Source: http://www.google.com/patents/US6244401?ie=ISO-8859-1
Timestamp: 2014-07-14 09:06:14
Document Index: 370149573

Matched Legal Cases: ['art 19', 'art 22', 'art 22', 'art 27', 'art 27', 'art 27', 'art 27', 'art 27', 'art 27', 'art 27', 'art 37', 'art 22', 'art 27', 'art 122', 'art 122', 'art 122', 'art 122', 'art 117', 'art 122', 'art 117', 'art 118', 'art 118', 'art 127', 'art 118', 'art 127', 'art 127', 'art 127', 'art 127', 'art 127', 'art 127', 'art 218', 'art 222', 'art 218', 'art 218', 'art 227', 'art 227', 'art 227', 'art 227', 'art 227', 'art 227', 'art 227', 'art 218', 'arts 318', 'art 318', 'art 318', 'art 322', 'art 322', 'art 322', 'art 322', 'arts 318', 'art 318', 'art 318', 'arts 518', 'arts 518', 'arts 518', 'art 727', 'art 778', 'arts 778', 'art 1078']

Patent US6244401 - Force transmitting apparatus - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign in<nobr>Advanced Patent Search</nobr>PatentsA torque-transmitting apparatus for motor vehicles includes a hydrokinetic torque converter with a housing connected to the driving shaft of an engine. The housing contains a pump and a turbine, the latter arranged to drive an input shaft of a power train. At least one damper is arranged in the power...http://www.google.com/patents/US6244401?utm_source=gb-gplus-sharePatent US6244401 - Force transmitting apparatusAdvanced Patent SearchPublication numberUS6244401 B1Publication typeGrantApplication numberUS 09/305,504Publication dateJun 12, 2001Filing dateMay 5, 1999Priority dateMay 6, 1998Fee statusPaidAlso published asDE19920542A1, US6439361, US6695110, US20010008198, US20020125093Publication number09305504, 305504, US 6244401 B1, US 6244401B1, US-B1-6244401, US6244401 B1, US6244401B1InventorsStephan Maienschein, Marc Meisner, Rudolf H�nemannOriginal AssigneeLuk Getriebe-Systeme GmbhExport CitationBiBTeX, EndNote, RefManPatent Citations (4), Referenced by (29), Classifications (16), Legal Events (4) External Links: USPTO, USPTO Assignment, EspacenetForce transmitting apparatusUS 6244401 B1Abstract A torque-transmitting apparatus for motor vehicles includes a hydrokinetic torque converter with a housing connected to the driving shaft of an engine. The housing contains a pump and a turbine, the latter arranged to drive an input shaft of a power train. At least one damper is arranged in the power flow path between the turbine and a rotary output element of the apparatus. The damper has an input member constrained to rotate with the turbine and an output member connected to the rotary output element. The input member and the output member are rotatable relative to each other against the opposing forces of energy-storing devices arranged between the input member and the output member. The input member has a radially outer portion in form-locking engagement with the turbine.
What is claimed is: 1. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member having a radially outer portion in form-locking engagement with the turbine.
11. The apparatus according to claim 6, wherein the axial plug-in connection is formed between a radially extending element and an axially extending element, and wherein further the radially extending element has an outward-directed toothed profile and the axially extending element has an axially directed toothed profile.
29. The apparatus according to claim 2, wherein the input member and the output member are connected by engagement means evenly distributed along a circle, said engagement means comprising in one of said members a set of elongated holes with a dimension corresponding at least to a maximum angle of relative rotation between said members, and comprising in the other of said members a set of matching connector means engaging said elongated holes, whereby the input member and the output member are allowed to rotate relative to each other.
36. The apparatus according to claim 34, wherein the rotation-limiting stop includes a flange-like part arranged on the rotary output element, at least one extremity of the flange-like part being axially engaged in at least one opening formed along a perimeter of the input member, the opening having an angular width that determines a range of rotary play.
37. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, the input member and the turbine being at least indirectly form-lockingly connected to each other by means of an axial plug-in connection.
40. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, wherein the lockup clutch is controlled by an axially moveable control piston and the control piston in an engaged state of the lockup clutch forms a plenum chamber with an essentially tight separation from a chamber formed by the housing.
41. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, wherein the lockup clutch is controlled by an axially moveable control piston, and the control piston is axially movable relative to the housing and has an outside perimeter along which the control piston is sealed against the housing.
42. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to at an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, wherein the lockup clutch is controlled by an axially moveable control piston and the control piston has a form-locking engagement with the housing.
44. The apparatus according to claim 43, wherein the axially oriented profiles are formed by alternating ridges and grooves in the shape of ring segments that are distributed over the outside perimeter where the ridges of the control piston engage the grooves of the housing.
45. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, wherein the lockup clutch has at least one friction-lining carrier with at least one friction lining, and the lockup clutch is controlled by an axially movable control piston and the friction-lining carrier is interposed axially between the control piston and a pressure plate and has an axial attachment to the housing along a radially outer portion of the pressure plate.
47. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, wherein the lockup clutch has at least one friction-lining carrier with at least one friction lining, and the lockup clutch is controlled by an axially moveable control piston and the friction-lining carrier is centered on the control piston by means of lugs protruding axially from the friction-lining carrier towards the housing and engaging a shoulder that is formed on the control piston and extends in an axial direction away from the friction-lining carrier.
