JP2000320614A - Power transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To effectively generate a friction force and reduce the resonant oscillation by interposing a tapered member between, at least, either one of a drive- side first rotary body or a driven-side second rotary body and an elastic body and frictionally contacting the tapered member with the other of the first and the second rotary bodies. SOLUTION: In a clutch disc, a drive plate 1 is formed by joining two members by a rivet 6 in the outer circumferential edge side and sandwiches a driven plate 2 therebetween. The plates 1, 2 define a plurality of mutually mated windows 11, 12 in the circumferential faces, springs 4 are stored in the respective windows 11, 12, and tapered shims 5A, 5B are stored in the both ends of the spring 4. The rotation of a flywheel 10 is transmitted to the drive plate 1 via a facing 9 and a cushioning plate 7, then transmitted to the driven plate 2 via the spring 4 and the tapered shim 5B, and lastly transmitted to a shaft via a hub 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch disk, a dual mass flywheel or the like having a built-in elastic body such as a spring, and an elastic body provided between a first rotating body on the driving side and a second rotating body on the driven side. The present invention relates to an improvement in a power transmission device that transmits power through the power transmission device.

[0002]

2. Description of the Related Art Conventionally, a clutch disk or a dual mass flywheel has first and second rotating bodies connected in the rotating direction via springs, and a first rotating body on a driving side and a second rotating body on a driven side. By transmitting power to the body via a spring, rotation fluctuations on the engine side are not transmitted to the transmission side.

[0003] However, resonance vibration may occur under certain conditions due to the presence of a spring. Normally, there is no problem because resonance vibration is set so as not to occur in the normal rotation range. However, resonance vibration occurs in an extremely low rotation range of, for example, 300 to 400 rpm. Will occur.

Therefore, conventionally, as shown in an example of a dual mass flywheel in Japanese Patent Application Laid-Open No. 7-71525, first and second motors are connected in a rotating direction via a spring.
A friction disk pressed by a disc spring and a washer is provided between the plate surfaces of the rotating body (primary and secondary flyholes) to generate a frictional force, thereby reducing resonance vibration.

[0005]

However, in the structure described in the above publication, (1) the number of parts is large, disadvantageous in terms of layout, and (2) the disc spring is dissipated by the heat generated when the friction disk generates friction. (3) In order to reduce the diameter of the friction disk in the layout, a larger pressing force is required to obtain the required friction torque. There was a problem of large wear.

Further, regardless of the occurrence of resonance vibration,
Since the frictional force is constant, there is also a problem that the original effect of suppressing the rotation fluctuation is hindered. The present invention has been made in view of such conventional problems, and has as its object to generate a frictional force more effectively with a simple structure and reduce resonance vibration.

[0007]

According to the first aspect of the present invention, there is provided a power transmission for transmitting power between a first rotating body on a driving side and a second rotating body on a driven side via an elastic body. In the apparatus, a tapered member that is displaced by causing a component force in a direction orthogonal to the rotation direction by a force in a rotation direction is interposed between at least one of the first and second rotation bodies and the elastic body. The tapered member is configured to make frictional contact with the other of the first and second rotating bodies due to its displacement.

In the invention according to claim 2, the tapered member is provided between the first rotating body and the elastic body and between the elastic body and the second rotating body. It is characterized by.

According to a third aspect of the present invention, the direction of displacement of the tapered member is outward in the rotational radius direction. The invention according to claim 4 is characterized in that the direction of displacement of the tapered member is set inward in the radial direction of rotation.

[0010]

According to the first aspect of the present invention, when power is transmitted between the first rotating body on the driving side and the second rotating body on the driven side via the elastic body, for example, the first rotating body is used. By providing a tapered member between the body and the elastic body, displacing the tapered member by a component force in a direction orthogonal to the rotation direction, and bringing the tapered member into frictional contact with the second rotating body, This produces an effect that a frictional force is generated between the second rotating bodies, and the resonance vibration can be reduced while maintaining the allowable transmission torque therebetween.

Further, the above-mentioned effect can be obtained by a compact structure.
In addition, it is possible to minimize the change in the component shape. That is, since only the tapered member is provided by slightly changing the shape of the elastic accommodating portion, there is little rebound to the layout, and the necessity of the conventionally required disc spring is eliminated to eliminate the set factor and the like. it can.

