JPH0571563A - Clutch brake device and control method therefor - Google Patents

Abstract

PURPOSE:To facilitate the clutch operation, speedily carry out the connection/ disconnection of a clutch, and carry out the light speed change operation by preventing the following turn of a clutch disc by pressing a brake disc onto a fixed member and suspending the revolution of an input shaft. CONSTITUTION:A clutch brake device 65 is equipped with the body 14 of a hydraulic device 12 fixed on the crank shaft 6 of an engine, clutch disc 11, brake disc 66, and a hydraulic cylinder 67. In this constitution, after the clutch disc 11 is separated from the body 1 of the hydraulic device 12 fixed on the crank shaft 6 by the clutch operation, the brake disc 66 installed on an input shaft 20 is pressed to a fixed member 68, and the following turn of the clutch disc 11 is prevented, and the revolution of the input shaft is suspended. Accordingly, the clutch operation is facilitated, and the connection/disconnection of the clutch is carried out speedily, and the light speed change operation can be carried out.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch brake device and a control method thereof, and more particularly, to a gear shifting operation after stopping the accompanying rotation of the input shaft due to the drag of the hydraulic clutch at a low temperature. And a control method thereof.

[0002]

2. Description of the Related Art Conventionally, a manual transmission type transmission or a transmission in which the manual transmission type is automatically changed by an actuator using a fluid pressure cylinder requires a mechanical clutch such as a dry type or a wet type. A hydraulic pressure-bonding type clutch has been proposed in order to improve the durability of the clutch and to quickly engage and disengage the clutch.

However, in the conventional hydraulic pressure-bonding type clutch, since the distance between the clutch cover and the clutch disc is always constant, the stroke of the piston for pressing the pressure plate is constant. Since the viscosity becomes extremely large, the clutch will be disengaged, so-called clutch drag will occur, the torque due to this clutch drag will increase, and problems such as difficulty in engaging the gear and difficulty in disengaging even if it enters There was a case to do.

[0006] One solution to this problem is as follows:
It is possible to increase the stroke of the piston, but this makes the clutch connection and disconnection slow at high temperatures,
This causes a problem that the speed change operation cannot be performed.

Another method is to change the stroke of the piston according to the temperature, that is, to reduce the stroke at high temperature and increase the stroke at low temperature. According to this method, the main body of the hydraulic system (exactly Indicates the position of the clutch disc when the clutch is disengaged, for example, when the piston stroke is large and the temperature is low, because the distance between the friction member fixed to the main body and the pressure plate fixed to the piston changes depending on the temperature. If the clutch disc is adjusted so as to be located at the center of the pressure plate, the clutch disc will be biased toward the main body side at high temperature, and if it is adjusted at high temperature, the clutch disc will be biased toward the pressure plate side at low temperature. The connection and disconnection of the gear becomes sluggish, and quick shift operation cannot be performed. Or Tsu, resulting in a problem arises that the dragging of the clutch occurs.

In order to solve the above problem, the applicant of the present application installed the shape memory alloy spring between the main body of the hydraulic device and the boss portion of the clutch disc to determine the position of the clutch disc when the clutch is disengaged. We have proposed a device that is always located in the center between the main body and the pressure plate regardless of the temperature.However, in order to make the clutch disc return force sufficiently large to ensure clutch disengagement, a shape memory alloy spring is used. This is disadvantageous in that the size is large, the cost is high, and the hydraulic crimp type clutch is large.

Further, in the conventional hydraulic pressure-bonding type clutch, a constant pressure oil is applied to a ring-shaped piston for pressing a pressure plate slidably contained in a cylinder chamber fixed to the main body of the hydraulic system. Then, the clutch disc is pressed between the pressure plate and the main body to connect the clutch. Since the movement resistance of the clutch disc was substantially constant over the entire stroke, the movement speed of the ring-shaped piston for pressing the pressure plate, that is, the movement speed of the clutch disc was constant, and the clutch was quickly connected. There is a problem that a shock is generated due to the engagement of the clutch. Further, in the above-mentioned configuration, since the hydraulic pressure does not change immediately before the clutch is engaged, it is impossible to slow the moving speed of the clutch disc thereafter and smoothly control the engagement.

