JP2000205339A - Elastic float body - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide high rigidity of an elastic float body made of an elastic resin material. SOLUTION: An elastic float body 80 is used in a damper mechanism for absorbing and damping the vibration in the direction of rotation of a rotary member. The elastic float body 80 is provided with a main body 81 and a seat part 82. The main body 81 is made of an elastic resin material and is long in one direction. The seat part 82 is fixed to both ends in the longitudinal direction of the main body 81. The seat part 82 is a highly rigid member having a larger diameter than the main body 81 and higher rigidity than the main body 81.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to an elastic float body,
In particular, the present invention relates to an elastic float used for a damper mechanism for absorbing and attenuating torsional vibration in a power transmission system.

[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]

The above-mentioned conventional elastic float body is formed of, for example, rubber and a pair of sheets made of a hard resin fixed to both ends thereof with an adhesive or the like. For the purpose of improving such a conventional elastic float, Japanese Patent Application Laid-Open No. 9-229138 discloses a structure in which the entire elastic float is integrally formed of an elastic resin material. However, when the elastic float body is integrally molded with the elastic resin, there are the following problems. First, it is conceivable that the diameter of the center portion in the longitudinal direction having the lowest rigidity cannot be sufficiently reduced, and the amount of contraction of the elastic float body decreases. Secondly, only a single rigidity is obtained in the torsional characteristics of the elastic float body, which may not be effective in absorbing vibration. Third, when the elastic float body comes into contact with the cross section of the pair of spring seats or plate members,
Only the radially outer portion of the elastic float body is pushed, and at that time, the posture with respect to other members becomes unstable at the initial stage of compression, and as a result, the contact surface of the elastic float body with respect to other members at the time of compression. There may be a problem that the contact does not occur entirely. In such a case, the elastic float body cannot generate a sufficient load, and a sufficiently large stopper torque cannot be obtained in the damper disk assembly.

An object of the present invention is to solve the problems of an elastic float made of an elastic resin material.

[0006]

The elastic float according to the first aspect is used for a damper mechanism for absorbing and attenuating rotational vibration of a rotating member. The elastic float body has a main body and a highly rigid member. The body is made of an elastic resin material and is long in one direction. The high rigidity members are fixed to both ends in the longitudinal direction of the main body. The high-rigidity member has a larger diameter than the main body and has higher rigidity than the main body.

In the elastic float according to the first aspect, when the elastic float is compressed in the longitudinal direction, the main body made of the elastic resin material is mainly compressed. Thereby, a desired elasticity is obtained. Here, since the diameter of the main body can be reduced by providing the high rigidity member, the main body can be sufficiently compressed.

The elastic float according to the second aspect is used for a damper mechanism for absorbing and attenuating the rotational vibration of the rotating member. The float body has a main body and an elastic body. The main body is made of an elastic resin material. The elastic body is mounted on the main body. The elastic body is not compressed in the initial stage of compression of the main body, and is compressed in parallel with the main body in the initial stage of compression of the main body and thereafter.

In the elastic float according to the second aspect, when the elastic float is compressed, two-stage characteristics of low rigidity and high rigidity are obtained. In the elastic float body according to the third aspect, in the second aspect, the elastic body is attached to a middle portion in a longitudinal direction of the main body.

In the elastic float body according to the third aspect, the elastic body does not directly contact another member. According to a fourth aspect of the present invention, there is provided the elastic float body according to the third aspect, wherein the main body includes a longitudinal middle portion, and longitudinal end portions provided at both longitudinal sides of the longitudinal middle portion and having a diameter larger than the longitudinal middle portion. are doing. The elastic body is an annular shape arranged around the middle part in the longitudinal direction.

In the elastic float according to the fourth aspect, the elastic float does not fall off the main body. Claim 5
In the elastic float body described in (4), in claim 4, the length in the longitudinal direction of the elastic body is shorter than the longitudinal length of the intermediate portion in the longitudinal direction.

