JP2001304341A - Seat member, elastic member assembly and damper mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a multistage characteristic with a simple structure in a damper mechanism. SOLUTION: Plates 12 and 13 have first window parts 51 and second window parts 52 of the same shape. A hub flange 6 has first window holes 53 and second window holes 54 of the same shape respectively, corresponding to the first window parts 51 and the second window parts 52. First elastic member assemblies 30 are arranged in the first window parts 51 and the first window holes 53, and have first coil springs 33 and first seat members 34. Second elastic assemblies are arranged in the second window parts 52 and the second window holes 54, and have second coil springs 36 and second seat members 37. When the first seat member 34 opens a clearance in the rotating direction from the first window hole 53, the first coil spring 33 is not compressed in a small torsional angle region, where the second coil spring 36 is compressed in the torsional characteristic, but is compressed in a large torsional angle region.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper mechanism for transmitting torque and absorbing / damping torsional vibration, an elastic member assembly used for the same, and a seat member used for the same.

[0002]

2. Description of the Related Art A damper mechanism used in a clutch disk assembly of a vehicle includes, for example, an input rotary member that can be connected to and disconnected from an input flywheel, and an output rotary member that is connected to an input shaft extending from a transmission. And a resilient connection mechanism for resiliently connecting the rotating members in the rotation direction. The input rotating member includes a clutch disk and a pair of input plates fixed to the inner peripheral side of the clutch disk. The output rotary member comprises a hub that is non-rotatably and axially movably connected to the input shaft. The hub has a cylindrical boss that is spline-engaged with the input shaft and a disk-shaped flange that extends radially outward therefrom. The elastic coupling mechanism includes a plurality of elastic member assemblies. Each elastic member assembly is composed of a single coil spring or a coil spring and sheet members disposed at both ends thereof. Each elastic member assembly is accommodated in a window formed in the flange, and both ends in the rotation direction are supported in the rotation direction. Also, each elastic member assembly is
It is supported in each direction by windows formed in a pair of input plates.

In the structure described above, when the pair of input plates and the hub rotate relative to each other, the coil spring is compressed in the rotational direction between the two members. Thus, the torsional vibration input to the clutch disk assembly is absorbed and attenuated by the damper mechanism. By the way, the noise of the drive system generated by the torsional vibration is classified into abnormal noise during idling, abnormal noise during traveling at a constant speed, abnormal noise during acceleration / deceleration, and muffled noise. Therefore, in order to absorb the torsional vibration that causes each abnormal noise, it is necessary to appropriately set the torsional characteristics of the damper mechanism. Specifically, a two-stage characteristic is used in which a region with a small torsion angle is made to have low rigidity and low hysteresis torque to absorb vibration during idling. In the two-stage characteristics described above,
Furthermore, in the area where the torsion angle is large, the medium rigidity and high hysteresis torque area for countermeasures against
There is also known a torsional characteristic that forms a high rigidity and high hysteresis torque region for noise suppression.

[0004]

The above-described damper mechanism for dividing a region having a large torsion angle into two regions further includes a first elastic member assembly and a second elastic member assembly. Both elastic members are disposed in the window of the flange, and both ends in the circumferential direction are supported in the rotation direction. Here, both ends in the circumferential direction of the second elastic member assembly are directly supported in the rotation direction by both ends in the circumferential direction of the window portion of the input plate, but the first elastic member assembly has both ends in the circumferential direction of the input plate. The window is supported at a predetermined angle from the circumferential end of the window. In the structure described above, when the input plate and the hub rotate relative to each other, initially, only the second elastic member assembly is compressed in the rotational direction, and a characteristic of medium rigidity is obtained. Subsequently, when the torsion angle is increased, the compression of the first elastic member assembly is started, and the two elastic member assemblies are compressed in parallel, whereby high rigidity characteristics are obtained.

In the above-described damper mechanism, a predetermined multi-stage torsion characteristic has been realized by a combination of a support portion (a window hole, a window portion) of a rotating member and an elastic member assembly. for that reason,
In order to realize different characteristics, hubs and plates must be manufactured for each of the torsional characteristics, and the types of rotating members have increased. In addition, the shape of the supporting portion is different in each rotating member, and the shape of each rotating member is complicated.

An object of the present invention is to solve the problem relating to the structure of a rotating member by enabling setting of the torsional characteristics of a damper mechanism irrespective of the rotating member.

[0007]

According to the present invention, there is provided a seat member for supporting an end of an elastic member disposed between a first rotating member and a second rotating member of a damper mechanism in a rotating direction. It is. The sheet member has a receiving surface for receiving an end of the elastic member, a first surface supported by the first rotating member,
A second surface is supported by the second rotating member, and has a second surface different in position in the rotation direction from the first surface. Here, the term “support” refers to a state of contact or contact in the rotational direction so that torque can be transmitted. The same applies hereinafter.

In this sheet member, since the rotational positions of the surfaces corresponding to the different members are different, the compression of the elastic member used by the sheet member must not be started to a predetermined twist angle without changing the shape of the rotating member. Can be. Thus, the torsional characteristics of the damper mechanism can be set by the seat member. An elastic member assembly according to a second aspect is arranged between the first rotating member and the second rotating member in the rotation direction of the damper mechanism, and supports the elastic member and an end of the elastic member. A pair of sheet members. 1
At least one of the pair of sheet members has a receiving surface for receiving an end of the elastic member and a first surface supported by the first rotating member.
And a second surface supported by the second rotating member and having a different rotational direction position from the first surface.

In this elastic member assembly, since at least one of the pair of sheet members has a different rotational position on each surface corresponding to a different member, compression of the elastic member can be prevented from starting to a predetermined twist angle. . Thus, the torsional characteristics of the damper mechanism can be set by the seat member. The elastic member assembly according to claim 3 is disposed between the first rotating member and the second rotating member in the rotation direction of the damper mechanism, and includes a first elastic member assembly, a second elastic member assembly, It has. The first elastic member assembly includes a first elastic member and a pair of first elastic members for supporting an end of the first elastic member.
And a sheet member. At least one of the pair of first sheet members has a first receiving surface for receiving an end of the elastic member, a first surface supported by the first rotating member, and a first surface supported by the second rotating member. And a second surface having a different rotational direction position. The second elastic member assembly is used to act in parallel with the first elastic member assembly.

This elastic member assembly has two types of elastic member assemblies acting in parallel. In the first sheet member of the first elastic member assembly, the rotational position of each surface corresponding to a different member is set. Are different. Therefore, by not starting the compression of the first elastic member to a predetermined torsion angle,
The region where only the elastic member is compressed, the first elastic member and the second
A multi-stage characteristic including an area where the elastic members are compressed in parallel can be realized. Thus, the torsional characteristics of the damper mechanism can be set by the combination of the elastic member assemblies.

According to a fourth aspect of the present invention, in the third aspect, both of the pair of first sheet members include a first receiving surface for receiving an end of the elastic member, and a first rotating member. And a second surface supported by the second rotating member and having a different rotational direction position from the first surface. In the elastic member assembly according to the fifth aspect, in the fourth aspect,
The second surface is located inside the first surface in the rotation direction.

According to a sixth aspect of the present invention, in the fifth aspect, the second elastic member assembly comprises a second elastic member and a pair of first elastic members for supporting an end of the second elastic member. And two sheet members. Each of the pair of second sheet members has a second receiving surface for receiving an end of the second elastic member,
It has a third surface supported by the first rotating member and a fourth surface supported by the second rotating member. The distance between the first surfaces of the first elastic member assembly is equal to the distance between the third surfaces of the second elastic member assembly.

In this elastic member assembly, a portion for supporting the first elastic member assembly in the first rotating member and the second rotating member are provided.
The rotational width angles of the portions for supporting the elastic member assembly are equal. This is made possible because the elastic member assembly can realize a multi-stage torsion characteristic, so that the elastic member supporting portion of the first rotating member can have the same shape.

According to a seventh aspect of the present invention, there is provided a damper mechanism including a first rotating member, a second rotating member, a first elastic member assembly, and a second elastic member assembly. The first rotating member has a first support portion and a second support portion having the same width angle in the rotation direction. Second
The rotation member has a third support portion and a fourth support portion corresponding to the first support portion and the second support portion, and having the same width angle in the rotation direction. The first elastic member assembly includes a first elastic member disposed in the first support portion and the third support portion, and a pair of first sheet members disposed at an end of the first elastic member. Second
The elastic member assembly is disposed in the second spring support and the fourth spring support. Each of the pair of first sheet members is a first sheet member.
It has a first surface supported by the support and a second surface supported by the fourth support. The rotational distance between the first surface and the first support is different from the rotational distance between the second surface and the fourth support.

