Source: http://russianpatents.com/patent/237/2374508.html
Timestamp: 2017-11-22 19:55:30
Document Index: 598796307

Matched Legal Cases: ['application No. 09', 'application No. 09', 'art) 14', 'art) 16', 'art 100', 'art 96', 'art 100', 'art 100', 'arts 100', 'arts 100', 'art 100', 'art 100', 'art 160', 'arts 160']

Damper's bearing structure
The present invention relates to a bearing structure of the dampers in the cylinder in which the piston is displaced in the axial direction of the cylinder when the supply of the working fluid. When this damper absorbs shocks arising at the junction of the above-mentioned piston to the covers.
Known hydraulic cylinder having inside the piston, moving with the flow of the working fluid is used, for example, as a device for moving the various parts. In the design of such a hydraulic cylinder uses a piston that fits with the possibility of displacement inside the chamber of the cylinder that forms the inner part of the tubular body of the cylinder, and has an elastic dampers, which can absorb shocks arising at the junction of the piston to the front cover and the cover stock, which are installed at both respective ends of the cylinder barrel.
Such elastic damper, for example, as a shock absorber, as claimed in the Japanese Publication laid patent applications utility model No. 07-034239 made of elastic material such as rubber, or similar material. Elastic dampers are located on both end surfaces of the piston are located against each other and combined into a single unit by the piston rod and connected to the piston nut. Thus this is the first design, the piston moves along the cylinder barrel, and his punches are amortized elastic dampers.
In Japanese Publication laid patent application No. 09-30320 sealing gasket, which act as elastic dampers are located between the ends of the cylinder barrel and covers, while the piston moves along the cylinder barrel and his punches are depreciated by the joining of the sealing strip.
It should be noted that elastic dampers in accordance with the Japanese Publication laid patent applications utility model No. 07-034239 are generally round cross-sectional shape. However, for example, in Japanese Publication laid patent application No. 09-303320 in the cylinder is flattened shape, which has a piston elliptical cross-section and passing in a horizontal direction of the main axis, as well as chamber of a cylinder of elliptical cross section, where moves this piston, the dimensions of the piston and lid height is small, and therefore it is difficult to provide the same seal as the piston with elastic dampers round cross-section. The result is a significant reduction cushioning damper with which it can absorb the shock piston.
Main objective of the present invention is to provide a carrier to the decomposition of the damper, having a predetermined capacity impact cushioning and a simple structure, which allows easy and reliable to install dampers on the piston or the covers.
These and other features and advantages of the present invention will become clearer from the following description presented in conjunction with the accompanying figures of the drawings, which illustrate examples illustrate preferred embodiments of the present invention.
Figure 1 is a perspective view of a cylinder used in which the supporting structure of the damper in accordance with the implementation of the present invention.
Figure 2 - exploded view view in perspective of the hydraulic cylinder shown in figure 1.
Figure 3 - General view of a vertical cross section of the cylinder shown in figure 1.
Figure 4 - exploded vertical cross-section of the cylinder shown in Figure 3.
Figa an enlarged perspective view of the elastic damper, shown in figure 2, Figb an enlarged perspective view of the elastic damper Figa presented from a different direction.
6 is a lateral projection on the cap side of the piston rod of the hydraulic cylinder shown in figure 1.
7 is a lateral projection on the cap side of the piston rod of the hydraulic cylinder shown in figure 1.
Fig - simple mountains the horizontal projection of the retaining ring.
Fig.9 is a simple image in term of elastic damper according to the first modified example.
Figure 10 is a partial cross-section in the vertical direction showing the state in which the elastic damper figure 9 is installed in the damper grooves of the piston.
11 - simple image in perspective elastic damper in accordance with the second modified example.
Fig - the horizontal projection of the piston, which has an elastic damper, shown at 11.
Fig - image in the future state, in which the cylinder is installed retaining ring in accordance with a modified example.
Fig is a simple projection of the retaining ring shown in Fig.
Fig - lateral projection, provided by the front cover of the cylinder shown in Fig.
Fig - side projection is presented on the cover side of the piston rod of the hydraulic cylinder shown in Fig.
Figure 1 under item 10 shows the hydraulic cylinder equipped with dampers that have a bearing construction of the damper in accordance with the implementation of the present invention.
As shown in Figure 1-4, the hydraulic cylinder 10 comprises a tubular backbone cylinder (cylinder body) 12, the front cover (closing part) 14, set the run at one end of the main cylinder 12, cover stock (closing part) 16, mounted on the other end of the main cylinder 12 and the piston 18 posted with the possibility of bias within the main cylinder 12.
