JP2000310282A - Damper disc assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide appropriate structure of a damper mechanism bringing about a characteristic of low rigidity to a damper disc assembly, having two pieces of spline hubs to be engaged with one shaft. SOLUTION: This damper disc assembly is furnished with two hubs 16, two hub flanges 20 and a first damper. The two hubs 16 are arranged in parallel in the axial direction, so as to be engaged with one shaft incapable of relative rotation. The two hub flanges 20 are respectively arranged on outer peripheral sides of the two hubs 16 and fixed with each other. The hub flanges 20 come to be free to relatively rotate at a prescribed angular region with respect to the hubs 16. The first damper has a small spring 7 to be compressed at the time, when the two hubs 16 and the two hub flanges 20 rotate relatively. A position of the first damper in the axial direction is provided between positions of the two hub flanges 20 in the axial directions.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a damper mechanism, and more particularly, to a damper mechanism for transmitting torque and attenuating and absorbing torsional vibration.

[0002]

2. Description of the Related Art A damper mechanism is a device used in a power transmission device for transmitting torque and absorbing and attenuating torsional vibration contained in the torque. The damper mechanism is incorporated in a clutch disk assembly, a flywheel assembly, and the like used for a clutch of an automobile. The damper mechanism mainly includes a first rotating member, a second rotating member, and an elastic member such as a spring disposed between the first rotating member and the second rotating member. The elastic member is disposed within the window of the first rotating member and the second rotating member, and is compressed between the first rotating member and the second rotating member when the first rotating member and the second rotating member rotate relative to each other.

[0003] A clutch disk assembly mainly includes a clutch disk having friction facing, a pair of disk-shaped members fixed to the clutch disk, and an output side hub having a flange disposed between the disk-shaped members. And a spring (torsion spring) for elastically connecting the flange and the pair of disk-shaped members in the circumferential direction. Here, a damper mechanism is constituted by a pair of disk-shaped members, a flange of a hub, and a spring.

[0004] As a problem of abnormal noise of a vehicle for which a measure is required for the clutch disk assembly, there are mainly a transmission rattling noise during a neutral state and a driving system rattling noise and a muffled noise during running. Particularly, in the case of diesel vehicles, the former noise problem is remarkable. For this reason, a structure is known in which a hub and a boss are divided, and a small spring having a small spring constant is provided between the hub and the hub flange.

[0005]

In a conventional clutch disk assembly, for example, in order to maximize a damper capacity within a limited outer diameter, springs constituting the damper are arranged in a double axial direction. There is a clutch disk assembly that has been completed. In order to realize such a structure without difficulty in manufacturing, two spline hubs arranged in the axial direction are used. However, if the first-stage low-rigidity damper is provided for each spline hub, the diameter becomes large and the structure becomes complicated.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an appropriate damper mechanism for providing a low-rigidity characteristic in a damper disk assembly having two spline hubs that engage one shaft. .

[0007]

According to a first aspect of the present invention, there is provided a damper disk assembly including two hubs, two annular rotating members, and a damper mechanism. The two hubs are arranged axially side by side so as to non-rotatably engage one shaft. The two annular rotating members are respectively arranged on the outer peripheral side of the two hubs and fixed to each other. The damper mechanism has an elastic member that is compressed when the two hubs and the two annular rotating members rotate relative to each other. The damper mechanism has an axial position between the axial positions of the two annular rotating members.

In this damper disk assembly, since the damper mechanism is not disposed axially outside the two annular rotating members, the space of the entire damper disk assembly can be reduced. In the damper disk assembly according to the second aspect, in the first aspect, at least a part of the damper mechanism is disposed axially between the two hubs.

In this damper disk assembly, the diameter of the damper mechanism can be reduced. In the damper disk assembly according to the third aspect, in the first or second aspect, the two hubs and the two annular rotating members have stopper portions that come into contact with each other at a predetermined torsion angle. In this damper disk assembly, when the two hubs and the stopper portions of the two annular rotating members abut, the compression of the elastic member of the damper mechanism does not proceed any further.

[0010] In the damper disk assembly according to the fourth aspect, in any one of the first to third aspects, the damper mechanism has a first member, a second member, and the elastic member.
Torque is input to the first member from the two annular rotating members. The second member outputs torque to the shaft. The elastic member is compressed between the first member and the second member when the first member and the second member rotate relative to each other.

According to a fifth aspect of the present invention, in the damper disk assembly according to the fourth aspect, the first member is an annular plate member having an inner peripheral portion disposed between the two hubs in the axial direction and supporting both sides in the rotational direction of the elastic member. It is. Since the inner peripheral portion of the first member is disposed between the two hubs in the axial direction, the diameter of the first member can be reduced. According to a sixth aspect of the present invention, the damper disk assembly according to the fifth aspect further includes a fixing member. The securing member extends axially to secure the two annular rotating members to each other. The fixing member is engaged with the first member so as not to rotate relatively.

In this damper disk assembly, the torque of the two annular rotating members is transmitted to the first member via the fixed member. In the damper disk assembly according to the seventh aspect, the second member according to any one of the fourth to sixth aspects, wherein:
An annular plate member having an inner peripheral portion disposed between two hubs in the axial direction and supporting both sides in the rotational direction of the elastic member.

[0013] In this damper disk assembly, the inner diameter of the second member is disposed between the two hubs in the axial direction, so that the diameter of the second member can be reduced. Claim 8
In the damper disk assembly described in the above, in claim 7, the second annular plate member is directly engaged with the shaft. In this damper disk assembly, there is no need to provide two hubs with teeth or the like for engaging with the second annular plate member.

According to a ninth aspect of the present invention, the damper disk assembly according to any one of the first to eighth aspects further includes a positioning member. The positioning member axially positions the two hubs with respect to the two annular rotating members. According to a tenth aspect of the present invention, there is provided a damper disk assembly according to the first aspect.
In any one of the first to ninth embodiments, a friction generating mechanism is further provided. The friction generating mechanism is a mechanism for generating friction when two hubs and two annular rotating members rotate relative to each other.

[0015] A damper disk assembly according to claim 11 includes two hubs, two annular rotating members, and a damper mechanism. The two hubs are arranged axially side by side so as to non-rotatably engage one shaft.
The two hubs have a plurality of outer teeth. The two annular rotating members are respectively arranged on the outer peripheral sides of the two hubs. 2
The two annular rotating members are fixed to each other. The two annular rotating members have a plurality of inner peripheral teeth that can rotate relative to the outer peripheral teeth up to a predetermined torsion angle. The damper mechanism has an elastic member. The elastic member is arranged at an axial position different from the outer teeth and the inner teeth. The elastic member is compressed in the rotational direction when the two hubs and the two annular rotating members rotate relative to each other.

