JPH04357335A - Oil pressure-contact type clutch - Google Patents

Abstract

PURPOSE:To separate a clutch disc from a main frame quickly when the supply of the pressure oil to a cylinder chamber of a hydraulic device is cut, and prevent the dragging phenomenon of a clutch by providing an elastic member for pushing the clutch disc toward a pressure plate for energization. CONSTITUTION:A flexible plate 9 is fixed to one end of a crank shaft 6 of an engine, and a hydraulic device 12 for pressure-contacting a pressure plate 10 to a clutch disc 11 is fixed to this flexible plate 9. This hydraulic deice 12 consists of a main frame 14, a cylinder 15, a ring-shape piston 16 and a vane pump 18, and the pressure plate 10 is fixed to the side surface 16a of the piston 16. A star disc spring 60, which is formed so that an input shaft 20 is passed through a hole 60d provided in the center thereof and that multiple locking parts 60c provided in the peripheral part thereof are engaged with the engaging parts of the clutch disc 11, is provided between the main frame 14 and the clutch disc 11 to push the clutch disc 11 toward the cylinder 15 for energization.

Description

[Detailed description of the invention]

0001

[Industrial Application Field] The present invention relates to a hydraulic compression type clutch, and in particular, the present invention relates to a hydraulic compression type clutch, in which the distance between the clutch disc and the friction member of the main body of a hydraulic device fixed to the crankshaft is always kept in an optimal state regardless of temperature changes. The present invention relates to a hydraulic compression type clutch that can smoothly and quickly engage and disengage the clutch.

0002

[Prior Art] Conventionally, a manual transmission or a transmission in which the manual transmission is automatically changed by an actuator using a fluid pressure cylinder requires a mechanical clutch, such as a dry or wet type. Hydraulic compression clutches have been proposed in order to improve the durability of the clutch and to quickly connect and disconnect the clutch.

However, in conventional hydraulic compression clutches, the distance between the clutch cover and the clutch disc was always constant, and as a result, the stroke of the piston for pressing the pressure plate was constant, and as a result, at low temperatures,
As the viscosity of the oil becomes extremely high, it becomes difficult for the clutch to disengage, resulting in so-called clutch dragging.The torque resulting from this clutch dragging increases, causing problems such as difficulty in engaging a gear, or difficulty in coming out of the gear even after it is engaged. may occur.

[0004] One idea to solve this problem is as follows.
It is conceivable to increase the stroke of the piston, but this causes the problem that the clutch engages and disengages slowly when the temperature is high, making it impossible to perform quick gear shifting operations.

Another method is to change the stroke of the piston depending on the temperature, that is, to make the stroke smaller when the temperature is high and to increase the stroke when the temperature is low. The distance between the clutch disc and the pressure plate changes depending on the temperature, so if you adjust the position of the clutch disc when the clutch is disengaged so that it is located in the center between the main body and the pressure plate when the piston stroke is large and the temperature is low, then At times, the clutch disc is biased toward the main body, and if it is adjusted at high temperatures, the clutch disc will be biased toward the pressure plate at low temperatures, causing slow engagement and disconnection of the clutch, making it difficult to perform quick gear shifting operations. This results in problems such as the clutch not being able to be used or the clutch dragging.

[0006] In order to eliminate such problems, the applicant of the present application installed a shape memory alloy spring between the main body and the clutch disc so that the position of the clutch disc when the clutch is disengaged can be adjusted regardless of the temperature. We proposed that the spring should always be located in the center between the main body and the pressure plate, but in order to sufficiently increase the returning force of the clutch disc and ensure clutch disengagement, the shape of the shape memory alloy spring had to be larger. This is disadvantageous in that the cost is high and the hydraulic compression type clutch is large.

[0007]

[Problems to be Solved by the Invention] The present invention has been made in order to eliminate the above-mentioned drawbacks of the prior art, and its purpose is to provide a hydraulic press-type clutch with a main body of a hydraulic system and a clutch disc. When the supply of pressure oil to the cylinder chamber of the hydraulic system is cut off, the clutch disc is immediately separated from the main body of the hydraulic system and mechanically engaged, so that the clutch disc is connected to the main body of the hydraulic system. By providing an elastic member that presses and urges the clutch disc toward the pressure plate to prevent it from separating from the main body by more than a predetermined distance, the clutch disc quickly separates from the main body when the clutch is disengaged. This also aims to prevent the clutch from dragging and allow the gear to be engaged and disengaged easily.

