CN107023611B

CN107023611B - Coupling assembly for coupling torsional vibration dampers

Info

Publication number: CN107023611B
Application number: CN201610878457.1A
Authority: CN
Inventors: T·扬茨; S·比希纳
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-10-09
Filing date: 2016-10-08
Publication date: 2020-06-16
Anticipated expiration: 2036-10-08
Also published as: CN107023611A; DE102016218670A1

Abstract

The invention relates to a coupling assembly (24) for coupling a torsional vibration damper (10), comprising: an output part (14) inserted into the receiving channel (18), wherein the output part (14) has a toothing (26) for forming a plug-in toothing; a first flange ring (36) fittable on a first axially inner side (20) of the receiving channel (18); a second flange ring (38) that can be fitted on a second axially inner side (22) of the receiving channel (18) facing the first axially inner side (20); a first tensioning disc (28) facing a first axial side of the output member (14); a second tensioning disk (30) facing the second axial side of the output part (14), wherein the first tensioning disk (28) and/or the second tensioning disk (30) has/have driving projections (32) which are inserted into the tooth spaces of the teeth (26) of the output part (14); and a tensioning spring (34) which can be fitted on the output part (14), the first tensioning disk (28) and the second tensioning disk (30) and which serves to eliminate backlash of the plug connection by a relative rotation of the driving lug (32) relative to the output part (14), wherein the first tensioning disk (28) and the second tensioning disk (30) are partially covered by a first flange ring (36) and a second flange ring (38) as viewed in the axial direction. This makes it possible to realize a torsional vibration damper with a small radial installation space requirement.

Description

Coupling assembly for coupling torsional vibration dampers

Technical Field

The invention relates to a coupling assembly by means of which a torsional vibration damper can be coupled to a drive train of a motor vehicle.

Background

A torsional vibration damper for a drive train of a motor vehicle is known from WO 2012/031582 a1, in the form of a dual mass flywheel, wherein an input element for introducing a torque forms a receiving channel for receiving a bow spring. The projection of the output part is inserted into the receiving channel, so that the arcuate spring can be fitted not only on the input part but also on the output part in order to transmit torque. A friction device having two flange rings is arranged radially inside the bow spring, wherein the flange rings bound the receiving channel radially inward and can slip friction on the receiving channel in order to thereby increase the damping proportion of the spring damper system formed by the torsional damper. The output part has an internal toothing on a radial inner side relative to the friction device, so that the friction clutch can be connected in a rotationally fixed manner by means of a plug-in engagement. In order to be able to eliminate backlash in the plug-in engagement, a tensioning assembly is provided radially inside the friction device, in which tensioning assembly the two tensioning disks can be rotated relative to the output part by means of a tensioning spring. The driving projections of one of the tensioning disks which are inserted into the tooth gaps of the toothing can thereby press the teeth of the component which is immediately following in the direction of the force flow, which are inserted into the toothing, against the teeth of the toothing.

There is a continuing need to reduce the radial installation space requirement of torsional vibration dampers.

Disclosure of Invention

The object of the invention is to indicate measures which enable a torsional vibration damper with a small radial installation space requirement.

According to the invention, this object is achieved by a coupling assembly having the features of claim 1. Preferred embodiments of the invention, which can each be used individually or in combination to describe an aspect of the invention, are given in the dependent claims and the following description.

According to the invention, a coupling arrangement for coupling a torsional vibration damper, in particular a dual mass flywheel, to a drivetrain of a motor vehicle is provided, having: an output part for outputting a torque of the torsional vibration damper, which is inserted into a receiving channel for receiving an energy storage element, in particular designed as a curved spring, wherein the output part has a toothing for forming a plug-in engagement, in particular a plug-in engagement with a clutch assembly for coupling a drive shaft of a motor vehicle engine to at least one transmission input shaft of a motor vehicle transmission; a first flange ring fittable over a first axially inner side of the receiving channel for partially radially bounding the receiving channel; a second flange ring fittable on a second axially inner side of the receiving channel facing the first axially inner side for partially radially delimiting the receiving channel; a first tension disc facing a first axial side of the output member; a second tensioning disk facing the second axial side, wherein the first tensioning disk and/or the second tensioning disk have/has a driving lug which is inserted into a tooth spacing of the toothing of the output part; and a tensioning spring which can be fitted on the output part, the first tensioning disk and the second tensioning disk and is used for eliminating backlash of the plug connection by relative rotation of the driving lug relative to the output part, wherein the first tensioning disk and the second tensioning disk are partially covered by the first flange ring and the second flange ring when viewed in the axial direction.