In this damper disk assembly, the elastic members of the damper mechanism are arranged at positions axially different from the inner peripheral teeth and the outer peripheral teeth which engage the two hubs and the two annular rotating members with each other. A plurality of outer teeth and inner teeth can be provided over the entire circumference. For this reason, by ensuring a sufficient contact area between the outer peripheral teeth and the inner peripheral teeth, the surface pressure on each tooth can be kept small.

A damper disk assembly according to a twelfth aspect includes two hubs, an annular rotating member, and a damper mechanism. The two hubs are arranged axially side by side so as to non-rotatably engage one shaft. The annular rotating member is disposed so as to be relatively rotatable on the outer peripheral side of the two hubs, and regulates movement of the two hubs in a direction away from each other in the axial direction. The damper mechanism has an elastic member that is compressed when the two hubs and the annular rotating member rotate relative to each other. The damper mechanism is at least partially sandwiched between the two hubs in the axial direction.

In this damper disk assembly, the outer diameter of the damper mechanism can be reduced by at least partly being sandwiched between the two hubs in the axial direction. A damper disk assembly according to a thirteenth aspect includes a hub, an annular rotating member, and a damper mechanism. The hub has an inner peripheral surface with splines that engage the shaft. The annular rotating member is arranged on the outer peripheral side of the hub so as to be relatively rotatable up to a predetermined torsion angle. The damper mechanism elastically connects the hub and the shaft in the rotational direction.

In this damper disk assembly, since the damper mechanism connects the annular rotating member and the shaft and is not engaged with the hub, there is no need to provide a structure for engaging the damper mechanism with the hub. . According to a fourteenth aspect, in the thirteenth aspect, the damper mechanism has a first member, a second member, and an elastic member. Torque is input to the first member from the annular rotating member. The second member is directly engaged with the shaft. The elastic member is arranged so as to be compressed between the first member and the second member when the first member and the second member rotate relative to each other.

In this damper disk assembly, since the second member is directly engaged with the shaft, there is no need to provide a structure for engaging the second member with the hub. Claim 15
In the damper disk assembly according to the present invention, in claim 14, the second member is an annular plate member having engagement teeth formed on the inner peripheral edge for engaging with the shaft.

In this damper disk assembly, since the second member is directly engaged with the shaft, there is no need to provide a structure for engaging with the second member on the hub.

[0022]

1 to 4 show a clutch disk assembly 1 according to an embodiment of the present invention. The clutch disc assembly 1 is a device used for a clutch of a vehicle. An engine and a flywheel (not shown) connected to the engine are arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of FIG. The clutch disk assembly 1 has a clutch function for transmitting and interrupting torque between the engine and the transmission, and a damper function for absorbing and attenuating torsional vibration.

OO shown in FIG. 1 is the rotation axis of the clutch disk assembly 1. An arrow R1 shown in FIGS. 2 and 3 is a rotation direction of the engine and the flywheel, and an arrow R1.
2 is the opposite direction. Clutch disk assembly 1
Are mainly composed of the input member 2, the output member 3, and the intermediate member 4.
, A first spring 5, a second spring 6, a first seat 7, and a second seat 8. The input member 2 is a member composed of a friction portion 11, first and second plates 12, 13 and the like, which will be described later, and is a member that is connected to a flywheel (not shown) to input torque to the clutch disk assembly 1. The output member 3 is a member including a first hub 16 and the like described later, is connected to a shaft 110 extending from a transmission (not shown), and is a member for outputting torque of the clutch disk assembly 1.
The intermediate member 4 is an intermediate member arranged to transmit torque between the input member 2 and the output member 3. The first spring 5 is a member for elastically connecting the input member 2 and the intermediate member 4 in the circumferential direction. The first spring 5, the input member 2, and the intermediate member 4 constitute a third damper 103. The second spring 6 is a member for elastically connecting the intermediate member 4 and the output member 3 in the circumferential direction. The second spring 6, the intermediate member 4 and the output member 3 constitute a second damper 102. Second damper 102 and third damper 1
03 is arranged to act in series. The first seat 7 is a member that supports both ends in the circumferential direction of the first spring 5 and connects the input member 2 and the intermediate member 4 so that torque is transmitted via the first spring 5. The second sheet 8 supports both ends of the second spring 6 in the circumferential direction,
A member that connects the intermediate member 4 and the output member 3 so that torque is transmitted through the second spring 6.

The input member 2 is mainly composed of a friction portion 11 and a pair of first and second plates 12, 13. The friction portion 11 (clutch disk)
It comprises a plurality of cushioning plates 28 and friction facings 29 fixed on both axial sides of the cushioning plate 28. First and second plates 1
Reference numerals 2 and 13 denote annular plates arranged at a predetermined distance in the axial direction, and are fixed to each other by a plurality of first pins 14. The first pin 14 allows the first and second plates 12 and 13 to keep a predetermined gap in the axial direction and rotate integrally.

The first plate 12 and the second plate 13 will be described in detail with reference to FIG. Since the first plate 12 and the second plate 13 have the same shape, only the second plate 13 will be described here. Second plate 1
Reference numeral 3 mainly includes an annular portion 31 as shown in FIG. The annular portion 31 has a plurality of support portions 32 projecting radially inward. The support portion 32 has a structure for transmitting torque to a first spring 5 described later.
A recess 33 is formed in the middle of the support 32 in the axial direction on both sides in the circumferential direction. The concave portion 33 has a trapezoidal shape in which the width in the radial direction becomes narrower toward the back, and both corners have a smooth shape with sharp corners.
In this manner, the circumferential end surface of the support portion 32 is connected to the first surface 34, the concave portion 33 recessed in the circumferential direction from the first surface 34, and the second peripheral surface of the annular portion 31 from the radially inner side. Face 35
Are formed. The space between the support portions 32 adjacent in the circumferential direction is a housing portion 36 for housing the first spring 5 described later. Further, the annular portion 31 of the second plate 13 has a hole 3 for inserting the first pin 14 therein.
7 are formed in the circumferential direction.

The intermediate member 4 is an annular or disk-shaped member as shown in FIG. The intermediate member 4 is disposed on the inner peripheral side of the input member 2 between the first and second plates 12 and 13 in the axial direction. The outer peripheral portion of the intermediate member 4 is close to the inner peripheral side of the first pin 14. The center of the intermediate member 4 has a circular center hole 4
6 are formed. A plurality of first window holes 48 are formed in the outer peripheral portion of the intermediate member 4. The first window hole 48 has an arc shape extending relatively long in the circumferential direction. Both ends in the circumferential direction of the first window hole 48 are shaped such that the width in the radial direction becomes smaller toward the outer side in the circumferential direction. On the inner peripheral side of the first window hole 48, the second
A window hole 49 is formed. The second window hole 49 has one first
The window 48 is divided into two in the circumferential direction so as to form two holes. Flat stop surfaces 71 are formed in the pair of second window holes 49 on the inner side in the circumferential direction (the sides facing each other). One first window hole 48 and a pair of second window holes 49 correspond to each other, and have different circumferential lengths but substantially the same center angle. The outer end in the circumferential direction of each second window hole 49 has such a shape that the width in the radial direction becomes smaller toward the outer side in the circumferential direction. Further, the first window hole 48 corresponds to the accommodating portion 36 of the first and second plates 12 and 13 in the axial direction.

