JP2000205296A - Damper disc assembly - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper disc assembly generating a sufficiently large stopper torque. SOLUTION: A coil spring assembly 13 is equipped with a minor coil spring 31 and a pair of spring sheets 64. The spring sheets 64 are arranged at the ends in circumferential direction of the minor coil spring 31. The spring sheets 64 support the two ends in circumferential direction of the minor coil spring and are engaged with the inside of the minor coil spring 31. The forefront of each spring sheets 64 serves as an abutting surface 71 in a flat form stretching in the axial direction, and a taper is formed such that the inner end in the radial direction is positioned nearer the confronting spring sheet 64 than the outer end in the radial direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper disk assembly, and more particularly to a method for absorbing torsional vibration in a power transmission system.
A damper disk assembly for damping.

[0002]

2. Description of the Related Art A damper disk assembly used in a clutch disk assembly of a vehicle includes an input member that can be connected to an input flywheel, an output member that is connected to a shaft extending from a transmission, and an input member and an output member. And a damper mechanism elastically connected in the rotation direction. The input member includes a friction facing and a pair of input plates fixed on the inner peripheral side. The output member comprises a hub which is non-rotatably connected to the shaft. The hub has a boss spline-engaged with the shaft and a flange extending radially from the boss. The damper mechanism includes a spring for elastically connecting the pair of input plates and the flange in the rotational direction, and a friction generating mechanism for generating friction between the pair of input plates and the flange. When the pair of input plates and the hub rotate relative to each other, the spring is compressed in the rotational direction, and the friction is generated by the friction generating mechanism. as a result,
Rotational torsional vibration is absorbed and attenuated.

[0003] A window hole (spring accommodation hole) for accommodating a spring is formed in the flange of the hub. further,
A spring supporting portion (spring accommodating portion) for supporting the spring is formed on the pair of input plates. The window supports both ends in the circumferential direction and both sides in the radial direction of the spring. The spring supporting portions support both ends in the circumferential direction, both sides in the radial direction, and both sides in the axial direction of the spring. As a result, when the pair of input plates and the flange rotate relative to each other, the spring is compressed between one circumferential end surface of the window hole and the circumferential opposite end surface of the spring support. At the time of this compression, the circumferential end face of the window hole or the spring support portion has a larger circumferential movement amount in the radially outer portion than in the radially inner portion, so that the circumferential width of the outer circumferential portion of the spring is larger. Is shorter than the circumferential width of the inner peripheral portion. When the spring is compressed in a non-parallel manner, a bending stress is generated in the spring in addition to the shear stress, and the life is shortened.

[0004]

As a kind of a spring disposed in a window hole and a support portion, an elastic float disposed inside a coil spring is known. The elastic float body is, for example, a columnar member formed of rubber and hard resin disposed at both ends thereof. The elastic float body is freely movable to a predetermined angle between both ends in the circumferential direction of the window and the support portion in the free state of the damper disk assembly. The elastic float body is compressed between one end in the circumferential direction of the window hole and the other end in the circumferential direction of the support portion during the course of the compression of the coil spring, thereby rapidly increasing the rigidity of the damper mechanism. In this way, the elastic float provides a stopper torque in the damper disk assembly.

However, when the coil spring is compressed in a non-parallel manner as described in the prior art, the posture of the elastic float body is inclined by the coil spring, and the end face of the elastic float body and another member (plate member end face) are inclined. Or a spring seat). In this case, the elastic float body cannot generate a sufficiently large load, and a desired stopper torque cannot be obtained.

It is an object of the present invention to realize a sufficiently large stopper torque in a damper disk assembly.

