JPH04211730A - Hydraulic clutch release device - Google Patents

Abstract

PURPOSE:To hold a resilient force for pressing a release shaft bearing against a diaphragm spring, irrespective of an abrasion loss of a clutch disc. CONSTITUTION:When hydraulic pressure is introduced into a cylindrical space 3 in association with a depression of a clutch pedal, a release bearing 8 presses the center part of a diaphragm spring 1. A weak pressure set by a control valve 26 remains in the above-mentioned cylindrical space 3 even after the clutch pedal is released. Further, the release bearing 8 is kept slightly pressed against the diaphragm spring 1 under the above-mentioned weak hydraulic pressure.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION A hydraulic clutch release device according to the present invention is incorporated into a clutch mechanism of an automobile with a manual transmission, and is used to press the center of a diaphragm spring during a gear change operation.

0002

[Prior Art] In the clutch mechanism of a car with a manual transmission, when the engine's driving force is cut off from being transmitted to the transmission shaft in order to perform a gear shifting operation, the clutch pedal is depressed. By pressing the center of the diaphragm spring, which is shaped like a mortar, and changing the angle of the diaphragm spring, the force that presses the clutch plate against the flywheel is released, and the rotation of the flywheel is transmitted to the shaft on the transmission side. To enable gear switching operations without removing the gear.

[0003] When the gear change operation of the transmission is completed, when the foot is released from the clutch pedal, the clutch plate is pressed against the flywheel by the elasticity of the diaphragm spring, and the clutch is connected, and the engine is activated. The driving force will be transmitted to the wheels.

By the way, among the clutch release devices that are incorporated in the clutch mechanism configured as described above and press the center portion of the diaphragm spring during a gear shifting operation, there is a clutch release device that transmits the movement of the clutch pedal to the diaphragm spring using hydraulic pressure.
The hydraulic clutch release device has conventionally been shown in Fig. 8 or 9.
It is configured as shown in 10 to 10.

First, in FIG. 8 showing a first example of a conventional structure, 1 is a diaphragm spring, 2 is a transmission housing, and 3 is a rotating shaft. This rotating shaft 3 passes through the transmission housing 2 and rolls. The transmission housing 2 is rotatably supported by a bearing 4.

A cylindrical stationary sleeve 5 is provided around the rotating shaft 3, and one end of the stationary sleeve 5 is connected and fixed to the transmission housing 2.
A movable sleeve 6, which also has a short cylindrical shape, is supported at the distal end thereof so as to be freely displaceable in the axial direction (horizontal direction in FIG. 8).

A release bearing 8 is supported on a mounting flange 7 formed on the outer peripheral surface of the moving sleeve 6 via a short cylindrical case 9. The inner ring 10 of the release bearing 8, which is a deep groove ball bearing, is made to protrude beyond the outer ring 11 held in the case 9, and its tip surface (the left end surface in FIG. 8) is located at the center of the diaphragm spring 1. It hits the part.

Furthermore, the inner peripheral edge of the flange 12, which is formed by bending the distal end of the movable sleeve 6 inward, is brought into oil-tight sliding contact with the outer peripheral surface of the stationary sleeve 5. A cylinder space 13 is formed between the outer peripheral surface of the sleeve 5 and the inner peripheral surface of the movable sleeve 6, so that the fixed sleeve 5 and the movable sleeve 6 can function freely as release cylinders.

An oil supply passage 14 is provided inside the stationary sleeve 5, and one end of this oil supply passage 14 is connected to the cylinder space 13, and the other end is connected to a hydraulic pipe to generate hydraulic pressure when the clutch pedal is depressed. They are connected to the master cylinders that are connected to each other.

With the hydraulic clutch release device of the first conventional example configured as described above, when the clutch is disengaged to perform a gear shift operation, the hydraulic pressure generated as the clutch pedal is depressed is released. It is fed into the cylinder space 13 through the oil supply passage 14.

As a result, the moving sleeve 6 moves to the left in FIG. 8, and the release bearing 8 supported by the moving sleeve 6 moves to the left.
The tip end surface of the inner ring 10 is pressed against the center of the diaphragm spring 1, and the inclination angle of the diaphragm spring 1 changes.

When the clutch pedal is released upon completion of the gear shifting operation, the movable sleeve 6 moves to the right in FIG. 8 due to the elasticity of the diaphragm spring 1, and the clutch plate is pressed against the flywheel, causing the clutch is connected, and the driving force of the engine is transmitted to the wheels.

