JP2000220661A - Clutch device for automobile - Google Patents

Abstract

PROBLEM TO BE SOLVED: To surely release a clutch even if a load is increased in the releasing operation of the clutch by providing a hydraulic releasing means for opening a third oil chamber when a first piston is actuated in a prescribed quantity. SOLUTION: A hydraulic releasing means 66 interrupts the communication of a third oil chamber 603 with an overflow chamber 604 by seating a ball valve 665 in a valve seat 663 by the spring force of a compression coil spring 667 in the non-operation of a switching cylinder 6. When hydraulic fluid is supplied to the third oil chamber 603 to move a first piston 62 to the right by a prescribed quantity, a seal boot 669 mounted at the front end of a front piston 621 makes contact with the right end wall 611 of a cylinder body 61 to relatively move a bush rod 668 to the left. Consequently, the ball valve 665 is pressed to the left against the spring force of the compression spring 667 and separated from the valve seat 663, and the third oil chamber 603 is allowed to communicate through a first hole 661 and a communicating hole 664 and opened. Accordingly, even if the load is increased, the clutch can be released.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch device for a motor vehicle, and more particularly to a clutch device for a motor vehicle capable of performing an automatic operation and a manual operation.

[0002]

2. Description of the Related Art In a motor vehicle configured to transmit the power of an engine to a transmission via a friction clutch, a so-called automatic shifting of the transmission in accordance with an operating state (vehicle speed, accelerator opening, engine speed, etc.) Automobiles equipped with automatic transmissions have been put to practical use. In an automobile equipped with such an automatic transmission, it is necessary to automatically connect and disconnect the clutch in accordance with the shift control of the transmission, and the vehicle is equipped with an automatic clutch. In addition, automobiles equipped with an auto clutch that operates the transmission manually (manually) and automatically connects and disconnects the clutch in accordance with starting and shifting operations have been put to practical use.

[0003] In an automobile equipped with an auto clutch for automatically performing connection and disconnection operations according to the driving state,
The friction clutch connection / disconnection control during gear shifting can be performed smoothly, but the friction clutch connection / disconnection control cannot cope with starting under special conditions such as starting over obstacles, starting on extremely steep slopes, or starting on snowy roads. In some cases, the driver cannot start as intended. In order to solve such a problem, an automatic clutch configured to enable manual operation for starting under the above-mentioned special conditions has been put to practical use. As described above, the automobile clutch device capable of performing the automatic operation (automatic) and the manual operation (manual) includes a slave cylinder for connecting and disconnecting the friction clutch, a hydraulic supply mechanism for automatic operation as an operating mechanism of the slave cylinder, and a manual operation. The hydraulic supply mechanism for automatic operation or the hydraulic supply mechanism for manual operation is provided between the slave cylinder and the hydraulic supply mechanism for automatic operation and the hydraulic supply mechanism for manual operation. And a changeover valve for changing over.

[0004] The above-mentioned clutch device for an automobile, which enables the automatic operation and the manual operation, includes a hydraulic supply mechanism for the automatic operation and a hydraulic pressure for the manual operation in a state where the hydraulic oil is supplied to the slave cylinder and the friction clutch is disconnected. When the switching with the supply mechanism is performed, there is a problem that hydraulic oil flows between the two hydraulic supply mechanisms, and the amount of one hydraulic oil increases and the amount of the other hydraulic oil decreases. Japanese Patent Application Laid-Open No. 9-269021 discloses a proposal for preventing the occurrence of imbalance in the amount of hydraulic oil between the hydraulic supply mechanism for automatic operation and the hydraulic supply mechanism for manual operation.

The clutch device disclosed in Japanese Patent Application Laid-Open No. 9-269021 is operated by any one of a mechanism between a slave cylinder for connecting and disconnecting a friction clutch and a hydraulic supply mechanism for automatic operation and a hydraulic supply mechanism for manual operation. A switching cylinder is provided. The switching cylinder includes a cylinder body, a first piston and a second piston slidably disposed in the cylinder body, and an oil formed by the first piston and the cylinder body. A chamber is connected to the slave cylinder, an oil chamber is formed by the second piston and the cylinder body, an oil chamber is connected to the hydraulic supply mechanism for manual operation, and an oil chamber is formed by the first piston and the second piston and the cylinder body. The chamber is connected to a hydraulic supply mechanism for automatic operation. The automatic operation hydraulic supply mechanism is configured to switch to the manual operation hydraulic supply mechanism to enable the vehicle to travel when the automatic operation hydraulic supply mechanism is activated and the clutch is disengaged and fails. And a relief valve that opens at a predetermined pressure when the electric motor driving the hydraulic motor continues to operate and the pressure in the hydraulic circuit rises abnormally.

