will not be explained in detail. Classically, during operation rotor 14 rotates with rotatable shaft 12 within stator 16, so that the annular air gap is maintained between the two components to form part of a closed magnetic flux path. An excitation current in the windings creates a magnetic force to drive the magnetic flux which attracts rotor 14 toward the stator 16, according to well-known principles of magnetism, and tends thus to urge the rotor to create a working torque output. The cooling is processed during the operation of the motor. An inlet manifold drives the liquid cooling flow from a liquid entry pipe (not shown) into the outer housing via the inlet hole 26A. This flow of liquid cooling circulates around the electrical motor and leaves by the outlet hole 26B in the outlet manifold. Figure 2 shows another embodiment of an electrical motor having an outer housing according to the invention which allows gas cooling. The different components of the electrical motors are the same and so not described one more time. They naturally have the same references. The outer housing (inlet and outlet) for the gas or liquid cooling are the same too. The only difference concerns the manifolds which are specific for gas and liquid cooling. More particularly, the cover plate 20 of the liquid cooling system is not present in the gas cooling system and the outer housing is directly connected with the inlet and the outlet manifolds 32. As illustrated, the inlet manifold drives the gas cooling flow from blower (for example but not shown) to the outer housing, circulates around the motor and leaves by the outlet manifold. This structure realizes a leak free mechanical interface between the gas blower and the housing of the motor as that realized between the liquid entry pipe and the housing in the liquid cooling system. With the invention, a common design is possible for several level of power of the electrical motor (no redesign of the outer housing is required except the two manifolds of the cooling device). Such versatile configuration allows easily changing the cooling media (air/water) and subsequently the reachable power of the motor. Although preferred embodiments have been shown and described, it should be understood that any changes and modifications may be made therein without departing from the scope of the invention. More particularly, if the invention has been described through an electrical motor, any other electrical device (including generators, starters, alternators, etc.) with stator laminations that interface with the disclosed versatile housing is conceivable.

1. A housing (20) for an electrical device comprising an interior surface (20A) configured to interface in a central portion with a laminated magnetic stack (16A) of the electrical device and an exterior surface (20B) comprising in said central portion cooling fins (24), wherein said cooling fins are alternatively higher and smaller on an inlet manifold and in opposition on an outlet manifold.

2. The housing of claim 1, comprising a cover plate (26) having an inlet hole (26A) and an outlet hole (26B) and which rests on said higher cooling fins in order to create a liquid cooling path between higher and smaller cooling fins from said inlet hole to said outlet hole. 3. The housing of claim 2, wherein said cover plate is affixed to the housing by fixing means (28) and seals (30) are fitted between said cover plate and the housing for isolating the liquid cooling. 4. The housing of claim 1 or claim 2, wherein said cooling fins are realised by sand casting such that the surface roughness of said exterior surface is well adapted for heat exchanges.

2879278

Versatile cooling housing for an electrical motor

Based on the following detailed description of an invention, generate the patent claims. There should be 4 claims in total. The first, independent claim is given and the remaining 3 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 is a longitudinal section view schematically illustrating one embodiment of an electrical device such as a motor having an outer housing which allows liquid cooling according to the invention. Basically, an electrical motor 10 comprises a rotatable shaft 12 a part of which forms a rotor 14 having at least a magnetic portion surrounded by a stator 16. The rotatable shaft is supported at each end by bearings 18A, 18B, for example rolling bearing as illustrated or magnetic bearings. The stator is disposed within an outer housing 20 of the motor and comprises a laminated magnetic stack 16A surrounded by a windings 16B and disposed along a periphery of the rotor to define an annular air gap therebetween. More particularly, the laminated magnetic stack abuts against a central portion of the outer housing 20 which also extends on either side to enclose the other components of the motor. Furthermore, transverse walls 22A, 22B close the outer housing on each side of the rotatable shaft and also form internal supports for the bearings. According to the invention, the outer housing 20 which has an interior surface 20A configured in its central portion to interface with the laminated magnetic stack 16A of the electrical motor comprises in said central portion an exterior surface 20B having not constant cooling fins 24. More particularly, the cooling fins have alternatively high and small height, all the high cooling fins having a same height and all the small cooling fins having the same height. A cover plate 26 is affixed to the outer housing 20 by fixing means 28 such as bolts or screws and seals 30 are fitted between the cover plate and the outer housing for isolating the liquid cool-ing. By resting on the higher cooling fins, the cover plate creates a cooling path (as illustrated by the arrows) between higher and smaller cooling fins from an inlet hole 26A (receiving the liquid cooling from an inlet manifold not shown) to an outlet hole 26B (delivering the liquid cooling to an outlet manifold not shown), all pierced in the cover plate. For creating this cooling path, alternatively higher and smaller cooling fins on the inlet manifold are in opposition on the outlet manifold. The outer housing with its cooling fins is preferably realised by sand casting (it means that the internal cooling system is leak free and the surface roughness is well adapted for heat exchanges). The operation of an electrical motor is known and will not be explained in detail. Classically, during operation rotor 14 rotates with rotatable shaft 12 within stator 16, so that the annular air gap is maintained between the two components to form part of a closed magnetic flux path. An excitation current in the windings creates a magnetic force to drive the magnetic flux which attracts rotor 14 toward the stator 16, according to well-known principles of magnetism, and tends thus to urge the rotor to create a working torque output. The cooling is processed during the operation of the motor. An inlet manifold drives the liquid cooling flow from a liquid entry pipe (not shown) into the outer housing via the inlet hole 26A. This flow of liquid cooling circulates around the electrical motor and leaves by the outlet hole 26B in the outlet manifold. Figure 2 shows another embodiment of an electrical motor having an outer housing according to the invention which allows gas cooling. The different components of the electrical motors are the same and so not described one more time. They naturally have the same references. The outer housing (inlet and outlet) for the gas or liquid cooling are the same too. The only difference concerns the manifolds which are specific for gas and liquid cooling. More particularly, the cover plate 20 of the liquid cooling system is not present in the gas cooling system and the outer housing is directly connected with the inlet and the outlet manifolds 32. As illustrated, the inlet manifold drives the gas cooling flow from blower (for example but not shown) to the outer housing, circulates around the motor and leaves by the outlet manifold. This structure realizes a leak free mechanical interface between the gas blower and the housing of the motor as that realized between the liquid entry pipe and the housing in the liquid cooling system. With the invention, a common design is possible for several level of power of the electrical motor (no redesign of the outer housing is required except the two manifolds of the cooling device). Such versatile configuration allows easily changing the cooling media (air/water) and subsequently the reachable power of the motor. Although preferred embodiments have been shown and described, it should be understood that any changes and modifications may be made therein without departing from the scope of the invention. More particularly, if the invention has been described through an electrical motor, any other electrical device (including generators, starters, alternators, etc.) with stator laminations that interface with the disclosed versatile housing is conceivable.