The input part may form a receiving channel for an energy storage element, in which the energy storage element may be arranged. The receiving channel forms in particular a radially outer wall against which the energy storage element can be applied by centrifugal force. The receiving channel can be closed by a first flange ring and a second flange ring. For this purpose, the first flange ring and the second flange ring may be designed in particular to be movable relative to one another in the axial direction and preferably to be pressed by spring force against the axially inner sides of the receiving channel facing one another. The first flange ring and the second flange ring can thus be parts of a friction device in order to thereby increase the damping portion of a spring damper system formed by a torsional damper. Preferably, the first flange ring and the second flange ring form a labyrinth seal in the radial direction. The first and second flange rings can, for example, prevent grease from escaping from the receiving channel. In this case, the tensioning disk can be arranged in the axial direction, in particular between the flange rings, so that the tensioning disk can be inserted from the radially inner side into the radial region covered by the flange rings. The positioning of the tensioning disk and the tensioning spring can thus be shifted radially outward, so that the toothing of the output part can also be shifted radially outward, as a result of which radial installation space can be saved. At the same time, the toothing of the output part can thus be displaced over a larger radius, as a result of which it is possible to transmit correspondingly larger torques without having to tolerate a significantly increased surface pressure of the toothing. For this purpose, the number of teeth of the toothing can be increased, for example, by means of an increased nominal diameter of the toothing. By the extension of the tensioning disk into the radial region of the flange ring, the tensioning disk, the tensioning spring and the toothing can be displaced radially outward, so that a torsional vibration damper which can transmit an increased torque with a small radial installation space requirement can be realized.

The torsional vibration damper can be designed, for example, as a dual-mass flywheel, the input part of which can be fastened indirectly or directly as a primary mass to a drive shaft of the motor vehicle engine and can be connected via the output part as a secondary mass to a clutch assembly for coupling the drive shaft of the motor vehicle engine to at least one transmission input shaft. The torsional vibration damper can also be designed as an in-disc damper, for example as a component of a clutch disc of a clutch assembly for coupling a drive shaft of a motor vehicle engine to at least one transmission input shaft. In the traction mode of the motor vehicle engine, torque can be introduced into the torsional vibration damper via the input part and can be discharged via the output part. In the propulsion mode of the motor vehicle engine, torque can be introduced into the torsional vibration damper via the output part and can be discharged via the input part. In particular, the input part and/or the output part can optionally rest against the energy storage element in the circumferential direction at a predetermined free angle in order to be able to transmit torque via the energy storage element between the input part and the output part. The relative rotatability of the output member with respect to the input member may be limited by the compressibility of the accumulator element.

The driving lug of the tensioning disk can preferably replace the teeth of the toothing of the output part which would otherwise be provided. During assembly, the next component, for example a clutch assembly, can be connected with sufficient backlash by means of a plug-in engagement in a substantially force-free manner. For this purpose, the tensioning spring can be slightly compressed during assembly and is preferably held in a prestressed state. After assembly, in particular when the drive train is first operated, the tensioning spring can be (preferably automatically) relaxed until the driving lug presses the tooth of a corresponding tooth of the plug-in toothing, which is inserted into one tooth, against the next tooth, so that a backlash and a possible rattling noise of the plug-in toothing can be avoided. The teeth inserted into the teeth of the output part can thus be clamped in the teeth substantially without play in the circumferential direction by means of the respective tensioning disc. The output part is arranged between the first tensioning disc and the second tensioning disc such that one axial side of the output part faces the first tensioning disc and a second axial side of the output part facing away from the first axial side faces the second tensioning disc.

The respective flange ring is in particular produced from a plastic material which, in comparison to the steel/steel frictional contact, has a lower coefficient of friction than the associated inner side of the receiving channel, so that essentially only a relative rotation of the entire coupling assembly relative to the receiving channel takes place. In this way, a relative rotation within the coupling assembly in the tensioned state of the plug-in connection can be avoided. The intentional friction effect of the coupling assembly is therefore essentially only related to the slipping relative rotation of the flange ring on the associated inner side of the receiving channel.

