JPH05263840A - Hydraulic pressure clutch and its connection control method - Google Patents

Abstract

PURPOSE:To smoothly connect a clutch to prevent passengers from feeling uncomfortable by increasing, when a clutch disc moves to a position at a specified distance from a hydraulic device main, resistance to the movement to rapidly increase hydraulic pressure applied to a piston, and detecting the increase of hydraulic pressure to limit the subsequent movement speed. CONSTITUTION:A piston moves a clutch disc 11 to the left with a pressure plate 10 while compressing a release spring 60. When the clutch disc 11 moves to a position at a specified distance from a friction member 21, a boss part 11a abuts a trigger spring 61 with a larger spring constant than that of the release spring 60, increasing the movement resistance of the clutch disc 11 operated by a hydraulic device 12. At this point, a sudden increase in hydraulic pressure is mechanically detected, converted into an electric signal, and inputted to a control device such as a computer. This constitution controls hydraulic pressure to reduce the subsequent movement speed of the clutch device for its smooth connection.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pressure-bonding type clutch and a connection control method therefor, and more particularly, when the clutch is connected, the hydraulic control is ideally performed immediately before the clutch connection, and the clutch connection is impacted. The present invention relates to a hydraulic pressure-bonding type clutch and a connection control method for the hydraulic pressure-bonding type clutch that are performed extremely smoothly.

[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 of the oil becomes extremely large, the clutch will be disengaged, so-called clutch drag will occur, and the torque due to this clutch drag will increase, making it difficult for the gear to enter, or difficult to disengage even if it enters. Sometimes occurred.

[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 it is adjusted so as to be located at the center of the pressure plate, the clutch disc will be biased toward the main body at high temperature, and if it is adjusted at high temperature, the clutch disc will be biased toward the pressure plate at low temperature.
As a result, the clutch becomes slow to connect and disconnect, which makes it impossible to perform a speed change operation, or causes the clutch to drag.

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. The clutch disc is operated by pressing the clutch disc between the pressure plate and the main body. 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 engagement was rapid. There is a problem in that the connection of the clutch causes an impact. 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 to eliminate the above-mentioned drawbacks of the prior art, and its purpose is to provide a clearance between the boss portion of the clutch disc and the main body of the hydraulic system. A release spring for urging the clutch disc to disengage from the main body of the hydraulic system, and the boss portion of the clutch disc comes into contact with the clutch disc when the clutch disc approaches the main body of the hydraulic system for a predetermined distance to prevent movement of the boss portion. A ring for pressing the pressure plate increases the resistance of the clutch disc with respect to the input shaft when the clutch disc comes close to the main body by a predetermined distance, that is, immediately before the engagement of the clutch, by mounting the trigger spring for increasing. Of the hydraulic pressure that acts on the piston in the shape of a cylinder, detects the hydraulic pressure rise, and detects the subsequent clutch. It is to control the moving speed of the disc so that the clutch can be smoothly engaged, and thus the impact due to the engagement of the clutch is prevented so that the driver and other occupants do not feel uncomfortable. It is to be.

Another object is to dispose a release spring for urging the clutch disc so as to disengage from the main body, between the boss portion of the clutch disc and the main body.
When the clutch is disengaged, the clutch disc is quickly disengaged from the main body, and the clutch disc is always located in the center between the main body of the hydraulic system and the pressure plate regardless of the temperature. The purpose is to prevent dragging so that gears can be put in and out easily.

[0010]