The backbone of the cylinder 12 has a generally rectangular shape in cross section and contains the channel cylinder 20 having an elliptical cross-sectional shape and passing in the axial direction inside the main cylinder 12. The channel of the cylinder 20 has a cross-sectional elliptical shape and is positioned so that its main axis runs in the horizontal direction (when the cylinder 10 is oriented as shown in Fig.6 and Fig.7), and on both ends of the channel has a pair of grooves 22A, 22b, which are elongated in the width direction from the center channel of the cylinder 20. On both end parts respectively formed of a pair of grooves 22A and 22b so that the grooves 22A, 22b are deepening arcuate shape and are mainly in the horizontal direction relative to the main cylinder 12 tapered shape. More specifically, the grooves 22A, 22b are located against each other, they just extended in directions from the center channel of the cylinder 20. In this case, the radius of curvature of the grooves 22A, 22b is made smaller than the radius of curvature of the two end parts of the channel of the cylinder 20.
More specifically, the inner peripheral surface of the feed cylinder 20 education is as well, both the extreme part of the channel of the cylinder 20 exceeds the relevant portions of the grooves 22A, 22b. In addition, between the grooves 22A, 22b and the Central region, along the axial direction of the cylinder chamber 20, are the stoppers 24.
In addition, both ends of the channel of the cylinder 20 along its inner peripheral surface toward the grooves 22A, 22b, respectively formed annular grooves 26. In the annular grooves 26 respectively installed retaining rings 28a and 28b.
In addition, on the inner surface of the main cylinder 12 is formed of a pair of first and second hydraulic channel 30 and 32 through which is fed and from which comes the working fluid. While the first and second hydraulic ports 30, 32 are separated from each other by a given distance along the axial direction of the main cylinder 12 and communicated respectively with the channel of the cylinder 20 through the supply channel 34 (see figure 3). Accordingly, the working fluid supplied to the first and second hydraulic ports 30, 32, passes through the supply channels 34 and enters the channel of the cylinder 20. In addition, on the outer side surface of the main cylinder 12, along its axial direction (in the direction of the arrows a and b), passes through several sensory grooves 36, which can be installed sensors, allowing to detect state the piston 18.
The front cover 14 has a cross-section in a generally elliptical shape corresponding to the cross-sectional shape of the channel of the cylinder 20, and is installed at one end (in the direction of the arrow a) of the main cylinder 12. There is also a pair of protrusions 38A, which act on a given length from the outer peripheral surface on both side parts of the front cover 14 corresponding to the location of the grooves 22A in the channel of the cylinder 20. The projections 38A are located on both side of the front cover 14, forming the outside arcuate bulge to a predetermined radius of curvature corresponding to the curvature of the grooves 22A (see Fig.6).
In an annular groove on the outer peripheral surface of the front cover 14 is installed sealing ring 40. When the front cover 14 is inserted into the channel of the cylinder 20 of the main cylinder 12, the latter will be supported in a sealed state due to the abutment of the sealing ring 40 to the inner peripheral surface of the channel of the cylinder 20.
Similarly, the front cover 14, the cover of rod 16 has a generally elliptical shape in cross-section, which corresponds to the channel shape of the cylinder 20, and the cover is installed on the other end (in the direction of arrow C) of the main cylinder 12. In addition, formed a pair of projections 38b, which act on a given length from the outside is perifericheskoi surface on both side parts in accordance with the location of the grooves 22b of the channel of the cylinder 20. The projections 38b are located on either side of the cover rod 16 forming outside arcuate bulge to a predetermined radius of curvature corresponding to the curvature of the grooves 22b (see Fig.7).
In the Central part of the cover of the stem 16 is formed the channel of the rod 42, which runs along the axial direction, and in the channel of the rod 42 is introduced to the piston rod 44 connected to the piston 18. Inside the channel of the rod 42 is set rod seal 46 and sleeve 48, which provides thereby the tightness inside the channel of the cylinder 20.
In addition, on the outer peripheral surface of the cover rod 16, in the Central part of the groove, there is a seal ring 40 is installed in the axial direction of the cover shaft 16. On the end part, symmetrically with the protrusions 38b, there are several (e.g. six) of the guide elements 49 which are separated at a predetermined distance between the elements has an annular groove (see Figure 2). Guide members 49 are at a predetermined height above the peripheral outer surface so that upon introduction of the cap rod 16 in the channel of the cylinder 20 guide members 49 ov contact with the inner peripheral surface of the channel of the cylinder 20. In other words, the guide members 49 are of the form, which corresponds to the inner peripheral surface of the channel of the cylinder 0. The number of guide elements 49 is not limited to any particular number, unless that number is equal to or more than four, and guide members 49 are mutually distant from each other at predetermined distances.
Due to the above, when the cover of rod 16 is inserted into the channel of the cylinder 20, a cover of rod 16 is directed into the channel of the cylinder 20 several guide elements 49, the lid shaft 16 is properly installed in the radial direction within the channel of the cylinder 20. As a result the Central axis of the channel of the cylinder 20 and the axial line of the cap rod 16 will coincide with each other, and the piston rod 44, which passes through the channel of the cylinder 20 may be introduced into the channel of the stem 42 of the cover of rod 16 will pass through it accurately and with high precision.