Another object of the present invention is to enable the clutch to be quickly engaged and disengaged with the above structure. Still another purpose is to reduce the stroke of the piston for pressing the pressure plate when the temperature is high and to increase it when the temperature is low.The return spring of the clutch disc of the hydraulic crimp type clutch is used as a disc spring to connect the main body of the hydraulic device and the clutch disc. By arranging the clutch disc between the two, the structure is simple, the detachability of the clutch disc is improved, and clutch drag is effectively prevented.

Still another object is to mechanically engage the disc spring and the clutch disc to prevent the clutch disc from disengaging beyond a predetermined distance from the main body, and thereby prevent the clutch from engaging. The goal is to be able to do it smoothly and quickly.

0010

[Means for Solving the Problems] In short, the present invention (claim 1) has a main body of a hydraulic device fixed to a crankshaft of an engine, and a cylinder chamber fixed to the main body that is slidably housed inside the hydraulic device. When the temperature is high, reduce the stroke,
A ring-shaped piston for pressing a pressure plate configured to increase the stroke at low temperatures, and when pressed by the piston, rotates integrally with the main body and can slide freely in the axial direction with respect to the input shaft. a clutch disc mounted on the main body, and a clutch disc disposed between the main body and the clutch disc, so that when the supply of pressure oil to the cylinder chamber is cut off, the clutch disc is quickly separated from the main body and mechanically The clutch disc is characterized by comprising an elastic member that presses and biases the clutch disc toward the pressure plate so as to prevent the clutch disc from separating from the main body by a predetermined distance or more when engaged. be. Further, the present invention (claim 2) includes a main body of a hydraulic device fixed to the crankshaft of an engine, and a cylinder chamber fixed to the main body that is slidably housed in the cylinder chamber to reduce the stroke when the temperature is high and to reduce the stroke when the temperature is low. A ring-shaped piston for pressing a pressure plate configured to increase the stroke; and a ring-shaped piston for pressing a pressure plate, which rotates integrally with the main body when pressed by the piston, and is mounted so as to be slidable in the axial direction of the input shaft. The clutch disc is disposed between the main body and the clutch disc, and when the supply of pressure oil to the cylinder chamber is cut off, the clutch disc is quickly separated from the main body and locked by elastic force. The clutch disc is characterized by comprising a disc spring configured to prevent the clutch disc from being separated from the main body by more than a predetermined distance when the clutch disc is engaged with the clutch disc. Further, the present invention (claim 3) includes a main body of a hydraulic device fixed to the crankshaft of an engine, and a cylinder chamber fixed to the main body that is slidably housed in the cylinder chamber to reduce the stroke when the temperature is high and to reduce the stroke when the temperature is low. A ring-shaped piston for pressing a pressure plate configured to increase the stroke; and a ring-shaped piston for pressing a pressure plate, which rotates integrally with the main body when pressed by the piston, and is mounted so as to be slidable in the axial direction of the input shaft. The clutch disc is fixed to the clutch disc between the main body and the clutch disc, and when the supply of pressure oil to the cylinder chamber is cut off, the clutch disc is quickly moved by elastic force. a disc spring configured to prevent the clutch disc from separating from the main body by more than a predetermined distance by causing the clutch disc to separate from the main body and having a locking portion engage with a stepped portion of the input shaft. It is characterized by this.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be explained below based on embodiments shown in the drawings. 1 to 8, a hydraulic pressure 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), and a ring-shaped piston 16 for pressing a pressure plate. , a clutch disc 11, and a disc spring 60, which is an example of an elastic member.

First, the basic structure of the hydraulic compression type clutch will be explained. The clutch housing 5 has an engine (
A crankshaft 6 (not shown) is rotatably fitted and protrudes into the clutch housing 5, and a flex plate 9 is fixed to one end of the crankshaft 6 with bolts 8. A hydraulic device 12 for press-fitting the pressure plate 10 to the clutch disc 11 is fixed by bolts 13 to the clutch disc 11 . The hydraulic system 12 includes a main 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 into 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,
An input shaft 2 is connected to the center of the shaft via a bearing 19.
0 is rotatably mounted, and a friction member 21 is fixed to the opposing surface 14a on the clutch disk 11 side.