Preferably, the first tensioning disc is connected to the second tensioning disc by means of a bolt. The bolt can in particular be braced against the output part in the circumferential direction, so that the maximum relative rotatability of the tensioning disk relative to the output part can be limited by the bolt. Only a small rotation of the tensioning disk relative to the output part is thereby required in order to be able to establish a plug-in engagement with the other components. In addition or alternatively, the first tensioning disk and/or the second tensioning disk can rest against the first flange ring and/or the second flange ring in the circumferential direction.

In particular, the bolts can preferably rest in the circumferential direction on the first flange ring and/or the second flange ring. The screw can thus act as a driver for the flange ring. In this way, it is ensured that the flange ring can be rotated at the same rotational speed as the output part in the tensioned state of the plug connection. Thus, relative rotation within the coupling assembly may be avoided.

In particular, a first spring element is provided which engages on the first flange ring and the first tensioning disk and/or a second spring element engages on the second flange ring and the second tensioning disk. The damping proportion of the vibratable spring damper system formed by the torsional damper can be intentionally increased by the spring element in order to reduce resonance effects, for example. The damping can be achieved by friction of the flange ring on the respective inner side of the receiving channel. The magnitude of the friction can be suitably adjusted here by the applied normal force provided by the spring element and the contact surface on the friction pair, so that the desired damping effect can be achieved.

Preferably, the first spring element and/or the second spring element is/are designed as a disk spring. The cup spring has a relatively small axial extension. This makes it possible to keep the axial installation space requirement small. In particular, only exactly one spring element is provided, which is designed as a disk spring. In this case, the tensioning disk, which is located further away from the spring element, is pressed directly against the associated flange ring by the spring force exerted by the disk spring, without the need for a further spring element.

Particularly preferably, the first spring element directly contacts the first tensioning disk and/or the second spring element directly contacts the second tensioning disk. In this case, the knowledge is fully utilized that the tensioning disk rotates substantially rotationally fixed with the output part after the backlash has been eliminated and therefore has substantially the same rotational speed as the output part. This prevents the spring element from coming into direct contact with the output part, so that a window for making direct contact of the spring element with the output part does not have to be provided in the tensioning disk arranged between the spring element and the output part. Instead, the spring element is fitted directly on the tensioning disc without contact with the output part. The structure can thus be kept simple and cost-effective.

In particular, the first spring element directly contacts the first flange ring and/or the second spring element directly contacts the second flange ring. This avoids intermediate insertion of components between the flange ring and the spring element.

Preferably, the first flange ring and/or the second flange ring have a maximum radial extension Δ r, wherein the radially outer edge of the tensioning spring has a spacing d in the rest state relative to the smallest radially inner edge of the first flange ring and/or the second flange ring, wherein-0.25 ≦ d/Δ r ≦ 1.00, in particular 0.00 ≦ d/Δ r ≦ 0.50, preferably 0.10 ≦ d/Δ r ≦ 0.30 and particularly preferably 0.20 ≦ d/Δ r ≦ 0.25. The spring element can thereby be displaced very far, in particular radially outward, onto the flange ring without impairing the functionality of the flange ring. Negative values of, for example, -0.25. ltoreq. d/Δ r. ltoreq.1.00 mean that the tensioning spring can even be inserted slightly between the flange rings and, viewed in the axial direction, is partially covered by the flange rings.

Particularly preferably, the first tensioning disk and/or the second tensioning disk have a maximum radial extension Δ R, wherein a radial portion A of the maximum radial extension Δ R is covered in the axial direction by the first flange ring and the second flange ring, wherein 0.00. ltoreq. A/Δ R. ltoreq.0.60, in particular 0.15. ltoreq. A/Δ R. ltoreq.0.50, preferably 0.25. ltoreq. A/Δ R. ltoreq.0.45 and particularly preferably 0.35. ltoreq. A/Δ R. ltoreq.0.40. As a result, the tensioning disk can be displaced very far, in particular radially outward, onto the flange ring without impairing the functionality of the flange ring.

