JPH1089413A - Vibration damping spring and damper mechanism using it - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a function for vibration damping with a simple structure. SOLUTION: A vibration damping spring element 1 is composed of a leaf spring 2 having a bent area 4 and a pair of lever areas 5 extending from both ends of the area 4, and a elastic body 3 deployed inside the leaf spring 2, which makes elastic deformation when the lever areas 5 deforms in the direction that they get close each other. When external force works in the direction that the lever areas 5 get close each other, the elastic body 3 makes elastic deformation, then in the elastic body 5 internal friction occurs. Here, by simple spring elements composed of the leaf spring 2 and the elastic body 3 a conventional elastic member and resistance generating mechanism are realized, thereby a high performance can be obtained with a compact structure.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping spring and a damper mechanism using the spring for damping torsional vibration.

[0002]

2. Description of the Related Art In a vehicle, for example, a damper mechanism is provided between a member on the engine side and a member on the transmission side to absorb fluctuations in engine torque. The damper mechanism is incorporated in a clutch disk assembly or a flywheel assembly. The damper mechanism includes an input-side member and an output-side member that can rotate relative to each other, a metal spring member such as a coil spring that is arranged so as to limit the rotation when the members rotate relative to each other, and the two members rotate relative to each other. And a friction generating mechanism for attenuating vibration by generating friction. Further, there is a type using a viscous resistance generating mechanism that generates viscous resistance to attenuate vibration instead of the friction generating mechanism. The viscous resistance generating mechanism can generate a larger resistance than the friction generating mechanism.

[0003]

Since the conventional damper mechanism uses a viscous resistance generating mechanism, a fluid chamber for containing a fluid and a sealing mechanism for the fluid chamber are required. Further, since two types of mechanisms, a metal spring member and a viscous resistance generating mechanism, are required, the structure becomes complicated. An object of the present invention is to obtain a damper function for damping vibration with a simple structure.

[0004]

According to a first aspect of the present invention, there is provided a vibration damping spring, comprising: a leaf spring having a bent portion and a pair of lever portions extending from both ends of the bent portion; and a lever disposed inside the leaf spring. A spring element comprising an elastic body which is elastically deformed when deformed in a direction approaching each other. When an external force acts in a direction in which the levers approach each other, the elastic body is elastically deformed and generates internal friction. Here, since a conventional spring member and a friction generating mechanism are realized by a simple spring element including a leaf spring and an elastic body, high-performance performance can be obtained with a compact structure.

[0005] In the vibration damping spring according to the second aspect, in the first aspect, the elastic body is fixed to the leaf spring. Therefore, the elastic body does not easily fall off from the leaf spring. According to a third aspect of the present invention, in the second aspect, the elastic body is formed integrally with the leaf spring. In the vibration damping spring according to a fourth aspect, in any one of the first to third aspects, the elastic body is made of rubber. Therefore, the elastic body generates large internal friction when elastically deforming.

According to a fifth aspect of the present invention, in the vibration damping spring according to any one of the first to fourth aspects, the leaf spring is made of metal.
According to a sixth aspect of the present invention, in the vibration damping spring according to any one of the first to fifth aspects, the elastic body includes a contact portion that is in close contact with the inner surface of the bent portion of the leaf spring, and the lever portion distal end side of the leaf spring from the contact portion. And a protruding portion extending from the lever portion. When an external force acts on the pair of levers in a direction approaching each other, the levers approach each other while being elastically deformed, thereby elastically deforming the elastic body. At this time, the length of the portion of the lever that is not in contact with the elastic body becomes shorter as the displacement of the lever increases. As a result, as the displacement increases, the rigidity of the lever portion increases.

[0007] In the vibration damping spring according to the seventh aspect, in any one of the first to sixth aspects, a plurality of spring elements are arranged and connected so as to be compressible in series. Therefore, a large amount of displacement and low rigidity can be obtained. The vibration damping spring according to claim 8 includes a leaf spring and an elastic body. The leaf spring extends in an alternately bent shape and has a plurality of bent portions and a plurality of lever portions connecting both ends of the plurality of bent portions. The elastic body is arranged between the lever portions, and elastically deforms when the lever portions deform in directions approaching each other. When a compressive force acts on the leaf spring in the extending direction, the lever portion is elastically deformed so as to sandwich the elastic body. Then, the elastic body is elastically deformed to generate internal friction. Here, since a conventional spring member and a friction generating mechanism are realized by a simple spring element including a leaf spring and an elastic body, high-performance performance can be obtained with a compact structure.

[0008] In the vibration damping spring according to the ninth aspect, in the eighth aspect, the elastic body is disposed between some lever portions. In this vibration damping spring, the portion where the elastic body is not arranged between the lever portions has low rigidity, and the portion where the elastic body is arranged between the lever portions has high rigidity. As a result, a low-rigidity region and a high-rigidity region are obtained in the bending characteristics.

According to a tenth aspect of the present invention, in the eighth or ninth aspect, the elastic body is fixed to the leaf spring. In the vibration damping spring according to claim 11, claim 1 is provided.
At 0, the elastic body is formed integrally with the leaf spring. In the vibration damping spring according to the twelfth aspect, in any one of the eighth to eleventh aspects, the elastic body is made of rubber.

According to a thirteenth aspect of the present invention, in the vibration damping spring according to any one of the eighth to twelfth aspects, the leaf spring is made of metal. A vibration damping spring according to a fourteenth aspect includes a leaf spring and a plurality of elastic bodies. The leaf spring extends in an alternately bent shape and has a plurality of bent portions and a plurality of lever portions connecting both ends of the plurality of bent portions. The plurality of elastic bodies are arranged between the plurality of lever portions, and elastically deform when the lever portions deform in a direction approaching each other. When a compressive force acts on the leaf spring in the extending direction, the lever portion is elastically deformed so as to sandwich each elastic body. Then, the elastic body is elastically deformed to generate internal friction. Here, since a conventional spring member and a friction generating mechanism are realized by a simple structure including a leaf spring and an elastic body, high performance can be obtained with a compact structure.

In the vibration damping spring according to a fifteenth aspect, in the fourteenth aspect, the plurality of elastic bodies are arranged between some of the lever portions. In this vibration damping spring, the portion where the elastic body is not arranged between the lever portions has low rigidity, and the portion where the elastic body is arranged between the lever portions has high rigidity. As a result, a low-rigidity region and a high-rigidity region are obtained in the bending characteristics.

According to a sixteenth aspect of the present invention, in the vibration damping spring according to the fourteenth or fifteenth aspect, the plurality of elastic bodies include those having different shapes. The rigidity increases in the portion where the small elastic body is disposed, and increases in the portion where the large elastic body is disposed. As a result, a low-rigidity region and a high-rigidity region are obtained in the bending characteristics. In the vibration damping spring according to a seventeenth aspect, in any one of the fourteenth to sixteenth aspects, the plurality of elastic bodies include those having different rigidities. As a result, a low-rigidity region and a high-rigidity region are obtained in the bending characteristics.

In the vibration damping spring according to the eighteenth aspect, the plurality of elastic bodies are fixed to the leaf spring in the fourteenth aspect. In the vibration damping spring according to the nineteenth aspect, in the eighteenth aspect, the plurality of elastic bodies are integrally formed with the leaf spring. In the vibration damping spring according to the twentieth aspect, in the fourteenth to nineteenth aspects, the plurality of elastic bodies are made of rubber.

In the vibration damping spring according to the present invention, the leaf spring is made of metal. According to the vibration damping spring described in claim 22, in claim 14 to 21, the leaf spring extends in an arc shape as a whole without an external force acting. The vibration damping spring according to claim 23, further comprising: an input-side rotator; an output-side rotator disposed so as to be rotatable relative to the input-side rotator; and an input-side rotator and an output-side rotator. 23. Arranged in an arc shape such that when the rotating bodies rotate relative to each other, they are compressed in the rotating direction between the two rotating bodies.
The vibration damping spring according to any one of the above. Here, when torsional vibration occurs between the input-side rotating body and the output-side rotating body, the leaf spring is compressed in the rotating direction, whereby the elastic body is elastically deformed and generates internal friction. In this structure, the leaf spring provides a wide torsion angle and low rigidity. Further, since the same vibration damping characteristics as those of the related art can be obtained only by combining a plurality of elastic bodies with the leaf spring, it is not necessary to use a viscous resistance. As a result, the need for a sealing mechanism is eliminated.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment [Structure] A vibration damping spring element 1 shown in FIGS.

The leaf spring 2 is made of metal, and is specifically made of spring steel. The leaf spring 2 has a shape that is bent so that both ends of the elongated plate face in the same direction. The bent and curved portion of the leaf spring 2 is referred to as a bent portion 4, and the portion extending from both ends of the bent portion 4 with a gap G in substantially the same direction is referred to as a lever portion 5. The width W and the thickness T of the leaf spring 2 are constant throughout.

The elastic body 3 is arranged inside the leaf spring 2, that is, between the pair of lever portions 5. The elastic body 3 is made of rubber, for example, and is molded, that is, integrally molded on the inner surface of the leaf spring 2 on the bent portion 4 side. More specifically, the elastic body 3 has a portion on the bent portion 4 side as a contact portion 3a, and a portion extending from the contact portion 3a in the longitudinal direction of the lever portion 5 as a projecting portion 3b. The contact portion 3a has a shape along the bent portion 4 and is molded on the inner surface of the bent portion 4. The protrusion 3b has a gap between the pair of levers 5. The protrusion 3
The length in the gap G direction gradually decreases toward the tip, and the gap with the lever portion 5 gradually increases. The elastic body 3 has a length in the width W direction shorter than that of the leaf spring 2 and is disposed at the middle of the leaf spring 2 in the width W direction. Let L be the length of the leaf spring 2 in the longitudinal direction of the lever 5, and let S be the length of the lever 5 from the tip to the portion in contact with the elastic body 3. [Operation] The vibration damping spring element 1 is used for vibration damping. The vibration damping spring element 1 is arranged so that the direction of the gap G coincides with the direction in which the vibration acts. When the vibration is transmitted to the vibration damping spring element 1, the lever portions 5 repeatedly elastically deform in a direction approaching each other, and repeatedly compress the elastic body 3. As a result, the vibration is damped.