In summary, according to the method of the present invention (claim 1), a main body of a hydraulic system in which a clutch disc mounted axially movably to an input shaft is fixed to a crankshaft of an engine. When a predetermined distance is approached, the pressure plate for slidably contained inside the cylinder chamber fixed to the main body by increasing the resistance force of the movement of the clutch disc with respect to the input shaft by mechanical means. A sudden increase in the hydraulic pressure acting on the ring-shaped piston is detected, and the moving speed of the clutch disc is controlled thereafter by detecting the increase in the hydraulic pressure so that the clutch is controlled to be smoothly connected. It is what Further, the present invention (claim 2) includes a main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc mounted movably in an axial direction of an input shaft, and a boss portion of the clutch disc. A trigger spring that is mounted between the main body and the clutch disc to increase the resistance of the movement of the boss when the clutch disc comes close to the main body by a predetermined distance. It is a feature. According to the present invention (claim 3), a main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc mounted movably in an axial direction of an input shaft, and a boss portion of the clutch disc. A release spring that is mounted between the main body and urges the clutch disc to disengage from the main body, and the clutch when the clutch disc is close to the main body by a predetermined distance. And a trigger spring having a spring constant larger than that of the release spring, with which the boss portion of the disk abuts to increase the resistance of the movement of the boss portion. The present invention (claim 4) is
The main body of the hydraulic device fixed to the crankshaft of the engine, the clutch disc mounted movably in the axial direction with respect to the input shaft, and the clutch disc mounted between the boss portion of the clutch disc and the main body. A release spring portion for urging the clutch disc away from the main body and a boss portion of the clutch disc come into contact with each other when the clutch disc comes close to the main body by a predetermined distance to increase resistance to the movement of the boss portion. And a star spring integrally formed with a trigger spring portion having a spring constant larger than that of the release spring portion.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the embodiments shown in the drawings. 1 to 4, a hydraulic pressure-bonding type clutch 1 according to the present invention includes a main body 14 of a hydraulic device 12 fixed to a crankshaft 6 of an engine (not shown), a clutch disc 11, a release spring 60, and Trigger spring 61
It has and.

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 a pressure plate 10 to a 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, and is fixed to the main body 14 by a bolt 22. Inside the cylinder chamber 15b and an oil passage 15c communicating with the cylinder chamber 15b are formed. 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. The oil discharged from the vane pump is supplied under high pressure from the high pressure side oil gallery 18g formed in the boss portion 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, the 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.

Referring also to FIG. 2, the vane pump 18 is fixed to the clutch housing 5 with bolts 28, and its main body 18e is divided into three parts and joined with bolts 29.
The rotor 30 is internally provided with the bush 31 and the sleeve 1
It is rotatably accommodated by being supported by 8a. The rotor 30 is housed in a ring 32, and the inner surface 32a of the ring has a plurality of radial grooves 30 formed in the rotor.
The vane 33 slidably accommodated in a slides while coming into contact with the centrifugal force due to the rotation, so that the oil can be compressed while keeping the airtightness. Notches 30b for power transmission are formed at two locations on the inner peripheral surface of the rotor 30, and the ends 26b of the retainer 26 engage with the notches so that power is transmitted from the retainer to the rotor 30. ing.

The center of the ring 32 and the center of rotation of the rotor 30 are eccentric by a predetermined eccentric amount, and this eccentric amount is variable. That is, a compression spring 34 for setting a pressure that presses and urges the ring pressing pin 47 is housed in a cover 36 fixed to the main body by a bolt 35 on the side of the main body 18e of the vane pump 18, and the compression spring 34 is attached to the ring. By being compressed by 32, the amount of eccentricity is reduced. A stopper 37 is fixed to the inner peripheral surface of the body 18e of the vane pump 18, and the ring 32 is fixed by the stopper 37.
The vertical position of is set.

Next, the structure of the valve device 54 using the shape memory alloy compression spring 53 will be described. The valve device is mounted at three positions at equal intervals in the circumferential direction of the piston 16 and the transmission of the piston 16 is installed. Side 1
6b is formed so as to be completely contained in the recessed portion 16c formed therein, and is configured so as not to project from the side surface 16b at all, and the valve body 50, the biasing compression spring 52, and the shape memory alloy compression spring 53. Consists of.

The valve body 50 slides in the direction opposite to the crankshaft 6 (transmission side) and its tip 50a.
Is configured to block the communication hole 15d and limit the stroke of the piston 16, and is formed in a hollow shape, and the cylindrical portion 50
b, a flange portion 50c formed at one end of the cylindrical portion, a valve portion 50d formed at the tip 50a, and a hole 50e for accommodating the shape memory alloy compression spring 53.
The diameter of 0d is formed larger than the diameter of the communication hole 15d, and when the valve portion is pressed against the communication hole 15d, the communication hole is blocked by the tip 50a.

