Bypass device for a torque converter

Abstract

Bypass device (6) for a torque converter (1), wherein the bypass device (6) is configured to allow or prevent torque transmission from a front cover (2) to a turbine wheel (4) of the torque converter (1), the bypass device (6) comprising: a coupling area (24) arranged between the front cover (2) and the turbine wheel (4), the coupling area (24) comprising a plurality of coupling plates (28, 29a, 29b) and a piston (30) for pressing the coupling plates (28, 29a, 29b) together, the coupling area (24) being configured to allow or block the transmission of torque; and a damping mechanism (25) configured for transmitting torque from the coupling area (24) to the turbine wheel (4) and for absorbing and damping torque vibration, wherein the damping mechanism (25) comprises: an input side element (44, 44', 55) into which the torque from the coupling area (24) is introduced; an output side element (45) that is connected to the turbine wheel (4); a plurality of elastic elements (46) which elastically connect the input side element (44, 44', 55) and the output side element (45) in a direction of rotation; an intermediate element (47, 47') that causes at least two of the plurality of elastic elements (46) to act in series, wherein the intermediate element (47, 47') can rotate relative to the input side element (44, 44', 55) and the output side element (45); and a limiting element (48, 54, 58) that prevents the intermediate element (47, 47') from moving in both the radial and axial directions, wherein the limiting element (48, 54, 58) is mounted on the inlet side element (44, 44', 55), wherein the limiting element (48, 54, 58) is attached at its inner circumferential region to the input side element (44, 55) of the damping mechanism (25), wherein the limiting element (48, 54, 58) has at its outer circumferential region a radial limiting region (48b, 54a, 58b) and an axial limiting region (48c, 54b, 58c), wherein the radial limiting region (48b, 54a, 58b) prevents the intermediate element (47, 47') from moving in the radial direction by supporting an inner circumferential end of the intermediate element (47, 47'), and wherein the axial limiting region (48c, 54b, 58c) prevents the intermediate element (47, 47') from moving axially, wherein the plurality of elastic elements (46), the intermediate element (47, 47') and both the radial limiting area (48b, 54a, 58b) as well as the axial limiting area (48c, 54b, 58c) of the limiting element (48, 54, 58) are arranged on an outer circumferential side of the coupling area (24).

Description

TECHNICAL AREA

[0001] The present invention relates to a bypass device, in particular a bypass device for a torque converter configured for the transmission or interruption of the transmission of torque from a front cover to a turbine wheel of the torque converter. TECHNICAL BACKGROUND

[0002] A torque converter is often equipped with a bypass device for the direct transmission of torque from a front cover to a turbine wheel. The bypass device comprises: a piston that can be frictionally connected to the front cover; a drive plate attached to the piston; a plurality of torsion springs supported by the drive plate; and a driven plate connected to the piston in the direction of rotation by the plurality of torsion springs. The driven plate is attached to the turbine wheel.

[0003] To increase the coupling capacity in the bridging device, a bridging device of the so-called multi-plate type has already been proposed, in which a large number of coupling plates are used (see PTL 1).

[0004] When a torque is transmitted through the bridging device, the stiffness and strain of the torsion springs must be reduced at a certain angle of rotation to dampen and mitigate variations in the torque applied to the torque converter by a drive motor. With this in mind, a device as described in PTL 2 was proposed. Pairs of torsion springs, forming a damping mechanism, act in series via an intermediate element.

[0005] In a bridging device according to PTL3, an inertial mass is rotatably arranged between a front cover and a turbine, the inertial mass being connected to the front cover via a first damping spring and to the turbine via a second damping spring. The damping springs are arranged radially outward from a maximally bulged area on the outside of the turbine. This is intended to achieve a wider range of low vehicle speeds in which the bridging device is directly connected, while improving damping reduction and maintaining a compact design.

[0006] According to PTL4, a disc-shaped piston of a bridging device is connected to a driven plate, which is connected to a turbine, by means of a torsion spring. A spring retainer, which can rotate relative to the piston and the driven plate, is radially fixed by means of a driving plate. The spring retainer has a radially outer support area for supporting the spring.