[0006]

SUMMARY OF THE INVENTION The above-mentioned Japanese Patent Application Laid-Open No. Hei 9
In the clutch device disclosed in JP-A-269021, it is difficult to set the valve opening pressure of the relief valve. That is,
When the vehicle is driven by activating the manual operation hydraulic supply mechanism when the automatic operation hydraulic supply mechanism fails, the clutch chamber is depressed and the oil chamber formed by the first and second pistons and the cylinder body is moved into the oil chamber. It is necessary to discharge the supplied hydraulic oil by opening the relief valve. At this time, if the valve opening pressure of the relief valve is high, a large pedaling force is required to operate the clutch pedal. Further, if the valve opening pressure of the relief valve is set high, the load on the electric motor that drives the hydraulic motor at the time of relief increases, causing problems such as generation of heat. If the opening pressure of the relief valve is set low in order to solve such a problem, if the load at the time of disengaging the clutch due to wear of the clutch facing increases, the relief valve must be released before the hydraulic pressure at which the clutch disengages is reached. However, there arises a problem that the clutch cannot be disengaged by opening the valve. Therefore, the valve opening pressure of the relief valve is such that the clutch can be disconnected even if the load when the clutch is disengaged is increased at the expense of the pedaling force of the clutch pedal and the load on the electric motor at the time of safety failure. At present, the pressure is set.

[0007] The present invention has been made in view of the above-mentioned facts, and its main technical problem is that the clutch pedal is not operated due to wear of the clutch facing without increasing the depressing force of the clutch pedal even at the time of failure. It is an object of the present invention to provide an automobile clutch device that can surely disconnect the clutch even when the load of the vehicle increases.

[0008]

According to the present invention, in order to solve the above-mentioned main technical problems, a slave cylinder for connecting and disconnecting a friction clutch, a hydraulic supply mechanism for automatic operation as an operating mechanism of the slave cylinder, and A hydraulic supply mechanism for manual operation, and a hydraulic supply mechanism for automatic operation or the hydraulic supply mechanism for manual operation, which is disposed between the slave cylinder and the hydraulic supply mechanism for automatic operation and the hydraulic supply mechanism for manual operation. An automotive clutch device comprising a switching cylinder selectively actuated, the switching cylinder comprising a cylinder body, a first piston and a second piston slidably disposed within the cylinder body. A first oil chamber formed by the first piston and the cylinder body and connected to the slave cylinder A second oil chamber formed by the second piston and the cylinder body and connected to the manual operation hydraulic supply mechanism, and formed by the first piston, the second piston, and the cylinder body. A third oil chamber connected to the hydraulic oil supply mechanism for automatic operation, and a hydraulic pressure release means for releasing the third oil chamber when the first piston operates by a predetermined amount. An automotive clutch device is provided.

The hydraulic pressure release means is formed through the first piston in the axial direction and communicates the third oil chamber with the oil tank side of the automatic operation hydraulic supply mechanism. And a valve mechanism for shutting off the communication of the hole and opening the hole when the first piston operates by a predetermined amount.

[0010]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a clutch apparatus for a vehicle constructed in accordance with the present invention.

FIG. 1 shows an embodiment of a clutch device for an automobile constructed according to the present invention. The clutch device in the illustrated embodiment includes a slave cylinder 3 for connecting and disconnecting the friction clutch 2, an automatic operation hydraulic supply mechanism 4 and a manual operation hydraulic supply mechanism 5 as operating mechanisms of the slave cylinder 3, and a slave cylinder 3. A switching cylinder 6 is provided between the automatic operation hydraulic supply mechanism 4 and the manual operation hydraulic supply mechanism 5. The friction clutch 2 includes a clutch driven plate 21 disposed on an input shaft of a transmission, a pressure plate 23 for pressing the clutch driven plate 21 against a flywheel 22 of an engine (not shown), and a pressure plate. And a clutch release fork 25 for operating the release 23 via a release bearing 24. When the above-described automatic operation hydraulic supply mechanism 4 and manual operation hydraulic supply mechanism 5 are not operated, the friction clutch 2 configured as described above causes the pressure of the pressure plate 23 to the left in FIG. The clutch facing 211 of the clutch driven plate 21 is frictionally engaged with the flywheel 22 and is maintained in contact with the flywheel 22. When the hydraulic supply mechanism 4 for automatic operation or the hydraulic supply mechanism 5 for manual operation is activated, the clutch release fork 25
1 is operated clockwise in FIG. 1 with the intermediate portion as a fulcrum 25a, and the pressure plate 23 moves rightward in FIG. 1 to frictionally engage the clutch facing 211 of the clutch driven plate 21 with the flywheel 22. Is released, and the friction clutch 2 is disconnected.