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.
Is attached to the cylindrical portion 50b of the
And the other end 52b of the other end 52b abuts on a lid member 55 formed in a substantially rhombic shape having the same shape as the recess 16c and is accommodated in the recess 16c. 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 lid member 55 has a hole 55a into which the cylindrical portion 50b of the valve body 50 is fitted, and is fixed to the piston 16 by two screws, and the surface of the lid member 55 is fixed when the lid member is mounted on the piston 16. The side surface 16b of the piston 16 is flush with the side surface 16b.

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, which are the main part of the present invention, will be described. First, the first embodiment will be described. In FIGS. 1 and 3 to 6, the release spring 60 is a normal metal spring, and has a large diameter portion 60a to a small diameter portion 60.
It is formed in a truncated cone shape or a dish shape that gradually becomes smaller toward b, and is mounted between the main body 14 and the boss portion 11a of the clutch disk 11 so that the clutch disk 11 can be inserted into the cylinder 15.
It is configured to press and urge toward.

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 S ₁ (see FIG. 4) which is reduced at high temperature. From the clutch disc 11 to the main body 1 of the hydraulic device 12
The distance t ₁ to the friction member 21 forming a part of 4 and the distance t ₂ to the pressure plate 10 are substantially equal to each other in the 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 that gradually decreases from the large diameter portion 61a to the small diameter portion 61b, and the main body 14 and the clutch disc are formed. 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 second embodiment will be described. In FIGS. 7 and 8, the release spring 60 and the trigger spring 61 have large diameter portions 60a and 61a, respectively, as in the first embodiment.
Is formed as four conical claws 60c, 61c that gradually decrease from the small diameter parts 60b, 61b toward the small diameter parts 60b, 61b, and the spring force is adjusted to an ideal value by adjusting the width of the claws. It is configured to be able to.
Then, similarly to the first embodiment, the main body 14 and the clutch disc 11 are mounted so as to overlap each other between the boss portion 11a.

Next, a third embodiment will be described. The release spring and the trigger spring are integrally formed as a star spring 62 with reference to FIGS. 11 to 15.
A release spring 62a is formed as four long pawls arranged at 90 ° intervals, and a trigger spring 62b is formed as four short pawls arranged at 90 ° intervals with a phase shift of 45 ° from the release springs. The main body 14 and the clutch disc 11
It is installed between and. Since the other construction is the same as that of the first embodiment, the same parts are designated by the same reference numerals in the drawings and the description thereof is omitted.

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. When the engine rotates, crankshaft 6, flex plate 9,
The main body 14, the cylinder 15, and the retainer 26 of the hydraulic device 12.
Also, the rotor 30 of the vane pump 18 rotates at the same speed, and the increased pressure 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 operates 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 in 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 and the space 1
The pressure plate 10 and the piston 16 can be pushed back to the right in the drawing by the low pressure oil pressure in 2a to disengage the clutch.

Next, the operation of the valve device 54 using the shape memory alloy compression spring 53 will be described. 1, FIG. 3, FIG. 4, FIG. 11 and FIG. 12, at the time of high temperature, the shape memory alloy compression spring 53 strongly tries to return to its memorized form, so that the valve body 50 is pressed and the valve body 50 is pressed. The valve portion 50d of the tip 50a of the cylinder abuts on the communication hole 15d of the cylinder 15. As a result, the communication hole 15d becomes the tip 50 of the valve body 50.
It is shielded by a, the cylinder chamber 15b is hydraulically locked, the stroke of the piston 16 is limited, the pressure plate 10 approaches the clutch disc 11, the gap between the pressure plate 10 and the clutch disc 11 becomes small, and the clutch It becomes possible to promptly connect and disconnect.

At low temperature, the shape memory alloy compression spring 53 loses the force to return to its memorized form. Therefore, 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
1 becomes larger, and thus, even if the viscosity of the oil increases at low temperatures, the clutch can be prevented from being dragged, the clutch can be completely disengaged, and the gears can be put in and out easily. As a result, the load on the actuator or the like using air can be reduced.

Next, the operation of the release spring 60 and the trigger spring 61 of the present invention will be described with reference to FIGS. When the pressure oil is supplied in the direction of arrow A, the piston 16 moves leftward in the figure together with the pressure plate 10, and the pressing force of the release spring (in the figure) while compressing the clutch disc 11 and the release spring 60. Against (right direction), move to the left in the figure. The movement of the clutch disc 11 and the state of the hydraulic pressure acting on the piston 16 at this time will be described with reference to FIGS. 9 and 10 as well.
Since the spring force is not so strong, the hydraulic pressure is almost constant without increasing, and the clutch disc 11 moves leftward in the figure at a relatively constant speed.

