JPH0642104Y2 - clutch - Google Patents

Description

[Detailed description of the device]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a so-called pull-type clutch in which a release lever connected to a clutch pedal pulls a release bearing toward a transmission for a release operation.

[0002]

2. Description of the Related Art In a conventional example of this kind, as shown in FIG. 4, a coil spring 100 arranged in an inclined state is used as a load generating member, a spring force is transmitted to a retainer 102, and a lever 104 is moved from the retainer 102. The pressure plate 106 is configured to exert a pressure contact force against the clutch disc 108 via the pressure plate 106 (Japanese Patent Publication No. 46-15).
046). However, there is a problem that the spring force of the coil spring 100 increases as the stroke of the clutch pedal increases, and the pedal effort at the time of clutch release increases. In addition, at high rotation, the coil spring 1
There is also a problem in that the coil spring 100 is compressed by the centrifugal force acting on 00, and the spring force on the pressure plate 106 is reduced.

[0003]

SUMMARY OF THE INVENTION An object of the present invention is to provide a clutch which uses a diaphragm spring as a load generating member and can solve a problem caused by using a coil spring as a load generating member in a so-called pull type clutch. I am trying.

[0004]

According to the present invention, in a clutch in which a release lever connected to a clutch pedal pulls a release bearing away from a flywheel to perform a release operation, a clutch disk is spline-fitted to an input shaft of a transmission, A sleeve is provided on the outer circumference of the input shaft, a release bearing is fixed to the end of the sleeve on the transmission side, and a retainer for load transmission is spline-fitted to the outer circumference of the flywheel side of the sleeve so that it cannot move axially. A clutch cover, which is connected to the wheel and covers the pressure plate for clutch disc pressure contact, is provided, and a diaphragm spring having a substantially disc-like annular shape and a plurality of inward tongue pieces is arranged between the clutch cover and the retainer, and the outer circumference of the diaphragm spring. Part through the wire ring Held in over the inner peripheral portion of the diaphragm spring is pressed against the transmission side end portion of the retainer and projecting from the clutch cover to the flywheel 2
Plural pairs of one pair of engaging protrusions are engaged with the outer peripheral protrusions of the retainer from both sides in the circumferential direction through the window holes provided in each tongue of the diaphragm spring, and are sandwiched between the retainer and the pressure plate. The inner fulcrum is held in the annular groove on the outer circumference of the retainer, and the outer fulcrum is pressed against the front surface of the adjuster ring that is screwed onto the clutch cover so that it can move axially. A lever for press contact is provided, and the load of the diaphragm spring that acts on the retainer is boosted and transmitted by the lever ratio between each fulcrum of this lever, and at the same time, a large number of protrusions protruding rearward from the adjuster ring are arranged. In the clutch, a lock plate that engages with a part of the clutch plate is fixed to an edge portion of a window hole of the clutch cover. Since the diaphragm spring generates a pressure contact force against the pressure plate, the depression force of the clutch pedal does not increase even during release, and the adverse effect of centrifugal force is small even at high speeds.

[0005]

1 is a longitudinal sectional view of a clutch according to the present invention.
In FIG. 2 (A-O-A sectional view of FIG. 2), 10 is a flywheel. On the rear surface of the flywheel 10, the clutch disc 12, the intermediate plate 14, the clutch disc 1
6 are sequentially in pressure contact with each other, and a pressure plate 18 for pressing them is provided. A pin 15 fixed to the flywheel 10 is provided radially outward of the intermediate plate 14, and the flywheel 10 and the intermediate plate 14 are integrally rotated by the pin 15.

A clutch cover 20 is provided behind the pressure plate 18 so as to cover the pressure plate 18, and the clutch cover 20 is formed thick by casting, for example. The clutch disks 12 and 16 are spline-fitted to the input shaft 22 of the transmission at the rear stage.

A cylindrical sleeve 24 is axially slidably fitted around the outer circumference of the input shaft 22 in the radial direction.
A release bearing 26 is fixed to a rear end portion of the sleeve 24, that is, an end portion on the transmission side by a snap ring 26a. A bearing holder 28 that covers the release bearing 26 is provided outside the release bearing 26, and a pressure contact plate 28 is provided on the rear end surface of the bearing holder 28.
a is fixed. The input shaft 22 is attached to the pressure plate 28a.
A through hole 28b is formed to pass through.