In this damper mechanism, the first support portion and the second support portion of the first rotating member have the same width angle in the rotation direction, and
The third support portion and the fourth support portion of the second rotating member have the same width angle in the rotation direction. Since the supporting portions of the rotating members have the same shape, the structure of each member is simplified. This is possible because the elastic member assembly can realize a multi-stage torsion characteristic, so that the elastic member supporting portion of the rotating member can have the same shape.

In the damper mechanism described in claim 8, in claim 7, the first surface is in contact with the first support portion, and the second surface is spaced from the fourth support portion in the rotational direction. In this damper mechanism, the initial stage of the twist angle is the second stage.
When only the elastic member is compressed and the torsion angle is increased, the compression of the first elastic member is started, and the first elastic member and the second elastic member are compressed in parallel. As described above, the multi-stage characteristic can be realized not by the combination of the rotating member and the elastic member but by the elastic member assembly.

In the damper mechanism according to the ninth aspect, in the seventh or eighth aspect, the second elastic member assembly comprises a second elastic member and a pair of second elastic members disposed at an end of the second elastic member. And a sheet member. In the damper mechanism according to claim 10, in claim 9, each of the pair of second sheet members has a third surface supported by the second support portion and a fourth surface supported by the third support portion. have. The third surface is in contact with the second support, and the fourth surface is in contact with the third support.

[0018] A method of manufacturing a damper mechanism having different torsion characteristics according to claim 11 is an elastic member set for elastically connecting the first rotating member, the second rotating member, and both members in the rotational direction. A damper mechanism having a three-dimensional structure includes the following steps. ◎ Step of preparing two first rotating members and two second rotating members ◎ Step of combining one first rotating member and one second rotating member to form two rotating member assemblies ◎ Elastic member and sheet Steps of Incorporating Different Kinds of Elastic Member Assemblies into Two Rotating Member Assemblies Each Conventionally, Desired Torsion Characteristics have been Realized by Combining a Supporting Part of the Rotating Member and the Elastic Member Assemblies. Therefore, in order to realize different torsional characteristics, it is necessary to prepare rotating members having different shapes. On the other hand, in the invention according to claim 11, the elastic member assembly has a structure in which a desired torsional characteristic is realized by a combination of the elastic member and the sheet member, so that the shape of the supporting portion of the rotating member is considered. The need is gone. Therefore, it is possible to realize a damper mechanism having different torsional characteristics even if the same type of rotating member is used.

According to a twelfth aspect of the present invention, in the damper mechanism, the first
A rotating member, a second rotating member, a first elastic member assembly, and a second elastic member assembly are provided. The first rotating member has a first support portion and a second support portion having the same shape. The second rotating member is
A third support portion and a fourth support portion having the same shape and corresponding to the first support portion and the second support portion, respectively. The first elastic member assembly is disposed in the first support portion and the third support portion, and has a first elastic member and first sheet members disposed at both ends of the first elastic member. The second elastic member assembly is disposed in the second support portion and the fourth support portion, and has a second elastic member and second sheet members disposed at both ends of the second elastic member.
Since the first sheet member has a gap in the rotation direction from one of the first and third support portions, the first elastic member has a small torsion angle in a region where the second elastic member is compressed in the torsion characteristic. The region is not compressed in the region and is compressed in the region where the torsion angle is large.

Conventionally, multi-stage characteristics have been realized by a combination of a supporting portion of a rotating member and an elastic member assembly. Therefore, each rotating member has a supporting portion having a different shape. On the other hand, according to the twelfth aspect of the invention, since the elastic member assembly has a structure that realizes multi-stage characteristics by a combination of the elastic member and the sheet member, it is not necessary to consider the shape of the supporting portion of the rotating member. . Therefore, it is possible to make the shape of the support portion the same in each rotating member.

A seat member according to a thirteenth aspect is a sheet member for supporting an end of an elastic member disposed between the first rotating member and the second rotating member of the damper mechanism in the rotating direction. The seat member includes a seat portion and a low-rigidity elastic member. The seat part is a part for supporting the end of the elastic member. The low-rigidity elastic member is provided on the opposite side of the seat portion from the elastic member. The low-rigidity elastic member has lower rigidity than the elastic member, and is compressible in the rotation direction between the seat portion and the second rotating member.

In this seat member, since the seat portion is provided with the low-rigidity elastic member, the torsional rigidity of the damper mechanism can be adjusted by the seat member. Claim 1
According to a fourth aspect of the present invention, in the thirteenth aspect, the seat member further includes a contact portion integrally formed on the opposite side of the elastic member of the seat portion and supported by the first rotating member.

In this sheet member, the sheet member is rotatably supported by the first rotating member by the contact portion. In the sheet member according to the fifteenth aspect, in the fourteenth aspect, the contact portion is a pair of protrusions extending outward in the rotational direction from both ends in the axial direction of the seat portion. The low-rigidity elastic member is disposed between the pair of protrusions.

In this sheet member, the low-rigidity elastic member is 1
Since it is arranged between the pair of protrusions, contact with other members is prevented. The sheet member according to claim 16,
In Claim 14 or 15, the contact portion extends further outward in the rotation direction than the low-rigidity elastic member. In this sheet member, for example, the low-rigidity elastic member is not compressed when the torsion angle is small, and the low-rigidity elastic member can be compressed when the torsion angle is large.

According to a seventeenth aspect of the present invention, in the sheet member according to any one of the thirteenth to sixteenth aspects, a hole is formed on a side of the seat portion opposite to the elastic member. One end of the low rigidity elastic member is inserted into the hole. In this sheet member, the low-rigidity elastic member is inserted into the hole and is not easily dropped from the sheet portion.

The elastic member assembly according to the present invention is arranged between the first rotating member and the second rotating member of the damper mechanism in the rotating direction. The elastic member assembly includes an elastic member and a pair of sheet members. The pair of sheet members is a member for supporting the end of the elastic member. At least one of the pair of sheet members has a sheet portion for supporting an end of the elastic member, and a low-rigidity elastic member provided on the opposite side of the sheet portion from the elastic member. The low-rigidity elastic member has lower rigidity than the elastic member, and can be compressed in the rotation direction between the seat portion and the second rotating member.

In this elastic member assembly, by providing the low-rigidity elastic member on at least one of the pair of sheet members,
It is possible to obtain a low rigidity torsional characteristic by the low rigidity elastic member and a high rigidity torsional characteristic by the elastic member. In the elastic member assembly according to the nineteenth aspect, in the eighteenth aspect, the seat member further includes a contact portion integrally formed on a side of the seat portion opposite to the elastic member and supported by the first rotating member.

[0028] In the elastic member assembly according to the twentieth aspect,
In claim 19, the contact portion is a pair of protrusions extending outward in the rotation direction from both ends in the axial direction of the seat portion. The elastic member is disposed between the pair of protrusions. In the elastic member assembly according to claim 21, in claim 19 or 20,
The contact portion extends further outward in the rotation direction than the low-rigidity elastic member.

[0029] In the elastic member assembly according to the twenty-second aspect,
In any one of claims 18 to 21, a hole is formed on a side of the sheet portion opposite to the elastic member. One end of the low rigidity elastic member is inserted into the hole. A damper mechanism according to a twenty-third aspect includes a hub flange, a disk-shaped member, and an elastic member assembly. The hub flange has a hub and a flange. The flange extends from the hub to the outer peripheral side to form an elastic member support. The disk-shaped member has a low-rigidity elastic member support portion that is arranged on the side of the flange and corresponds to the elastic member support portion. The elastic member assembly is disposed in the first and low rigidity elastic member support portions, and has an elastic member and a pair of sheet members. The pair of sheet members is a member for supporting the end of the elastic member. At least one of the pair of sheet members has a sheet portion for supporting an end of the elastic member. The seat portion has a first surface that faces in the rotation direction with respect to one of the hub flange and the disc-shaped member, and a second surface that faces in the rotation direction with the other of the hub flange and the disc-shaped member.
Surface. The rotation direction angle between the second surface and the other is greater than the rotation direction angle between the first surface and the one. The one of the pair of sheet members includes a low-rigidity elastic member that is disposed between the second surface and the other and has lower rigidity than the elastic member.

In this damper mechanism, a low-rigidity elastic member is provided on at least one of the pair of sheet members. For this reason, low rigidity torsional characteristics are obtained by the low rigidity elastic member in a region where the torsional angle is small, and high rigidity torsional characteristics are obtained by the elastic member in a region where the torsional angle is large. In the damper mechanism according to claim 24, in claim 23, the hub and the flange are separate members. The damper mechanism further includes a low-rigidity damper. The low rigidity damper has lower rigidity than the elastic member. The low rigidity damper elastically connects the hub and the flange in the rotational direction.