In the elastic float body according to the fifth aspect, the elastic body is disposed so as to be movable in the longitudinal direction between both ends in the longitudinal direction around the intermediate portion in the longitudinal direction. The elastic float body according to claim 6 is used for a damper mechanism for absorbing and attenuating the rotational vibration of the rotating member. The elastic float body has a main body and a low-rigidity member. The main body is made of an elastic resin material. The low rigidity member is mounted on the main body. The low rigidity member has a lower rigidity than the main body, and is a member for adjusting the posture of the main body by being elastically deformed before the main body when an external force acts on the main body.

In the elastic float according to the sixth aspect, when the elastic float is compressed in the longitudinal direction, the posture of the main body is adjusted by first elastically deforming the low-rigidity elastic member. Thereby, the contact surfaces of the elastic float body and the other members are entirely in contact with each other.

According to a seventh aspect of the present invention, in the sixth aspect, the main body is long in one direction, and the low-rigidity members are mounted on both ends in the longitudinal direction of the main body. In the elastic float body according to the seventh aspect, the low-rigidity elastic member abuts on another member before the main body and is compressed.

According to the eighth aspect of the present invention, in the seventh aspect, the main body has a protrusion on a front end surface in the longitudinal direction, and the low-rigidity elastic member has an annular shape engaged with the protrusion. In the elastic float body according to the eighth aspect, the low-rigidity member has a simple shape engaged with the projection of the main body.

[0016]

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 composed of a clutch plate 5, a retaining plate 6, and a 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 part that is pressed 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 is arranged 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
The spline hub 3 is connected to the spline hub 3 in a rotational direction 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. Further, each coil spring assembly 13 includes an elastic float body 80.

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 is a trapezoid having a wide radial width on the opening side.
Thereby, the contact portion 24 of the window hole 21 is formed by the notch 27 and the 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. 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 spring seat 64 is made of, for example, a hard resin. The spring seat 64 mainly includes a support portion 65 and a protruding portion 73. The support portion 65 extends long in the axial direction. The support portion 65 has a flat support surface 68 on one side and a trapezoidal engagement 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 trapezoidal shape in which the width in the radial direction decreases toward the side opposite to the support surface 68. 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 supported on the inner side in the circumferential direction with respect to the contact portion 24 (on the side of the opposing spring seat 64) so as to be detachable, but not movable or rotated in the radial direction.

The projecting portion 73 has a substantially cylindrical shape and extends in the circumferential direction from the axially intermediate portion of the support surface 68. The protrusion 73 has an outer peripheral surface 74 and a contact surface 78 at the tip. The diameter of the outer peripheral surface 74 is substantially the same as the inner diameter of the small coil spring 31. The contact surface 78 is a flat surface that extends along the axial direction at the tip of the protrusion 73, 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 78 is an inclined surface. In other words, the contact surface 78 is not parallel to the straight portions 17, 18 of the contact portion 16 and the straight portions 25, 26 of the contact portion 24, but is 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.

Two restricting portions 67 are provided on the engaging surface 69. 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. Two regulation units 6
Numerals 7 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 hub flange 8 is engaged.
Are restricted from moving in both axial directions.

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.

The elastic float member 80 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 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.

As shown in FIG. 6, the elastic float body 80 includes an elastic resin portion 81 (main body) and sheet portions 82 (high rigid members) at both ends. The elastic resin portion 81 is a columnar member that extends long in the circumferential direction. The elastic resin portion 81 is made of, for example, a thermoplastic polyester elastomer.
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. Seat part 82
A hole 84 is formed on the inside in the circumferential direction. 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 attitude of the elastic float body 80 with respect to the small coil spring 31 is determined by the pair of seat portions 82. Further, the outside of the seat portion 82 in the circumferential direction is the spring seat 6.
The contact surface 83 is opposed to the contact surface 78 of No. 4. The contact surfaces 83 are parallel to each other, and the contact surfaces 83 are in the neutral state in FIG.
4 are parallel to the straight portions 25 and 26.