[0008]

SUMMARY OF THE INVENTION The present invention has been made in order to eliminate the above-mentioned drawbacks of the prior art. The object of the present invention is to dispose a clutch disc in a main body of a hydraulic system (to be exact, the main body). The friction member fixed to the input shaft) to cut off the transmission of power from the crankshaft to the input shaft, and then press the brake disc against the fixed member to apply the braking force to the input shaft, thereby inputting with the accompanying rotation. This is to prevent the shaft from rotating reliably, and in particular, it eliminates the deterioration of the clutch disengagement due to the increase of the oil viscosity at low temperature and eliminates the difficulty of engaging and disengaging the clutch. The clutch operation is facilitated, and the clutch can be quickly engaged and disengaged so that a light shift operation can be performed.

[0009]

In summary, according to the method of the present invention (claim 1), the clutch disc is disengaged from the main body of the hydraulic device fixed to the crankshaft by the clutch operation, and then the brake disc mounted on the input shaft. Is pressed against a fixing member to prevent the clutch disc from rotating together and to stop the rotation of the input shaft. The present invention (Claim 2) is such that a main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc movably attached to an input shaft in an axial direction thereof, and an integral body to the input shaft. And a fluid pressure cylinder that presses the brake disc against a fixing member to stop the rotation of the input shaft. Is.

[0010]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the embodiments shown in the drawings. 1, a clutch brake device 65 according to the present invention is a crankshaft 6 of an engine (not shown).
It is provided with a main body 14 of the hydraulic device 12 fixed to the above, a clutch disc 11, a brake disc 66, and a fluid pressure cylinder 67.

First, the basic structure of the hydraulic pressure-bonding type clutch will be described. A crankshaft 6 of an engine (not shown) is rotatably fitted in the clutch housing 5 and protrudes into the clutch housing 5. A flex plate 9 is fixed to one end of the crankshaft 6 by a bolt 8, and a hydraulic device 12 for crimping the pressure plate 10 to the clutch disc 11 is fixed to the flex plate 9 by a bolt 13.

The hydraulic system 12 includes a body 14 and a cylinder 1.
5, a ring-shaped piston 16, and a vane pump 18, which is an example of a hydraulic pump. The main body 14 is formed in a circular shape so as to be rotatable together with the flex plate 9,
Fixed to the flex plate 9 with bolts 13,
At the center of the input shaft 2 via a bearing 19.
0 is rotatably mounted, and a friction member 21 is fixed to the facing surface 14a on the clutch disk 11 side.

The cylinder 15 is rotatably formed in a circular shape together with the main body 14, is fixed to the main body 14 by a bolt 22, and a cylinder chamber 15b and an oil passage 15c communicating therewith are formed inside. The cylinder chamber 15b and the oil passage 15c are connected by a communication hole 15d,
The oil passage 15c is a sleeve 18a of the vane pump 18.
Is rotatably supported by a bearing 23 and is communicatably connected to an oil passage 26a of a retainer 26 rotatably fitted in a boss portion 18b of the vane pump 18 through a plurality of seal members 24, 25. 26 is fixed to the cylinder 15 via a seal member 27.

The oil passage 26a of the retainer 26
Communicates with an oil gallery 18d that is in communication with an oil discharge port 18c of the vane pump 18 via an electromagnetic valve (not shown) housed in a solenoid valve housing 18f fixed to the boss 18b of the vane pump 18. , So that the oil discharged from the vane pump is supplied under high pressure from the high pressure side oil gallery 18g formed in the boss 18b through the communication hole 26d formed in the retainer 26 under the control of the solenoid valve. Is becoming The end of the oil passage 15c is sealed by a steel ball 15e.

The cylinder 15 has an oil passage 15c.
An oil passage 15f is formed at a circumferential position different from that of the oil passage 15f.
And an oil passage 26c formed at a circumferential position different from that of the oil passage 26a. The oil passage 26c is a solenoid valve (not shown) different from the above. Through the oil gallery 18d, the oil discharged from the vane pump 18 is controlled by the solenoid valve, and the low pressure side oil gallery 18h formed in the boss portion 18b passes through the communication hole 26e formed in the retainer 26. It is supplied to the space 12a at a low pressure,
The hydraulic pressure to disengage the clutch is obtained. Further, the oil in the space 12a is discharged from a communication hole 15h communicating with an oil suction port (not shown) of the vane pump 18 and sucked into the oil suction port of the vane pump 18.