5. A electrical device comprising a housing (20) having cooling fins (24) located in a central portion along an exterior surface (20B) of said housing and a laminated magnetic stack (16A) disposed within said housing and interfacing with an interior surface (20A) of said housing at said central portion, wherein said cooling fins are alternatively higher and smaller on an inlet manifold and in opposition on an outlet manifold.

6. The electrical device of claim 5, wherein the housing comprises a cover plate (26) having an inlet hole (26A) and an outlet hole (26B) and which rests on said higher cooling fins in order to create a liquid cooling path between higher and smaller cooling fins from said inlet hole to said outlet hole. 7. The electrical device of claim 5, wherein the housing is directly connected with inlet and outlet manifolds (32) for creating a gas cooling flow. 8. The electrical device of claim 5, comprising one of the following devices: a motor, a generator, a starter, an alternator.

2884368

An apparatus for moving a fluid

Based on the following detailed description of an invention, generate the patent claims. There should be 9 claims in total. The first, independent claim is given and the remaining 8 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Before describing the various embodiments of the disclosure, a brief description of an exemplary known oscillation blade fan, in this example being a piezoelectric fan, is provided with reference to figure 1. It is to be noted that the present description of a known piezoelectric fan is provided only to help facilitating a better understanding of the present disclosure and is not to be construed as being limited to only the described aspects. Typically a piezoelectric fan 100 is made of a piezoelectric element 110 comprising a body of a solid material having the property of accumulating electrical charge when a mechanical stress such as a pressure is applied thereupon. Conversely, such piezoelectric body may exhibit a mechanical movement in response to an electric current applied thereto. Some examples of materials exhibiting piezoelectric property are certain crystals or ceramics. A piezoelectric fan further comprises a planar, typically thin, body 120 (sometimes referred to as blade or cantilever). One end 121 of the planar body 120 is attached, e.g. bonded, to the piezoelectric element 110 and the other end 122 of the body is free and movable. When an alternating electric current is applied to the piezoelectric element 110, the latter exhibits a mechanical movement, causing the opposite free end 122 of the planar body 120 to move in an oscillating pattern which is represented in the figure by dashed lines 120-a and 120-b. The oscillation of the free end 122 of the planar body generates an airflow in a similar manner as a conventional hand fan. The piezoelectric element 110 is typically coupled to a coupling which includes electrical connections used for conveying an alternating current to the piezoelectric element. Although piezoelectric fans have advantages over the conventional rotary or radial fans, for example due their better reliability, they still suffer from certain shortcomings. One such shortcoming is that a conventional piezoelectric fan is typically only capable of generating airflows in the order of 10 liters/min with local velocities of about 1.5m/s. These performance parameters may not be sufficient for applications where relatively compact circuit packs are to be cooled, especially where such compact circuit packs are designed to process large volumes of data. Similar considerations may be given to known oscillation blade fans using electromagnetic drivers in terms of possible insufficiency of their performance parameters for certain applications. Figure 2 illustrates an exemplary schematic representation of some structural aspects of an oscillation blade fan according to some embodiments. In this nonlimiting example, the fan uses a piezoelectric material as a driver for the fan blade as will be described below, however other drives, such as for example electromagnetic drivers may likewise be used and are to be considered within the scope of the present disclosure. In figure 2, like elements have been provided with like reference numerals as those of figure 1. The piezoelectric fan 100 of figure 2 comprises a driver 110 of piezoelectric material and a planar body 120. The planar body comprises a flat and thin sheet 127. One end 121 of the planar body 120 is attached, e.g. bonded, to the driver 110 and the other end 122 of the body is free and movable. When an external excitation, such as an alternating electric current is applied to the piezoelectric element of driver 110, the latter exhibits a mechanical movement, causing the opposite free end 122 of the planar body 120 to move in an oscillating pattern. The oscillation of the free end 122 of the planar body generates an airflow. The flat sheet 127 of the planar body has at least two lateral sides 123 and 124 where each of the two lateral sides has a respective first end 123-a, 124-a, connected to the driver 110 and a respective second end 123-b,124-b, opposite to the respective first end, which is free and moveable. According to embodiments of the present disclosure the two lateral sides 123 and 124 diverge from each other in a direction moving away from the driver 110. As shown in the figure, such direction of movement is from the respective first ends 123-a, 124-a to the respective second ends 123-b, 124-b respectively. The direction from the respective first ends to the respective second ends is shown in figure 2 by arrow A and the divergence effect is represented in the figure by divergent arrows B and C. In the example of figure 2, the planar body is shown to have a generally triangular shape. However, this is only exemplary and other suitable geometries may also be used for the planar body 120. Figures 3A, 3B, 3C and 3D, illustrate embodiments implementing some of such alternative geometries for the planar body. In particular, the lateral sides 123, 124 and the free end 122 may have linear shapes such as the embodiment of figure 3A, curved shapes such as the embodiment of figure 3B or a combination of curved and linear shapes. Furthermore, each of the two lateral sides may have multiple linear segments. For example, the planar body 120 of figure 3C is shown to have lateral sides 123 and 124 where the lateral side 123 may comprise a first linear segment 123-1 and a second linear segment 123-2 and the lateral side 124 may comprise a first linear segment 124-1 and a second linear segment 124-2. Similarly (although not shown in the figures) each of the two lateral sides may have multiple curved shapes. For example, each of the lateral sides of the planar body may comprise a first curved portion and a second curved portion. Still further, the lateral sides having multiple linear segments may diverge from the first end substantially at 180 degrees. For example, the planar body 120 of figure 3D is shown to have lateral sides 123, 124 with linear segments123-1, 123-2 and 124-1 and 124-2 respectively, wherein the linear segments 123-1 and 123-2 diverge from the first end 121 at an angle which is substantially at 180 degrees. The planar body further comprises rigid structures on the lateral sides of the planar body. Figures 4A and 4B illustrate examples of embodiments in which the planar body of the fan 100 comprises such rigid structures. In figures 4A and 4B like elements have been provided with like reference numerals as those of the previous figures. The fan 100 of figure 4A is in many aspects similar to that of figure2. However, the fan of figure 4A further includes rigid structures 125 and 126 located on the lateral sides 123 and 124 of the planar body respectively. The rigid structures may be used as a supporting frame for the flat sheet 127 which is also a part of the planar body 120. In some embodiments, such as the one shown in figure 4A, individual rigid structures 125 and 126 may be in the form of an elongated linear beam, and at least two elongated beams provide support for the flexible flat sheet. One advantage of using rigid structures on the lateral sides of the planar body is that they may contribute to improving the frequency of oscillation of the planar body as compared to piezoelectric fans which do not have rigid structures on the lateral sides of their planar body. For example, it is expected that using the rigid structures may enable reaching frequencies in the range of about 88Hz which is a significant improvement as compared to the conventional piezoelectric fans which, for the same oscillation amplitude, typically operate at frequencies of about 60Hz. Figure 4B illustrates an alternative shape of the planar body 120 where the planar body also comprises rigid structures 125 and 126 on lateral sides of the planar body which support the flat sheet 127. The characteristics of the fan of figure 4B is in many aspects similar to that of figure 4A and therefore a detailed description thereof is considered not necessary. The main difference between the embodiments of figures 4A and 4B is in the geometrical shape of the respective planar bodies which in the former it is composed of linear lateral sides 123, 124 as well as linear geometry of the free end 122 and in the latter it is composed of curved lateral sides 123, 124 as well as curved geometry of the free end. Similar to the embodiment of figure 4A, the rigid structures 126, 126 may be in the form of an elongated curved beam and at least two elongated curved beams provide support for the flexible flat sheet. Preferably the shape of the planar body may resemble the shape of a fishtail. For example the planar bodies of the embodiments of figures 3A, 3B, 3C, 4A and 4B illustrate fishtail shapes. This may be based on a biomimetic approach for designing the planar bodies which may be very advantageous as it takes advantage of natural shapes of fishtails that have been evolving over millions of years to optimize their efficiency in facilitating the movements of the fish in water. The movement of a fish using its fishtail in water (a fluid) may therefore be resembled to the movement of a planar body of a piezoelectric fan in air (a fluid). In the context of the