[0007]

According to a first aspect of the present invention, there is provided a damper disk assembly including a first rotating member, a second rotating member, a coil spring, and a pair of spring seats. The first rotating member is a plate-like member having a spring receiving hole formed therein. The second rotating member is a plate-shaped member in which a spring accommodating portion corresponding to the spring accommodating hole is formed and arranged near the first rotating member. The coil spring is disposed in the spring receiving hole and the spring receiving portion, and is capable of transmitting torque between the first rotating member and the second rotating member. The pair of spring seats are arranged at both ends in the circumferential direction of the coil spring. The spring seat supports both ends in the circumferential direction of the coil spring and is engaged with the inside of the coil spring. The pair of spring seats can be circumferentially engaged with both ends of the spring receiving hole and the spring receiving portion in the circumferential direction. The distal ends of the pair of spring seats have inclined surfaces whose radial inner ends are located closer to the opposing spring seat than radial outer ends.

In the damper disk assembly according to the first aspect, for example, when torque is input to the second rotating member,
Torque is transmitted to the first rotating member via the coil spring. When the torque fluctuation is input to the second rotating member, the first rotating member and the second rotating member rotate relatively, and the coil spring is compressed in the rotating direction. As a result, torsional vibration is absorbed and attenuated. Here, since the tips of the pair of spring seats are inclined surfaces, the members that come into contact with each other to generate the stopper torque come into full contact with each other, and a sufficiently large stopper torque can be obtained.

According to a second aspect of the present invention, in the first aspect, when the first and second rotating members rotate relative to each other and the pair of spring seats approach each other, the distal ends of the pair of spring seats are moved toward each other. It comes into contact.

[0010] In the damper disk assembly according to the second aspect, when the pair of spring seats abut against each other, the abutting surfaces at the distal ends abut the entirety because the tips are inclined surfaces. As a result, a sufficiently large stopper torque can be obtained.

According to a third aspect of the present invention, there is provided a damper disk assembly according to the first aspect, further comprising an elastic float disposed in the coil spring so as to be movable in a circumferential direction.

In the damper disk assembly according to the third aspect, when the relative rotation angle between the first rotating member and the second rotating member increases, the elastic float body is sandwiched between the pair of spring seats. At this time, the elastic float body is elastically deformed by the inclined surfaces at the tips of the pair of spring seats.
For this reason, the front ends of the pair of spring seats and the elastic float come into contact with each other over the entire surface, and the elastic float can generate a sufficiently large load.

[0013]

DETAILED DESCRIPTION OF THE INVENTION First Embodiment Figure 1 shows a cross-sectional view of a clutch disk assembly 1 as an embodiment of the present invention, showing the plan view in FIG. The clutch disk assembly 1 is a power transmission device used for a clutch device of a vehicle, and has a clutch function and a damper function. 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 input from the flywheel side by a spring or the like.

In FIG. 1, OO is the rotation axis of the clutch disk assembly 1. An engine and a flywheel (not shown) are arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of FIG. Further, the arrow R1 side in FIG. 2 is the drive side (positive side) in the rotational direction of the clutch disc assembly 1, and the arrow R2 is the opposite side (negative side).

The clutch disk assembly 1 mainly includes an input rotary member 2, a spline hub 3, and a damper mechanism 4 disposed between the input rotary member 2 and the spline hub 3.

The input rotator 2 is a member to which torque is input from a flywheel (not shown). Input rotator 2
Is mainly a clutch plate 5 and a retaining plate 6
(The second rotating member) and the clutch disk 12. The clutch plate 5 and the retaining plate 6 are both circular or annular members made of sheet metal, and are arranged at predetermined intervals in the axial direction. The clutch plate 5 is arranged on the engine side, and the retaining plate 6 is arranged on the transmission side. The clutch plate 5 and the retaining plate 6 are fixed to each other by a plate-like connecting portion 7, so that the axial distance is determined and the clutch plate 5 and the retaining plate 6 rotate integrally.

The clutch disk 12 is a portion that is pressed against and connected to a flywheel (not shown). The clutch disc 12 includes a cushioning plate and a friction facing. The clutch disk 12 is fixed to the outer periphery of the clutch plate 5 and the retaining plate 6 by rivets 10.