48. Apparatus for transmitting torque comprising a hydrokinetic torque converter with at least one housing connectable to a driving shaft of a prime mover, the housing containing and imparting torque to at least one pump and also containing a rotary turbine connectable to and arranged to drive an input shaft of a power train, and with further at least one damper arranged in a power flow path between the turbine and a rotary output element of the apparatus, the damper having an input member constrained to rotate with the turbine and an output member connected to the rotary output element, the input member and the output member being rotatable relative to each other at least against the opposition of a restoring force of energy-storing devices arranged between them, and the input member is connected to an engageable and disengageable lockup clutch, wherein a lateral part constituting the input member is bent along an inside perimeter to extend axially towards the lockup clutch and has an axially directed toothed profile in form-locking engagement with a radially inward-directed toothed profile at an inner perimeter of the lockup clutch.
In accordance with one presently preferred embodiment of the improved torque-transmitting apparatus, the damper at its outside perimeter is directly or indirectly connected to the turbine through a positive rotational constraint. This connection may be free of play relative to coaxial rotational displacements but may allow an axial displacement of the turbine and the input member of the damper relative to each other. For example, the connection may be axially displaceable by means of an axial plug-in connection with the damper rigidly attached to a hub. The problem can further be solved through a torque-transmitting apparatus with a damper whose connection to the turbine shell or turbine, or to the hub, is rotationally fixed both along an inside and outside perimeter, while in the axial direction the connection is fixed only along one perimeter, either on the hub or on the turbine shell, so that axial stresses are relieved by an axial displacement at the axially nonrestrained connection.
As already described above, the lockup clutch is connected through one of its components to the input member of the damper. In one embodiment, the connecting part may be the control piston itself in the manner described above, in which case the piston may be connected to lateral parts of the input member by rivets, weld joints or similar means. A further embodiment employs a ring-shaped friction-lining carrier that may form an axial plug-in connection by virtue of an appropriately shaped lateral portion. In this case the friction-lining carrier has a form-fitting engagement with the input member of the damper, e.g., by means of internal teeth at its inside perimeter and, e.g., an axially oriented profile on the lateral part of the input member. The advantages of axial plug-in connections in accordance with the invention are that they compensate for axial displacements and facilitate the manufacturing process by virtue of a modular configuration, because systems of this kind can be built by plug-in assembly without further resort to fastening undertakings such as, e.g., welding or riveting, thus allowing the use of work stations that are not equipped with the respective infrastructure.
A further advantageous embodiment may include a flange-like part in the shape of an annular disk that adjoins along its inside perimeter the turbine shell and conforms to the shape of the turbine shell towards the inside in the radial direction, is attached in the shape-conforming portion as described above and then curves into the axial direction. The profile facing away from the turbine shell in axial direction, e.g., a toothed profile, engages in closed recesses distributed over the circumference of a radially directed lateral part and in this manner forms an axial plug-in connection. To form this plug-in connection, it may be necessary for the axially directed toothed profile to pass through the output member before engaging the input member of the damper, given that the output member is interposed axially between the turbine and the input member. For this purpose, the output member has a circular arrangement of elongated holes matching the number of teeth. The angular width of the holes corresponds to the maximum angular displacement of the input and output members relative to each other so that at the same time the elongated holes in combination with the axially directed teeth of the axially oriented flange-like part that is connected to the turbine form at least one stop for the angular displacement of the damper.
In an advantageous arrangement, the axially extending flange-like part can itself be in the form of a hub that carries the turbine, the latter being connected to the hub by, e.g., welding or riveting. The hub carrying the turbine, in turn, can be seated on a further hub that performs the function of the rotary output element and is attached to the transmission shaft. The axially extending flange-like part has a profile established, e.g., by axially oriented teeth that extend into enclosed cutouts corresponding to the number of teeth in the flange whereby an axial plug-in connection is formed. Depending on the configuration of the damper, it may be necessary with this embodiment, too (as described above), to provide in the output member an appropriate arrangement of elongated holes which, in combination with the axially directed profile of the axially oriented flange for the axial plug-in connection, can function as stops for the relative displacement between the input and output members of the damper. The output member, being a radial extension of the hub that is attached to the transmission shaft, may also be configured as a separate flange-like part, in which case the flange needs to be centered on the hub and attached through a rotationally fixed connection.
It can be advantageous to provide the individual damper stages with displacement properties that depend on the direction from which the torque is introduced. Thus, the damper system may be designed to function in two stages in the �pull� mode and in one stage in the �push� mode. In this manner, the damper characteristic may be adapted to the possibility of hard transient peaks in the torque-flow that are introduced from the �push� side, i.e., from the input shaft of the transmission, in which case, e.g., the soft damper stage is bypassed completely and the firm damper stage is effective instantly. The bypass can accomplished by means of limit stops that block angular displacement against the drive direction in the input and output members of the damper stage that is inactive in the push mode.
Further in the interest of optimizing cost, the disk-shaped parts may take on additional functions. For example, as mentioned already, one or more disk-shaped parts may form a chamber for the energy storing devices, or they may contain the axial plug-in connection between the damper and the turbine, and/or they may perform other functions.
It is advantageous to provide displacement-limiting stops insofar as a damper or either some or all of the damper stages can be bypassed, so that the damper or the damper stages can be protected from wear. This may apply particularly in the case of wear-prone versions with storage devices that, e.g., contain arc-shaped springs, permit large angular displacements, and/or are exposed to strong shock loads. To guard against premature failure, it is advantageous if initially one damper stage is totally bypassed by means of displacement-limiting stops, while the second stage is either not bypassed at all or only at a later point. When a damper or a damper stage reaches its limit stop, the torque that previously entered into the energy-storing device is transmitted through the stop directly to the output member of the bypassed damper or damper stage. It may also be advantageous to provide different angular displacement limits in the damper device and its damper stages depending on the direction of the torque, i.e., whether the torque works in the pull or push direction, respectively. Thus, it may be advantageous, for example, to provide limit stops in such a manner that a damper stage is entirely bypassed in the costing mode. Likewise, there may be advantages to a configuration in which, e.g., one damper stage works only in the coasting direction while the other stage works only in the pull direction.
