JPH08121500A - Hydraulic clutch release cylinder device - Google Patents

Abstract

PURPOSE: To more shorten dimensions or improving sliding smoothness of hydraulic clutch release cylinder device. CONSTITUTION: In a hydraulic clutch release cylinder device having a cylinder 2 having an annular groove, cylindrical piston 4 slid together in the annular groove and a release bearing 6 mounted in an external end of the cylindrical piston, the cylinder is constituted of in/out double coaxially arranged cylindrical parts 7a, 7b of different diameter and of outward facing flange parts 8a, 8b formed in each one end of the cylindrical part further to be superposed on each other, to provide in at least any one of the two outward facing flange parts a groove, for a brake fluid to flow, followed by press molding. Otherwise, a bearing carrier 5 of the release bearing is integrally formed in an external end of the cylindrical piston 4, and of the in/out double coaxially arranged cylindrical parts of different diameters, in the cylindrical part provided in the inside, an elongation part 33 of sliding together an internal peripheral surface of the bearing carrier is formed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic clutch release cylinder device, and more particularly to a liquid clutch type release cylinder device in which a slave cylinder is provided coaxially with an input shaft of a transmission and a release bearing is directly driven by a piston of the slave cylinder. The present invention relates to a pressure clutch release cylinder device.

[0002]

2. Description of the Related Art Conventionally, for a vehicle clutch, a slave cylinder is stroked by a hydraulic pressure generated by a master cylinder directly connected to a clutch pedal, thereby moving a release bearing along an axial direction via a release fork. A release mechanism configured to displace the pressure plate by pressing the central portion of the diaphragm spring with this release bearing is often used.

On the other hand, the output transmission capacity of the clutch must be increased as the output of the engine is increased, and the release operation force of the clutch is also increasing accordingly. Therefore, in recent years, reduction of the operating force has become one of the important issues in designing the release mechanism of the clutch.

Incidentally, in order to reduce the pedaling force in the conventional manner, for example, it is conceivable to increase the bore of the slave cylinder, add a booster device utilizing negative suction pressure, and lengthen the release fork. It is difficult to say that it is preferable because it causes an increase in external dimensions.

In order to improve such inconvenience, a slave cylinder concentrically provided with the input shaft allows
C that allows the release bearing to be driven directly
An oncentric Slave Cylinder (CSC) type release device has been proposed in US Pat. No. 4,983,332 and the like. This is to receive a cylindrical piston slidably in the annular groove in the axial direction and supply the hydraulic pressure of the master cylinder from the bottom of the annular groove.By using the cylindrical piston, a large pressure receiving area can be made compact. Can be obtained in configurations.

[0006]

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention
In the release device of the type, since it is necessary to provide the hydraulic pressure supply passage of the master cylinder at the bottom of the annular groove of the slave cylinder, the axial dimension that does not contribute to the stroke is required correspondingly on the bottom side of the slave cylinder. This is not preferable for promoting the shortening of the release device.

On the other hand, it is extremely difficult to match the circumference on which the thrust of the cylindrical piston acts with the circumference on which the reaction force of the diaphragm spring applied to the release bearing acts, and there is a difference in the diameters of both circumferences. Occurrence is unavoidable. Therefore, a bending moment acts on the tubular piston, but in order to withstand this bending moment and ensure sliding smoothness, high rigidity must be imparted to the tubular piston. This can be one obstacle in promoting the weight reduction of the cylindrical piston.

The present invention has been devised in order to eliminate such disadvantages of the prior art, and the first object thereof is a hydraulic clutch constructed so as to promote further shortening. It is to provide a release cylinder device. A second object of the present invention is to provide a hydraulic clutch release cylinder device that is configured to ensure sliding smoothness without increasing the weight of the cylindrical piston.