In particular, the tensioning spring can be locked in the installation position in the pretensioned state by a locking device, wherein the locking device can be released in particular by a relative rotation of the output part relative to the input part. The locking device can be closed during assembly, so that the plug connection can be formed by an axial relative movement with substantially no force. After assembly, the locking device can be released in order to tension the plug connection. Suitable locking means are given in particular by the locking possibilities described in WO 2012/031582, the content of which is hereby made part of the present invention.

Particularly preferably, the first tensioning disk and/or the second tensioning disk blocks the tensioning spring in the axial direction. The tension disk can thereby prevent the tension spring from coming out axially.

In particular, the output part and/or the first tensioning disk and/or the second tensioning disk have a window for at least partially receiving the tensioning spring. The tensioning spring can thereby easily come to rest against the output part in the circumferential direction inside the window of the output part in order to transmit torque. Furthermore, the tensioning spring can rotate relative to one another in the interior of the tensioning disk, which is configured as a correspondingly long window in the circumferential direction, without the tensioning disk being entrained. The tensioning disk therefore does not need to be molded on the tensioning spring along the extension in the axial direction, so that a small installation space in the axial direction is achieved.

The invention further relates to a torsional vibration damper, in particular a dual mass flywheel or an in-disc vibration damper, for damping torsional irregularities in a drivetrain of a motor vehicle, having an input part for introducing a torque, wherein the input part forms a receiving channel for receiving an energy accumulator element, in particular in the form of a bow spring, and the torsional vibration damper has a coupling arrangement which can be configured and improved as described above and is partially inserted into the receiving channel. By the extension of the tensioning disk into the radial region of the flange ring of the coupling arrangement, the tensioning disk, the tensioning springs and the toothing can be displaced radially outward, so that a torsional vibration damper which can transmit an increased torque with a small radial installation space requirement can be realized.

The invention further relates to a torsional vibration arrangement for damping torsional irregularities in a drivetrain of a motor vehicle, having a torsional vibration damper, which is designed and improved as described above, and which can be coupled to an engine shaft of a motor vehicle engine, and having a clutch assembly, which is coupled in a rotationally fixed manner via a toothing of an output part, for coupling a drive shaft to at least one transmission input shaft of a motor vehicle transmission. By the extension of the tensioning disk into the radial region of the flange ring of the coupling assembly of the torsional vibration damper, the tensioning disk, the tensioning spring and the toothing can be displaced radially outward, so that a torsional vibration assembly which can transmit an increased torque can be realized.

Drawings

The invention is illustrated below in accordance with preferred embodiments with reference to the accompanying drawings, in which the following features can describe one aspect of the invention, both individually and in combination. In the drawings:

figure 1 shows a schematic cross-sectional view of a torsional vibration damper,

figure 2 shows a schematic cross-sectional view of a coupling assembly of the torsional vibration damper from figure 1,

fig. 3 shows a schematic cross-sectional view of the coupling assembly of fig. 2 along a cross-sectional plane offset in the circumferential direction.

Detailed Description

The torsional vibration damper 10 shown in fig. 1 is designed as a dual-mass flywheel having an input part 12 acting as a primary mass and an output part 14 acting as a secondary mass. The input member 12 may be connected directly or indirectly to an engine shaft of an engine of a motor vehicle. The input part 12 can rest in the circumferential direction against an energy storage element 16, which is designed as a compression spring, in particular as an arc spring, and which in turn can rest in the circumferential direction against the output part 14, which is rotatable in a limited manner relative to the input part 12, in order to be able to transmit the torque introduced via the input part 12 to the output part 14 in a torsional vibration-damped manner. The accumulator element 16 is arranged in a receiving channel 18 formed by the input part 12. The receiving channel 18 has a first inner side facing substantially in the axial direction and a second inner side 22 facing in the opposite axial direction, in particular in the radial region of the output part 14.

The output part 14 is also a part of the coupling arrangement 24, with the aid of which it can be connected to a component that is to be connected in the direction of force flow, in particular a clutch assembly for coupling a drive shaft of a motor vehicle engine to at least one transmission input shaft of a motor vehicle transmission. The coupling arrangement 24 can slide in a sliding manner on the

inner sides

20, 22 of the receiving channel 18 in the manner of a friction device during a relative rotation of the input part 12 with respect to the output part 14 and thus provides intentional friction for increasing the damping portion of the torsional vibration damper.