In this damper mechanism, since the low-rigidity damper is provided in the eleventh aspect, the characteristics in the region where the torsional angle is small can be adjusted by the combination of the low-rigidity damper and the low-rigidity elastic member. In the damper mechanism according to the twenty-fifth aspect, in the twenty-fourth aspect, a torsion angle of
Thus, the first region where only the low-rigidity damper or the low-rigidity damper and the low-rigidity elastic member are compressed in series, the second region where only the low-rigidity elastic member is compressed, and the third region where only the elastic member is compressed are formed. Thus, the rigidity of the low-rigidity damper, the low-rigidity elastic member, and the elasticity of the elastic member are set.

According to this damper mechanism, the rigidity can be made higher in the second region having a larger torsion angle in the first region than in the first region, so that the small torsional vibration during idling can be quickly attenuated. In the damper mechanism according to the twenty-sixth aspect, the hub and the flange are formed integrally.

In this damper mechanism, since the hub and the flange are formed integrally, the low-rigidity elastic member realizes low-rigidity characteristics near a torsion angle of 0. In the damper mechanism according to the twenty-seventh aspect, in the twenty-sixth aspect, the rotation direction angle between the low rigidity elastic member on one side in the rotation direction and the other of the hub flange and the disc-shaped member in different elastic member assemblies is different.

In this damper mechanism, for example, only one low-rigidity elastic member is compressed first, and then the other low-rigidity elastic member is compressed. Rigidity characteristics can be provided, and as a result, small torsional vibration during idling can be effectively attenuated.

[0035]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment FIG. 1 is a plan view of a clutch disk assembly 1 as one embodiment of the present invention, and FIG. 2 is a sectional view thereof. The clutch disc assembly 1 is a power transmission device used for a clutch device of a vehicle, and has a clutch function and a damper mechanism. The clutch function is a function of transmitting and interrupting torque by connecting and disconnecting to and from a flywheel (not shown). The damper function is a function of absorbing and attenuating a torque fluctuation or the like input from the flywheel side by a spring or the like.

In FIG. 2, OO is the rotation shaft of the clutch disk assembly 1. An engine and a flywheel (not shown) are arranged on the left side of FIG. 2, and a transmission (not shown) is arranged on the right side of FIG. Further, the arrow R1 side in FIG. 1 is the drive side (rotation direction positive side) of the clutch disk assembly 1, and the arrow R2 side is the opposite side (rotation direction negative side). In the following description, the “rotational (circumferential) direction”, “axial direction”, and “radial direction” refer to the respective directions of the clutch disk assembly 1 as a rotating body, unless otherwise specified.

The clutch disk assembly 1 mainly includes an input rotary member 2, an output rotary member 3, and an elastic coupling mechanism 4 disposed between the rotary members 2, 3. In addition, each member constitutes a damper mechanism for transmitting torque and attenuating torsional vibration. The input rotary member 2 is a member to which torque is input from a flywheel (not shown). The input rotary member 2 mainly includes a clutch disk 11 and a clutch plate 12.
And a retaining plate 13.
The clutch disk 11 is a portion that is pressed and connected to a flywheel (not shown). The clutch disk 11 includes a cushioning plate 15 and a pair of friction facings 16 and 17 fixed on both sides in the axial direction by rivets 18.

The clutch plate 12 and the retaining plate 13 are both disk-shaped and annular members made of sheet metal, and are arranged at a predetermined distance from each other in the axial direction. The clutch plate 12 is arranged on the engine side, and the retaining plate 13 is arranged on the transmission side. Retaining plate 1
A cylindrical wall 22 extending toward the clutch plate 12 is formed on the outer peripheral portion of 3. Further, a plurality of fixing portions 23 extend radially inward from the tip of the wall 22. The fixing portion 23 is arranged on the transmission side surface of the clutch plate 12 and is fixed to each other by a plurality of rivets 20. As a result, the clutch plate 12 and the retaining plate 13 rotate integrally, and further, the axial distance is determined. In addition, rivet 2
Reference numeral 0 designates an inner peripheral portion of the cushioning plate 15 as a fixing portion 23.
And is fixed to the outer peripheral portion of the clutch plate 12.

Each of the clutch plate 12 and the retaining plate 13 has a center hole. A boss 7 described later is arranged in the center hole. Each of the clutch plate 12 and the retaining plate 13 has a plurality of windows (51, 52) arranged in the circumferential direction. Each of the windows (51, 52) has the same shape, and a total of 4 at the same radial position and at equal intervals in the circumferential direction.
One is formed. Each window (51, 52) extends substantially in the circumferential direction.

Here, a pair of windows arranged in the horizontal direction in FIG. 1 is referred to as a first window 51, and a pair of windows arranged in the vertical direction in FIG. It is referred to as the second window 52. First window 51 and second window 52
Are of the same shape, and these shapes will be described collectively. Each of the windows 51 and 52 includes a hole penetrating in the axial direction, and a support formed along the edge of the hole.
The support portion includes an outer peripheral side support portion 55, an inner peripheral side support portion 56, and a rotation direction support portion 57. In plan view, the outer peripheral side support portion 55 is curved in a shape substantially along the circumferential direction, and the inner peripheral side support portion 56 extends substantially linearly. The rotation direction support portion 57 extends substantially linearly in the radial direction. However, the rotation direction support portion 57 is not parallel to a straight line passing through the center in the circumferential direction of the windows 51 and 52 and the center O of the clutch disc assembly 1, The inner side in the direction is inclined such that the inner side in the rotational direction is located closer to the inner side in the rotational direction than the outer side in the radial direction (the center in the circumferential direction in the window portions 51 and 52). Therefore, in each of the windows 51 and 52, the rotation direction support portions 57 are not parallel to each other. The outer peripheral side support portion 55 and the inner peripheral side support portion 56 are portions raised in the axial direction from other plate portions.

The output rotary member 3 will be described. The output rotary member 3 includes a boss 7, a hub flange 6, and a low-rigidity damper 8.
It is composed of Boss 7 is clutch plate 12
And a cylindrical member disposed in the center hole of the retaining plate 13. Boss 7 is in spline engagement with a transmission input shaft (not shown) inserted into its center hole. Further, a disk-shaped and annular hub flange 6 is arranged on the outer periphery of the boss 7. That is, the hub flange 6 is disposed between the clutch plate 12 and the retaining plate 13 in the axial direction. The inner peripheral portion of the hub flange 6 is elastically connected to the boss 7 in the rotational direction by a low-rigidity damper 8. That is, when the hub flange 6 and the boss 7 rotate relative to each other, the small coil spring provided on the low-rigidity damper 8 is compressed in the rotation direction.

Window holes (53, 54) are formed in the hub flange 6 corresponding to the windows 51, 52. That is, four window holes (53, 54) are formed at the same radial position and at equal intervals in the circumferential direction. Here, a pair of windows arranged in the left and right direction in FIG. 1 is referred to as a first window hole 53, and a pair of windows arranged in the vertical direction in FIG. The hole 54 will be referred to. Since the first window 53 and the second window 54 have the same shape, their shapes will be described together. The window holes 53 and 54 are holes punched in the axial direction, and extend long in the circumferential direction.
The window holes 53 and 54 are formed between the outer peripheral side support portion 63 and the inner peripheral side support portion 64.
And a rotation direction support portion 65. In plan view, the outer peripheral side support portion 63 has a curved shape along the circumferential direction, and the inner peripheral side support portion 64 extends substantially linearly. Further, the rotation direction support portions 65 extend substantially linearly in the radial direction. More specifically, the rotation direction support portions 65 are connected to the window holes 53 and 54.
Is not parallel to the straight line connecting the center of the rotational direction of the clutch disc 1 and the center O of the clutch disc assembly 1, but is inclined such that the radially inner side is located closer to the window holes 53 and 54 in the rotational direction than the radially outer side.

To summarize the above, (1) the window or window in each rotating member has the same shape, and (2) the window or window corresponding to the axial direction (for example, the first window 53 and the first window 53). Part 5
1, the second window 54 and the second window 52) have the same shape,
Match in the axial direction. The elastic connecting mechanism 4 includes a plurality of elastic member assemblies 9. In this embodiment, four elastic member assemblies 9 are used. Each elastic member assembly 9 is disposed in the window holes 53 and 54 and the window portions 51 and 52. The elastic member assembly 9 includes a first elastic member assembly 30 disposed in the window hole 53 and the window portion 51 and a second elastic member assembly 31 disposed in the window hole 54 and the window portion 52.
It is composed of types.