The piston 16 is formed in a ring shape, a pressure plate 10 is fixed to a side surface 16a of the piston 16 on the clutch disc 11 side, and a seal member 17 is provided.
It is accommodated slidably in the cylinder chamber 15b in the horizontal direction via the, and is configured to press the pressure plate 10 against the clutch disc 11 by moving to the left in the drawing.

Next, the structure of the valve device 54 using the compression spring 53 made of shape memory alloy will be described. The valve device is mounted at three positions at equal intervals in the circumferential direction of the piston 16, and the piston 16 has the transmission side. Side of 16
It is designed to be completely accommodated in the concave portion 16c formed in b, and is configured so as not to project from the side surface 16b at all, and the valve body 50, the bias compression spring 52, and the shape memory alloy compression spring 53. Consists of.

The valve body 50 is slid toward the crankshaft 6 so that its tip 50a blocks the communication hole 15d and limits the stroke of the piston 16. It comprises a flange portion formed at one end of the portion, a valve portion formed at the tip 50a, and a hole for accommodating the shape memory alloy compression spring 53, and the diameter of the valve portion is formed larger than the diameter of the communication hole 15d. When the valve portion is pressed against the communication hole 15d, the communication hole is moved to the tip 50.
It is shielded by a.

The bias compression spring 52 is designed to bias the valve body 50 toward the piston 16 and is a normal metal spring that is not a shape memory alloy.
Of the valve body 50, one end of which is in contact with the flange portion of the valve body 50, and the other end of which is in contact with the lid member 55 formed in a substantially rhombic shape having the same shape as the recessed portion 16c so as to be in the recessed portion 16c. It is contained. The spring constant is weaker than the restoring force of the shape memory alloy compression spring 53 to the memory form (extended state), and the shape memory alloy compression spring 53 has a secondary permanent deformation processing form (compressed state). Is set to such a value that the compression spring made of the shape memory alloy can be compressed at the time of return.

The shape memory alloy compression spring 53 is used for the valve body 50.
It is stored in the hole 50e of the above, and is memorized so that the valve body 50 is pressed and urged toward the communication hole 15d to be expanded by a change in temperature. It is manufactured as a secondary permanent deformation processing form. That is, when the temperature exceeds a certain value, the shape memory alloy compression spring 53 tries to expand by generating a very strong extension force because the shape returns to the memory form, and when the temperature becomes less than the certain value,
The force for maintaining the stretched state is lost so that the secondary permanent deformation working form may be restored.

Shape memory alloys include Ni--Ti alloys and Cu.
Although roughly divided into -Zn-Al alloys, Cu-Zn-Al alloys are cheaper than Ni-Ti alloys, and have the advantages that they quickly follow changes in temperature, have a small hysteresis, and have a wide transformation temperature range. However, the Ni—Ti alloy is said to have a large amount of shape recovery, high durability (heat cycle) of about two digits, excellent functional properties, and high reliability. In the present invention, any of these alloys can be used for the shape memory alloy compression spring 53. Then, when the temperature is high, the compression spring 53 made of the shape memory alloy returns to its memorized form so that the valve body 5
0 makes the stroke of the piston 16 smaller by blocking the communication hole 15d and hydraulically locking the cylinder chamber 15b, and when the temperature is low, the compression spring 53 for biasing the shape memory alloy is compressed by the compression spring 52 for biasing so that the valve body 50 becomes a piston. 15d, the communication hole 15d is opened and the piston 16
Is configured to increase the stroke of the.

Next, the release spring 60 and the trigger spring 61 for operating the clutch disc will be described with reference to FIG.
In the above, the release spring 60 is a normal metal spring, and is formed in a truncated cone shape or a dish shape that gradually decreases from the large diameter portion 60 a to the small diameter portion 60 b, and the release spring 60 is formed between the main body 14 and the boss portion 11 a of the clutch disc 11. It is mounted between and is configured to press and urge the clutch disc 11 toward the cylinder 15.

That is, the clutch disk 11 is the cylinder 1
When pressed by 5, the release spring 60 is also compressed to press the clutch disk 11 toward the cylinder 15, and when the supply of pressure oil to the cylinder 15 is cut off,
The clutch disc 11 is moved toward the cylinder 15 by the release spring 60, and the position of the clutch disc at that time is adjusted so as to be at the center of the stroke which becomes smaller at high temperature. The distance to the friction member 21 that forms a part of the main body 14 of the device 12 and the distance to the pressure plate 10 are located at a substantially central portion.