Reference numeral 27 in the figure denotes a release lever connected to the clutch pedal, and the release lever 27 is used to move the release bearing 26 in the axial direction.

Spline external teeth 30 are formed on a portion of the sleeve 24 other than the portion where the release bearing 26 is provided, and a retainer 32 is provided on the spline external teeth 30.
Are spline-fitted. The retainer 32 is retained by a snap ring 32a, and the sliding range of the retainer 32 forward is restricted.

The retainer 32 is, for example, a cast product and is formed in a substantially annular shape. A pressure contact portion 34 is formed over the entire circumference on the rear end surface of the retainer 32, and an annular groove 36 is formed on the front end portion. Retainer 32
The protrusions 38 are integrally formed at, for example, three positions on the outer peripheral portion in the radial direction at equal intervals in the circumferential direction.

An engaging protrusion 40 is integrally formed on the inner surface of the clutch cover 20 corresponding to the protrusion 38. As shown in FIG. 2, two engagement projections 40 are formed along both side surfaces of the projection 38, and the engagement projection 40 allows the clutch cover 20 and the retainer 32 to rotate integrally in both circumferential directions. Are linked to.

Between the clutch cover 20 and the protrusion 38, as shown in FIG. 1, a diaphragm spring 4 having a substantially disk shape.
Two are provided. The outer peripheral portion of the diaphragm spring 42 is fixed to the clutch cover 20 by a stud pin 46 via two wire rings 44. The inner peripheral portion of the diaphragm spring 42 is in pressure contact with the pressure contact portion 34 of the retainer 32. As shown in FIG. 2, a rectangular window hole 42 a through which the engagement protrusion 40 penetrates is formed in a portion of the diaphragm spring 42 corresponding to the engagement protrusion 40.

As shown in FIG. 1, a threaded portion 20a is formed on the inner peripheral surface of the clutch cover 20 radially outward of the diaphragm spring 42, and the threaded portion 20a is provided with a substantially annular adjuster ring 48. Outer thread 48
a is screwed together.

On the rear end surface of the adjuster ring 48, projections 50 extending in the axial direction are formed at, for example, 24 places at equal intervals in the circumferential direction. The protrusion 50 is formed on the outer peripheral portion in the radial direction of the rear surface of the adjuster ring 48, and a space 51 is formed inside the protrusion 50 to allow the outer peripheral portion of the diaphragm spring 42 to move by a release operation.

A window hole 52 is formed in the clutch cover 20 so as to correspond to the protrusion 50, and a radially inner end portion of the lock plate 54 is provided at the window hole 5 at the radially outer edge of the window hole 52.
It is fixed with a bolt 56 so as to project into the inside of the unit 2. The lower end of the lock plate 54 in the drawing is fitted to the protrusion 50, and the adjuster ring 48 and the clutch cover 20 are integrally connected by the lock plate 54 in a state where the position adjustment of the adjuster ring 48 in the axial direction is allowed. ing.

Pressure plate 18 and retainer 3
Between the two, levers 60 for release operation are provided at six positions at equal intervals in the circumferential direction. The inner peripheral side fulcrum 62 of the lever 60 is fitted into the annular groove 36, and the outer peripheral side fulcrum 64
Is pressed against the front end surface of the adjuster ring 48, and the intermediate fulcrum 66 is pressed against the fulcrum land portion 18a protruding rearward from the rear surface of the pressure plate 18. The lever length of the inner peripheral side fulcrum 62 and the outer peripheral side fulcrum 64,
The lever ratio of the lever length between the outer peripheral side fulcrum 64 and the intermediate fulcrum 66 is set to L1: L2.

The above-described lever 60 is, for example, a sheet metal component, and as shown in FIG. 2, two cutting lines 68 are formed on the outer peripheral portion of the lever 60 in the radial direction, and the outer side piece 70 is bent to form the above-mentioned cutting line 68. An outer peripheral side fulcrum 64 and an intermediate fulcrum 66 (Fig. 1) are formed, and a central piece 72 of the central part extending outward in the radial direction is fitted into the recess 48b of the adjuster ring 48.

