TORSIONAL VIBRATION DAMPER, CLUTCH DISC, AND CLUTCH

Abstract

A torsional vibration damper includes a rotational axis, an input part mounted about the rotational axis, an output part rotatable about the rotational axis to a limited extent relative to the input part; a spring device opposing rotation of the output part relative to the input part, a first cam mechanism, and a first intermediate element. The first intermediate element is arranged for radial displacement by the first cam mechanism when the output part rotates relative to the input part. The first intermediate element has a first intermediate element first part, and a first intermediate element second part. In an example embodiment, the damper includes a second cam mechanism and a second intermediate element arranged to be radially displaced by the second cam mechanism when the output part rotates relative to the input part. The spring device is arranged between the first intermediate element and the second intermediate element.

Claims

1.-9. (canceled)

10. A torsional vibration damper for a clutch disk within a drive train of a motor vehicle, comprising: a rotational axis extending in an axial direction; an input part mounted about the rotational axis; an output part rotatable about the rotational axis to a limited extent relative to the input part; a spring device opposing rotation of the output part relative to the input part; a first cam mechanism; and a first intermediate element arranged for radial displacement by the first cam mechanism when the output part rotates relative to the input part, comprising: a first intermediate element first part; and a first intermediate element second part.

11. The torsional vibration damper of claim 10 further comprising: a second cam mechanism; a second intermediate element arranged to be radially displaced by the second cam mechanism when the output part rotates relative to the input part, comprising: a second intermediate element first part; and a second intermediate element second part, wherein the spring device is arranged between the first intermediate element and the second intermediate element.

12. The torsional vibration damper of claim 10 wherein the first intermediate element first part and the first intermediate element second part are spaced apart from one another in the axial direction.

13. The torsional vibration damper of claim 10 wherein a portion of the input part is disposed axially between the first intermediate element first part and the first intermediate element second part.

14. The torsional vibration damper of claim 13, wherein the input part comprises an input part first element and an input part second element.

15. The torsional vibration damper of claim 14, wherein the input part further comprises a friction element disposed axially between and fastened to the input part first element and the input part second element.

16. The torsional vibration damper of claim 10, wherein: the output part comprises an output part first element and an output part second element; and a portion of the first intermediate element is disposed axially between the output part first element and the output part second element.

17. The torsional vibration damper of claim 16, wherein the first intermediate element first part is formed symmetrically relative to the first intermediate element second part between the output part first element and the output part second element.

18. A clutch disk comprising the torsional vibration damper of claim 10.

19. A clutch comprising the clutch disk of claim 18.

20. A torsional vibration damper comprising: a rotation axis; an input part comprising a first ramp profile; an output part comprising a second ramp profile; an intermediate part comprising a pair of intermediate part elements, each of the pair of intermediate part elements comprising: a third ramp profile; and a fourth ramp profile; a first roller contacting the first ramp profile and the third ramp profile; and a second roller contacting the second ramp profile and the fourth ramp profile, wherein: the first roller and the second roller are arranged to roll along their respective ramp profiles when the output part rotates about the rotational axis relative to the input part; and the intermediate part is radially displaced by the first roller and the second roller when the output part rotates about the rotational axis relative to the input part.

21. The torsional vibration damper of claim 20, further comprising a third roller, wherein: the input part comprises a fifth ramp profile; each of the pair of intermediate part elements comprises a sixth ramp profile; and the third roller is arranged to roll along the fifth ramp profile and the sixth ramp profile to radially displace the intermediate part when the output part rotates about the rotational axis relative to the input part.

22. The torsional vibration damper of claim 20 wherein the second roller is longer than the first roller.

23. The torsional vibration damper of claim 20 wherein a portion of the input part is disposed axially between the pair of intermediate part elements.

24. The torsional vibration damper of claim 23 wherein the input part comprises a pair of input part elements.

25. The torsional vibration damper of claim 20 wherein: the output part comprises a pair of output part elements; and a portion of the intermediate part is disposed axially between the pair of output part elements.

26. The torsional vibration damper of claim 20 further comprising a pair of spring elements opposing radially inward displacement of the intermediate part.

27. The torsional vibration damper of claim 20 wherein the input part further comprises a friction disk having a portion disposed axially between the pair of intermediate part elements.