The cylinder 15 is formed into a circular shape so as to be rotatable together with the main body 14, and is fixed to the main body 14 with bolts 22, and has a cylinder chamber 15b and an oil passage 15c communicating therewith formed inside. The cylinder chamber 15b and the oil passage 15c are connected to each other through a communication hole 15d,
The oil passage 15c is the sleeve 18a of the vane pump 18.
The retainer 26 is rotatably supported via a bearing 23 and is rotatably fitted into the boss portion 18b of the vane pump 18 via a plurality of seal members 24 and 25. 26 is fixed to the cylinder 15 via a seal member 27. The oil passage 26a of the retainer 26 is communicatively connected to the oil discharge port 18c of the vane pump 18 via a solenoid valve (not shown) housed in a solenoid valve accommodating portion 18f fixed to the boss portion 18b of the vane pump 18. oil gallery 18d
The oil discharged from the vane pump is controlled by the solenoid valve and 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. It has become so. Note that the end of the oil passage 15c is sealed by a steel ball 15e.

The cylinder 15 also has an oil passage 15c.
An oil passage 15f is formed at a circumferential position different from the space 12a in the hydraulic device 12.
through a communication hole 15g, and communicates with an oil passage 26c formed at a different circumferential position from the oil passage 26a, and the oil passage 26c is connected to a separate electromagnetic valve (not shown). The oil discharged from the vane pump 18 is controlled by the solenoid valve to flow from the low pressure side oil gallery 18h formed in the boss portion 18b through the communication hole 26e formed in the retainer 26. is supplied to the space 12a in a low pressure state,
This provides the hydraulic pressure needed to disengage the clutch. 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 is sucked into the oil suction port of the vane pump 18.

The piston 16 is formed into a ring shape, and a pressure plate 10 is fixed to a side surface 16a on the clutch disk 11 side, and a seal member 17 is attached to the piston 16.
It is housed in the cylinder chamber 15b so as to be slidable in the horizontal direction, and is configured to press the pressure plate 10 against the clutch disc 11 by moving to the left in the figure.

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.
A rotor 30 is connected to the sleeve 1 through a bush 31 inside.
8a and is 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.
A vane 33, which is slidably housed in a, slides in contact with the centrifugal force that accompanies rotation, and can compress oil while maintaining confidentiality.

Furthermore, cutouts 30b for power transmission are formed at two locations on the inner circumferential surface of the rotor 30, and the retainer 26 is inserted into the cutouts.
The end portion 26b of the retainer is engaged so that power is transmitted from the retainer to the rotor 30. The center of the ring 32 and the rotation center of the rotor 30 are eccentric by a predetermined amount of eccentricity, and this amount of eccentricity is variable. That is, on the side of the main body 18e of the vane pump 18, a compression spring 34 for pressure setting that presses and biases the ring pressing pin 47 is housed in a cover 36 fixed to the main body with bolts 35.
4 is compressed by the ring 32, so that the amount of eccentricity is reduced. Further, a stopper 37 is fixed to the inner peripheral surface of the main body 18e of the vane pump 18, and the vertical position of the ring 32 is set by the stopper.

Next, the configuration of the valve device 54 using the compression spring 53 made of shape memory alloy will be explained. side side 1
The valve element 50, the bias compression spring 52, and the shape memory alloy compression spring 53 are completely contained in the concave portion 16c formed in the side surface 16b, and are configured so as not to protrude from the side surface 16b at all. It consists of

The valve body 50 is configured to slide in the direction of the crankshaft 6 so that its tip 50a blocks the communication hole 15d to limit the stroke of the piston 16. A flange portion 50c formed at one end of the cylindrical portion and a valve portion 50d formed at the tip 50a.
and a hole 50 for accommodating a compression spring 53 made of shape memory alloy.
e, the diameter of the valve portion 50d 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. There is.

The bias compression spring 52 is designed to press and 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 valve body 50, and one end 52a thereof is attached to the valve body 50.
The other end 52b abuts on a substantially diamond-shaped lid member 55 having the same shape as the recess 16c, and is housed in the recess 16c.

The spring constant has a compression force that is weaker than the force for returning the shape memory alloy compression spring 53 to its memorized state (stretched state). The value is set to such a value that the shape memory alloy compression spring can be compressed when returning to the state).

The lid member 55 has a hole 55a into which the cylindrical portion 50b of the valve body 50 fits, and is fixed to the piston 16 with two screws, so that when the lid member is attached to the piston 16, its surface is It is designed to be flush with the side surface 16b of the piston 16.