The coupling arrangement 24 shown in fig. 2 and 3 has the output part 14 with teeth 26 for plug-in engagement, which are designed as internal teeth. In order to eliminate backlash in the plug-in connection after assembly, a first tensioning disk 28 and a second tensioning disk 30, which is connected to the first tensioning disk 28 by means of screws in a rotationally fixed manner, are provided. The second tensioning disk 30 has a driving lug 32 which is inserted into the tooth space of the toothed segment 26. The locking of the pretensioned tensioning spring 34 can be automatically released when the input part 12 rotates relative to the output part 14 when the motor vehicle is started for the first time. The tensioning spring 34, which is fitted on the output part 14 and on the

tensioning disks

28, 30, can thus rotate the

tensioning disks

28, 30 relative to the output part 14 to such an extent that the teeth inserted into the toothing 26 can be clamped without backlash between the driving lug 32 and the next tooth 28.

The

tensioning disks

28, 30 and/or the bolts connecting the

tensioning disks

28, 30 to one another can rest in the circumferential direction on the first flange ring 36 and the second flange ring 38. This allows the flange rings 36, 38 to be moved positively. Additionally, the flange rings 36, 38 may partially overlap in the circumferential direction, so that the first flange ring 36 may rest on the second flange ring 38 and be driven in the circumferential direction, or vice versa. In principle, it is therefore sufficient that the first tensioning disk 28 and/or the second tensioning disk 30 and/or the screws can rest in the circumferential direction only against the first flange ring 36 or only against the second flange ring 38. Upon relative rotation of the output member 14 with respect to the input member 12, the first flange ring 36 may slidably slide on the first inner side 20 of the receiving channel 18, and the second flange ring 38 may slidably slide on the second inner side 22 of the receiving channel 18, and provide damping defined by friction generated thereby. The flange rings 36, 38, which are in particular made of plastic, are embodied such that they can be moved relative to one another in the axial direction and first spring elements 40, which can be embodied as cup springs, are pressed away from one another toward the

inner sides

20, 22. The only first spring element 40 provided for this purpose can bear directly against the first flange ring 36 and the first tensioning disk 28.

The

tensioning disks

28, 30 extend partially between the first flange ring 36 and the second flange ring 38, so that a partial radius region a of the

tensioning disks

28, 30 is covered by the flange rings 36, 38. The flange rings 36, 38 have a radial extension Δ r which may coincide with this covered portion a. Here, the

tensioning disks

28, 30 have a radial extension Δ R. As a result, the tensioning spring 34 can be displaced radially outward to such an extent that the tensioning spring 34 is spaced radially inward from the flange rings 36, 38 only by a very small radial distance d, so that radial installation space is saved inside the flange rings 36, 38, and the toothing 26 can have a particularly large nominal diameter.

List of reference numerals

10 torsional vibration damper

12 input unit

14 output member

16 energy storage element

18 receiving channel

20 first inner side

22 second inner side

24 coupling assembly

26 tooth part

28 first tensioning disc

30 second tensioning disk

32 driving protrusion

34 tensioning spring

36 first flange ring

38 second flange ring

40 first spring element

Part A

d distance between

Radial extension of Deltar Flange Ring

Radial extension of the DeltaR tensioning disc

Claims

1. A coupling assembly for coupling a torsional vibration damper (10) to a drivetrain of a motor vehicle, the coupling assembly having:

an output part (14) which projects into a receiving channel (18) for receiving an energy storage element (16) and which serves to dissipate a torque of the torsional vibration damper (10), wherein the output part (14) has a toothing (26) for forming a plug-in toothing;

a first flange ring (36) fittable on a first axially inner side (20) of the receiving channel (18) for partially radially delimiting the receiving channel (18);

a second flange ring (38) fittable on a second axially inner side (22) of the receiving channel (18) facing the first axially inner side (20) for partially radially delimiting a boundary of the receiving channel (18);

a first tensioning disc (28) facing a first axial side of the output member (14);

a second tensioning disk (30) facing the second axial side of the output part (14), wherein the first tensioning disk (28) and/or the second tensioning disk (30) has/have a driving lug (32) which projects into a tooth spacing of a tooth (26) of the output part (14); and

a tensioning spring (34) that can be fitted on the output part (14), the first tensioning disk (28) and the second tensioning disk (30) and is used to eliminate backlash of the plug connection by a relative rotation of the driving lug (32) with respect to the output part (14),

wherein the first tensioning disk (28) and the second tensioning disk (30) are partially covered by the first flange ring (36) and the second flange ring (38) as viewed in the axial direction.