A plurality of protrusions 50 are formed on the outer periphery of the intermediate member 4 to protrude outward in the radial direction. Projection 50
Are arranged between the plurality of first pins 14 in the circumferential direction as shown in FIG. That is, the first pins 14 and the protrusions 50 are alternately arranged in the circumferential direction at the same position in the radial direction. The circumferential angle between the first pin 14 and the protrusions 50 on both sides thereof is θ3. That is, the first pin 14 and the protruding portion 50 form the third stopper 106 that allows the intermediate member 4 and the input member 2 to relatively rotate only within the range of θ3.

The first springs 5 are arranged on both sides of the intermediate member 4 in the axial direction. More specifically, the first springs 5 are arranged on both axial sides of the first window hole 48 of the intermediate member 4, and are arranged in the receiving portions 36 of the first and second plates 12 and 13. The first spring 5 is a coil spring as is clear from FIG. The first spring 5 includes two coil springs (a large coil spring 5a and a small coil spring 5a).
b) is a member that is combined. Each first spring 5
Is arranged to be able to abut or abut on the circumferential end surface of the support portion 32. More specifically, the large coil spring 5a of the first spring 5 is connected to the first surface 34 of the support 32 and the second coil spring 5a.
It is in contact with the surface 35.

Next, the first sheet 7 will be described in detail with reference to FIG. The first sheet 7 is a member that is elongated in the axial direction and is made of, for example, a resin. The first sheet 7 penetrates both ends in the circumferential direction of the first window hole 48 of the intermediate member 4, and both ends in the axial direction are the accommodating portions 36 of the first and second plates 12 and 13.
At a position between the support portion 32 and the first spring 5.

The specific components of the first sheet 7 will be described. The first sheet 7 mainly includes a main body 60 extending in the axial direction. The main body 60 has a shorter radial width than the first spring 5. The main body 60 has a first main surface 63 on the first spring 5 side and a second main surface 64 on the support portion 32 side. The end turn end of the large coil spring 5a of the first spring 5 is in contact with or close to the first main surface 63 so as to be able to contact. As described above, since the main body 60 has a smaller radial width than the first spring 5, the main body 60 is
Abuts only on the apexes on both sides in the axial direction. As shown in FIG. 10, the second main surface 64 has a smaller width in the radial direction than the first main surface 63, and has a smooth trapezoidal shape with a rounded corner. As shown in FIG. 10, the main body 60 is disposed in a concave portion 33 formed in the support portion 32 of the first and second plates 12 and 13 and is in a state of being in close contact with an end surface thereof. In this state, movement and rotation of the main body 60, that is, the first sheet 7, in the radial direction with respect to the support portion 32 are prohibited, and only movement away in the circumferential direction is possible.
Further, the detachment and engagement of the main body 60 and the concave portion 33 in the circumferential direction are smoothly performed because the two members are guided by the shape having the inclined portions on both sides in the radial direction. Further, a protruding portion 61 protruding in the circumferential direction is formed at the axially intermediate portion on the second main surface 64 side of the main body 60. As shown in FIG. 12, the protruding portions 61 are in contact with both ends in the circumferential direction of the first window hole 48 of the intermediate member 4. The both ends in the axial direction of the protrusion 61 are shown in FIG.
As is clear from FIG. 5, the inclination is such that the height in the axial direction decreases toward the outer side in the circumferential direction. The inclined surface 65 of the projection 61 is sandwiched between the first and second plates 12 and 13. More specifically, the protrusion 61 is
In the axial direction of the circumferential edge, more specifically, in the axial direction of a portion further in the circumferential direction than the concave portion 33 (center side of the support portion 32). That is, the first sheet 7 is
In the state where the second plates 12 and 13 are engaged, the movement in the axial direction is restricted. The projecting portion 61 has an inclined surface 65.
Is formed, the operation in which the protruding portion 61 is detached from and engaged with the first and second plates 12 and 13 in the circumferential direction is guided by the inclined surface 65 to be smooth. On the first main surface 63 side of the main body 60, an insertion portion 62 protruding in the circumferential direction is formed. The insertion portion 62 has a columnar shape wider than the main body 60, and has the first surface 34 of the support portion 32 and the second surface 34.
It is in contact with the surface 35. The insertion portion 62 is inserted into the end turn of the large coil spring 5a, and its outer peripheral surface is in contact with the inner peripheral surface of the end turn. An end turn of the small coil spring 5b is in contact with the main surface of the insertion portion 62. With this structure, both ends of the first spring 5 in the circumferential direction are engaged with the first seat 7, and are not movable in the radial direction and the axial direction.

The radial width of the main body 60 of the first sheet 7 corresponds to the radial width of the first window 48 of the intermediate member 4.
The main body 60 is disposed at both ends in the circumferential direction of the first window hole 48,
It is arranged to be able to abut or abut on both ends. More specifically, the protruding portion 61 formed on the main body 60 is in contact with the circumferential edge as shown in FIG. In this state, the movement and rotation of the first sheet 7 in the radial direction with respect to the intermediate member 4 are prohibited, and only the movement in the circumferential direction is possible. In addition, the main body 60, the protruding portion 61 and the first window hole 4
The separation and engagement in the circumferential direction with the end portion 8 are smoothly performed by guiding both members in a shape having inclined portions on both radial sides.

In the neutral state and the torsion state, the first spring 7 is always engaged with the first and second plates 12, 13 or the intermediate member 4 so as not to move in the radial direction. Outward movement is restricted. Further, since the first spring 5 is restricted from moving in the axial direction by the first and second plates 12, 13, the first spring 5 moves in the axial direction with respect to the first and second plates 12, 13. Movement is restricted. For this reason, it is not necessary to provide a member for restricting the movement of the first spring 5 in the axial direction on the first and second plates 12 and 13. As a result, the shapes of the first and second plates 12 and 13 are simplified. Further, the first spring 5 can increase the average diameter. First spring 5
In FIG. 2, half or more of the first and second plates 12, 13 protrude in the axial direction, and the whole appears to be exposed even in the plan view of FIG.

To summarize the functions of the first sheet 7 described above, the first sheet 7 is composed of two first sheets 7 arranged in the axial direction.
The torque is transmitted by supporting both ends of the spring 5 in the circumferential direction, and a pair of the first springs 5 is connected to the first and second plates 12 and 12.
13 is engaged. As shown in FIGS. 12 and 17, a second torsion angle θ2 is secured between the first main surface 56 of the second sheet 8 and the stop surface 71. In this manner, the second stopper 10 that allows the relative rotation between the intermediate member 4 and the output member 3 (such as the hub flange 20) only within θ2 by the second sheet 8 and the second window hole 49 of the intermediate member 4.
5 are formed. Here, since the sheet is used as the stopper constituent member, the structure is simple. θ2 is smaller than θ3.