present disclosure biomimetic may be understood to refer to an approach that mimics the shape and function of a structure that has been biologically produced in the nature. It is therefore considered that designs based on fishtail geometries would improve the performance of the planar body in moving air or other fluids including water. In some embodiments the flat sheet 127 of the planar body 120 is made of a flexible material. This is advantageous because the flexibility of the flat sheet makes it capable of undergoing an elastic deflection. By elastic deflection it is meant to refer to the capability of the flexible flat sheet 127 to deform during the oscillation of the planar body. Figures 5A and 5B illustrate this feature. Figure 5A is an exemplary schematic representation in perspective of a fan having a flexible flat sheet included in the planar body thereof, and figure 5B is a front view of the piezoelectric fan of figure 5A. In these figures like elements have been given like reference numerals as those of the previous figures. It is assumed that in both figures 5A and 5B, the fan 100 is in operation in which the planar body 120 is undergoing an oscillating movement in the direction of arrow O (it is further noted that the entire oscillation of the tip of the planar body may define a curved pattern, however arrow O is intended to show the instantaneous vector at the instant of oscillation shown in the figure, therefore the arrow is shown to be linear). Due to the movement of the planar body in the direction of arrow O and the fact that the flat sheet 127, spanning between the two rigid structures 123 and 124 is flexible, the flat sheet 127 undergoes a deformation which deepens as one moves from the sides of the flat sheet to the center thereof, therefore forming a concave shape on the surface 127-a of the planar body, which is the upper surface of the flat sheet 127 being in the direction of oscillation O as shown in figures 5A and 5B. This deformation constitutes, within the context of the present disclosure, an elastic deflection of the flat sheet 127. As it may be readily observed from the figures 5A and 5B, when the planar body is moving in the direction of arrow O (upward in the figures), the elastic deflection is generated in the opposite direction (downward in the figures). The direction in which the elastic deflection is generated is shown in the figures by arrows D. Such elastic deformation offers a significant advantage as compared to conventional oscillation blade fans in which the planar bodies do not typically undergo such elastic deflection, because it allows the planar body to capture comparatively higher volumes of air within the elastically deformed region as shown under the arrow D in figures 5A and 5B, thereby moving a larger volume of air toward the electronic components to be cooled. The material of flexible flat sheet may be of any known type available on the market. One example of such material may be latex. For the sake of clarity of description it is noted that the term rigid, as referred to the structures supporting the flat sheet is to be understood as a structure having less flexibility as compared to the flat and flexible sheet used in the planar body. Although rigidity and flexibility are both relative properties, it is noted that within the context of the present disclosure, a person of ordinary skill in the art will be able to select the desired level of rigidity for the rigid structures in view of the level of flexibility selected for the flexible flat sheet for each specific design such that an optimum fluid movement is obtained. It is expected that oscillation blade fans constructed according to the embodiments of the disclosure may present improved performance in air moving efficiency from typical peak velocities in the range of 1.5m/s for conventional piezoelectric fans to peak velocities in the range of 5m/s. Although the above exemplary embodiments have been described in relation to a cooling mechanism which uses air as the cooling fluid, the disclosure is not so limited and other fluids, such as for example water, may also be used as cooling fluids within the context of the present disclosure. As mentioned above, the disclosure is not limited to the use of piezoelectric drivers and oscillation blade fans (or cantilever fans) using other known driver mechanisms, such as electromagnetic drivers may likewise be employed within the context of the present disclosure. By way of a non-limiting example, electromagnetic drivers may use electromagnetic force which is applied to the blade, the latter being anchored at one end to a fixed point and free at another. The electromagnetic driver (which may be an electromagnetic coil) may be located at a convenient position away from the body of the blade. By applying an external excitation, such as an alternating current, or by turning the current on and off periodically, a magnetic force is periodically induced in the coil which as a result periodically attracts the blade towards the coil, thereby generating an oscillation movement in the blade. Another non-limiting example of electromagnetic drivers may use an induction device to move a magnet which may be anchored to a blade and thereby cause movement therein. Some embodiments feature an equipment in which the piezoelectric fan according the various embodiments of the disclosure may be implemented. Figure 6 is an exemplary schematic representation of a circuit for such an equipment according to some embodiments. The circuit 200 of figure 6 comprises a circuit board 210 on which a plurality of electronic components 220 are provided. The electronic components are of the type that generates heat during their operation. A plurality of heat sinks 230 is provided configured to passively cool the electronic circuits. As shown in the figure, individual electronic components 220 and individual heat sinks are provided in thermal contact with each other and pairs of electronic component-heat sink are located at various locations on the surface of the board 210 which may be at certain distance with respect to each other. According to embodiments of the disclosure, a plurality of oscillation blade fans 240 are located on the board 210 in such a manner that one or more piezoelectric fans 240 may be located proximate to a respective heat sink and be used to locally cool the respective heat sink (and the electronic component). In figure 6, thee electronic components 220 are shown in thermal contact with three heat sinks 230 and for each pair of component-heat sink, two fans 240 are located proximate thereto. The number of fans used in the figure is only exemplary and of course any suitable number of piezoelectric fans may be used proximate to a component-heat sink pair to meet the requirements of each specific design. This arrangement has important advantages over the arrangements used in known equipment. Indeed the arrangements used in known equipment are typically cooled by forced convection via a bank of fans. The fans may be axial or radial and due to the size of such fans, they are typically located on a side, e.g. the bottom of the board in a vertically positioned board. The airflow therefore moves from the bottom to the top of the board. This configuration often causes difficulty in cooling various components on the circuit packs as the air moving from the bottom to the top becomes progressively heated as it flows over the electronic components and the heat sinks. Therefore the components located further away from the fans (downstream the flow of air) will receive warmer air as compared to those located closer to the fans (upstream the flow o fair). The oscillation blade fans according to the present disclosure may help improve the situation because, on the one hand, due to their reduced size they may be located within the board (as opposed to a side of the board) and proximate to each electronic component - heat sink pair to thereby locally cool such components; and on the other, they may produce larger volumes of airflow due to the specific shape of these fans having a comparatively larger surface for the planar body as compared to known piezofans. The use of a flexible material supported between rigid structures for the planar body enhances still more the performance of the fan, as described above. The use of the fans as featured herein within the surface of the board would not significantly affect the availability of space on the board as the footprint that the fan occupies is very small, and furthermore, various components could easily be positioned below the fan at locations which do not obstruct the oscillating movement of the tip of the fan. Optionally, the fan as proposed herein may be used for generating a local airflow in addition to the use of a remote airflow which may be provided using rotary or axial fans on a side of the board, wherein the local and remote airflows are in the same direction. This option may therefore help increase further the airflow over the entire board. Such a combined airflow would be difficult to achieve with other air moving technologies such as axial/radial fans especially in small and compact devices. Here again, the specific shape of the fan as proposed herein would generate a local increase in airflow which may be significantly greater than what could be generated by a known piezoelectric fan. The various embodiments of the present invention may be combined as long as such combination is compatible and/or complimentary. Further it is to be noted that the list of structures corresponding to the claimed elements is not exhaustive and that one skilled in the art understands that equivalent structures can be substituted for the recited structure without departing from the scope of the invention. It should be appreciated by those skilled in the art that any block diagrams herein represent conceptual views of illustrative circuitry embodying the principles of the invention. Similarly, it will be appreciated that any flow charts, flow diagrams, state transition diagrams, pseudo code, and the like represent various processes which may be substantially represented in computer readable medium and so executed by a computer or processor, whether or not such computer or processor is explicitly shown.