[0007] In a bridging device according to PTL5, a coupling plate is mounted between a piston and the front cover. The coupling plate is rotationally fixed to a drive plate, which is rotatably connected via torsion springs to an output plate that is attached to a turbine. DOCUMENT LIST PATENT LITERATURE PTL 1: JP 2010-48291 A PTL 2: JP 2002-89657 A PTL3: JP 2009-041662 A PTL4: JP 2002-048217 A PTL5: JP 2007-132522 A OVERVIEW OF TECHNICAL PROBLEMS

[0008] The intermediate element described in PTL 2 can rotate within the damping mechanism relative to both the input and output elements. Furthermore, in PTL 2, the intermediate element is prevented from moving in both the axial and radial directions by an input-side plate attached to a piston forming the bridging device.

[0009] Particularly in a multi-plate bridging device, as described in PTL1, the piston and the damping mechanism are arranged far apart. In a bridging device with such a design, the intermediate element cannot be supported by the piston and the input-side plate of the damping mechanism. Furthermore, the axial space of a coupling component is increased in the multi-plate bridging device, which means that not enough axial space can be created for the mechanism to support the intermediate element and limit its movement.

[0010] It is an object of the present invention to provide a space-saving mechanism for limiting the movement of an intermediate element, particularly in a bridging device in which the piston and the damping mechanism are arranged in positions far apart from each other. PROBLEM SOLVING

[0011] The invention provides a bridging device according to claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

[0012] A bypass device for a torque converter according to the present invention is a device configured to allow or prevent torque transmission from a front cover to a turbine wheel and comprising a clutch section and a damping mechanism. The clutch section is arranged between the front cover and the turbine wheel, comprises a plurality of clutch plates and a piston for pressing the plurality of clutch plates against each other, and is configured to allow or prevent torque transmission. The damping mechanism is configured to transmit torque from the front cover to the turbine wheel and absorbs and dampens torsional vibration.Furthermore, the damping mechanism comprises: an input side element into which the torque from the coupling area is introduced; an output side element connected to the turbine; a plurality of elastic elements that elastically connect the input and output side elements in one direction of rotation; an intermediate element; and a limiting element. The intermediate element can rotate relative to the input and output side elements, causing at least two of the plurality of elastic elements to act in series. The limiting element is mounted on the input side element and prevents the intermediate element from moving in both a radial and axial direction.

[0013] In the device, when the clutch is engaged (power transmission state), the torque from the front cover is introduced from the clutch area into the damping mechanism and, with absorption and damping of a torque oscillation, is transmitted to the turbine. Within the damping mechanism, the torque is introduced into the input element and transmitted to the output element via several elastic elements. At least two of the elastic elements act in series via the intermediate element. This allows for a large damper torsion angle and low stiffness. Furthermore, the intermediate element is prevented from moving in both the axial and radial directions by the limiting element mounted on the input element of the damping mechanism.

[0014] Here, the intermediate element is designed such that it is prevented from moving in both the axial and radial directions by the limiting element mounted on the input-side element of the damping mechanism. This allows the device to be designed in a more space-saving manner in the axial direction. The present invention is therefore effective in a multi-plate bridging device where the coupling area occupies a relatively large space.

[0015] Preferably, the intermediate element is formed by an annular plate element. Furthermore, the limiting element is attached to the output side element of the damping mechanism at its inner circumferential region and has a radial limiting region and an axial limiting region at its outer circumferential region. The radial limiting region prevents the intermediate element from moving in the radial direction by supporting an inner circumferential end of the intermediate element. The axial limiting mechanism prevents the intermediate element from moving in the axial direction by positioning an inner circumferential end region of the intermediate element between the axial limiting region and the input side element of the damping mechanism.

[0016] Similar to the above, the space occupied by the entire device can be reduced by reducing the space in the axial direction.

[0017] Preferably, the intermediate element comprises: an inner circumferential end region extending along the inlet-side element; a lateral support region supporting the front-cover-side lateral regions of the elastic elements; and an outer support region extending from the outer circumferential end of the lateral support region towards the turbine wheel and supporting outer circumferential regions of the elastic elements. Furthermore, the limiting element is attached to the inlet-side element of the damping mechanism at its inner circumferential region.The limiting element has a radial limiting region on its outer circumferential area, which prevents the intermediate element from moving in the radial direction by supporting an inner circumferential end of the intermediate element; and an axial limiting region, which prevents the intermediate element from moving in the axial direction by placing the lateral support region of the intermediate element between the axial limiting region and the elastic elements.

[0018] Similar to the above, the space occupied by the entire device can be reduced by reducing the space in the axial direction.

[0019] A bridging device for a torque converter according to the present invention comprises the plurality of elastic elements, the intermediate element and both the radial limiting area and the axial limiting area of ​​the limiting element arranged on an outer circumferential side of the coupling area.

