JP2666000B2 - Hydraulic pressure type clutch and connection control method thereof - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic press-type clutch and a connection control method therefor. The present invention relates to a hydraulic pressure-type clutch and a connection control method for the hydraulic pressure-type clutch which can be performed extremely smoothly without any problem.

[0002]

2. Description of the Related Art Conventionally, a manual transmission type transmission or a transmission in which the manual transmission type transmission is automatically shifted by an actuator employing a hydraulic cylinder requires a mechanical clutch such as a dry type or a wet type. Hydraulic pressure-type clutches have been proposed to improve the durability of the clutch and to promptly connect and disconnect the clutch.

[0003] However, in the conventional hydraulic crimping type clutch, the distance between the clutch cover and the clutch disc is always constant, so that the stroke of the piston for pressing the pressure plate is constant.
Since the viscosity of the oil becomes very large, the clutch disengages poorly, causing a so-called clutch drag, which increases the torque caused by the drag of the clutch, making it difficult for the gear to be engaged or difficult to disengage when the gear is engaged. May occur.

[0004] One solution to this problem is to:
It is conceivable to increase the stroke of the piston, but this will cause the clutch connection and disconnection to become slow at high temperatures,
A problem arises in that it is not possible to perform a prompt shifting operation.

As another method, the stroke of the piston is changed depending on the temperature, that is, the stroke is reduced at a high temperature, and the stroke is increased at a low temperature. The distance between the friction plate fixed to the main body and the pressure plate fixed to the piston changes with the temperature, so that the position of the clutch disk when the clutch is disengaged, for example, when the piston stroke is large and at low temperature, If the clutch disc is adjusted to be located at the center with the pressure plate, the clutch disc is biased toward the body at high temperatures, and if adjusted at high temperature, the clutch disc is biased toward the pressure plate at low temperatures.
As a result, the disengagement and disengagement of the clutch becomes slow, so that it is impossible to perform a quick shift operation, and a problem that the clutch is dragged occurs.

In order to solve the problem, the applicant of the present application has set the position of the clutch disk when the clutch is disengaged by mounting a spring made of a shape memory alloy between the main body of the hydraulic device and the boss of the clutch disk. Although it was proposed to always position it at the center between the main body and the pressure plate regardless of the temperature, in order to make the return force of the clutch disk large enough to ensure that the clutch is disengaged, it was necessary to use a shape memory alloy spring. This is disadvantageous in that the size becomes large, the cost is high, and the hydraulic pressure-type clutch becomes large.

In the conventional hydraulic pressure-type clutch, a constant pressure oil is applied to a ring-shaped piston for pressing a pressure plate slidably mounted inside a cylinder chamber fixed to the main body of the hydraulic device. To press the clutch disk between the pressure plate and the main body to connect the clutch. Since the movement resistance of the clutch disk 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 disk was constant, and the connection of the clutch was rapidly performed. There has been a problem that the connection of the clutch causes an impact. Further, in the above-described configuration, since there is no change in the hydraulic pressure even immediately before the connection of the clutch, it is impossible to reduce the moving speed of the clutch disk thereafter and smoothly control the connection. In addition, in Japanese Utility Model Laid-Open 61-117927,
Although a pressure clutch is disclosed, the conventional example merely
Only a throttle is provided in the
The throttle is always open while the latch disk crimping piston is moving.
Since only the applied hydraulic pressure acts on the piston,
Ton movement also slows down, making clutch connection quicker
In that it is impossible to do this,
The effect is completely different. Japanese Patent Application Laid-Open No. 58-2
11026 discloses a wet clutch.
The conventional example is an invention having basically the same purpose as the present invention.
However, the clutch is used to detect changes in hydraulic pressure.
Uses only one kind of release spring to improve the cut
And the spring constant of the release spring is too large.
Then, the force for connecting the clutch disc is quite
Larger because it will decrease over a wide stroke range
Must press the clutch disk with
Work over a narrower stroke range
Trigger spring with a larger spring constant than the release spring
The present invention differs from the present invention in that
Different inventions. In addition, in real opening 49-72843,
Although a clutch device is disclosed, the conventional example merely discloses a clutch device.
Latch disc boss to prevent clutch disconnection
This is only provided with a disc spring.
It does not disclose the technology used for detection,
Are inventions with completely different purposes, configurations, and effects.
You.

