JP2000018273A - Clutch disc - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch disc which has twisting characteristics that are smoothly shifted from their low stiffness stage to their high stiffness stage, and can sufficiently reduce vibration and noises taking place in their power transmission system. SOLUTION: A driving plate 11 at the input side is elastically linked with a hub 1 to be linked with the output side 5 by means of a compression spring 14 in such a way that relative rotation can thereby be made. It is so constituted that the hub 1 is linked with the drive plate 11 by way of an inner hub 2 to be linked with the output shaft 5 and the compression spring 14, and is formed out of an outer hub 3 capable of being relatively rotated by a specified angle with respect to the inner hub 2, and of a curved spring member 4 linking the inner hub 2 with the outer hub 3 in such a way that they can be elastically and relatively rotated. Both the ends of the curved spring member 4 are inserted into engaging holes formed up for the inner hub 2 and the outer hub 3 respectively. An elastic member 10 is provided between the end part of the curved spring member 4 and each engaging hole.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch disc used in a clutch device for controlling power transmission of an automobile or the like.

[0002]

2. Description of the Related Art A clutch disk used in a clutch device for controlling power transmission effectively absorbs torsional vibration superimposed on a driving torque from an engine, and generates undesirable vibration and noise in a power transmission system. It has appropriate elasticity in the torsional direction in order to prevent inconvenience.

[0003] Therefore, the torsional characteristics given to this kind of clutch disc are designed to absorb torsional vibration and noise generated in the power transmission system and to transmit a sufficient torque to a small input torque range. It is desired that the torsional rigidity be reduced to enhance the vibration absorption effect, and that a large torque be transmitted with sufficient rigidity and sufficient torque transmission.

For this reason, as this type of clutch disk, for example, Japanese Utility Model Laid-Open Publication No. 2-119526 discloses a drive plate to which a drive torque is input and a hub connected to an output shaft can be relatively rotated by a main spring member. And the hub comprises an inner hub connected to an output shaft and an outer hub connected to a door live plate, and the inner hub and the outer hub are positioned at a predetermined angle relative to each other via a curved spring member. A clutch disk rotatably connected is shown.

In the conventional clutch disk, the main spring and the outer hub are relatively rotated and the curved spring member acts on the low rigidity stage, and after the relative rotation between the inner hub and the outer hub is stopped, the main spring is stopped. It has torsional characteristics consisting of a high rigidity stage in which the member acts.

[0006]

In the prior art, the transition from the low rigidity stage to the high rigidity stage of the torsional characteristic is straightforward, and the torsional rigidity changes rapidly. It is a characteristic.

For this reason, when a vibration that is slightly larger than the vibration that can be absorbed in the low rigidity stage of the torsional characteristic is input, the high rigidity stage becomes apparently rigid in view of the magnitude of the vibration. Since there is no vibration absorbing function, there is a possibility that vibration and noise generated in the power transmission system cannot be sufficiently reduced.

The present invention has been devised in view of the circumstances of the prior art described above, and has a smooth transition from a low rigidity stage to a high rigidity stage in the torsional characteristic, and a vibration generated in the power transmission system. It is another object of the present invention to provide a clutch disk capable of sufficiently reducing noise.

[0009]

According to the first aspect of the present invention, a drive plate to which a drive torque is input and a hub connected to an output shaft are connected by a main spring member so as to be elastically relatively rotatable. The inner hub is connected to the output shaft, the outer hub is connected to the drive plate via a main spring member, and is rotatable relative to the inner hub by a predetermined angle. In a clutch disc comprising a curved spring member elastically and relatively rotatably connected to an outer hub, ends of the curved spring member are inserted into engagement holes formed in each of the inner hub and the outer hub. An elastic member is provided between the end of the curved spring member and the engagement hole.

According to a second aspect of the present invention, a drive plate to which a driving torque is input and a hub connected to an output shaft are connected by a main spring member so as to be relatively rotatable elastically, and the hub is connected to the hub. Are connected to the drive plate via a main spring member, the outer hub is rotatable relative to the inner hub by a predetermined angle, and the inner hub and the outer hub are elastically connected. A clutch disk comprising a curved spring member linked to the inner hub and / or the inner hub and / or
Alternatively, the outer hub is provided with a contact portion with which the inner or outer circumference of the curved spring member comes into contact during the relative rotation between the inner hub and the outer hub.

