JP2011149534A - Damper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper for transmitting torque from an engine to a transmission and damping torsional vibration, achieving the excellent characteristics of wide torsional angle and lower rigidity to damp the input torsional vibration to a demanded extent. <P>SOLUTION: The damper 1 includes an input side disc 10, an output side disc 20 arranged coaxially with the input side disc 10 and rotatable relatively to the input disc 10, and a power transmission mechanism 50 transmitting power between the input side disc 10 and the output side disc 20. The power transmission mechanism 50 includes: an elastic member 33 provided between the input side disc 10 and the output side disc 20, expanding and contracting in the axial direction and absorbing torque between them; and a power transmission part 34 giving to the elastic member 33 compressive force according to a relative rotation amount between the input side disc 10 and the output side disc 20. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a damper for transmitting power from an engine to a transmission and attenuating torsional vibration.

  2. Description of the Related Art Conventionally, some flywheels that are rotated by a vehicle engine are provided with a damper for the purpose of suppressing abnormal noise generation on the transmission side. This damper has a function of absorbing and attenuating torsional vibration (torque fluctuation) from the engine side and making it difficult to transmit to the transmission side. Known types of vehicle vibration include idle vibration, travel vibration, tip-in / tip-out vibration, and large torsional vibration when passing through a resonance point. For small torsional vibrations such as vibration during idling and vibration during running, it is preferable to generate a small hysteresis torque corresponding to the rigidity by minimizing the torsional rigidity of the damper. In order to avoid resonance in the actual use range of the engine, it is preferable to reduce the resonance point by reducing the torsional rigidity of the damper as much as possible. On the other hand, it is preferable to attenuate the torsional vibration by generating a large hysteresis torque in the damper against a large torsional vibration when passing through the resonance point or when a large torque of the engine is generated.

  Therefore, Patent Document 1 proposes a clutch disk assembly having a damper function having different characteristics depending on the magnitude of input torsional vibration. The clutch disk assembly includes an input plate and an output plate that are coupled to each other so as to be relatively rotatable within a predetermined angle, and a torsion spring that is an elastic coupling member disposed therebetween. The torsion spring is disposed so as to expand and contract in the circumferential direction. The clutch disk assembly further includes a first washer having a high coefficient of friction that contacts the input plate, a second washer having a low coefficient of friction that contacts the output plate, and an annular disposed between the first washer and the second washer. A hysteresis torque generating mechanism comprising a plate is provided. In this clutch disk assembly, when a torsional vibration is input, the elastic connecting member is compressed in the circumferential direction, and the input plate and the output plate rotate relative to each other, and the annular plate and the first washer against the small torsional vibration. The second washer slides between the annular plate and the output plate by rotating together, and for large torsional vibrations, the annular plate and the output plate rotate together and the first washer is between the annular plate and the input plate. Is configured to slide.

Japanese Patent Laid-Open No. 10-131981

  As described above, the clutch disk assembly described in Patent Document 1 can generate a suitable hysteresis torque according to the magnitude of the input torsional vibration, but has a wide torsion angle and a low rigidity required for the damper. It does not have enough characteristics. The clutch disk assembly can achieve a wide torsion angle and low rigidity by extending the circumferential length of the elastic connecting member. However, there are restrictions due to the arrangement of the elastic connecting member and the like. In some cases, it is structurally difficult to achieve the wide torsional angle and low rigidity necessary to attenuate torsional vibrations to the required level and avoid resonance in the actual use range of the engine. In addition, when the clutch disk assembly described in Patent Document 1 is used, a countermeasure for increasing the moment of inertia of the flywheel to attenuate torsional vibration during traveling can be considered. Then, there is a problem that energy loss due to fluctuations in engine rotation is large.

  Therefore, in view of the above, the present invention is a damper for transmitting torque from the engine to the transmission and attenuating torsional vibration, in order to attenuate the input torsional vibration to the required level and lower the resonance point. An object of the present invention is to provide a device capable of realizing a wide twist angle and a low rigidity characteristic.

  The damper according to the present invention includes a first disk, a second disk arranged coaxially with the first disk and rotatable relative to the first disk, the first disk, and the first disk. A power transmission mechanism for transmitting power between the two disks, the power transmission mechanism extending and contracting in the axial direction to absorb the input torque, the first disk, and the second disk And a power transmission unit that applies a compressive force according to the relative rotation amount to the disk to the elastic member.