The first elastic member assembly 30 includes a first coil spring 33 and a pair of seat members 34 (spring seats) disposed at both ends thereof. The first coil spring 33 has an elliptical or oval cross section. Both ends of the first coil spring 33 have closed ends to form an end winding. However, the surface portion of the end winding is not ground and maintains the cross-sectional shape of the spring material.
Here, the end winding is a portion corresponding to one winding at both ends of the first coil spring 33.

The sheet member 34 is made of a hard resin or an elastic resin material. An example of the elastic resin material is a thermoplastic polyester elastomer. The seat portion 40 of the seat member 34 has a seat surface 40 a for receiving the end turn surface portion of the first coil spring 33. A column-shaped projection 44 is formed on the seat surface side of the seat portion 40, so that the seat surface 40a is annular. The seat surface 40a is composed of a substantially flat first semicircle and a second semicircle inclined from one end to the other end (in the left-handed direction in plan view) such that the surface gradually increases. One end of the second semicircle is formed continuously from the first semicircle, and the other end of the second semicircle forms a step with the first semicircle. At this step portion, a contact surface 45 is formed, which faces the circumferential direction of the seat surface 40a (the left-handed direction in plan view). The shape of the seat surface 40 a corresponds to the end surface of the first coil spring 33, and the end surface of the end turn comes into contact with the contact surface 45. As a result, the first coil spring 33 cannot rotate around its own central axis with respect to the pair of first sheet members 34. That is, since the contact surfaces 45 of the first sheet members 34 face the opposite sides in the winding direction of the first coil spring 33, the first coil spring 33 cannot rotate to either side around the central axis.

The protrusion 44 has a circular hole 44a penetrating in the rotation direction. The hole 44a includes a first hole 44b on the inner side in the rotation direction and a second hole 44c on the second contact surface 42 side. The second hole 44c is concentric with the first hole 44b but has a large diameter. On the opposite side of the seat portion 40 from the seating surface 40a, a pair of projecting portions 41 are formed to protrude in the rotational direction on both sides in the axial direction. The tip of the projection 41 is the first
It is the contact surface 41a. A second contact surface 42 is formed between the two protrusions 41 in the axial direction. That is, the second contact surface 42 is located on the inner side in the rotational direction with respect to the first contact surface 41a. The first contact surface 41a is the plate 1
The second window portions 51 are supported in contact with the rotation direction support portions 57 of the first window portions 51. The second contact surface 42 is at a predetermined angle θ1 from the rotation direction support portion 65 of the first window hole 53 of the hub flange 6.
(Specifically, 15 degrees), it is supported in the rotation direction by being spaced apart. This means that the first coil spring 33 is not compressed until the torsion angle between the hub flange 6 and the plates 12, 13 in the elastic connection mechanism 4 exceeds 15 degrees.

The outer peripheral side of the first sheet member 34 has an arc shape along the outer peripheral side support portion 55 and the outer peripheral side support portion 63. The movement of the first sheet member 34 in the axial direction is restricted by the outer peripheral side support portion 55 and the inner peripheral side support portion 56 of the first window portion 51. In the first coil spring 33, the effective number of turns on the inner peripheral side is three, and the effective number of turns on the outer peripheral side is two, that is, the effective number of turns on the inner peripheral side is larger by one than the effective number of turns on the outer peripheral side. This state is always maintained because the first coil spring 33 cannot rotate around its own center axis. The reason is,
(A) The first coil spring 33 is non-rotatably locked to the first sheet members 34 disposed at both ends thereof, and (b) the first sheet member 34 supports the hub flange 6 in the rotation direction. The first coil spring 33 is non-rotatably engaged with the rotation direction support portion 57 of the portion 65 and the plates 12 and 13.
By making the number of effective turns on the inner side larger than the number of effective turns on the outer side in this way, it is possible to disperse excessive stress on the inner side due to a large amount of deflection on the outer side to each inner part, and as a result, As a result, it is possible to reduce the stress difference between each inner peripheral portion and the outer peripheral portion.

Next, the second elastic member assembly 31 will be described. The second elastic member assembly 31 includes a second coil spring 36 and second sheet members 37 disposed at both ends in the rotation direction. Second coil spring 36
Has an oval or oval cross section. The second coil spring 36 has closed ends at both ends to form an end winding. However, the surface portion of the end winding is not ground and maintains the cross-sectional shape of the spring material. Here, the end winding is a portion corresponding to one winding at both ends of the second coil spring 36. The second coil spring 36 has the same coil diameter, wire diameter, and pitch as the first coil spring 33, but has a different number of turns, and as a result, is longer in the rotation direction.

The second sheet member 37 is made of a hard resin or an elastic resin material. An example of the elastic resin material is a thermoplastic polyester elastomer. Second sheet member 3
7 has a seat surface 46 a for receiving the end turn surface portion of the second coil spring 36. A column-shaped projection 48 is formed on the seat surface side of the seat portion 46, so that the seat surface 46a is annular. The shape of the seat surface 46a is substantially the same as the above-described seat surface 40a.

Surface 4 of seat portion 46 opposite to seat surface 46a
Reference numeral 7 denotes a flat surface, and the second window hole 54 of the hub flange 6 is provided.
Of the second window 52 of the plates 12 and 13 in contact with and supported by the circumferential direction end 61 of the second window 52. This means that the second elastic member assembly 31
2 and 13, the width angle in the rotational direction is the same as that of the first elastic member assembly 30, and the hub flange 6
Means that the width angle in the rotation direction is different from that of the first elastic member assembly 30.

The outer peripheral side of the second sheet member 37 has an arc shape along the outer peripheral side support portion 55 and the outer peripheral side support portion 63. The movement of the second sheet member 37 in the axial direction is restricted by the outer peripheral side support portion 55 and the inner peripheral side support portion 56 of the second window portion 52. In the second coil spring 36, the effective number of turns on the inner peripheral side is seven, and the effective number of turns on the outer peripheral side is six, that is, the effective number of turns on the inner peripheral side is larger by one turn than the effective number of turns on the outer peripheral side. This state is always maintained because the second coil spring 36 cannot rotate around its own central axis. The reason is,
(A) The second coil spring 36 is non-rotatably locked to a second sheet member 37 disposed at both ends thereof, and (b) the second sheet member 37 supports the hub flange 6 in the rotation direction. The second coil spring 36 is non-rotatably engaged with the rotation direction support portion 57 of the portion 65 and the plates 12 and 13.

When the low rigidity damper 8 is functioning, the clutch disk assembly 1
A first friction generating mechanism 49 for generating a low hysteresis torque by sliding between the hub flange 6 and the plates 12, 13 when the elastic coupling mechanism 4 is functioning. A second friction generating mechanism 50 for generating torque.

Next, a plan view of the clutch disk assembly shown in FIGS. 1, 9 and 10, a schematic diagram for explaining the torsion operation shown in FIGS. 11 to 13, and a torsion characteristic shown in FIG. The torsion operation of the clutch disk assembly 1 will be described with reference to a diagram. Here, the input rotary member 2 is fixed from the neutral state in FIG. 1, and the boss 7 is twisted in the rotation direction R2 side in the torsional characteristic positive side region (at this time, the input rotary member 2 Will be twisted in the rotation direction R1 with respect to the output rotation member 3). The characteristics in this case are shown by solid lines in FIG.

In the region where the torsion angle is small, the low-rigidity damper 8 is compressed, and the characteristics of low rigidity and low hysteresis torque are obtained. At this time, almost no torsion occurs in the elastic connection mechanism 4. If the twist angle exceeds 8 degrees, the boss 7
The hub flange 6 and the hub flange 6 rotate together, and the hub flange 6 rotates with respect to the plates 12 and 13. That is, the elastic connection mechanism 4 performs a twisting operation. Specifically, from the state of FIG. 11, the hub flange 6 moves in the rotation direction R2 with respect to the plates 12 and 13, and the second elastic member assembly 3
1 is compressed in the rotation direction. At this time, the reason that the first coil spring 33 is not compressed in the first elastic member assembly 30 is that the second coil spring 33 of the first sheet member 34 in the rotation direction R1 side is not compressed.
This is because the contact surface 42 is arranged at a predetermined angle away from the rotation direction support portion 65 on the rotation direction R1 side. As a result, characteristics of medium rigidity and high hysteresis torque are obtained in the range of 8 to 23 degrees in FIG.

As shown in FIGS. 9 and 12, the rotation direction R1
When the rotation direction support portion 65 on the side contacts the second contact surface 42 of the first sheet member 34 on the rotation direction R1, the first coil spring 33 and the second coil spring 36 are thereafter compressed in the rotation direction in parallel. Is done. As a result, 23 to 3 in FIG.
The characteristics of high rigidity and high hysteresis torque shown in the region of 2 degrees are obtained.