Each of the clutch plate 5 and the retaining plate 6 has a center hole. The spline hub 3 is arranged in the center hole. A shaft extending from a transmission (not shown) is spline-engaged with the spline hub 3. A hub flange 8 (first rotating member) is disposed between the plates 5 and 6 in the axial direction on the outer peripheral side of the spline hub 3. The hub flange 8 is a circular slope member having a center hole. The hub flange 8 is rotationally connected to the spline hub 3 by a coil spring 9.

Next, the structure of the damper mechanism 4 provided between the plates 5, 6 and the hub flange 8 will be described. The damper mechanism 4 includes a plurality of coil spring assemblies 1.
3 is comprised. Each coil spring assembly 13
Are the large coil spring 30 and the small coil spring 3
1 and a pair of spring seats 64 arranged at both ends of the small coil spring 31.

Next, the plates 5, 6 and the hub flange 8
, The structure of the portion supporting the coil spring assembly 13 and the relationship between those portions and the coil spring assembly 13 will be described in detail.

The hub flange 8 is provided at regular intervals in the rotation direction.
Window holes 21 are formed. The window hole 21 has a shape that extends long in the rotation direction. The edge of the window hole 21 has contact portions 24 on both sides in the circumferential direction (both ends in the circumferential direction) and outer peripheral portions 22 on the outer peripheral side.
And an inner peripheral portion 23 on the inner peripheral side. The contact portion 24 is formed substantially parallel to a radial line passing through the center of the window hole 21 in the circumferential direction. The outer peripheral portion 22 extends curvedly along the rotation direction of the clutch disk assembly 1, and the inner peripheral portion 23 extends substantially perpendicular to the contact portion 24. A notch 27 is provided at a radially intermediate portion of the contact portion 24. The notch 27 has a trapezoidal shape that opens in the circumferential direction.
The notch 27 has a trapezoidal shape whose radial width on the open side increases. As a result, the contact portion 24 of the window hole 21 has the notch 2
7 and straight portions 25 and 26 on both sides in the radial direction.

The coil spring assembly 13 is disposed in the window 21. Both ends in the circumferential direction of the large coil spring 30 are supported by the contact portions 24. In particular,
Both ends in the radial direction of both ends in the circumferential direction of the large coil spring 30 are in contact with or close to the linear portions 25 and 26 of the contact portion 24, respectively. The small coil spring 31 has a smaller wire diameter and a smaller coil diameter than the large coil spring 30, and has a smaller spring constant than the large coil spring 30. Small coil spring 31 is large coil spring 3
0. Both ends in the circumferential direction of the small coil spring 31 are supported by the contact portion 24 via a spring seat 64 (described later).

Next, the structure of the spring seat 64 will be described. The entire spring seat 64 is integrally formed from an elastic resin material. An example of the elastic resin material is a thermoplastic polyester elastomer.

The spring seat 64 is mainly composed of a support portion 65 and a projecting portion 66. The support portion 65 extends long in the axial direction. The support portion 65 has a flat support surface 6 on one side.
8 and a trapezoidal engaging surface 69 on the other side. That is, the support portion 65 has a substantially trapezoidal shape in a plan view or a cross section that intersects in the axial direction. The support portion 65 has a radially intermediate portion engaged with the notch 27 from the circumferential direction. In this state, the spring seat 64 is brought into contact with the contact portion 24.
Circumferentially inward (the opposing spring seat 64
Side) is supported so as to be detachable and not to be able to move or rotate in the radial direction.