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 easy to bend. Four spring support portions 11 are formed on the outer peripheral portions of the clutch plate 5 and the retaining plate 6 at equal 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 11 is provided with an outer peripheral side cover 14 and an inner peripheral side cover 15. The outer peripheral side cover portion 14 is a raised portion formed by drawing and serves to limit the movement of the coil spring assembly 13 to the outside in the axial direction and the outside in the radial 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.
The reinforcing portion 14a 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 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 move in the radial direction.

The one restricting portion 67 is located axially inside the plate 5 (on the plate 6 side), and the other restricting portion 67
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.

FIG. 7 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. 7, 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.
In this state, the contact surface 78 of the pair of spring seats 64 and the contact surface 83 of the elastic float 80 abut against 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 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 radially outer portion has a larger amount of movement in the rotation direction than the inner portion, so that the large coil 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.

The spring seat 64 during the above operation
Will be described in more detail. The spring seat 64 on the R1 side is supported by the R1 contact portion 24 of the window hole 21, and the spring seat 64 on the R2 side is
Are supported by the R2 side contact portion 16 of the spring support portion 11. 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 at the engaging surface 69 of the support portion 65, particularly at the axially intermediate portion. ing. The R2 side spring seat 64 has a notch 19 of the contact portion 16 of the plates 5 and 6 at the engagement surface 69 of the support portion 65, particularly at both axial portions.
Are respectively supported in the circumferential direction of the clutch disc assembly 1. In the above state, each of the spring seats 64 is urged by the small coil spring 31 against each of the notches 19 and 27.

In the above operation, the elastic float 80
The desired elasticity is obtained mainly by compressing the elastic resin portion 81. Here, since the outer diameter of the elastic resin portion 81 is significantly shorter than the inner diameter 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. As described above, since the elastic float body 80 can be more elastically deformed, the degree of adhesion between the contact surface 78 of the spring seat 64 and the contact surface 83 of the elastic float body 80 is improved.

The above effects are obtained only when the sheet portion 82 is used.
This is because the diameter of the elastic resin portion 81 can be reduced by having the function of abutting the inside of the small coil spring 31 on the elastic member. Further, the seat portion 82 also has a function of a contact surface that contacts the spring seat 64. Second Embodiment In the second embodiment, 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 according to the second embodiment comprises a large coil spring 30, a small coil spring 31, a pair of spring seats 64, and an elastic float body 85, as in the previous embodiment.
The large coil spring 30 and the small coil spring 31 are the same as in the above-described embodiment.

The spring seat 64 shown in FIG. 9 mainly comprises a support portion 65 and a projecting portion 75. The spring seat 64 is made of, for example, a hard resin. The support portion 65 extends long in the axial direction. The support 65 has a flat support surface 68 on one side and a trapezoidal engagement surface 69 on the other side.
have. 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 trapezoidal shape in which the width in the radial direction decreases toward the side opposite to the support surface 68.

The projecting portion 75 has a substantially cylindrical shape, and extends from the axially intermediate portion of the support surface 68 in the circumferential direction. The protrusion 75 has an outer peripheral surface 76 and a contact surface 77 at the tip. The diameter of the outer peripheral surface 74 of the projection 73 is substantially the same as the inner diameter of the small coil spring 31. The contact surface 77 is a flat surface that extends along the axial direction at the tip of the protrusion 66. The contact surface 77 is parallel to the support surface 68. In the neutral state of FIG. 14, the contact surfaces 77 are also parallel to each other, and the contact surfaces 77 are parallel to the linear portions 17 and 18 of the contact portion 16 and the linear portions 25 and 26 of the contact portion 24.

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.