Between the outer periphery of the pressure plate 18 and the clutch cover 20, there are provided four well-known strap plates 74 extending in the circumferential direction at equal intervals in the circumferential direction.

Further, the pressure contact plate 28a and the transmission side end surface 7 of FIG.
An inertia brake 78 is interposed between 6 and 6 in a state of being spline-fitted to the input shaft 22. The inertia brake 78 has facings 80 and 82 on both end surfaces, and a release margin Rr is provided between the facing 82 and the pressure contact plate 28a.

Next, the operation will be described. At the time of setting in the initial state shown by the solid line in FIG. 1, the diaphragm spring 42
The spring force P of pushes the pressure contact portion 34 of the retainer 32 forward. This spring force P is transmitted to the lever 60 from the fulcrum 62 on the inner peripheral side of the annular groove 36, and the lever ratio L1: L2 is, for example, 3
The force is doubled and transmitted from the intermediate fulcrum 66 to the fulcrum land portion 18a as the pressure contact force of the clutch discs 12 and 16. In this state, the diaphragm spring 4
Since 2 is arranged in a substantially flat posture, even if it rotates at a high speed, the influence of the centrifugal force acting on the diaphragm spring 42 is small, and the clutch discs 12, 16
There is no fear that the pressure contact force to will be reduced by centrifugal force.

If the clutch discs 12, 16 are worn over a long period of time, the pressure plate 18 moves forward, and the retainer 32 also moves. Diaphragm spring 42 during wear-in
Becomes the posture of W shown by the chain double-dashed line in FIG. In this state, the outer peripheral portion of the lever 60 is in a rearwardly tilted posture,
After removing the lock plate 54, the adjuster ring 48 is screwed forward to maintain the lever 60 in a predetermined posture.

The spring characteristic of the diaphragm spring 42 is, as shown by the characteristic 90 in FIG. 3 showing the relationship between the flexure amount D and the spring force P, the wear-in margin Wr corresponding to the wear amount of the clutch disks 12 and 16. Since it has a convex shape upward, the spring force P from the diaphragm spring 42 has a characteristic 9 in the case of the conventional coil spring 100 (FIG. 4).
2, the pressure contact force of the pressure plate 18 to the clutch discs 12, 16 is increased as compared with the conventional case.

When the clutch discs 12 and 16 are worn, the spring force P decreases from the set load P1 to the wear-in load P2 in the characteristic 92, but only in the set 90 from the set load P1 to the wear-in load P3 in the characteristic 90. Does not decrease,
The so-called wear-in load increases when the clutch discs 12, 16 wear. Moreover, since the characteristic 90 as described above also reduces the release force required for release,
The pedal effort of the clutch pedal is also light.

Next, when the clutch pedal is released, the release lever 27 is used to release the release bearing 26.
Moves rearward, and the sleeve 24 slides together with the release bearing 26. Retainer 32 held by snap ring 32a when sleeve 24 slides backward
Is pulled rearward against the spring force P of the diaphragm spring 42, and the diaphragm spring 42 enters the state of R in FIG. At this time, the fulcrum 62 on the inner peripheral side of the lever 60
Moves rearward around the outer peripheral side fulcrum 64, and the intermediate fulcrum 66 also moves rearward, so that the pressure plate 18
Moves backward due to the spring force of the strap plate 74, and the pressure contact between the clutch disks 12 and 16 is released.

[0025]

As described above, in the clutch according to the present invention, instead of the conventional coil spring 100, the diaphragm spring 42 is housed inside the narrow clutch cover 20, and the spring force P of the diaphragm spring 42 is accommodated.
Is transmitted to the retainer 32, and the lever 60 that doubles the lever ratio of L1: L2 is interposed between the retainer 32 and the pressure plate 18, so that the centrifugal force that acts on the diaphragm spring 42 even when rotating at a high speed. Is less affected, and it is possible to prevent the pressure contact force to the clutch discs 12 and 16 from being reduced by centrifugal force.

The spring characteristic of the diaphragm spring 42 is in the range of the wear-in allowance Wr corresponding to the abrasion amount of the clutch discs 12 and 16 as shown by the characteristic 90 of FIG. 3 showing the relationship between the flexure amount D and the spring force P. Since it has a convex shape upward, the spring force P from the diaphragm spring 42 becomes larger than the characteristic 92 in the case of the conventional coil spring 100 (FIG. 4), and the pressure contact force of the pressure plate 18 to the clutch discs 12, 16 is reduced. It can be increased.