The projecting portions 66 have a structure for realizing a stopper torque by making contact with each other. The protrusion 66 is provided on the support surface 68 side, and extends in the circumferential direction from the axial middle of the support surface 68. The protrusion 66 has an outer peripheral surface 70 and a contact surface 71 at the tip. The protrusion 66 has a substantially cylindrical shape, and extends in the circumferential direction from an axially intermediate portion of the support surface 68. The protruding portion 66 has a cylindrical shape whose diameter gradually decreases from the root portion on the support surface 68 side toward the tip. However, the projecting portion 66 has a radially outer portion extending perpendicularly from the support surface 68, and a radially inner edge is inclined so as to approach the radially outer side toward the tip. Thus, the outer peripheral surface 70 of the protruding portion 66 has a radially outer portion abutting or approaching the radially outer surface of the inner surface of the small coil spring 31. Further, the diameter of the root portion of the outer peripheral surface 70 of the protrusion 66, that is, the portion close to the support surface 68, is substantially the same as the inner diameter of the small coil spring 31. The contact surface 71 is a flat surface extending along the axial direction at the tip of the protrusion 66, and the radially inner portion is located on the inner side in the circumferential direction, that is, on the side of the opposing spring seat 64 as compared with the radially outer portion. I have. That is, the contact surface 71 is an inclined surface. In other words, the contact surface 71 includes the straight portions 17 and 18 of the contact portion 16 and the straight portions 25 and
It is not parallel to 26 but inclined. Specifically, the opposing contact surfaces 71 are closer in the radially inner side than in the outer side. Further, both contact surfaces 71 are viewed from a plane,
It has an inclination angle respectively corresponding to two straight lines passing through the center O of the clutch disk assembly 1.

Two restricting portions 67 are provided on the opposite side of the engaging surface 69 from the supporting portion 65. The two restricting portions 67 are formed at an axially intermediate portion at an interval in the axial direction. The restricting portion 67 extends over the entire engaging surface 69. The two restricting portions 67 are located on both axial sides of the hub flange 8. That is, the two restricting portions 67 are axially opposed to a portion further outward in the circumferential direction from the notch 27 in the hub flange 8. As a result, when the spring seat 64 is engaged with the circumferential end of the window hole 21, the movement of the spring flange 64 in both axial directions with respect to the hub flange 8 is restricted.

The small coil spring 31 is provided on the support surface 68.
And both ends of the large coil spring 30 (particularly, both sides in the axial direction) are supported. Large coil spring 30
Are supported by the contact portions 24 of the hub flange 8 and the contact portions 16 of the plates 5 and 6. Both ends in the axial direction of the small coil spring 31 (particularly, both sides in the radial direction) are supported by the contact portions 24 of the hub flange 8.

On the outer peripheral portions of the clutch plate 5 and the retaining plate 6, four spring support portions 11 (spring accommodation portions) are formed at regular intervals in the rotation direction. Each spring support 11 is a hole penetrating in the axial direction. The position and shape of the spring support portion 11 are formed corresponding to the window hole 21. Each spring support portion 11 has an outer peripheral side covering portion 14 and an inner peripheral side covering portion 15.
Are formed. The outer peripheral side cover portion 14 is a raised portion formed by drawing, and the coil spring assembly 1
3 is for restricting the movement in the axially outward direction and the radially outward direction. The inner peripheral side cover portion 15 has a shape cut and raised integrally from the plate main body, and serves to limit the axially outward and radially inward movement of the coil spring assembly 13. Although both ends in the circumferential direction of the inner cover 15 are cut and raised from the plate body, both ends in the circumferential direction of the outer cover 14 have reinforcing portions 14a extending radially inward from the outer portion. ing. Reinforcing part 14
a extends vertically from the plate body.

The spring supporting portion 11 has an outer peripheral edge composed of an outer peripheral side covering portion 14, an inner peripheral edge substantially composed of an inner peripheral side covering portion 15, and contact portions 16 on both sides in the circumferential direction. The contact portion 16 is formed with a notch 19 at a radially intermediate portion. The notch 19 has a similar shape corresponding to the notch 27. That is, the contact portion 16 is constituted by straight portions 17 and 18 on both sides in the radial direction, and a notch 19 formed therebetween. In addition, the linear portion 17 on the outer peripheral side
Is formed substantially on the inner side surface of the reinforcing portion 14a, and the straight portion 18 on the inner peripheral side is constituted by a sheared surface formed by cutting and raising the inner peripheral side covering portion 15.