The slave cylinder 3 includes a cylinder body 31, a piston 32 slidably disposed in the cylinder body 31, and a piston rod 33 connected to the piston 32. The tip of 33 is engaged with the upper end of the clutch release fork 25 in FIG. When hydraulic oil is supplied to the hydraulic chamber 34, the piston 32 moves to the right in FIG. 1 in the slave cylinder 3 configured as described above, and the clutch release fork 25 is moved clockwise in FIG. Operate in the direction.

Next, the automatic operation hydraulic supply mechanism 4 will be described. The automatic operation hydraulic supply mechanism 4 in the illustrated embodiment includes a hydraulic pump 42 that is rotationally driven by an electric motor 41 as a drive source. The suction side of the hydraulic pump 42 is connected to the oil tank 43 by a pipe 401. The hydraulic oil discharged from the hydraulic pump 42 is sent to a third oil chamber (described later) of the switching cylinder 6 via the pipe 402, the check valve 44, and the pipe 403. The pipe 403 and the pipe 404 connected to the oil tank 43 are connected by pipes 405 and 406, and the pipes 405 and 406 are provided with solenoid valves 45a and 45b, respectively. Also,
One end of a pipe 407 is connected to the pipe 404, and the other end of the pipe 407 is connected to a later-described first oil chamber of the switching cylinder 6.

The manual operation hydraulic supply mechanism 5 includes:
The illustrated embodiment includes a clutch pedal 51 and a clutch master cylinder 52 operated by the clutch pedal 51. The hydraulic chamber 521 of the clutch master cylinder 52 is connected to a later-described second oil chamber of the switching cylinder 6 via the pipe 50.

Next, the switching cylinder 6 will be described.
The switching cylinder 6 in the illustrated embodiment includes a cylinder main body 61, and a first piston 62 and a second piston 63 slidably disposed in the cylinder main body 61. The first piston 62 includes a front piston 621
, A rear piston 622, and a connecting portion 623 connecting the front piston 621 and the rear piston 622. At the front end (right end in FIG. 1) of the front piston 621 of the first piston 62, a projection 623 having a small diameter is provided at the center, and at the rear end (left end in FIG. 1) of the rear piston 622. A projection 624 having a small diameter is provided at the center. The second piston 63 is provided with a small-diameter projection 631 at the center of the front end (right end in FIG. 1) and the small-diameter projection 6 at the center of the rear end (left end in FIG. 1).
32 are provided. The first piston 62 and the cylinder body 6 are provided in the cylinder body 61 provided with the first piston 62 and the second piston 63 configured as described above.
1, the first oil chamber 60 is formed by the right end wall 611.
1 is formed, and the second piston 63 and the cylinder body 61 are formed.
A second oil chamber 602 is formed by the plug 64 attached to the left end in the figure, and a third oil chamber 603 is formed by the first piston 62 and the second piston 63 cylinder body 61. An overflow chamber 604 is formed by the connection portion 623 of the first piston 62 and the cylinder main body 61.

A compression coil spring 65 is provided in the first oil chamber 601. The compression coil spring 65
The piston 62 and the second piston 63 are always urged to move to the left in the drawing. Compression coil spring 6
The first piston 62 and the second piston 63 urged to move leftward by 5 are maintained in a state where the second piston 63 is in contact with the plug 64 when not operating. The capacity of the first piston 62 in the first oil chamber 601 when the first piston 62 is not shown in FIG. 1 is equal to the capacity of the clutch master cylinder 52 when the clutch pedal 51 is at full stroke.