When the clutch disks 12 and 16 are worn, the spring force P decreases from the load P1 at the time of setting to the load P2 at the time of wear-in in the characteristic 92, but in the characteristic 90 only from the load P1 at the time of setting to the wear-in load P3. Does not decrease,
It is possible to increase the so-called wear-in load when the clutch disks 12 and 16 are worn. Moreover, since the release force required at the time of release is reduced due to the characteristics 90 as described above, the depression force of the clutch pedal is also reduced.

In the present invention, the engaging projection 40 projecting from the clutch cover 20 to the flywheel side is engaged with the outer peripheral projection 38 of the retainer 32 through the window hole 42a of the diaphragm spring 42. The relative rotation of the retainer 42 and the retainer 32 can be stopped at the same time, the wear of each part is prevented, and the assembly becomes easy. Further, since the lock plate 54 that engages with a part of the large number of protrusions 50 of the adjuster ring 48 that serves as a fulcrum on the outer peripheral side is fixed to the clutch cover 20, the lock plate 54 is removed when the clutch disks 12 and 16 are worn. Later adjuster ring 4
There is an advantage that the lever 60 can be screwed forward and the lever 60 can be maintained in a predetermined posture, and the spring force can be reliably transmitted.

A plurality of pairs of engaging projections 40 are provided with each pair of projections 38.
Since the projections 38 are held by being engaged with both sides in the circumferential direction, the clutch cover 20 and the retainer 32 cannot rotate in both circumferential directions and can slide in the axial direction. In addition, each engaging projection 40 has a tongue piece 1 that faces inwardly of the diaphragm spring 42.
Since the single window hole 42a provided in each piece is penetrated, it is possible to reduce the rigidity of the tongue as much as possible and to secure the detent for the clutch cover 20 while securing the lever function. There are advantages.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a clutch to which the present invention is applied.

FIG. 2 is a view on arrow II of FIG.

FIG. 3 is a graph showing the relationship between the spring force and the amount of flexure of a diaphragm spring.

FIG. 4 is a vertical sectional view showing a conventional example.

[Explanation of symbols]

 10 Flywheel 12 Clutch Disc 16 Clutch Disc 18 Pressure Plate 20 Clutch Cover 22 Input Shaft 24 Sleeve 26 Release Bearing 32 Retainer 42 Diaphragm Spring 48 Adjuster Ring 60 Lever

Claims (1)

[Scope of utility model registration request] 1. In a clutch in which a release lever connected to a clutch pedal pulls a release bearing away from a flywheel to perform a release operation, a clutch disk is spline-fitted to an input shaft on the transmission side, and an outer circumference of the input shaft is provided. The release bearing is fixed to the end of the sleeve on the transmission side, and the retainer for load transmission is spline-fitted to the outer periphery of the end of the sleeve on the flywheel side so that it cannot move in the axial direction. A clutch cover is provided to cover the pressure plate for pressure contact of the clutch disc, and a diaphragm spring having a substantially disc-like annular shape and a plurality of inward tongues is arranged between the clutch cover and the retainer, and the outer peripheral portion of the diaphragm spring is wired. Hold on the clutch cover via , The inner peripheral portion of the diaphragm spring is brought into pressure contact with the transmission side end of the retainer, and a plurality of pairs of one pair of engaging projections projecting from the clutch cover to the flywheel side are provided on each tongue piece of the diaphragm spring.
Engage and hold the outer protrusions of the retainer from both sides in the circumferential direction through the individually provided window holes, and retain the inner fulcrum in the annular groove on the outer periphery of the retainer between the retainer and the pressure plate, and the outer fulcrum. Is pressed against the front of the adjuster ring that is screwed onto the clutch cover so that it can move in the axial direction,
A lever that presses the intermediate fulcrum against the fulcrum land on the rear surface of the pressure plate is provided, and the lever ratio between the fulcrums of this lever is used to boost and transmit the load of the diaphragm spring that acts on the retainer. A clutch characterized in that a lock plate engaging with a part of a large number of projections protruding rearward at equal intervals is fixed to an edge portion of a window hole of a clutch cover.