The trigger spring 61 is an ordinary metal spring, and like the release spring 60, is formed in a truncated cone shape or a dish shape in which the diameter gradually decreases from the large diameter portion 61a to the small diameter portion 61b. 11 and the release spring 60 are overlapped and mounted between them, and the clutch disk 11 is pressed by the cylinder 15 to move,
When the distance between the main body 14 and the clutch disc 11 reaches a predetermined distance (for example, 0.5 mm), it comes into contact with the boss portion 11a of the clutch disc 11 to increase the movement resistance of the clutch disc 11.

Next, the clutch brake device 65, which is a main part of the present invention, will be described with reference to FIG. The clutch brake device 65 is for applying a braking force to the input shaft 20 to completely stop the input shaft 20,
It is composed of a brake disc 66 and a fluid pressure cylinder 67. The brake disc 66 has a disc shape, a female spline portion 66 a is formed in the center thereof, and a male spline portion 20 a formed on the input shaft 20.
And the friction member 6 on both sides.
6b is fixed. The friction member 66b is arranged so as to face the fixing member 68 fixed to the main body of the vane pump 18 fixed to the clutch housing 5 with the bolt 28 with the bolt 29.

In the fluid pressure cylinder 67, a ring-shaped piston 69 is slidably fitted in a ring-shaped cylinder chamber 5a formed in the clutch housing 5 and a pressure fluid is supplied to the oil passage 5b to supply the piston 69. Are moved to the left in the figure and are arranged opposite to each other.
6 is pressed against the fixing member 68 to apply a braking force to completely stop the rotation of the input shaft 20 due to the accompanying rotation. The solenoid valve 70 for connecting and disconnecting the oil supply to the cylinder chamber 15b and the cylinder chamber 5a
Clutch brake valve 71 for connecting and disconnecting the supply of oil to the
The shift valve 71 and the clutch switch 73 are electrically connected to a control device 78 including a central processing unit (CPU) 74, an external storage device 75 such as RAM and ROM, and a computer including an input / output port (I / O) 76. It is connected and controlled according to the command of the control device 78.

The method according to the present invention (claim 1) comprises:
After the clutch disc 11 is disengaged from the main body 14 of the hydraulic device 12 fixed to the crankshaft 6 by the clutch operation, the brake disc 66 mounted on the input shaft 20 is pressed against the fixing member 68 to rotate the clutch disc 11 together. Is to prevent the rotation of the input shaft 20.

The present invention is configured as described above,
The operation will be described below. First, the basic operation of the hydraulic pressure-bonding type clutch 1 will be described. In FIG.
When the engine rotates, the crankshaft 6, the flex plate 9, the main body 14 of the hydraulic device 12, the cylinder 1
5, retainer 26 and rotor 30 of vane pump 18
Rotate at the same speed, and the pressurized oil is discharged from the vane pump 18.

In the state shown in FIG. 1, the oil from the vane pump 18 passes through the low pressure side oil gallery 18h, the oil passage 26c, the oil passage 15f and the communication hole 15g,
Further, the pressure is reduced by the solenoid valve and is supplied only to the space 12a, and the space is filled with low-pressure oil.
c and the oil passage 15c are not supplied. Therefore, the pressure plate 10 and the piston 16 are pressed rightward in the figure by the low-pressure oil filled in the space 12a, the clutch disc 11 is released, and the clutch is disengaged.

When the clutch is engaged, the solenoid valve is operated to connect the discharge port 18c of the vane pump 18 to the oil passage 26a, and the high pressure side oil gallery 18g.
Through the communication hole 26d, the high-pressure oil flows into the oil passage 26a, and the high-pressure oil is supplied from the oil passage 26a to the oil passage 15c. Then, the oil flows into the cylinder chamber 15b through the communication hole 15d, high-pressure oil pressure is generated in the cylinder chamber, and the piston 16 moves leftward in the drawing together with the pressure plate 10, and the clutch disc 11 Is pressed against the friction member 21 of the main body 14, power is transmitted to the clutch disc 11, and the clutch is engaged.

Further, the oil of the vane pump 18 is prevented from being supplied to the oil passage 15c by the operation of the solenoid valve, so that the oil pressure in the cylinder chamber 15b disappears.
The low pressure hydraulic pressure in the space 12a can push the pressure plate 10 and the piston 16 back to the right in the drawing to disengage the clutch.