The housing 2 comprises a shell 4 adjoining the driving shaft or the combustion engine and a further shell 5 axially distant from the driving shaft and attached to the housing shell 4 by means of a weld 2 a. The two housing shells 4 and 5 are connected and sealed at their radially outer portions by a welded connection 6. In the illustrated embodiment, the housing shell 5 simultaneously serves as the outer shell of the pump 7. This is accomplished by connecting the vane portions 8 to the housing shell 5 in a manner known manner per se. A turbine 10 is interposed axially between the pump 7 and the radially extending wall 9 of the housing shell 4. A stator 11 is provided between the radially interior portions of the pump 7 and the turbine 10.
The output hub or rotary output element 14 is non-rotatably connected, e.g., welded or caulked, to the flange-like output member 17 of the torque-elastic damper 13. The input member 18 of the torque-elastic damper 13 is at its outer perimeter bent in the axial direction towards the turbine and forms an axially oriented flange-like part 19 with a rim of axially directed teeth 20. At its interior perimeter the input member 18 is bent in the axial direction towards the housing shell 4 and has a rim of axially directed teeth 21 so that the input member 18 transmits the torque flow through form-locking connections to the lockup clutch 13 and the turbine 10 by means of the toothed rims 20, 21. For this purpose, a radially oriented flange-like part 22 is attached to the turbine 10 by a weld 24 along its inner perimeter to the outside of the turbine shell 23. The flange-like part 22 along its outside perimeter has a toothed rim 26 and thereby forms an axial plug-in connection 78 to the input member 18 of the damper 13.
Input member 18 and output member 17 in the axial space between them enclose a flange-like intermediate part 27 which simultaneously constitutes the output member of the first damper stage 28 a and the input member of the second damper stage 28 b. Input member 18, output member 17 and intermediate part 27 are equipped in an essentially known manner with windows for holding the energy-storing devices in the form of coil springs 29, 30 for the two damper stages 28 a, 28 b. In the axial direction, input member 18 is connected to an intermediate part 27, and the intermediate part 27 is connected to the output member 17 by means of fasteners, here in the form of rivets 31, 32. The given range of play by which the parts can rotate relative to each other is limited by the rivets passing through elongated perforations 33, 34 that are arranged along a circle on the input member 18 and on the intermediate part 27, forming stops limiting the extent of travel of the rivets within the holes. As axial retainers for the rivets 31, 32, ring-shaped membranes 35, 36 are provided on the side of the perforations 33, 34. The axial spacing of the input member 18 from the intermediate part 27 and of the intermediate part 27 from the output member 17 is provided by energy-storing devices working in the axial direction between the respective parts, represented in this embodiment by plate springs 44, 45.
The input member 18 at its interior perimeter has a profile shape designed to accommodate the energy-storing devices 30 so as to make optimum use of the available axial space, then turning into the axial direction to form an axially oriented flange-like part 37 with a rim of axially directed teeth 21, where the input member 18 meets the exterior toothed rim 39 of a friction-lining carrier 38 in a form-locking engagement. The friction-lining carrier 38 is centered on a shoulder 41 by means of lugs 40 bent into the axial direction towards the control piston 43 and is faced on both sides with friction linings 42 along its outer perimeter. The friction-lining carrier 38 is interposed in the axial direction between the control piston 43 and the annular disk 46. The latter is attached in a rotation-blocking connection to the housing shell 4, which in the respective area extends in the radial direction. Fastener means such as the impulse weld 48 of the present example are used for the connection. The annular disk 46 has cut-outs 47 distributed along a circle that serve to promote circulation and cooling of the chamber 49 that is formed between the annular disk 46, the control piston 43 and the friction-lining carrier 38. The annular disk is centered on the housing 2 by means of projections 57 arranged in a circle on the housing shell 4.
The embodiment of FIG. 1 illustrates the function of the torque-transmitting apparatus 1 as follows: When the lockup clutch is open, the torque is transmitted by the pump 7 driving the turbine 10, assisted in known manner by the free-wheeling stator 11, through the converter medium that fills the interior space 12 to the flange-like part 22 from where the torque is introduced through an axial plug-in connection formed by the engagement of toothed rims 20, 26 into the input member 19 of the damper 13. When the lockup clutch 15 is closed, the torque-flow path runs through the form-locking engagement of the mutually complementary profiles 54, 56 as well as through the annular disk 46 that is connected to the housing 2. Through the friction engagement of the control piston 43 and the annular disk 46 with the friction linings 42, the torque is introduced into the friction-lining carrier 38 which, by means of the axial plug-in connection with toothed rims 21, 40, transmits the torque to the input member 18. Continuing from the input member 18, the torque flow is smoothed in the damper 13 by means of energy-storing devices 29, 30. The angular displacement of both damper stages 28 a, 28 b is bounded by limit stops 33, 34 and matched to the characteristics and properties of the energy-storing devices 29, 30. If a friction component is needed in the damper 13, i.e., in the damper stages 28 a, 28 b, the energy-storing devices 44, 45 are designed independently of each other in such a manner that a frictional engagement occurs for the first damper stage 28 a between the securing membranes 35, 36 and the input member 17 and/or for the second damper stage 28b between the securing membranes 35, 36 and the intermediate part 27. The output member 17 of the damper 13 transmits the torque to the hub 14 representing the rotary output element of the torque-transmitting apparatus 1, from where the torque is introduced into the transmission shaft.