The piston 18 has a generally elliptical shape in cross section. On the outer peripheral surface of the piston 18 has a pair of sections with a flat surface 50 and a pair of arcuate sections 52 that extend beyond the outer side, have given radius of curvature and is connected to both end sections of the flat surface 50. On the outer peripheral surface is set piston seal 54 and the magnetic piece 56, while the magnetic piece 56 is closed, the piston cap 58. The outer peripheral surface of the piston cover 58 lies on the W is the surface that and the outer peripheral surface of the piston 18.
In addition, on the inner part of the piston 18 is formed piston channel 60, which passes in the axial direction (in the direction of the arrows a and b), and through the piston channel 60 is entered coupling piece 62 of the piston rod 44. Piston channel 60 has a first channel 64, which is open on the cap side of the piston 16 (in the direction of arrow C), the second channel 66, which is adjacent to the first channel 64 and has a smaller diameter and a cone-shaped channel 68, which is adjacent to the second channel 66 and which gradually increases in diameter toward the front cover 14 (in the direction of arrow A). The first and second channels 64, 66 and tapered channel 68 are mutually interconnected.
In addition, on both end surfaces of the piston 18 has the damper grooves 70A and 70b, and the damper grooves 70A and 70b is cut to a predetermined depth. In each of the damper grooves 70A and 70b inserted elastic dampers 72A and 72b, respectively (hereinafter indicated simply dampers).
The damper grooves 70A and 70b are oriented strictly perpendicular to the axis of the piston 18 along both end surfaces, and are held between a pair of sections with a flat surface 50. In addition, the damper grooves 70A and 70b provide the first grooves 74 that are adjacent to both end surfaces of the piston 18, and storagelarge 76, which is slightly more recessed inward from the both end surfaces than the first grooves 74, and the width of which increases the width of the first grooves 74. The second grooves 76 increase in width at a pre-specified amount in the direction perpendicular mainly to the direction in which extend the damper grooves 70A, 70b.
As shown in Figa and Figb, elastic dampers 72A, 72b are flat elements of rectangular cross section made of elastic material such as urethane rubber or its analogues, and are arranged so that they compete for a certain length outward from both end surfaces of the piston 18. Dampers 72A, 72b contain channels 78 that pass along the axial direction of the damper mainly by their centers, the basic elements 80, which are respectively inserted in the damper grooves 70A, 70b, and guide members 82, which have a width greater than the basic elements 80 and respectively inserted into the second grooves 76 of the damper grooves 70A, 70b.
The cross-sectional shape of dampers 72A, 72b is basically the same as the cross-sectional shape of the damper grooves 70A, 70b, causing the guide members 82 are inserted into the second grooves 76, while the basic elements 80 is inserted into the first grooves 74 and, accordingly, are drug the MS on a given length relative to both end surfaces of the piston 18.
The longitudinal dimensions of the dampers 72A, 72b is equal to mainly longitudinal dimensions of the damper grooves 70A, 70b. Consequently, when installing dampers 72A, 72b in the damper grooves 70A, 70b end surface of the dampers 72A, 72b does not jut out over the section with the flat surfaces 50 of the piston 18 and the holes 78 on the dampers are located just opposite the piston channel 60 of the piston 18. In addition, the piston rod 44 is inserted through the opening 78 of the damper 72b mounted in the piston 18 on one surface of the cover shaft 16 (in the direction of the arrow). The damper grooves 70A, 70b are completely closed elastic dampers 72A, 72b due to the fact that they have elastic dampers 72A, 72b.
As for the dampers 72A, 72b, the relative displacement of these dampers in the axial direction relative to the piston 18 is regulated, since the guide members 82, which are the width for the base members 80, concatenated with the second grooves 76 of the damper grooves 70A, 70b. In other words, dampers 72A, 72b are installed so that they can move only in directions perpendicular to the axis of the piston 18 along which pass damper grooves 70A, 70b.
In addition, the dampers 72A, 72b are adjacent respectively to the front cover 14 and the cover of rod 16 before joining the piston 18 when the displacement of the piston 18 along the highway qi is Indra 12 in the end position of the piston 18. Due to this properly amortized and is absorbed by the dampers 72A, 72b strokes that occur at the contact of the piston 18 with the front cover 14 and the cover of the piston 16 and thereby prevents the impact of such shocks on the piston 18. In other words, dampers 72A and 72b act as buffer mechanisms, which help to cushion and absorb the shock on the piston 18.
The piston rod 44 comprises a shaft having a predetermined length in the axial direction. At one end of the shaft has a radially decreasing in diameter coupling piece 62, which is connected with the piston 18. The fitting 62 is inserted in the second channel 66 and tapered channel 68 of the piston channel 60. On the other hand, the second end of the piston rod 44 is inserted through the channel of the rod 42 and is supported with the possibility of displacement of the sleeve 48 and stem seal 46.