In the case of a minute amplitude vibration, the lever portion 5 is mainly elastically deformed, and a low rigidity characteristic is obtained. At this time, since the elastic deformation amount of the elastic body 3 is small, the internal friction is small. With the above characteristics, the minute amplitude vibration is effectively absorbed.
In the case of large-amplitude vibration, the elastic deformation amount of the elastic body 3 increases, so that characteristics of high rigidity and large internal friction can be obtained. With the above characteristics, the large amplitude vibration is effectively attenuated.

The elastic deformation operation of the vibration damping spring element 1 is shown in FIG.
This will be described in more detail with reference to FIGS. In the state of FIG. 3, no external force acts on the vibration damping spring element 1. It is assumed that the external force F acts on the pair of lever portions 5 of the vibration damping spring element 1 from the state of FIG. Then, as shown in the order of FIGS. 4 and 5, the lever portion 5 is elastically deformed and compresses the elastic body 3. In the course of this elastic deformation, the lever portion 5 undergoes the greatest elastic deformation at a length S from the tip. As the elastic deformation of the lever portion 5 progresses, the length of a portion that is not in close contact with the elastic body 3 decreases, and the rigidity increases. In this process, the elastic deformation of the elastic body 3 increases, and the internal friction also increases. [Advantageous Effect] Since both the metal spring member and the friction generating mechanism are realized only by the combination of the leaf spring 2 and the elastic body 3, the vibration damping spring element 1 has a compact structure and a high function. Further, by combining the metal leaf spring 2 and the rubber elastic body 3, the vibration damping spring element 1 has sufficiently high strength and is light in weight. Further, since the elastic body 3 can be easily changed to an arbitrary shape, the leaf spring 2 is made to have a simple structure (for example, a uniform width and a uniform thickness), and
Can change the characteristics of the vibration damping spring element 1.

Since the leaf spring 2 has a bent plate shape, its shape is more compact than, for example, a coil spring. In particular, the width W can be reduced. Since the elastic body 3 is integrally fixed to the leaf spring 2, the elastic body 3 does not fall off from the leaf spring 2. Therefore, the vibration damping spring element 1 can be carried as one member, and transportation and management become easy.

Since the elastic body 3 is made of rubber, it generates a large internal friction when elastically deformed. Further, rubber can be easily formed into an arbitrary shape. The advantageous effects described above are common to all the embodiments described below. [Modification] Vibration damping spring element 1 in this embodiment
Is merely an example of the present invention, and the shape, material, and the like of each member are not limited thereto. For example, the elastic body 3
Is not limited to rubber, but may be a resin or a solid viscoelastic body. Further, the elastic body 3 may have all side surfaces in close contact with the lever portion without having a protruding portion.

The elastic body 3 does not necessarily have to be fixed to the leaf spring 2. If the elastic body 3 is detachable from the leaf spring 2, the bending characteristic of the vibration damping spring element 1 can be changed by replacing the elastic body. The modifications described above are common to all the embodiments described below. Second Embodiment A vibration damping spring 6 shown in FIG. 6 includes a leaf spring 7 and an elastic body 8.

The leaf spring 7 is made of metal, and is specifically made of spring steel. The leaf spring 7 has an S-shaped bent shape, the curved portion being a bent portion 9, a portion connecting one ends of the two bent portions 9, and a portion extending from the other end of the bent portion 9. Is the lever unit 10. As in the first embodiment, the leaf spring 7 has a constant width and thickness throughout.

The elastic body 8 is arranged only inside one bent portion 9 of the leaf spring 7. The elastic body 8 is made of rubber, for example, and is molded on the inner surface of the bent portion 9 of the leaf spring 7 and the pair of lever portions 10. The elastic body 8 extends in the longitudinal direction of the lever portion 10 and is in close contact with the lever portion 10 except for the tip. No elastic body is disposed on the other bent portion 9.

The vibration damping spring 6 is used for vibration damping. The vibration damping spring 6 is arranged so that the direction in which the vibration damping spring 6 extends (the left and right in FIG. 6) matches the direction in which the vibration acts. When the vibration is transmitted to the vibration damping spring 6, the lever portions 10 repeatedly elastically deform in a direction approaching each other, and repeatedly compress the elastic body 8. As a result, the vibration is damped.

At the time of the minute amplitude vibration, mainly, the lever portion 10 and the bent portion 9 on the side where the elastic body is not disposed are elastically deformed, and low rigidity characteristics are obtained. At this time, since the elastic deformation amount of the elastic body 8 is small, the internal friction is small. With the above characteristics, the minute amplitude vibration is effectively absorbed. In the case of a large amplitude vibration, the elastic deformation of the lever portion 10 and the bent portion 9 on the side where the elastic body 8 is not disposed becomes large, and the elastic deformation of the elastic body 8 also becomes large. The characteristics of internal friction are obtained. With the above characteristics, the large amplitude vibration is effectively attenuated.

The basic effect obtained by the combination of the leaf spring 7 and the elastic body 8 is the same as the effect obtained by the vibration damping spring element 1 of the first embodiment. Further, in this embodiment, by forming a portion where the elastic body is not provided in the bent portion 9 of the leaf spring 7, the leaf spring 7 is provided in a small deformation range.
And a large resistance due to the elastic body 8 is obtained in a large deformation range. That is, a two-stage bending characteristic is obtained by operating the leaf spring and the elastic body in series.

The dimensions, shape, and material of the leaf spring 7 and the elastic body 8 are not limited to this embodiment. Third Embodiment The vibration damping spring 6 shown in FIG. 7 has a structure similar to the vibration damping spring 6 shown in the second embodiment, and the elastic body 8 is arranged in the vibration damping spring 6 shown in the second embodiment. The second portion made of the same material as the elastic body 8
The elastic body 8a is arranged. The length of the second elastic body 8a in the longitudinal direction of the lever portion 10 is shorter than that of the elastic body 8, and is less than half the length of the lever portion 10.

In the vibration damping spring 6, the second elastic body 8a
Is less rigid than the opposite side. By providing portions having different rigidities in series in this manner, the same effect as in the second embodiment can be obtained. In particular, in this embodiment, a two-stage bending characteristic is obtained by using a leaf spring and a plurality of elastic bodies having the same material but different shapes. Fourth Embodiment The vibration damping spring 6 shown in FIG. 8 has a structure similar to the vibration damping spring 6 shown in the second embodiment, and the elastic body 8 is arranged in the vibration damping spring 6 shown in the second embodiment. The third portion made of the same material as the elastic body 8
The elastic body 8b is arranged. The length of the third elastic body 8b in the longitudinal direction of the lever portion 10 is shorter than that of the elastic body 8, and is about half the length of the lever portion 10.

In the vibration damping spring 6, the third elastic body 8b
Is less rigid than the opposite side. By providing portions having different rigidities in series in this manner, the same effect as in the second embodiment can be obtained. In particular, in this embodiment, a two-stage bending characteristic is obtained by using a leaf spring and a plurality of elastic bodies having the same material but different shapes. Fifth Embodiment The vibration damping spring 6 shown in FIG. 9 has a structure similar to the vibration damping spring 6 shown in the second embodiment, and the elastic body 8 is arranged in the vibration damping spring 6 shown in the second embodiment. The fourth elastic body 8c is arranged on the side of the bent portion 9 that has not been bent.
The fourth elastic body 8c has the same shape as the elastic body 8, but is made of a material having lower rigidity than the elastic body 8.

In the vibration damping spring 6, the fourth elastic body 8c
Is less rigid than the opposite side. Therefore, the same effect as in the second embodiment can be obtained. here,
By using a leaf spring and a plurality of elastic bodies having different rigidities, a two-stage bending characteristic is obtained. As a matter of course, in the third to fifth embodiments, a plurality of elastic bodies having different materials and shapes may be combined with the leaf spring. Sixth Embodiment A vibration damping spring 11 shown in FIG. 10 includes a leaf spring 12 extending in one direction and a plurality of elastic members 13 provided on the leaf spring 12. The leaf spring 12 has a plurality of bent portions 14 and a plurality of lever portions 15 connecting both ends of the plurality of bent portions 14 by being alternately bent. The plurality of elastic bodies 13 are arranged inside the bent portion 14, respectively. The relationship between the bent portion 14 and the lever portion 15 and the elastic body 13 is the same as in the first embodiment. for that reason,
It may be considered that a plurality of the vibration damping springs 11 are connected so that the vibration damping spring elements 1 of the first embodiment act in series.

When vibration is transmitted to the vibration damping spring 11 in the direction in which the vibration damping spring 11 extends, the vibration damping spring 11 repeats elastic deformation in that direction. At this time,
Each lever 15 is elastically deformed and compresses the elastic body 13. The operations and characteristics of the individual bent portions 14, the lever portions 15, and the elastic members 13 are the same as those described in the first embodiment. Here, since the vibration damping spring elements 1 of the first embodiment are equivalent to being connected in series, a large displacement and low rigidity can be obtained.