An outlet 612 communicating with the first oil chamber 601 is provided on the right end wall 611 of the cylinder body 61, and the outlet 612 is connected to the hydraulic chamber 34 of the slave cylinder 3 via the pipe 30. It is connected. Also, in the cylinder body 61, a return oil port 613 in which the first piston 62 communicates with the first oil chamber 601 in the non-operating state shown in FIG. Hydraulic oil inlet 614 and the third oil chamber 603
A hydraulic oil inlet 615 for automatic operation is provided which communicates with the hydraulic fluid. Further, the overflow chamber 604 is provided in the cylinder body 61.
An overflow port 616 is provided for communication with the fluid. Thus, the return oil port 613 and the overflow port 616 provided in the cylinder body 61 are connected to the pipe 407, the hydraulic oil inlet 614 for manual operation is connected to the pipe 50, and the hydraulic oil inlet 615 for automatic operation is connected. It is connected to the pipe 403.

The switching cylinder 6 configured as described above
Has hydraulic pressure release means 66 for releasing the third oil chamber 603 when the first piston 62 has moved rightward by a predetermined amount from the non-operation state shown in FIG. The hydraulic pressure releasing means 66 will be described with reference to FIG. The hydraulic pressure release means 66 in the illustrated embodiment is provided with the first piston 6
2 is incorporated. First piston 62
Is provided with a hole 660 penetrating in the axial direction. The hole 660 includes a first hole 661 formed from a rear end (left end in the figure) of the rear piston 622 to an intermediate portion of the connection portion 623, and a front end of the front piston 621 formed continuously with the first hole 661. The second hole 662 has a smaller diameter than the first hole 661 reaching the right end (in the figure, the right end in the figure), and a valve seat 663 is formed at a connecting portion between the first hole 661 and the second hole 662. ing. Then, a communication hole 66 formed in the connection portion 623 in the axial direction with the second hole 662 is formed.
4 communicates with the overflow chamber 604.
A ball valve 665 seated on the valve seat 663 is disposed in the first hole 661, and the ball valve 665 and a spring receiver 666 provided at the rear end (the left end in the figure) of the rear piston 622. A compression coil spring 667 is disposed between the compression coil spring 667 and the ball valve 665.
7 is always urged to be seated on the valve seat 663 by a spring force. The second hole 662 has a ball valve 66.
5 is provided so as to be slidable in the axial direction. The push rod 668 has a left end formed with a small diameter in the figure, and a right end in the figure protruding from a front end (right end in the figure) of the front piston 621. The ball valve 665, the compression coil spring 667, and the push rod 668 are valves that communicate the first hole 661 and the second hole 662 when the first piston 62 moves rightward in a predetermined amount from the state of FIG. 1. Make up the mechanism. Note that a seal boot 669 that covers the push rod 668 is attached to the tip of the protrusion 623 provided at the front end of the front piston 621.

The hydraulic release means 66 constructed as described above
When the switching cylinder 6 is not operated, the ball valve 665 is seated on the valve seat 663 by the spring force of the compression coil spring 667 as shown in FIG. 1, and the communication between the third oil chamber 603 and the overflow chamber 604 is established. Is shut off. When hydraulic oil is supplied to the third oil chamber 603 from the state shown in FIG. 1 and the first piston 62 moves a predetermined amount to the right in the figure, the seal boot 669 mounted on the front end of the front piston 621 is moved to the cylinder body 61. The push rod 668 is relatively moved leftward while contacting the right end wall 611. As a result, as shown in FIG. 2, the ball valve 665 is pushed to the left in the figure against the spring force of the compression coil spring 667 to be separated from the valve seat 663, and the third oil chamber 603 is in the first hole 661. And communication hole 6
It is communicated through 64 and is opened. In the illustrated embodiment, the ball valve 665 and the push rod 66
Although the example in which 8 is configured separately is shown, the valve and the push rod may be integrally configured.