The elastic float body 85 shown in FIG.
1 and the larger coil spring 3 in the spring support 11
0 and an elastic member disposed in the small coil spring 31. The elastic float body 85 is a member for realizing high rigidity characteristics by being compressed when the torsion angle increases. That is, the elastic float body 85 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 85 is mainly composed of a main body 86 and an elastic body 87. The main body 86 is a member integrally formed of an elastic resin material. The main body 86
It has a substantially cylindrical shape, and includes a longitudinal central portion 88 and seat portions 89 provided at both ends of the longitudinal central portion 88. The diameter of the seat portion 89 is larger than that of the central portion 88 and substantially coincides with the inner diameter of the small coil spring 31. Both ends of the seat portion 89 in the longitudinal direction are spring seats 6.
The contact surface 90 is opposed to the contact surface 77 of No. 4. The contact surfaces 90 are parallel to each other, and in the neutral state in FIG. 11, the contact surfaces 90 are the straight portions 17 and 18 of the contact portion 16 and the contact portions 2.
4 are parallel to the straight portions 25 and 26. The elastic body 87 is an elastic body made of rubber, for example, and has a main body 86.
Is a ring-shaped or cylindrical member wound around a central portion 88. The elastic body 87 does not fall off the main body 86 because it is wound around the central portion 88, and does not come into contact with the spring seat 64 because it is mounted in the middle of the main body 86 in the longitudinal direction. The outer diameter of the elastic body 87 is slightly smaller than the outer diameter of the seat portion 89. For this reason, the elastic body 87 does not easily contact the inside of the small coil spring 31. Further, the length of the elastic body 87 in the longitudinal direction is shorter than the length of the central portion 88 in the longitudinal direction, that is, between the longitudinal inner ends of the sheet portion 89. In this state, the elastic body 87 is movable by a predetermined distance between the seat portions 89 in the longitudinal direction. This also means that the compression of the elastic body 87 is not started until the longitudinal compression of the main body 86 reaches a predetermined amount.

The operation of shifting from the state of FIG. 11 to the state of FIG. 12 will be described. FIG. 11 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. 11, 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 large coil spring 30 and the small coil spring 31 are arranged in parallel between the R1 contact portion 24 of the window hole 21 of the hub flange 8 and the R2 contact portion 16 of the spring support portions 11 of the plates 5 and 6. Is compressed. When the relative rotation angle between the plates 5 and 6 and the hub flange 8 increases and the state shown in FIG. 8 is reached, the contact surfaces 77 of the pair of spring seats 64 abut on the elastic float body 85 and the two rotating members (the plates 5 and 6) And the hub flange 8) stops relative rotation. At this time, a sufficiently large stopper torque is obtained by the elastic float body 99.

Specifically, the contact surface 77 and the contact surface 90 first contact each other in the radially outer portions. This is R1
This is because the radially outer portion of the side spring seat 64 has a larger amount of movement in the circumferential direction than the radially inner portion. When the rotation angles of both rotating members further increase, the contact surfaces 77 of the pair of spring seats 64 gradually compress the elastic float body 85 from the outside in the radial direction. Thereby, the radial inside of the contact surface 90 comes into contact with the contact surface 77 of the spring seat 64 while being compressed from the radial outside of the main body of the elastic float body 85. At this time, the central portion 88 of the main body 86 is mainly compressed. As a result,
The pair of seat portions 89 approach each other and sandwich the radially outer portion of the elastic body 87. Thereby, the elastic body 87 is compressed in parallel with the main body 86, and the overall rigidity is increased. As described above, at the initial stage of compression of the main body 86, the elastic body 8
7 has low rigidity because it is not compressed. Since the main body 86 and the elastic body 87 are compressed in parallel after the initial stage of compression, high rigidity is obtained. In this way, two-stage characteristics of low rigidity and high rigidity can be obtained when the stopper torque is generated.

The spring seat 64 during the above operation
Will be described in more detail. The spring seat 64 on the R1 side is supported by the R1 contact portion 24 of the window hole 21, and the spring seat 64 on the R2 side is
Are supported by the R2 side contact portion 16 of the spring support portion 11. 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 at the engaging surface 69 of the support portion 65, particularly at the axially intermediate portion. ing. The R2 side spring seat 64 has a notch 19 of the contact portion 16 of the plates 5 and 6 at the engagement surface 69 of the support portion 65, particularly at both axial portions.
Are respectively supported in the circumferential direction of the clutch disc assembly 1. In the above state, each of the spring seats 64 is urged by the small coil spring 31 against each of the notches 19 and 27. 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 according to the third embodiment comprises a large coil spring 30, a small coil spring 31, a pair of spring seats 64, and an elastic float body 85, as in the previous embodiment.
The large coil spring 30, the small coil spring 31, and the pair of spring seats 64 are the same as in the above embodiment.