The axial plug-in connection 178 in this embodiment is formed by the flange-like part 122, which is engaged without play in recesses 120 that are distributed over the circumference of the input member 118. At its interior perimeter, the flange-like part 122 is connected to the shell 123 of the turbine 10�by a weld 124 in the illustrated example. Subsequently, the flange-like part 122 conforms to the shape of the turbine shell at a radial distance, then turns into the axial direction towards damper 113, where its rim of axially oriented teeth 126 engages the openings 120 of the input member 118. The toothed engagement occurs at a radius inside the first damper stage 128 a and outside the second damper stage 128 b where the flange-like part 122 runs in the axial direction and passes through elongated perforations 133 formed along a circle on the intermediate part 117 that is provided as output member of the first damper stage 128 a. Simultaneously, the flange-like part 122 forms the limiting stops for the relative angular displacement between the input member 118 and the intermediate part 117 within the angular range that is delimited by the perforations 133. Thus, the energy-storing devices 129 are bypassed in the case of large angular displacements and are protected against the possibility of harmful effects from high transient peaks in the torque flow. In this embodiment, the energy-storing devices of the first, radially exterior damper stage 128 a are formed in a known manner as arc-shaped springs 129 that are accommodated and retained at their outside radius by a chamber 118 b formed by the peripheral portion of the input member 118 that is bent into the axial direction towards the turbine 110 and by an additional lateral part 118 a enclosing the arc-shaped springs on the side facing the turbine 110. The chamber 118 b has provisions for applying a force in the longitudinal direction of the springs in the shape of protrusions 118 c of the input member 118 and the lateral part 118 a, and wear-protection shells may be interposed between the inside wall at the circumference of the chamber 118 b and the arc-shaped springs 129. The intermediate part 127 representing the output member of the first damper stage 128 a is arranged between the input member 118 and the lateral part 118 a (relative to the axial direction) and is equipped with radially arranged extremities 127 a along its outside perimeter. A further radially extending flange-like part 127 b is connected to the intermediate part 127 through fasteners such as the rivets 131 shown in the present embodiment. With openings 130 a formed in a known manner, the flange-like part together with the intermediate part 127 holds the energy-storing devices of the second damper stage 128 b, in this embodiment represented by short, stiff helix springs 130 distributed evenly along a circle. On the output side, the force introduction into the springs is accomplished with the output member 117 that is interposed in the axial direction between the intermediate part 127 and the flange-like part 127 b with openings 117 a corresponding to the dimensions of the helix springs 130 that in the present embodiment consist of sets of helix springs nested inside each other. At its outer perimeter, the output member 117 has extremities 117 b that are directed outwards in the radial direction and engage openings 127 c in the flange-like part 127 b with play, thus allowing the intended range of angular displacement for the second damper stage 128 b and providing limit stops so that the second damper stage 128 b will be bypassed when the angular displacement of the extremities 117 b within the openings 127 c has reached the limit.
The clutch disks 238 a and an additional annular disk 277 that serves as take-up surface against the clutch force are at their exterior circumference engaged by a rotation-blocking toothed profile and secured axially by a retaining ring 276 a in the exterior disk holder 276 that is welded to the housing 204. The friction-lining carriers 238 are held at their inside perimeter in the interior disk holder 218 e by a rotation-blocking tooth profile. Consequently, when there is friction engagement between the clutch disks 238 a and the friction linings 242, a torque-locked connection is established between the housing 202 and the interior disk holder 218 e, whereby the latter imparts the applied torque to the input member 218. For this purpose, the inner disk holder is shaped as a ring of approximately rectangular cross-sectional profile. The portion of the disk holder that is running in the axial direction towards the housing 204 supports the friction-lining carriers 238, while the second portion, extending outwards in the radial direction, is attached to a radially directed portion of the input member 218 in a non-rotatable connection by means of fasteners such as the rivets 231 that are arranged along a circle in the illustrated example.
As has been described, the input member 218 of the damper 213 takes up the applied torque in the case where the lockup clutch 215 is closed or at least partially engaged. When the lockup clutch 215 is open as well and when it is slipping, the torque (or a portion of the torque when the lockup clutch 215 is slipping) is passed on from the turbine 210 through an axial plug-in connection 278 to the input member 218 in the same manner as was described in the context of FIG. 1, but using the arrangement and functional concept of FIG. 2, where the input member 218 together with the lateral part 218 a forms a chamber 218 b to accommodate the arc-shaped springs 229 with the wear-protection shells 218 d inserted at the contact surfaces. In order to form the axial plug-in connection 278, the axially directed portion of the input member 218 is extended at the outer circumference towards the turbine in such a manner that its axially directed toothed rim 226 can engage the outward-pointing toothed rim 220 of the radially directed flange-like part 222 that is attached to the turbine.
Input member 218 and lateral part 218 a are connected by means of fasteners represented in the present embodiment by the rivets 231 with spacer bolts 231 a to hold them at a fixed distance from each other. Arranged in the space extending in the axial direction between input member 218 and lateral part 218 a is the intermediate part 227 in the shape of a disk-shaped part 227 serving as output member of the first damper stage 228 a and as input member of the second damper stage 228 b. The detail configuration of the disk-shaped part 227 is illustrated in a partial view in FIG. 4.
