JPH04203532A - Multiple plate type clutch device - Google Patents

Abstract

PURPOSE:To reduce the frictional loss in idle revolution by interposing an elastic member between a frictional plate and an opponent plate so that both can be separatad, keeping a gap, when a pressing means for friction-engaging a plurality of frictional plates and opponent plates is released. CONSTITUTION:A ring shaped rubber 7 is inserted into the inner peripheral side between the contiguous frictional plates 5, and a ring-shaped rubber 7' is inserted into the outer peripheral side between the contiguous opponent plates 6, and the thickness of the rubber plate 7 is determined so that tha gap in the axial direction between the opponent plate 6 and the frictional plate 5 has a proper value. When a piston 3 is shifted to the left side by the pressurized oil supplied from an oil passage la, the ring-shaped rubbers 7 and 7' contract in the axial direction, and the opponent plate 6 and the frictional plate 5 contact, and the frictional engagement is generated. When the pressurized oil is removed, the piston 3 is shifted to the right side by the springy force of a spring 4, and since the frictional plate 5 and the opponent plate 6 do not contact during the relative revolution, the frictional loss is reduced, and efficiency is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a device for securing a clearance between clutch plates of a multi-disc clutch for a vehicle.

[Conventional technology]

As described in Japanese Utility Model Application Publication No. 63-173525, in the conventional device, there is no restriction on the axial position of the clutch plate and the mating plate, so the clutch is disengaged, that is, the piston moves the clutch plate and the mating plate. When the pressure is removed, the clutch plate and the mating plate are free in the axial direction, and often the clutch plate and the mating plate are in side-to-side contact. Since the mating plate or friction plate on the input shaft side is rotating, a burr may occur between the friction plate or the mating plate on the output shaft side and friction loss increases.

The prior art will be explained with reference to FIG. Input shaft housing 1
has a built-in piston 3, and the piston 3 moves to the left in the figure by pressure oil from the oil passage]-a of the input shaft housing. At that time, an internal gear 1a carved on the inner surface of the outer periphery of the input shaft housing 1 and an external gear 3a carved on the outer periphery of the piston.
Since the two are in mesh, the piston is restrained in its direction of rotation. The friction plates 5 and the mating plates 6 of the clutch are arranged alternately. The friction plate 5 rotates integrally with the output shaft hub 2 because the internal gear 5a carved on the inner peripheral surface and the external gear 2a carved on the outer peripheral surface of the output shaft hub 2 mesh with each other. The mating plate 6 meshes with an external gear 6a carved on the outer circumferential surface and an internal gear [a] of the input shaft housing 1, so that it rotates together with the input shaft housing.

The left mating plate 6a is restrained from moving to the left by a stopper 8 embedded in the internal gear 1a of the input shaft housing 1. The piston 3 is moved to the left by hydraulic pressure and first comes into contact with the friction plate 5, and all the mating plates and friction plates sequentially come into frictional engagement. At this time, the input shaft housing 1 and the output shaft hub are engaged, and power is transmitted from the input shaft to the output shaft. When the supply of pressure oil is cut off, the piston is returned to the right side in the figure by the repulsive force of the spring 4. Friction plate 5. Since the mating plate 6 is not restrained in the axial direction, it swings around, and the adjacent friction plates 5 and mating plate 6 often come into contact with each other.

[Problem to be solved by the invention]

The above conventional technology does not take into account the axial position of the friction plate and the mating plate after the pressure from the piston is removed, and the friction plate and the mating plate often come into contact during idle rotation, increasing friction loss and causing the clutch device to This reduces the efficiency of the system.

The purpose of the present invention is to provide an appropriate axial clearance between adjacent friction plates and a mating plate by using spring action after the suppression is removed, thereby preventing the friction plates and the mating plate from coming into contact with each other during idling, thereby reducing friction loss. It is in.

[Means to solve the problem]

In order to achieve the above object, the present invention interposes an elastic member between the friction plate and the mating plate, and after the pressure is removed, the elastic member is restored to its original position by its spring force.

Regarding elastic members to achieve the above purpose, leaf springs,
Rubber is considered and three examples are shown below.

[Effect]

The elastic member deflects under load and returns to its original position when the load is removed. Therefore, when no load is applied to the elastic member,
Place the mating plate and the friction plate in positions that ensure proper clearance.

〔Example〕

A first embodiment of the present invention will be described below with reference to FIGS. 1 and 2.

The operation up to frictional engagement between the input shaft housing 1 and the output shaft hub 2 is the same as that of the conventional example, and will therefore be omitted.

After the pressure oil is removed, the piston 3 moves to the right in the figure by the force of the spring 4.

In the present invention, a ring-shaped rubber 7 is inserted between adjacent friction plates 5 on the inner periphery side, and a ring-shaped rubber 7' is inserted between adjacent mating plates 6 on the outer periphery side. The axial clearance between the mating plate 6 and the friction plate 5 is an appropriate value (0.2 to 0.6 m).
The thickness of the rubber 7 is determined so that A stop ring 9 is embedded in the internal gear 1a of the input shaft housing 1, and a stop ring 10 is embedded in the external gear 2a of the output shaft hub 2 to regulate the axial position of the friction plate 5° and the mating plate 6.

When the piston 3 moves to the left in the figure due to the pressure oil from the oil passage 1a, the ring-shaped rubber 7 and the ring-shaped rubber 7'
contracts in the axial direction, contacts the mating plate 6 and the friction plate 5, and is frictionally engaged.