When the torsion angle is 32 degrees as shown in FIGS. 10 and 13, the tips of the projecting portions 48 of the second sheet member 37 in the second elastic member assembly 31 abut, and the first When the coils of the first coil spring 33 are brought into close contact with each other in the elastic member assembly 30, the plate 1
The relative rotation between the hub flanges 2 and 13 and the hub flange 6 stops. The stopper mechanism for stopping the relative rotation between the plates 12 and 13 and the hub flange 6 may have a structure in which the two directly contact each other. [Effects of the present invention] As described above, the middle to high rigidity region is made to have two-stage characteristics by using different assemblies of the first elastic member assembly 30 and the second elastic member assembly 31. Specifically, in the first elastic member assembly 30, the second contact surface 42 supported by the hub flange 6 is separated from the rotation direction support portion 65 of the hub flange 6 by a predetermined angle in a neutral state.

As described above, since the elastic member assembly has a structure in which the multi-stage characteristics are realized by the combination of the elastic member and the sheet member, the following excellent effects can be obtained. (1) It is no longer necessary to consider the shapes of the windows 51, 52 of the plates 12, 13 or the windows 53, 54 of the hub flange 6. Therefore, it is possible to make the shape of the support portion the same in each rotating member. Specifically, the windows 51 and 52 of the plates 12 and 13 can all have the same shape, and the window holes 53 and 54 of the hub flange 6 can all have the same shape. This means that the plates 12,1
3 and the structure of the hub flange can be simplified, which means that the manufacturing cost can be reduced. (2) By changing only the elastic member assembly using the same type of plate or flange, different damper mechanisms having different torsional characteristics can be manufactured. For this reason,
The number of types of rotating members can be reduced, and manufacturing and maintenance costs can be reduced. In addition, all the elastic member assemblies
FIGS. 15 and 16 each show a structure in which the second elastic member assembly 31 is used. In this case, the torsional characteristic is a linear characteristic indicated by a two-dot chain line in FIG. As described above, it is possible to determine whether the middle / high torsion angle region has the multi-step characteristic or the stepless characteristic by changing the elastic member assembly without changing the plate or the hub flange. Further, it is clear from the above that different multi-stage characteristics can be realized only by changing the elastic member assembly on the assumption that the same kind of rotating member is used. Second Embodiment In the above-described embodiment, the first elastic member assembly 30 is in contact with the plates 12 and 13 in the rotational direction to secure a gap in the rotational direction with respect to the hub flange 6. In the embodiment, conversely, the first elastic member assembly 30 secures a gap in the rotational direction with respect to the plates 12 and 13 so as to abut on the hub flange 6 in the rotational direction.

The structure according to this embodiment is basically the same as the structure according to the above embodiment. Here, the same structure is denoted by the same number, and corresponding but different structures are distinguished by adding the apostrophe (') to the same number. The only difference is in the structure of the first elastic member assembly, in particular, the structure of the first sheet member. In the schematic diagrams of the elastic coupling mechanism 4 shown in FIGS. 17 to 19, the first contact surface 41a 'of the first sheet member 34' of the first elastic member assembly 30 '.
Is disposed at a predetermined angle θ1 from the rotation direction support portion 57 of the plates 12 and 13. Also, the first sheet member 3
The second contact surface 42 'of 4' is in contact with the rotation direction support portion 65 of the hub flange 6 and is supported in the rotation direction. In such a structure, the first sheet member 34 ′ is attached to the hub flange 6.
It is preferable to have a projection 70 that is locked to the rotation direction support portion 65 so as to be unable to move in the axial direction.

Next, the torsional operation of the elastic coupling mechanism 4 will be described with reference to the schematic diagrams of FIGS. 17 to 19 and the torsional characteristic diagram of FIG. Here, the boss 7 is twisted in the rotation direction R2 with respect to the input rotary member 2 fixed from the neutral state in FIG. (It will be twisted in the rotation direction R1 with respect to the rotating member 3). The characteristics in this case are shown by solid lines.

In the region where the torsion angle is small, the low-rigidity damper 8 is compressed, and characteristics of low rigidity and low hysteresis torque are obtained. When the twist angle exceeds 8 degrees, the boss 7 and the hub flange 6 rotate integrally, and the hub flange 6 rotates with respect to the plates 12 and 13. Specifically, from the state of FIG.
The second elastic member assembly 31 is moved in the rotation direction R2 with respect to the direction of rotation 13 to compress the second elastic member assembly 31 in the rotation direction. At this time, the first elastic member assembly 30 ′ is not compressed because the first contact surface 41 a ′ of the first sheet member 34 ′ on the rotation direction R2 side is at a predetermined angle θ1 from the rotation direction support portion 57 on the rotation direction R2 side. This is because they are arranged apart. As a result, as shown in FIG.
The characteristics of medium rigidity and high hysteresis torque shown at 23 degrees are obtained.

As shown in FIG. 18, the first rotation direction R2 side
The first contact surface 41a 'of the sheet member 34' is rotated in the rotation direction R2.
The first elastic member assembly 30 'and the second elastic member assembly 31 are thereafter compressed in parallel in the rotational direction when the first elastic member assembly 30' and the second elastic member assembly 31 are in contact with each other. As a result, 23 to 3 shown in FIG.
Twice high rigidity and high hysteresis torque characteristics can be obtained.

As shown in FIG. 19, the second elastic member assembly 3
The tips of the projecting portions 48 of the first second sheet member 37 abut against each other, and the coils of the first coil springs 33 in the first elastic member assembly 30 come into close contact with each other, so that the plates 12 and 13 and the hub flange 6 Relative rotation stops. The stopper mechanism for stopping the relative rotation between the plates 12 and 13 and the hub flange 6 may have a structure in which the two directly contact each other.

Since the torsional characteristic negative side region is the same as the positive side, the description is omitted. The effects and advantages obtained in this embodiment are the same as those in the above embodiment. [Modification] The specific structure resulting from the change of the torsion characteristic by changing the elastic member assembly is not limited to the above embodiment. For example, in the first elastic member assembly 30, R1
The angle between the second contact surface 42 on the R side and the rotation direction support portion 65 and the angle between the second contact surface 42 on the R2 side and the rotation direction support portion 65 are made different from each other, and The characteristic may be different between the positive side and the negative side of the torsion characteristic. Further, it is not necessary that the entire contact surface of the second elastic member assembly 31 be directly supported by the rotational direction contact portion of the rotating member. Further, the present invention is not limited to the two-stage characteristic, and may have a three-stage / four-stage multi-stage characteristic by a combination of elastic member assemblies.

The type of the elastic member is not necessarily limited to the coil spring. Further, the shape of the sheet member is not limited to the above embodiment. Further, the shapes, the number, and the positions of the window holes and window portions in the plate and the hub flange are not limited to those in the previous embodiment. Further, the present invention is not limited to the damper mechanism of the clutch disk assembly, but may be applied to a lock-up device of a torque converter or a damper mechanism incorporated in a divided flywheel. Third Embodiment In each of the following embodiments, the structure of the clutch disk assembly 101 as a whole is the same as that of the first embodiment. Therefore, in the following description, only points different from the first embodiment will be described, and description of the same structure will be omitted. The specific numerical values of the gap angles used in the following description are exemplifications for explaining the relationship between the sizes of the respective gap angles, and do not limit the present invention.

The elastic connecting mechanism 104 includes a plurality of elastic member assemblies 109. In this embodiment, four elastic member assemblies 109 are used. Each elastic member assembly 109 includes window holes 153 and 154 and window portions 151 and 15.
2 are arranged. The elastic member assembly 109 includes a first elastic member assembly 130 disposed in the window 153 and the window 151, and a second elastic member assembly 131 disposed in the window 154 and the window 152. It is composed of types.

As shown in FIG. 21, the first elastic member assembly 130 includes a first coil spring 133 (elastic member).
And a pair of sheet members 134A,
134B and a viscous rubber 158.
The sheet member 134A is disposed on the rotation direction R1 side, and the sheet member 134B is disposed on the rotation direction R2 side.

On the opposite side of the seat portion 140A of the seat portion 140 from the seating surface, a pair of projecting portions 141 (contact portions) are formed on both sides in the axial direction so as to protrude in the rotational direction. The tip of the protrusion 141 is a first contact surface 141a. A second contact surface 142 is formed between the two protrusions 141 in the axial direction. That is, the second contact surface 142 is located on the inner side in the rotation direction with respect to the first contact surface 141a. The first abutment surface 141a abuts against and is supported by the rotation direction support 157 of the first window 151 of the plates 112 and 113. The second contact surface 142 is supported in the rotation direction at a predetermined angle (3.5 °) away from the rotation direction support portion 165 of the first window hole 153 of the hub flange 106.