As for the piston rod 44, the end region of the piston rod 44 with the connecting piece 62 is in contact with the locking part between the first channel 64 and the second channel 66, and thereby the piston rod 44 is in a fixed state relative to the piston 18. The preload of the end fitting 62, which is inserted into the tapered channel 68, toward the side of the second channel 66 (in the direction of arrow C) end fittings flexibly deformed along conoseibe the aqueous channel 68 and increases in diameter. In the connection piece 62 is sealed to the cone-shaped channel 68 of the piston 18 to its deformed end portion, thereby connecting between the piston rod 44 and the piston 18. In this connection piece 62 of the piston rod 44 does not extend beyond the end surface of the piston 18 and is sealed in such a way that it forms basically the same surface as the end surface of the piston 18.
As shown in Fig, locking rings 28a, 28b have a U-shaped cross-section, made of metal and are installed respectively in a pair of annular grooves 26, which are formed in the channel of the cylinder 20 of the main cylinder 12. The locking rings 28a, 28b have a shape corresponding to the shape of the annular grooves 26, and contains a curved section 84 which is bent to a predetermined radius of curvature, a pair of lever sections 86, which are strictly straight lines at both ends of the curved section 84, and a pair of clamping sections 88, located at the ends of the arm sections 86, which are curved with a predetermined radius of curvature and separated from each other by a predetermined distance. Clamping section 88 is installed opposite the curved section 84, which is located between the lever sections 86 and locking rings 28a and 28b have some power of elasticity, resulting in the two parts of the clamping sections 88 are moving away from each other in mutually the but opposite directions at a specified distance.
The curved section 84 has a predefined radius of curvature that matches the radius of curvature of both sides of the channel of the cylinder 20, with the clamping section 88 similarly have a predefined radius of curvature that matches the radius of curvature of the side walls of the channel of the cylinder 20.
On a hook sections 86 has a convex section 90, which are bent toward the inner side surface toward each other. In convex sections 90, respectively, formed fixing holes 92. More specifically, the convex section 90 and the locking holes 92 are located on the lever sections 86, coinciding with the sides curved section 84. In addition, the introduction of a not shown lock in a pair of fixing holes 92 and mutual displacement of the convex sections 90 with the locking holes 92 in the directions to each other can elastically deform the lever sections 86 and clamping section 88 so that they come closer to each other and almost connects to the curved section 84.
More specifically, the curved section 84 and clamping section 88 of locking rings 28a, 28b are connected to both side surfaces of the channel of the cylinder 20 in the annular grooves 26.
In addition, once in the annular grooves 26 are respectively the locking rings 28a, 28b, the front cover 14 and the cover of rod 16 is mounted on the channel Zilin is RA 20 of the main cylinder 12. After that, the front cover 14 and the cover of rod 16 is fixed by means available to them protrusions 38A, 38b and locking rings 28a, 28b, respectively. When the front cover 14 and the cover of rod 16 do not extend beyond the end surface of the main cylinder 12.
The hydraulic cylinder 10, which uses the damper in accordance with the present invention is constructed basically as described above. Next will be described the Assembly of the cylinder 10.
First, when the dampers 72A, 72b are installed on the piston 18 on the respective sides of the piston 18 are guide members 82 dampers 72A, 72b and the end sides of the open damper grooves 70A, 70b are mounted dampers 72A, 72b. In addition, the dampers 72A, 72b are shifted from sliding toward the piston 18 to enter the guide elements 82 in the second groove 76. When the dampers 72A, 72b are shifted along the damper grooves 70A, 70b in the direction perpendicular to the axis of the piston 18. Due to this elastic dampers 72A, 72b, which are part of the guide elements 82, are found in the second grooves 76 and along with this, their basic elements 80 are inserted into the first grooves 74.
Finally, the installation of dampers 72A, 72b ends when the ends of the elastic dampers 72A, 72b will come in line and aligned with the sections of the flat surface 50 of the piston 18. In this case, the channels 78 dem is Perov 72A, 72b will are coaxially aligned with the piston channel 60 of the piston 18, and the dampers 72A, 72b will be on pre-determined height with respect to both end surfaces of the piston 18 (see figure 3).
In the same way can be easily installed dampers 72A, 72b sliding displacement of the dampers 72A, 72b relative to the damper grooves 70A, 70b, available on both end surfaces of the piston 18, in the directions perpendicular to the axis of the piston 18. In addition, the dampers 72A, 72b may not be displaced in axial directions relative to the piston 18, as guiding elements 82 coupled with the second grooves 76.
Although the dampers 72A, 72b can be displaced in directions perpendicular to the axis of the piston 18, when the input piston 18 in the channel of the cylinder 20 of the main cylinder 12, the displacement of the dampers 72A, 72b perpendicular to the axis of the piston 18 will be adjusted due to the fact that the outer peripheral surface of the piston 18 will be covered by the inner peripheral surface of the channel of the cylinder 20.