The elastic float 92 shown in FIG.
1 and the larger coil spring 3 in the spring support 11
0 and an elastic member disposed in the small coil spring 31. The elastic float body 92 is a member for realizing high rigidity characteristics by being compressed when the twist angle increases. That is, the elastic float body 92 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 angle of both the rotating bodies becomes large.

The elastic float body 92 mainly comprises a main body 93 and a low-rigidity member 94. The main body 93 is a substantially cylindrical member integrally formed from an elastic resin material. The main body 93 includes a central portion 95 in the longitudinal direction, and sheet portions 96 provided at both ends in the longitudinal direction of the central portion 95. The diameter of the seat portion 96 is larger than that of the central portion 95 and substantially coincides with the inner diameter of the small coil spring 31. A protrusion 98 is provided on the seat portion 96. The protrusion 98 is a protrusion that extends in the circumferential direction at the center of the longitudinal end face of the sheet portion 96.

The low rigidity member 94 is an annular member made of, for example, rubber or the like. The low rigidity member 94 is mounted on the longitudinal end surface of the seat portion 96. Specifically, the low rigidity member 9
4 is arranged around the projection 98 and is fixed to the sheet portion 96 by means such as an adhesive. As described above, the shape of the low-rigidity member 94 is simple. As a result, both ends (contact surfaces) in the longitudinal direction of the elastic float body 92 are constituted by the projection 98 made of the elastic resin material and the low rigid member 94 made of rubber or the like arranged around the projection 98. Both ends in the longitudinal direction are parallel to each other, and both ends in the longitudinal direction are straight portions 17, 18 of the contact portion 16 and straight portions 25, 25 of the contact portion 24 in the neutral state in FIG.
26 is parallel.

The operation when shifting from the state of FIG. 14 to the state of FIG. 15 will be described. FIG. 14 shows a neutral state,
The plates 5, 6 and the hub flange 8 do not rotate relative to each other. From the state shown in FIG. 14, 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 large coil spring 30 and the small coil spring 31 are arranged in parallel between the R1 contact portion 24 of the window hole 21 of the hub flange 8 and the R2 contact portion 16 of the spring support portions 11 of the plates 5 and 6. Is compressed. When the relative rotation angle between the plates 5 and 6 and the hub flange 8 increases and the state shown in FIG. 15 is reached, the pair of spring seats 64 sandwich the elastic float body 92 in the rotation direction, and the two rotating members (the plates 5 and 6 and the hub The relative rotation of the flange 8) stops. At this time, the elastic float body 9
9 allows a sufficiently large stopper torque to be obtained.

Specifically, a pair of spring seats 64
The contact surface 77 has a radially outer portion in contact with a radially outer portion of the elastic float body 92 (a radially outer portion of the low-rigidity member 94). This is because the spring seat 64 on the R1 side moves a large amount in the circumferential direction of the radially outer portion with respect to the radially inner portion. Thus, in the initial stage of compression, the low-rigidity members 9 at both ends in the longitudinal direction are used.
4 is compressed. Thereby, the elastic float body 92 is adjusted so as to take a preferable posture between the pair of spring seats 64. When the entire elastic float body is made of, for example, an elastic resin material, the posture of the elastic float body may be disturbed in the initial stage of the contact, and the torsional characteristics due to the subsequent compression of the elastic float body may be unfavorable. There is. When the relative rotation of the rotating member further increases,
The contact surfaces 77 of the pair of spring seats 64 gradually contact the elastic float body 92 over the entire longitudinal end face while compressing the radially outer portion of the elastic float body 92. Thereby, the main body 93 of the elastic float body 92, particularly the central portion 95, is compressed in the circumferential direction, so that desired elasticity can be obtained. Here, since the posture of the elastic float body 92 is adjusted by the compression of the low-rigidity member 94 in the initial stage of compression, the contact surfaces (94, 94) of the elastic float body 92 are adjusted.
98) and the contact surface 77 of the spring seat 64 are entirely in contact.