The second springs 6 are arranged on both sides of the intermediate member 4 in the axial direction. More specifically, the second spring 6 is disposed on both sides of the intermediate member 4 in the axial direction of the second window hole 49, and is disposed in a housing portion 44 (described later) of the hub flange 20. Second
The spring 6 is a coil spring as is apparent from FIG. The length of the second spring 6 in the circumferential direction is shorter than that of the first spring 5, but the compressible tearing angle is substantially equal. Further, the second spring 6 has a larger wire diameter than the large coil spring 5a, but the spring constant of the first spring 5 is substantially equal to that of the whole spring 1a. Each of the second springs 6 includes a support 21
Abuts or is arranged to be able to abut on the circumferential end face. More specifically, the end turn of the second spring 6 is the first surface 42.
And the second surface 43.

Next, the second sheet 8 will be described in detail with reference to FIG. The second sheet 8 is a member that is elongated in the axial direction and is made of, for example, a resin. The second sheet 8 penetrates both ends in the circumferential direction of the second window hole 49 of the intermediate member 4, and both ends in the axial direction are between the support part 21 and the second spring 6 in the housing part 44 (described later) of the hub flange 20. Are located in Specific components of the second sheet 8 will be described. Second
The seat 8 mainly includes a main body 52 extending in the axial direction. The main body 52 has a shorter radial width than the second spring 6. The main body 52 includes a first main surface 56 on the second spring 6 side,
The second main surface 57 on the support portion 21 side is formed. First
An end winding end of the second spring 6 is in contact with or close to the main surface 56 so as to be in contact therewith. As described above, the main body 52 includes the second spring 6.
The main body 52 has a small width in the radial direction with respect to the second spring 6.
Abuts only on the apexes on both sides in the axial direction. As shown in FIG. 11, the width of the second main surface 57 is shorter than that of the first main surface 56, and the cross section has a smooth trapezoidal or chevron shape with rounded corners. As shown in FIG. 11, the main body 52 is disposed in the concave portion 41 formed in the support portion 21 of the hub flange 20 and is in a state of being in close contact with the end surface thereof. In this state, movement and rotation of the main body 52, that is, the second sheet 8 in the radial direction with respect to the support portion 21 are prohibited, and only movement away in the circumferential direction is possible. Further, the separation and engagement of the second sheet 8 and the concave portion 41 in the circumferential direction are smoothly performed because the two members are guided by the shape having the inclined portions on both sides in the radial direction. Further, the second main surface 57 of the main body 52
A protruding portion 53 protruding in the circumferential direction is formed at an intermediate portion in the axial direction. As shown in FIG. 12, the projecting portions 53 are in contact with both circumferential ends of the second window 49 of the intermediate member 4. 8, both ends in the axial direction of the protruding portion 53 are inclined so that the height in the axial direction becomes lower toward the outer side in the circumferential direction. Inclined surface 58 of projection 53
Is sandwiched between a pair of hub flanges 20. More specifically, the protruding portion 53 is sandwiched between both ends of the support portion 21 in the circumferential direction in the axial direction. More specifically, the support portion 21 is further deeper in the circumferential direction than the concave portion 41 (center side of the support portion 32). )
Is sandwiched between the parts. That is, the movement of the second sheet 8 in the axial direction while being engaged with the hub flange 20 is restricted. An insertion portion 54 that protrudes in the circumferential direction is formed on the first main surface 56 side of the main body 52. The insertion portion 54 has a cylindrical shape, is inserted into the end turn of the second spring 6, and its outer peripheral surface is in contact with the inner peripheral surface of the end turn. With this structure, both ends of the second spring 6 in the circumferential direction are engaged with the second seat 8, and are not movable in the radial direction and the axial direction.

The radial width of the main body 52 of the second sheet 8 corresponds to the radial width of the second window 49 of the intermediate member 4.
The main body 52 is arranged at both ends in the circumferential direction of the second window hole 49, and is arranged so as to abut or abut at both ends. More specifically, the projecting portion 53 formed on the main body 52 is in contact with the circumferential edge as shown in FIG. In this state, the movement and rotation of the second sheet 8 in the radial direction with respect to the intermediate member 4 are prohibited, and only the movement in the circumferential direction is possible. In addition, the main body 52 and the protruding portion 53 and the second window hole 4
Disengagement and engagement in the circumferential direction with the end portion 9 are guided by a shape having inclined portions on both sides, and are smoothly performed.

Further, since the second seat 8 is always immovably engaged with the hub flange 20 or the intermediate member 4 in the neutral state and the tearing state, the second spring 6 always moves outward in the radial direction. Movement is restricted. Further, since the second spring 6 is restricted from moving in the axial direction by the hub flange 20, the second spring 6 is
Are restricted from moving in the axial direction. For this reason,
There is no need to provide a member on the hub flange 20 for restricting the movement of the second spring 6 in the axial direction. As a result,
The shape of the hub flange 20 is simplified. Further, the second spring 6 can increase the average diameter. Half or more of the second spring 6 protrudes from the hub flange 20 in the axial direction, and the entire second spring 6 appears to be exposed even in a plan view in FIG.

The functions of the second seat 8 described above can be summarized as follows: the two second springs 6 arranged in the axial direction are supported at both circumferential ends thereof to transmit torque, and a pair of second springs 6 are provided.
The spring 6 is engaged with the hub flange 20. As a result, the pair of first springs 5 is arranged at each position with the intermediate member 4 interposed therebetween in the axial direction. More specifically,
The first spring 5 extends along the first window hole 48 of the intermediate member 4 and contacts both sides of the first window hole 48 in the radial direction. As described above, the pair of first springs 5 is axially positioned with respect to the first and second plates 12, 13 via the first sheet 7, and the pair of first springs 5 is an intermediate member. Are positioned between the first and second plates 12, 13 and the intermediate member 4 in the axial direction. The pair of second springs 6 are arranged on the inner peripheral side of each of the first springs 5 with the intermediate member 4 interposed therebetween in the axial direction. More specifically, the second spring 6 extends along the second window hole 49 of the intermediate member 4 and is in contact with both sides of the second window hole 49 in the radial direction. As described above, the pair of second springs 6
Are positioned in the axial direction with respect to the hub flange 20 via the second sheet 8, and the pair of second springs 6 sandwich the intermediate member 4 between the hub flange 20 and the intermediate member 4. Axial positioning is performed.