Between the front surface of the stationary sleeve 5 (left surface in FIG. 8) and the rear surface of the movable sleeve 6 (right surface in FIG. 8), there is a compression spring having a much smaller elasticity than the elasticity of the diaphragm spring 1. A spring 24 is provided so that even when the clutch pedal is released, the inner ring 1 constituting the release bearing 8
0 elastically presses the tip surface of the diaphragm spring 1 to prevent slippage between the tip surface and the diaphragm spring 1, and as the clutch pedal is depressed, the inner ring 10 immediately The diaphragm spring 1 is started to be pushed.

On the other hand, the second structure of the conventional structure shown in FIGS.
In this example, the release fork 15 presses the release bearing 8 against the center of the diaphragm spring 1.

That is, as shown in FIG.
The other end of the hydraulic piping 18, one end of which is connected to the master cylinder 17 that generates hydraulic pressure when the driver 6 is depressed,
It is connected to the release cylinder 19.

As shown in FIG. 10, this release cylinder 19 has a piston 21 inside a cylindrical cylinder case 20.
It is constructed by fitting them in an oil-tight manner. A pressure oil supply/discharge port 22 is provided at one end of the cylinder case 20 (the right end in FIGS. 9 and 10), and pressure oil can be freely fed into the cylinder case 20 through this supply/discharge port 22.

One end of a rod 23 is abutted against the other end surface of the piston 21, and the other end of the rod 23 is abutted against one end of the release fork 15. The release fork 15 has its middle portion pivoted, and its other end facing the center portion of the diaphragm spring 1.

With the conventional second example hydraulic clutch release device configured as described above, when the clutch is to be disengaged to perform a gear change operation, hydraulic pressure is applied to the master cylinder 17 by depressing the clutch pedal 16. This hydraulic pressure is generated and sent to the release cylinder 19 through the hydraulic piping 18.

As a result, the piston 21 within the cylinder case 20 of the release cylinder 19 moves to the left in FIGS. swing in the direction. As a result, the tip of the release fork 15 presses the center of the diaphragm spring 1, changing the inclination angle of the diaphragm spring 1.

When the clutch pedal is released upon completion of the gear shifting operation, the piston 21 moves to the right in FIGS. is connected, and the driving force of the engine is transmitted to the wheels.

A compression spring 25, which also has a much smaller elasticity than the diaphragm spring 1, is provided between the inner surface of one end of the release cylinder 19 and one end surface of the piston 21. Even when released, the tip end surface of the inner ring 10 (see FIG. 8) constituting the release bearing 8 is elastically pressed against the center of the diaphragm spring 1 to prevent slippage between the tip end surface and the diaphragm spring 1. In addition to preventing this from occurring, the inner ring 10 immediately starts pushing the diaphragm spring 1 when the clutch pedal 16 is depressed.

[0022]

However, the conventional hydraulic clutch release device constructed and operated as described above has the following problems.

That is, the pressing force applied to the moving sleeve 6 by the compression spring 24 (in the case of the first example shown in FIG. 8), or the pressing force applied to the piston 21 by the compression spring 25 (in the case of the first example shown in FIG. 9).
Even if the conditions (in the case of the second example shown in 10 to 10) are initially regulated to an appropriate range, the inclination angle of the diaphragm spring 1 changes due to wear of the clutch plate, and the position of the center of the diaphragm spring 1 changes. Change (move to the right in Figure 8, to the left in Figure 9)
Then, the compression springs 24 and 25 tend to be compressed, and the pressing force applied to the moving sleeve 6 and the release fork 15 by these compression springs 24 and 25 changes (increases).

Therefore, in order to prevent the force with which the compression springs 24, 25 press against the release bearing 8 from becoming excessive even when the clutch plates are worn out, the compression springs 24, 25 must be
It is conceivable to set the elasticity of No. 5 to a low value to reduce the pressing force when the clutch plate is new and has sufficient thickness.

On the other hand, if the initial pressing force is reduced, slippage will occur between the tip surface of the inner ring 10 constituting the release bearing 8 and the diaphragm spring 1 when the clutch plate is new. It has been difficult to design the compression springs 24 and 25 with appropriate elasticity, as there is a risk that abnormal noises may be generated.

The hydraulic clutch release device of the present invention includes:
This solves the above-mentioned inconveniences.