1. An apparatus comprising: - a planar body; - a driver connected to the planar body and configured to generate a motion in the planar body in response to an external excitation; wherein the planar body comprises a flexible flat sheet with a first lateral side and a second lateral side, the first lateral side and the second lateral side diverging from each other in a direction moving away from the planar body; and: wherein the planar body further comprises a plurality of rigid structures wherein a first rigid structure is attached to the first lateral side of the flexible flat sheet and a second rigid structure is attached to the second lateral side of the flexible flat sheet such that the rigid structures provide support for the flexible flat sheet.

2. The apparatus of claim 1, wherein the flexible flat sheet is capable of elastically deflecting during an oscillation of the planar body said elastic deflection being opposite to a direction of oscillation of the planer body and generating a concave shape on the surface of the planar body which is in the direction of oscillation. 3. The apparatus of any one of the preceding claims, wherein a rigid structure is in the form of an elongated beam, and at least two elongated beams provide support for the flexible flat sheet. 4. The apparatus of any one of the preceding claims, wherein a rigid structure is in the form of a curved beam, and at least two curved beams provide support for the flexible flat sheet. 5. The apparatus of any one of the preceding claims wherein a lateral side comprises a multiple of segments and at least one segment on each lateral side is supported by a rigid structure. 6. The apparatus of any one of the previous claims, wherein the planar body has the shape of a fishtail. 7. The apparatus of any one of the preceding claims, wherein the driver comprises a piezoelectric element. 8. The apparatus of any one of the preceding claims 1 to 7, wherein the driver comprises an electromagnetic element. 9. An equipment comprising a plurality of electronic components, a plurality of heat sinks each configured to cool a respective one of the plurality of electronic components, the electronic components and the heat sinks being located on a board, the equipment further comprising a plurality of apparatus as claimed in any one of the claims 1 to 8, wherein a first apparatus is located proximate to a first heat sink and configured to locally cool the first heat sink and a second apparatus is located proximate to a second heat sink and configured to locally cool the second heat sink, and wherein the first heat sink and second heat sink are located at distant locations with respect to each other on the surface of the board.