[0020] Preferably, the boundary element is formed by a plate element whose thickness is less than the thickness of the intermediate element.

[0021] Here, the thickness of the boundary element is less than that of the intermediate element. For this reason, the axial space can be further reduced.

[0022] Preferably, the intermediate element is formed by an annular plate element. Furthermore, the limiting element has a radial limiting region and an axial limiting region, both of which are formed as part of the input side element of the damping mechanism. The radial limiting region prevents the intermediate element from moving in the radial direction by supporting an inner circumferential end of the intermediate element, whereas the axial limiting region prevents the intermediate element from moving in the axial direction by positioning an inner circumferential end region of the intermediate element between the axial limiting region and the input side element of the damping mechanism.

[0023] Here, the limiting element is prevented from moving in both the radial and axial directions by a part of the input side element of the damping mechanism, so that further space can be saved in the axial direction. Advantageous effects of the invention

[0024] As described above, in a bridging device equipped with a multi-plate coupling area in which a piston and a damping mechanism are arranged in positions far apart, a mechanism for limiting an intermediate element can be designed in a more space-saving manner. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a partial sectional view of a torque converter equipped with a lock-up clutch according to an embodiment of the present invention; Fig. Figure 2 is an enlarged view of a coupling area of ​​the Fig. 1 bridging device shown; Fig. Figure 3 is an enlarged view of a damping mechanism that is in Fig. 1 bridging device shown; Fig. Figure 4 is a schematic representation of a boundary element according to a further embodiment of the present invention; Fig. Figure 5 is a schematic representation of a boundary element according to a further embodiment of the present invention. DESCRIPTION OF DESIGN FORMS Overall design of the torque converter

[0025] Fig. Figure 1 is a vertical sectional view of a torque converter 1 in which a first exemplary embodiment of the present invention is applied. The torque converter 1 is a device for transmitting torque from a crankshaft of a drive engine to an input shaft of a transmission. Fig. 1. The drive motor (not shown in the figure) is located on the left side, while the transmission (not shown in the figure) is located on the right side. A line OO in Fig. 1 designates a rotation axis of the torque converter 1.

[0026] The torque converter 1 mainly comprises a front cover 2, three types of impellers (a pump impeller 3, a turbine impeller 4 and a guide wheel 5) and a bridging device 6. Front cover

[0027] The front cover 2 is a disc-shaped element with a central hub 8 welded to its inner circumferential end. The central hub 8 is a cylindrical element extending axially and inserted into a central opening in the crankshaft (not shown in the figures).

[0028] It should be noted that the front cover 2 is designed such that it can be connected to the crankshaft of the drive machine via a flexible plate, although this is not shown in the figures. In other words, a plurality of bolts are attached to the drive-machine-side surface of the outer circumferential region of the front cover 2 and are aligned at equal intervals in the circumferential direction. The outer circumferential region of the flexible plate is fastened to the front cover 2 by nuts that are screwed onto the bolts 9.

[0029] An outer-circumferential tubular section 2a is formed in the outer circumferential region of the front cover 2 and extends axially towards the gearbox. The pump impeller 3 is welded to the front end of the outer-circumferential tubular section 2a. Thus, the front cover 2 and the pump impeller 3 form a fluid chamber filled internally with operating oil. pump wheel

[0030] The impeller 3 mainly comprises an impeller housing 10 and a plurality of impeller vanes 11 attached to the inside of the impeller housing 10. Furthermore, the outer circumferential front end region of the impeller housing 10 is welded to the front cover 2, as described above. It should be noted that a tubular section is formed at an inner circumferential end region of the impeller hub 10 and extends towards the gearbox. Turbine wheel

[0031] The turbine wheel 4 is arranged opposite the pump wheel 3 in the fluid chamber. The turbine wheel 4 mainly comprises: a turbine wheel housing 14; a plurality of turbine wheel blades 15 attached to the inside of the turbine wheel housing 14; and a turbine wheel hub 16 arranged at the inner circumferential end region of the turbine housing 14. The turbine wheel housing 14 and the turbine wheel hub 16 are fastened by a plurality of rivets 17.