[0008]

SUMMARY OF THE INVENTION The present invention has been made to eliminate the above-mentioned drawbacks of the prior art, and has as its object to reduce the distance between the boss portion of the clutch disc and the main body of the hydraulic device. A release spring for urging the clutch disk to be disengaged from the hydraulic device main body, and a boss portion of the clutch disk abutting when the clutch disk approaches a predetermined distance from the hydraulic device main body to reduce the resistance of the boss portion to movement. When the clutch disk approaches the main body by a predetermined distance, that is, immediately before the clutch is connected, the resistance for moving the clutch disk to the input shaft is increased to provide a ring for pressing the pressure plate. Causes a sudden rise in hydraulic pressure acting on the piston in the shape of a cylinder, To control the speed of movement of the disk so that the clutch can be connected smoothly, and thereby to prevent the shock due to the connection of the clutch so as not to cause discomfort to the driver or other occupants. It is to be.

Another object is to dispose a release spring between the boss portion of the clutch disc and the main body so as to urge the clutch disc to be detached from 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 at the center between the main body of the hydraulic device and the pressure plate, regardless of the temperature, and thereby the clutch disc is disengaged. An object of the present invention is to make it possible to lightly perform gear shifting and gear shifting by preventing dragging.

[0010]

SUMMARY OF THE INVENTION In short, the method of the present invention (claim 1) comprises a boss portion of a clutch disk and an engine crankshaft movably mounted in an axial direction with respect to an input shaft. a body of fixed hydraulic device
Between the clutch disc and the main body of the hydraulic device.
A release spring for biasing the
Switch disc has approached the main body of the hydraulic device for a predetermined distance.
When the boss of the clutch disc comes into contact with the boss,
From the release spring to increase the resistance of the
Separately or integrally with the release spring with a large spring constant
Attach the configured trigger spring and
When click approaches a predetermined distance in the main body of the hydraulic device, wherein
The trigger spring increases the resistance of the movement of the clutch disk to the input shaft, thereby acting on a pressure-plate-pressing ring-shaped piston slidably housed inside a cylinder chamber fixed to the main body. It is characterized in that a sudden increase in the hydraulic pressure is caused, and that the increase in the hydraulic pressure is detected to control the subsequent moving speed of the clutch disk so as to smoothly connect the clutch. The present invention (claim
2 ) The main body of the hydraulic device fixed to the crankshaft of the engine, the clutch disk movably mounted in the axial direction with respect to the input shaft, and a boss between the clutch disk and the main body. A release spring that is mounted and urges the clutch disk to be disengaged from the main body; and a boss portion of the clutch disk that is configured separately from the release spring so that the boss portion of the clutch disk comes into contact when the clutch disk approaches the main body by a predetermined distance. A trigger spring having a spring constant larger than that of the release spring for increasing the resistance of the movement of the boss portion in contact therewith. The present invention (claim 3 )
A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disk movably mounted in an axial direction with respect to an input shaft, and a clutch disk mounted between a boss portion of the clutch disk and the main body. When the clutch disk approaches the main body by a predetermined distance, a release spring portion for urging the clutch disk to disengage from the main body contacts the boss portion of the clutch disk to increase the resistance of the boss portion to the movement. A trigger spring having a spring constant larger than that of the release spring and a star spring integrally formed with the trigger spring.

[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 press-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 disk 11, a release spring 60, Trigger spring 61
And