[0009]

The first aspect of the present invention as described above
The purpose of is a cylinder formed of an annular groove that is deep along the axial direction of the input shaft of the transmission and is coaxial with the input shaft, and a cylinder that is received in the annular groove and is extruded by the hydraulic pressure in the annular groove. In a hydraulic clutch release cylinder device having a cylindrical piston and a release bearing mounted on the axially outer end of the cylindrical piston, the cylinders are coaxial with each other with a gap for receiving the cylindrical piston. And a cylindrical portion of different diameters arranged inside and outside, and an outward flange portion formed at one end of each of these two cylindrical portions and overlapping each other.
The present invention is achieved by providing a hydraulic clutch release cylinder device characterized in that a groove through which brake fluid flows is recessed by press molding in at least one of the two outward flange portions.

A second object of the present invention is to provide a hydraulic clutch release cylinder device of the above-mentioned type in which the bearing carrier of the release bearing is integrally formed at the axially outer end of the cylindrical piston, and A cylindrical portion of different diameter arranged coaxially with each other inside and outside so as to have a gap for receiving the cylindrical piston, and the other inside of the two cylindrical portions. The present invention is achieved by providing a hydraulic clutch release cylinder device characterized in that an extended portion is formed at an end and an inner peripheral surface of the bearing carrier is slid on an outer peripheral surface of the extended portion.

[0011]

According to this structure, since the brake fluid supply passage can be formed without providing a spacer or the like between the joint surfaces of the flange portions of the cylinder, it is necessary to make a large gap between the flanges. Disappears.

Further, since the extending portion formed on the inner cylindrical portion secures the position of the bearing carrier integrally formed on the cylindrical piston, the thrust acting circle of the cylindrical piston and the reaction force of the diaphragm spring applied to the release bearing are secured. Even if the working circle does not match, the bending moment does not act on the cylindrical piston.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of the present invention will be described in detail below with reference to specific embodiments shown in the accompanying drawings.

FIGS. 1 and 2 show a clutch release cylinder device constructed according to the present invention. The upper side from the center line in FIG. 2 shows the clutch disengaged state in which hydraulic pressure is applied to the release cylinder device. The side shows the clutch engagement state in which the hydraulic pressure of the release cylinder device is released. The clutch release cylinder device 1 includes a cylinder 2 fixed to the transmission housing TH side, a cylindrical piston 4 slidably fitted in an annular groove 3 formed in the cylinder 2.
It is composed of a release bearing 6 mounted on a bearing carrier 5 integrally formed with the tubular piston 4 at the axially outer end of the tubular piston 4, and is mounted coaxially with an input shaft S of the transmission.

The cylinder 2 is a combination of two members consisting of cylindrical portions 7a and 7b and flange portions 8a and 8b formed outward at one end of the cylindrical portions 7a and 7b. These two members are formed by drawing a metal material, and the diameters of the cylindrical portions 7a and 7b are different from each other in accordance with the thickness of the cylindrical piston 4, and both flange portions 8a and 8b are formed.
The basic outlines of both are the same. In this way, an annular groove 3 that is deepened along the axis of the input shaft S is formed between the two cylindrical portions 7a and 7b that are double-sided. Further, the flange portions 8a and 8b of the two members are
The O-ring 10 is interposed between the joint surfaces of the two, and the plurality of ear plates 11 provided on the outer peripheral portion of the flange portion 8b integral with the inner peripheral side cylindrical portion 7b are integrated with the outer peripheral side cylindrical portion 7a. By bending the upper surface of the portion 8a (see FIG. 3), they are integrally coupled in a state in which the liquid-tightness of their joint surfaces is maintained.

The two flanges 8a and 8b of the two members constituting the cylinder 2 are provided with a pair of ears 1 at line symmetrical positions.
2 are provided. A connector member 13 is fixed to these ears 12 with rivets 14. A pipe joint mounting hole 15 is formed in the connector member 13, and a pipe joint 16 is mounted in the mounting hole 15 with an O-ring 17 mounted at its end. A flange portion 18 is formed at an end of the pipe joint 16, and the pipe joint 16 is prevented from coming off by inserting a pin 19 in a pin shape into the connector member 13 so as to press the flange portion 18. ing. Also, the pipe joint mounting hole 1
Reference numeral 5 indicates a hydraulic pressure supply passage 21 and an outer peripheral side cylindrical portion 7a provided inside the connector member 13 with respect to a groove 20 recessed by press molding on an inner surface of a flange portion 8b integral with the inner peripheral side cylindrical portion 7b. It is adapted to communicate with each other through a hole 22 formed in the integral flange portion 8a. The master cylinder is connected to one of the two connector parts 13 and the air vent plug is connected to the other.