The protrusion 144 has a circular hole 149 penetrating therethrough in the rotation direction. The hole 149 has a first hole 149a on the inner side in the rotation direction and a second hole 149 on the second contact surface 142 side.
b. The second hole 149b is concentric with the first hole 149a but has a large diameter. A small coil spring 209A (a low-rigidity elastic member) is arranged in the second hole 149b. The end of the small coil spring 209A in the rotation direction R1 abuts or approaches the rotation direction support portion 165, and the rotation direction R
The second side end is in contact with or close to the bottom surface of the second hole 149b. The small coil spring 209A has a pair of protrusions 141.
Since it is arranged between the members, contact with other members is prevented. Also, since one end of the small coil spring 209A is inserted into the second hole 149b, it is difficult for the small coil spring 209A to drop off from the seat portion. The small coil spring 209A may be maintained in a free state, or may be held in a state of being compressed in the rotational direction.

The outer end of the sheet member 134B in the rotation direction has a rotation direction support portion 157 (not shown) of the first window 151 of the plates 12 and 13 and a rotation direction support portion 165 of the first window hole 153 of the hub flange 106. Is in contact with That is, the sheet member 134B is supported in a state of being in contact with both input and output members in the rotational direction. Viscous rubber 1
Reference numeral 58 denotes a member disposed inside the first coil spring 133 between the two seat members 134A and 134B in the rotation direction. The viscous rubber 158 has the property of generating frictional resistance inside but not providing rigidity. Both ends of the viscous rubber 158 are inserted and locked in the holes 149. A cylindrical collar 159 is disposed around the viscous rubber 158. The collar 159 is movable in the rotation direction between the two sheet members 134A and 134B. The collar 159 is a member for preventing contact between the viscous rubber 158 and the first coil spring 133.

As shown in FIG. 22, the second elastic member assembly 131 has a second coil spring 136 (elastic member).
And sheet members 137 disposed at both ends in the rotation direction.
A, 137B. Sheet member 137
A is disposed on the rotation direction R1 side, and the sheet member 13
7B is disposed on the rotation direction R2 side. Sheet member 1
A small coil spring 209B (a low-rigidity elastic member) is provided on the outer side in the rotation direction of 37A similarly to the seat member 134A. Since the structure of the sheet member 137A is the same as that of the sheet member 134A, the description is omitted here.
The sheet member 137B, like the sheet member 134B,
It is supported in a state of being in contact with the rotation direction support portion 157 and the rotation direction support portion 165 in the rotation direction.

As described above, each elastic member assembly 1
30 and 131, the sheet member 1 on the rotation direction R1 side
Small coil springs 209A and 209B are arranged only in 34A and 137A. The rigidity of the small coil springs 209A and 209B is the same as that of the coil spring 13
The rigidity of each of the low-rigidity dampers 108 is set to be much lower than the rigidity of the low-rigidity damper 108.

The torsional characteristics of the elastic coupling mechanism 104 described above will be described with reference to FIGS. 23 and 24. As shown in FIG. 24, when the torsion angle is between −2 ° and + 6.5 °, only the low-rigidity damper 108 or the low-rigidity damper 108 and the small coil spring 209A are compressed in series, and low-rigidity characteristics are obtained. In the above region, the first friction generating mechanism 49 generates a low hysteresis torque. The twist angle is +
Between 6.5mm and + 10mm, small coil spring 2
09A and 209B are compressed, and the low-rigidity damper 10
8 has higher rigidity than the compressed region. In the above region, a high hysteresis torque is generated by the second friction generating mechanism 50. In this way, by providing a region of relatively high rigidity and high hysteresis torque at the positive end of the low rigidity first stage region, a so-called jumping phenomenon during idling can be effectively prevented.

The torsion angle is + 10 ° to + 30 ° or -2
In the region from ° to -22 °, the coil springs 133, 1
36 are compressed, and high rigidity characteristics are obtained. In addition, at this time, in addition to the high hysteresis torque in the second friction generating mechanism 50, the viscous rubber 158 is compressed in the rotation direction, so that relatively large friction is obtained. In this damper mechanism, the small coil springs 209A and 209B and the low-rigidity damper 8 are used.
The characteristics in the region where the torsion angle is small can be adjusted by the combination with. In this embodiment, only the low-rigidity damper 8 or the low-rigidity damper 8 and the small coil springs 209A and 209B are compressed in series from the torsion angle 0.
The rigidity of each coil spring is set such that an area, a second area where only the small coil spring 209A is compressed, and a third area where only the coil springs 133 and 136 are compressed are formed. Preferably, the stiffness of the first region is 0.01 to 0.1 N · m / °, and the stiffness of the third region is 1 N · m / °. Therefore, the second region has an intermediate value of 0.1 to 1 N · m / °.

As described above, in this embodiment, it is possible to realize a multi-stage damper for idling countermeasures. Specifically, the small coil spring 209 is added to the structure of the first embodiment.
By adding A, 209B, the torsional angle and the torsional torque in the idling countermeasure region can be increased, and more specifically, the first stage region has high rigidity characteristics at the positive end. A second region can be provided. Moreover, this characteristic can be obtained only by changing the seat member with respect to the conventional structure, and there is no need to change the main body structure such as the clutch plate and the hub flange.

Although the small coil spring 209 is provided in all the elastic member assemblies in this embodiment, it may be provided in only some of the elastic member assemblies. Fourth Embodiment In a clutch disk assembly 201 shown in FIG. 25, a hub and a flange are formed integrally. That is, the low-rigidity damper in the embodiment is not provided.

The first elastic member assembly 230 shown in FIG.
Is composed of a first coil spring 233 and a pair of sheet members 234A and 234B arranged at both ends thereof. The sheet member 234A is disposed on the rotation direction R1 side, and the sheet member 234B is disposed on the rotation direction R2 side. The first seat member 234A has a small coil spring 208A as in the above-described embodiment.
The main difference from the above embodiment is that the rotation direction support portion 265
The circumferential angle between the first contact surface 242 and the second contact surface 242 is as wide as 7 °.

The second sheet member 234B is connected to the second contact surface 2
A predetermined circumferential angle (3.5 °) is ensured between the rotation direction support portion 42 and the rotation direction support portion 265. The small coil spring is not provided on the second seat member 234B.
In the second elastic member assembly 231 shown in FIG. 27, the sheet member 237A is arranged on the rotation direction R1 side, and the sheet member 237B is arranged on the rotation direction R2 side. The small coil spring is not provided on the seat member 237A, and the small coil spring 20 is provided on the seat member 237B.
8B are provided. That is, the first elastic member assembly 2
30 and the second elastic member assembly 231 are different in the arrangement of the small coil springs. In addition, in the second elastic member assembly 231, the second contact surface 24 is attached to the sheet member 237A.
The circumferential angle between the second support member 265 and the rotation direction support portion 265 is 7 °, and the circumferential angle between the second contact surface 242 of the sheet member 237B and the rotation direction support portion 265 is 3.5 °. It is. The rigidities of the small coil springs 208A and 208B are set to be significantly lower than the rigidities of the coil springs 233 and 236.

As described above, the relationship between the clearance angle between the first elastic member assembly 230 and the second elastic member assembly 231 and the small coil springs 208A and 208B is summarized as follows. (1) In both the first elastic member assembly 230 and the second elastic member assembly 231, the second contact surface 2 on the rotation direction R1 side
The gap angle between the rotation direction support portion 265 and the rotation direction support portion 265 is set to be larger than that in the rotation direction R2 side, and is about twice. This is to make the positive side portion of the first stage area wider than the negative side portion. (2) The small coil spring 208A used to obtain a predetermined rigidity in the first-stage positive side region is provided only on the rotation direction R1 side of the first elastic member assembly 230.
In order to obtain a predetermined rigidity in the first-stage negative side region, the small coil spring 208B is connected to the second elastic member assembly 231.
Are provided only on the rotation direction R2 side. Like this one
By using only one small coil spring in one elastic member assembly, management of each elastic member assembly and assembling to a window or the like become easy.

In the structure described above, the small coil spring 208 provided on the first elastic member assembly 230
A and the small coil spring 208B of the second elastic member assembly 231 realize the first stage low rigidity region of the clutch disk assembly 201. The above torsional characteristics are clear from the torsional characteristic diagrams shown in FIGS. 28 and 29. In addition,
In this embodiment, only one small coil spring is provided for one elastic member assembly, but small coil springs may be provided for both sheet members on both sides in one elastic member assembly. However, when one small coil spring is used as in the present embodiment, the assembling work when assembling the elastic member assembly to the window hole or the like is easier. Further, by omitting one of the small coil springs, low rigidity is achieved.