[0032] The turbine wheel hub 16 comprises: a disc-shaped flange region 16a to which the inner circumferential end region of the turbine housing 14 is attached; a first tubular section 16b in a shape extending from the inner circumferential region of the flange region 16a towards the gearbox; and a second tubular section 16c in a shape extending in the opposite direction to the tubular region 16b. As described above, the turbine housing 14 is further secured radially by rivets 17 to an approximately central region of the flange region 16a. Furthermore, a wedge opening is formed in the inner circumferential region of the second tubular region 16c, which engages with a keyed hub formed at the front end of the gearbox input shaft. guide wheel

[0033] The guide vane 5 is a mechanism arranged between the inner circumferential region of the pump impeller 3 and that of the turbine 4, and serves to regulate the flow of operating oil returning from the turbine impeller 4 to the pump impeller 3. The guide vane 5 is cast in one piece from resin, an aluminum alloy, or the like. The guide vane 5 mainly comprises an annular guide vane housing 20 and a plurality of guide vane blades 21 formed on the outer circumferential surface of the guide vane housing 20. The guide vane housing 20 is connected to a stationary shaft (not shown in the figures) via a one-way coupling. Bridging device

[0034] The bridging device 6 is a device arranged between the front cover 2 and the turbine wheel 4 and serves for the direct transmission of power from the front cover 2 to the turbine wheel 4. The bridging device 6 comprises: a coupling section 24 arranged between the front cover 2 and the turbine wheel 4; and a damping mechanism 25 configured for the transmission of torque from the coupling section 24 to the turbine wheel. Clutch area

[0035] The coupling area 24 corresponds to the hydraulically actuated multi-plate type and is configured for transmitting torque from the front cover 2 to the damping mechanism 25 or for blocking torque transmission between the front cover 2 and the damping mechanism 25. As shown in the enlarged view of Fig. As shown in Figure 2, the coupling area 24 comprises a coupling input element 26, a coupling output element 27, a drive plate (first coupling plate) 28, two driven plates (second coupling plates) 29a and 29b and a piston 30.

[0036] The coupling input element 26 is annular and comprises: a disk-shaped fixing area 26a; an outer tubular area 26b extending from the outer circumferential end of the first fixing area 26a towards the transmission; and an inner tubular area 26c extending from the inner circumferential end of the fixing area 26a towards the transmission. The fixing area 26a is welded to the surface of the front cover 2 located on the side of the turbine wheel 4. A plurality of convex-concave areas are formed on the inner circumferential surface of the outer tubular area 26b and extend axially and at predetermined intervals in the circumferential direction.

[0037] The coupling output element 27 is annular and comprises: a disk-shaped disc section 27a; and a tubular section 27b extending from the inner circumferential end of the disk section 27a towards the drive machine. The disk section 27a is fastened by rivets 32 to elements forming the damping mechanism 25. A plurality of grooves are formed on the tubular section 27b and extend axially and oriented at predetermined intervals in the circumferential direction.

[0038] The drive plate 28 is annular. A plurality of teeth are formed at the outer circumferential end of the drive plate 28 such that these teeth engage with the concave-convex regions of the outer tubular region 26b of the coupling input element 26. In such a design, the drive plate 28 can move axially with respect to the coupling input element 26, but cannot rotate relative to it.

[0039] The two driven plates 29a and 29b are annular in shape. A plurality of teeth are formed at the inner circumferential ends of the two driven plates 29a and 29b, so that the teeth can mesh with the plurality of grooves of the tubular area 27b of the coupling output element 27. In this design, both driven plates 29a and 29b can move axially with respect to the coupling output element 27, but cannot rotate relative to it. Furthermore, annular friction elements are attached to both surfaces of the driven plate 29a, which is located on the side of the turbine wheel 4. In addition, an annular friction element is attached to the side surface of the driven plate 29b, which is located on the side of the front cover 2 and is located on the side of the turbine wheel 4.It should be noted that no friction element is mounted on the surface of the driven plate 29b located on the side of the front cover 2.

[0040] An annular support ring 34 is attached to the far side of the driven plate 29a, which faces the turbine wheel 4. The support ring 34 has an inner diameter that is approximately the same as the inner diameter of the friction element mounted on the driven plate 29. Furthermore, a plurality of teeth are formed on the outer circumferential end of the support ring 34, which can engage with the convex-concave regions of the outer tubular region 26b of the coupling input element 26. In this design, the support ring 34 can move axially with respect to the coupling input element 26, but cannot rotate relative to the coupling input element 26. It should be noted that a snap ring 35 is provided on the side of the support ring 34 facing the turbine wheel 4 to prevent the support ring 34 from moving towards the turbine wheel 4.The snap ring 35 engages with an annular groove formed by the outer tubular area 26b of the coupling input element 26.