The leaf springs 12 may be formed by combining individual leaf spring pieces instead of integrally. Also, leaf spring 1
The shape, size, and arrangement position of the elastic body 2 and the elastic body 13 are not limited to this embodiment. In this embodiment, the elastic bodies 13 have the same shape and the same material, but may have different shapes and materials as in the third to fifth embodiments. Seventh Embodiment A vibration damping spring 11 shown in FIG. 11 includes a leaf spring 12 extending in one direction and a plurality of elastic members 13 provided on the leaf spring 12. The leaf spring 12 is the same as that described in the sixth embodiment. The plurality of elastic bodies 13 are
4, every other one is arranged inside. That is, the bent portions of the leaf springs include those in which the elastic body is arranged and those in which the elastic body is not arranged. This vibration damping spring 11
May be considered that the leaf springs of the second embodiment are connected in series in one direction. The elastic body 13 has one bent portion 14
And extends to the other bent portion 14, and is in full contact with the lever portion 15.

The vibration damping spring 11 is used for vibration damping. The vibration damping spring 11 is arranged such that the direction in which the vibration damping spring 11 extends matches the direction in which the vibration acts. When the vibration is transmitted to the vibration damping spring 11, the lever portions 15 are elastically deformed repeatedly in directions approaching each other,
The elastic body 13 is repeatedly compressed. As a result, the vibration is damped.

In the case of the minute amplitude vibration, the bent portion 14 on which the elastic body is not arranged is mainly elastically deformed, so that a characteristic of low rigidity is obtained. At this time, since the elastic deformation of the elastic body 13 is small, the internal friction is small. With the above characteristics, the minute amplitude vibration is effectively absorbed. In the case of large-amplitude vibration, the bent portion 14 on which the elastic body 13 is disposed also undergoes large elastic deformation, and the elastic body 13 also has a large amount of elastic deformation. Can be With the above characteristics, the large amplitude vibration is effectively attenuated.

Here, the vibration damping spring 6 of the second embodiment is used.
Are connected in series, so that the displacement amount is large and low rigidity is obtained. Further, in this embodiment, by providing an elastic body at a part of the plurality of bent portions 14 of the leaf spring 12, the leaf spring 1 is provided in a small deformation range.
2 and a large resistance due to the elastic body 13 is obtained in a large deformation range. That is, a two-stage bending characteristic is obtained by operating the leaf spring and the elastic body in series.

The dimensions and shapes of the leaf spring 12 and the elastic body 13
The material is not limited to this embodiment. The leaf springs 12 may be formed by combining individual leaf spring pieces instead of being integrated. Eighth Embodiment A modular clutch 101 shown in FIGS. 12 to 14 mainly includes a second flywheel 102, a clutch cover assembly 103, a clutch disc assembly 104, and a damper mechanism 109. An engine (not shown) is arranged on the left side of FIGS. 13 and 14, and a transmission (not shown) is arranged on the right side. The modular clutch 101 is a device for transmitting or interrupting torque from an engine crankshaft 105 to a main drive shaft 106 extending from the transmission side. In FIGS. 13 and 14, OO is the rotation axis of the modular clutch 101.

At the tip of the crankshaft 105, a flexible plate 107 and an inertia member 117 (first flywheel) are provided. The flexible plate 107 is a disk-shaped plate member, and a disk-shaped plate member 114 is fixed to the inner peripheral portion by rivets 115. The inner peripheral portion of the flexible plate 107 is fixed to the engine-side crankshaft 105 by bolts 112 together with the plate member 104. At a radially intermediate portion of the flexible plate 107, a plurality of round holes 107a are formed at equal intervals in a circumferential direction. The flexible plate 107 has high rigidity in the circumferential direction, but can bend in the bending direction.

An inertia member 117 is fixed to an outer peripheral end of the flexible plate 107 by a rivet 116. The inertia member 117 is a cylindrical member that extends long in the axial direction. The ring gear 113 is fixed to the inertia member 117. In the inertia member 117, operation holes 117a communicating the inner peripheral side and the outer peripheral side are formed at three places at equal intervals in the circumferential direction.

As described above, the flexible plate 107 and the inertia member 11 are previously provided on the crankshaft 105 side.
7, and a modular clutch 111 is attached thereto. Next, each structure of the modular clutch 101 will be described. Damper mechanism 109
Is mainly composed of a first input plate 141, a second input plate 142, a vibration damping spring 21, and a driven member 143. The first input plate 141 is a disk-shaped plate member arranged on the side of the flexible plate 107. The outer peripheral portion of the first input plate 141 is in contact with the inner peripheral surface of the inertia member 117. Further, a radially intermediate portion of the first input plate 141 is a convex portion protruding toward the transmission. The second input plate 142 is a disk-shaped plate member arranged on the side of the first input plate 141. Second input plate 142
Is in contact with the inner peripheral surface of the inertia member 4.
The outer peripheral portion of the second input plate 142 and the outer peripheral portion of the first input plate 141 are in contact with each other and are fixed to each other by rivets 148. The inner peripheral portion of the first input plate 141 extends further inward than the inner periphery of the second input plate 142. The inner peripheral portion of the first input plate 141 has an inner peripheral protruding portion 1 that protrudes in a tubular shape toward the engine.
41b.

Further, the first and second input plates 14
The outer peripheral portions of 1,142 are arranged in three places at equal intervals in the circumferential direction.
Each of the bolts 111 is fixed to the inertia member 4. Bolt 111 is fixed from the transmission side. A groove 117b is formed in the inertia member 117 at a portion corresponding to each bolt 111.
An annular space formed by the first input plate 141 and the second input plate 142 is a spring accommodating chamber 120. A pair of vibration damping springs 21 are arranged in the spring housing chamber 120.

The vibration damping spring 21 arranged in the spring accommodating chamber 120 will be described. This vibration damping spring 21
The damper mechanism 109 is a damper that transmits torque and attenuates torsional vibration caused by engine torque fluctuation. As shown in FIG. 15, the vibration damping spring 21 is a spring accommodating chamber 12 in a state where the entire vibration damping spring 11 used in the seventh embodiment is curved in an arc shape.
It is arranged in 0. The vibration damping spring 21 includes a leaf spring 22 extending in a circumferential direction, and a plurality of elastic members 23 provided on the leaf spring 22. The leaf spring 22 is made of metal, and is specifically made of spring steel. The leaf spring 22 extends about 180 degrees in the circumferential direction. The leaf springs 22 are alternately bent, as shown in FIGS.
It comprises a plurality of radially outer bent portions 24, a plurality of radially inner bent portions 26, and a plurality of lever portions 25 connecting both ends of the bent portions 24, 26. Leaf spring 22
Has a constant width W and thickness T throughout. The diameter of the radially outer bend 24 is greater than the diameter of the radially inner bend 26. In addition, a pair of lever portions 25 extending from the individual bent portions 24 or 26
, Linearly extend from the opposite ends to the opposite bent portion 24 or 26 side, and are inclined so as to gradually approach each other as approaching the opposite bent portion 24 or 26 side.

The plurality of elastic members 23 are arranged inside the radially outer bent portion 24, that is, between each pair of lever portions 25 extending from both ends of the radially outer bent portion 24.
The elastic body 23 is made of rubber, for example, and is molded on the inner surface of the leaf spring 22 on the bent portion 24 side. Elastic body 23
Extend in the radial direction along the lever portions 25 on both sides. As shown in FIG. 16, the elastic body 23
The portion on the side is referred to as a contact portion 23a, and the portion extending in the direction in which the lever portion 25 extends from the contact portion 23a is referred to as a protrusion 23b. The contact portion 23a has a shape along the bent portion 24, and is molded on the inner surface of the bent portion 24 and the bent portion 24 side of the lever portion 25. The protrusion 23b is a pair of levers 2
5 has a gap. The length of the protrusion 23b in the gap G direction gradually decreases toward the tip, and the gap between the protrusion 23b and the lever 25 gradually increases. As shown in FIG. 18, the elastic body 23 has a shorter length in the width W direction than the leaf spring 2, and is disposed at the middle of the leaf spring 2 in the width W direction. The length in the longitudinal direction (radial direction) of the lever portion 25 of the leaf spring 22 is represented by L
And

At both ends in the circumferential direction of the vibration damping spring 21, a lever portion 25A extends from the radially outer bent portion 24A to the middle in the radial direction. Length of elastic body 23A
Is arranged. Note that the lever portions at both ends in the circumferential direction may be extended to the inside in the radial direction, and the radial dimension of the elastic body at both ends in the circumferential direction may be increased like the other elastic bodies.

The driven member 143 is a disk-shaped member, and has a pair of engagement portions 143a extending radially outward integrally from the disk portion. The engaging portions 143a extend into the spring accommodating chamber 120 at two locations facing each other in the radial direction, and abut on the circumferential ends of the pair of vibration damping springs 21, respectively. Also, the first and second input plates 14
Reference numerals 1 and 142 have support portions 141a and 142a that protrude in the axial direction at two locations facing each other in the radial direction and abut against both circumferential ends of the vibration damping spring 21.

The second flywheel 102 has a flat friction surface 102a on the transmission side on the outer periphery. The second flywheel 102 has a friction surface 10.
A communication hole 102j communicating between both surfaces is formed on the inner peripheral side of 2a. A driven member 143 is fixed to an inner peripheral end of the flywheel 102 by a rivet 160. The inner periphery of the second flywheel 102 and the driven member 143 is connected to the first input plate 141 via a bearing 161.
Are supported by the inner peripheral projection 141b. On the outer peripheral surface of the flywheel 102, engaging portions 102k are formed at three locations at equal intervals in the circumferential direction. The engaging portion 102k protrudes radially outward. The engine-side end of the engagement portion 102k is inclined so as to be deeper toward the inside in the radial direction.