As a result, the dampers 72A, 72b in the normal state are shifted as a whole, and in Concord with the displacement of the piston 18, thereby providing a reliable and adequate damping of the shock acting on the piston when it is offset in the end position.
Instead of the mentioned dampers 72A, 72b can also use the find is shown in Figure 9 and Figure 10 elastic dampers 102A, 102b (hereinafter called simply dampers 102A, 102b)having a rounded portion 96 on the guide member 94, and a wedge-shaped part 100 on the side surfaces of the base element 98.
Dampers 102A, 102b have chamfered portion 96 with a semicircular cross-sectional shape and protrude outwards in the direction of basic element 98 on the side surfaces of the guide elements 94, while the rounded portion 96 along the guide elements 94.
On the other hand, the damper grooves a, 104b, which are formed on the piston 18a, contain grooves 108, into which you insert the rounded part 96, with grooves 108 formed within the second grooves 106, in which the inserted guide members 94. The grooves 108 are of semicircular cross-sectional shape and extended in directions to both end surfaces of the piston 18a (see Figure 10).
In addition, the base element 98, which is part of dampers 102A, 102b, formed wedge-shaped part 100, which gradually decrease in width in the direction of the guide elements 94, and a wedge-shaped part 100 extends along the reference element 98. On the other hand, in the first grooves 110 of the damper grooves a, 104b are formed wedge-shaped surface 112 with predetermined angles corresponding to the shape of the wedge-shaped parts 100. Wedge-shaped surface 112 is performed so that the first grooves 110 are gradually narrowing toward the end surfaces of the piston 18a.
Thus, the formation of the rounded portions 96 on the guide member 94 dampers 102A, 102b and the grip curved portions 96 with grooves 108 formed in the damper grooves a, 104b, it is possible to reliably prevent removing the dampers 102A, 102b from the piston 18 even when the dampers 102A, 102b pulled out in the direction of separating them from the damper grooves a, 104b of the piston 18a (in the directions of arrows a and b), since the rounded portion 96 coupled with the grooves 108.
Further, the formation of wedge-shaped portions 100 on the base element 98, which forms the dampers 102A, 102b, and wedge connection parts 100 with wedge-shaped surfaces 112 of the first grooves 110 that are part of the damper grooves a, 104b, may be even more reliably prevented from removing the dampers 102A, 102b from the piston 18a, as a result of the engagement of the wedge-shaped part 100, even when the dampers a, 104b are drawn in the directions separating them from the damper grooves a, 104b of the piston 18a (in the directions of arrows a and b).
The invention is not limited to the above-described case, in which simultaneously with the dampers 102A, 102b are formed rounded portion 96 and a wedge-shaped part 100. You can also prevent removing the dampers 102A, 102b from the piston 18a and when there is only one of these parts is rounded portion 96 or wedge-shaped hour and 100.
Further, when the piston 18 with a pair of installed dampers 72A, 72b is inserted into the main cylinder 12 and the front cover 14 and the cover shaft 16 are mounted on both ends of the main cylinder 12, the front cover 14 is inserted through the channel of the cylinder 20 from one side of the main cylinder 12 and tightened within the channel of the cylinder 12 to the piston 18 (in the direction of the arrow B) until such time as the protrusions 38A is set opposite the retaining portion 24 of the grooves 22b formed in the channel of the cylinder 20. Next, after the protrusions 38b will be opposite the retaining portion 24 and the offset of the front cover 14 to the other end side of the main cylinder 12, which is the front side of the piston 18 (in the direction of the arrow B), shall be adjusted, retaining ring 28b is inserted into the channel of the cylinder 20 and is mounted in an annular groove 26 on the other end side of the main cylinder 12.
In this case, the lever section 86 and the mounting section 88 are deformed in such directions that are pressed to each other by a clamp (not shown)which are inserted into a pair of fixing holes 92, and after the retaining ring 28a will be very close to the annular groove 26, the retaining ring 28a is again deformed by unlocking the locking state of the arm sections 86 of the latch, after which the retaining ring 28 with the em its elasticity will expand in the radial direction and come into engagement with the annular groove 26.
Accordingly, the offset cover stock 14 into the main cylinder 12 (in the direction of the arrow C) is adjustable in axial direction of the clutch projections 38A of the front cover 14 with the grooves 22A of the channel of the cylinder 20. In addition, the offset of the front cover 14 out of the main cylinder 12 (in the direction of arrow A) are also regulated by the retaining ring 28a mounted inside the annular groove 26. That is, the front cover 14 is secured in one end side of the main cylinder 12 and fit in this place, not speaking out from the end of the main cylinder 12.
Thus, as the cover of rod 16 is directed along the channel of the cylinder 20 several guide elements 49, which are located on the outer peripheral surface of a cover of a rod 16, the axis of the channel of the rod 42 in the lid of the rod 16 and the center channel of the cylinder 20 can be appropriately combined with each other so that the piston rod 44, which is introduced through the channel of the cylinder 20 can be easily and reliably inserted through the channel of the rod 42.