2. Coupling assembly according to claim 1, characterized in that the first tensioning disk (28) is connected with the second tensioning disk (30) by means of bolts, wherein the bolts can rest in the circumferential direction on the first flange ring (36) and/or the second flange ring (38).

3. Coupling assembly according to claim 1, characterized in that a first spring element (40) fitted on the first flange ring (36) and the first tensioning disc (28) and/or a second spring element fitted on the second flange ring (38) and the second tensioning disc (30) is provided.

4. The coupling assembly according to claim 3, wherein the first spring element (40) directly contacts the first tensioning disc (28) and/or the second spring element directly contacts the second tensioning disc (30).

5. The coupling assembly according to claim 3, wherein the first spring element (40) directly contacts the first flange ring (36) and/or the second spring element directly contacts the second flange ring (38).

6. The coupling assembly according to claim 4, wherein the first spring element (40) directly contacts the first flange ring (36) and/or the second spring element directly contacts the second flange ring (38).

7. The coupling assembly according to claim 1, characterized in that the first flange ring (36) and/or the second flange ring (38) have a maximum radial extension Δ r, wherein a radially outer edge of the tensioning spring (34) has a spacing d in the rest state relative to a minimum radially inner edge of the first flange ring (36) and/or the second flange ring (38), wherein-0.25 ≦ d/Δ r ≦ 1.00.

8. The coupling assembly of claim 7, wherein 0.00 ≦ d/Δ r ≦ 0.50.

9. The coupling assembly of claim 7, wherein 0.10 ≦ d/Δ r ≦ 0.30.

10. The coupling assembly of claim 7, wherein 0.20 ≦ d/Δ r ≦ 0.25.

11. Coupling assembly according to claim 1, wherein the first tensioning disc (28) and/or the second tensioning disc (30) have a maximum radial extension Δ R, wherein a radial portion A of the maximum radial extension Δ R is covered in the axial direction by the first flange ring (36) and the second flange ring (38), wherein 0.00 ≦ A/Δ R ≦ 0.60.

12. The coupling assembly of claim 11, wherein 0.15A/Δ R0.50.

13. The coupling assembly of claim 11, wherein 0.25A/Δ R0.45.

14. The coupling assembly of claim 11, wherein 0.35A/Δ R0.40.

15. Coupling assembly according to one of claims 1 to 14, wherein the tensioning spring (34) can be locked in the pre-tensioned state in the assembled position by a locking device.

16. Coupling assembly according to claim 15, wherein the locking means are releasable by relative rotation of the output member (14) with respect to the input member (12).

17. The coupling assembly of any one of claims 1 to 14, wherein the torsional vibration damper is a dual mass flywheel.

18. The coupling assembly according to one of claims 1 to 14, wherein the toothing is intended to form a plug-in engagement with a clutch assembly of a drive shaft of a motor vehicle engine coupled with at least one transmission input shaft of a motor vehicle transmission.

19. The coupling assembly according to any one of claims 1 to 14, wherein the accumulator element is made as an arc-shaped spring.

20. A torsional vibration damper for damping torsional irregularities in the drive train of a motor vehicle, having an input part (12) for introducing a torque, wherein the input part (12) forms a receiving channel (18) for receiving an energy storage element (16), and having a coupling assembly (24) according to one of claims 1 to 19, which is inserted partially into the receiving channel (18).

21. A torsional vibration arrangement for damping torsional irregularities in the drive train of a motor vehicle, having a torsional vibration damper (10) as claimed in claim 20, which can be coupled to an engine shaft of a motor vehicle engine, and having a clutch assembly which is coupled in a rotationally fixed manner via a toothing (26) of an output part (14) and is used for coupling a drive shaft to at least one transmission input shaft of a motor vehicle transmission.