  According to the above configuration, when the driving torque from the engine is input to the damper, the first disk and the second disk rotate relatively. When the relative rotational amount of the first disk and the second disk increases in accordance with the increase of the driving torque from the engine, the elastic member of the power transmission mechanism is compressed in the axial direction, and the torque reaction force of the power transmission mechanism is reduced. Will increase. This damper is not restricted by the relative rotation amount between the first disk and the second disk due to the torsion spring that expands and contracts in the circumferential direction as in the conventional product, so that the allowable range of the relative rotation amount is made wider. Can do. For this reason, the damper concerning this invention can be equipped with the characteristic of the low rigidity and the wide torsion angle which were superior to the conventional product.

  The damper further includes a friction member that is pressed between the first disk and the second disk, and the second disk reciprocates in the axial direction relative to the first disk. Preferably, the friction member is biased so as to be pressed by the compressed elastic member.

  According to the above configuration, the frictional resistance generated between the friction member and the first disk (or the second disk) increases with the amount of compression of the elastic member, so that the torque input to the damper increases. Increases frictional resistance. This frictional resistance becomes a hysteresis torque between the two disks. Therefore, the damper can generate a small hysteresis torque when a small torque is input, and can generate a large hysteresis torque when a large torque is input, effectively attenuating torsional vibration input to the damper. be able to.

  In the damper, the power transmission unit is provided on a power transmission path between the first disk and the second disk, and rotates integrally with the second disk. It is configured to reciprocate in the axial direction so as to approach and separate from the disk, and is attached in a direction approaching the first disk by the elastic member disposed between the disk and the second disk. One or more intermediate members that are energized, and are provided between the first disk and the intermediate member, and roll in the circumferential direction on at least one surface of the first disk and the intermediate member. At least one of the surfaces of the first disk and the intermediate member on which the rolling element rolls increases the amount of relative rotation between the first disk and the second disk. Before It can be provided with a function-shaped portion having the function of increasing the distance of the axial direction between the first disk and the intermediate member. Here, the functional shape portion may be an annular groove in which a circumferential surface of the rolling element contacts a groove bottom in which a depth is formed. At this time, it is preferable that the groove bottom of the annular groove has alternately valleys and peaks connected by smooth slopes in the circumferential direction.

  According to the above configuration, when the first disk and the second disk rotate relatively, the intermediate member rotates relative to the first disk, and the peripheral surface of the rolling element comes into contact with this. As the groove bottom portion moves, the intermediate member moves in the direction in which the axial distance from the first disk increases. With such a mechanical structure, a compressive force corresponding to the relative rotation amount of the first disk and the second disk can be applied to the elastic member that urges the intermediate member.

  According to the present invention, as the torque input to the damper increases, the amount of relative rotation between the first disk and the second disk increases, the amount of compression of the elastic member increases, and the torque reaction of the damper increases. As the force increases, the frictional resistance of the friction member also increases. Therefore, when the input torque is small, the damper according to the present invention produces a small torque reaction force and a small hysteresis torque to effectively buffer the small torsional vibration. When the input torque is large, a large torque reaction force and a large hysteresis torque corresponding to the input torque are generated, and a large torsional vibration can be effectively buffered. Further, the damper according to the present invention is not restricted by the amount of relative rotation by the elastic member that expands and contracts in the circumferential direction unlike the conventional product. For this reason, since the allowable range of the torsion angle that increases in accordance with the input torque can be made wider, it is possible to have characteristics of a wider torsion angle and lower rigidity than the conventional product.

It is sectional drawing which shows the structure of the damper which concerns on embodiment of this invention. It is a perspective view which shows an input side disk. It is a partial expanded sectional view of a damper in the state where the torsional vibration explaining the operation of a damper was inputted. It is a figure explaining the relationship between a rolling element and an annular groove, (a) shows the rolling element and the annular groove in a steady state, (b) shows the rolling element and the annular groove in a state where torque is input. (C) shows the force acting between the rolling element in the state where torque is inputted and the annular groove. It is a figure explaining the modification of a rolling element and an annular groove, (a) has shown the rolling element and annular groove of a steady state, (b) is the rolling element and annular groove of the state into which torque was input. Show.

  Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings. In the following description, the same or corresponding elements are denoted by the same reference symbols throughout the drawings, and redundant description thereof is omitted.