On the other hand, the cover of rod 16 is inserted through the channel of the cylinder 20 with the other end of the main cylinder 12, while the piston rod 44 is inserted through the channel of the rod 42, and cover the stem 16 is tightened within the channel of the cylinder 20 to the piston 18 (in the direction of arrow A) until such time as the projections 38b is set opposite the lock cha the tee 24 grooves 22b, located in the channel of the cylinder 20. Moreover, after the protrusions 38b will be opposite the retaining portion 24 of the grooves 22b and offset cover stock 16 to one end side of the main cylinder 12, which is the front side of the piston 18 (in the direction of arrow A), shall be adjusted, retaining ring 28b is inserted into the channel of the cylinder 20 and is mounted in an annular groove 26 on the other end side of the main cylinder 12. In this case, the lever sections 86 and clamping sections 88 are deformed in such directions that are pressed to each other by a clamp (not shown)which are inserted into a pair of fixing holes 92, and after the retaining ring 28b will be very close to the annular groove 26, the retaining ring 28b again deformed by unlocking the locking state of the arm sections 86 of the latch, after which the retaining ring 28b will expand due to its elasticity in the radial direction and are fixed inside the annular groove 26.
Accordingly, displacement of the cover shaft 16 inside the main cylinder 12 (in the direction of arrow A) is adjustable in axial direction of the clutch with the projections 38b of the cover rod 16 within the grooves 22b of the channel of the cylinder 20. In addition, the displacement of the cover shaft 16 outside line of the cylinder 12 (in the direction of the arrow) is also regulated by the retaining ring 28b installed in Utri annular groove 26. That is, the cover of rod 16 will be in a fixed state with the other end of the main cylinder 12 and fit in this place, not speaking out the other end of the main cylinder 12.
Similarly, when the front cover 14 and the cover of rod 16 is installed on both ends of the main cylinder 12, a pair of protrusions 38A, 38b engage respectively with the pairs of grooves 22A, 22b, available in the channel of the cylinder 20 of the main cylinder 12, and the locking rings 28a, 28b, which are inserted on the ends of the feed cylinder 20, together with the annular grooves 26, as a result of displacement of the front cover 14 and the cover shaft 16 in the axial direction can be easily and reliably adjusted.
Below are explanations of the description of the operations and the implementation of the work cylinder 10, which was assembled in the manner described. Such explanations will be given with reference to the condition shown in Figure 3, which taken as a starting position, when the piston 18 is displaced to the front cover 14 (in the direction of arrow A).
First, the working liquid is not shown in the drawings, the power source is introduced into the first fluid channel 30. In this case, the second channel 32 is soobshayem atmosphere condition due to a switch not shown of the valve directional control. In the result, the working fluid is injected NR is tri channel of the cylinder 20 from the first hydraulic channel 30 through the supply channel 34, consequently, the piston 18 is pressed against the end cap rod 16 (in the direction of arrow C) of the working fluid introduced between the front cover 14 and the piston 18. In addition, due to the abutment of the elastic damper 72b mounted on the end surface of the piston 18 opposite the end surface of the cap rod 16, the displacement of the piston 18 reaches its end position. While the shock generated by impact will be amortized damper 72b, and such attacks will not have any effect on the piston 18.
On the other hand, when the piston 18 moves in the opposite direction (in the direction of arrow A), the working fluid will be supplied to the second fluid channel 32, while the first fluid channel 30 will move to a different state and will be open to the atmosphere due to the switching action of the directional control valve (not shown). The working fluid is supplied into the cylinder chamber 20 from the second hydraulic channel 32 through the supply channel 34, so that the piston 18 is pressed against the end face of the front cover 14 (in the direction of the arrow A) of the working fluid received between the cap of the rod 16 and the piston 18. In addition, when the displacement of the piston 18, the piston rod 44 and the damper 72A together will shift to the side of the front cover 14, and by adjunction damper 72A, which resists arena the cover 14 in contact with the end surface of the front cover 14, the piston 18 will return to its pre-adjusted initial position. While similarly generated by the adjacency impacts will be depreciated damper 72A, which prevents the impact of such shocks on the piston 18.
In the same way, this made the invention the damper grooves 70A, 70b are arranged respectively along both end surfaces of the piston 18, while the damper grooves 70A, 70b formed of the first grooves 74 which are open on both end surfaces, and second grooves 76, which is adjacent to the first grooves 74 and pass them along. Dampers 72A, 72b posted with the possibility of sliding displacement in the damper grooves 72A, 72b and the second groove 76 formed on the inner surface of the piston 18, entered the guide element 82, the base element 80 is held in the first groove 74 and, accordingly, the dampers 72A, 72b can be easily inserted in the piston 18.