In the present embodiment, since the adjustment of the compression of the small coil spring is adjusted by the shape of the sheet member, it is not necessary to provide a rotation-direction projection or the like on a support portion such as a flange or a plate. Fifth Embodiment The structure of a clutch disk assembly 301 shown in FIG. 30 is substantially the same as the structure of the clutch disk assembly of the fourth embodiment. In particular, the basic structure of each of the elastic member assemblies 330 and 331 is the same as that of the fourth embodiment, and is a structure obtained by improving or changing the basic structure. Here, only different points will be described.

In the first elastic member assembly 330 shown in FIG. 31, a small coil spring 308B is provided on the seat member 334B in addition to the structure of the above-described embodiment. In the second elastic member assembly 331 shown in FIG. 32, a small coil spring 309 is provided on the seat member 337A in addition to the structure of the above-described embodiment. The small coil spring 309 is second compared to the small coil spring 308A.
The amount of protrusion from the contact surface 342 outward in the rotation direction is short. Therefore, a clearance of 3.5 ° is secured between the end of the small coil spring 309 in the rotation direction R1 and the rotation direction support portion 365. The small coil spring 308A,
The rigidity of 308B and 309 is as follows:
It is set to be significantly lower than the rigidity of 336.

As described above, the relationship between the clearance angle between the first elastic member assembly 330 and the second elastic member assembly 331 and the small coil springs 308A, 308B, 309 is summarized as follows. (1) In both the first elastic member assembly 330 and the second elastic member assembly 331, the second contact surface 3 on the rotation direction R1 side
The gap angle between the rotation direction support portion 365 and the rotation direction support portion 365 is set to be larger than that in the rotation direction R2 side, and is about twice. This is to make the positive side portion of the first stage area wider than the negative side portion. (2) Since the small coil spring 309 is arranged on the rotation direction R1 side of the second elastic member assembly 331, the combination of the small coil spring 308A and the small coil spring 308A realizes multi-stage torsional characteristics in the first stage positive side region. it can. That is, the small coil spring 308A is twisted over the entire torsional characteristic first stage positive side region, and the small coil spring 308B is twisted only in the range of the torsion angle of + 3.5 ° to + 7.5 °. (3) Since the small coil spring 308B is also provided on the rotation direction R2 side of the first elastic member assembly 330, the combination of the small coil spring 308B of the second elastic member assembly 331 and the one-stage torsion characteristic is achieved. The rigidity on the negative side of the eye region
It is higher than the embodiment.

As a result, as shown in the torsional characteristic diagrams of FIGS. 33 and 34, the region where the torsional angle is small, ie, -3.
Between 5 ° and + 3.5 °, the small coil springs 308A and 308B are compressed, and between + 3.5 ° and + 7 °, the small coil spring 309 is compressed in addition to the small coil spring 308A. As a result, +3.
In the range from 5 ° to + 7 °, from -3.5 ° to +
A region with higher rigidity is realized as compared with a region up to 3.5 °. As a result, as described above, the small torsional vibration during engine idling can be effectively attenuated.

As described above, by adjusting the arrangement of the small coil springs in the seat member, it is possible to provide not only the first-stage low-rigidity region but also a higher-rigidity region at the positive end thereof. Sixth Embodiment In a clutch disk assembly 401 shown in FIG. 35, a hub and a flange are formed integrally. Therefore, no low-rigidity damper is provided.

The first elastic member assembly 430 includes a coil spring 433, a sheet member 434, and a float body 45.
And 1. The sheet member 434 is supported in a state in which the rotation direction end surface thereof is in contact with the rotation direction support portion 465 and the like, unlike the above-described embodiment. The float body 451 is a member disposed inside the coil spring 433, and is movable in the circumferential direction between the two sheet members 434. The float body 451 includes an elastic portion 463 made of rubber, an elastic resin, or the like, and cylindrical protection portions 464 provided on both sides of the elastic portion 463 in the rotation direction. The protection portion 464 is made of, for example, a hard resin and protects both ends in the rotation direction and the outer peripheral surface of the elastic portion 463.

A stopper torque generating member 431 is arranged in the window hole 454 and the window 452. The stopper torque generating member 431 is made of, for example, thermoplastic polyester.
It is made of an elastic resin material such as an elastomer. As shown in FIGS. 37 to 39, the stopper torque generating member 431 includes a central portion 460 and an outer portion 461 provided outside the central portion 460 in the axial direction. The central portion 460 has a substantially rectangular shape. The outer portion 461 projects further to both sides in the circumferential direction than the center portion 460. As shown in the figure, a gap of 12 ° is secured between the rotation direction end surface 463 of the center portion 460 and the rotation direction end surface 462 of the outer portion 461 on the R1 side and 10.5 ° on the R2 side. The outer part 4
The shape of 61 is substantially the same as that of the window portion and the window hole, and its edge is supported by the window portion and the window hole. As the torsion angle increases in the clutch disk assembly 401, the coil spring 433 is compressed to obtain a predetermined rigidity. When the torsion angle further increases, the float body 451 is compressed between the two sheet members 434 and the center portion 46 of the stopper torque generating member 431 is formed.
0 is compressed in the rotation direction between the window and the rotation direction support of the window hole. As a result, a predetermined stopper torque is generated.

In this clutch disk assembly 401,
A member 431 for generating a stopper torque is disposed in the window and the window hole. Therefore, by adjusting the shape and properties of the stopper torque generating member, the stopper torque generation angle and the magnitude of the stopper torque can be easily adjusted. The shape of the stopper torque generating member is not limited to the above embodiment.

In the structure according to the present invention, since the torsional characteristics are set by the combination of the elastic member and the sheet member of the elastic member assembly, the damper mechanism can be simplified and the cost can be reduced.

[Brief description of the drawings]

FIG. 1 is a plan view of a clutch disk assembly according to a first embodiment of the present invention.

FIG. 2 is a longitudinal sectional view of a clutch disk assembly.

FIG. 3 is a plan view of a first sheet member.

FIG. 4 is a cross-sectional view of a first sheet member.

FIG. 5 is a front view of a first sheet member.

FIG. 6 is a sectional view taken along line VI-VI of FIG. 5;

FIG. 7 is a side view of the first sheet member.

FIG. 8 is a rear view of the first sheet member.

FIG. 9 is a plan view for explaining a torsion operation of the clutch disk assembly.

FIG. 10 is a plan view for explaining a torsion operation of the clutch disk assembly.

FIG. 11 is a schematic view of a damper mechanism of the clutch disk assembly.

FIG. 12 is a schematic diagram for explaining a twisting operation of the damper mechanism.

FIG. 13 is a schematic diagram for explaining a twisting operation of the damper mechanism.

FIG. 14 is a torsional characteristic diagram of a damper mechanism of the clutch disk assembly.

FIG. 15 is a plan view of a clutch disk assembly according to a modification.

FIG. 16 is a schematic view of a damper mechanism of the clutch disk assembly shown in FIG.

FIG. 17 is a schematic view of a damper mechanism of the clutch disk assembly according to the second embodiment.

FIG. 18 is a schematic diagram for explaining a twisting operation according to the second embodiment.

FIG. 19 is a schematic diagram for explaining a twisting operation according to the second embodiment.

FIG. 20 is a plan view of a clutch disk assembly according to a third embodiment.

FIG. 21 is a cross-sectional view of the first elastic member assembly.

FIG. 22 is a cross-sectional view of the second elastic member assembly.

FIG. 23 is a torsional characteristic diagram of a clutch disk assembly according to a third embodiment.

FIG. 24 is a diagram illustrating a first-stage region of torsional characteristics.

FIG. 25 is a plan view of a clutch disk assembly according to a fourth embodiment.

FIG. 26 is a cross-sectional view of the first elastic member assembly.

FIG. 27 is a cross-sectional view of the second elastic member assembly.

FIG. 28 is a torsional characteristic diagram of a clutch disk assembly according to a fourth embodiment.

FIG. 29 is a diagram showing a first-stage area.

FIG. 30 is a plan view of a clutch disk assembly according to a fifth embodiment.

FIG. 31 is a cross-sectional view of the first elastic member assembly.

FIG. 32 is a cross-sectional view of the second elastic member assembly.

FIG. 33 is a torsional characteristic diagram of a clutch disk assembly according to a fifth embodiment.

FIG. 34 is a torsional characteristic diagram showing a first-stage region.

FIG. 35 is a plan view of a clutch disk assembly according to a sixth embodiment.

FIG. 36 is a cross-sectional view of the first elastic member assembly.

FIG. 37 is a transverse sectional view for explaining a stopper torque generating member.

FIG. 38 is a plan view of a stopper torque generating member.

FIG. 39 is a front view of a stopper torque generating member.