The FIGS. 3 and 4 show a disk-shaped part 227 with radially directed extremities 227 a arranged at the exterior circumference and serving as force-introduction elements for the arc-shaped springs (FIG. 3). Distributed along a circle of smaller radius in the disk-shaped part are elongated openings 233 through which the rivets 231 pass, permitting relative rotation between the input member and the output member of the first damper stage 228 a within a limited angular range. As soon as the rivets 231 reach the borders of the cutouts 233, the first damper stage 228 a is bypassed and the applied torque is transmitted through the contact points between the rivets 231 and the cutouts 233, whereby the arc-shaped springs are protected against greater amounts of torque and angular displacement. The rest position of the rivets 231 in the illustrated embodiment is not centered within the cutouts 233 (seen in the circumferential direction), meaning that the range of angular displacement is not equal in both directions but is smaller in the �push� direction than in the �pull� direction. In an inventive embodiment not shown in the drawing, the rivets 231 can be in direct contact with the border 233 a of the elongated openings 233 so that this damper stage is being bypassed immediately in the push direction without an angular displacement, thus providing a damper with one active stage in the push direction and two active stages in the pull direction. Distributed over another yet smaller circle in the disk-shaped part are further openings 227 b to hold the energy-storing devices in the form of short helix springs 230 nested inside each other (FIG. 3). At their outer radius, the openings 227 b have flaps 230 a that are bent towards the lockup clutch 215 to secure the helix springs 230 in the axial direction. By means of the rivets 232 passing through holes 227 c (FIG. 4) distributed along a circle of intermediate radius between the openings 233, 227 b, the disk-shaped part 227 is connected to a further flange-like part (227 b) that has openings with flaps (227 c) bent axially towards the turbine to accommodate the helix springs 230. The flange-like part (227 c) is formed into the shape of a cup extending in the axial direction to provide space in the axial dimension between the intermediate part 227 and the flange-like part (227 b) to accommodate the hub 214. The hub 214 is extended radially into a disk shape to serve as output member 217 of the damper 213 and thus of the second damper stage 228 b. To provide space for and couple a force to the helix spring 230, the output member 217 has openings 217 a distributed along a circle so that the hub 217 is rotatable relative to the intermediate part 227 against the restoring force of the helix springs 230. This produces the damping effect of the second damper stage 228 b wherein the range of angular displacement is limited by the play of the bolts 273 in the openings 274.
The input member 218 and the output member 227 of the first damper stage 228 a as well as the input member 227 and the output member 217 of the second damper stage 228 b are elastically clamped against each other by the action of the interposed plate springs 244, 245. Thus, with an appropriate selection of the spring characteristic, a friction effect of a desired magnitude can be generated between the respective input and output members 218, 227 and 227, 217 at the friction surfaces 244 a, 245 a, where the friction surface 245 a is provided by a series of projections distributed along a circle on the lateral part 218 a. FIG. 5 illustrates an embodiment of a damper 313 in single-stage configuration. The torque to be transmitted is introduced into the damper 313 through the two lateral parts 318 a, 318 b that form the input member 318. The contributions to the torque coming from the lockup clutch 315 are introduced into the damper 313 through the toothed rim 321 of the lateral part 318 a of the input member 318. The contributions to the torque coming from the turbine 310 are introduced through the inventive plug-in connection 378 into the input member 318, represented by its lateral part 318 b. In addition, a disk-shaped part 322 is connected by means of rivets 332 with the turbine 310, with the hub 314 (that represents the output element and is connected to the transmission shaft 372 through a toothed profile 316) and with the output member 317. The spacer bolts 332 a are provided to allow an angular displacement of the output member 317 relative to the turbine 310, hub 314 and lateral part 322 within a range that is delimited by the borders of elongated openings 334. The disk-shaped part 322 is engaged in a toothed exterior profile 314 a of the hub 314 without play. At its outer circumference, the disk-shaped part 322 has an exterior toothed rim 326 that forms the play-free plug-in connection 378. Also engaged in the toothed exterior profile 314 a of the hub 314 is the output member 317 of the damper 313, which has a toothed inner perimeter 317 a with an amount of play between the opposing tooth flanks that determines the range of relative angular displacement between the input member and the output member in opposition to the restoring torque of the energy-storing devices 329. It should be noted, however, that the openings 334 and the elongated further openings 333 that are located farther out in the radial direction on the output member 317 will permit a larger amount of angular displacement. Nevertheless, it is conceivable in principle that the maximum amount of angular displacement is determined by any one of the three elements 317 a, 333, 334.
The lateral parts 318 a, 318 b are connected in the axial direction by means of rivets 331 and spacer bolts 331 a and are held at a suitable distance from each other to allow the output member 317 to be arranged within the axial space between them. Interposed between the lateral part 318 a and the output member 317 is a plate spring whose axial thrust determines the intensity of the frictional engagement between the output member 317 and a circular ridge 318 d formed on the lateral part 318 b. FIG. 6 illustrates a further embodiment of a two-stage damper 413 of the kind that was described in the context of FIG. 3, except for the following distinguishing features:
The turbine 410 is supported in a manner permitting relative rotation directly by the hub 414 that forms the output element; it is centered on a shoulder 414 b provided for this purpose and secured in the axial direction by a retaining ring. Thus the hub 210 a shown in FIG. 3 can be omitted. The bolts 473 delimiting the maximum angular displacement between output member 417 and output member 418 are distributed along a circle and configured to protrude directly from the hub 414 into the axial direction, engaging the input member 418 through elongated openings 474 that provide the limiting stops. For the form-locking engagement with the lockup clutch (not shown), a ring 418 e of rectangular profile is attached to the input member 418 by means of rivets (231) that are arranged along a circle. The radially directed portion of the ring 418 e is riveted to the input member 418, while the axially directed portion provides the form-locking engagement with the lockup clutch by means of an axially directed profile.