[0041] The piston 30 is arranged between the front cover 2 and the driven plate 29b on the inner circumferential side of the clutch input element 26. The piston 30 is annular in shape, and its outer circumferential surface is slidably held by and along the inner circumferential surface of the inner tubular section 26c of the clutch input element 26. A sealing element 37 is mounted on the outer circumferential surface of the piston 30 and provides a seal between the piston 30 and the clutch input element 26. Furthermore, a tubular section 30a is formed at the inner circumferential end of the piston 30 and extends towards the transmission. The inner circumferential surface of the tubular section 30a of the piston 30 is slidably held by and along a piston support element 38.

[0042] As the Fig. 1 and Fig. As shown in Figure 2, the piston support element 38 is a disc-shaped element with a ring shape. The piston support element 38 is circumferentially welded to the front cover 2 at a multitude of positions. It should be noted that Fig. Figure 1 shows the areas of the piston support element 38 that are attached to the front cover 2, whereas grooves 38a (shown by a dashed line), which extend through the piston support element, are formed on the other areas of the piston support element 38 that are not attached to the front cover 2. The operating oil is guided from the inner circumferential side through the grooves 38a into the space formed between the piston 30 and the front cover 2. An outer tubular area 38b is formed at the outer circumferential end of the piston support element 38 and extends towards the drive motor, whereas an inner circumferential tubular area 38c is formed at the inner circumferential end of the piston support element 38 and extends towards the transmission.As described above, the outer tubular section 38b is a support area for the piston 30, and a sealing element 40 is mounted on this section to provide a seal between the piston 30 and the piston support element 38. Furthermore, a sealing element 42 is mounted on the outer circumferential surface of the first tubular section 16b of the turbine wheel hub 16, so that the sealing element 42 provides a seal between the piston support element 38 and the turbine wheel hub 16. Damping mechanism

[0043] As in Fig. As shown in Figure 3, the damping mechanism 25 comprises: an input plate 44 to which the coupling output element 27 of the coupling area 24 is attached; an output plate 45 which is attached to the turbine wheel housing 14 of the turbine wheel 4; a plurality of torsion springs 46; an intermediate element 47 and a limiting plate 48. It should be noted that Fig. 3 merely represents the damping mechanism 25 and the related components taken from the bridging device 6.

[0044] The input plate 44 is ring-shaped and comprises: a disk area 44a; spring receiving areas 44b formed at the outer circumferential end of the disk area 44a; and a support area 44c formed at the inner circumferential end of the disk area 44a and extending towards the drive machine. As described above, the output element 27 is attached to the disk area 44a by rivets 32. The spring receiving areas 44b comprise: spring support areas 44d for supporting the inner circumferential sides of the torsion springs 46; and engagement areas 44e for supporting the end faces of the torsion springs 46.

[0045] The output plate 45 engages with both circumferential ends of each pair of torsion springs 46, which are configured such that their torsion springs act in series. Accordingly, the torque introduced by the input plate 44 is transmitted via the torsion springs 46 to the output plate 45 and further to the turbine wheel 4.

[0046] The multiple torsion springs 46 are arranged in the spring mounting areas 44b of the input plate 44. In this case, a total of eight torsion springs 46 are provided in pairs of two torsion springs.

[0047] The intermediate element 47 is an element that causes the two torsion springs 46 of each pair to act in series. The intermediate element 47 has a ring shape and an inverted L-shaped cross-section. The intermediate element 47 is arranged on the outer circumferential side of the coupling area 24 (specifically the coupling input element 26) and has an inner circumferential end region 47a, a lateral support region 47b, and an outer support region 47c. The inner circumferential end region 47a extends along the disc area 44a of the input plate 44 to the inner circumferential side. The lateral support region 47b extends from the inner circumferential end region 47a to the outer circumferential side and supports the drive-machine-side (on the side of the front cover 2) lateral regions of the torsion springs 46.Furthermore, claws (not shown in the figures) supporting the end faces of each pair of torsion springs 46 are formed and shaped such that they extend from the lateral support areas 47b towards the transmission (i.e., towards the turbine wheel 4). The outer support area 47c extends from the outer circumferential end of the lateral support area 47b towards the transmission and supports the outer circumferential areas of the torsion springs 46.