Further, the pair of first springs 5 and the pair of second springs 6 are close to each other in the radial direction and close to each other without any other members interposed therebetween. That is, the first spring 5 and the second spring 6 are arranged as densely as possible in a limited space in the axial direction and the radial direction. To explain the above structure from another viewpoint, the input member 2, the pair of first springs 5, the pair of first sheets 7, and the intermediate member 4 constitute a third damper 103, and the intermediate member 4, The pair of second springs 6, the pair of second seats 8, and the output member 3 form a second damper 102. Each of the dampers 102 and 103 includes a first rotating plate (intermediate member 4), a pair of second rotating plates (plates 12, 13 or a pair of hub flanges 20), and a pair of coil springs (first spring 5). Or, the second spring 6) and a pair of sheets (the first sheet 7 or the second sheet 8). The first rotating plate has a first window (window hole). 1
The pair of second rotating plates are fixed to each other on both axial sides of the first window, and each have a second window (accommodating portion) corresponding to the first window. The pair of coil springs are disposed on both axial sides of the first window of the first rotating plate, and are disposed in the second window. A pair of sheets is the first
A body extends axially through both ends of the window in the circumferential direction and has both ends in the axial direction engaged with a pair of coil springs.

This damper mechanism includes a pair of coil springs arranged in parallel in torque transmission, and further includes a pair of seats engaged with both ends in the circumferential direction of the pair of coil springs. Here, since two coil springs are supported by a pair of sheets,
The number of parts is reduced. In the present embodiment, two damper mechanisms described above are arranged in series, but only one may be used as another application example. In that case,
The first rotating plate becomes the flange of the hub and the pair of second rotating plates becomes the conventional input side plate. Or vice versa.

Output member 3 (damper disk assembly)
Is mainly composed of a pair of hubs 16 and a pair of hub flanges 20.
(Annular rotating member) and a first damper 101 (damper mechanism) for elastically connecting both members in the rotating direction. The hub 16 and the pair of hub flanges 20
May be regarded as the first damper. The two hubs 16 are arranged side by side in the axial direction so as to engage with the shaft 110 in a relatively non-rotatable manner. Each hub 16 has a cylindrical boss 18 and a flange 9 extending radially outward from the boss 18.
Four. As shown in FIG. 7, a plurality of outer teeth 94a projecting further outward from the flange 94 are formed. The plurality of outer teeth 94a are formed at regular intervals in the circumferential direction, and in this embodiment, there are a total of six teeth 94a. An axially extending spline 18 a is formed in the center hole (inner peripheral surface) of each boss 18. This spline 18a is engaged with the spline 110a of the shaft 110. Thus, torque can be output from the pair of hubs 16 to the shaft 110.

The hub flange 20 is an annular plate member arranged on the outer peripheral side of each hub 16. The inner peripheral surface of each hub flange 20 is provided with inner peripheral teeth 97 that engage with the outer peripheral teeth 94 a of the hub 16. A predetermined gap is secured between the inner peripheral teeth 97 and the outer peripheral teeth 94a in the rotation direction. The pair of hubs 16 and the hub flange 20 can rotate relative to each other within the twist angle θ1 of the gap. In this embodiment, the torsion angle is defined as one rotating member (for example, the hub 16).
With respect to the other rotating member (for example, the hub flange 20) from the neutral position to the positive side or the negative side (arrow R1 side or R
2) is described as a circumferential angle that can be twisted to one side. As described above, the first stopper 104 is configured by the inner peripheral teeth 97 and the outer peripheral teeth 94a. The pair of hub flanges 20 are fixed to each other by a plurality of second pins 15 (fixing members) arranged in the circumferential direction. The second pin 15 extends in the axial direction to fix the two hub flanges 20 to each other. This second pin 1
5 allows the pair of hub flanges 20 to be positioned in the axial direction and to rotate integrally. A plurality of holes 45 to which the second pin 15 is fixed are formed in the annular portion of the hub flange 20. The second pin 15 is connected to the intermediate member 4.
Are arranged further inward of the center hole 46 so as not to interfere with the intermediate member 4. The hub flange 20 on the axial direction engine has the same axial position as the first plate 12, and the hub flange 20 on the axial transmission side has the same axial position as the second plate 13.

Annular washers 26 are arranged in contact with both sides of the inner peripheral portion of the intermediate member 4. Wave springs 27 are arranged between the washer 26 and the hub flanges 20 on both sides. The wave spring 27 is disposed in a state of being compressed in the axial direction, and urges the washer 26 toward the intermediate member 4. The wave spring 27 is bent alternately in the radial direction, and is located radially inward with respect to the second pin 15 and radially outward with respect to the small spring 75 (described later). I have. The washer 26 has a second pin 1
A hole 85 through which 5 passes is formed. As a result, the washer 26 is engaged with the second pin 15 so as not to be able to rotate and move in the radial direction and to be movable in the axial direction. The washer 26 has a friction surface 88 that contacts the intermediate member 4.
On the outer peripheral side. Further, the washer 26 has a plurality of protrusions 86 protruding radially inward at the inner peripheral edge. The aforementioned wave spring 27 is provided with the projection 8
6. A notch 87 is formed between the projections 86. Since the notch 87 corresponds to the position of the small spring 75, interference between the small spring 75 and the washer 26 when the small spring 75 is twisted is prevented.

Washer 26 and wave spring 27
With the configuration described above, the axial positioning of the hub flange 20 and the intermediate member 4 is performed, and the frictional resistance (hysteresis torque) between the intermediate member 4 and the washer 26 when the intermediate member 4 and the hub flange 20 relatively rotate. Is caused to occur. The hub flange 20 is formed with a plurality of support portions 21 extending further radially outward from the annular portion. The support portion 21 has a structure for supporting both ends of the second spring 6 in the circumferential direction. The support portion 21 has a fan shape whose circumferential width increases radially outward. A notch-shaped concave portion 41 is formed at a radially intermediate portion of the circumferential end surface of the support portion 21. The concave portion 41 has a trapezoidal shape in which the width in the radial direction becomes narrower from the middle to the depth, and both corners have a smooth shape with sharp corners. As a result, the first surface 42, the concave portion 41, and the second surface 43 are formed on the circumferential end surface of the support portion 21 from the inner peripheral side toward the outer peripheral side. An accommodating portion 44 for accommodating a second spring 6 to be described later is provided between the support portions 21 adjacent in the circumferential direction. The housing portion 44 corresponds to the second window hole 49 of the intermediate member 4.

An annular plate 90 (positioning member) is fixed to the outside of each hub flange 20 in the axial direction by a second pin 15. The inner periphery of the plate 90 is located outside the flange 94 of each hub 16 in the axial direction. As a result, each hub 16 is not detached axially outward from the pair of hub flanges 20. That is, the plate 90 axially positions the two hubs 16 with respect to the two hub flanges 20. Note that an annular washer 91 is disposed between the flange 94 and the inner peripheral portion of the plate 90. The washer 91 constitutes a friction generating mechanism for generating friction when the two hubs 16 and the two hub flanges 20 rotate relative to each other.