The clutch cover assembly 103 mainly includes a clutch cover 121, a pressure plate 122, a diaphragm spring 123, a connection plate 128, a stud pin 126, two wiring rings 127, and a cone spring 129. The clutch cover 121 is a plate-shaped plate member having a large-diameter hole formed in the center, and has an outer peripheral portion provided at regular intervals in the circumferential direction.
An extension 162 having a predetermined width and extending toward the flywheel 102 is formed at a certain location. A bent portion 163 that is bent inward is formed at the tip of each extension portion 162. The bent portion 163 is the second flywheel 1
02 is engaged with the engaging portion 102k. Thus, the clutch cover 121 cannot move toward the transmission with respect to the flywheel 102. A notch extending in the circumferential direction is formed at the tip of the extension 162, and a plate 164 that also extends in the circumferential direction is engaged with this notch. Plate 164 is bolt 1
65, the outer peripheral surface 102b of the second flywheel 102
It is fixed to. Thus, the clutch cover 1
Numeral 21 cannot rotate relative to the flywheel 102. Also, by eliminating the bolt mounting seat of the flywheel 102 in this way, the flywheel 10
2 is reduced in size in the radial direction.

The pressure plate 122 is an annular member disposed inside the clutch cover 121. The pressure plate 122 has a pressing surface 122 a facing the friction surface 102 a of the flywheel 102.
Further, the pressing surface 122 of the pressure plate 122
An annular protruding portion 122b protruding toward the transmission is formed on a surface opposite to the side a. Further, the pressure plate 122 is formed with a flange portion 122c extending radially inward.

The diaphragm spring 123 is a disk-shaped member, and is disposed between the bottom of the clutch cover 121 and the pressure plate 122. The diaphragm spring 123 includes an annular elastic portion 123a and a plurality of lever portions 123b extending inward therefrom. A first hole 123c is formed on the outer peripheral side between the plurality of lever portions 123b. In each slit, second holes 123d are formed in three places at equal intervals in the circumferential direction. The second hole 123d extends longer inward in the radial direction than the first hole 123c, and extends to near the flange portion 122c of the pressure plate 122. Annular elastic part 1
Reference numeral 23a denotes a wiring 127 on both sides of the inner peripheral end to be described later.
And the outer peripheral part is a pressure plate 1
22 is in contact with the annular protrusion 122b. In this state, the elastic portion 123a urges the pressure plate 121 toward the flywheel 102.

The support structure 125 for supporting the diaphragm spring 123 will be described. The plurality of stud pins 126 fixed to the inner peripheral end of the bottom of the clutch cover 121 are provided in the first hole 12 of the diaphragm spring 123.
3c and extends to the pressure plate 122 side. The other end of each stud pin 126 has a connecting plate 1
28 (described later) is fixed. Each stud pin 126
On the outer peripheral side, wirings 127 are arranged between a connection plate 128 (described later) and the diaphragm spring 123 and between the diaphragm spring 123 and the bottom of the clutch cover 121, respectively. That is, the inner peripheral portion of the elastic portion 123a of the diaphragm spring 123 is sandwiched between the pair of wirings 127.

The connecting plate 128 is an annular plate member
And the inner peripheral portion thereof has a circumferential direction R. ₁Arc on the side (Fig. 12)
Three connecting portions 128a extending in a long shape are integrally formed.
ing. The tip of the connecting portion 128a is
c, the flange portion 122 of the pressure plate 122
c. The position of the rivet 122c is diamond
Corresponds to the second hole 123d of the flam spring 123.
You. The connecting portion 128a has high rigidity in the circumferential direction and flexes in the axial direction.
Only possible. The connection part 128a is a pressure pre
Direction of moving the seat 122 away from the second flywheel 102
It is energizing.

The cone spring 129 is arranged on the outer periphery of the connecting plate 128. Cone spring 1
The inner peripheral end of 29 is supported by the connection plate 128, and the outer peripheral end urges the outer peripheral end of the diaphragm spring 123, that is, the portion close to the annular projection 122 b of the pressure plate 122 in the direction away from the pressure plate 122.

As described above, the connection plate 128
Connects the clutch cover 121 and the pressure plate 122 and supports the cone spring 129. As described above, the connection plate 128 is provided with a plurality of functions to reduce the number of components. The plurality of locking members 164 are fixed to the pressure plate 122 by fixing pins 165, and one end thereof is connected to the diaphragm spring 12.
3 is sandwiched between the outer peripheral end of the pressure plate 122 and the annular projection 122b. This locking member 1
A hole 121c is formed at the position of the extension 162 corresponding to the hole 64.

The clutch disk assembly 104 includes the clutch connecting portion 131, the hub 134, and the plate 166.
It is mainly composed of The clutch connecting portion 131 is disposed between the friction surface 102a of the flywheel 102 and the pressing surface 122a of the pressure plate 122.
The hub 134 is connected to the main drive shaft 1 on the engine side.
06 is in spline engagement. The plate 166 has an inner peripheral portion fixed to the flange of the hub 134 by rivets 119 and an outer peripheral portion fixed to the clutch connecting portion 131 by rivets 118. A plurality of holes 166a are formed in the plate 166 at equal intervals in the circumferential direction.

The main drive shaft 106 extending from the transmission side has a tip end of the crankshaft 10.
5 is supported via a bearing 169. The release device 108 is arranged movably in the axial direction around the main drive shaft 106. One end of the release device 108 has a lever portion 123 of the diaphragm spring 123.
b Engage with the side surface on the tip transmission side. When the release device 108 moves to the engine side,
When 3b is moved to the engine side, the urging force from the elastic portion 123a to the pressure plate 122 is released.

Although the bolt 200 is shown in FIG. 13, the bolt 200 is not used when the modular clutch 101 is used. The bolt 200 is used when assembling or disassembling the clutch cover assembly 103 to the flywheel 102. Multiple bolts 200
Is screwed into the pressure plate 122 through a hole formed on the inner peripheral side of the bottom of the clutch cover 121, further through the first hole 123 c of the diaphragm spring 123, further through the connecting plate 128. [Operation] Next, the operation of the modular clutch 101 will be described.

When the crankshaft 105 on the engine side rotates, torque is transmitted to the modular clutch 101 via the flexible plate 107. Then, the torque is applied to the flywheel 10 via the damper mechanism 109.
2 and output to the clutch disk assembly 104. The pressure plate 122 rotates integrally with the clutch cover 121 via the connection plate 128. As described above, the rotational drive of the pressure plate 122 is performed by the inner peripheral portion of the pressure plate 122 and the clutch cover 1.
Since the connection is performed by the connecting plate 128 connecting the inner peripheral portion of the clutch cover 121 to the inner peripheral portion of the clutch cover 121, there is no need to provide a notch for accommodating the strap plate on the outer peripheral portion of the clutch cover 121 as in the related art.

Since the inertia member 117 is fixed to the first and second input plates 141 and 142, the inertia moment of the input system in the power input / output system divided into the input system and the output system via the curved leaf spring 146 is reduced. We can secure enough. As a result, the resonance frequency can be set to be equal to or lower than the practical rotation speed region of the engine. Since the inertia member 117 is arranged on the outer peripheral portion, the first and second input plates 141 and 142, which are members constituting the spring housing chamber 120, can be made thin in the axial direction. As a result, the modular clutch 10
1 is reduced in size in the axial direction. Further, since the inertia member 117 extends long in the axial direction, the whole does not increase in size in the radial direction. Even if the inertia member 117 is provided on the outer peripheral portion of the damper mechanism 109 as described above, the entire apparatus does not increase in size in the radial direction.
Abolition of the clutch mounting seat from the
Can be arranged more inward in the radial direction.

When bending vibration is transmitted from the crankshaft 105, the flexible plate 107 bends in the bending direction to absorb the vibration. When the torsional vibration is transmitted from the engine side, in the damper mechanism 109,
The first and second input plates 141 and 142 and the driven member 143 perform a periodic relative rotation. At this time, the vibration damping spring 21 is compressed in the circumferential direction. Here, the vibration damping spring 21 is considered to have a pair of lever portions 25, a bent portion 24, and a spring element composed of the elastic body 23 arranged in series in the circumferential direction. Stiffness characteristics are obtained.

Vibration damping spring 2 during transmission of torsional vibration
The operation 1 will be described in detail. When the small torsional vibration caused by the torque fluctuation of the engine is transmitted, the vibration damping spring 21 changes alternately between the state of FIG. 16 and the state of FIG. The vibration damping spring 21 is moved from the state of FIG.
When shifting to the state of No. 9, the radially inner bent portion 26 is mainly elastically deformed, and low rigidity is obtained. In FIG. 19,
The radially inner bent portion 26 side portion of the lever portion 25 abuts on the protrusion 23 b of the elastic body 23, but the entire lever portion 25 does not strongly pinch the elastic body 23. Therefore, large internal friction does not occur in the elastic body 23. In this manner, the characteristics of low rigidity and small resistance make it difficult for the small torsional vibration to be transmitted to the flywheel 102 side.

If an excessive torque fluctuation occurs in the damper mechanism 109 when passing through the resonance point in the low rotational speed region, the displacement angle of the vibration damping spring 21 increases, and the lever 25
Of the elastic body 23, the amount of elastic deformation of the elastic body 23 increases, and large internal friction occurs. Excessive torque fluctuation is attenuated by the large friction generated at this time. More specifically, the vibration damping spring 21 shifts from the state of FIG. 16 to the state of FIG. 20 via the state of FIG. FIG.
In the transition from the state shown in FIG. 9 to the state shown in FIG.
Is elastically deformed by being strongly sandwiched between the lever portions 25 on both sides. At this time, large internal friction is generated in the elastic body 23. Due to the characteristics of high rigidity and large internal friction at this time, excessive vibration is attenuated. In the state where the displacement angle shown in FIG. 20 is the maximum, the bent portions 24 of the leaf spring 22 abut against each other in the circumferential direction. In this state, the elastic bodies 25 abut in series in the circumferential direction to prevent elastic deformation of the bent leaf spring 21 beyond a predetermined angle. That is, the elastic body 25 functions as a stopper of the damper mechanism 109.