According to a third aspect of the present invention, in the second aspect of the invention, the contact portion is formed in a projecting shape so as to make point contact with the curved spring member.

According to a fourth aspect of the present invention, in the configuration of the second and third aspects, a lubricant film is formed between the contact portion and the curved spring member. It is.

According to a fifth aspect of the present invention, in the second aspect of the present invention, the contact portion is made of a synthetic resin material.

Here, in the first aspect of the present invention, the elastic member provided between the end of the curved spring member and the engagement hole is made of rubber or a synthetic resin material, and is used when the clutch disk is operated. Has a greater rigidity than the rigidity exhibited by the curved spring member.

Therefore, according to the present invention, when the driving torque is output from the drive plate to the output shaft via the hub (the inner hub and the outer hub), the clutch disk is driven as follows. Operate.

That is, in a region where the torque input to the drive plate is small, the outer hub connected to the drive plate via the main spring member is substantially integrated with the drive plate, and is relatively rotated with respect to the inner hub. Move. As a result, the spring action of the curved spring member is exerted, and a torsional characteristic in a low rigidity stage is obtained (A region in FIG. 6).

When the torque input to the drive plate increases, the amount of relative rotation between the inner hub and the outer hub, that is, the torsion angle of the outer hub with respect to the inner hub increases. For this reason, while the spring action of the curved spring member continues, the elastic member is compressed between the end of the curved spring member and the engagement hole, and the spring action of the elastic member is applied. The spring action by the curved spring member and the elastic member is exerted within a predetermined angle range in which the inner hub and the outer hub can relatively rotate. Thereby, an intermediate stage torsional characteristic is obtained (region B in FIG. 6).

When the torque input to the drive plate further increases, the inner hub and the outer hub become integral after the inner hub and the outer hub rotate relative to each other by a predetermined angle. Rotate relative to the outer hub. Therefore, the spring action of the curved spring member and the elastic member continues, and the spring action of the main spring member is added. Thereby, the torsional characteristics at the high rigidity stage are obtained (region C in FIG. 6).

Thus, the main spring member operates after the relative rotation between the inner hub and the outer hub is stopped from the low rigidity stage in which the inner hub and the outer hub rotate relative to each other and the curved spring member operates. The transition to the high-rigidity stage provides smooth torsional characteristics. For this reason, vibration and noise generated in the power transmission system can be sufficiently reduced.

Accordingly, a clutch disk having a smooth transition of the torsional characteristic from the low-rigidity stage to the high-rigidity stage and capable of sufficiently reducing the vibration and noise generated in the power transmission system can be obtained.

According to the second aspect of the present invention, when the drive torque is output from the drive plate to the output shaft via the hub (the inner hub and the outer hub), the clutch disk operates as follows. I do.

That is, in a region where the torque input to the drive plate is small, the outer hub connected to the drive plate via the main spring member is substantially integrated with the drive plate, and is relatively rotated with respect to the inner hub. Move. Thereby, the spring action of the curved spring member is exerted, and a torsional characteristic at a low rigidity stage is obtained (FIG. 11).
A region).

When the torque input to the drive plate increases, the amount of relative rotation between the inner hub and the outer hub, that is, the torsion angle of the outer hub with respect to the inner hub increases. When the torsion angle increases, the inner diameter or outer diameter of the curved spring member decreases or the outer diameter dimension increases. Therefore, the inner or outer periphery of the curved spring member is provided on the inner hub and / or the outer hub. Touch the contact. When the inner circumference or the outer circumference of the curved spring member comes into contact with the contact portion, the degree of freedom of deformation of the curved spring member decreases, and the rigidity increases. For this reason, the curved spring member exhibits a spring effect in a state where the degree of freedom of deformation is small and the rigidity is increased. Further, the spring action in a state where the curved spring member is in contact with the contact portion is exerted within a predetermined angle range in which the inner hub and the outer hub can relatively rotate. Thereby, an intermediate stage torsional characteristic is obtained (region B in FIG. 11).