(Configuration of damper 1)
First, a schematic configuration of the damper 1 according to the present embodiment will be described with reference to FIG. The damper 1 according to the present embodiment is arranged between an engine (not shown) arranged on the left side of FIG. 1 and a transmission (not shown) arranged on the right side of FIG. It has the function of absorbing and attenuating and making it difficult to transmit to the transmission side. The damper 1 absorbs vibration between the input side disk 10, the output side disk 20, a hysteresis torque generating mechanism 40 that generates hysteresis torque in the damper 1, and the input side disk 10 and the output side disk 20. And a power transmission mechanism 50 that performs power transmission. Hereinafter, each component of the damper 1 will be described in detail. In the following, for convenience of explanation, the engine side (left side in FIG. 1) of the damper 1 is “left” and the transmission side (right side in FIG. 1) is “right”. The direction of the input shaft 52 is referred to as “axial direction”, and the direction of rotation about the axis of the input shaft 52 is referred to as “circumferential direction”.

  The input side disk 10 is an annular member having an input shaft 52 to the transmission as an axis, and is fixed to a flywheel 51 that rotates in response to the output of the engine and rotates integrally with the flywheel 51. An annular groove 11 in which a rolling element 30 described later rolls is formed on the right surface of the input side disk 10.

  On the other hand, the output side disk 20 is an annular member arranged coaxially with the input side disk 10 and has a cylindrical boss portion 23 extending in the axial direction and a boss provided on the right side of the boss portion 23. The flange portion 24 having a larger diameter than the portion 23 is integrally provided. A male spline (internal tooth) 23 a is formed on the inner periphery of the boss portion 23 of the output side disk 20, and a female spline (groove) 52 b formed in the outer periphery of the male spline 23 a and the input shaft 52 extends in the axial direction. And are fitted. Thus, since the output side disk 20 is spline fitted to the input shaft 52 so as to be slidable in the axial direction, the output side disk 20 and the input shaft 52 rotate integrally, and the output side disk 20 is input. It can reciprocate in the axial direction relative to the side disk 10. Further, the flange portion 24 of the output side disk 20 has a pressure receiving portion 24a that receives pressure from an elastic member 33 described later on the left surface thereof, and also has a female spline (external teeth) 24c that extends in the axial direction on the outer peripheral surface thereof. is doing.

  The power transmission mechanism 50 is provided between the input side disk 10 and the output side disk 20 and elastically transmits power while absorbing vibration between them by extending and contracting in the axial direction, and the input side disk 10 and a power transmission unit 34 that transmits power from the input side disk 10 to the elastic member 33 while applying pressure to the elastic member 33 so as to be compressed according to the relative rotation amount between the output side disk 20 and the output side disk 20. . Hereinafter, each component of the power transmission mechanism 50 will be described in detail.

  The power transmission unit 34 is provided between the intermediate member 35 provided on the power transmission path between the input side disk 10 and the output side disk 20, and between the input side disk 10 and the intermediate member 35. And one or more rolling elements 30 that roll (rotate) in the circumferential direction on at least one surface of the intermediate member 35.

  The intermediate member 35 is an annular member externally fitted to the output side disk 20, and includes a male spline (internal tooth) 35 a extending in the axial direction on the inner periphery thereof. The spline 24c is fitted. Thus, since the intermediate member 35 is fitted to the output side disc 20 so as to be slidable in the axial direction, the output side disc 20 and the intermediate member 35 rotate integrally, and the intermediate member 35 is connected to the input side. It can reciprocate in the axial direction so as to approach or leave the disk 10. In addition, since the intermediate member 35 should just be connected with the output side disk 20 so that the sliding to an axial direction is possible, these connection forms are not limited to the above spline fitting.

  Further, the intermediate member 35 has a protrusion protruding in a cross-sectional shape from the left surface to the left inner peripheral side, and includes a pressure receiving portion 35b on the right surface of the protrusion. Between the pressure receiving portion 35b of the intermediate member 35 and the pressure receiving portion 24a of the output side disk 20, an elastic member 33 that is elastically deformable so as to expand and contract in the axial direction is disposed. The compressed elastic member 33 applies a pressing force to the pressure receiving portion 35b of the intermediate member 35 and the pressure receiving portion 24a of the output side disk 20 so as to repel the intermediate member 35 to the input side disk 10. While urging in the approaching direction (left side), the output side disk 20 is urged to the right side to pressurize the friction member 41. The elastic member 33 according to the present embodiment is configured by stacking a plurality of annular disc springs that are externally mounted on the boss portion 23 of the output side disk 20 in the axial direction. The elastic member 33 is in this form. It is not limited. For example, an elastically deformable member such as a compression coil spring that extends and contracts in the axial direction that is sheathed on the boss portion 23 of the output-side disk 20, or a plurality of members disposed so as to surround the outer periphery of the boss portion 23 of the output-side disk 20 The elastic member 33 can also be configured by an elastically deformable member such as a compression coil spring that expands and contracts in the axial direction.