The compression spring 53 made of shape memory alloy is connected to the valve body 50.
The valve body 50 is stored in the hole 50e of the valve body 50, and is stored in such a way that the valve body 50 is pressed and biased toward the communication hole 15d and expands due to temperature changes. It is manufactured as a secondary permanent deformation process. In other words, when the temperature exceeds a certain value, the shape memory alloy compression spring 53 returns to its memorized state and tries to expand by generating a very strong tensile force, and when the temperature falls below a certain value, it undergoes secondary permanent deformation. The force that maintains the extended state is lost so that it may return to the processed configuration.

[0024] The shape memory alloy is made of Ni-Ti alloy and Cu.
-Zn-Al alloys, but Cu-Zn-Al alloys are cheaper than Ni-Ti alloys, have the advantage of being able to quickly follow temperature changes, have low hysteresis, and have a wide transformation temperature range. Ni-Ti alloys are said to have a large shape recovery, double-digit durability (thermal cycle), 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. When the temperature is high, the shape memory alloy compression spring 53 returns to its memorized state, and the valve body 50 blocks the communication hole 15d and hydraulically locks the cylinder chamber 15b, thereby reducing the stroke of the piston 16, and when the temperature is low, the bias compression spring 52
The shape memory alloy compression spring 53 is compressed and the valve body 5
0 is drawn toward the piston, the communication hole 15d is opened, and the stroke of the piston 16 is increased.

Next, the disc spring 60 for actuating the clutch disk, which is the main part of the present invention, will be explained. A first embodiment of the present invention will be described with reference to FIGS. 1, 3, 4, and 5. The disc spring 60 is a star-shaped spring having six legs 60c made of ordinary metal. , is formed in a truncated conical shape that gradually becomes smaller from the large diameter part 60a to the small diameter part 60b, and the tip of the large diameter part 60a is bent inward to form the locking part 6.
0c is formed.

The input shaft 20 passes through the hole 60d between the main body 14 and the clutch disc 11, and the locking part 60c is connected to the engaging part 11a of the clutch disc 11.
The clutch disc 11 is configured to be mounted so as to be engaged with the cylinder 15 so as to press the clutch disc 11 toward the cylinder 15. That is, when the clutch disc 11 is pressed by the cylinder 15, the disc spring 60 is also compressed and urges the clutch disc 11 toward the cylinder 15.
When the supply of pressure oil to clutch disc 1 is cut off, clutch disc 1
1 is adapted to be moved toward the cylinder 15 by a disc spring 60.

The stroke of the cylinder 15 is determined by the distance between the main body 14 and the cylinder 15 (strictly speaking, the friction member 2
1 and the pressure plate 10, the same applies hereinafter. )S
The distance S2 between the main body 14 and the cylinder 15 is set to be large, for example 10 mm, to make the distance S2 between the main body 14 and the cylinder 15 wider at low temperatures. amount t
1 is a certain amount, for example, about 2 mm. Further, the maximum movement amount t2 of the clutch disc 11 is the locking portion 60c.
is limited by engaging with the engaging portion 11a, so that the clutch disc 11 is not separated from the main body 14 by more than 5 mm.

Next, a second embodiment of the present invention will be described with reference to FIGS. 6 to 8.
Explain with reference to. The disc spring 61 is made of ordinary metal, and has four truncated conical legs 60b with a hole 61a in the center, and a flange portion 61d with six mounting holes 61c on the outer periphery. There is. and the disc spring 6
1, the small diameter portion 20 of the input shaft 20 is inserted into the hole 61a.
The flange portion 61d is fixed to the clutch disc 11 by the pin 62 in a state where the flange portion 61d is passed through the cylinder 15, and is configured to press and bias the clutch disc 11 toward the cylinder 15.

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 disc spring 61, but since the disc spring 61 also moves together with the clutch disc 11, the leg 60b is in the input position. This is limited by engagement with the stepped portion 20b of the shaft 20, so that the clutch disc 11 is not separated from the main body 14 by more than 5 mm (t2).

The present invention is configured as described above,
The effect will be explained below. First, the operation of the hydraulic pressure bonding type clutch 1 will be explained. When the engine turns,
The crankshaft 6, flex plate 9, main body 14 of the hydraulic device 12, cylinder 15, retainer 26, and rotor 30 of the vane pump 18 rotate at the same speed, and pressurized oil is discharged from the vane pump 18.