When the torque input to the drive plate further increases, the inner hub and the outer hub become integral with each other after the inner hub and the outer hub rotate relative to each other by a predetermined angle. Rotate relative to the outer hub. Therefore, the spring action of the curved spring member continues, and the spring action of the main spring member is added. As a result, torsional characteristics at the high rigidity stage can be obtained (region C in FIG. 11).

Thus, after the relative rotation between the inner hub and the outer hub is stopped from the low rigidity stage in which the inner hub and the outer hub rotate relative to each other and the curved spring member operates, the main spring member operates. The transition to the high-rigidity stage provides smooth torsional characteristics. For this reason, vibration and noise generated in the power transmission system can be sufficiently reduced.

Therefore, a clutch disk having a smooth transition of the torsional characteristic from the low rigidity stage to the high rigidity stage and capable of sufficiently reducing the vibration and noise generated in the power transmission system can be obtained.

According to the third aspect of the present invention, the contact portion is formed in a projecting shape so as to make point contact with the curved spring member. As a result, the torsional rigidity of the curved spring member is stably obtained.

According to the fourth aspect of the present invention, since the lubricant film is formed between the contact portion and the curved spring member, the contact portion and the curved spring member can be worn. Can be prevented as much as possible.

According to the fifth aspect of the present invention, since the contact portion is formed of a synthetic resin material, a contact sound generated when the curved spring member contacts the contact portion is minimized. Can be reduced.

[0030]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a plan view showing a clutch disk according to an embodiment of the present invention with a part cut away, and a part on the right side is a view showing one drive plate removed, and FIG. 3 is a plan view of the hub shown in FIG. 1, FIG. 4 is an enlarged sectional view taken along the line AA of FIG. 3, and FIG. 5 is a view taken along the line BB of FIG. FIG. 6 is a torsional characteristic diagram of the clutch disk shown in FIG.

In FIG. 1, reference numeral 1 denotes a hub. The hub 1 is an inner hub 2, an outer hub 3 rotatable relative to the inner hub 2 by a predetermined angle, and elastically connects the inner hub 2 and the outer hub 3. And a curved spring member 4 which is connected so as to be relatively rotatable.

The inner hub 2 has a boss 2a and a projecting flange 2b formed on the outer periphery of the boss 2a so as to protrude outward in the radial direction. The boss 2a
A spline 6 for connecting to the output shaft 5 is formed on the inner circumference of the. In this embodiment, three flanges 2b are formed and arranged at equal intervals in the circumferential direction. One end of the curved spring member 4 is inserted into one of the flanges 2b. Engagement hole 7 is formed.

The outer hub 3 is disposed on the outer peripheral side of the inner hub 2 and has an inner protrusion 3a disposed between adjacent flange portions 2b of the inner hub 2. One of them has an engagement hole 8 into which the other end of the curved spring member 4 is inserted. The inner hub 2 has three windows 9 opened to the outer peripheral side.
The windows 4 are annularly arranged.

Adjacent flange 2 of the inner hub 2
A predetermined play angle is provided in the rotation direction between the inner protrusion 3a and the inner protrusion 3a of the outer hub 3, and thereby,
The inner hub 2 and the outer hub 3 are relatively rotatable by a predetermined angle. The relative rotatable angle between the inner hub 2 and the outer hub 3 is determined when the curved spring member 4 described later is in a free state, as shown in FIG.
Is an angle θa for clockwise rotation, and an angle θb for counterclockwise rotation.

The curved spring member 4 has a C-shape as a whole, and both end portions are bent in the same direction to each other, so that the inside of the engagement hole 7 and the outer hub 3 formed in the flange portion 2 b of the inner hub 2, respectively. It is inserted into an engaging hole 8 formed in the one side projection 3a. Thereby, the curved spring member 4 connects the inner hub 2 and the outer hub 3 elastically and relatively rotatably. That is, FIG. 3 shows the free state of the bending spring member 4, and the inner hub 2 is
When rotating in the clockwise direction, the curved spring member 4 is deformed so that its inner diameter is reduced to exert a spring force, while when the inner hub 2 is rotated counterclockwise, the curved spring member 4 is rotated. Is deformed so that its outer diameter increases, and exerts a spring force.