28. The torsional vibration damper of claim 27 wherein: the input part comprises a pair of input part elements; and the portion of the friction disk is disposed axially between the pair of input part elements.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Both the disclosure and the technical environment will be explained in more detail below with reference to the figures. It should be pointed out that the disclosure is not intended to be limited by the exemplary embodiments shown. For example, unless explicitly stated otherwise, it is also possible to extract partial aspects of the matter explained in the figures and to combine same with other components and findings from the present description and/or figures. It should also be pointed out that the figures and, in particular, the proportions shown, are only schematic. The same reference numerals designate the same objects, so that explanations from other figures can be used as a supplement. In the figures:

[0016] FIGS. 1 and 2 show a torsional vibration damper assumed to be known;

[0017] FIG. 2 shows a detail of the torsional vibration damper assumed to be known;

[0018] FIG. 3 shows a detail of an example of a torsional vibration damper in the neutral, undeflected state;

[0019] FIGS. 4 and 5 show details of two examples of torsional vibration dampers in section;

[0020] FIG. 6 shows a detail of an example of a torsional vibration damper in the deflected state;

[0021] FIGS. 7 and 8 show two views of the torsional vibration damper in the non-deflected state;

[0022] FIGS. 9 and 10 show two views of the torsional vibration damper in the deflected state;

[0023] FIG. 11 shows an example of a clutch disk; and

[0024] FIG. 12 very schematically shows a clutch.

DETAILED DESCRIPTION

[0025] In the Detailed Description, the same parts are provided with the same reference symbols. The torsional vibration damper 1 shown as known in FIGS. 1 and 2 includes an input part 2, intermediate elements 3, cam mechanisms 4, 5, ramp devices 6, 7, a spring device 8 having energy stores 9 arranged between the intermediate elements 3, and an output part 10. The input part 2 of the torsional vibration damper 1 of FIG. 1 has ramps 11, such as cam tracks of the ramp devices 6, in the two cam mechanisms 4 which are opposite one another with respect to the rotational axis d of a shaft 17.

[0026] Two mutually opposite intermediate elements 3, each having two ramps 12 complementary to the input part 2, such as cam tacks of the ramp devices 6, and the rolling elements 13 complete the cam mechanism 4 between the input part 2 and the intermediate elements 3. When the input part 2 is rotated around the rotational axis d, the rolling elements 13 are guided on the ramps 11, 12 such that the radial movement of the intermediate elements 3 results in a parallel spring compression of the two energy stores 9, which are arranged between the intermediate elements 3. The ramps 11 of the input part 2 and the ramps 12 of the intermediate elements 3 together with the associated rolling elements 13 form the cam mechanism 4.

[0027] The intermediate elements 3 each include a further ramp 14 radially on the inside, which are operatively connected to ramps 15 arranged in the output part 10. When the output part 10 is rotated around the rotational axis d in the opposite direction to the rotation of the input part 2, the intermediate elements 3 are also guided via rolling elements 16 which roll freely between the appropriately designed ramps 14, 15 such that the movement thereof again signifies a parallel spring compression of the energy stores 9. The ramps 14 of the intermediate elements 3 and the ramps 15 of the output part 10 together with the associated rolling elements 16 form the cam mechanism 5.

[0028] As a result of the coupling of the two cam mechanisms 4, 5 via the intermediate elements 3, the total angle of rotation between the input part 2 and the output part 10 results from the sum of the angles of rotation which are set in the respective cam mechanism 4, 5 having a certain spring compression of the energy stores 9. The torque at the input part 2 for the rotational movement is supported as a pure torsional moment at the output part 10. The unit consisting of intermediate elements 3 and energy stores 9 is not subject to an external torque effect, but determines the amount of the transmitted torque via the amount of force from the parallel spring compression of the energy stores 9.

[0029] The ramps 11, 12, 14, 15 of the cam mechanisms 4, 5 of the torsional vibration damper 1 are linear in design, for example, to transmit the movements during rotation in the marked direction and to indicate the ability to transmit torque in contact via the rolling elements 13, 16 in this direction. In the case of constructions carried out, on the other hand, the design of the ramps 11, 12, 14, 15 is a free form as a result of the desired translations for the torsion characteristic curve while fulfilling the rolling conditions for the rolling elements 13, 16.

[0030] FIG. 3 shows a detail of an example of a non-deflected torsional vibration damper 1 with an input part 1 which can move in the circumferential direction 18, an intermediate element 3 which is connected to another intermediate element 3 (not shown) via a spring device 8. The movement of the intermediate element 3 in the direction of movement 19 is predetermined by the energy store 9 (spring elements) of the spring device 8. Furthermore, an output part 10 is formed which is connected to a shaft (not shown) which has the rotational axis d.