Further, as the torque on the driving side increases and the torsion angle increases, a large component force is generated and the frictional force increases. Therefore, when the torque on the driving side increases due to the occurrence of resonance vibration. Thus, the frictional force can be effectively increased, and the resonance vibration can be reduced. On the other hand, the original effect of suppressing the rotation fluctuation during the normal operation is hardly hindered.

According to the second aspect of the invention, the tapered member is provided between the first rotating body and the elastic body, and between the elastic body and the second rotating body.
By providing each of them between the rotating body and the rotating body, it is possible to generate a larger frictional force.

According to the third aspect of the present invention, since the displacement direction of the tapered member is set outward in the rotational radius direction, a frictional force can be generated even by centrifugal force, and a larger frictional force can be obtained. Can be.

According to the fourth aspect of the present invention, since the displacement direction of the tapered member is set to the inner side in the radial direction of rotation, the centrifugal force acts in the direction of decreasing the frictional force. Generates relatively large frictional force to prevent resonance vibration at low rotation speeds, reduces frictional force at high rotation speeds where centrifugal force is large, improves the effectiveness of springs, and reduces noise at high rotation speeds. Can be increased.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to an example applied to a clutch disk. FIG. 1 is a front view of a clutch disk showing one embodiment of the present invention, and FIG.
3 is a front view of a spring housing portion, and FIG. 4 is a BB cross-sectional view of FIG.

Drive plate (first rotating body on the driving side)
Reference numeral 1 denotes a member in which two members are joined by a rivet 6 on an outer peripheral edge side, and a driven plate (second rotating body on a driven side) 2
Is sandwiched.

The driven plate 2 has a hub 3 integrally at the center. The hub 3 is mounted on a shaft (transmission input shaft) on the transmission (not shown) and transmits rotation to the shaft while being movable in the axial direction of the shaft.

The drive plate 1 and the driven plate 2 have a plurality of windows 11 and 12 corresponding to each other on the peripheral surface.
A spring (elastic body) 4 is housed in each of the windows 11 and 12, and tapered shims (tapered members) 5A and 5B are housed at both ends of the spring 4. Accordingly, as shown in FIGS. 3 and 4, the rotation of the drive plate 1 is transmitted to the driven plate 2 via the taper shim 5A, the spring 4, and the taper shim 5B.

A cushioning plate 7 is attached to the outer peripheral side of the drive plate 1 by the rivets 6 by tightening together, and a facing (friction material) 9 is attached to the cushioning plate 7 by rivets 8. The facing 9 faces the flywheel 10 driven by the engine.

Therefore, when the hub 3 moves in the axial direction and the facing 9 frictionally contacts the flywheel 10, the rotation of the flywheel 10 is transmitted to the drive plate 1 via the facing 9 and the cushioning plate 7, and the drive The rotation of the plate 1 is tapered shim 5A,
Driven plate 2 via spring 4 and taper shim 5B
The rotation of the driven plate 2 is transmitted to a shaft (not shown) via the hub 3.

Here, when the rotation of the drive plate 1 is transmitted to the driven plate 2, the spring 4 is interposed to prevent the rotation fluctuation of the engine from being transmitted to the transmission.

The role of the taper shims 5A and 5B will be described in more detail with reference to FIGS. Taper shim 5
A is disposed in the windows 11 and 12 of the drive plate 1 and the driven plate 2 so as to be located between the drive plate 1 and the spring 4 and has a tapered shape that becomes wider outward in the radial direction of rotation. The contact portion on the drive plate 1 side is also formed in a tapered shape (tapered portion 11a). A contact portion (pressed portion) 12b on the driven plate 2 side is arranged outside the tapered shim 5A in the rotation radial direction.

The taper shim 5B is disposed between the spring 4 and the driven plate 2 in the windows 11 and 12 of the drive plate 1 and the driven plate 2, and has a width that increases toward the outside in the rotation radial direction. The contact portion on the driven plate 2 side is also formed in a tapered shape (tapered portion 12a). A contact portion (pressed portion) 11b on the drive plate 1 side is arranged outside the tapered shim 5B in the rotation radial direction.