The clutch device for a vehicle in the illustrated embodiment is configured as described above, and its operation will be described below. When the hydraulic supply mechanism 4 for automatic operation and the hydraulic supply mechanism 5 for manual operation do not operate, the first piston 62 and the second piston 63 of the switching cylinder 6 are positioned as shown in FIG. At this time, the first oil chamber 601 communicates with the return oil port 613, and the hydraulic pressure in the hydraulic chamber 34 in the slave cylinder 3 is released. Therefore, the friction clutch 2 is maintained in the contact state. When the state is switched to the manual operation from the state shown in FIG. 1 and the clutch pedal 51 is depressed, hydraulic oil flows from the clutch master cylinder 52 into the second oil chamber 602 of the switching cylinder 6 via the pipe 50. As a result, the second
The piston 63 and the first piston 62 move rightward in FIG. 1 against the spring force of the compression coil spring 65,
When the first piston 62 moves rightward, communication between the return oil port 613 and the first oil chamber 601 is interrupted, so that the hydraulic oil in the first oil chamber 601 is pressurized. As a result, the hydraulic oil in the first oil chamber 601 is sent to the hydraulic chamber 34 of the slave cylinder 3 via the pipe 30, and the piston 32 moves rightward in FIG. 1 to disconnect the friction clutch 2 as described above. . Then, the seal clutch 669 mounted on the protrusion 623 provided on the front piston 621 of the first piston 62 moves by a predetermined amount until the seal boot 669 comes into contact with the right end wall 611 of the cylinder body 61, thereby completely engaging the friction clutch 2. Can be turned off. Here the clutch pedal 51
Is released, the spring force of the clutch spring (not shown) of the friction clutch 2 causes the piston 32 of the slave cylinder 3 to move.
Is moved to the left in the figure, and the friction clutch 2 comes into contact. When the piston 32 of the slave cylinder 3 moves to the left in FIG. 1, the operating oil supplied to the hydraulic chamber 34 flows into the first oil chamber 601 of the switching cylinder 6 via the pipe 30. The first piston 62 and the second piston 63 are moved to the left in FIG. When the first piston 62 and the second piston 63 reach the inoperative position in FIG.
13 communicates with the first oil chamber 601 to release the hydraulic pressure, and the friction clutch 2 comes into complete contact.

Next, switching from the non-operation state of FIG. 1 to the automatic operation, and when the electric motor 41 is driven by the control signal from the control means (not shown) to operate the hydraulic pump 42, the hydraulic oil discharged from the hydraulic pump 42 Piping 40
2. The oil is sent to the third oil chamber 603 of the switching cylinder 6 via the check valve 44 and the pipe 403. At this time, the solenoid valves 46a and 46b are closed. When the operating oil flows into the third oil chamber 603 of the switching cylinder 6, the first piston 62 opposes the spring force of the compression coil spring 65 and the seal boot mounted on the protrusion 623 to the right in FIG. 669 is moved by a predetermined amount until it comes into contact with the right end wall 611 of the cylinder body 61, and the friction clutch 2 is disconnected as described above. At this time, as described above, the hydraulic release means 6
6 moves relatively to the left and pushes the ball valve 665 leftward in the figure against the spring force of the compression coil spring 667. As a result, the third oil chamber 603 becomes the first hole. 661 and the communication hole 664 are opened. In order to connect the friction clutch 2 from the disconnected state in this way, the electric motor 41 is stopped by a control signal from control means (not shown), and the electromagnetic valve 4
By controlling the opening and closing of 6a and 46b, the operating oil in the third oil chamber 603 is returned from the pipe 404 to the oil tank 43 via the electromagnetic valves 46a and 46b. Accordingly, the first piston 62 moves to the left in FIG. 1 by the spring force of the compression coil spring 65, so that the piston 32 of the slave cylinder 3 is moved by the spring force of the clutch spring (not shown) of the friction clutch 2 as described above. At 1, the friction clutch 2 is moved to the left and comes into contact.

In the clutch disengagement operation by the automatic operation hydraulic supply mechanism 4 described above, the third oil chamber 603 is not opened until the first piston 62 moves by a predetermined amount. Even if the load at the time of disengaging the clutch increases, the clutch can be reliably disengaged. After the clutch is completely disengaged, the third oil chamber 603 is opened as described above. Therefore, even if the electric motor 41 that drives the hydraulic pump 42 continues to operate, the load on the hydraulic pump 42 is small. The electric motor 41 does not generate heat.

In the above-described clutch disengagement operation by the automatic operation hydraulic supply mechanism 4, if the clutch is disengaged and the failure occurs in the state shown in FIG. 2, the clutch is switched to manual and the clutch pedal of the manual operation hydraulic supply mechanism 5 is operated. By depressing 51 to operate the clutch master cylinder 52, the operating oil flows into the second oil chamber 602 of the switching cylinder 6 via the pipe 50, and the second piston 63 is moved rightward in FIG. It is necessary to discharge the hydraulic oil in the third oil chamber 603. At this time, the third oil chamber 60
2 is released by the hydraulic pressure release means 66 as shown in FIG. 2, the hydraulic oil in the third oil chamber 603 is supplied to the first hole by the second piston 63 moving rightward in the figure. 661, communication hole 664, overflow chamber 604, overflow port 6
16, oil tank 4 via pipe 407 and pipe 404
Returned to 3. Therefore, the third oil chamber 603 as in the related art
Since it is not necessary to open the relief valve disposed in the hydraulic circuit to discharge the hydraulic oil in the clutch pedal 51,
Pedaling force is reduced.