The end of the curved spring member 4 and the engagement holes 7 and 8
Between them, an elastic member 10 is provided. The elastic member 10 is formed of rubber or a synthetic resin material into a cylindrical shape with both ends open, and the end of the curved spring member 4 and the engagement holes 7 and 8 are formed.
And is inserted in the gap between them. Further, the elastic member 1
0 has a rigidity greater than the rigidity exerted by the curved spring member 4 when the inner hub 2 and the outer hub 3 of the hub 1 relatively rotate.

Reference numeral 11 denotes a pair of drive plates. The drive plates 11 are disposed on both sides of the outer hub 3 of the hub 1 and are connected to each other by rivets 12 on the outer peripheral side. In addition, the drive plate 1
Each of the windows 1 has three windows 13 corresponding to the windows 9 formed in the outer hub 3. That is, the windows 8 formed in the drive plate 11 are annularly arranged corresponding to the windows 4 formed in the hub 1.

The outer hub 3 and the drive plate 1
The hub 1 (outer hub 3) and the drive plate 1
A pair of compression springs 14 is housed as a main spring member that elastically connects the first and second springs to each other. The pair of compression springs 14 are double nested springs inside and outside, and are operated in series by the idlers 15 in the accommodated windows 9 and 13.

The idler 15 has an annular connecting portion 15a located on the outer periphery of the hub 1 (outer hub 3), and an arm portion 15b extending radially inward from the annular connecting portion 15a. 15b extends between a pair of compression springs 14 housed in the windows 9 and 13, and the pair of compression springs 14 act in series in the windows 9 and 13. Therefore, in this embodiment, when the hub 1 and the drive plate 11 rotate relatively, the three spring groups acting in series in the windows 9 and 13 act in parallel to obtain elasticity. Become.

Reference numeral 21 denotes a first friction damping device for giving a friction damping resistance to the relative rotation between the inner hub 2 and the outer hub 3 of the hub 1. The first friction damping device 21 includes a cylindrical retainer 22 having one end engaged with the outer hub 3.
And a friction plate 23 in contact with the other end of the retainer 22.
And a disc spring 25 for pressing the friction plate 23 against the retainer 22 via the plate member 24.

Reference numeral 27 denotes the hub 1 and drive plate 11
This is a second friction damping device that gives a friction damping resistance to relative rotation with respect to. The friction damping device 27 is provided between the outer hub 3 and a pair of drive plates 11 facing both sides of the outer hub 3, and is disposed between the outer hub 3 and one drive plate 11, One end is provided with a retainer 28 that engages with the outer hub 3, a friction plate 29 in contact with the retainer 28, and a disc spring 31 that presses the friction plate 29 against the retainer 28 via the plate member 30. Further, a friction plate 32 is provided between the outer hub 3 and the other drive plate 11 and is in contact with the drive plate 11 and the retainer 22 of the first friction damping device 21. Reference numeral 33 denotes a bush disposed between the inner hub 2 and the retainer 28.

Reference numeral 35 denotes a cushioning plate. The cushioning plate 35 has a flat base 35a.
And an elastic portion 35b provided with elasticity in the plate thickness direction, and the elastic portion 35b of the cushioning plate 35 is provided.
On both sides of b, annular main friction plates 36 are attached by rivets 37.

The cushioning plate 35 has a flat base 35a connected to the outer peripheral sides of the pair of drive plates 11 by rivets 12 in a state where the main friction plate 36 is attached to the elastic portion 35b.

The clutch disk having such a configuration is incorporated in a clutch device (not shown), and the main friction plate 36 is pressed against the friction surface of the flywheel by a pressure plate (not shown), so that the driving force from the flywheel is applied to the clutch. Output to the output shaft 5 via the disk.