Next, the operation of the valve device 54 using the shape memory alloy compression spring 53 will be described. In FIG. 1, at a high temperature, the shape memory alloy compression spring 53 strongly tries to return to its memorized form, so that it presses the valve body 50 and the valve portion 50d of the tip 50a of the valve body causes the cylinder portion 15 to move.
15d of the communication hole. As a result, the communication hole 15d is blocked by the tip 50a of the valve body 50, and the cylinder chamber 15
b is hydraulically locked, the stroke of the piston 16 is limited, and the pressure plate 10
, The gap between the pressure plate 10 and the clutch disc 11 becomes small, and the clutch can be quickly engaged and disengaged.

At low temperatures, the shape memory alloy compression spring 53 loses the force to return to its memorized form, so the restoring force of the bias compression spring 52 is superior, and the shape memory is restored by the bias compression spring. Alloy compression spring 53
Is returned from the expanded state to the compressed state, that is, the secondary permanent deformation working state, and the tip 50a of the valve body 50 opens the communication hole 15d, so that the hydraulic lock of the cylinder chamber 15b is released. As a result, the stroke of the piston 16 increases, and the pressure plate 10 and the clutch disc 1
Therefore, even if the oil viscosity increases at low temperatures, the drag of the clutch can be considerably prevented, the clutch is disengaged, and the gear engagement and disengagement are performed smoothly. It is possible to reduce the load on the actuator or the like that uses air.

Next, the release spring 60 and the trigger spring 61
The action of will be described. When the pressure oil is supplied into the cylinder chamber 15b, the piston 16 moves the pressure plate 1
It moves to the left in the figure with 0, and clutch disc 1
1 is moved in the left direction in the drawing against the pressing force of the release spring (right direction in the drawing) while compressing the release spring 60. The movement of the clutch disc 11 and the state of the hydraulic pressure acting on the piston 16 at this time are almost constant without the hydraulic pressure rising because the spring force of the release spring 60 is not so strong. It moves to the left in the figure at a relatively constant speed.

The clutch disk 11 is the friction member 2
1 and the distance between the clutch disc 11 and the friction member 21 reaches a predetermined distance, for example, 0.5 mm, the boss portion 11a comes into contact with the trigger spring 61 having a spring constant larger than that of the release spring 60. Disk 11
The movement resistance of is increased.

Therefore, the hydraulic pressure rises and the trigger spring 61
The clutch disc 11 is further moved to the left in the figure while compressing the trigger spring, and this sudden increase in hydraulic pressure can be detected mechanically. If converted into a signal and input to a control device (not shown) such as a computer, the control device controls the hydraulic pressure to slow down the moving speed of the clutch disc and control the clutch to connect smoothly. can do.

When the supply of pressure oil to the oil passage 15c is cut off by the operation of the solenoid valve from the connected state of the clutch in which power is transmitted to the clutch disk 11, the cylinder chamber 1
Since the hydraulic pressure in 5b disappears, the clutch disc 1 is pressed by the release spring 60 and the trigger spring 61.
Although 1 is rapidly separated from the friction member 21 by about 0.5 mm by the action of the trigger spring 61 having a large spring force, it is further moved rightward in the figure by the action of the release spring 60.
When the stroke is high and the temperature is high, the clutch disc 11
Is further moved to the right in the figure by the operating force of the release spring 60, and is quickly moved to the center position of its stroke to disengage the clutch.

When the stroke is large and the temperature is low, the clutch disc 11 is first operated by the operating force of the release spring 60.
Is moved to the right in the figure to promptly disengage the clutch, and subsequently the low-pressure oil filled in the space 12a flows between the clutch disc 11 and the main body 14 and the pressure plate 10. The clutch is disengaged by moving 11 to the right in the figure to position it in the center of a large stroke.

As described above, the action of the trigger spring 61 causes the clutch disc 11 to rapidly approach the main body 14 when the clutch is engaged, and then the moving speed of the clutch disc 11 is reduced to slowly move the clutch disc 11 to the main body 14. The friction member 21 can be pressed to smoothly connect the clutch.

When the clutch is disengaged, as soon as the hydraulic pressure in the cylinder chamber 15b disappears due to the action of the release spring 60, the clutch disc 11 is quickly disengaged from the friction member 21 of the main body 14 and the clutch is disengaged. Since the clutch disc 11 is reliably disengaged from the main body 14 by the action of the release spring 60 even if the viscosity of the oil increases at low temperatures, the clutch can be dragged and disconnected quickly. It can be prevented considerably.