FIG. 40 is a torsional characteristic diagram of the clutch disk assembly according to the sixth embodiment.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 clutch disk assembly 2 input rotating member 3 output rotating member 4 elastic coupling mechanism 6 hub flange 7 boss 8 low rigidity damper 9 elastic member assembly 30 first elastic member assembly 31 second elastic member assembly 33 first elastic member 34 First sheet member 40 First receiving surface 41 Projecting portion 41a First contact surface (first surface) 42 Second contact surface (second surface)

Claims (27)

[Claims] 1. A sheet member for supporting an end of an elastic member disposed between a first rotating member and a second rotating member of a damper mechanism in a rotating direction, for receiving an end of the elastic member. And a second surface supported by the second rotating member and having a different rotational position from the first surface. 2. An elastic member assembly disposed between rotation directions of a first rotating member and a second rotating member of a damper mechanism, the elastic member including a pair of elastic members for supporting an end of the elastic member. At least one of the pair of sheet members has a receiving surface for receiving an end of the elastic member, a first surface supported by the first rotating member, and a second rotating member. An elastic member assembly having a second surface supported by a member and having a rotational position different from the first surface. 3. An elastic member assembly disposed between a rotation direction of a first rotation member and a second rotation member of a damper mechanism, and supports the first elastic member and an end of the first elastic member. And at least one of the pair of first sheet members is supported by a first receiving surface for receiving an end of the elastic member and the first rotating member. A first elastic member assembly, the first elastic member assembly having a first surface supported by the second rotating member and a second surface different in rotational position from the first surface. And a second elastic member assembly used to act in parallel. 4. A first receiving member for receiving an end of the elastic member, wherein the first sheet member has a first receiving surface for receiving an end of the elastic member.
4. The elastic member assembly according to claim 3, wherein the elastic member assembly has a first surface supported by a rotating member and a second surface supported by the second rotating member and having a different rotational position from the first surface. . 5. The elastic member assembly according to claim 4, wherein said second surface is located inward of said first surface in the rotation direction. 6. The second elastic member assembly includes a second elastic member and a pair of second sheet members for supporting an end of the second elastic member. Each of the sheet members has a second receiving surface for receiving an end of the second elastic member, a third surface supported by the first rotating member, and a fourth surface supported by the second rotating member. The elastic member assembly according to claim 5, wherein a distance between the first surfaces of the first elastic member assembly is equal to a distance between the third surfaces of the second elastic member assembly. . 7. The first support portion and the second support portion having the same width angle in the rotation direction.
A first rotating member having a support, and respectively corresponding to the first support and the second support;
A second rotating member having a third supporting portion and a fourth supporting portion having the same rotation direction width angle; a first elastic member disposed in the first supporting portion and the third supporting portion; and a first elastic member A first elastic member assembly having a pair of first sheet members disposed at ends of the first elastic member assembly; and a second elastic member assembly disposed within the second spring support portion and the fourth spring support portion. Wherein each of the pair of first sheet members has a first surface supported by the first support portion and a second surface supported by the fourth support portion. The rotation direction distance between the first support and the second surface is different from the rotation direction distance between the second surface and the fourth support.
Damper mechanism. 8. The damper mechanism according to claim 7, wherein said first surface is in contact with said first support portion, and said second surface is spaced from said fourth support portion in a rotational direction. 9. The second elastic member assembly according to claim 7, wherein the second elastic member assembly includes a second elastic member and a pair of second sheet members disposed at an end of the second elastic member. Damper mechanism. 10. Each of the pair of second sheet members has a third surface supported by the second support portion and a fourth surface supported by the third support portion. The surface is in contact with the second support, and the fourth
The damper mechanism according to claim 9, wherein a surface is in contact with the third support portion. 11. A method for manufacturing a damper mechanism having a first rotating member, a second rotating member, and an elastic member assembly for elastically connecting the two members in a rotational direction, and having different torsional characteristics. A step of preparing two first rotating members and two second rotating members; a step of combining one first rotating member and one second rotating member to form two rotating member assemblies; Incorporating different types of elastic member assemblies consisting of an elastic member and a sheet member into the two rotating member assemblies, respectively, wherein the damper mechanisms have different torsion characteristics. 12. A first rotating member having a first support portion and a second support portion having the same shape, a third support portion and a third support member having the same shape and corresponding to the first support portion and the second support portion, respectively. A second rotating member having four support portions; a first elastic member disposed in the first support portion and the third support portion; and first sheet members disposed at both ends of the first elastic member. A second elastic member having a first elastic member assembly; a second elastic member disposed in the second support portion and the fourth support portion; and second sheet members disposed at both ends of the second elastic member. A member assembly, wherein the first sheet member has a gap in the rotation direction from one of the first and third support portions, so that the first elastic member has a torsion characteristic so that the second elastic member is compressed. In the region where the twist angle is small in the region where The damper mechanism is designed to be compressed in critical areas. 13. A sheet member for supporting an end of an elastic member disposed between the rotation direction of a first rotating member and a second rotating member of a damper mechanism, for supporting an end of the elastic member. A low-rigidity elastic member that is provided on the opposite side of the elasticity member of the seat portion, has lower rigidity than the elastic member, and is compressible in the rotational direction between the seat portion and the second rotating member. When,
A sheet member comprising: 14. The seat member according to claim 13, further comprising a contact portion integrally formed on a side of the seat portion opposite to the elastic member and supported by the first rotating member. 15. The contact portion is a pair of protrusions extending outward in the rotational direction from both ends in the axial direction of the seat portion, and the low-rigidity elastic member is disposed between the pair of protrusions. ,
The sheet member according to claim 14. 16. The abutting portion extends further outward in the rotational direction than the low-rigidity elastic member.
6. The sheet member according to 5. 17. The sheet member according to claim 13, wherein a hole is formed on a side of the sheet portion opposite to the elastic member, and one end of the low-rigidity elastic member is inserted into the hole. Sheet member. 18. An elastic member assembly disposed between the rotation direction of a first rotation member and a second rotation member of a damper mechanism, comprising: a pair of elastic members for supporting an end of the elastic member. At least one of the pair of sheet members is provided on a side opposite to the elastic member of the sheet portion for supporting an end of the elastic member, and is provided on the opposite side of the elastic member. An elastic member assembly comprising: a low rigidity elastic member having low rigidity and capable of being compressed in a rotational direction between the seat portion and the second rotating member. 19. The elastic member assembly according to claim 18, further comprising a contact portion formed integrally with the sheet portion on a side opposite to the elastic member and supported by the first rotating member. 20. The contact portion is a pair of protrusions extending outward in the rotational direction from both ends in the axial direction of the seat portion, and the low-rigidity elastic member is disposed between the pair of protrusions. ,
The elastic member assembly according to claim 19. 21. The abutting portion extends further outward in the rotational direction than the low-rigidity elastic member.
An elastic member assembly according to claim 0. 22. The low-rigidity elastic member according to claim 18, wherein a hole is formed on a side of the sheet portion opposite to the elastic member, and one end of the low-rigidity elastic member is inserted into the hole. Elastic member assembly. 23. A hub flange having a hub, a flange extending outward from the hub and having an elastic member supporting portion formed thereon, and a low rigidity elastic member disposed on a side of the flange and corresponding to the elastic member supporting portion. An elastic member having a disk-shaped member having a member supporting portion, an elastic member disposed in the first and low-rigid elastic member supporting portions, and a pair of sheet members for supporting an end of the elastic member. At least one of the pair of sheet members has a seat portion for supporting an end of an elastic member, and the seat portion is provided on one of the hub flange and the disc-shaped member. A first surface facing in the rotational direction, and a second surface facing in the rotational direction with respect to the other of the hub flange and the disc-shaped member; The rotation direction angle is between the first surface and the A rotational direction angle between the elastic member and one of the sheet members, the one of the pair of sheet members having a low rigidity elastic member disposed between the second surface and the other and having a lower rigidity than the elastic member; Has a damper mechanism. 24. The hub and the flange are separate members, the rigidity being lower than the elastic member, and further comprising a low-rigidity damper for elastically connecting the hub and the flange in a rotational direction. 24. The damper mechanism of claim 23, wherein: 25. A first region in which only the low-rigidity elastic member or the low-rigidity elastic member and the low-rigidity damper are compressed in series from a torsion angle of 0, and a first region in which only the low-rigidity elastic member is compressed. 25. The damper according to claim 24, wherein the rigidity of the low-rigidity damper, the low-rigidity elastic member and the elastic member is set such that two regions and a third region where only the elastic member is compressed are formed. mechanism. 26. The damper mechanism according to claim 23, wherein said hub and said flange are formed integrally. 27. The rotation direction angle between the low rigidity elastic member on one side in the rotation direction and the other of the hub flange and the disc-shaped member in different elastic member assemblies is different.
7. The damper mechanism according to 6.