Then, when the clutch disc 11 approaches the friction member 21 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 has a spring constant larger than that of the release spring 60. Since it comes into contact with the trigger spring 61 having the clutch disc 1
The movement resistance of 1 increases. Therefore, the hydraulic pressure is B (Fig. 10)
And the clutch disc 11 is further moved to the left in the figure while compressing the trigger spring to overcome the biasing force of the trigger spring 61. At this time, mechanically detect the sudden increase in the hydraulic pressure. Therefore, if this is converted into an electrical signal and input to a control device (not shown) such as a computer, the hydraulic pressure is controlled by the control device to slow down the moving speed of the clutch disc thereafter and the clutch is moved. Can be controlled to connect smoothly.

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 disc 11, the cylinder chamber 1
Since the hydraulic pressure in 5b disappears, the clutch disc 11 pressed by the release spring 60 and the trigger spring 61 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. The release spring 60 further moves to the right in the drawing, but when the stroke is high and the temperature is small as shown in FIG. 4, the clutch disc 11 is moved to the right in the drawing by the distance t ₁ by the operating force of the release spring 60. , And the clutch is disengaged by quickly moving to the center position of the stroke S ₁ .

When the stroke is large and the temperature is low as shown in FIG. 3, the operating force of the release spring 60 first moves the distance t _{1 to the} right in the drawing to quickly disengage the clutch, and then the low pressure filling the space 12a. Oil from the clutch disc 11, the body 14 and the pressure plate 1
Since it flows in during 0, the clutch disc 11 is further moved to the right in the figure (distance t ₃ ), positioned at the center of the stroke S ₂ , and the clutch is completely disengaged.

As described above, due to the action of the trigger spring 61, when the clutch is engaged, the clutch disc 11 is rapidly brought close to the main body 14, and then the moving speed of the clutch disc 11 is slowed to slowly move the clutch disc 11 to the main body 14. The friction member 21 can be pressed to smoothly connect the clutch without impact. When the clutch is disengaged, the release spring 60 acts so that the cylinder chamber 1
As soon as the hydraulic pressure in 5b disappears, the clutch disc 11
Is quickly disengaged from the friction member 21 of the main body 14 and the clutch is disengaged, so that the clutch can be quickly engaged and disengaged. Even if the viscosity of the oil increases at low temperature, the clutch disc 11 remains Since the release spring 60 surely disengages from the main body 14, the clutch can be prevented from being dragged, the clutch can be completely disengaged, and the gear engagement and the gear disengagement can be performed lightly.

Also, in the third embodiment shown in FIGS. 11 and 12, the release spring 60 and the trigger spring 61 are two.
The action of one spring is the release spring 6 of one star spring 62.
2a is different from the trigger spring 62b only in the point that it is performed, and therefore the description of the operation will be omitted.

[0042]

As described above, according to the present invention, the release spring for urging the clutch disc from the main body of the hydraulic device between the boss portion of the clutch disc and the main body of the hydraulic device and the clutch disc are hydraulically operated. Since the boss portion of the clutch disc comes into contact with the main body of the device for a predetermined distance to increase the resistance of movement of the boss portion, a trigger spring is mounted. Immediately before the connection, the resistance force of the movement of the clutch disc with respect to the input shaft is increased to cause a sharp increase in the hydraulic pressure acting on the ring-shaped piston for pressing the pressure plate, and the increase in the hydraulic pressure is detected and thereafter. This has the effect of controlling the moving speed of the clutch disc so that the clutch can be connected smoothly. Since this result can prevent the impact due to engagement of the clutch, there is an effect that does not give an unpleasant feeling to the driver or other occupants.

Since the release spring for urging the clutch disc to disengage from the main body is arranged between the boss portion of the clutch disc and the main body, the clutch disc quickly separates from the main body when the clutch is disengaged. The clutch disc can always be located in the center between the body of the hydraulic system and the pressure plate regardless of the temperature, and as a result, the clutch can be prevented from being dragged and the gears can be easily inserted and removed. The effect is that it can be done.