2887502

Rotor assembly with permanent magnets and method of manufacture

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

The present invention will be described in connection with preferred embodiments which are given by way of examples. A typical arrangement of a first embodiment of the invention is illustrated in Figures 1, 3 and 5. As shown in Figure 1, in order to constitute a permanent magnet rotor assembly having at least two poles, a cylindrically shaped shaft 1 having a longitudinal axis of rotation is prepared. The shaft 1 has an outer surface extending in the direction of the longitudinal axis and presents first and second ends 11, 12 having a reduced section. Figure 1 further shows a plurality of elements to be magnetized 22 to become permanent magnets or a plurality of already existing permanent magnets 22. The elements to be magnetized or permanent magnets 22 constitute portions of annular segments and are mounted in a cylindrical magnet housing 21 being formed of a magnetic material and having an inner diameter ΦX corresponding to an outer diameter of the cylindrically shaped shaft 1 less an interference fit IF1. The outer diameter of the cylindrically shaped shaft 1 is thus equal to ΦX+IF1. The plurality of permanent magnets or elements to be magnetized 22 are bonded into the cylindrical magnet housing 21 which may be made of one piece comprising a cylindrical portion and two closing flanges. The permanent magnets or elements to be magnetized 22 may be installed into the housing 21 by gluing, molding, pressing or any other method that allows the elements or magnets 22 to be bonded into the housing 21. If elements to be magnetized 22 are used at this stage, instead of already magnetic permanent magnets, the magnet assembly comprising the housing 21 and the elements 22 and having an outer diameter ΦY, may be machined at this stage if needed, without the inconvenience of magnetized chips or particles that are likely to stick to any other magnetic material. Once the magnet assembly comprising the housing 21 and the elements 22 is finished, it may be magnetized for its final function. An outer retaining cylindrical sleeve 23 is then inserted around the plurality of permanent magnets 22 installed into the cylindrical magnet housing 21. The next step of a method of manufacturing a rotor motor assembly according to the invention is illustrated in Figure 3. An end 12 of the shaft 1 is held tight in a fixed frame 13, whereas the other end 11 faces the magnet ring assembly 2 which has been manufactured in the step of Figure 1 and comprises the permanent magnets 22 located in their housing 21 and retained by the sleeve 23. The assembly 2 is then moved forward toward the shaft 1 which is inserted into the inner diameter of the cylindrical magnet housing 21, whilst preloading the outer retaining sleeve 23 by a resultant interference fit IF2 which is defined by the following formula: [MATHS id=math0003]: where ΦY is an external diameter of the plurality of permanent magnets 22, ΦX is an internal diameter of the cylindrical magnet housing 21, and IF1 is a primary interference fit between an external diameter of the cylindrically shaped shaft 1 and the internal diameter of the cylindrical magnet housing 21. In Figure 3, the arrows show the direction of application of the force exerted on a flange of the magnet ring assembly 2 to insert it onto the shaft 1. The required preload on the sleeve 23 depends on the application but may be guaranteed with a high precision by the resultant interference fit given by the above-mentioned formula (1). Figure 5 illustrates the resulting rotor assembly 10 with permanent magnets 22 which comprises the magnet ring assembly 2 inserted on the shaft 1 with the primary interference fit IF1 and a resultant interference fit IF2 being shown in the drawing, as well as the longitudinal axis X-X' of the rotor assembly 10. The two-step process of creating an interference fit according to the invention, including the second step of pushing pre-assembled magnet rings 2 onto a shaft 1, permits to obtain the required high interference without having to apply the excessively high or low temperatures required according to the known methods for assembling permanent magnet rotors of the prior art using the thermal expansion coefficient of the parts for a sliding fit at high or low temperature. Figures 2, 4 and 6 illustrate a variant embodiment which is generally similar to the embodiment of Figures 1, 3 and 5 and will not be described in detail, but which comprises a cylindrical magnet housing 21a, 21b, 21c which comprises a central cylindrical portion 21a and two separate closing flanges 21b, 21c. In the embodiment of Figures 2, 4 and 6 the elements which are identical to the elements of the embodiment of Figures 1, 3 and 5 bear the same reference numerals and will not be described again. The central cylindrical portion 21a, like the cylindrical magnet housing 21 is made of magnetic material. The separate closing flanges 21b, 21c can be made either of magnetic material or of non-magnetic material. In the embodiment of Figures 2, 4 and 6, the outer retaining sleeve 23' surrounding the plurality of permanent magnets 22 installed into the cylindrical magnet housing 21a, 21b, 21c may be made of composite material and may be installed by wounding around the cylindrical portion 21a of the cylindrical magnet housing. The method according to the present invention and the resulting rotor assembly with pre-assembled rings has a number of advantages. An easy in-situ magnetization of the magnet ring assembly 21, 22 or 21a, 21b, 21c, 22 may be done prior to insertion of the retaining sleeve 23, 23' because the mass of the full shaft 1 is not present, thus facilitating the assembly and machining of magnets 22 that are not yet magnetized. In particular, the risks of damage during transport of the assemblies are reduced because a magnetic field does not exist during the transport and will only be created later on before insertion of a retaining sleeve 23; 23'. When using the press insertion method as explained above, a sleeve 23, 23' will only receive radial loads, since the force is applied on the surface of the full assembly 2, 2' (e.g. on the flange 21b) which has a bigger surface and is more able to withstand axial efforts. The present invention allows the manufacturing of the magnets on a different assembly 2, 2' than the shaft 1, so that a complete assembly 2, 2' may be inserted on a shaft 1 and different steps of assembling and machining on the shaft 1 used in the prior art are eliminated, thus reducing the manufacturing cycle time and making a serial production easier. Finally, the invention permits to precisely apply a preload on the sleeve 23; 23'. Generally speaking, the invention provides a simplification in the manufacturing process, increases performance and reduces cost.