In the state shown in FIG. 1, 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 the oil is supplied only to the space 12a, so that the space is filled with low-pressure oil, and the oil passage 26c
And it is not supplied to the oil passage 15c. Therefore, the pressure plate 10 and the piston 16 are pressed rightward in the figure by the low-pressure oil filling the space 12a, the clutch disc 11 is released, and the clutch is disengaged.

When the clutch is connected, the solenoid valve is activated to communicate the discharge port 18c of the vane pump 18 with the oil passage 26a, and connect the high pressure side oil gallery 18g.
High-pressure oil flows from the oil passage 26a to the oil passage 26a through the communication hole 26d, and the high-pressure oil is supplied from the oil passage 26a to the oil passage 15c (in the direction of arrow A in FIG. 4). Then, oil passes through the communication hole 15d and enters the cylinder chamber 15b.
high pressure oil is generated in the cylinder chamber, and the piston 16 moves to the left in the figure together with the pressure plate 10, pressing the clutch disc 11 against the friction member 21 of the main body 14, and pressing the clutch disc 11 against the friction member 21 of the main body 14. 11, and the clutch is connected.

Furthermore, by preventing the oil from the vane pump 18 from being supplied to the oil passage 15c by operating the solenoid valve, the hydraulic pressure in the cylinder chamber 15b is eliminated,
The clutch can be disengaged by pushing the pressure plate 10 and piston 16 back to the right in the figure by the low hydraulic pressure in the space 12a.

Next, the operation of the valve device 54 using the shape memory alloy compression spring 53 will be explained. Figure 1, Figure 4
5, FIG. 7, and FIG. 8, at high temperatures, the shape memory alloy compression spring 53 tries to strongly return to its memorized state, so it presses the valve body 50, and the tip 50a of the valve body
The valve portion 50d contacts the communication hole 15d of the cylinder 15. As a result, the communication hole 15d is blocked by the tip 50a of the valve body 50, the cylinder chamber 15b is hydraulically locked, the stroke of the piston 16 is restricted, the pressure plate 10 approaches the clutch disc 11, and the pressure plate 10 and the clutch disc 11 becomes smaller, and it becomes possible to quickly connect and disconnect the clutch.

Furthermore, when the temperature is low, the force of the shape memory alloy compression spring 53 to return to its memorized state disappears, so the restoring force of the bias compression spring 52 prevails, and the bias compression spring 53 retains its shape memory. Alloy compression spring 53
is returned from the expanded state to the compressed state, that is, to the secondary permanent deformation 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 clutch disc 1
1 and 1, which prevents the clutch from dragging even when the viscosity of the oil increases at low temperatures, allowing the clutch to be completely disengaged and shifting into and out of gear to be easier. This reduces the load on actuators, etc. that use air.

Next, the operation of the disc springs 60 and 61 of the present invention will be explained with reference to FIGS. 1 to 8. Pressure oil is supplied, and the piston 16 moves to the left in the drawing together with the pressure plate 10, compressing the disc springs 60 and 61 by a compression amount t1 against the elastic force, and moving the clutch disc 11 into the main body 14. From the connected state of the clutch, which presses against the friction member 21 and transmits power to the clutch disc 11,
When the supply of pressure oil to the oil passage 15c is cut off by the operation of the solenoid valve, the hydraulic pressure in the cylinder chamber 15b disappears, so that the clutch disc 11, which is being pressed by the disc springs 60 and 61, is pressed by the disc springs 60 and 61. The clutch is quickly moved to the right in the figure by the amount of compression t1, and the clutch is disengaged (FIG. 4).

Furthermore, at low temperatures with a large stroke as shown in FIG. 5, the operating force of the disk springs 60 and 61 first moves the clutch by t1 to the right in the figure, and the clutch is immediately disengaged, and then the low pressure filling the space 12a is released. The oil is applied to the clutch disc 11, main body 14 and pressure plate 1.
0, the clutch disc 11 is further moved to the right in the figure. However, in the disc spring 60 of the first embodiment of the present invention shown in FIG.
a, and the second embodiment of the present invention shown in FIG.
In the disk spring 61 of the embodiment, the leg 60b engages with the stepped portion 20b of the input shaft 20, so that the maximum movement amount t2 of the clutch disc 11 is limited, and the clutch disc 11 is never separated from the main body 14 by more than 5 mm. . Therefore, the clutch can be connected with a small amount of movement of the clutch disk 11, and the clutch can be connected quickly.