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

The hydraulic device 12 includes a main body 14 and a cylinder 1
5, a ring-shaped piston 16, and a vane pump 18 as 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,
It is fixed to the flex plate 9 by bolts 13,
The input shaft 2 is provided at the center through 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 formed in a circular shape so as to be rotatable together with the main body 14, is fixed to the main body 14 by bolts 22, and has a cylinder chamber 15b and an oil passage 15c communicating therewith. The cylinder chamber 15b and the oil passage 15c are communicatively connected by a communication hole 15d,
The oil passage 15c is connected to the sleeve 18a of the vane pump 18.
The bearing is rotatably supported via a bearing 23 and is connected to an oil passage 26a of a retainer 26 rotatably inserted into the boss portion 18b of the vane pump 18 via a plurality of seal members 24 and 25, and is connected to the retainer 26. 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 connected to an oil discharge port 18c of the vane pump 18 via an electromagnetic valve (not shown) housed in an electromagnetic valve housing 18f fixed to the boss 18b of the vane pump 18. , oil discharged from the vane pump is provided in the high pressure state passes through the communication hole 26d that is controlled is formed from the high-pressure side oil Gallery Li 1 8 g formed in the boss portion 18b to the retainer 26 by the solenoid valve It has become. 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 15a.
And an oil passage 26c formed at a circumferential position different from the oil passage 26a. The oil passage 26c is connected to another electromagnetic valve (not shown). The oil discharged from the vane pump 18 is controlled by the solenoid valve and passes through a communication hole 26e formed in the retainer 26 from the low-pressure side oil gallery 18h formed in the boss 18b. It is supplied to the space 12a at a low pressure,
The hydraulic pressure for disengaging the clutch is obtained. 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 is sucked into the oil suction port of the vane pump 18.

The piston 16 is formed in a ring shape, and the pressure plate 10 is fixed to a side surface 16a on the clutch disk 11 side.
The pressure plate 10 is slidably accommodated in the cylinder chamber 15b in the horizontal direction via the pressure plate 10 and is moved leftward in the drawing to press the pressure plate 10 against the clutch disk 11.

Referring also to FIG. 2, the vane pump 18 is fixed to the clutch housing 5 by bolts 28, and its main body 18e is divided into three parts and connected by bolts 29.
Inside the rotor 30 is a sleeve 1 via a bush 31.
8a and rotatably accommodated. 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 is slid while contacting with the centrifugal force accompanying the rotation, and can compress oil while keeping airtight. Power transmission notches 30b are formed at two locations on the inner peripheral surface of the rotor 30, and the ends 26b of the retainers 26 are engaged with the notches, so that power is transmitted from the retainers to the rotor 30. ing.

The center of the ring 32 and the rotation center of the rotor 30 are eccentric by a predetermined eccentric amount, and this eccentric amount is variable. That is, on the side of the main body 18e of the vane pump 18, a pressure setting compression spring 34 for pressing and urging the ring pressing pin 47 is accommodated in a cover 36 fixed to the main body with bolts 35, and the compression spring 34 The eccentricity is reduced by being compressed by the compression unit 32. A stopper 37 is fixed to the inner peripheral surface of the main body 18e of the vane pump 18, and the stopper 37
Is set in the vertical direction.

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

The valve body 50 slides in the direction opposite to the crankshaft 6 (on the transmission side) to move its tip 50a.
Is designed to limit the stroke of the piston 16 by blocking the communication hole 15d.
b, a flange portion 50c formed at one end of the cylindrical portion, a valve portion 50d formed at the distal end 50a, and a hole 50e for accommodating a compression spring 53 made of a shape memory alloy.
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 shielded by the distal end 50a.

The biasing compression spring 52 urges 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 which the one end 52a is
The other end 52b abuts on a substantially rhombus-shaped lid member 55 having the same shape as the concave portion 16c, and is accommodated in the concave portion 16c. The spring constant is smaller than the return force of the shape memory alloy compression spring 53 to the memorized form (extended state), and is changed to the secondary permanent deformation working form (compressed state) of the shape memory alloy compression spring 53. Is set to such a value that the shape memory alloy compression spring can be compressed at the time of return.

The cover member 55 has a hole 55a into which the cylindrical portion 50b of the valve body 50 is fitted. The cover member 55 is fixed to the piston 16 by two screws, and the surface of the cover member 55 when the cover member is mounted on the piston 16 is formed. The side surface 16b of the piston 16 is flush with the side surface 16b.

The compression spring 53 made of a shape memory alloy is provided with a valve body 50.
The valve 50 is pressed toward the communication hole 15d and is stored in such a manner that the valve 50 is expanded by a change in temperature. It is manufactured as a secondary permanent deformation form. That is, when the temperature exceeds a certain value, the shape memory alloy returns to the memory mode, so that the shape memory alloy compression spring 53 generates a very strong extension force and tries to expand.
In order to return to the secondary permanent deformation form, the force for maintaining the stretched state is lost.