Next, the first damper 101 will be described. The first damper 101 has a pair of hub flanges 20 and 1.
This is a mechanism for elastically connecting the pair of hubs 16 in the rotational direction. As shown in FIGS. 13 and 14, the first damper 101 is disposed between the pair of hub flanges 20 in the axial direction. That is, the axial position of the first damper 101 is between the axial positions of the pair of hub flanges 20. Since the first damper 101 is not disposed outside the pair of hub flanges 20 in the axial direction, the axial dimension of the entire clutch disc assembly 1 does not increase. Further, since the first damper 101 (also the small spring 75) is located at an axial position different from the respective teeth 97 and 94a of the hub flange 20 and the hub 16, a plurality of outer teeth 94a and inner teeth 97 are provided over the entire circumference. be able to. For this reason,
By ensuring a sufficient contact area between the outer teeth 94a and the inner teeth 97, the surface pressure on each of the teeth 94a and 97 can be kept small.

The position of the first damper 101 will be described in more detail. First, the radial position of the first damper 101 will be described. The first damper 101 is arranged on the inner peripheral side of the intermediate member 4. That is, the outer diameter of the first damper 101 is smaller than the inner diameter (center hole 46) of the intermediate member 4, and the axial positions of the two substantially coincide. A plurality of second pins 15 are arranged between the center hole 46 of the intermediate member 4 and the radial direction of the first damper 101, as shown in FIG. Further, the first damper 101 is arranged on the outer peripheral side of the shaft 11, and no other member is arranged between both. That is, the inner diameter of the first damper 101 is substantially equal to the outer diameter of the shaft 110. Next, the first damper 1
The axial position 01 will be described. The outer peripheral portion of the first damper 1 is located between the inner peripheral portions of the pair of washers 26, and the inner peripheral portion of the first damper 1 is located between the bosses 18 of the pair of hubs 16. A gap is secured in the axial direction between the outer peripheral portion of the first damper 1 and the inner peripheral portion of the pair of washers 26, so that no friction occurs between the two.

The first damper 101 (damper mechanism) includes the drive plate 76 (first member) and the driven plate 7
7 (second member) and a small spring 75 (elastic member). The drive plate 76 receives torque from the two hub flanges 20. Driven plate 77
Outputs torque to shaft 110. The small spring 75 is compressed between the drive plate 76 and the driven plate 77 when the two rotate relative to each other. Drive plate 76
The inner peripheral portion is disposed between the two hubs 16 in the axial direction. Thus, the diameter of the drive plate 76 can be reduced. The drive plate 76 is an annular plate member, and has a plurality of notches 79 on the outer peripheral side in the circumferential direction. The notch 79 is a portion whose outer peripheral side is open, and the small spring 75 is disposed there.

The small spring 75 is an elastic member that is compressed when the two hubs 16 and the two hub flanges 20 rotate relative to each other. Notches 7 at both ends in the circumferential direction of the small spring 75
9 are in contact with both ends in the circumferential direction. Furthermore, the notch 79
Are formed at both ends in the circumferential direction. As a result, the small spring 75 does not separate from the drive plate 76 in the radial direction and the axial direction. The outer peripheral edge of the drive plate 76
A concave portion 81 that engages with the radially inner portion of the pin 15 is formed. By this engagement, the drive plate 76 rotates integrally with the second pin 15, that is, the hub flange 20. As a result, the two hub flanges 20
Is transmitted to the drive plate 76 via the second pin 15.
Is transmitted to The drive plate 76 is movable in the axial direction with respect to the second pin 15. The inner diameter of the drive plate 76 is the spline 110a of the shaft 110.
The drive plate 76 does not interfere with the shaft 110 because it is slightly larger than the outside diameter of the drive plate 76.

The driven plate 77 is a pair of annular plate members arranged on both sides of the drive plate 76 in the axial direction. Driven plate 77 is drive plate 7
6, the inner and outer diameters are almost the same. As shown in FIG. 4, a notch 77 a for preventing interference with the second pin 15 is formed on the outer peripheral edge of the driven plate 77.
Further, the inner peripheral portion of the driven plate 77 has a pair of bosses 1.
8 in the axial direction. For this reason, the diameter of the driven plate 77 is small. A plurality of engaging teeth 84 are formed on the inner peripheral edge of the pair of driven plates 77. The engagement teeth 84 are connected to the splines 110 of the shaft 110.
a. As described above, since the driven plate 77 directly engages with the shaft 110 to directly output torque to the shaft 110, the two hubs 16
It is not necessary to provide teeth or the like for engaging with the output side member of the first damper 101. Therefore, a pair of hubs 1
The structure of No. 6 is simplified, and the processing cost can be reduced.

The driven plate 77 has a notch 83 for accommodating the small spring 75. The notch 83 opens radially outward. The circumferential ends of the small spring 75 are in contact with the circumferential ends of the notch 83. Inner circumference of drive plate 76 and driven plates 77 on both sides thereof
Washers 92 are respectively disposed between the inner peripheral portions of the washer. The washer 92 is a friction generating mechanism for generating friction when the two hubs 16 and the two hub flanges 20 rotate relative to each other.

Further, a wave spring 89 is arranged between the inner peripheral portion of the pair of driven plates 77 and the flange 94. The wave spring 89 is compressed in the axial direction. A pair of driven plates 77
Are biased in a direction approaching each other by the bias of the wave spring 89, and are pressed against the drive plate 76 via the washer 92. That is, the washer 92 is sandwiched between the inner peripheral portion of the drive plate 76 and the inner peripheral portions of the driven plates 77 on both sides thereof. Further, the pair of hubs 16 is provided with a wave spring 89.
And is pressed against the inner peripheral portion of the plate 90 via the washer 91. That is, the washer 91 is connected to the flange 9 of the hub 16.
4 and the inner peripheral portion of the plate 90.

The inner peripheral portion of each driven plate 77 and the axially inner end face of each hub 16 may be separated from each other,
Since they do not rotate relative to each other, they may be in contact with each other.
As the wear of the washers 91 and 92 progresses, the axial gap between the driven plate 77 and the hub 16 increases. The first damper 101 and the pair of hubs 16 are axially positioned with respect to the pair of hub flanges 20 by a wave spring 89.

In the above structure, the first damper 101
The features that have been miniaturized in order to arrange in a limited space will be described together. First, since the small spring 75 is moved in the radial and axial directions by the projections 80 inserted into the small spring 75, the support structure is arranged radially outside and small outside the small spring 75. No need. For example, the notches 79 and 83 do not have a portion disposed radially outward or axially outward of the small spring 75. Therefore, the axial dimension of the first damper 101 is substantially equal to the axial dimension of the small spring 75, and the outer diameter of the first damper 101 is
Is substantially equal to the radial position of the outer peripheral side portion of. Second
In addition, the first damper 101 outputs torque directly to the shaft 110 without passing through the hub 16. Specifically, the first damper 101 is directly engaged with the shaft 110 in an axial gap between the two hubs. Thereby, the outer diameter of the first damper 101 can be kept small. When the first damper is configured to be engaged with the hub, the first damper is disposed on the outer peripheral side of the hub, and the outer diameter of the first damper increases. Furthermore, the first damper 1
01 is a conventional spline 110 of the shaft 110
a, and there is no need to newly provide a special structure for engagement. Further, the first damper 101 is connected to the hub 16.
, There is no need to provide engaging teeth or the like on the outer peripheral surface of the hub 16, and manufacturing costs can be reduced.