[0031] Furthermore, the torsional vibration damper 1 has rolling elements 13 which are guided by ramps 11 of the input part 2 and ramps 12 of the intermediate element 3, as discussed above. Furthermore, a rolling element 17 is formed which is guided by ramps 14 of the intermediate element 3 and ramps 15 of the output part 10, as discussed above.

[0032] FIGS. 4 and 5 show details of two possible examples of torsional vibration dampers 1 in section, in which the intermediate element 3 is formed in two parts from two element parts 20. These element parts 20 are constructed symmetrically and are designed to be spaced apart from one another in the direction of the rotational axis d, so that the input part 2 can be received between the element parts 20.

[0033] In FIG. 4, the input part 2 is constructed from two input part elements 21 which are connected to one another in a non-positive and form-fitting manner via rivets 22 enabling a friction element 23 to be fixed between the input part elements 21, e.g., by the rivets 22. The rivets 22 may be countersunk and conical in order to allow a connection of the input part elements 21 that does not cause any further structural restrictions, since the rivet 2 ends flush with the respective axial outer side of the input part elements 21. The term friction element 23 is also to be understood here as an element that serves as a carrier for a friction ring, for example. For example, the friction element 23 may be part of a corresponding friction clutch (not shown here).

[0034] FIG. 5 shows an example in which the input part 2 is formed in one piece. Here, the friction element 23 is fastened to an axial surface of the input part 2 by means of corresponding rivets 22.

[0035] If FIG. 2 is compared to FIGS. 4 and 5, it can be seen that, in the embodiment according to FIGS. 5 and 6, the bearing surface for the rolling elements 13, 17 in the intermediate element 3 or the element parts 20 is symmetrical and flat, while in the embodiment of FIG. 2, the influence of, for example, the non-uniformities of the support surface produced by the punch entry and exit is greater. In this way, a more uniform movement of the rolling elements 13, 16 in the respective ramp tracks 11, 12, 14, 15 can be achieved, in which a lateral movement of the components 2, 3, 10 can be reduced.

[0036] FIG. 6 shows an example of a torsional vibration damper 1 which is deflected in comparison to FIG. 3, analogously to FIG. 3.

[0037] FIGS. 7 and 8 show parts of a torsional vibration damper 1 in the non-deflected state, FIGS. 9 and 10 in the deflected state. Reference is made to the above disclosure. FIGS. 7 to 10 show that a simple connection of the friction element 23 to the input part 2 is possible without the shape and the range of movement of the intermediate elements 3 being restricted as a result. The intermediate elements 3 or the element parts 20 can use the maximum installation space and in particular the maximum possible radius in the clutch disk, so that the size of the spring devices 8 and in particular the energy store (springs) 9 can be optimized, so that the energy store 9 can provide a large spring energy.

[0038] FIG. 11 shows a clutch disk 24 with a torsional vibration damper 1 as described, for example, in connection with FIG. 4. Reference is made to the embodiments outlined above. The friction element 23 is connected to the input part elements 21 by rivets 22. The friction element 23 has friction surfaces 25 which can be detachably connected via a frictional connection to corresponding friction partners (not shown) forming a clutch.

[0039] Furthermore, a hub flange 26 is shown which can be connected via an intermediate toothing 27 to a hub (not shown) which in turn can be connected to a shaft, for example a transmission input shaft.

[0040] Finally, FIG. 12 very schematically shows a clutch 28 with a clutch disk 24. The clutch 28 can, for example, be arranged in the drive train of a motor vehicle.

REFERENCE NUMERALS

[0041] 1 Torsional vibration damper

[0042] 2 Input part

[0043] 3 Intermediate element

[0044] 4 Cam mechanism

[0045] 5 Cam mechanism

[0046] 6 Ramp device

[0047] 7 Ramp device

[0048] 8 Spring device

[0049] 9 Energy store

[0050] 10 Output part

[0051] 11 Ramp

[0052] 12 Ramp

[0053] 13 Rolling element

[0054] 14 Ramp

[0055] 15 Ramp

[0056] 16 Rolling element

[0057] 17 Shaft

[0058] 18 Circumferential direction

[0059] 19 Direction of movement

[0060] 20 Element part

[0061] 21 Input part elements

[0062] 22 Rivet

[0063] 23 Friction element

[0064] 24 Clutch disk

[0065] 25 Friction surface

[0066] 26 Hub

[0067] 27 Intermediate gearing

[0068] 28 Clutch

[0069] d Rotational axis