The support portions 65 are provided in the notches 19 of the plates 5 and 6.
Are engaged with each other (particularly on both axial sides).
As a result, the spring seat 64 is circumferentially inward with respect to the contact portion 16 (on the side of the opposing spring seat 64).
, And cannot be moved or rotated in the radial direction.

The one restricting portion 67 is located on the inner side in the axial direction of the plate 5 (on the plate 6 side).
Is located axially inside the plate 6 (the plate 5 side). That is, the two regulating portions 67 are axially opposed to portions of the plates 5 and 6 that are further circumferentially outward from the notch 19. As a result, in the state where the spring seat 64 is engaged with the circumferential end of the spring support portion 11, the movement of the springs 64 to both axial sides with respect to the plates 5 and 6 is restricted.

Next, the operation of the damper mechanism 4 will be described with reference to FIGS. FIG. 6 shows a neutral state, in which the plates 5, 6 and the hub flange 8 are not relatively rotated. From the state shown in FIG. 6, the plates 5 and 6 are fixed to other members so as not to rotate, and the hub flange 8 is rotated in the rotation direction R2 with respect thereto. Then, the hub flange 8
The large coil spring 30 and the small coil spring 31 are compressed in parallel between the R1 contact portion 24 of the window hole 21 and the R2 contact portion 16 of the spring support portions 11 of the plates 5 and 6. . In the state shown in FIG. 7, the contact surfaces 71 of the pair of spring seats 64 contact each other, and the relative rotation of both rotating members (the plates 5, 6 and the hub flange 8) stops. At this time, a sufficiently large stopper torque is obtained by the pair of spring seats 64.

While the large coil spring 30 and the small coil spring 31 are being compressed, the spring seat 64 on the R1 side moves with the rotation of the hub flange 8, and the amount of movement of the radially outer part is the movement of the radially inner part. Greater than quantity. As a result, in the contact state shown in FIG. 7, the contact surfaces 71 of both spring seats 64 face each other in parallel. Therefore, the contact surfaces 71 are entirely in contact with each other, and a load is generated in a direction perpendicular to the contact surface 71. As a result, the spring seat 64 generates a sufficiently large load.

The spring seat 64 during the above operation
Will be described in more detail. The R1 side spring seat 64 is supported by the R1 side contact portion 24 of the window hole 21 of the hub flange 8, and the R2 side spring seat 64.
Are the R2 side contact portions 16 of the spring support portions 11 of the plates 5 and 6.
It is supported by. More specifically, the spring seat 64 on the R1 side is supported in the circumferential direction of the clutch disc assembly 1 by the notch 27 of the contact portion 24, particularly at the axially intermediate portion of the engaging surface 69 of the support portion 65. ing. The spring seat 64 on the R2 side has the engagement surface 69 of the support portion 65, particularly the axially both sides thereof, formed by the notch 19 of the contact portion 16 of the plates 5 and 6 so that the clutch disc assembly 1
Are supported in the circumferential direction.

As described above, the pair of spring seats 64 come into contact with each other when the plates 5, 6 and the hub flange 8 rotate relative to each other, and generate a large load to achieve a desired stopper torque. Here, since the pair of spring seats 64 is made of an elastic resin material,
The desired elastic function is obtained.

In this embodiment, the conventional elastic float body can be dispensed with, the number of parts is reduced, and the manufacturing cost is reduced. Second Embodiment In the second embodiment shown in FIGS. 8 to 10, description of the same parts as in the first embodiment will be omitted, and different parts will be mainly described.

The coil spring assembly 13 includes a large coil spring 30, a small coil spring 31, a pair of spring seats 64, and an elastic float 99. The large coil spring 30 and the small coil spring 31 are the same as in the above-described embodiment.