The cylindrical piston 4, which is slidably received in the annular groove 3 in the axial direction, is liquid-tightly fitted in the annular groove 3 with a seal member 23 provided at the inner end thereof. From the axially outer end of the cylindrical piston 4, the cylindrical piston 4
A dust cover 24 that extends coaxially and integrally with the cylindrical piston 4 extends so as to cover the outer peripheral surface of the. The free end of the dust cover 24 is provided with a seal member 25 that is in sliding contact with the outer peripheral surface of the outer peripheral side cylindrical portion 7a to prevent dust from entering the sliding contact surface between the annular groove 3 and the tubular piston 4. To prevent.

On the outer peripheral surface of the dust cover 24, an axial groove 26 is provided at an axially symmetrical position, and the axial groove 26 has a projection 27 projecting radially inward from the connector member 13. Are engaged. The engagement between the axial groove 26 and the protrusion 27 prevents relative displacement of the cylinder 2 and the tubular piston 4 in the circumferential direction.

The release bearing 6 mounted on the bearing carrier 5 formed integrally with the cylindrical piston 4 has a self-aligning mechanism, and the contact flange 28 fixed to the inner race of the release bearing 6 has a diaphragm spring DS. It is arranged so as to come into contact with the central part of the evenly in the circumferential direction. Further, in order to secure the self-aligning function of the release bearing 6, the release bearing 6 is elastically supported in the axial direction with a wave washer 29 on the bearing carrier 5. This wave washer 2
9 is prevented from slipping off by hooking an engaging claw 31 formed at an end of a leg portion 30 integrally formed at a proper position on an outer peripheral portion thereof with a step portion 32 formed on an outer peripheral portion of the bearing carrier 5. ing.

A stretched portion 33 having a reduced diameter is formed at the end of the inner cylindrical portion 7b. The extending portion 33 surrounds the input shaft S and extends in the axial direction, and the inner peripheral wall of the bearing carrier 5 is slidably fitted on the outer peripheral surface thereof. At the end of the extending portion 33, a plurality of (three in this embodiment) retaining claws 34 are formed by making a notch and expanding the tip outward in the radial direction. The tubular cylinder 2 is prevented from coming off.

Between the annular groove 35 formed between the inner peripheral side cylindrical portion 7b and the extending portion 33 and the bottom wall of the bearing carrier 5, displacement is caused according to wear of the clutch facing (not shown). The preload spring 36 is contracted so as to push out the release bearing 6 following the inner end position of the diaphragm spring DS. This allows
The cylindrical piston 4 is always elastically urged with a low load in the pushing direction.

Next, the operating procedure of the above embodiment will be described. When the clutch pedal is not depressed, that is, when the hydraulic pressure does not act on the tubular piston 4, the tubular piston 4 is recessed in the annular groove 3, and the release bearing 6 is pressed by the diaphragm spring DS to transmit the transmission. It is on the housing TH side. In this state, the pressure plate (not shown) presses the clutch disc toward the flywheel by the reaction force of the diaphragm spring DS, and the power of the engine is transmitted to the transmission. As the clutch disc wears, the central portion of the diaphragm spring DS is displaced toward the transmission housing TH and the amount of the cylindrical piston 4 sinking into the annular groove 3 increases. The state shown by the solid line on the side shows the state in which the clutch disc is completely worn and the cylindrical piston 4 is fully immersed in the annular groove 3, and when the clutch is engaged in the initial state, it is shown by the imaginary line. The cylindrical piston 4 is adapted to be retracted to a position approximately in the middle of the annular groove 3.

A hydraulic pressure from a master cylinder (not shown) enters the annular groove 3 through the hydraulic pressure supply passage 21 to the hole 22 to the groove 20 via the one pipe joint 16 and pushes out the cylindrical piston 4. As a result, the cylindrical piston 4
The release bearing 6 is pushed out together with the bearing carrier 5 formed integrally with the diaphragm spring D.
The central portion of S is pressed to release the pressing force of the pressure plate. This disengages the clutch disc from the flywheel and interrupts the transmission of engine power to the transmission.