[0048] The limiting plate 48 is formed by a plate whose thickness is less than that of the intermediate element 47. The limiting plate 48 is annular and has a locking area 48a, a radial limiting area 48b, and an axial limiting area 48c. The locking area 48a is disc-shaped and is fastened to the coupling output element 27 and the coupling input plate 44 by rivets 32, with its inner circumferential area positioned between these elements 27 and 44. The radial limiting area 48b extends from the outer circumferential end of the locking area 48a toward the drive machine, while the axial limiting area 48c is curved from the front end of the radial limiting area 48b to the further outer circumferential side. The inner circumferential end of the intermediate element 47 is in contact with or near the radial limiting area 48b.Furthermore, the inner circumferential end region 47a of the intermediate element 47 is connected between the axial limiting region 48c and the input plate 44 and held there.

[0049] In the above construction, the intermediate element 47 is prevented from radial movement by the radial limiting area 48b of the limiting plate 48 and from axial movement by the axial limiting area 48c of the limiting plate 48.

[0050] Furthermore, an inlet plate support element 50 is mounted on the inner circumferential side of the inlet plate 44. The inlet plate support element 50 is ring-shaped, and its inner circumferential end region is fastened to the turbine wheel hub 16, together with the turbine wheel housing 14, by rivets 17. A plate support region 50a and a stop region 50b are formed in the outer circumferential region of the inlet plate support element 50. The plate support region 50a is tubular and supports the inner circumferential surface of the support region 44c of the inlet plate 44. The stop region 50b is formed by a front end of the plate support region 50a that is bent towards the outer circumferential side. The stop region 50b allows the front end of the support region 44c of the inlet plate to contact the stop region 50b and prevents the damping mechanism 25 from moving towards the drive motor.

[0051] As in Fig. As shown in Figure 3, a stop ring 52 is attached to the drive-machine-side surface of the turbine wheel housing 14. The stop ring 52 is annular and has a plurality of inner stop claws 52a and a plurality of outer stop claws 52b. The inner stop claws 52a are formed by cutting into the inner circumferential region of the stop ring 52 and bending the cut areas outwards towards the drive machine. The outer stop claws 52b are formed by cutting into the outer circumferential region of the stop ring 52 and bending the cut areas outwards towards the drive machine.

[0052] The inner stop claws 52a can be brought into contact with the surface of the inlet plate 44 located on the side of the turbine wheel 4, thereby preventing the damping mechanism 25 as a whole from moving towards the turbine wheel. Furthermore, the outer stop claws 52b are inserted into the stop grooves 44f formed on the inlet plate 44. Each stop groove 44f is a longitudinal groove with a predetermined circumferential length that is larger than the circumferential length of each outer stop claw 52b. Accordingly, the torsional angle of the damping mechanism 25 is limited to a predetermined angular range. How it works

[0053] When the bridging device 6 is disengaged, the operating oil is not directed into the space formed between the piston 30 and the front cover 2. In this case, the torque is transmitted from the front cover 2 via the fluid from the pump impeller 3 to the turbine impeller 4.

[0054] If, however, operating oil is directed into the space formed between the piston 30 and the front cover 2, the piston 30 is moved towards the gearbox. Consequently, the drive plate 28 and the driven plates 29a and 29b are pressed together.

[0055] This brings the bridging device 6 into the clutch state, and the torque from the front cover 2 is transmitted to the damping mechanism 25 in the following way and in the order mentioned, namely via the clutch input element 26; the drive plate 28 and the driven plates 29a and 29b; and the clutch output element 27.

[0056] In the damping mechanism 25, the torque introduced from the clutch area 24 into the input plate 44 is transmitted via the torsion springs 46 and the output plate 45 to the turbine wheel 4 and via the turbine wheel hub 16 further to the transmission input shaft.

[0057] In the bridging device described above, the intermediate element 47 is prevented from moving in both the radial and axial directions by the limiting element 48. This stabilizes the actuation. Furthermore, the damping mechanism 25 is prevented from moving radially by the input plate support element 50 and from moving axially by the input plate support element 50 and the stop ring 52. This also stabilizes the actuation. Features

[0058] In the present exemplary embodiment of the invention, the intermediate element 47 is prevented from moving by the limiting element 48, as described above, so that the space occupied by the bridging device 6 can be reduced. In particular, the limiting element 48 is designed with a thickness that is less than that of the intermediate element 47. This allows for greater space savings. Especially in a multi-plate coupling area, there is a tendency towards a greater axial space requirement. By using the limiting element in the present exemplary embodiment, the axial space can be reduced. Further examples of implementation

[0059] The present invention is not limited to the exemplary embodiment described above. Numerous changes and modifications are possible without departing from the scope of the present invention. (1) Fig. Figure 4 shows another embodiment of a boundary element. A Fig. The limiting element 54 shown in Figure 4 is formed by bending a portion of an input plate 55 that forms the damping mechanism. In other words, a radial limiting region 54a is formed by bending a portion of the input plate 55 towards the drive motor, and an axial limiting region 54b is further formed by bending the front end of the radial limiting region 54a towards the outer circumferential side. The inner circumferential end of the intermediate element 47 is supported by the radial limiting region 54a, while the inner circumferential end region of the intermediate element 47 is inserted and held between the axial limiting region 54b and a portion of the input plate 55, i.e., a region extending towards the outer circumferential side.