In a circular area of smaller radius than the friction linings 542, the piston 543 has protuberances 543 a projecting in the axial direction towards the input member 518 where the piston 543 is connected to the lateral parts 518 a and 518 b by means of bolts 543 b in a manner permitting axial but blocking rotational movement of the piston in relation to the input member 518. The two lateral parts 518 a, 518 b are riveted together at their outer circumference (rivets not shown), while the bolts 543 b are inserted into cutouts 518 c on the lateral parts 518 a, 518 b that are open at the outer perimeter and thereby permit an axial play between the piston 543 and the input member 518. The purpose is to prevent negative effects on the axial mobility of the piston 543 from stresses that occur during the engagement and disengagement of the lockup clutch between the piston 543 and the already torque-loaded input member 518.
FIG. 8 illustrates a further possible configuration of a damper device 613 of the inventive torque-transmitting apparatus. In contrast to the damper devices described above, the hub 614 is composed of two hub components 614 a, 614 b. The hub component 614 a is mounted on the transmission shaft 672 in play-free and rotation-blocking connection. The hub component 614 b is supported and aligned on a shoulder 614 d arranged axially on the hub component 614 a on the side towards the transmission. The hub component 614 b is secured axially by means of a retaining ring 614 c. The turbine 610 is firmly connected with the hub component 614 b, e.g., by welding or keying. To form a meshing engagement with play between the first and second hub components 614 a, 614 b, the second hub component 614 b has axially directed projections 673 distributed along its circumference, which engage openings 674 of the hub component 614 a. The dimension of the openings 674 in the circumferential direction is such that the projections 673 in concert with the openings 674 permit a desired amount of relative angular displacement between the turbine 610 and the hub component 614 a, with the damper 613 being interposed between them. The output member 617 of the damper device 613 is arranged axially between the two hub components 614 a, 614 b, centered on the hub component 614 a and rotationally tied to it by means of the keyed connection 614 e. The output member 617 rests against the hub component 614 a along a series of projections distributed on a circle or a circular ridge 614 f protruding in the axial direction. At locations that correspond to the openings 674, the flange-like output member 617 of the damper device 613 has openings 675 that are engaged by the projections 673 of the hub component 614 b. It is advantageous if the openings 675 are wider in the circumferential direction than the openings 674, so that the limits of angular play are determined by the openings 674. This prevents the torque from entering the hub component 614 a through the keyed connection 614 e, so that the latter does not have to be dimensioned for the torque loads that would occur in that case. The function of the further components of the damper device 613 is otherwise comparable with the other damper devices that have been described above.
In contrast to the hub 214 and the output member 217 being configured together as one piece as in FIG. 3, the dampers 713 a-d of FIGS. 9-12 have output members 717 and hubs 714 in two-piece configuration, in which the output members 717 are sheet metal stampings attached to and centered on the hub 714 in a rotation-blocking connection, e.g., by shrink-fitting. To accommodate the energy-storing devices of the second damper stage, the disk-shaped output members 717 have window-shaped openings 717 a distributed along a circle. The disk-shaped output members 717 limit the angular displacement of the second damper stage by means of radially directed extremities 717 b distributed along the circumference, which are engaged with the required amount of angular play in corresponding openings of the disk-shaped part 727 b that serves as input member of the second damper stage.
In the dampers 713 a, 713 c of the FIGS. 9 and 11, respectively, the input members 718 a, 718 c of the damper that transmit an applied torque from the converter lockup clutch 715 and/or from the turbine 710 to the damper 713 a, 713 c are of single-piece configuration, i.e., they have at their inner circumference an axially directed extension 778 a, 778 c with a hprofile 780 a, 780 b for a rotation-blocking engagement of the disks 742 a, 742 b. The profile 780 a (FIG. 9) is impressed into the exterior circumference of the extension 778 a, while the profile 780 c (FIG. 11) is formed by axially oriented openings distributed over the circumference of the extension 778 c for a rotation-blocking engagement of the correspondingly profiled disks 742 b. The dampers 713 b, 713 d of FIGS. 10, 12 have an input member 718 b, 718 d firmly connected, preferably riveted as shown here, to the flange-like part 778 b, 778 d of L-shaped crosssection. The flange-like parts 778 b, 778 d have profiles 780 b, 780 d corresponding to the extensions 778 a, 778 c of FIGS. 9, 11 for a rotation-blocking connection with the disks 742 a, 742 b of the converter lockup clutch 715.
The damper 813 is attached to the turbine shell 823 by means of a weld seam or spot welds 822 a using essentially known welding methods such as, e.g., induction welding, laser welding, impulse welding, or other suitable welding methods. It is to be understood that any other fastening method such as riveting, as well as self-locking connections, could also be used advantageously. In the illustrated embodiment, a connector flange 822�or alternatively an arrangement of connector lugs in the shape of circular segments distributed over a circumference�is attached, e.g., welded, to the turbine shell 823. The axially directed extension 820 of the input member 819 is slipped over the connector flange 822 or the connector lugs and then attached as described above. It can be advantageous if in the attachment process the connector flange 822 is centered on the turbine and the input member 819 is centered on the connector flange.