1. A permanent magnet rotor assembly having a longitudinal axis of rotation X'-X, first and second ends (11, 12) and at least two poles, comprising a cylindrically shaped shaft (1) having an outer surface extending in the direction of said longitudinal axis X'-X, a plurality of permanent magnets (22) constituting portions of annular segments and extending in the direction of said longitudinal axis X-X' and an outer retaining cylindrical sleeve (23, 23') surrounding said plurality of permanent magnets (22), characterized in that it further comprises a cylindrical magnet housing (21; 21a, 21b, 21c) mounted on said cylindrically shaped shaft (1) for supporting said plurality of permanent magnets (22), said cylindrical magnet housing (21; 21a, 21b, 21c) being formed of a magnetic material and in that the retaining cylindrical sleeve (23; 23') is preloaded by a resultant interference fit IF2 which is defined by the following formula: [MATHS id=math0004]: where ΦY is an external diameter of said plurality of permanent magnets (22),: Φ X is an internal diameter of said cylindrical magnet housing (21; 21a, 21b, 21c), and IF1 is a primary interference fit between an external diameter of said cylindrically shaped shaft (1) and said internal diameter of said cylindrical magnet housing (21; 21a, 21b, 21c).

2. The permanent magnet rotor assembly according to claim 1, wherein said cylindrical magnet housing (21) is made of one piece comprising a cylindrical portion and two closing flanges. 3. The permanent magnet rotor assembly according to claim 1, wherein said cylindrical magnet housing (21a, 21b, 21c) comprises a central cylindrical portion (21a) and two separate closing flanges (21b, 21c). 4. The permanent magnet rotor assembly according to any one of claims 1 to 3, wherein said retaining cylindrical sleeve (23) is made of a metallic material. 5. The permanent magnet rotor assembly according to any one of claims 1 to 3, wherein said retaining cylindrical sleeve (23') is made of a composite material. 6. The permanent magnet rotor assembly according to claim 5, wherein said retaining cylindrical sleeve (23') made of a composite material is wound on the assembly comprising said cylindrical magnet housing (21a, 21b, 21c) and said plurality of permanent magnets (22). 7. The permanent magnet rotor assembly according to any one of claims 1 to 6, wherein said permanent magnets (22) are installed and bound in said cylindrical magnet housing (21; 21a, 21b, 21c) by gluing, molding or pressing. 8. A method for making a permanent magnet rotor assembly according to claim 1, comprising the steps of: forming a cylindrically shaped shaft (1), forming a cylindrical magnet housing (21; 21a, 21b, 21c) having an inner diameter ΦX corresponding to an outer diameter of said cylindrically shaped shaft (1) less an interference fit IF1, said cylindrical magnet housing (21; 21a, 21b, 21c) being formed of a magnetic material, installing in said cylindrical magnet housing (21; 21a, 21b, 21c) a plurality of magnetic or magnetizable elements (22) constituting portions of annular segments, bonding said plurality of magnetic or magnetizable elements (22) into said cylindrical magnet housing (21; 21a, 21b, 21c), and if necessary magnetizing such magnetizable elements to constitute permanent magnets (22), installing an outer retaining cylindrical sleeve (23, 23') surrounding said plurality of permanent magnets (22) installed into said cylindrical magnet housing (21; 21a, 21b, 21c), and: inserting said cylindrically shaped shaft (1) into the inner diameter of said cylindrical magnet housing (21; 21a, 21b, 21c) whilst preloading said outer retaining cylindrical sleeve (23, 23') by a resultant interference fit IF2 which is defined by the following formula: [MATHS id=math0005]: where ΦY is an external diameter of said plurality of permanent magnets (22), ΦX is an internal diameter of said cylindrical magnet housing (21; 21a, 21b, 21c), and IF1 is a primary interference fit between an external diameter of said cylindrically shaped shaft (1) and said internal diameter of said cylindrical magnet housing (21; 21a, 21b, 21c). 9. The method according to claim 8, wherein said step of installing in said cylindrical magnet housing (21; 21a, 21b, 21c) a plurality of magnetic or magnetizable elements (22) constituting portions of annular segments comprises machining said magnetic or magnetizable elements (22) and magnetizing said magnetizable elements to constitute permanent magnets. 10. The method according to claim 8 or claim 9, wherein said outer retaining cylindrical sleeve (23) surrounding said plurality of permanent magnets (22) installed into said cylindrical magnet housing (21) is installed by simple insertion. 11. The method according to claim 8 or claim 9, wherein said outer retaining cylindrical sleeve (23') surrounding said plurality of permanent magnets (22) installed into said cylindrical magnet housing (21a, 21b, 21c) is made of composite material and is installed by wounding around said cylindrical magnet housing (21a, 21b, 21c). 12. The method according to any one of claims 8 to 11, wherein said permanent magnets (22) are installed and bound in said cylindrical magnet housing (21; 21a, 21b, 21c) by gluing, molding or pressing. 13. The method according to any one of claims 8 to 12, wherein said cylindrical magnet housing (21) is made of one piece comprising a cylindrical portion and two closing flanges. 14. The method according to any one of claims 8 to 12, wherein said cylindrical magnet housing (21a, 21b, 21c) comprises a central cylindrical portion (21a) and two separate closing flanges (21b, 21c). 15. The method according to any one of claims 8 to 12, wherein said permanent magnets (22) are firstly inserted and bounded in the cylindrical magnet housing (21; 21a, 21b, 21c) as non-magnetized elements, then the resultant magnet assembly (21, 22; 21a, 21b, 21c, 22) is machined and said non-magnetized elements are magnetized to constitute operational permanent magnets (22) prior to installation of said sleeve (23; 23').