When the driver steps on the clutch pedal, one end of the release device 108 moves the lever portion 123b of the diaphragm spring 123 toward the engine. As a result, the outer peripheral end of the elastic portion 123a is
22 is separated from the annular projection 122b. Then, the pressure plate 122 is separated from the clutch connecting portion 131 of the clutch disc assembly 104 by the urging force of the connecting portion 128a of the connecting plate 128. As a result, transmission of torque from the second flywheel 102 to the clutch disk assembly 104 is interrupted. During the release operation described above, since the cone spring 129 applies a load to the transmission side to the diaphragm spring 123, the release load is reduced and becomes flat, and the pedal depression force is reduced. [Advantageous Effect] Since the vibration damping spring 21 realizes both the elastic member and the friction generating mechanism only by the combination of the leaf spring 22 and the elastic body 23, it has a high function with a compact structure. As a result, the size of the damper mechanism 109 can be reduced. In addition, since the leaf spring 22 has a shape obtained by bending a plate, the vibration damping spring 21 has a larger shape than a conventional coil spring.
Can be reduced in width W dimension. As a result, the damper mechanism 10
9 and the entire axial dimension of the modular clutch 101 can be reduced.

Further, in this embodiment, a bent portion where the elastic body is disposed and a bent portion where the elastic body is not disposed are provided so that the high-rigidity portion and the low-rigidity portion act in series. Specifically, the radially outer bent portion 24 is a high rigidity portion, and the radially inner bent portion 26 is a low rigidity portion. As a result, in the range where the torsion angle is small in the damper mechanism 109, the radially inner bent portion 2 is formed.
6 and a large resistance due to the elastic body 23 in the radially outer bent portion 24 in a large range of the torsion angle.

The vibration damping spring 21 can obtain the same vibration damping characteristics as the conventional one simply by combining a plurality of elastic members 23 with the leaf spring 22, so that it is not necessary to use a viscous resistance. As a result, the spring mechanism 120 does not need a sealing mechanism,
The damper mechanism 109 is greatly simplified. [Modification] The vibration damping spring 21 may be one that extends in an arc shape in a free state.

In all the embodiments, it is assumed that the rigidity of the elastic body is made of the same material unless otherwise specified. However, in a vibration damping spring in which a plurality of elastic bodies are arranged as in this embodiment, elastic bodies made of different materials and having different rigidities may be arranged. Ninth Embodiment A vibration damping spring 21 shown in FIG. 21 has the same structure as the vibration damping spring 21 of the eighth embodiment. Here, only different points will be described. Elastic body 23 of vibration damping spring 21
Is less than half or less than half the radial length L of the leaf spring 22. This vibration damping spring 21
Is less rigid than the vibration damping spring 21 of the eighth embodiment. Other effects are the same as those of the eighth embodiment. Tenth Embodiment In one vibration damping spring 21, elastic bodies having different shapes and sizes may be arranged. Thereby, the rigidity of each part in the vibration damping spring 21 can be made different.

In the vibration damping spring 21 shown in FIG. 22, a plurality of first radially long
An elastic body 23a is arranged, and a plurality of second elastic bodies 23b which are short in the radial direction are arranged on both circumferential sides of the leaf spring 22. With such a structure, the vibration damping spring 21 has lower rigidity at both ends in the circumferential direction than the central portion, and has lower rigidity as a whole than the eighth embodiment.

As described above, by disposing the elastic members having different shapes, the portions having different rigidities are arranged in series over the entire spring. As a result, a region of low rigidity and high rigidity can be obtained in the bending characteristic. The operation of the vibration damping spring 21 during the transmission of torsional vibration will be described. When small torsional vibration caused by engine torque fluctuation is transmitted,
The vibration damping spring 21 mainly has elastically deformed portions on both sides in the circumferential direction, and low rigidity can be obtained. In this way, due to the characteristics of low rigidity and small resistance, small torsional vibrations
It is difficult to be transmitted to the 02 side.

If an excessive torque fluctuation occurs in the damper mechanism 109 when passing through the resonance point in the low rotational speed region, the displacement angle of the vibration damping spring 21 increases, and the lever 25
Of the elastic body 2 at the center in the circumferential direction
3, the amount of elastic deformation increases, and a large internal friction occurs. Excessive torque fluctuation is attenuated by the large friction generated at this time. Eleventh Embodiment In the vibration damping spring 21 shown in FIG. 23, the elastic bodies 23 are arranged every other in the circumferential direction with respect to each radially outer bent portion 24. As described above, the vibration damping spring 21 has lower rigidity than that of the eighth embodiment due to the radially outer bent portion 24 where the elastic body 23 is not disposed.

As described above, by arranging every other elastic member at one bent portion, the rigidity at the bent portion where no elastic member is disposed can be reduced. The operation of the vibration damping spring 21 during the transmission of torsional vibration will be described.
When the small torsional vibration caused by the torque fluctuation of the engine is transmitted, the vibration damping spring 21 mainly includes the radially inner bent portion 26 and the radially outer bent portion 24 where the elastic body 23 is not disposed. Is elastically deformed, and low rigidity is obtained. In this manner, the characteristics of low rigidity and small resistance make it difficult for the small torsional vibration to be transmitted to the flywheel 102 side.

When passing through the resonance point in the low rotational speed region, the damper
When excessive torque fluctuation occurs in the mechanism 109, the vibration damping spring
21, the displacement angle of the lever 21 increases,
And the elastic deformation amount of the elastic body 23 increases.
Large and large internal friction occurs. Occurs at this time
Excessive torque fluctuation is attenuated by the large friction. Twelfth embodiment In the vibration damping spring 21 shown in FIG.
Resilient in the radially outer bends 24 at the center in the direction
The body 23 is disposed, and a plurality of
The elastic body 23 is disposed in the radially outer bent portion 24.
Not in. With such a structure, the vibration damping spring 21
The rigidity at both ends in the circumferential direction is lower than that at the center.
The rigidity of the body is lower than that of the eighth embodiment.

As described above, by disposing no elastic body in a certain area, a low-rigidity portion can be formed. As a result, a region of low rigidity and high rigidity can be obtained in the bending characteristic. The operation of the vibration damping spring 21 during the transmission of torsional vibration will be described. When the small torsional vibration caused by the torque fluctuation of the engine is transmitted, the vibration damping spring 21 is elastically deformed mainly on both sides in the circumferential direction, and low rigidity is obtained. In this manner, the characteristics of low rigidity and small resistance make it difficult for the small torsional vibration to be transmitted to the flywheel 102 side.

If an excessive torque fluctuation occurs in the damper mechanism 109 when passing through the resonance point in the low rotation speed region, the displacement angle of the vibration damping spring 21 increases, and the lever 25
Of the elastic body 2 at the center in the circumferential direction
3, the amount of elastic deformation increases, and a large internal friction occurs. Excessive torque fluctuation is attenuated by the large friction generated at this time. Thirteenth Embodiment In a vibration damping spring 21 shown in FIG. 25, an outer elastic body 23 arranged inside a radially outer bent portion 24 and an inner elastic body 26 arranged inside a radially inner bent portion 26 are provided. ing. The outer elastic body 23 has a longer radial length and a longer circumferential length than the inner elastic body 28. The size and shape of the outer elastic body 23 and the inner elastic body 28 are not limited to this embodiment. Fourteenth Embodiment In a vibration damping spring 21 shown in FIG. 26, similarly to the thirteenth embodiment, an outer elastic body 23 disposed inside a radially outer bent portion 24 and a radially inner bent portion 26 are disposed. An inner elastic body 28 is provided. Outer elastic body 23
Is the longest in the radial direction at the middle part in the circumferential direction, and becomes gradually shorter toward both sides in the circumferential direction. The inner elastic body 28 at the intermediate portion in the circumferential direction is the longest in the radial direction, and becomes shorter gradually toward both sides in the circumferential direction. As a result, the outer elastic body 23 and the inner elastic body 28 largely overlap in the radial direction at the middle part in the circumferential direction, and the overlap in the radial direction becomes smaller toward both sides in the circumferential direction, and eventually the overlap disappears. The spacing in the direction is increasing.

As described above, the rigidity of each part can be changed by changing the shape of the elastic body depending on the arrangement position. In the vibration damping spring 21, the rigidity on both sides in the circumferential direction is the lowest, and gradually increases toward the center in the circumferential direction. The operation of the vibration damping spring 21 during the transmission of torsional vibration will be described in detail. When the small torsional vibration caused by the torque fluctuation of the engine is transmitted, the vibration damping spring 21 is elastically deformed mainly on both sides in the circumferential direction.
Low rigidity can be obtained. In this manner, the characteristics of low rigidity and small resistance make it difficult for the small torsional vibration to be transmitted to the flywheel 102 side.

If an excessive torque fluctuation occurs in the damper mechanism 109 during the passage of the resonance point in the low rotation speed region, the displacement angle of the vibration damping spring 21 increases, and the lever 25
Of the elastic body 2 at the center in the circumferential direction
3, the amount of elastic deformation increases, and a large internal friction occurs. Excessive torque fluctuation is attenuated by the large friction generated at this time. Fifteenth Embodiment In a vibration damping spring 21 shown in FIG. 27, a plurality of elastic bodies 30 extending in the radial direction are arranged between the lever portions 25 on both sides in the circumferential direction. The elastic body 30 is molded on each lever 25. Both ends in the radial direction of the elastic body 30 are separated from both bent portions 24 and 26. In this vibration damping spring 21, the rigidity on both sides in the circumferential direction increases,
The rigidity at the middle part in the circumferential direction decreases.