The turbine 810 is supported through a turbine hub 873 on an axially projecting shoulder 814 b of the hub 814. The turbine hub 873 has limited rotational play relative to the hub 14 and is axially secured by a retaining ring 814 c. The angular displacement of the turbine 810 relative to the hub 814, i.e., the working range of the damper 813, is limited by axially directed projections 873 a distributed along a circle on the turbine hub 873 that are engaged with angular play in the exterior toothed profile 814 a of the hub 814. It is to be understood that the toothed interior rim 817 a of the output member 817 and the projections 873 a of the turbine hub 873 do not have to be arranged side by side as shown in FIG. 13 but may instead be one above the other for the benefit of minimizing the overall axial dimensions, in which case it is advantageous if the projections 873 a are arranged inside the radius of the toothed rim 817 a. FIG. 14 illustrates a damper 913 that has been modified in comparison to the damper 813 of FIG. 13 in that the disk-shaped input member 927 b of the second damper stage is shaped at its interior periphery in such a manner that by means of an axially directed extension 927 c, the damper 913 can be centered on the exterior toothed profile 914 a of the hub 914. By means of the centering feature 988, the first damper stage 928 a can be centered on the second damper stage 928 b. The axially and rotationally fixed connection of the input member 918 to the turbine shell (not shown) can thus be made with a tighter tolerance, e.g., according to the embodiment of FIG. 15.
An alternative to the solution shown in FIG. 13 for attaching the damper 813 to the turbine shell 823 by means of a connector flange 822 is illustrated in the detail view of FIG. 15. The rim 920 a of the axially directed extension 920 of the input member 918 of the damper is adapted to the shape of the turbine shell 923 of the turbine 910 and attached along a circle by a continuous weld seam or individual spot welds 922 a. FIG. 16 shows a partial section of a further embodiment of a torque-transmitting apparatus device 1001 that is similar to the embodiment of FIG. 13. Modifications that deviate from the embodiment of FIG. 13 are in the hub area, including a hub 1014 that is also shown in the detail view of FIG. 17.
As may be seen in FIGS. 16 and 17, the two form-locking connections for the transmission of the torque from the damper 1013 through its output member 1017, and from the turbine 1010 through the turbine hub 1073, to the hub 1014 and from there through the toothed-profile connection 1016 to the transmission shaft are spatially separated from each other. At its exterior circumference, the hub 1014 has an outward-facing profile, such as the illustrated toothed rim 1014 a, that meets the complementary interior profile 1017 a of the output member 1017 in a form-fitting engagement that is preferably free of play and permits axial displacement. Inside of the toothed rim of the hub 1014 are window-shaped openings 1014 b distributed along a circle, shown here in an arrangement of four, but arrangements of two or six openings may also be advantageous. The axially directed projections 1073 a of the turbine hub 1073 pass through the window-shaped openings 1014 b and establish a positive engagement with a maximum play angle a-b (amounting to, e.g., 10� to 70� in the case where four openings are used), between the hub 1014 and the turbine hub 1073 that is rotatable and axially constrained on the hub 1014, whereby the maximum angular working range a-b of the damper 1013 is being determined in an advantageous manner. For reasons of structural integrity, the openings 1014 b are widened and rounded in both radial directions in the vicinity 1014 c of the contact areas for the projections 1073 a. The toothed rim profile 1014 a is interrupted in the circumference segments 1014 d adjacent to the radial enlargements 1014 c. The axial fixation of the damper 1013 is modified slightly in comparison to the embodiment 801 of FIG. 13 in that, unlike the connector flange 822 of FIG. 13, the connector flange 1022 is not fitted to the radial shape of the turbine shell 1023 and then continued in an outward radial direction. Rather, the connector flange 1022 has a planar, radially outward-directed shape with a taper 1022 b at the contact surface to the turbine shell 1023 and is connected to the latter preferably at its inner perimeter through weld seams or a string of evenly distributed spot welds 1022 c, 1022 d. The connection 1022 a between the connector flange 1022 and the input member 1018 of the damper 1013 is made in the same manner as in the embodiment 801 shown in FIG. 13.
In analogous manner, the rivet bolts 1032 connecting the input member 1077 of the second damper stage 1013 b (which also represents the output member of the first damper stage 1013 a) with the disk-shaped part 1078 restrict the angular displacement of the second damper stage 1013 b as they perform the function of rotation-limiting stops for the radially directed extremities 1017 e on the circumference of the output member 1017, whereby the range of relative rotation between the input members 1077, 1078 and the output member 1017 is determined by the amount of play between the rivet bolts 1032 and the extremities 1017 e. Preferably, the ranges between stops for the first and second damper stages 1013 a, 1013 b as well as for the entire damper are coordinated in such a manner that the individual damper stages 1013 a, 1013 b reach their stops at a point before the limit angle of the entire damper has been attained by the projections 1073 a reaching the end of their play. For specific applications it may further be advantageous if the first damper stage is stopped before the second stage or vice versa.
It must be understood that features and functions described for individual embodiments of the torque-transmitting apparatus can also be advantageously applied in the rest of the embodiments, regardless of whether or not they are being shown, even if these features and functions have not been described in detail in the context of the respective embodiment and that, therefore, such features and functions are considered to be included in the coverage of all embodiments to which they are applicable.