More specifically, the driving force from a flywheel (not shown) is applied to the main friction plate 36 and the cushioning plate 3.
5, transmitted to the hub 1 via the drive plate 11 and the compression spring 14. The driving force transmitted to the hub 1 via the compression spring 14 is first input to the outer hub 3,
The power is transmitted from the outer hub 3 to the inner hub 2 via the curved spring member 4, and is output to the output shaft 5 via the spline 6 of the inner hub 2.

At this time, the vibration superimposed on the driving force from the flywheel (not shown) is absorbed by the spring force of the bending spring member 4 and the compression spring 14, and the first friction damping device 2
It is damped by the first and second friction damping devices 27.

Here, when the drive torque is output from the drive plate 11 to the output shaft 5 via the hub 1 (the inner hub 2 and the outer hub 3), the clutch disk operates as follows.

That is, in a region where the torque input to the drive plate 11 is small, the outer hub 3 connected to the drive plate 11 via the compression spring (main spring member) 14 is substantially integrated with the drive plate 11. And rotate relative to the inner hub 2. Thereby, the spring action of the curved spring member 4 is exerted, and a torsional characteristic at a low rigidity stage is obtained (A region in FIG. 6).

When the torque input to the drive plate 11 increases, the amount of relative rotation between the inner hub 2 and the outer hub 3, that is, the torsion angle of the outer hub 3 with respect to the inner hub 2 increases. For this reason, while the spring action of the curved spring member 4 continues, the elastic member 10 is compressed between the end of the curved spring member 4 and the engagement holes 7 and 8,
The spring action of the elastic member 10 is added. The spring action of the curved spring member 4 and the elastic member 10 is exerted within a predetermined angle range (θa, θb) in which the inner hub 2 and the outer hub 3 can relatively rotate. Thereby, an intermediate stage torsional characteristic is obtained (region B in FIG. 6).

When the torque input to the drive plate 11 further increases, the inner hub 2 and the outer hub 3 become integral with each other after the inner hub 2 and the outer hub 3 rotate relative to each other by a predetermined angle. The plate 11 rotates relatively to the inner hub 2 and the outer hub 3. Therefore, the spring action of the curved spring member 4 and the elastic member 10 continues, and the spring action of the compression spring (main spring member) 14 is added. Thereby, the torsional characteristics at the high rigidity stage are obtained (region C in FIG. 6).

Thus, after the relative rotation between the inner hub 2 and the outer hub 3 is stopped from the low rigidity stage in which the inner hub 2 and the outer hub 3 are relatively rotated and the curved spring member 4 acts, Compression spring (main spring member) 14
The transition to the high stiffness stage in which the torsion acts acts on a smooth torsional characteristic. For this reason, vibration and noise generated in the power transmission system can be sufficiently reduced.

Accordingly, a clutch disk having a smooth transition of the torsional characteristic from the low-rigidity stage to the high-rigidity stage and capable of sufficiently reducing vibration and noise generated in the power transmission system can be obtained.

FIGS. 7 to 11 show another embodiment of the present invention. This embodiment is different from the above-described embodiment in that the inner hub 2 is provided with an inner hub 2 and an outer hub 3. Is that a contact portion 40 is provided in contact with the inner periphery of the curved spring member 4 during the relative rotation of. In this embodiment, the end of the curved spring member 4 is
The inner hub 2 and the outer hub 3 are inserted without play into engagement holes 7 and 8 respectively formed in the outer hub 3.

First, in the embodiment shown in FIG.
The outer diameter of the boss portion 2a of the inner hub 2 is set to a predetermined size, and the outer periphery of the boss portion 2a is used as the contact portion 40. When the inner hub 2 is rotated clockwise in FIG. 7, the contact portion 40 has a position at which the inner diameter of the curved spring member 4 is reduced and the inner periphery of the curved spring member 4 first contacts, for example, approximately C.
The contact portion 40 and the curved spring member 4 are formed at positions corresponding to the central portion in the circumferential direction of the U-shaped curved spring member 4.
Is defined as t.

When the inner periphery of the curved spring member 4 comes into contact with the contact portion 40, a lubricant is applied to the contact portion 40 in order to prevent wear of the contact portion 40 and the curved spring member 4 as much as possible. The inner periphery of the curved spring member 4 and the contact portion 40
A lubricant film is formed between the two.