2886890

Thrust disc, magnetic bearing and apparatus

Based on the following detailed description of an invention, generate the patent claims. There should be 15 claims in total. The first, independent claim is given and the remaining 14 dependent claims need to be written. Do not repeat the first claim. The claims should be clear, precise, consistent and consice and should be grounded in the information in the detailed description.

Figure 1 shows a magnetic bearing 1 according to the invention. Magnetic bearing 1 is mounted on a shaft 2 belonging to an apparatus, for example a turbomachine. Shaft 2 has a cylindrical outer surface 3 centered on a central axis X2. Shaft 2 is movable in rotation around axis X2. Magnetic bearing 1 is adapted to generate an axial thrust along axis X2. Magnetic bearing 1 comprises two thrust stators 5 and 6, schematically represented for simplification purpose. Bearing 1 also comprises an axial thrust disc 10 according to the invention, mounted on shaft 2. Thrust stators 5 and 6 are fixed to a housing not shown, while thrust disc 10 is movable in rotation around axis X2. Thrust disc 10 comprises a body 20 and two flanges 50 and 60, each having an annular shape. When thrust disc 10 is mounted on shaft 2, then body 20 and flanges 50, 60 are centered on axis X2. Flanges 50 and 60 are destined to form a magnetic coupling with thrust stators 5 and 6, respectively. Flanges 50 and 60 are fixed to body 20 in a position where they can interact with thrust stators 5 and 6 to form the magnetic bearing 1. Preferably, for a magnetic bearing 1 used in a corrosive environment, body 20 and flanges 50, 60 are made of corrosion resistant materials and are compliant with norm NACE MR0175, also designated as norm ISO 15156-3. Thus, thrust disc 10 is resistant to corrosive elements such as CO _2 and H _2 S. In this regard, body 20 and flanges 50, 60 are preferably subjected to heat treatment, in particular post welding heat treatment when applicable. Body 20 comprises a base portion 30 for mounting on shaft 2 and a radial portion 40 for receiving flanges 50 and 60. Body 20 is a single part, in other words portions 30 and 40 are formed integral with each other. Portion 30 extends principally along a direction parallel to axis X2, while portion 40 extends principally along a direction radial to axis X2. Portion 30 comprises a cylindrical bore 32 receiving surface 3 of shaft 2. Portion 40 includes two annular recesses 45 and 46, formed on opposite sides of body 20. Body 20 has a first offset yield strength Rp20 at 0.2% strain and a first magnetic permeability µ20. Preferably, Rp20 is equal or superior to 800 MPa, more preferably equal or superior to 1000 MPa. In addition, µ20 is preferably equal or superior to 0,0002 H/m, more preferably equal or superior to 0,0008 H/m.. For example, body 20 is made of a martensitic stainless steel, such as 17-4PH, having an offset yield strength Rp20 generally comprised between 1100 and 1300 Mpa. According to another example, body 20 is made of a Nickel based alloy, such as Inconel (registered trademark). Each flange 50 and 60 is preferably formed as a single part. Alternatively, each flange 50 and 60 may be made of several sectors. Flanges 50 and 60 are fastened by screws 90 in recess 45 or 46, respectively. More precisely, screws 90 press flanges 50 and 60 in recesses 45 and 46 and are threaded into portion 40 of body 20. Screws 90 are preferably made of a corrosion resistant material, such as 17-4PH, K44 or Inconel (registered trademark). Alternatively, flanges 50 and 60 may be fastened to body 20 by glue, welding, riveting or any suitable means. Flange 50 has a second offset yield strength Rp50 at 0.2% strain and a second magnetic permeability µ50. Flange 60 has a third offset yield strength Rp60 at 0.2% strain and a second magnetic permeability µ60. Flanges 50 and 60 are preferably made of the same material, so that Rp50 and Rp60 are equal and that µ50 and µ60 are equal. Preferably, µ50 and µ60 are superior to 0,001 H/m, more preferably superior to 0,002 H/m. In addition, Rp50 and Rp60 are preferably equal or superior to 350 MPa. For example, flanges 50 and 60 are made of a ferritic stainless steel, such as AISI 444. In practice, when the thrust disc 10 is in operation and rotates around axis X2, centrifugal stresses applied to thrust disc 10 are concentrated close to shaft 2. Consequently, centrifugal stresses applied to body 20 and in particular to base portion 30 are higher than centrifugal stresses applied to flanges 50 and 60. Furthermore, the magnetic properties of the flanges 50 and 60 are chosen to reach a magnetic flux density preferably superior to 1,4 T (teslas) between thrust disc 10 and thrust stators 4 and 5. According to the invention, constitutive materials of the thrust disc 10 are chosen such as mechanical properties of body 20 are higher than mechanical properties of flanges 50 and 60, while magnetic properties of body 20 are smaller than magnetic properties of flanges 50 and 60. More precisely, offset yield strength Rp20 is higher than offset yield strengths Rp50 and Rp60, while magnetic permeability µ20 is smaller than magnetic permeabilities µ50 and µ60. Other embodiments are represented on figures 2 to 7. In these embodiments, elements similar to the first embodiment have the same references and work in the same way. Only the differences with respect to the first embodiment are described hereafter. Shaft 2 and thrust stators 4 and 5 are not represented on figures 2 to 7 for simplification purpose. In the second embodiment represented on figure 2, the thrust disc 10 comprises two outer flanges 150 and 160 and two inner flanges 170 and 180. Flange 150 is disposed around flange 170 in recess 45, while flange 160 is disposed around flange 180 in recess 46. Each flange 150, 160, 170 and 180 is fixed by a screw 90 to body 20. Smaller flanges 150, 160, 170 and 180 are easier to manufacture than larger flanges 50 and 60. Flanges 150 and 160 can be made of the same material than flanges 170 and 180 or, alternatively, of different materials such as materials well known in the field. In the third embodiment represented on figure 3, the thrust disc 10 comprises one flange 250 fixed in an annular recess 245 formed in body 20. Flange 250 is fastened to body 20 by several welding points 290 distributed on the thrust disc 10. Only one welding point 290 is shown on figure 3 for simplification purpose. A thermal treatment may be applied to the thrust disc 10 to release the weld stresses and keep it compliant with norm NACE MR0175, for example "H 1150 M" treatment. Weldings 290 limit the creation of centrifugal stress concentrations and the deformation of flange 250 created by magnetic axial pull up force. A final machining may be performed on thrust disc 10 after the heat treatment. In the fourth embodiment represented on figure 4, the thrust disc 10 comprises one flange 350 similar to flange 250. Flange 350 is fastened to body 20 by radial weldings 390 distributed around the central axis of the thrust disc 10. In the fifth embodiment represented on figure 5, the thrust disc 10 comprises one magnetic plate 480 made of three superposed flanges 450, 460 and 470, which are fixed to the body 20 and to each other by performing successive welding points 490. Flanges 450, 460 and 470 are easier to manufacture with a small thickness, for example below 4 millimeters. Their superposition allows obtaining a larger magnetic plate 480 with suitable magnetic properties. To comply with norm NACE MR0175, only external flange 470 may be subjected to a heat treatment. Flanges 450, 460 and 470 can be made of the same material or, alternatively, of different materials such as materials well known in the field In the sixth embodiment represented on figure 6, the thrust disc 10 comprises two flanges 550 and 560 similar to flanges 50 and 60 of the first embodiment, except that flanges 550 and 560 are fixed to body 20 by fastening means 590 including rivets 591 and weldings 592. Rivets 591 extend through the flanges 550 and 560 and body 20 and are fixed to the flanges 550 and 560 by weldings 592. Rivets 591 are preferably made of a corrosion resistant material, such as K44. When flanges 550, 560 and rivets 591 are made of K44, no further heat treatment is required to comply with norm NACE MR0175. In the seventh embodiment represented on figure 7, the thrust disc 10 comprises two flanges 650 and 660 fastened to body 20 by fastening means 690 including weldings 692 and inserts 693 and 694. In a first step, inserts 693 and 694 are fixed to body 20, preferably by welding. In a second step, flanges 650 and 660 are welded to inserts 693 and 694. Thus, no further heat treatment is required to comply with norm NACE MR0175. In a third step, holes 695 may be formed through body 20 and/or flanges 650, 660, for internal and external pressure equilibrium of the thrust disc 10. Whatever the embodiment, offset yield strength Rp20 of body 20 is higher than offset yield strength Rp50, Rp60, of each flange and magnetic permeability µ20 of body 20 is smaller than magnetic permeability µ50, µ60, of each flange 50, 60, 150, 160, 170, 180, 250, 350, 450, 460, 470, 550, 560, 650 and 660. Other non-shown embodiments can be implemented within the scope of the invention. In particular, body and flanges of the thrust disc 10 may have different configurations. In addition, technical features of the different embodiments can be, in whole or part, combined with each other. Thus, magnetic bearing 1 and thrust disc 10 can be adapted to the specific requirements of the application.