[Brief description of drawings]

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

FIG. 2 is a vertical sectional view of a vane pump.

FIG. 3 is an enlarged vertical sectional view of an essential part showing the action of the release spring of the first embodiment at a low temperature.

FIG. 4 is an enlarged vertical sectional view of an essential part showing the action of the release spring and the trigger spring of the first embodiment at a high temperature.

FIG. 5 is a perspective view showing front surfaces of a release spring and a trigger spring according to the first embodiment.

FIG. 6 is a perspective view showing the back side of the release spring and the trigger spring of the first embodiment.

FIG. 7 is a perspective view showing front surfaces of a release spring and a trigger spring according to a second embodiment.

FIG. 8 is a perspective view showing a back surface side of a release spring and a trigger spring of the second embodiment.

FIG. 9 is a diagram showing a state in which the moving speed of the clutch disc changes.

FIG. 10 is a diagram showing a state of change in hydraulic pressure acting on a piston.

FIG. 11 is an enlarged longitudinal sectional view of an essential part showing the action of the release spring of the third embodiment at a low temperature.

FIG. 12 is an enlarged vertical sectional view of an essential part showing the action of the release spring and the trigger spring of the third embodiment at a high temperature.

FIG. 13 is a front view showing a release spring and a trigger spring according to a third embodiment.

FIG. 14 is a perspective view showing a front side of a release spring and a trigger spring according to a third embodiment.

FIG. 15 is a perspective view showing the back surface side of a release spring and a trigger spring of the third embodiment.

[Explanation of symbols]

 1 Hydraulic Crimping Clutch 6 Crank Shaft 11 Clutch Disc 11a Boss 14 Body of Hydraulic System 15b Cylinder Chamber 16 Piston 20 Input Shaft 60 Release Spring 61 Trigger Spring 62 Star Spring 62a Release Spring 62b Trigger Spring

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[Procedure amendment]

[Submission date] March 24, 1993

[Procedure Amendment 1]

[Document name to be corrected] Drawing

[Correction target item name] All drawings

[Correction method] Change

[Correction content]

[Fig. 2]

[Figure 5]

[Figure 6]

[Figure 9]

FIG. 15

[Figure 1]

[Figure 7]

[Figure 8]

[Figure 10]

[Fig. 13]

FIG. 14

[Figure 3]

[Figure 4]

FIG. 11

[Fig. 12]

Claims (4)

[Claims] 1. When a clutch disc mounted movably in the axial direction of an input shaft approaches a main body of a hydraulic device fixed to a crankshaft of an engine by a predetermined distance, the clutch disc of the clutch disc is mechanically operated. By increasing the resistance force of the movement with respect to the input shaft, the hydraulic pressure acting on the ring-shaped piston for pressing the pressure plate slidably contained in the cylinder chamber fixed to the main body is rapidly increased. A connection control method for a hydraulic pressure-bonding type clutch, characterized in that the increase in hydraulic pressure is detected, and the moving speed of the clutch disc thereafter is controlled to smoothly connect the clutch. 2. A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc mounted on an input shaft so as to be movable in an axial direction thereof, and between a boss portion of the clutch disc and the main body. And a trigger spring that increases the resistance to the movement of the boss portion of the clutch disc when the clutch disc comes close to the body by a predetermined distance. Formula clutch. 3. A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc mounted on an input shaft so as to be movable in an axial direction thereof, and between a boss portion of the clutch disc and the main body. A release spring that is attached to the main body and urges the clutch disc to disengage from the main body; and a boss portion of the clutch disc that is configured as a separate body from the release spring when the clutch disc approaches the main body for a predetermined distance. And a trigger spring having a spring constant larger than that of the release spring, which abuts to increase the resistance of the movement of the boss portion. 4. A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disc mounted on an input shaft so as to be movable in an axial direction thereof, and between a boss portion of the clutch disc and the main body. A release spring portion that is attached to the main body and urges the clutch disc to separate from the main body, and the boss portion of the clutch disc abuts when the clutch disc approaches the main body for a predetermined distance, and the boss portion moves. And a star spring integrally formed with a trigger spring portion having a spring constant larger than that of the release spring portion, which increases the resistance of the hydraulic pressure clutch.