As described above, by partially molding the elastic body in the circumferential direction, portions having different rigidities can be formed in series. As a result, a region of low rigidity and high rigidity can be obtained in the bending characteristic. The operation of the vibration damping spring 21 during the transmission of torsional vibration will be described. When the small torsional vibration caused by the torque fluctuation of the engine is transmitted, the vibration damping spring 21 is elastically deformed mainly at the center in the circumferential direction, and low rigidity is obtained. In this way, due to the characteristics of low rigidity and small resistance, small torsional vibrations
It is difficult to be transmitted to the 02 side.

If an excessive torque fluctuation occurs in the damper mechanism 109 when passing through the resonance point in the low rotation speed region, the displacement angle of the vibration damping spring 21 increases, and the lever 25
And the elastic members 23 on both sides in the circumferential direction are increased.
And the amount of elastic deformation increases, causing large internal friction.
Excessive torque fluctuation is attenuated by the large friction generated at this time. Sixteenth Embodiment The sixteenth to nineteenth embodiments described below are application examples in which the vibration damping spring shown in the eighth embodiment (including the ninth to fifteenth embodiments) is used for a damper mechanism of another form.

FIGS. 28 and 29 show a clutch disk assembly 201 according to an embodiment of the present invention. In the figure, OO is a center line. At the center of the clutch disc assembly 201, a spline hub 202 that can be connected to an output shaft (not shown) is arranged. The spline hub 202 has at its center a spline hole 202a that meshes with an outer spline portion of an output shaft (not shown). Further, the spline hub 202 is integrally formed with a flange portion 203 protruding outward. As shown in FIG. 29, two protrusions 203a are formed on the outer periphery of the flange 203 at positions facing each other in the radial direction. A plurality of elongated holes 203b penetrating in the axial direction and extending in the circumferential direction are formed in the flange portion 203 at predetermined intervals.

On the outer peripheral side of the spline hub 202, substantially disk-shaped side plates 204 and 205 made of sheet metal are arranged. The side plates 204 and 205 are arranged at predetermined intervals in the axial direction, and the inner peripheral portion thereof has a flange portion 203.
Are located on both sides. Side plates 204, 20
5 are fixed to each other by a plurality of stop pins 6. The stop pin 206 is connected to the flange 203
Is inserted into the long hole 203b.

A bent portion 205a bent toward the side plate 204 is formed on the outer peripheral portion of the side plate 205. The bent portion 205a is
9 (friction plate) and a rivet 208 fixed to the outer peripheral portion of the side plate 204. In addition, bending part 2
In FIG. 05a, locking portions 205b formed so as to be depressed inward by drawing are formed at two locations opposed to each other in the radial direction so as to correspond to the projections 203a of the flange portion 203.

With such a configuration, the spline hub 1
The side plates 204 and 205 arranged on both side surfaces of the spring member form an annular spring accommodating chamber 210 whose outer peripheral portion is closed. The annular spring accommodating chamber 210 includes a projection 203a.
And the locking portion 205b divides it into two semicircular arc-shaped chambers. A vibration damping spring 2 is provided in each arc-shaped chamber.
21 are arranged. The structure and effects of the vibration damping spring 221 are the same as those of the vibration damping spring 21 of the eighth embodiment, and a description thereof will be omitted. In addition, the vibration damping springs disclosed in the ninth to fifteenth embodiments are combined with the clutch disc assembly 2
01 may be used. Seventeenth Embodiment FIG. 30 shows a damper device 3 as one embodiment of the present invention.
01 is shown. The damper device 1 is a device for transmitting torque from a crankshaft 390 on the engine side to a main drive shaft 391 of the transmission. In FIG. 1, an engine (not shown) is arranged on the left side of the figure, and a transmission (not shown) is arranged on the right side of the figure. Furthermore, O- in FIG.
The O line is the rotation axis of the damper device 301.

The damper device 301 mainly includes a flexible plate 302, a ring member 308 fixed to the flexible plate 302, a hub flange 303,
And a damper 304. The flexible plate 302 is a substantially disk-shaped member, can bend in the bending direction, and has high rigidity in the rotation direction. The flexible plate 302 has a center hole 302a at the center. Further, the flexible plate 302 has a plurality of round holes 302b formed at an intermediate portion in the radial direction at equal intervals in the circumferential direction. A plurality of bolt holes 302c are formed at equal intervals in the circumferential direction on the inner peripheral side of the round hole 302b. The bolt 306 penetrating through the bolt hole 302c causes the inner peripheral end of the flexible plate 302 to
0. Further, a plurality of arc-shaped inertia members 307 are fixed to the outer peripheral portion of the flexible plate 302 on the engine side by rivets 351. The inertia member 307 allows the damper device 3
01 is increased. Further, since the inertia member 307 has a shape obtained by dividing the annular member in the circumferential direction, the bending of the flexible plate 302 in the bending direction is guaranteed. The outer peripheral end of the flexible plate 302 is fixed to the ring member 308 via a disk plate 309 by a plurality of bolts 310. The inertia member 307 has a notch corresponding to the bolt 310.

The hub flange 303 has a boss 303a,
Flange 303b integrally formed on the outer periphery of boss 303a
Consists of A spline hole 303c is formed at the center of the boss 303a to engage with spline teeth of the main drive shaft 391 extending from the transmission side. The damper 304 mainly includes the first input side plate 3
13, a second input side plate 314, a driven plate 319, and a pair of vibration damping springs 321.

The first input side plate 313 and the second input side plate 314 are disk-shaped sheet metal members. The inner peripheral end of the first input side plate 313 extends further radially inward than the inner peripheral end of the second input side plate 314. The second input side plate 314 has a cylindrical wall 314 a on the outer peripheral portion, which extends toward the engine and is fixed to the outer peripheral end of the first input side plate 313. Also, this cylindrical wall 314a
Are welded to the inner periphery of the ring member 308. Also,
In the cylindrical wall 314a, two engaging portions 31 which are formed so as to be depressed inward by drawing are provided at two locations facing each other in the radial direction.
4b is formed. Thus, the first and second
The input side plates 313 and 314 rotate integrally with the ring member 308. That is, the plates 313 and 314 function as a part of the input side member. The first input side plate 313 and the second input side plate 314 form an annular spring housing chamber 320 whose outer peripheral portion is closed. First
In addition, since the second input side plates 313 and 314 are made of sheet metal disk plates, the axial dimension of the damper 304 is short. Since the ring member 308 is fixed to the outer peripheral portions of the plates 313 and 314, a sufficient moment of inertia of the input side member is secured without increasing the axial dimension of the damper 304.

The driven plate 319 is a disk-shaped member, and the inner peripheral end is connected to the flange 303 b of the hub flange 303 by a plurality of rivets 323. In this way, the driven plate 319 is connected to the hub flange 3.
03 and rotate together. That is, the driven plate 31
9 functions as a flange of the hub flange 303, that is, as a part of the output side member. Driven plate 31
9, two support portions 319a projecting outward in the radial direction are formed at two positions facing each other in the radial direction.

In the annular spring accommodating chamber 320, the locking portion 314a of the second input side plate 314 and the driven plate 3
It is divided into a pair of arc-shaped chambers by the 19 support portions 319a. A vibration damping spring 321 is provided in each arc-shaped chamber.
Is arranged. The structure and effects of the vibration damping spring 321 are the same as those of the vibration damping spring 21 of the eighth embodiment, and a description thereof will be omitted.

The center hole at the inner peripheral end of the first input side plate 313 is fitted to the boss 315 and fixed by welding.
The engine-side outer peripheral surface 315 a of the boss 315 is fitted in the center hole 302 a of the flexible plate 302. A bearing 317 is disposed between the transmission-side outer peripheral surface of the boss 315 and the inner peripheral portion of the boss 303a of the hub flange 303. The bearing 317 supports the boss 315 and the hub flange 303 so as to be relatively rotatable. Bearing 31
The inner ring 7 is fixed to a groove of the boss 315. Bearing 3
The outer ring 17 is fixed to the inner periphery of the boss 303a.
As described above, the boss 315 is connected to the flexible plate 302.
And the bearing 317 is positioned. As a result, the concentricity of the flexible plate 302, the boss 315, and the bearing 317 is improved.

The hub flange 303 is connected to a main drive shaft 391 of the transmission. Therefore, the hub flange 303 is hardly displaced, and the bearing 317
Extremely large force does not act on Furthermore, since the flexible plate 302 absorbs bending vibration, the bearing 317
The bending load acting on is reduced. Therefore, the diameter can be reduced so that the bearing 317 can be arranged inside the pitch circle of the crank bolt 306. Without the use of a flexible plate, it is difficult to reduce the size of the bearing. Even if the size can be reduced, a specially strong bearing must be used, which is expensive.

An inertia member 342 (inertia) is provided on the transmission side of the flange 303b of the hub flange 303. The inertia member 342 is a disk-shaped member that covers the transmission side of the second input side plate 314, and the inner peripheral end is fixed to the flange 303b and the driven plate 319 by rivets 323. Further, since the inertia member 342 has a disk shape, the entire damper device 301 is compact in the axial direction. The provision of the inertia member 342 increases the moment of inertia of the output-side mechanism. Further, an engine start ring gear 311 is welded to the outer periphery of the inertia member 342. Inertia member 3
Since 42 is a disk-shaped member, the ring gear 311 is easily fixed. Therefore, the cost is reduced. The ring gear 311 is a member conventionally welded to the outer periphery of the ring member 308, but by moving from the input side mechanism to the output side mechanism as in this embodiment, the moment of inertia of the output side mechanism can be easily increased. . When the moment of inertia of the output mechanism increases, the resonance frequency of the drive system including the damper device 301 can be reduced to be equal to or lower than the idling speed (practical speed) of the vehicle. Conventional ring gear 3
By using 11, the cost is reduced.