The operation of the clutch brake device 65 will now be described with reference to FIG. 3 as well. When a clutch pedal (not shown) is depressed and operated, the depression is detected by the clutch switch 73 in step S ₁ . It is transmitted to the control device 78.

In step S ₂ , the solenoid valve 70 is closed by the command from the controller 78 so as not to supply the oil to the oil passage 15c, so that the oil pressure in the cylinder chamber 15b disappears and the low pressure oil in the space 12a By the action of the release spring 60 and the trigger spring 61, the pressure plate 10 and the piston 16 are pushed back to the right in the figure, and the clutch is disengaged.

Although the clutch disc 11 is not accompanied by oil due to the action of the release spring 60 and the trigger spring 61 as described above, it may occur when the temperature is extremely low, which is completely prevented. Is difficult to do.

Next, at step S ₃ , the clutch brake valve 71 is opened to supply pressure oil to the ring-shaped cylinder chamber 5a, and the piston 69 is moved leftward in FIG. Is pressed against the fixing member 68, and a braking force is applied to the input shaft 20 by the frictional force between the friction member 66b and the fixing member 68 to completely stop the accompanying rotation of the input shaft 20.

In step S ₄ , it is confirmed whether the brake disc 66 is pressed and the operation of the clutch brake is completed. If the operation is not completed, the operation returns to the point A via the route R ₁ , Step S ₃ again
The clutch brake valve 71 is repeatedly opened.

Next, when the operation of the clutch brake is completed, the routine proceeds to step S ₅ , where the shift valve 71 is opened and the gear change is performed. Securely gear change in step S _6, i.e. after the shift was confirmed whether it has finished, if completed, the flow proceeds to step S _7, the supply of pressure oil to the cylinder chamber 5a closes the clutch brake valve 71 Then, the brake disc 66 is released from the pressing force of the brake disc 66 against the fixing member 68, and the braking action of the input shaft 20 is released.

If the shift is not complete, return to point B by route R ₂ . When the shift is completed, by the action of solenoid valve 70 in step S _8, it is moved to the left in FIG. 1 with the pressure plate 10 to the piston 16 by supplying high pressure oil to the cylinder chamber 15b,
The clutch disc 11 is pressed against the friction member 21 of the main body 14 to connect the clutch, and the shift is completed.

As described above, the gear change is performed in a state where the input shaft 20 is completely stopped by applying the braking force, so that it can be performed easily and quickly, and it is difficult to engage and disengage the clutch. Can be eliminated.

In the above embodiment, the clutch brake device 65 is connected to the trigger spring 61 and the release spring 60.
However, the present invention is not limited to the combined use of both devices, and the clutch / brake device 65 may be used alone.

[0050]

As described above, according to the present invention, the clutch disc is disengaged from the main body of the hydraulic system (more precisely, the friction member fixed to the main body) to interrupt the transmission of power from the crankshaft to the input shaft. After that, since the brake disc is pressed against the fixing member to apply the braking force to the input shaft, the rotation of the input shaft due to the accompanying rotation can be reliably prevented, and as a result, the viscosity of the oil at a low temperature can be prevented. The clutch disengagement caused by the rise can be eliminated, and the effect of eliminating the difficulty of engaging and disengaging the clutch and facilitating the clutch operation is provided. There is an effect that a light shift operation can be performed.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a hydraulic pressure-bonding clutch.

FIG. 2 is a block diagram showing a configuration of a clutch brake device and a control device.

FIG. 3 is a flowchart showing a routine of operation of the clutch brake device.

[Explanation of symbols]

 6 Crank Shaft 11 Clutch Disc 14 Main Body of Hydraulic System 20 Input Shaft 65 Clutch Brake Device 66 Brake Disc 67 Fluid Pressure Cylinder 68 Fixing Member

Claims (2)

[Claims] 1. A clutch disc is disengaged from a main body of a hydraulic device fixed to a crankshaft by a clutch operation, and a brake disc mounted on an input shaft is pressed against a fixing member to prevent the clutch disc from rotating together. A method for controlling a clutch brake, wherein the rotation of the input shaft is stopped. 2. A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc mounted movably in an axial direction of the input shaft, and integrally rotated with the input shaft. A clutch brake device comprising: a brake disc mounted movably in the axial direction; and a fluid pressure cylinder for pressing the brake disc against a fixing member to stop the rotation of the input shaft.