1. A thrust disc (10) for a magnetic bearing (1), wherein the thrust disc (10) comprises: - a body (20) which is adapted to be mounted on a shaft (2) and which has a first offset yield strength (Rp20) and a first magnetic permeability (µ20), and - at least one flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) which is fixed to the body (20) in a position where it can interact with a thrust stator (5 ; 6) in order to form a magnetic bearing (1) and which has a second offset yield strength (Rp50 ; Rp60) and a second magnetic permeability (µ50 ; µ60) ; wherein the first offset yield strength (Rp20) is higher than the second offset yield strength (Rp50 ; Rp60) ;: and wherein the first magnetic permeability (µ20) is smaller than the second magnetic permeability (µ50 ; µ60).

2. Thrust disc (10) according to claim 1, wherein it comprises several flanges (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660), wherein the first offset yield strength (Rp20) of the body (20) is higher than the offset yield strength (Rp50 ; Rp60) of each flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660), and wherein the first magnetic permeability (µ20) of the body (20) is smaller than the magnetic permeability (µ50 ; µ60) of each flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660). 3. Thrust disc (10) according to any one of the previous claims, wherein the body (20) and the flange or flanges (50, 60) are made of corrosion resistant materials. 4. Thrust disc (10) according to any one of the previous claims, wherein the body (20) has a first offset yield strength (Rp20) equal or superior to 800 MPa, preferably equal or superior to 1000 MPa. 5. Thrust disc (10) according to any one of the previous claims, wherein the body (20) is made of a martensitic stainless steel, preferably 17-4PH. 6. Thrust disc (10) according to any one of the previous claims, wherein the or each flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) has a magnetic permeability (µ50 ; µ60) equal or superior to 0,001 H/m, preferably equal or superior to 0,002 H/m. 7. Thrust disc (10) according to any one of the previous claims, wherein the or each flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) is made of a ferritic stainless steel, preferably AISI 444. 8. Thrust disc (10) according to any one of the previous claims, comprising means for fastening the flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) to the body (20), which include at least one screw (90). 9. Thrust disc (10) according to any one of the previous claims, comprising means for fastening the flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) to the body (20), which include at least one welding (290 ; 390 ; 490 ; 592 ; 692). 10. Thrust disc (10) according to claim 9, comprising means for fastening the flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) to the body (20), which include at least one radial welding (390). 11. Thrust disc (10) according to any one of the previous claims, comprising means (90) for fastening the flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) to the body (20), which include at least one rivet (591). 12. Thrust disc (10) according to any one of the previous claims, wherein several flanges (450, 460, 470) are superposed to form a magnetic plate (480). 13. Thrust disc (10) according to any one of the previous claims, wherein holes (695) are formed in the body (20) and/or the flange (50, 60 ; 150, 160, 170, 180 ; 250 ; 350 ; 450, 460, 470 ; 550, 560 ; 650, 660) for internal and external pressure equilibrium of the thrust disc (10). 14. A magnetic bearing (1), comprising a thrust disc (10) according to any one of the previous claims 1 to 13. 15. An apparatus, comprising a magnetic bearing (1) according to claim 14.