[0060] It should be noted that the axial limiting region 54b is formed partially, but not completely, in the circumferential direction on the inlet plate 55. Furthermore, during assembly, the intermediate element 47 is positioned such that its inner circumferential end region does not overlap with the axial limiting region 54b. Subsequently, the intermediate element 47 is rotated relative to the axial limiting region 54b and thus positioned within the area defined in the Fig. Positioned in the 4th shown state.

[0061] (2) Fig. Figure 5 shows a further example of the limiting element. An intermediate element 47' of this example has a similar construction to that described in the preceding exemplary embodiment. The intermediate element 47' is annular and has an inverted L-shaped cross-section. The intermediate element 47' has an inner circumferential end region 47a', a lateral support region 47b', and an outer support region 47c'.

[0062] In the present exemplary embodiment, a limiting plate 58 is formed by a plate whose thickness is less than that of the intermediate plate 47'. The limiting plate 58 is annular and has a fixing area 58a, a radial limiting area 58b, an axial limiting area 58c, and a connecting area 58d. The fixing area 58a is disc-shaped, and its inner circumferential area is fastened to the input plate 44' by rivets 59. The radial limiting area 58b is designed such that it extends from the outer circumferential end of the fixing area 58a toward the drive unit (toward the front cover 2). The connecting area 58d has a shape that curves from the front end of the radial limiting area 58b to the further outer circumferential side of the drive unit.The axial limiting region 58c has a shape that is curved from the front end of the connecting region 58d approximately parallel to the inlet plate 44' and extends to the outer circumferential side.

[0063] In such a construction, the inner circumferential end of the intermediate element 47' is arranged in contact with or near the outer circumferential surface of the radial limiting region 58b. Furthermore, the lateral support region 47b' of the intermediate element 47' is positioned between the axial limiting region 58c and the torsion springs 46 and held there.

[0064] In the construction described above, the intermediate element 47' is prevented from radial movement by the radial limiting area 58b of the limiting plate 58 and from axial movement by the axial limiting area 58c of the limiting plate 58.

[0065] It should be noted that the remaining construction is similar to that of the exemplary embodiments described above, which are shown in the Fig. Figures 1 to 3 are shown.

[0066] Even with the present exemplary embodiment, it is possible to achieve similarly advantageous effects as with the advantageous embodiments described above. INDUSTRIAL APPLICABILITY

[0067] The present invention provides a space-saving mechanism for limiting an intermediate element in a bridging device equipped with a multi-plate coupling area in which a piston and a damping mechanism are arranged in positions far apart from each other. REFERENCE MARK 1 torque converter 2 Front cover 2a outer circumferential tubular area 3 Pump wheel 4 turbine wheel 5 Guide wheel 6 Bridging device 8 hub 9 bolts 10 Pump impeller housings 11 pump impeller blades 14 turbine wheel housings 15 turbine wheel blades 16 Turbine wheel hub 16a disc-shaped flange area 16b first tubular section 16c second tubular section 17 rivets 20 guide wheel housings 21 Guide vane 24 Clutch area 25 Damping mechanism 26 Coupling input element 26a Area of ​​determination 26b outer tubular area 26c inner tubular area 27 Coupling output element 27a Disc area 27b tubular area 28 Drive plate (first clutch plate) 29a, 29b driven plate (second coupling plate) 30 pistons 30a tubular area 32 rivets 34 Support ring 35 Snap ring 37 Sealing element 38 Piston support element 38a Nut 38b outer tubular area 38c inner circumferential pipe area 40 sealing element 42 Sealing element 44, 44', 55 Entrance panel (entrance side element) 44a Disc area 44b Spring mounting area 44c support area 44d spring support area 44e Intervention area 44f stop groove 45 Output plate (output side element) 46 Torsion spring (elastic element) 47, 47' Intermediate element 47a inner circumferential end area 47b lateral support area 47c outer support area 48, 54, 58 Boundary element 48a, 58a Scope of application 48b, 54a, 58b radial limiting area 48c, 54b, 58c axial limiting area 50 entrance plate support element 50a Plate support area 50b stop area 52 Stop ring 52a inner stop claw 52b outer stop claw 58d connection area