The shape memory alloy is composed of a Ni--Ti alloy, Cu
-Cu-Zn-Al alloys are generally less expensive than Ni-Ti alloys, have the advantage of quicker follow-up to temperature changes, smaller hysteresis, and a wider transformation temperature range. The Ni-Ti alloy is said to have a large shape recovery amount, a high durability (thermal cycle) of about two digits, excellent functional properties, and high reliability. In the present invention, any of these alloys can be used for the compression spring 53 made of a shape memory alloy. When the temperature is high, the compression spring 53 made of a shape memory alloy returns to its memory form, so that the valve element 5
0 closes the communication hole 15d and hydraulically locks the cylinder chamber 15b to reduce the stroke of the piston 16. At low temperatures, the compression spring 53 made of shape memory alloy is compressed by the bias compression spring 52, and the valve body 50 Side, the communication hole 15d is opened, and the piston 16
Is increased.

Next, a description will be given of a release spring 60 and a trigger spring 61 for operating the clutch disk, which are main parts of the present invention. First, the first embodiment will be described. In FIGS. 1 and 3 to 6, the release spring 60 is a normal metal spring, and the large diameter portion 60 a to the small diameter portion 60 a.
The clutch disk 11 is formed between the main body 14 and the boss portion 11a of the clutch disk 11 so that the clutch disk 11 is
Is configured to be urged toward.

That is, the clutch disk 11 is
5, the release spring 60 is also compressed to urge the clutch disk 11 toward the cylinder 15, and when the supply of the pressure oil to the cylinder 15 is cut off,
The clutch disk 11 is moved toward the cylinder 15 by the release spring 60, and the position of the clutch disk at that time is adjusted so as to be at the center of the reduced stroke S ₁ (see FIG. 4) at high temperatures. And the clutch disc 11 to the main body 1 of the hydraulic device 12
The distance t ₁ to the friction member 21, which forms a part of the pressure plate 4, and the distance t ₂ to the pressure plate 10 are located at the center where they are substantially equal.

The trigger spring 61 is a normal metal spring, and is formed in a truncated conical shape or a dish shape which gradually becomes smaller from the large diameter portion 61a to the small diameter portion 61b, like the release spring 60, and includes the main body 14 and the clutch disk. 11, the clutch disc 11 is pressed by the cylinder 15 and moved.
When the distance between the main body 14 and the clutch disk 11 becomes a predetermined distance (for example, 0.5 mm), the clutch disk 11 comes into contact with the boss 11a to increase the movement resistance of the clutch disk 11.

Next, a description will be given of a second embodiment. 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.
Are formed as four pawls 60c, 61c formed in a conical shape that gradually decreases toward the small diameter portions 60b, 61b, and the spring force is adjusted to an ideal value by adjusting the width of the pawls. It is configured to be able to.
Then, similarly to the first embodiment, the clutch disk 11 is mounted so as to overlap between the main body 14 and the boss 11a of the clutch disk 11.

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.
A release spring 62a is formed as four long claws arranged at 90 ° intervals, and a trigger spring 62b is formed as four short claws arranged at 90 ° intervals out of phase with the release spring by 45 °. And the main body 14 and the clutch disc 11
It is installed between and. Since other configurations are the same as those of the first embodiment, the same components are denoted by the same reference numerals in the drawings, and description thereof will be omitted.

The present invention is configured as described above,
Hereinafter, the operation will be described. First, the basic operation of the hydraulic pressure type clutch 1 will be described. When the engine rotates, the crankshaft 6, the flex plate 9,
Body 14, cylinder 15, retainer 26 of hydraulic device 12
And 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 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 disk 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 with the oil passage 26a, and the high-pressure side oil gallery 18g
High-pressure oil flows through the communication hole 26d into the oil passage 26a, and supplies the high-pressure oil from the oil passage 26a to the oil passage 15c. Then, oil flows into the cylinder chamber 15b through the communication hole 15d, and high-pressure oil pressure is generated in the cylinder chamber. The piston 16 moves to the left along with the pressure plate 10 in the drawing, and the clutch disk 11 Is pressed against the friction member 21 of the main body 14, power is transmitted to the clutch disk 11, and the clutch is connected. Also, by preventing the oil of the vane pump 18 from being supplied to the oil passage 15c by the operation of the solenoid valve, the oil pressure in the cylinder chamber 15b is lost, and the space 1
The clutch can be disengaged by pushing the pressure plate 10 and the piston 16 back to the right in the drawing by the low oil pressure in 2a.