In the embodiment shown in FIG. 8, the contact portion 40 is formed of a synthetic resin material by embedding a synthetic resin material on the outer periphery of the boss portion 2a of the inner hub 2. In this embodiment, the lubricant coating between the inner periphery of the curved spring member 4 and the contact portion 40 can be eliminated. In the embodiment shown in FIG. 9, the contact portion 40 is formed in a projecting shape so as to make point contact with the curved spring member 4. Also in this embodiment, a lubricant film is formed between the curved spring member 40 and the protruding contact portion 40.

In the embodiment shown in FIG. 10, the projecting contact portion 40 is formed of a synthetic resin material by embedding a synthetic resin material around the boss 2a of the inner hub 2. . In this embodiment, the lubricant coating between the inner periphery of the curved spring member 4 and the contact portion 40 can be eliminated.

The other components are the same as those of the above-described embodiment. Therefore, the same components are denoted by the same reference numerals, and redundant description will be omitted.

In the embodiment shown in FIGS. 7 to 10, the drive torque is
When output to the output shaft 5 via the (inner hub 2 and outer hub 3), the clutch disk operates as follows.

That is, in a region where the torque input to the drive plate 11 is small, the outer hub 3 connected to the drive plate 11 via the compression spring (main spring member) 14 is substantially integrated with the drive plate 11. And rotate relative to the inner hub 2. Thereby, the spring action of the curved spring member 4 is exerted, and a torsional characteristic at a low rigidity stage is obtained (A region in FIG. 11).

When the torque input to the drive plate 11 increases, the amount of relative rotation between the inner hub 2 and the outer hub 3, that is, the torsion angle of the outer hub 3 with respect to the inner hub 2 increases. When the torsion angle increases and the inner hub 2 rotates clockwise in the drawing,
Since the inner diameter of the curved spring member 4 is reduced, the inner periphery of the curved spring member 4 is contacted with the contact portion 4 provided on the inner hub 2.
Touch 0. The inner periphery of the curved spring member 4 is a contact portion 40
, The degree of freedom of deformation of the curved spring member 4 is reduced, and the rigidity is increased. For this reason, the bending spring member 4 has a small degree of freedom of deformation,
It exerts a spring action when the rigidity is high. Further, the spring action in a state where the curved spring member 4 is in contact with the contact portion 40 is exerted within a predetermined angle range in which the inner hub 2 and the outer hub 3 can relatively rotate. Thereby, an intermediate stage torsional characteristic is obtained (region B in FIG. 11).

When the torque input to the drive plate 11 further increases, the inner hub 2 and the outer hub 3 become integral with each other after the inner hub 2 and the outer hub 3 rotate relative to each other by a predetermined angle. The plate 11 rotates relatively to the inner hub 2 and the outer hub 3. Therefore, the spring action of the curved spring member 4 continues and the spring action of the compression spring (main spring member) 14 is added. As a result, torsional characteristics at the high rigidity stage can be obtained (region C in FIG. 11).

Accordingly, after the relative rotation between the inner hub 2 and the outer hub 3 is stopped from the low rigidity stage in which the inner hub 2 and the outer hub 3 are relatively rotated and the curved spring member 4 acts, Compression spring (main spring member) 14
The transition to the high stiffness stage in which the torsion acts acts on a smooth torsional characteristic. For this reason, vibration and noise generated in the power transmission system can be sufficiently reduced.

Therefore, also in this embodiment,
It is possible to obtain a clutch disk that has a smooth transition characteristic of the torsional characteristic from the low rigidity stage to the high rigidity stage, and can sufficiently reduce vibration and noise generated in the power transmission system.

Further, the contact portion 40 is connected to the curved spring member 4
In this case, the contact position of the contact portion 40 with respect to the curved spring member 4 is stabilized, and the torsional rigidity of the curved spring member 4 is stably obtained.

Also, by forming a lubricant film between the contact portion 40 and the curved spring member 4, the contact portion 4
0 and wear of the curved spring member 4 can be prevented as much as possible.