FIG. 18 is a mechanical circuit diagram relating to the damper mechanism of the clutch disk assembly 1 according to the present invention. This mechanical circuit diagram is a diagram for explaining the relationship of members when the damper mechanism of the clutch disk assembly 1 operates in the positive region of the torsional characteristic. The first spring 5 uses a pair of springs arranged in the axial direction as one unit, and the second spring 6 uses a pair of springs arranged in the axial direction as one unit. As is clear from this mechanical circuit diagram, the damper mechanism formed between the input member 2 and the shaft 110 is composed of a first damper 101 and a second damper 102 arranged to act in series.
And a third damper 103. In the region where the torsion angle is small, only the first damper 101 operates,
Next, the second damper 102 and the third damper 103 are operated in series, and the operation of one damper is stopped halfway, and only the other damper is operated. First
The damper 101 mainly includes a small spring 75 and has the lowest rigidity. The second damper 102 and the third damper 103 are the second
Each of the spring 6 and the first spring 5 has substantially the same rigidity. Each damper 101, 102, 103
, Each stopper 104, 105, 106 is arranged in parallel. For this reason, each stopper 104, 10
When contact occurs at 5, 106, each damper 10
The compression of the small springs 75, the second spring 6, and the first spring 5 of 1, 102, and 103 is stopped.

The torque transmitting operation of the clutch disk assembly 1 will be described. When the friction portion 11 of the input member 2 is pressed against a flywheel (not shown), torque is input to the clutch disc assembly 1. The torque is applied in the order of the first spring 5, the first seat 7, the intermediate member 4, the second spring 6, the second seat 8, the hub flange 20, the first damper 101, and the hub 16 from the first and second plates 12, 13. Is transmitted to As a result, the torque is output to a shaft 110 extending from a transmission (not shown).

When the torque fluctuation from the engine is input to the clutch disk assembly 1, the input member 2 and the output member 3
Between the small spring 75 and a plurality of pairs of the first springs.
The spring 5 and a plurality of pairs of second springs 6 are compressed in series.
The operation of the clutch disk assembly 1 when torsional vibration occurs will be described. Here, the friction portion 1 of the input member 2
1 is fixed to another member, and the shaft 1
10 will be described as an operation of statically twisting in one direction. FIG.
FIG. 9 is a torsion characteristic diagram used to explain the operation in FIG.
When the input member 2 is twisted to the second side (the input member 2 is twisted to the rotation direction R1 side, that is, the positive side with respect to the shaft 110), it indicates a positive side area. In FIG. 18, the shaft 110 is
Twist to two sides. Then, the outer teeth 94a and the inner teeth 97
In the range of the torsion angle θ1 until the small spring 75
Is compressed. As a result, a low-rigidity first-stage characteristic is obtained in the torsional characteristic diagram shown in FIG. At this time, slip occurs due to the friction generating mechanism including the washers 91 and 92,
Low hysteresis torque is generated. Such low rigidity
Due to the characteristic of low hysteresis torque, for example, a small torsional vibration during idling in a diesel vehicle can be effectively absorbed. In the first stage, the high-rigidity first and second springs 5 and 6 are hardly compressed. After the contact occurs at the first stopper 104, the small spring 75 is not further compressed. That is, at the angle a or more, the torque is transmitted by the first stopper 104 in the output member 3.

After the angle a (= θ1), the first spring 5 and the second spring
Since the spring 6 and the spring 6 are compressed in series, a rigidity characteristic higher than the first stage range is obtained. At this time washer 2
6 slides against the intermediate member 4 to generate a relatively large hysteresis torque. Torsional angle b (= θ1 + θ2)
Then, the contact occurs at the second stopper 105, the relative rotation between the intermediate member 4 and the hub flange 20 is stopped, and as a result, the compression of the second spring 6 is stopped. As a result, when the torsion angle is equal to or larger than the angle b, only the first spring 5 is compressed, and a higher stiffness than the second stage range is obtained. Torsion angle c (= θ1 + θ3)
Then, the contact occurs at the third stopper 106, and the relative rotation between the input member 2 and the output member 3 stops.

Next, the operation when the second spring 6 and the first spring 5 are compressed in series will be described in detail. The output member 3 is twisted to the R2 side. Then, the support portion 21 of the hub flange 20 moves together with the second sheet 8 on the R1 side to the second position.
The spring 6 is pushed toward R2. The second sheet 8 on the R1 side moves away from the R1 side end of the second window hole 49 of the intermediate member 4 toward the R2 side. Further, the support portion 21 engaged with the second sheet 8 on the R2 side moves away from the second sheet 8 toward the R2 side. As a result, the second spring 6 is compressed between the hub flange 20 and the intermediate member 4 via the second sheets 8 on both sides.

In the above operation, the R1 end of the second spring 6 is restricted from moving in the radial and axial directions by the hub flange 20 via the second seat 8 on the R1 side. The side end is restricted from moving in the radial direction by the intermediate member 4 via the second sheet 8 on the R2 side. Also a pair of second
Since the spring 6 sandwiches the intermediate member 4 in the axial direction, it is difficult to move in the axial direction.

On the other hand, the intermediate member 4 urged to the R2 side
Move to the second side, and push the first sheet 7 on the R1 side to the R2 side.
The first sheet 7 on the R1 side includes first and second plates 12, 1
3, the first spring 5 is pushed toward the R2 side while moving away from the R1 side support portion 32 toward the R2 side. The R2 side of the first spring 5 is supported by the support portion 32 of the first and second plates 12, 13 and the second sheet 8 on the R2 side. For this reason, the first spring 5 is compressed between the intermediate member 4 and the first and second plates 12 and 13 via the first sheets 7 on both sides.

In the above operation, the end of the first spring 5 on the R1 side is restricted from moving in the radial direction by the intermediate member 4 via the first sheet 7 on the R1 side. R
1st and 2nd plate 1 via 2nd 1st sheet 7
The movements in the radial and axial directions are regulated by the members 2 and 13. Further, since the pair of first springs 5 sandwich the intermediate member 4 in the axial direction, it is difficult to move in the axial direction.

When the output member 3 is twisted to the R1 side, R1 and R2 are interchanged in the above description. [Modification] A stopper between the pair of hubs 16 and the intermediate member 4 is constituted by a second pin 15 and a notch or hole 47 provided on the inner peripheral edge of the intermediate member 4 as shown in FIGS. You may.