Next, the operation of the valve device 54 using the compression spring 53 made of a shape memory alloy will be described. 1, 3, 4, 11, and 12, at a high temperature, the compression spring 53 made of a shape memory alloy tries to strongly return to its memory form. The valve section 50d of the tip 50a of the cylinder 15 contacts the communication hole 15d of the cylinder 15. As a result, the communicating hole 15 d is
a, the cylinder chamber 15b is hydraulically locked, the stroke of the piston 16 is limited, the pressure plate 10 approaches the clutch disk 11, the distance between the pressure plate 10 and the clutch disk 11 decreases, and the clutch The connection and disconnection can be performed promptly.

Also, at low temperatures, the compression spring 53 made of a shape memory alloy loses the force of returning to its memory form, so that the restoring force of the bias compression spring 52 is superior, and the shape memory is released by the bias compression spring. Alloy compression spring 53
Is returned from the extended state to the compressed state, that is, the secondary permanent deformation state, and the distal end 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
The distance between the gears is increased so that even when the viscosity of the oil increases at low temperatures, dragging of the clutch can be prevented, the clutch is completely disengaged, and gear shifting and disengaging are performed lightly. In this case, 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 to the left in the figure together with the pressure plate 10 and presses the clutch disc 11 while compressing the release spring 60 (the pressing force of the release spring). (Right direction) and move leftward in the figure. The movement of the clutch disk 11 and the state of the hydraulic pressure acting on the piston 16 at this time are described with reference to FIGS.
Since the spring force of the clutch disk 11 is not so strong, the hydraulic pressure is almost constant without increasing, and the clutch disk 11 moves to the left in the figure at a relatively high constant speed.

When the clutch disk 11 approaches the friction member 21 and the distance between the clutch disk 11 and the friction member 21 becomes a predetermined distance, for example, 0.5 mm, the boss portion 11a has a spring constant larger than the release spring 60. Abuts on the trigger spring 61 having
1 is increased. Therefore, the hydraulic pressure is B (FIG. 10)
The clutch disc 11 is further moved to the left in the figure while compressing the trigger spring. At this time, it is necessary to mechanically detect a sudden increase in the hydraulic pressure. If this is converted to an electrical signal and input to a control device (not shown) such as a computer, the control device controls the oil pressure to slow down the subsequent moving speed of the clutch disk to reduce the clutch speed. Can be controlled to connect smoothly.

When the supply of pressure oil to the oil passage 15c is interrupted 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
5b, the clutch disc 11 pressed by the release spring 60 and the trigger spring 61 is quickly separated from the friction member 21 by about 0.5 mm by the action of the trigger spring 61 having a large spring force. while moving further to the right in the drawing by the action of the release spring 60, the clutch disk 11 when a small hot strokes shown in FIG. 4 is moved by a distance t ₁ rightward in the figure by the operation force of the release spring 60 the clutch is turned off to move quickly to the position of the center of the stroke S _1.

Further during large cold stroke shown in FIG. 3 immediately clutch is moved to the first distance t ₁ only the right in the drawing direction by the operation force of the release spring 60 is turned off, followed by filling the space 12a and the low pressure The oil of the clutch disc 11, the body 14, and the pressure plate 1
Since flows between 0, by further moving the clutch disk 11 rightward in the figure (distance t _3), clutch is positioned in the middle of the stroke S ₂ is completely cut.

As described above, when the clutch is engaged, the clutch disk 11 is quickly brought close to the main body 14 by the action of the trigger spring 61, and then the moving speed of the clutch disk 11 is reduced, and the clutch disk 11 is slowly moved to the main body 14. And the clutch can be smoothly connected without impact. When the clutch is disconnected, the action of the release spring 60 causes the cylinder chamber 1
As soon as the oil pressure in 5b disappears, the clutch disc 11
Is quickly disengaged from the friction member 21 of the main body 14, the clutch is disengaged, and the clutch can be quickly connected and disconnected. Even if the viscosity of the oil increases at low temperatures, the clutch disc 11 Since the release spring 60 ensures that the clutch is disengaged from the main body 14, the clutch can be prevented from being dragged, the clutch is completely disengaged, and the gear can be engaged and disengaged lightly.