The pair of spring seats 64 are made of, for example, hard resin or metal. The spring seat 64 has substantially the same structure as the spring seat in the above embodiment. The spring seat 64 includes a support portion 65 and a protrusion 73. The protrusion 73 extends in a circumferential direction from an axially intermediate portion of the support surface 68. Projection 73
Has a substantially cylindrical shape, and its diameter is small coil spring 3.
1 is approximately equal to the inner diameter. A contact surface 7 is provided at the tip of the projection 73.
8 are formed. The contact surface 78 is a flat surface along the axial direction, and is inclined so that its radially inner portion is located more inward in the circumferential direction than the radially outer portion.
That is, the contact surface 78 is inclined. In other words, the abutment surface 78 includes the straight portions 17 and 18 of the abutment portion 16 and the abutment portion 24.
Are not parallel to the straight portions 25 and 26 but inclined.
Specifically, the opposing contact surfaces 78 are closer to each other on the inner side in the radial direction than on the outer side.

An elastic float 99 is arranged between the pair of spring seats 64. The elastic float member 99 is an elastic member disposed in the large coil spring 30 and the small coil spring 31 in the window hole 21 and the spring support portion 11. The elastic float body 99 is a member for realizing high rigidity characteristics by being compressed when the torsion angle increases. That is, the elastic float body 99 is movable within the small coil spring 31 by a predetermined distance or angle between the pair of spring seats 64 in the circumferential direction, and is not compressed until the torsional angles of both the rotating bodies become large.

The elastic float body 99 is formed integrally from, for example, an elastic resin material. The elastic resin material includes, for example, a thermoplastic polyester elastomer. The elastic float body 99 has a substantially columnar shape, but has a smaller diameter at the middle portion in the longitudinal direction than at both ends in the longitudinal direction. In other words, the elastic float body 99 is smoothly constricted so that the diameter gradually decreases from both ends in the longitudinal direction. Therefore, the elastic float body 99 has low rigidity in the middle portion in the longitudinal direction, and is easily bent. The diameter of both ends in the longitudinal direction of the elastic float body 99 is substantially equal to the inner diameter of the small coil spring 31. Further, flat contact surfaces 100 are formed at both ends in the longitudinal direction of the elastic float body 99. The contact surfaces 100 are parallel to each other, and in the neutral state in FIG. 9, the contact surfaces 100 are the linear portions 17 and 18 of the contact portion 16 and the linear portions 2 of the contact portion 24.
5 and 26 are parallel.

The circumferential length or circumferential angle of the elastic float body 99 is determined by the contact surface 78 of the pair of spring seats 64.
It is shorter than the circumferential length or circumferential angle of each other. This means that the elastic float body 99 can move in the circumferential direction between the pair of spring seats 64, and furthermore, until the relative rotation angle between the plates 5, 6 and the hub flange 8 reaches a predetermined angle. Means uncompressed.

FIG. 9 shows a neutral state, in which the plates 5, 6 and the hub flange 8 do not rotate relative to each other. From the state shown in FIG. 9, the plates 5 and 6 are fixed to other members so as not to rotate, and the hub flange 8 is rotated in the rotation direction R2 with respect thereto. Then, the radius R of the window hole 21 of the hub flange 8 is changed.
The large coil spring 30 and the small coil spring 31 are compressed in parallel between the first contact portion 24 and the R2 contact portion 16 of the spring support portions 11 of the plates 5 and 6. FIG.
When the state becomes zero, the contact surfaces 78 of the pair of spring seats 64 and the contact surfaces 100 of the elastic float body 99 contact each other,
The relative rotation of both rotating members (plates 5, 6 and hub flange 8) stops. At this time, a sufficiently large stopper torque is obtained by the elastic float body 99.