[0027]

[Means for Solving the Problems] The hydraulic clutch release device of the present invention, like the conventional clutch release device described above, includes a clutch pedal and a master cylinder that generates hydraulic pressure when the clutch pedal is depressed. ,
It consists of a hydraulic pipe connected at one end to the master cylinder, a release cylinder connected to the other end of the hydraulic pipe, and a release bearing that moves as pressure oil is introduced into the release cylinder.

Furthermore, in the hydraulic clutch release device of the present invention, the pressure on the release cylinder side is lower than the pressure on the master cylinder side, and the pressure on the release cylinder side is lower than the pressure on the master cylinder side. It is characterized by providing a control valve that opens only when the pressure on the release cylinder side is higher than the pressure on the master cylinder side by a certain amount.

[0029]

[Function] The hydraulic clutch release device of the present invention configured as described above presses the center part of the diaphragm spring to connect and disconnect the clutch plate and the flywheel. This is similar to the case of the type clutch release device.

However, in the case of the hydraulic clutch release device of the present invention, a constant hydraulic pressure always exists in the cylinder space due to the action of the control valve, and based on this constant hydraulic pressure, the moving sleeve Pressed by the diaphragm spring.

As a result, the force with which the diaphragm spring presses the release bearing supported by the moving sleeve remains constant regardless of the amount of wear on the clutch plate, causing slippage between the release bearing and the diaphragm spring. Things will go away.

[0032]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, the present invention will be explained in more detail with reference to the illustrated embodiments.

1 to 5 show a first embodiment of the present invention, FIG. 1 is a cross-sectional view showing the overall configuration, and FIGS. 2 to 5 show the operating status of the control valve. FIG. 3 is a corresponding enlarged cross-sectional view.

Similar to the first example of the conventional hydraulic clutch release device described above, a cylindrical stationary sleeve 5 is provided around the rotating shaft 3 which is rotatably supported by the transmission housing 2 via a rolling bearing 4. A movable sleeve 6 is supported on the outer periphery of the distal end of the fixed sleeve 5 so as to be freely displaceable in the axial direction, and a release bearing 8 is supported on a mounting flange 7 formed on the outer peripheral surface of the movable sleeve 6. ing. A cylinder space 13 is provided between the outer circumferential surface of the stationary sleeve 5 and the inner circumferential surface of the movable sleeve 6, and an oil supply passage 1 is provided inside the stationary sleeve 5.
One end of the cylinder 4 communicates with the cylinder space 13, and the other end communicates with the master cylinder 17 (see FIG. 9).

Furthermore, in the hydraulic clutch release device of the present invention, a control valve 26 is provided at the opening of the oil supply passage 14 on the outer peripheral surface of the proximal end of the stationary sleeve 5, and the control valve 26 is , are connected in series with the oil supply passage 14.

This control valve 26 is connected to the cylinder space 13.
When the pressure at the side is lower than the pressure at the port 27 portion communicating with the master cylinder 17, and when the cylinder space 1
It opens only when the pressure on the third side is higher than the pressure at the port 27 by a certain amount or more.

That is, as shown in detail in FIG. 2, this control valve 26 includes a short cylindrical check ball housing 29 in a housing 28 fixed to the outer peripheral surface of the stationary sleeve 5.
It is configured such that it can be freely displaced slightly in the axial direction (vertical direction in FIGS. 1 and 2). Oil-tightness between the outer circumferential surface of the check ball housing 29 and the inner circumferential surface of the housing 28 is maintained by an O-ring 30, and the check ball housing 29 is supported by a disc spring 31, which is an elastic pressing means. Therefore, the cylinder space 13 side (Fig. 1
2).

A valve seat portion 32 is provided in the check ball housing 29 so as to face the cylinder space 13 side, and the check ball 33 is pushed onto the valve seat portion 32 by a compression spring 34. It is elastically pressed towards the target. That is, the direction in which the compression spring 34 presses the check ball 33 and the direction in which the disc spring 31 presses the check ball housing 29 are opposite to each other.

Furthermore, a support ring 35 is fixed inside the housing 28 between the check ball housing 29 and the port 27, and a pin serving as a displacement prevention means is fixed at the center of the support ring 35. The proximal end of 36 is supported.

As shown in FIG. 4, when the check ball housing 29 moves upward in FIGS. By abutting against the check ball 33, the check ball 33 has a function of preventing movement and separating the check ball 33 from the valve seat portion 32.