Further, by forming the contact portion 40 from a synthetic resin material, the curved spring member 4
It is possible to reduce as much as possible the contact sound that occurs when touching zero.

Although the embodiment has been described with reference to the drawings, the specific configuration is not limited to this embodiment and can be changed without departing from the spirit of the invention.
For example, in the embodiment shown in FIGS.
Although the embodiment in which the inner hub 2 is provided with the contact portion 40 in which the inner periphery of the curved spring member 4 is in contact with the inner hub 2, the contact portion 40 in which the inner periphery of the curved spring member 4 is in contact with the outer hub 3 is described.
May be provided.

The inner hub 2 or the outer hub 3 and the contact portion 40 with which the inner periphery of the curved spring member 4 comes into contact.
May be provided with a contact portion with which the outer periphery of the curved spring member 4 contacts. In this case, in both directions (clockwise and counterclockwise) of the relative rotation between the inner hub 2 and the outer hub 3, a torsional characteristic in which the transition to the high rigidity stage is smooth can be obtained.

[0071]

As described above in detail, according to the present invention, the transition of the torsional characteristic from the low rigidity stage to the high rigidity stage has a smooth characteristic, and the vibration and the vibration generated in the power transmission system are reduced. A clutch disk capable of sufficiently reducing noise is obtained.

[Brief description of the drawings]

FIG. 1 is a plan view showing a clutch disk according to an embodiment of the present invention with a part cut away, and the right half is a plan view showing one drive plate removed.

FIG. 2 is a sectional view taken along line AOA of FIG. 1;

FIG. 3 is a plan view of the hub shown in FIG. 1;

FIG. 4 is an enlarged sectional view taken along line AA of FIG. 3;

FIG. 5 is an enlarged sectional view taken along line BB of FIG. 3;

FIG. 6 is a torsional characteristic diagram of the clutch disk shown in FIG. 1;

FIG. 7 is a view similar to FIG. 3, showing another embodiment of the present invention.

FIG. 8 is a view similar to FIG. 3, showing another embodiment of the present invention.

FIG. 9 is a view similar to FIG. 3, showing another embodiment of the present invention.

FIG. 10 is a view similar to FIG. 3, showing another embodiment of the present invention.

11 is a torsional characteristic diagram of the clutch disc shown in FIGS. 7 to 10. FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hub 2 Inner hub 3 Outer hub 4 Curved spring member 5 Output shaft 7 Engagement hole 8 Engagement hole 10 Elastic member 11 Drive plate 14 Compression spring (main spring member)

Claims (5)

[Claims] 1. A drive plate to which drive torque is input and a hub connected to an output shaft are connected by a main spring member so as to be elastically relatively rotatable.
An inner hub connected to the output shaft, an outer hub connected to the drive plate via a main spring member and rotatable relative to the inner hub by a predetermined angle, and elastically moving the inner hub and the outer hub relative to each other. In a clutch disk comprising a curved spring member rotatably connected, an end of the curved spring member is inserted into an engagement hole formed in each of an inner hub and an outer hub. An elastic member is provided between an end portion and an engagement hole. 2. A drive plate, to which drive torque is input, and a hub connected to an output shaft are connected by a main spring member so as to be elastically relatively rotatable.
An inner hub connected to the output shaft, an outer hub connected to the drive plate via a main spring member and capable of rotating relative to the inner hub by a predetermined angle, and elastically connecting the inner hub and the outer hub to each other. In the clutch disk comprising a curved spring member connected to be relatively rotatable, the inner hub and / or the outer hub may be provided with an inner periphery or an outer periphery of the curved spring member during the relative rotation between the inner hub and the outer hub. A clutch disc characterized by having a contact portion in contact therewith. 3. The clutch disk according to claim 2, wherein the contact portion is formed in a projecting shape so as to make point contact with the curved spring member. 4. Between the contact portion and the curved spring member,
4. The clutch disk according to claim 2, wherein a lubricant film is formed. 5. The clutch disk according to claim 2, wherein said contact portion is formed of a synthetic resin material.