Patent CitationsCited PatentFiling datePublication dateApplicantTitleUS4138003 *Aug 12, 1977Feb 6, 1979General Motors CorporationVibration damper for a torque converter lock-up clutchUS4347717 *Jun 29, 1981Sep 7, 1982Borg-Warner CorporationTwo-stage torsional vibration damperUS5667042 *Apr 11, 1995Sep 16, 1997Luk Lamellen Und Kupplungsbau GmbhTorque transmitting apparatus with hydrokinetic torque converterUS5975261 *Jun 15, 1998Nov 2, 1999Daimlerchrysler AgArrangement of a 2-path torsion damper unit and a clutch in a hydrodynamic torque converter* Cited by examinerReferenced byCiting PatentFiling datePublication dateApplicantTitleUS6431335 *Jul 13, 2000Aug 13, 2002Mannesmann Sachs AgHydrodynamic torque converterUS6439361 *Mar 13, 2001Aug 27, 2002Luk Getriebe-Systeme GmbhTorque-transmitting apparatusUS6508345 *Nov 1, 2000Jan 21, 2003Yutaka Giken Co., Ltd.Lockup clutch for torque converterUS6508346 *Oct 16, 2000Jan 21, 2003Ford Global Technologies, Inc.Torque converter assemblyUS6695110 *May 3, 2002Feb 24, 2004Luk Getriebe-Systeme GmbhTorque-transmitting apparatusUS6814195Dec 4, 2002Nov 9, 2004Yutaka Giken Co., Ltd.Lockup clutch for torque converterUS6988601 *Apr 15, 2004Jan 24, 2006Zf Sachs AgTorque converterUS7017724 *Sep 10, 2003Mar 28, 2006Aisin Aw Co., LtdClutch assemblyUS7077253 *Nov 6, 2003Jul 18, 2006Luk Lamellen Und Kupplungsbau Beteiligungs KgTorque converterUS7143879 *Oct 27, 2004Dec 5, 2006Zf Friedrichshafen AgTorsional vibration damperUS7207888 *Nov 12, 2001Apr 24, 2007ValeoTorsional vibration damping device for motor vehicle clutchUS7654373 *Sep 6, 2006Feb 2, 2010Luk Lamellen Und Kupplungsbau Beteiligungs KgTorque transmission deviceUS7699150Feb 27, 2007Apr 20, 2010Zf Friedrichshafen AgHydrodynamic clutch deviceUS7708126 *Aug 6, 2003May 4, 2010Valeo EmbrayagesHydrokinetic coupling device intended, in particular, for a motor vehicleUS7837018 *Jul 11, 2008Nov 23, 2010Exedy CorporationLock-up damperUS8047344 *Oct 21, 2006Nov 1, 2011Schaeffler Technologies Gmbh & Co. KgTorsional vibration damper and hydrodynamic torque converter device for an automotive drive trainUS8127905Oct 24, 2008Mar 6, 2012Schaeffler Technologies AG & Co. KGSeries damper with hysteresis in one damperUS8135525Nov 7, 2008Mar 13, 2012Schaeffler Technologies AG & Co. KGTorque converter with turbine mass absorberUS8387764 *Jul 29, 2008Mar 5, 2013Schaeffler Technologies AG & Co. KGTorque converter with piston centered in clutch plateUS8479901 *Apr 23, 2010Jul 9, 2013Schaeffler Technologies AG & Co. KGHydrodynamic torque converterUS8579093 *Aug 13, 2012Nov 12, 2013Schaeffler Technologies AG & Co. KGHydrodynamic torque converterUS8708118Mar 23, 2012Apr 29, 2014Schaeffler Technologies AG & Co. KGTorque converter clutch and damperUS8727086Dec 8, 2011May 20, 2014Schaeffler Technologies Gmbh & Co. KgThree-stage hysteresis for series damperUS20080149444 *Nov 29, 2007Jun 26, 2008Luk Lamellen Und Kupplungsbau Beteiligungs KgTorsional vibration damperUS20100269497 *Apr 23, 2010Oct 28, 2010Luk Lamellen Und Kupplungsbau Beteiligungs KgHydrodynamic torque converterUS20110209964 *May 6, 2011Sep 1, 2011Luk Vermoegensverwaltungsgesellschaft MbhWet clutchUS20120205213 *Oct 5, 2010Aug 16, 2012Zf Friedrichshafen AgWet clutch arrangementDE102008056636A1Nov 10, 2008Jul 23, 2009Luk Lamellen Und Kupplungsbau Beteiligungs KgDrehmomentwandler mit Turbinen-MassentilgerEP1582771A2 *Feb 23, 2005Oct 5, 2005Exedy CorporationFluid transmission apparatus with a lockup clutch* Cited by examinerClassifications U.S. Classification192/3.3, 192/70.17, 192/213.1, 464/68.7International ClassificationF16H45/02Cooperative ClassificationF16H2045/007, F16H2041/246, F16H2045/0226, F16H2045/0247, F16H2045/0231, F16H2045/0278, F16H2045/0284, F16H2045/021, F16H45/02, F16H2045/0294European ClassificationF16H45/02Legal EventsDateCodeEventDescriptionDec 6, 2012FPAYFee paymentYear of fee payment: 12Nov 20, 2008FPAYFee paymentYear of fee payment: 8Nov 30, 2004FPAYFee paymentYear of fee payment: 4Aug 9, 1999ASAssignmentOwner name: LUK GETRIEBE-SYSTEME GMBH, GERMANYFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MAIENSCHEIN, STEPHAN;MEISNER, MARC;HONEMANN, RUDOLF;REEL/FRAME:010155/0243;SIGNING DATES FROM 19990622 TO 19990625RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services©2012 Google