  Further, the intermediate member 35 has an annular groove (annular groove 36) centered on the input shaft 52 on the left surface facing the input side disk 10. The groove bottom of the annular groove 36 is provided with a shallow depth, and the circumferential surface of the rolling element 30 is in contact with the groove bottom. As shown in FIG. 4A, the annular groove 36 has a plurality of valleys having a depth approximately equal to the radius of the rolling element 30 and a mountain part having a shallower groove, and the valley part and the mountain part have a plurality of valleys. The grooves are alternately arranged in the groove bottom, and the adjacent valleys and peaks are connected by a smooth slope. The annular groove 36 may be a single or a plurality of arc-shaped grooves, an inclined flat surface, or a concave spherical surface instead of an annular shape.

  On the other hand, the input side disk 10 has an annular groove (annular groove 11) centered on the input shaft 52 on the right surface facing the intermediate member 35. The groove bottom of the annular groove 11 is provided with a shallow depth, and the circumferential surface of the rolling element 30 is in contact with the groove bottom. As shown in FIGS. 2 and 4 (a), the annular groove 11 has a plurality of troughs having a depth approximately equal to the radius of the rolling element 30 and a shallower crest than the troughs. The portions are alternately arranged in a ring shape at the groove bottom, and the adjacent valley portions and mountain portions are connected by a smooth slope. The annular groove 11 may be a single or a plurality of arc-shaped grooves, an inclined plane, or a concave spherical surface instead of an annular shape. The annular groove 11 of the input side disk 10 and the annular groove 36 of the intermediate member 35 have corresponding shapes, and these annular grooves 11, 36 are arranged to face each other, and between these annular grooves 11, 36. The rolling elements 30 are arranged on the front side.

  The rolling element 30 is sandwiched between the input side disk 10 and the intermediate member 35 by the urging force of the elastic member 33. The annular grooves 11 and 36 according to the present embodiment each have 16 valleys arranged in an annular shape. In a steady state where there is no torsional torque, the intermediate member 35 is biased in a direction in which the distance between the opposed annular grooves 11 and 36 becomes smaller. The rolling elements 30 exist on a straight line that faces each other and connects the valleys that face each other.

  The rolling element 30 may be one that rotates in the circumferential direction while its peripheral surface is in contact with the groove bottoms of the annular grooves 11, 36, one that revolves in the circumferential direction, or one that rotates and revolves as described above. it can. The rolling element 30 may be, for example, a sphere, a cylinder, a cone, or a cylinder. Moreover, the rolling element 30 does not need to be arrange | positioned at all the trough parts of the annular groove 11 or the annular groove 36, and is suitably arrange | positioned in the position where balance is possible, such as every other trough part and four trough parts. Just do it.

  Next, the hysteresis torque generating mechanism 40 will be described. The hysteresis torque generating mechanism 40 is a mechanism for attenuating torsional vibration by generating friction when the input side disk 10 and the output side disk 20 are relatively rotated and the elastic member 33 is compressed. The hysteresis torque generating mechanism 40 includes a friction member 41 provided so as to be in contact with the attached member of the input side disk 10 and the output side disk 20 and pressed between them.

  The auxiliary member of the input side disk 10 includes an annular first member 12 having an annular friction receiving portion 12a that contacts the friction member 41 on the left surface thereof, and a fastening member such as a bolt on the outer peripheral side of the first member 12 It is comprised with the cyclic | annular second member 13 fastened by. An adjusting member such as a shim is interposed between the first member 12 and the second member 13 in order to finely adjust the position of the output side disk 20. The second member 13 is fixed to the flywheel 51 by a fastening member such as a bolt together with the input side disk 10, and the first member 12 and the second member 13 rotate integrally with the input side disk 10. The first member 12 is supported via a bearing 54 on a support member 53 that is spline-fitted to the input shaft 52 while being spaced apart from the flywheel 51 in the axial direction. Between the wheel 51, the input side disk 10 and the output side disk 20 are arranged.