The hydraulic clutch release device of the present invention configured as described above presses the inner circumferential portion of the diaphragm spring to connect and disconnect the clutch plate and the flywheel as follows. be.

That is, when the clutch is disengaged to perform a speed change operation, the hydraulic pressure generated in the master cylinder by depressing the clutch pedal is sent into the cylinder space 13 through the oil supply passage 14. At this time, the check ball 33 that constitutes the control valve 26 separates from the valve seat portion 32 against the elasticity of the compression spring 34, as shown in FIG.
The inner passage 39 is opened to allow pressure oil to be fed into the cylinder space 13 through the oil supply passage 14.

As a result, the moving sleeve 6 moves to the left in FIG. 1, and the release bearing 8 supported by the moving sleeve 6 moves to the left in FIG.
The tip end face of the inner ring 10 is pressed against the center of the diaphragm spring 1, and the inclination angle of the diaphragm spring 1 changes, causing the clutch plate and flywheel to separate.

When the clutch pedal is released upon completion of the gear shifting operation, the movable sleeve 6 is moved to the right in FIG. 1 by the elasticity of the diaphragm spring 1, and the clutch plate is pressed against the flywheel. , the clutch is connected, and the driving force from the engine is transmitted to the wheels via the transmission.

At this time, the hydraulic pressure in the port 27 is increased by the force applied to the moving sleeve 6 by the diaphragm spring 1 as the operating force applied to the clutch pedal is released. It also becomes more expensive.

As a result, the check ball housing 29 constituting the control valve 26 is connected to the disc spring 31 as shown in FIG.
However, since the check ball 33 hits the pin 36, the check ball 33 does not displace as much as the check ball housing 29, regardless of the elasticity of the compression spring 34.

Therefore, as shown in FIG. 4, the check ball 33 is separated from the valve seat 32, allowing the pressure oil in the cylinder space 13 to be returned to the master cylinder through the port 27.

As a result, when the oil pressure on the cylinder space 13 side decreases to a certain extent, the check ball housing 29
is returned by the elasticity of the disc spring 31, and as shown in FIG. 5, the check ball 33 comes into contact with the valve seat 32, and the pressure oil in the cylinder space 13 is no longer returned to the master cylinder. .

That is, in this state, the cylinder space 13
A pressure corresponding to the elasticity of the disc spring 31 remains inside. However, since the elasticity of the disc spring 31 is much smaller than that of the diaphragm spring 1, the elasticity of the diaphragm spring 1
The clutch is reliably engaged.

As described above, in the case of the hydraulic clutch release device of the present invention, a constant hydraulic pressure is always present in the cylinder space 13 according to the elasticity of the disc spring 31 due to the action of the control valve 26. Based on this constant oil pressure, the moving sleeve 6 is pressed against the center portion of the diaphragm spring 1.

As a result, the force pressing the release bearing 8 supported by the mounting flange 7 on the outer circumferential surface of the moving sleeve 6 against the diaphragm spring 1 is always constant regardless of the amount of wear on the clutch plate. There is no possibility of slippage occurring between the tip end surface of the inner ring 10 of 8 and the diaphragm spring 1.

Next, FIG. 6 shows a second embodiment of the present invention. In the case of this embodiment, the cylinder case 20 that constitutes the release cylinder 19 that communicates with the master cylinder 17 (see FIG. 9) via the hydraulic piping 18, that is, the end on the side where the supply/discharge port 22 is formed, is provided with the In one embodiment, a control valve 26 similar to that provided in oil supply passageway 14 (FIG. 1) is provided.

As described above, since the control valve 26 is provided at one end of the cylinder case 20, the cylinder space 37 existing between the control valve 26 and the piston 21 is filled with the air in the first embodiment. Similarly to the cylinder space 13 in the above, a constant oil pressure always exists depending on the elasticity of the disc spring 31 (see FIGS. 2 to 5 for details) that constitutes the control valve 26, and this constant oil pressure Based on this, the other end of the rod 23, which has one end in contact with the piston 12, is pressed against the central portion of the diaphragm spring 1.

As a result, the other end of the release fork 15 (see FIG. 9) connects the release bearing 8 to the diaphragm spring 1.
The pressing force is always constant regardless of the amount of wear of the clutch plate, and no slipping occurs between the tip surface of the inner ring 10 of the release bearing 8 and the diaphragm spring 1.