Therefore, when the spring 4 is pressed through the taper shim 5A by the rotation of the drive plate 1, a force in the rotation direction generates a component force in the rotation radial direction outer side perpendicular to the rotation direction due to the rotation direction force, and the taper shim 5A rotates. It is pushed radially outward and comes into frictional contact with the contact portion 12b on the driven plate 2 side. Thus, the resonance vibration can be reduced by bringing the drive plate 1 and the driven plate 2 into frictional contact with each other via the taper shim 5A.

When the driven plate 2 is pressed and driven by the spring 4 via the tapered shim 5B, a force in the rotating direction generates a component component in a radially outward direction orthogonal to the rotational direction due to the rotational direction, thereby causing the tapered shim 5B to rotate. And is in frictional contact with the contact portion 11b on the drive plate 1 side. Also in this case, the drive plate 1 and the driven plate 2 are brought into frictional contact with each other via the tapered shim 5B, so that the resonance vibration can be reduced.

FIG. 5 schematically shows the resonance vibration damping effect of one taper shim 5A. The power is orthogonal to the spring 4 direction according to the taper amount set between the drive plate 1 and the taper shim 5A. In the direction (rotational direction outside), and a component force (pressing load) in the orthogonal direction acts on the taper shim 5A, so that frictional resistance is generated between the tapered shim 5A and the driven plate 2, and the frictional resistance is generated. Shows a basic structure capable of greatly attenuating resonance vibration while increasing allowable transmission torque by acting as hysteresis.

In particular, as the torque on the drive side increases and the torsion angle increases, a large component force (pressing load) is generated and the frictional force increases, so that the torque on the drive side increases due to the occurrence of resonance vibration. When this happens, the frictional force can be effectively increased and the resonance vibration can be reduced, but the original effect of the spring 4 on suppressing the rotation fluctuation during normal operation is less likely to be hindered.

In this embodiment, the tapered shims 5A, 5A
The direction of displacement of B is defined as the outer side in the radial direction of rotation, and by making the direction of action of centrifugal force the same as that of
The frictional force can be increased.

However, as shown in FIG. 6 as another embodiment, the taper shims 5A and 5B are tapered so as to become wider inward in the radial direction of rotation.
By setting the direction of displacement of A and 5B to the inside of the rotational radius direction and in the opposite direction to the direction of action of the centrifugal force, a large frictional force is generated in a low rotational range where the centrifugal force is small, and resonance vibration in the low rotational range To prevent this, the frictional force may be reduced in the high rotation range where the centrifugal force is large, so that the effect of the spring 4 may be improved and the quietness in the high rotation range may be enhanced.

In the above, an example of application to a clutch disk has been described. However, similar effects can be obtained by applying the present invention to a dual mass flywheel.

[Brief description of the drawings]

FIG. 1 is a front view of a clutch disc showing an embodiment of the present invention.

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

FIG. 3 is a front view of a spring housing portion.

FIG. 4 is a sectional view taken along line BB of FIG. 3;

FIG. 5 is a principle diagram of a damping action of resonance vibration.

FIG. 6 is a front view of a spring storage portion showing another embodiment.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 drive plate (first rotating body on driving side) 2 driven plate (second rotating body on driven side) 3 hub 4 spring (elastic body) 5A, 5B taper shim (tapered member) 7 cushioning plate 9 facing 10 engine side Flywheel 11,12 Window 11a, 12a Tapered part 11b, 12b Contact part (pressed part)

Claims (4)

[Claims] 1. A power transmission device for transmitting power between a first rotating body on a driving side and a second rotating body on a driven side via an elastic body, wherein at least one of the first and second rotating bodies. A tapered member that is displaced by generating a component force in a direction orthogonal to the rotation direction by a force in the rotation direction is interposed between one of the elastic members and the elastic body, and the first and second tapered members are displaced by the displacement. A power transmission device characterized in that it is configured to make frictional contact with the other of the two rotating bodies. 2. The apparatus according to claim 1, wherein said tapered member is provided between said first rotating body and said elastic body, and between said elastic body and said second rotating body. 1. The power transmission device according to 1. 3. The power transmission device according to claim 1, wherein the direction of displacement of the tapered member is outward in the rotation radial direction. 4. The power transmission device according to claim 1, wherein the direction of displacement of the tapered member is set inward in the rotational radius direction.