  Further, the disc-shaped friction member 41 is fixed to a portion facing the friction receiving portion 12 a of the first member 12 on the right surface of the flange portion 24 of the output side disk 20. The friction member 41 functions to contact the friction receiving portion 12 a of the input side disk 10 to generate a frictional resistance and to attenuate torsional vibrations input to the input side disk 10 and the output side disk 20. Although the friction member 41 according to the present embodiment is fixed to the output side disk 20, it may be fixed to the first member 12.

(Damper 1 operation)
Here, the operation (torsional characteristics) of the damper 1 having the above configuration will be described. When torque is input to the damper 1, the input side disk 10 and the output side disk 20 rotate in the opposite directions around the input shaft 52, and the input side disk 10 and the intermediate member 35 are also relatively reversed. Rotate in the direction. As a result, the position (phase) of the valley portion between the annular groove 11 of the input side disk 10 and the annular groove 36 of the intermediate member 35 is shifted, and the groove bottom portion where the peripheral surface of the rolling element 30 is in contact is a valley portion. To move along the slope. That is, as shown in FIG. 4A, the groove bottom portion with which the peripheral surface of the rolling element 30 is in contact is formed between the confronting troughs and troughs of the annular grooves 11 and 36 as shown in FIG. As shown to b), it moves between a trough part and an inclined surface or between an inclined surface and an inclined surface, and, thereby, between annular grooves 11 and 36 is expanded. In this way, the intermediate member 35 moves away from the input side disk 10 (to the right in the axial direction). As shown in FIG. 3, when the intermediate member 35 moves away from the input side disk 10, the elastic member 33 that is in contact with the pressure receiving portion 35 b of the intermediate member 35 is compressed. Thus, when the engine torque is input to the damper 1, the elastic member 33 transmits power from the intermediate member 35 to the output side disk 20 while compressing and absorbing torsional vibration.

  As described above, the force that compresses the elastic member 33 increases as the relative rotation amount between the input side disk 10 and the output side disk 20 increases, so that the rolling element 30 presses the input side disk 10 and the intermediate member 35. Power also increases. The force with which the rolling element 30 presses the input side disk 10 and the intermediate member 35 acts as a pressing force F between the rolling element 30 and the inclined surfaces of the annular grooves 11 and 36 as shown in FIG. This pressing force F acts substantially at right angles to the slope formed at the groove bottoms of the annular grooves 11 and 36. The pressing force F is a component F1 in a direction orthogonal to the axial direction and a component F2 parallel to the axial direction. The component F2 balances with the force pressing the two disks 10 and 20 of the elastic member 33, and the product of the distance R from the axis of the input shaft 52 to the point of action of the component F1 and the component F1 (F1 × R ) Becomes the torque reaction force of the damper 1 and balances with the torque from the engine applied to the damper 1.

  On the other hand, the output side disk 20 is pressed to the right side by the compressed elastic member 33, and a frictional resistance is generated between the friction receiving portion 12a of the first member 12 and the friction member 41, and the torsional vibration is attenuated by this frictional resistance. To do. Then, as the input torque increases, the friction receiving portion 12a is pressed against the friction member 41 with a larger force, so that a larger frictional resistance is generated between the friction receiving portion 12a of the first member 12 and the output side disk 20. Since this frictional resistance appears as a hysteresis torque of the damper 1, the hysteresis torque increases as the torque input to the damper 1 increases. As described above, the damper 1 has a characteristic that a small hysteresis torque is generated when a small torque is input, and a large hysteresis torque is generated when a large torque is input. Therefore, the damper 1 attenuates torsional vibration more effectively. be able to.

  The input side disk 10 and the output side disk 20 are relatively rotated between the input side disk 10 and the intermediate member 35 until the rolling element 30 exceeds one peak from the valleys of the annular grooves 11 and 36. can do. Since the damper 1 is not restricted by the torsion angle due to the torsion spring that expands and contracts in the circumferential direction unlike the conventional product, the relative rotation amount between the input side disk 10 and the output side disk 20, that is, the allowable range of the torsion angle is set. Can be wider. If this is expressed as a specific numerical value, the damper 1 according to the present embodiment has 16 valleys in one circumference, so that the input side disk 10 and the output side disk 20 are approximately 13.5 °. Can rotate relatively. On the other hand, in an example of a damper having a conventional torsion spring that expands and contracts in the circumferential direction, an allowable twist angle is about 4 °. Thus, the damper 1 according to the present embodiment can realize a wider torsion angle that is superior to the conventional one.