During the compression of the large coil spring 30 and the small coil spring 31, in the R1 contact portion 24 of the window hole 21, the amount of movement in the rotational direction of the outer portion in the radial direction is larger than that of the inner portion. It is conceivable that the compression amount of the outer peripheral side portion of the spring 30 and the small coil spring 31 becomes larger than the compression amount of the inner peripheral side portion. On the other hand, in this embodiment, a pair of spring seats 64 are provided.
The contact surface 78 of the spring seat 64 and the elastic float 99
Abuts on almost the entire surface. That is, a force acts on the contact surfaces 78 and 100 almost perpendicularly. As a result, the elastic float body 99 can generate a sufficiently large load while being elastically compressed, and as a result, the clutch disk assembly 1 can obtain a sufficiently large stopper torque. Third Embodiment In the third embodiment, description of the same parts as in the second embodiment will be omitted, and different parts will be mainly described.

The coil spring assembly 13 in the third embodiment includes a large coil spring 30, a small coil spring 31, a pair of spring seats 64, and an elastic float 80. Large coil spring 3
0, the small coil spring 31 and a pair of spring seats 64 are the same as in the above-described embodiment.

The elastic float member 80 is an elastic member disposed in the window coil 21 and the spring support portion 11 and further in the large coil spring 30 and the small coil spring 31. The elastic float body 80 is a member for realizing high rigidity characteristics by being compressed when the torsion angle increases. That is, the elastic float body 80 is movable within the small coil spring 31 by a predetermined distance or angle between the pair of spring seats 64 in the circumferential direction, and is not compressed until the torsional angles of both the rotating bodies become large.

The elastic float body 80 comprises an elastic resin portion 81 and sheet portions 82 at both ends. Elastic resin part 8
Reference numeral 1 denotes a columnar member that extends long in the circumferential direction. The elastic resin portion 81 is about half as short as the inner diameter of the small coil spring 31. The seat portion 82 is a columnar member made of, for example, a hard resin. A hole 84 is formed in the circumferential direction inside of the seat portion 82. Both ends of the elastic resin portion 81 are inserted into the hole 84 and fixed by an adhesive or other means. The outer diameter of the seat 82 is substantially the same as the inner diameter of the small coil spring 31. That is, the posture of the elastic float body 80 with respect to the small coil spring 31 is determined by the pair of seat portions 82. Further, a contact surface 83 facing the contact surface 78 of the spring seat 64 is provided outside the seat portion 82 in the circumferential direction. The contact surfaces 83 are parallel to each other, and in the neutral state in FIG. 12, the contact surfaces 83 are parallel to the straight portions 17 and 18 of the contact portion 16 and the straight portions 25 and 26 of the contact portion 24. I have.

With the structure described above, the elastic float body 80 has a low rigidity at the elastic resin portion 81, which is an intermediate portion in the longitudinal direction, and is more easily bent than the elastic float body of the above embodiment.

FIG. 12 shows a neutral state, in which the plates 5, 6
And the hub flange 8 do not rotate relative to each other. From the state shown in FIG. 12, the plates 5 and 6 are fixed to other members so as not to rotate, and the hub flange 8 is rotated in the rotation direction R2 with respect thereto. Then, the R1 side contact portion 24 of the window hole 21 of the hub flange 8 and the spring support portion 11 of the plates 5 and 6
The large coil spring 30 and the small coil spring 31 are compressed in parallel with the R2 side contact portion 16 of FIG. When the state shown in FIG. 13 is reached, the contact surfaces 78 of the pair of spring seats 64 and the contact surfaces 83 of the elastic float body 80 contact each other,
The relative rotation of both rotating members (plates 5, 6 and hub flange 8) stops. At this time, a sufficiently large stopper torque is obtained by the elastic float body 99.