Further, the dampers 72A, 72b can be securely fastened to the piston 18 by using a simple structure in which the damper grooves 70A, 70b are formed on both end surfaces of the piston 18, and the dampers 70A, 70b, which are inserted in the damper grooves 70A, 70b, are the basic elements 80 and guide members 82. Consequently, unlike used in the traditional cylinder fastening damp the EPA dampers 72A, 72b can be fixed by means of simplified construction and low cost.
Moreover, since the dampers 72A, 72b are guide members 82 that extend relative to the base element 80, and the guide members 82 are connected with the second grooves 76, dampers 72A, 72b are protected from displacement in the axial direction (in the direction of the arrows a and b) relative to the piston 18. Consequently, the pair of dampers 72A, 72b, which are mounted on both surfaces of the piston 18 can be freely displaced together with the piston 18.
In addition, since the dampers 72A, 72b surrounded by the inner peripheral surface of the channel of the cylinder 20 in position when the dampers 72A, 72b are installed in the damper grooves 70A, 70b of the piston 18, dampers 72A, 72b may not be displaced along the damper grooves 70A, 70b. That is, a pair of dampers 72A, 72b are usually installed as a single piece with these grooves and cannot be separated from the piston 18 in the outer part of the main cylinder 12.
Moreover, since the dampers 72A, 72b have a rectangular cross-sectional shape and can be moved with the slide relative to the damper grooves 70A, 70b, which is impossible in elastic dampers traditional cylinder, then you can be sure that the area of the surfaces of the dampers 72A, 72b, which are opposite the front cover 14 and the cover of rod 16, dostat is a rule large. The result can be guaranteed a certain shock-absorbing ability of the shock absorption on the piston 18 dampers 72A, 72b.
Although there has been described a case where the above-mentioned hydraulic cylinder 10 dampers 72A, 72b are arranged on both end surfaces of the piston 18, the invention is not limited to this feature. Possible is also the case when the damper grooves formed respectively on the end surfaces of the front cover 14 and the cover of the piston 16 and converted to both end surfaces of the piston 18, which is thereby set the dampers 72A, 72b.
Next, as shown at 11 and Fig, the base element 122 dampers 120A, 120b may include a pair of V-shaped grooves 124, with the first grooves 128 of the piston 126 is formed by a pair of tabs 130, in which are inserted the dampers 120A, 120b so that the V-shaped grooves 124 which engage respectively with the projections 130.
The width of the V-shaped grooves 124 gradually decreases from both end parts of the dampers 120A, 120b so that the narrow Central part of the base element 122 adjacent to the hole 78. On the other hand, the protrusions 130 are generally triangular cross-sectional shape corresponding to the form of V-shaped grooves 124, so that the area facing the holes 78 dampers 120A, 120b, most strongly act in the direction of the dampers 120A, 120b.
Relevant to the military, in a state where the dampers 120A, 120b is installed in the damper grooves 132A, 132b, they can be fixed even more firmly in the piston 126, since the pair of V-shaped grooves 124 is connected respectively with the protrusions 130 of the piston 126. Moreover, even when the dampers 120A, 120b are pushed in the direction of the damper grooves 132A, 132b, dampers 120A, 120b is separated from the damper grooves 132A, 132b, because V-shaped grooves 124 are connected with the protrusions 130 of the piston 126.
The locking rings 28a, 28b, which are fixed, respectively, the front cover 14 and the cover of the rod 16 on the highway of the cylinder 12, is not limited to the above-described configuration, containing protruding section 90 and the locking holes 92 located in intermediate positions on a pair of lever sections 86 to lock the rings.
For example, can also be used shown in Fig - Fig retaining rings 150A, 150b, which contain a fixing hole 154 formed respectively on both ends of the lever section 152.
Such retaining rings, as shown in Fig - Fig, have U-shaped cross section, made of metal and mounted respectively within a pair of annular grooves 26, which are formed in the chamber of the cylinder 20 of the main cylinder 12 (see Fig).
Retaining rings 150A, 150b have a shape corresponding to the shape of the annular grooves 26, and who will win the curved section 156, which is bent to a predetermined radius of curvature, a pair of lever sections 152, running in a straight line from both ends of the curved section 156, and a pair of clamping sections 158 located at the ends of the lever sections 152, which are curved with a predetermined radius of curvature and separated from each other by a predetermined distance. Clamping sections 158 are located on opposite sides of the curved section 156, between clamping and curved sections has a lever section 152 and the retaining rings 150A, 150b have a certain elasticity, which ensures that the divergence of the pair of clamping sections 158 from each other in opposite directions at a predetermined distance. The curved section 156 has the same structure as the curved section 84, forming the locking rings 28a, 28b, and therefore detailed explanation of this feature is ignored.
Clamping section 158 contain convex portion 160, which protrude towards the inner side surface of the clamping sections 158 and are located against each other. Fixing hole 154 formed respectively on each of the convex part 160. In addition, the introduction of a not shown lock in a pair of fixing holes 154 and offset convex parts 160 together with the locking holes 154 in the direction towards each other can elastically deform the lever section 12 and clamping section 158, that they will converge among themselves, when connected to a curved section 156.