Claims

[1] Bypass device (6) for a torque converter (1), wherein the bypass device (6) is configured to allow or prevent torque transmission from a front cover (2) to a turbine wheel (4) of the torque converter (1), the bypass device (6) comprising: a coupling area (24) arranged between the front cover (2) and the turbine wheel (4), the coupling area (24) comprising a plurality of coupling plates (28, 29a, 29b) and a piston (30) for pressing the coupling plates (28, 29a, 29b) together, the coupling area (24) being configured to allow or block the transmission of torque; and a damping mechanism (25) configured for transmitting torque from the coupling area (24) to the turbine wheel (4) and for absorbing and damping torque vibration, wherein the damping mechanism (25) comprises: an input side element (44, 44', 55) into which the torque from the coupling area (24) is introduced; an output side element (45) that is connected to the turbine wheel (4); a plurality of elastic elements (46) which elastically connect the input side element (44, 44', 55) and the output side element (45) in a direction of rotation; an intermediate element (47, 47') that causes at least two of the plurality of elastic elements (46) to act in series, wherein the intermediate element (47, 47') can rotate relative to the input side element (44, 44', 55) and the output side element (45); and a limiting element (48, 54, 58) that prevents the intermediate element (47, 47') from moving in both the radial and axial directions, wherein the limiting element (48, 54, 58) is mounted on the inlet side element (44, 44', 55), wherein the limiting element (48, 54, 58) is attached at its inner circumferential region to the input side element (44, 55) of the damping mechanism (25), wherein the limiting element (48, 54, 58) has at its outer circumferential region a radial limiting region (48b, 54a, 58b) and an axial limiting region (48c, 54b, 58c), wherein the radial limiting region (48b, 54a, 58b) prevents the intermediate element (47, 47') from moving in the radial direction by supporting an inner circumferential end of the intermediate element (47, 47'), and wherein the axial limiting region (48c, 54b, 58c) prevents the intermediate element (47, 47') from moving axially, wherein the plurality of elastic elements (46), the intermediate element (47, 47') and both the radial limiting area (48b, 54a, 58b) as well as the axial limiting area (48c, 54b, 58c) of the limiting element (48, 54, 58) are arranged on an outer circumferential side of the coupling area (24). [2] Bridging device (6) for a torque converter (1) according to claim 1, wherein the intermediate element (47) is formed by an annular plate element and wherein the axial limiting region (48c, 54b) prevents the intermediate element (47) from axial movement by inserting an inner circumferential end region (47a) of the intermediate element (47) between the axial limiting region (48c, 54b) and the input side element (44, 55) of the damping mechanism (25). [3] Bridging device (6) for a torque converter (1) according to claim 1, wherein the intermediate element (47') comprises: an inner circumferential end region (47a') extending along the input side element (55); a lateral support region (47b') supporting the front cover-side lateral regions of the elastic elements (46); and an outer support region (47c') extending from an outer circumferential end of the lateral support region (47b') towards the turbine wheel (4), wherein the outer support region (47c') supports outer circumferential regions of the elastic elements (46) and wherein the axial limiting region (58c) prevents the intermediate element (47') from moving in the axial direction by inserting the lateral support region (47b') of the intermediate element (47') between the axial limiting region (58c) and the elastic elements (46). [4] Bridging device (6) for a torque converter (1) according to one of claims 1 to 3, wherein the limiting element (48, 54, 58) is formed by a plate element whose thickness is less than the thickness of the intermediate element (47, 47'). [5] Bridging device (6) for a torque converter (1) according to claim 1, wherein the intermediate element (47) is formed by an annular plate and wherein the limiting element (54) has a radial limiting region (54a) and an axial limiting region (54b), wherein both the radial limiting region (54a) and the axial limiting region (54b) are formed on a region of the input side element (55) of the damping mechanism (25), wherein the radial limiting region (54a) prevents the intermediate element (47) from moving in the radial direction by supporting an inner circumferential end of the intermediate element (47), and wherein the axial limiting region (54b) prevents the intermediate element (47) from moving in the axial direction by having an inner circumferential end region (47a) of the intermediate element (47) between the axial limiting region (54b) and the input side element (55) of the damping mechanism (25). is switched on.

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