During the compression of the large coil spring 30 and the small coil spring 31, in the R1 contact portion 24 of the window hole 21, the amount of movement in the rotational direction of the outer portion in the radial direction is larger than that of the inner portion. It is conceivable that the compression amount of the outer peripheral side portion of the spring 30 and the small coil spring 31 becomes larger than the compression amount of the inner peripheral side portion. On the other hand, in this embodiment, a pair of spring seats 64 are provided.
The contact surface 78 of the spring seat 64 and the elastic float 80
Abuts on almost the entire surface. That is, a force acts on the contact surfaces 78 and 83 almost perpendicularly. As a result, the elastic float body 99 can generate a sufficiently large load while being elastically compressed, and as a result, the clutch disk assembly 1 can obtain a sufficiently large stopper torque.

In particular, since the outer diameter of the elastic resin portion 81 is shorter than that of the small coil spring 31, the rigidity of the entire elastic float body 80 is low. Thereby, the elastic float body 80 can exhibit sufficient elasticity in addition to the advantage of using the elastic resin. Since the elastic float body 80 can be elastically deformed in this way, the contact surface 78 of the spring seat 64 and the contact surface 8 of the elastic float body 80 can be deformed.
3 is improved. Also, elasticity can be obtained when a stopper torque is generated. [Other Embodiments] Although the hub flange 8 is separated from the spline hub 3 in the above embodiment, it may be formed integrally.

The damper disk assembly according to the present invention can be applied not only to a clutch disk assembly but also to a damper mechanism of a flywheel assembly and a lock-up damper of a torque converter.

[0052]

In the damper disk assembly according to the present invention, since the ends of the pair of spring seats are inclined surfaces, the members that come into contact with each other in order to generate the stopper torque come into full contact with each other, and Large stopper torque can be obtained.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view of a clutch disk assembly to which an embodiment of the present invention is applied.

FIG. 2 is a plan view of the clutch disc assembly.

FIG. 3 is a partially enlarged view of FIG. 1;

FIG. 4 is a partially enlarged view of FIG. 2;

FIG. 5 is a perspective view of a spring seat.

FIG. 6 is a schematic partial plan view for explaining the operation of the damper mechanism.

FIG. 7 is a schematic partial plan view for explaining the operation of the damper mechanism.

FIG. 8 is a perspective view of a spring seat according to a second embodiment.

FIG. 9 is a schematic partial plan view for explaining the operation of the damper mechanism.

FIG. 10 is a schematic partial plan view for explaining the operation of the damper mechanism.

FIG. 11 is a partial cross-sectional view of an elastic float according to a third embodiment.

FIG. 12 is a schematic partial plan view for explaining the operation of the damper mechanism.

FIG. 13 is a schematic partial plan view for explaining the operation of the damper mechanism.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Clutch disk assembly 2 Input rotating body 3 Spline hub 4 Damper mechanism 5 Clutch plate 6 Retaining plate 8 Hub flange 31 Small coil spring 64 Spring seat 65 Support part 66 Projection part 68 Support surface 71 Contact surface

Claims (3)

[Claims] A first rotating member having a spring receiving hole formed therein; and a second plate-like rotating member having a spring receiving portion formed therein corresponding to the spring receiving hole and disposed near the first rotating member. A rotating member, a coil spring disposed in the spring receiving hole and the spring receiving portion, and capable of transmitting torque between the first rotating member and the second rotating member; and disposed at circumferential ends of the coil spring. And a pair of circumferentially opposite ends of the coil spring that are supported and engage with the inside of the coil spring, and are circumferentially engageable with both ends of the spring receiving hole and the spring receiving portion in the circumferential direction. A damper disk assembly comprising: a spring seat; and a tip of the pair of spring seats has an inclined surface whose radial inner end is located closer to the opposing spring seat than the radial outer end. 2. A tip of the pair of spring seats is configured to abut each other when the first and second rotating members rotate relatively to each other and the pair of spring seats approach each other. 2. The damper disk assembly according to claim 1. 3. The damper disk assembly according to claim 1, further comprising an elastic float disposed in said coil spring so as to be movable in a circumferential direction.