Also, in the third embodiment shown in FIGS. 11 and 12, the release spring 60 and the trigger spring 61
The release spring 6 of the star spring 62 acts as one spring.
2a and the trigger spring 62b are different only, and the description of the operation is omitted.

[0042]

As described above, the present invention provides a release spring for urging the clutch disk from the main body of the hydraulic device between the boss of the clutch disk and the main body of the hydraulic device, When the clutch disk comes close to the main body by a predetermined distance, that is, when the clutch disk approaches the main body of the clutch by a predetermined distance. Immediately before the connection, the resistance of the movement of the clutch disc to the input shaft is increased to cause a rapid increase in the hydraulic pressure acting on the ring-shaped piston for pressing the pressure plate. This has the effect of controlling the speed of movement 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.

Further, since a release spring is provided between the boss portion of the clutch disk and the main body so as to release the clutch disk from the main body, the clutch disk is quickly released from the main body when the clutch is disengaged. , Regardless of the temperature, the clutch disc can always be located in the center between the main body of the hydraulic device and the pressure plate, and as a result, the clutch can be prevented from being dragged, and the gears can be engaged and disengaged lightly. There is an effect that can be made.

[Brief description of the drawings]

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

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

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

FIG. 4 is an enlarged vertical cross-sectional view of a main part showing the operation of the release spring and the trigger spring of the first embodiment at a high temperature.

FIG. 5 is a perspective view showing a surface side of a release spring and a trigger spring of 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 a surface side of a release spring and a trigger spring of a second embodiment.

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

FIG. 9 is a diagram showing a state of a change in the moving speed of the clutch disk.

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

FIG. 11 is an enlarged vertical cross-sectional view of a main part showing the operation of the release spring of the third embodiment at a low temperature.

FIG. 12 is an enlarged longitudinal sectional view of a main 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 of 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 side of the release spring and the trigger spring of the third embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Hydraulic pressure-type clutch 6 Crankshaft 11 Clutch disk 11a Boss part 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

Continuation of the front page (56) References JP-A-58-211026 (JP, A) JP-A-61-117927 (JP, U) JP-A-49-72843 (JP, U) JP-A-64-31220 (JP) , U) Japanese Utility Model Showa 51-104258 (JP, U) Japanese Utility Model Showa 60-86627 (JP, U)

Claims (3)

(57) [Claims] A hydraulic device fixed to a boss portion of a clutch disk and an engine crankshaft mounted movably in an axial direction with respect to an input shaft.
Between the clutch disk and the main body of the hydraulic device.
A release spring biasing the release spring from the
When the latch disk approaches the main body of the hydraulic device for a predetermined distance,
When the boss of the clutch disk comes into contact with
Release spring so as to increase resistance to movement of the part.
Separate or integral with the release spring with a larger spring constant
And a clutch spring.
When disk is approaching a predetermined distance in the main body of the hydraulic device, before
By increasing the resistance of the movement of the clutch disc to the input shaft by the trigger spring , a ring-shaped piston for pressing a pressure plate slidably stored inside a cylinder chamber fixed to the main body is formed. A hydraulic pressure-type clutch which causes a sudden rise in the hydraulic pressure acting thereon, detects the rise in the hydraulic pressure, and controls the moving speed of the clutch disk thereafter so as to smoothly connect the clutch. Connection control method. 2. A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disk movably mounted in an axial direction with respect to an input shaft, and a portion between a boss portion of the clutch disk and the main body. A release spring mounted on the main body and biasing the clutch disk to be disengaged from the main body; and a boss portion of the clutch disk configured as a separate body from the release spring when the clutch disk approaches the main body by a predetermined distance. And a trigger spring having a spring constant larger than that of the release spring, the trigger spring being in contact with the boss to increase the resistance of the movement of the boss. 3. A main body of a hydraulic device fixed to a crankshaft of an engine, a clutch disk movably mounted in an axial direction with respect to an input shaft, and a portion between a boss portion of the clutch disk and the main body. When the clutch disc approaches the main body by a predetermined distance, a release spring portion mounted on the main body and urging the clutch disc to be disengaged from the main body contacts the boss portion of the clutch disc to move the boss portion. And a trigger spring having a greater spring constant than the release spring, and a star spring integrally formed with the release spring.