The vibration damping springs disclosed in the ninth to fifteenth embodiments may be used for the damper device 301. Eighteenth Embodiment FIG. 31 shows a damper device 4 as one embodiment of the present invention.
01 is shown. The damper device 101 is a device that transmits torque from the crankshaft 490 on the engine side to the main drive shaft 491 of the transmission and attenuates torsional vibration. 31, an engine (not shown) is arranged on the left side of the figure, and a transmission (not shown) is arranged on the right side of the figure.
1 is the rotation axis.

The damper device 401 mainly includes a flexible plate 402, a ring member 408 fixed to the flexible plate 402, a hub flange 403,
And a damper 404. The flexible plate 402 is a substantially disk-shaped member, can be bent in a bending direction, and has high rigidity in a circumferential direction. The flexible plate 402 has a center hole 402a at the center. Further, the flexible plate 402 has a plurality of window holes 402b formed at an intermediate portion in the radial direction at equal intervals in the circumferential direction. A plurality of bolt holes 402c are formed on the inner peripheral side of the window hole 402b at equal intervals in the circumferential direction. The inner peripheral end of the flexible plate 402 is fixed to the tip of the crankshaft 490 by the crank bolt 406 penetrating through the bolt hole 402c. Further, a plurality of arc-shaped inertia members 407 are fixed to the outer peripheral portion of the flexible plate 402 on the engine side by rivets 451. The inertia member 407 increases the moment of inertia of the damper device 401. Also,
Since the inertia member 407 has a shape obtained by dividing the annular member in the circumferential direction, the bending of the flexible plate 402 in the bending direction is guaranteed. Flexible plate 40
The outer peripheral end of 2 is fixed to a ring member 408 by a plurality of bolts 410 via a disk-shaped plate 409 therebetween. The inertia member 407 has a notch corresponding to the bolt 410.

The hub flange 403 includes a boss 403a,
Flange 403b integrally formed on the outer periphery of boss 403a
Consists of The boss 403a protrudes toward the engine, and has a spline hole 403c formed at the center thereof to engage with spline teeth of a main drive shaft 391 extending from the transmission side. A cap-shaped member 141 for closing the center hole is fixed to the engine side of the center hole of the boss 403a.

The damper 404 mainly includes a first input side plate 413, a second input side plate 414, a driven plate 419, and a vibration damping spring 221. First input side plate 413 and second input side plate 4
14 is a disk-shaped sheet metal member. The first input side plate 413 includes a disk portion 413a and a hollow cap 413b protruding from the center of the disk portion 413a toward the engine. The hollow cap 413 is integrally formed by drawing from the center of the disk portion 413a. A center hole 413c is formed in the center of the hollow cap 413b. The second input side plate 414 has a cylindrical wall 414 a that extends toward the engine at an outer peripheral portion and is fixed to the outer peripheral end of the first input side plate 413. The cylindrical wall 414a is welded to the inner periphery of the ring member 408. Thus, the first and second input side plates 4
13, 414 rotate integrally with the ring member 408. That is, the plates 413 and 414 function as input-side members. In the cylindrical wall 414a, locking portions 314b formed so as to be recessed inward by drawing are formed at two locations facing each other in the radial direction.

As described above, the first input side plate 413 and the second input side plate 414 form an annular spring accommodating chamber 420 whose outer peripheral portion is closed. Since the first and second input side plates 413 and 414 are formed of sheet metal disc plates, the axial dimension of the damper 404 is short. Ring members 408 are plates 413 and 41
4, the inertia moment of the input side member is sufficiently ensured without increasing the axial dimension of the damper 404.

The driven play 419 is a disc-shaped member, and has an inner peripheral end connected to the flange 403b of the hub flange 403 by a plurality of rivets 423. In this way, the driven plate 419 is connected to the hub flange 403.
And rotate together. That is, the driven plate 419 is
It functions as a flange of the hub flange 403, that is, as a part of the output side member. The driven plate 419 is provided with support portions 419a extending radially outward at two locations facing each other in the radial direction.

The inside of the annular spring accommodating chamber 420 includes the locking portion 414 a of the second input side plate 414 and the driven plate 4.
The 19 support portions 419a divide the chamber into a pair of arc-shaped chambers. A vibration damping spring 421 is provided in each arc-shaped chamber.
Is arranged. The structure and effects of the vibration damping spring 421 are the same as those of the vibration damping spring 21 of the eighth embodiment, and thus description thereof is omitted.

The hollow cap 413 b of the first input side plate 413 is connected to the center hole 40 of the flexible plate 402.
2a. That is, the first input side plate 413 is positioned and centered by the flexible plate 402 (centering portion on the crankshaft side) fixed to the crankshaft 490. The boss 403a of the hub flange 403 is the first input side plate 4
Thirteen hollow caps 413b are arranged. The boss 403a is housed within most of the axial dimension of the damper 404 (the first and second input side plates 413, 414). As a result, the damper device 401 is compact in the axial direction. Inner circumference of disk portion 413a of first input side plate 413 and boss 403a of hub flange 403
A bearing 417 is disposed between the bearing and the outer periphery. Bearing 4
17 is a support member 452 having an annular outer ring and a rivet 45.
3, the outer ring is fixed to the first input side plate 413. Thus, the bearing 417 is securely supported by the first input side plate 413. The boss 403a is inserted inside the inner ring of the bearing 417, and further has a portion that contacts the transmission-side end surface of the inner ring.

In this way, the first input side plate 41
3 is positioned (centered) in the center hole 402 a of the flexible plate 402, and the first input side plate 413 supports the bearing 417. Thereby, the flexible plate 402, the first input side plate 413,
The concentricity of the bearing 417 and the hub flange 403 is improved.

The hub flange 403 is connected to the main drive shaft 402 of the transmission. Therefore, the hub flange 403 is hardly displaced, and the bearing 417
Extremely large force does not act on Further, since the flexible plate 402 absorbs bending vibration, the bearing 417
The bending load acting on is reduced. Therefore, the diameter can be reduced so that the bearing 417 can be arranged inside the pitch circle of the crank bolt 406. Without the use of a flexible plate, it is difficult to reduce the size of the bearing. Even if the size can be reduced, a specially strong bearing must be used, which is expensive.

In this embodiment, the hub flange 40
The third boss 403a is inserted into the hollow cap 413b of the first input side plate 413. As a result, the axial dimension of the entire damper device 401 is reduced. Moreover,
In this structure, the bearing 417 is connected to the first input side plate 41.
3, the bearing 417 can be further miniaturized in the radial direction. This reduces costs.

The first inertia member 442 is provided on the transmission side of the flange 403b of the hub flange 403. The first inertia member 442 is a disk-shaped member that covers the transmission side of the second input side plate 414, and has an inner peripheral end fixed to the flange 403b and the driven plate 119 by rivets 420. A second inertia member 444 is fixed to the transmission side of the first inertia member 442 by a rivet 443. The second inertia member 444 is a disk-shaped member, and is entirely in contact with the first inertia 442 on the transmission side. The first inertia member 442 and the second inertia member 444 increase the moment of inertia of the output side mechanism. Since the first and second inertia members 442 and 444 are disc-shaped, the entire damper device 401 is compact in the axial direction. Further, an outer ring of the first inertia member 442 is welded with a ring gear 411 for starting the engine. The engine starting ring gear 411 is a member that has been conventionally welded to the outer periphery of the ring member 408. However, by moving from the input side mechanism to the output side mechanism as in this embodiment, the moment of inertia of the output side mechanism can be easily determined. The ratio can be increased. When the inertia moment ratio of the output side mechanism increases, it becomes possible to lower the resonance frequency in the drive system including the damper device 401 to be equal to or lower than the idle speed (practical speed) of the vehicle. The cost is reduced by using the conventional engine start ring gear 411.

The vibration damping springs disclosed in the ninth to fifteenth embodiments may be used for the damper device 301. Nineteenth Embodiment FIG. 32 shows a torque converter 501 employing an embodiment of the present invention. In the figure, OO is the rotation axis of the torque converter 501, and an engine (not shown) is arranged on the left side of the figure, and a transmission (not shown) is arranged on the right side of the figure.

The torque converter 501 mainly includes a torque converter body 502 and a lock-up device 503. The front cover 504 connected to an engine-side member (not shown) has a cylindrical projection 504a protruding toward the transmission on an outer peripheral portion, and the projection 504a is formed on the impeller shell 505 of the impeller 505.
a. The front cover 504 forms a hydraulic oil chamber filled with hydraulic oil together with the impeller shell 505a.

[0103] Torque converter main body 502 is mainly composed of impeller 505, turbine 506 driven by the flow of fluid from impeller 505, and stator 507. Impeller shell 505 of impeller 505
As for a, its inner peripheral end is fixed to the impeller hub 505c. A plurality of impeller blades 505b are fixed inside the impeller shell 505a. Impeller 5
The turbine 506 is disposed at a position facing the turbine 05. The turbine 506 includes a turbine shell 506a,
It comprises a plurality of turbine blades 506b fixed to a turbine shell 506a. An inner peripheral end of the turbine shell 506a is fixed to a flange portion 508a of the turbine hub 508 by a plurality of rivets 509. The turbine hub 508 has a spline hole 50 on its inner peripheral side that
8b.