In addition, the retaining rings 150A, 150b are inserted respectively in the annular grooves 26 after the front cover 14 and the cover of rod 16 will be installed on the chamber of the cylinder 20 of the main cylinder 12. Accordingly, the front cover 14 and the cover of rod 16 are fixed by having them protrusions 38A, 38b and retaining rings 150A, 150b. When the front cover 14 and the cover of rod 16 do not extend beyond the end surface of the main cylinder 12.
Dampers 72A, 72b, used in the hydraulic cylinder 10 in accordance with the present invention is not limited to the above examples made of the invention and can be used in a variety of other configurations, but without deviating from the essential features and essence of the present invention.
1. The supporting structure of the damper, located in the hydraulic cylinder (10) for attaching the damper (72A, 72b, 102a, 102b), which weakens the shock that occurs when the junction of the piston (18) to the lid (14, 16)mounted on the ends of the housing cylinder (12), the said piston (18) is installed inside the cylinder (12) and is shifted in the above-mentioned hydraulic cylinder (10) working fluid, while the supporting structure of the damper contains:
the damper groove (70A, 70b, 104a, 104b, 132a, 132b), formed at the end surface of the above paragraph is RSNA (18), addressed to said lid (14, 16) and perpendicular to the axis of the above-mentioned piston (18), while the damping groove (70A, 70b, 104a, 104b, 132a, 132b) contains:
first the groove (74, 110, 128), outdoor of the said end surface; and
the second groove (76, 106), located adjacent to the first-mentioned groove (74, 110) and extending with regard to him;
the above-mentioned damper (72A, 72b, 102a, 102b), containing:
basic element (80, 98, 122), entered in the above-mentioned first groove (74, 128); and
the guide element (82, 94), entered in the above-mentioned second groove (76, 106) and expanding on the said base element(80, 98, 122).
2. The supporting structure of the damper according to claim 1, characterized in that the said guide member (82, 94) comprises a pair of guide elements located on both sides of the base element(80, 98, 122).
3. The supporting structure of the damper according to claim 2, characterized in that the said guide element (94) includes a rounded portion (96), which is converted to the base element (98), and mentioned rounded portion (96) includes a groove (108)formed in said second groove (106) on the end surface of the above-mentioned piston (18a).
4. The supporting structure of the damper according to claim 3, characterized in that the base element (98) includes a wedge-shaped part (100), which post is i.i.d. decreases in width in the direction of said guide element (94), with the first mentioned groove (110), which introduced the mentioned basic element (98)has a tapered shape that gradually decreases in width in the direction of the said end surface corresponding to the aforementioned wedge-shaped part (100).
5. The supporting structure of the damper according to claim 1, characterized in that the damper (72A, 72b) is in the above-mentioned hydraulic cylinder (10), containing the said piston (18)having an elliptical cross-sectional shape, and the said cylinder body (12) has a camera of the cylinder (20) with elliptical cross-sectional shape in which you have entered the above mentioned piston (18)and cover (14, 16) with elliptical cross-sectional shape, which close both ends of the mentioned chamber of the cylinder (20).
6. The supporting structure of the damper according to claim 1, characterized in that the base element (122) comprises a pair of V-shaped grooves (124), which are set into the side of the base element (122), and the aforementioned V-shaped grooves (124) coupled respectively with a pair of protrusions (130)formed in said first groove (128).
7. The supporting structure of the damper placed in the cylinder (10) for mounting damper, which helps absorb the shock that occurs at the junction of the piston (18) to the lid (14, 16)mounted on the end of the housing cylinder (12)and the said piston (18) is recovered within the said housing cylinder (12) and is shifted in the above-mentioned hydraulic cylinder (10) working fluid; while the supporting structure of the damper contains:
the damper groove formed on the end surface of the said cover (14, 16)facing said piston (18) and perpendicular to the axis of the said cover (14, 16); moreover, the damper groove includes a first groove, outdoor of the said end surface; and
a second groove located adjacent to the first-mentioned groove and extending relative to the first mentioned groove;
the said damper includes:
basic element included in said first groove; and
the guide element included in said second groove and extending relative to the base element.
Slider-crank mechanism of internal combustion engine // 2362930
SUBSTANCE: invention is related to stop ring used in hydraulic cylinder to fix cover to cylinder body. Stop ring is installed in hydraulic cylinder, having chamber with elliptical shape of cross section, and fixes covers that are installed at ends of mentioned body of cylinder. Stop ring comprises bent section, which is installed on surface of internal wall of cylinder chamber and is bent along surface of internal wall of cylinder chamber, a pair of straight sections that diverge from both ends of bent sections and passing parallel to each other, and a pair of convex sections installed on mentioned straight sections and having openings.
EFFECT: invention provides for improved reliability of hydraulic cylinder chamber cover fixation with elliptical shape of cross section.