Next, FIG. 7 shows a third embodiment of the present invention. In the case of this embodiment, a housing 38 is connected in series to the hydraulic piping 18 at an intermediate portion (section B in FIG. 9) of the hydraulic piping 18 connecting the master cylinder 17 and the release cylinder 19, and the housing 38 is connected in series to the hydraulic piping 18. Within 38
A control valve 26 having the same structure as in the first to second embodiments is provided.

The housing 38 has a right end opening communicating with the master cylinder 17 in FIG. 7, and a left end opening communicating with the release cylinder 19 (see FIG. 9). The other configurations and operations are the same as in the first embodiment described above.

[0057] The control valve does not have to be integrated as in the illustrated embodiment; it can also be composed of a pair of check valves that open based on a pressure difference in opposite directions. . That is, the first check valve opens when the pressure on the master cylinder side is higher than the pressure on the release cylinder side, and the second check valve opens when the pressure on the release cylinder side is higher than the pressure on the master cylinder side by a certain amount. The above control valve can also be obtained by combining stop valves in parallel with each other.

[0058]

[Effects of the Invention] The hydraulic clutch release device of the present invention is configured and operates as described above, but since the release bearing can be pressed against the diaphragm spring with an appropriate pressing force regardless of the amount of wear on the clutch plate, It is possible to always prevent the occurrence of abnormal noises caused by slipping.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing the overall configuration of a first embodiment of the present invention.

[Fig. 2] A of Fig. 1 showing the first stage of the operation status of the control valve.
FIG.

FIG. 3 is a cross-sectional view similar to FIG. 2, also showing the second stage.

FIG. 4 is a cross-sectional view similar to FIG. 2, also showing the third stage.

FIG. 5 is a cross-sectional view similar to FIG. 2, also showing the fourth stage.

FIG. 6 is a sectional view of a release cylinder showing a second embodiment of the present invention.

FIG. 7 is a sectional view of a housing containing a control valve, showing a third embodiment of the present invention.

FIG. 8 is a half sectional view showing a first example of a conventional structure.

FIG. 9 is a schematic vertical sectional view showing a second example of a conventional structure.

FIG. 10 is a sectional view of a conventionally used release cylinder.

[Explanation of sign]

1 Diaphragm spring 2 Transmission housing 3 Rotation axis 4 Rolling bearing 5 Fixed side sleeve 6　Moving side sleeve 7 Mounting flange 8 Release bearing 9 Case 10 Inner circle 11 Outer ring 12　Trim section 13 Cylinder space 14 Refueling passage 15 Release fork 16 Clutch pedal 17 Master cylinder 18 Hydraulic piping 19 Release cylinder 20 Cylinder case 21 Piston 22 Supply/discharge port 23 Rod 24 Compression spring 25 Compression spring 26 Control valve 27 Port 28 Housing 29 Check ball housing 30 O-ring 31 Disc spring 32 Valve seat part 33 Check ball 34 Compression spring 35 Support ring 36 pin 37 Cylinder space 38 Housing 39 Passage

Claims (3)

[Claims] Claim 1: A clutch pedal, a master cylinder that generates hydraulic pressure when the clutch pedal is depressed, a hydraulic pipe connected at one end to the master cylinder, and a release cylinder connected to the other end of the hydraulic pipe. In a hydraulic clutch release device consisting of a release bearing that moves as pressurized oil is introduced into the release cylinder, the pressure on the release cylinder side is applied to the area between the master cylinder and the release cylinder. A hydraulic clutch release device comprising a control valve that opens only when the pressure on the release cylinder side is lower than the pressure on the master cylinder side and when the pressure on the release cylinder side is higher than the pressure on the master cylinder side by a certain amount. . 2. A release cylinder includes a peripheral surface of a cylindrical stationary sleeve that is fixed to the transmission housing while surrounding the rotating shaft, and a movable sleeve that is supported by the stationary sleeve so as to be freely displaceable in the axial direction. 2. The hydraulic clutch release device according to claim 1, wherein the release bearing is supported by the moving sleeve. 3. A control valve is provided within the housing so as to be slightly displaceable in the axial direction, and is directed toward a check ball housing that is pressed in one direction by an elastic pressing means and a valve seat within the check ball housing. When the elastically pressed check ball and the check ball housing move against the elasticity of the elastic pressing means in a direction opposite to the pressing direction of the elastic pressing means, the check ball is prevented from moving. Displacement preventing means for preventing the check ball from separating the valve seat portion from the valve seat portion.
2. The hydraulic clutch release device according to any one of 2.