The inner peripheral portion of the impeller 505 and the turbine 506
The stator 507 is disposed between the inner peripheral portion and the inner peripheral portion. The stator 507 is connected to the impeller 5 from the turbine 506.
05 to increase the torque ratio by adjusting the direction of the hydraulic oil returned to the annular stator carrier 507a.
And a plurality of stator blades 507b provided on the outer peripheral surface of the stator carrier 507a.
Stator carrier 507a is connected to inner race 510 via a one-way clutch mechanism. Inner race 510 is connected to a fixed shaft (not shown) extending from the transmission side.

The lock-up device 503 is disposed between the front cover 504 and the turbine 506. The lock-up device 503 includes a disc-shaped piston 511.
And a damper mechanism 514. The radially inner end of the piston 511 is slidably supported on the outer peripheral surface of the turbine hub 8 in the axial and circumferential directions. An annular friction member 515 is adhered to an outer peripheral portion of the piston 11 on a surface of the front cover 504 facing the friction surface 504b. The piston 511 has a cylindrical outer peripheral wall 511a extending rearward in the axial direction (rightward in FIG. 32) at an outer peripheral end. A plurality of notches 511b are formed in the outer peripheral wall 511a at equal intervals in the circumferential direction.

The damper mechanism 514 mainly includes a pair of first and second side plates 516 and 517 arranged at a predetermined interval in the axial direction, a driven plate 512, and a pair of vibration damping springs 521. Is configured. First
The side plate 516 has a cylindrical wall 516a extending toward the transmission at an outer peripheral portion and fixed to the outer peripheral end of the second side plate 517. In the cylindrical wall 516a, locking portions 516c formed by drawing inside are formed at two locations facing each other in the radial direction. The first side plate 516 and the second side plate 517 are formed by the cylindrical wall 516a and the second side plate 51.
7 has protrusions 516b and 517b that project radially outward at predetermined intervals in the circumferential direction. The protrusions 516b and 517b are fixed to each other by a plurality of rivets 526, and are slidably engaged with the notch 511b of the piston 511 in the axial direction.

In this way, the first side plate 51
6 and the second side plate 517 form an annular spring accommodating chamber 520 whose outer peripheral portion is closed. A pair of vibration damping springs 521 and a driven plate 512 are housed in the annular spring housing chamber 520. The driven plate 512 is a disk-shaped member, and has two protruding portions 512a that protrude radially outward at two locations corresponding to the locking portions 516c in the radial direction. An inner peripheral end of the driven plate 512 is fixed to a flange portion 508 a of the turbine hub 508 by a rivet 509.

The annular spring accommodating chamber 520 is provided between the locking portion 516c of the first side plate 516 and the driven plate 51.
It is divided into a pair of arc-shaped chambers by the two projections 512a. A vibration damping spring 521 is arranged in each arc-shaped chamber. The vibration damping spring 521 is the same as the vibration damping spring 21 of the eighth embodiment, and a description thereof will be omitted.

The vibration damping springs disclosed in the ninth to fifteenth embodiments may be used for the torque converter 501.

[0110]

The vibration damping spring according to the present invention realizes a conventional spring member and a friction generating mechanism by a simple spring element composed of a leaf spring and an elastic body. Is obtained.

[Brief description of the drawings]

FIG. 1 is a perspective view of a vibration damping spring element according to a first embodiment.

FIG. 2 is a view taken in the direction of the arrow II in FIG.

FIG. 3 is a view taken in the direction of the arrow III in FIG. 1;

FIG. 4 is a diagram showing an operation state of a vibration damping spring element.

FIG. 5 is a view showing one state of operation of a vibration damping spring element.

FIG. 6 is a plan view of a vibration damping spring according to a second embodiment.

FIG. 7 is a plan view of a vibration damping spring according to a third embodiment.

FIG. 8 is a plan view of a vibration damping spring according to a fourth embodiment.

FIG. 9 is a plan view of a vibration damping spring according to a fifth embodiment.

FIG. 10 is a partially omitted plan view of a vibration damping spring according to a sixth embodiment.

FIG. 11 is a partially omitted plan view of a vibration damping spring according to a seventh embodiment.

FIG. 12 is a step-by-step plan view of a clutch mechanism using a vibration damping spring according to an eighth embodiment.

FIG. 13 is a sectional view taken along line XIII-XIII of FIG.

14 is a sectional view taken along the line XIV-O in FIG.

FIG. 15 is a plan view of a vibration damping spring.

FIG. 16 is a partial view of FIG.

FIG. 17 is a partial perspective view of a vibration damping spring.

18 is a sectional view taken along the line XVIII-XVIII in FIG.

FIG. 19 is a view corresponding to FIG. 16 and showing one operation state of the vibration damping spring;

FIG. 20 is a view corresponding to FIG. 16 and showing one operation state of the vibration damping spring;

FIG. 21 is a view corresponding to FIG. 15 in a ninth embodiment;

FIG. 22 is a view corresponding to FIG. 15 in a tenth embodiment.

FIG. 23 is a view corresponding to FIG. 15 in the eleventh embodiment.

FIG. 24 is a view corresponding to FIG. 15 in a twelfth embodiment;

FIG. 25 is a view corresponding to FIG. 15 in the thirteenth embodiment;

FIG. 26 is a view corresponding to FIG. 15 in a fourteenth embodiment.

FIG. 27 is a view corresponding to FIG. 15 in a fifteenth embodiment;

FIG. 28 is a longitudinal sectional view of a clutch disk assembly according to a sixteenth embodiment.

FIG. 29 is a sectional view taken along the line XXIX-XXIX of FIG. 28;

FIG. 30 is a longitudinal sectional view of a damper device using a vibration damping spring according to a seventeenth embodiment.

FIG. 31 is a longitudinal sectional view of a damper device using a vibration damping spring according to an eighteenth embodiment.

FIG. 32 is a longitudinal sectional view of a torque converter using a vibration damping spring according to a nineteenth embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Vibration damping spring element 6,11,22 Vibration damping spring 2,12,22 Leaf spring 3,8,8a, 8b, 8c, 13,23 Elastic body 4,9,14,24 Bending part 5,10,15, 25 lever part

Claims (23)

[Claims] 1. A leaf spring having a bent portion and a pair of lever portions extending from both ends of the bent portion, and is disposed inside the leaf spring and elastically deforms when the levers are deformed in directions approaching each other. A vibration damping spring having a spring element made of an elastic body. 2. The vibration damping spring according to claim 1, wherein said elastic body is fixed to said leaf spring. 3. The vibration damping spring according to claim 2, wherein said elastic body is formed integrally with said leaf spring. 4. The elastic body according to claim 1, wherein said elastic body is made of rubber.
The vibration damping spring according to any one of the above. 5. The apparatus according to claim 1, wherein said leaf spring is made of metal.
The vibration damping spring according to any one of the above. 6. The elastic body has a contact portion that is in close contact with the inner surface of the bent portion of the leaf spring, and a protruding portion that extends from the contact portion to the distal end of the lever portion of the leaf spring and is separated from the lever portion. The vibration damping spring according to any one of claims 1 to 5, comprising: 7. The spring element according to claim 1, wherein a plurality of said spring elements are arranged and connected so as to be compressible in series.
The vibration damping spring according to any one of the above. 8. A shape which is alternately bent and extended,
A leaf spring having a plurality of bent portions and a plurality of lever portions connecting both ends of the plurality of bent portions; and a leaf spring disposed between the lever portions, and elastically deforming in a direction in which the lever portions approach each other. A vibration damping spring comprising: a deformable elastic body. 9. The vibration damping spring according to claim 8, wherein said elastic body is disposed between some of said lever portions. 10. The vibration damping spring according to claim 8, wherein said elastic body is fixed to said leaf spring. 11. The vibration damping spring according to claim 10, wherein said elastic body is formed integrally with said leaf spring. 12. The method according to claim 8, wherein said elastic body is made of rubber.
12. The vibration damping spring according to any one of 11). 13. The apparatus according to claim 8, wherein said leaf spring is made of metal.
13. The vibration damping spring according to any one of 12 above. 14. A leaf spring having a shape bent and extended alternately and having a plurality of bent portions and a plurality of lever portions connecting both ends of the plurality of bent portions, and is disposed between the lever portions. A plurality of elastic bodies elastically deformed when the levers are deformed in directions approaching each other;
A vibration damping spring. 15. The vibration damping spring according to claim 14, wherein said plurality of elastic bodies are arranged between a part of said lever portions. 16. The vibration damping spring according to claim 14, wherein said plurality of elastic bodies include those having different shapes. 17. The vibration damping spring according to claim 14, wherein said plurality of elastic members include members having different rigidities. 18. The vibration damping spring according to claim 14, wherein said plurality of elastic bodies are fixed to said leaf spring. 19. The vibration damping spring according to claim 18, wherein said plurality of elastic bodies are integrally formed with said leaf spring. 20. The vibration damping spring according to claim 14, wherein said plurality of elastic bodies are made of rubber. 21. The plate spring according to claim 14, wherein said leaf spring is made of metal.
21. The vibration damping spring according to any one of items 20 to 20. 22. The vibration damping spring according to claim 14, wherein said leaf spring extends in an arc shape as a whole without an external force acting thereon. 23. An input-side rotator, an output-side rotator arranged to be rotatable relative to the input-side rotator, and the two rotators between the input-side rotator and the output-side rotator. 23. The vibration damping spring according to claim 14, wherein the vibration damping spring is arranged in an arc shape such that when the members rotate relative to each other, the two members are compressed in a rotational direction.