FIG. 2 is a sectional view taken along the line ■-■ in FIG. 1. The rubber 7' may be ring-shaped, but by carving external teeth 7a', the rotational direction can be restricted and slippage with the mating plate 6 can be prevented. Although the rubber 7 is not shown, by carving the outer teeth in the same manner, it is possible to prevent the rubber from sliding against the friction plate 5.

Next, a second embodiment will be explained with reference to FIGS. 3 to 6. FIG. 4 is a sectional view taken along the line TV-IV in FIG. 3.

FIG. 5 is a sectional view taken along the line -V in FIG. 4. Figure 6 is the 4th
It is a partially enlarged view of the figure. In FIG. 3, the friction plates 5 and the mating plates 6 are arranged alternately with a proper clearance maintained between them. Friction plate 5
A plurality of leaf springs 7' (in FIG. 4, the positions are divided into three parts of the circumference) are rotatably attached to the inner circumference with pins 12', and the other end is attached to the circumferential slit 11 cut in the external gear 2a. ' (Figures 4 and 6). The slit 11 is the friction plate 5
The same number of grooves are carved in the face width direction of the external gear 2a.

The depth of the slit is up to the bottom circle of the external gear 2a.

The mating plate 6 has a plurality of leaf springs 7 (positions divided into three circumferences in FIG. 5) rotatably attached to the outer periphery of the mating plate 6 with pins 12, and the other end is inserted into a slit on the circumference of the internal gear 1a. (FIG. 5) The same number of slits 11 as the number of mating plates 6 are cut in the face width direction of the internal gear 1a. The depth of the slit is internal gear 1a
up to the root circle of the tooth.

The piston 3 moves to the left in the figure, and the friction plate 5 and the mating plate 6
When pressed, the leaf spring 7' fixes the external gear 2a side as the fixed end.
By bending the leaf spring 7 with the internal gear 1a side as a fixed end, the mating plate 6 and the friction plate 5 come into contact with each other and are frictionally engaged.

When the pressure oil in the piston 3 is removed and the piston 3 returns to the right side in the figure by the spring force of the spring 4, each friction plate 5
Then, the mating plate 6 returns to its original position by the restoring force of the leaf spring 7' and the leaf spring 7, and the clearance between the friction plate 5 and the mating plate 6 is maintained.

Friction plate 5. Connect the mating plate 6 to the output shaft hub 2. When assembled into the input shaft housing 1, each leaf spring has a friction plate 5 in its longitudinal direction. Pin in the direction that corresponds to the circumferential direction of the mating plate 6】-2,
The friction plate 5. rotates around the pin 12'. It is pushed into a predetermined axial position of the mating plate 6, and the leaf spring is inserted into the friction plate 5. Rotate the mating plate 6 in the radial direction and insert it into the slit.

Internal gear] The crest, backlash, and backlash between the external gear of the mating plate 6 and a are set to be larger than normal values, so that the mating plate 6 is tilted at a predetermined angle.

The crest, back and backlash between the external gear 2a and the internal gear of the friction plate 5 are also increased.

Next, a third embodiment will be explained with reference to FIGS. 7 and 8.

FIG. 8 is a partially enlarged view of FIG. 7.

Friction plate 5. Connect the mating plate 6 to the output shaft hub 2. Insert them alternately into the space inside the input shaft housing. The mating plate 6 has a plurality of U-shaped leaf springs 7 fixed to the end of the external gear 6 by machine screws 2 or spot welding. Similarly, the friction plate 5 has a plurality of U-shaped leaf springs 7' fixed to the end of the internal gear 5a by machine screws 12' or spot welding.

In order to maintain an appropriate clearance between the adjacent mating plate 6 and friction plate 5, the internal gear is equipped with a stopper 8° and a stop ring 9 on the a side. The external gear 2a side is a stopper 8'.

Determine the position 4 of the stop ring 10.

The piston 3 moves to the left in the figure due to the pressure oil from the oil passage 1a, and the friction plate 5. When the mating plate 6 is pressed, the tJ-shaped plate spring 7
, 7' are deflected, and the adjacent friction plates 5° and the mating plates 6 come into contact. When the piston 3 returns to the right side in the figure due to pressure oil removal, t
The friction plate 5 and the mating plate 6 return to their original positions by the restoring force of the J-shaped leaf springs 7, 7', and a clearance between the friction plate 5 and the mating plate 6 is secured.

〔Effect of the invention〕

According to the present invention, a clearance is maintained between the friction plate 5 and the mating plate 6 even when the pressure oil is removed due to the restoring force of the elastic member interposed therebetween.

Due to the existence of this gap, the friction plate 5 and the mating plate 6 do not come into contact even during relative rotation after the clutch is released, thereby reducing friction loss and improving efficiency.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of one embodiment of the present invention, FIG. 2 is a sectional view taken along the line nn in FIG. The figure is a sectional view taken along the line ■-■ in FIG. 3, FIG. 5 is a sectional view taken along the line V-V in FIG. 3, FIG. 6 is a partially enlarged view of FIG. Longitudinal sectional view of the third embodiment, No. 8
The figure is a perspective view of a portion of FIG. 7, and FIG. 9 is a longitudinal sectional view of the prior art. 1... Input shaft housing, 2... Output shaft hub, 3...
...Piston, 4...Spring, 5...Friction plate,
6...Mating plate, 7...Elastic member, 8...Stopper, 9
,1.0...S11 3rd 6th 70th

Claims (1)

[Claims] 1. A multi-disc clutch device having a plurality of friction plates and a plurality of mating plates arranged alternately and a pressing means for moving the friction plates or the mating plates in the axial direction and frictionally engaging them. A multi-plate clutch device characterized in that an elastic member is interposed between the friction plate and the mating plate so that the friction plate and the mating plate can be separated while maintaining a gap when the pressing means is released. .