Further, as a stopper between the intermediate member 4 and the input member 2, as shown in FIGS.
The window 48 is divided into two parts in the circumferential direction, and the first window 48
A stop surface 74 that can contact the sheet 7 may be formed. Furthermore, as shown in FIG. 24, the close contact of the springs or the contact between the spring seats may be used without using a special stopper mechanism. For example, if the configuration is such that the close contact of the second spring 6 occurs before the close contact of the first spring 5, high rigidity characteristics can be obtained after the close contact of the second spring 6.

The above-described stopper mechanisms (engagement of the pin with the hole or notch, engagement of the spring seat with the stop surface, close contact of the spring or contact of the spring seats) are the first and second stages. The eye stoppers may be realized by the same type or different types of combinations. The present invention is not limited to the clutch disk assembly, but can be applied to other damper disk assemblies. For example, a damper disk assembly for elastically connecting two flywheels in a rotational direction and a damper disk assembly used for a lock-up device of a torque converter.

The first-stage damper disk assembly according to the present invention can be employed in a mechanism in which separate clutch disk assemblies are provided for two hubs.

[0067]

In the damper disk assembly according to the present invention, since the damper mechanism is not disposed axially outside of the two annular rotating members, the space of the entire damper disk assembly can be reduced.

[Brief description of the drawings]

FIG. 1 is a clutch disc assembly according to a first embodiment of the present invention.

FIG. 2 is a plan view of the clutch disk assembly, as viewed in the direction of arrow II in FIG. 1;

FIG. 3 is a plan view of the clutch disk assembly with each part removed stepwise;

FIG. 4 is a partially enlarged view of FIG. 3;

FIG. 5 is a plan view of a plate.

FIG. 6 is a plan view of an intermediate member.

FIG. 7 is a plan view of a hub and a hub flange.

FIG. 8 is a partial cross section showing the configuration of a first spring and a first seat.

FIG. 9 is a partial sectional view showing a structure of a second spring and a second seat.

FIG. 10 is a partially enlarged view of FIG. 3;

FIG. 11 is a partially enlarged view of FIG. 3;

FIG. 12 is a partially enlarged view of FIG. 3;

FIG. 13 is a partially enlarged view of FIG. 1;

FIG. 14 is a partially enlarged view of FIG. 1;

FIG. 15 is a plan view of a washer.

16 is a sectional view taken along the line XVI-XVI of FIG.

FIG. 17 is a schematic plan view showing the structure of a first stopper and a second stopper.

FIG. 18 is a mechanical circuit diagram of a clutch disk assembly.

FIG. 19 is a torsional characteristic diagram of the clutch disk assembly.

FIG. 20 is a schematic plan view showing the structure of a first stopper and a second stopper.

FIG. 21 is a mechanical circuit diagram of a clutch disk assembly.

FIG. 22 is a schematic plan view showing the structure of a first stopper and a second stopper.

FIG. 23 is a mechanical circuit diagram of a clutch disk assembly.

FIG. 24 is a mechanical circuit diagram of a clutch disk assembly.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Clutch disk assembly 2 Input member 3 Output member 4 Intermediate member 5 1st spring 6 2nd spring 7 1st sheet 8 2nd sheet 11 Friction part 16 Hub 20 Hub flange 75 Torsion spring 76 Drive plate 78 Driven plate 101 1st Damper 110 shaft

Claims (15)

[Claims] 1. Two hubs which are arranged in the axial direction so as to engage with one shaft so as to be relatively non-rotatable, and two annular members which are respectively arranged on outer peripheral sides of the two hubs and fixed to each other. A damper having a rotating member, an elastic member compressed when the two hubs and the two annular rotating members rotate relative to each other, and having an axial position between the axial positions of the two annular rotating members. A damper disk assembly comprising: a mechanism; 2. The damper disk assembly according to claim 1, wherein said damper mechanism is at least partially disposed axially between said two hubs. 3. The damper disk assembly according to claim 1, wherein said two hubs and said two annular rotating members have stopper portions which come into contact with each other at a predetermined torsion angle. 4. The damper mechanism includes a first member to which torque is input from the two annular rotating members, a second member to output torque to the shaft, and the first member and the second member. 4. The elastic member according to claim 1, further comprising: an elastic member arranged to be compressed between the two members when the members rotate relative to each other.
A damper disk assembly according to any one of the above. 5. The damper disk according to claim 4, wherein the first member is an annular plate member having an inner peripheral portion disposed between the two hubs in the axial direction and supporting both sides of the elastic member in the rotation direction. Assembly. 6. The fixing device according to claim 5, further comprising a fixing member extending in an axial direction to fix the two annular rotating members to each other and engaged with the first member so as to be relatively non-rotatable. Damper disk assembly. 7. The second member according to claim 4, wherein an inner peripheral portion is disposed between the two hubs in the axial direction, and the second member is an annular plate member that supports both sides of the elastic member in the rotation direction. 4. The damper disk assembly according to claim 1. 8. The damper disk assembly according to claim 7, wherein said second member is directly engaged with said shaft. 9. The damper disk assembly according to claim 1, further comprising a positioning member for positioning said two hubs axially with respect to said two annular rotating members. 10. The damper disk assembly according to claim 1, further comprising a friction generating mechanism for generating friction when said two hubs and said two annular rotating members rotate relative to each other. . 11. Two hubs which are arranged in the axial direction so as to engage with one shaft in a relatively non-rotatable manner and have a plurality of outer peripheral teeth, and are respectively arranged on outer peripheral sides of the two hubs; Two annular rotating members having a plurality of inner peripheral teeth fixed to each other and relatively rotatable to a predetermined torsion angle with respect to the outer peripheral teeth, and arranged at different axial positions from the outer peripheral teeth and the inner peripheral teeth,
A damper disk assembly comprising: a damper mechanism having an elastic member that is compressed in a rotational direction when the two hubs and the two annular rotating members rotate relative to each other. 12. Two hubs arranged in the axial direction so as to engage with one shaft so as to be relatively non-rotatable, and two hubs arranged relative to the outer peripheral side of the two hubs so as to be relatively rotatable. An annular rotating member that regulates movement of the hubs in a direction away from each other in the axial direction; and an elastic member that is compressed when the two hubs and the annular rotating member relatively rotate, A damper mechanism partly interposed between the two hubs in the axial direction. 13. A hub having an inner peripheral surface on which a spline engaged with a shaft is formed, an annular rotating member disposed on the outer peripheral side of the hub so as to be relatively rotatable to a predetermined torsion angle, and the annular rotating member. A damper disk assembly comprising: a damper mechanism for elastically connecting a member and the shaft in a rotational direction. 14. The damper mechanism according to claim 1, wherein a first member to which torque is input from said annular rotating member, a second member directly engaged with said shaft, and a relative rotation between said first member and said second member. 14. The damper disk assembly according to claim 13, further comprising an elastic member arranged to be compressed between the two. 15. The damper disk assembly according to claim 14, wherein said second member is an annular plate member having engagement teeth formed on an inner peripheral edge thereof for engaging said shaft.