  Furthermore, when the input side disk 10 and the output side disk 20 are relatively rotated beyond the allowable range of the torsion angle, the rolling element 30 that has been in contact with the valleys of the annular grooves 11 and 36 is one peak. It reaches the position where it abuts against the adjacent valley part beyond the part and is reset to the steady state before the damper 1 is overloaded. Thus, the damper 1 has a torque limiter function in addition to the original function of the damper.

  In the damper 1, the annular grooves 11 and 36 are provided in both the input side disk 10 and the intermediate member 35, but an annular groove may be provided in either the input side disk 10 or the intermediate member 35. And the surface shape of the input side disk 10 or the intermediate member 35 which the rolling element 30 contacts is not restricted to an annular groove. In other words, on the surface on which at least one of the rolling elements 30 of the input side disk 10 and the intermediate member 35 rolls, the input side disk 10 and the intermediate disk 35 become intermediate with the increase in the relative rotation amount of the input side disk 10 and the output side disk 20. What is necessary is just to provide the shape part (functional shape part) which has the function to increase the distance of the axial direction with the member 35. FIG. The functional shape portion is not limited to the groove, and may be, for example, a slope or a protrusion formed on the surface on which at least one rolling element 30 of the input side disk 10 and the intermediate member 35 rolls.

  For example, in the example shown in FIG. 5A, the annular groove 11 having a valley and a peak is formed only in the input side disk 10, and the rolling element 30 is centered on the rotating shaft 31 fixed to the intermediate member 35 side. As a rotating roller. In this configuration, when the torsional vibration is input to the damper 1 and the input side disk 10 rotates relative to the output side disk 20, as shown in FIG. 5B, the damper 1 is in contact with the valley of the annular groove 11. The circumferential surface of the rolling element 30 moves on the slope connecting the valley and the mountain. As a result, the space between the input side disk 10 and the intermediate member 35 expands, and the elastic member 33 is compressed as described above. Thus, by providing an annular groove having a trough and a peak at the groove bottom in one of the input side disk 10 and the intermediate member 35, the processing cost can be reduced.

  The damper according to the present invention can be disposed in a power transmission system from the engine to the transmission, and is not limited to an independent damper. For example, the function of this damper can be incorporated into a clutch or a torque converter.

DESCRIPTION OF SYMBOLS 10 Input side disk 11 Annular groove 12 First member 12a Friction receiving part 13 Second member 20 Output side disk 23 Boss part 24 Flange part 24a Pressure receiving part 30 Rolling body 33 Elastic member 34 Power transmission part 35 Intermediate member 36 Annular groove 40 Hysteresis Torque generating mechanism 41 Friction member 50 Power transmission mechanism 51 Flywheel 52 Input shaft

Claims (5)

The first disc,
A second disk disposed coaxially with the first disk and rotatable relative to the first disk;
A power transmission mechanism for transmitting power between the first disk and the second disk;
The power transmission mechanism applies to the elastic member an elastic member that absorbs input torque by expanding and contracting in the axial direction, and a compression force according to the relative rotation amount of the first disk and the second disk. A damper comprising: A friction member that is pressurized between the first disk and the second disk;
The second disk is configured to reciprocate in the axial direction relative to the first disk, and is biased to press the friction member by the compressed elastic member. The damper according to claim 1. The power transmission unit is
A shaft provided on a power transmission path between the first disk and the second disk so as to rotate integrally with the second disk and to approach and separate from the first disk. An intermediate member configured to reciprocate in a direction and biased in a direction approaching the first disk by the elastic member disposed between the second disk and the second disk;
One or more rolling elements provided between the first disk and the intermediate member and rolling in a circumferential direction on at least one surface of the first disk and the intermediate member;
At least one of the surface of the first disk and the intermediate member on which the rolling element rolls is the first disk as the amount of relative rotation between the first disk and the second disk increases. The damper according to claim 1, further comprising a functional shape portion having a function of increasing the axial distance between the intermediate member and the intermediate member.   4. The damper according to claim 3, wherein the functional shape portion is an annular groove in which a circumferential surface of the rolling element is in contact with a groove bottom in which a depth is formed.   5. The damper according to claim 4, wherein the groove bottom of the annular groove has troughs and crests alternately connected in a circumferential direction in a smooth slope.

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