The spring seat 64 during the above operation
Will be described in more detail. The spring seat 64 on the R1 side is supported by the R1 contact portion 24 of the window hole 21, and the spring seat 64 on the R2 side is
Are supported by the R2 side contact portion 16 of the spring support portion 11. 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 at the engaging surface 69 of the support portion 65, particularly at the axially intermediate portion. ing. The R2 side spring seat 64 has a notch 19 of the contact portion 16 of the plates 5 and 6 at the engagement surface 69 of the support portion 65, particularly at both axial portions.
Are respectively supported in the circumferential direction of the clutch disc assembly 1. In the above state, each of the spring seats 64 is urged by the small coil spring 31 against each of the notches 19 and 27. [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.

[0059]

According to the elastic float of the present invention, it is possible to obtain more excellent effects while taking advantage of the advantage that the main body is made of an elastic resin material.

[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 FIG. 1;

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 partially cutaway front view of the elastic float body.

FIG. 7 is a schematic partial cross-sectional view for explaining the operation of the damper mechanism.

FIG. 8 is a schematic partial sectional view for explaining the operation of the damper mechanism.

FIG. 9 is a perspective view of a spring seat according to a third embodiment.

FIG. 10 is a partial cross-sectional view of an elastic float according to a third embodiment.

FIG. 11 is a schematic partial cross-sectional view for explaining the operation of the damper mechanism.

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

FIG. 13 is a partial cross-sectional view of an elastic float according to a third embodiment.

FIG. 14 is a schematic partial sectional view for explaining the operation of the damper mechanism.

FIG. 15 is a schematic partial cross-sectional view for explaining the operation of the damper mechanism.

[Explanation of symbols]

 Reference Signs List 80 elastic float body 81 main body 82 seat portion 85 elastic float body 86 main body 87 elastic body 88 central portion 89 seat portion 90 contact surface 92 elastic float body 93 main body 94 low rigid member 95 central portion 96 seat portion

Claims (8)

[Claims] 1. An elastic float body used for a damper mechanism for absorbing and attenuating rotational vibration of a rotating member, comprising: a main body made of an elastic resin material and extending in one direction; and fixed to both longitudinal ends of the main body. A high-rigidity member having a diameter larger than the main body and higher in rigidity than the main body. 2. An elastic float body used in a damper mechanism for absorbing and attenuating rotational vibration of a rotating member, comprising: a main body made of an elastic resin material; And an elastic body which is not compressed and is compressed in parallel with the main body after the initial stage of compression of the main body. 3. The elastic float body according to claim 2, wherein the main body is long in one direction, and the elastic body is mounted at an intermediate portion in a longitudinal direction of the main body. 4. The main body includes a longitudinal middle portion, and both longitudinal longitudinal end portions provided on both longitudinal sides of the longitudinal middle portion and having a diameter larger than the longitudinal middle portion. 4. The elastic float according to claim 3, wherein the elastic float is annular around a middle portion in the longitudinal direction. 5. The elastic float according to claim 4, wherein the length of the elastic body in the longitudinal direction is shorter than the longitudinal length of the intermediate portion in the longitudinal direction. 6. An elastic float body used for a damper mechanism for absorbing and attenuating rotational vibration of a rotating member, comprising: a main body made of an elastic resin material; and a rigid body mounted on the main body and having lower rigidity than the main body. A low rigidity member for adjusting the posture of the main body by being elastically deformed before the main body when an external force acts on the main body,
The elastic float body provided with. 7. The elastic float according to claim 6, wherein the main body is long in one direction, and the low-rigidity members are mounted on both ends in a longitudinal direction of the main body. 8. The elastic float body according to claim 7, wherein the main body has a projection on a front end surface in a longitudinal direction, and the low-rigid member has an annular shape engaged with the projection.