Next, another embodiment of the sealing means provided on the protrusion 623 provided on the front piston 621 of the first piston 62 will be described with reference to FIG. An oil seal 70 having a hole in the center is mounted on the inner peripheral surface of the second hole 662 formed in the first piston 62 on the protruding portion 623 side. On the other hand, the second hole 66
The right end of the push rod 668 slidably disposed in FIG. 2 has a small diameter, and the small diameter portion 668a is slidably fitted in a hole formed in the center of the oil seal 70. The sealing means shown in FIG. 3 can be made more compact than the sealing boot 669 shown in FIGS.

[0025]

The vehicle clutch device according to the present invention is constructed as described above, and has the following effects.

That is, when the first piston of the switching cylinder disposed between the slave cylinder for connecting and disconnecting the friction clutch and the automatic operation hydraulic supply mechanism and the manual operation hydraulic supply mechanism is operated by a predetermined amount, the third piston is actuated. Since the oil pressure release means for opening the oil chamber is provided, the third oil chamber is not opened until the first piston moves by a predetermined amount when the clutch is disengaged by the automatic operation hydraulic supply mechanism. The clutch can be reliably disengaged even when the load at the time of disengaging the clutch increases due to wear of the shing. After the clutch is completely disengaged, the third oil chamber is opened, so that even if the electric motor driving the hydraulic pump continues to operate, the load on the hydraulic pump is small, so that the electric motor may not generate heat. Absent. In addition, when switching to the manual operation hydraulic supply mechanism when the clutch is disengaged by the automatic operation hydraulic supply mechanism, the third oil chamber is opened as described above. When the oil chamber is discharged, the depression force of the clutch pedal can be reduced.

[Brief description of the drawings]

FIG. 1 is a hydraulic circuit diagram showing an embodiment of a vehicle clutch device configured according to the present invention.

FIG. 2 is a sectional view showing an operating state of a switching cylinder provided in the clutch device of the vehicle shown in FIG.

FIG. 3 is an essential part cross-sectional view showing another embodiment of the switching cylinder.

[Explanation of symbols]

 2: Friction clutch 2 21: Clutch driven plate 211: Clutch facing 23: Presser plate 24: Release bearing 25: Clutch release fork 3: Slave cylinder 4: Hydraulic supply mechanism for automatic operation 41: Electric motor 42: Hydraulic pump 43: Oil tank 44: Check valve 45a, 45b: Solenoid valve 5: Hydraulic supply mechanism for manual operation 51: Clutch pedal 52: Clutch master cylinder 6: Switching cylinder 61: Cylinder main body 62: First piston 63: Second Piston 65: compression coil spring 66: hydraulic release means 665: ball valve 667: compression coil spring 668: push rod 669: seal boot 70: oil seal

Claims (2)

[Claims] 1. A slave cylinder for connecting and disconnecting a friction clutch, an automatic operation hydraulic supply mechanism and a manual operation hydraulic supply mechanism as an operation mechanism of the slave cylinder, the slave cylinder, the automatic operation hydraulic supply mechanism, and A switching cylinder disposed between the manual operation hydraulic supply mechanism and the automatic operation hydraulic supply mechanism or a switching cylinder selectively operated by the manual operation hydraulic supply mechanism; Is formed by the cylinder body, a first piston and a second piston slidably disposed in the cylinder body, and a first piston formed by the first piston and the cylinder body and connected to the slave cylinder. The manual operation formed by the first oil chamber, the second piston and the cylinder body. A second oil chamber connected to the hydraulic pressure supply mechanism for use, and a third oil chamber formed by the first piston, the second piston, and the cylinder body and connected to the hydraulic supply mechanism for automatic operation. A clutch release device for opening the third oil chamber when the first piston operates by a predetermined amount. 2. A hydraulic pressure release means, which is provided in the first piston, communicates the third oil chamber with the oil tank side of the automatic operation hydraulic supply mechanism, and is disposed in the hole. The vehicle clutch device according to claim 1, further comprising a valve mechanism that cuts off communication with the hole and, when the first piston operates by a predetermined amount, connects the hole.