The rotation preventing means between the cylinder 2 and the cylindrical piston 4 is, as shown in FIGS. 4 and 5, a plurality of grooves (or protrusions) 37 extending along the axial direction on the outer peripheral surface of the extending portion 33. Is provided, and the corresponding protrusion (or groove) 3
It is also possible to provide 8 on the inner peripheral surface of the bearing carrier 5 and regulate the relative circumferential displacement of the cylinder 2 and the tubular piston 4 by their engagement.

[0025]

As described above, according to the present invention, since the brake fluid supply groove is formed by press molding on the joint surface of the flange portion integrally formed with the two members constituting the cylinder, the cylindrical piston It is not necessary to sandwich another member between the flanges to form a passage for introducing the hydraulic pressure at the end. Therefore, a great effect can be achieved in reducing the axial dimension of the release cylinder device. In addition, since the inner cylindrical portion that constitutes the cylinder is extended to form a guide with which the bearing carrier that is integrally formed with the cylindrical piston slides, the sliding smoothness of the cylindrical piston does not depend on its rigidity. Can be secured. Therefore, a great effect can be achieved in reducing the weight of the cylindrical piston.

[Brief description of drawings]

FIG. 1 is a side view of a clutch release cylinder device according to the present invention.

FIG. 2 is a vertical sectional view taken along the line II-II in FIG.

3 is a partial vertical cross-sectional view taken along the line III-III in FIG.

FIG. 4 is a partial vertical cross-sectional view showing another embodiment.

5 is a partial vertical cross-sectional view taken along the line VV in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Clutch release cylinder device 2 Cylinder 3 Annular groove 4 Cylindrical piston 5 Bearing carrier 6 Release bearing 7a, 7b Cylindrical part 8a, 8b Flange part 10 O-ring 11 Ear plate 12 Ear part 13 Connector member 14 Rivet 15 Pipe joint mounting hole 16 Pipe joint 17 O-ring 18 Collar 19 Pin 20 Groove 21 Hydraulic supply passage 22 Hole 23 Seal member (for piston) 24 Dust cover 25 Seal member (for dust cover) 26 Axial groove 27 Protrusion 28 Contact flange 29 Wave washer 30 Leg Part 31 Engaging Claw 32 Step Part 33 Extended Part 34 Stopper Claw 35 Annular Groove 36 Preload Spring 37 Groove 38 Ridge S Input Shaft DS Diaphragm Spring TH Transmission Housing

Claims (2)

[Claims] 1. A cylinder comprising an annular groove deep in the axial direction of an input shaft of a transmission and coaxial with the input shaft; and a cylinder received in the annular groove and extruded by hydraulic pressure in the annular groove. A hydraulic clutch release cylinder device having a tubular piston and a release bearing mounted on an outer end in the axial direction of the tubular piston, wherein the cylinders are coaxial with each other with a gap for receiving the tubular piston. A tubular portion having different diameters, which are arranged in a double pattern inside and outside, and an outward flange portion formed at one end of each of these two tubular portions and overlapped with each other. A hydraulic clutch release cylinder device, characterized in that a groove through which brake fluid flows is recessed by press molding in at least one of the above. 2. A cylinder comprising an annular groove that is deep in the axial direction of the input shaft of the transmission and is coaxial with the input shaft; and a cylinder that is received by the annular groove and is extruded by the hydraulic pressure in the annular groove. A hydraulic clutch release cylinder device having a tubular piston and a release bearing mounted on an axially outer end of the tubular piston, wherein a bearing carrier of the release bearing is provided on an axially outer end of the tubular piston. In addition to being integrally formed, the cylinder has cylindrical portions of different diameters which are coaxially arranged inside and outside in a space to receive the cylindrical piston. A hydraulic clutch characterized in that an extended portion is formed at the other end of the inner portion, and the inner peripheral surface of the bearing carrier is slidably engaged with the outer peripheral surface of the extended portion. Release cylinder device.