Furthermore, even if the viscosity of the oil increases at low temperatures, the clutch disc 11 is reliably separated from the main body 14 due to the action of the disc springs 60 and 61, so it is possible to prevent the clutch from dragging. is completely cut off, making it easy to shift into and out of gear.

[0040]

Effects of the Invention The present invention is arranged between the main body of the hydraulic device of a hydraulic compression type clutch and the clutch disk as described above, and when the supply of pressure oil to the cylinder chamber of the hydraulic device is cut off, the clutch disk The clutch disc is pressed and biased toward the pressure plate so as to quickly disengage from the main body of the hydraulic system and mechanically engage to prevent the clutch disc from disengaging beyond a predetermined distance from the main body of the hydraulic system. Since the clutch disc is equipped with an elastic member that allows the clutch to disengage, it has the effect of quickly separating from the main body when the clutch is disengaged, and as a result, it prevents the clutch from dragging, making it easier to shift into and out of gear. You can get the effect you want.

[0041] Furthermore, the above-mentioned configuration has the effect of quickly engaging and disengaging the clutch. Furthermore, the return spring of the clutch disc of the hydraulic compression clutch is designed to make the stroke of the piston for pressing the pressure plate smaller when the temperature is high and larger when the temperature is low, using a disk spring.
Since it is disposed between the main body of the hydraulic system and the clutch disk, the structure is simple, and the detachability of the clutch disk can be improved, and clutch drag can be effectively prevented. Furthermore, by mechanically engaging the disc spring and the clutch disc, it is possible to prevent the clutch disc from separating from the main body by more than a predetermined distance, and as a result, the clutch can be connected smoothly and quickly. You can get the desired effect.

[Brief explanation of drawings]

1 to 5 relate to a first embodiment of the present invention, and FIG. 1 is a longitudinal cross-sectional view showing the entire hydraulic pressure clutch.

FIG. 2 is a longitudinal sectional view of the vane pump.

FIG. 3 is a perspective view of a disc spring.

FIG. 4 is an enlarged vertical cross-sectional view of a main part showing the action of a disc spring at high temperatures.

FIG. 5 is an enlarged vertical cross-sectional view of a main part showing the action of a disc spring at low temperatures.

6 to 8 relate to a second embodiment of the present invention, and FIG. 6 is a perspective view of a disc spring of the second embodiment.

FIG. 7 is an enlarged vertical cross-sectional view of a main part showing the action of a disc spring at high temperatures.

FIG. 8 is an enlarged vertical cross-sectional view of a main part showing the action of a disc spring at low temperatures.

[Explanation of symbols]

1 Hydraulic crimp type clutch 6 Crankshaft 10 Pressure plate 11 Clutch disc 12 Hydraulic device 14 Main body 15b Cylinder chamber 16 Piston 20 Input shaft 20b Step portion 60 of input shaft Disc spring 60c which is an example of an elastic member Locking portion

Claims (3)

[Claims] Claim 1: A main body of a hydraulic system fixed to the crankshaft of an engine, and a cylinder chamber fixed to the main body that is slidably housed in the hydraulic system and configured to reduce the stroke when the temperature is high and increase the stroke when the temperature is low. a ring-shaped piston for pressing a pressure plate; and a clutch disc that rotates integrally with the main body when pressed by the piston and is slidably mounted on the input shaft in the axial direction thereof. ,
The clutch disc is disposed between the main body and the clutch disc, and when the supply of pressure oil to the cylinder chamber is cut off, the clutch disc is quickly separated from the main body and mechanically engaged with the clutch disc. an elastic member that presses and urges the clutch disc toward the pressure plate to prevent the clutch disc from separating from the main body by more than a predetermined distance. Claim 2: A main body of a hydraulic system fixed to the crankshaft of the engine, and a cylinder chamber fixed to the main body that is slidably housed in the cylinder chamber and configured to reduce the stroke when the temperature is high and increase the stroke when the temperature is low. a ring-shaped piston for pressing a pressure plate; and a clutch disc that rotates integrally with the main body when pressed by the piston and is slidably mounted on the input shaft in the axial direction thereof. ,
A locking part is disposed between the main body and the clutch disc, and when the supply of pressure oil to the cylinder chamber is cut off, the clutch disc is quickly separated from the main body by elastic force, and the locking part is connected to the clutch disc. A hydraulic pressure bonding type clutch comprising a disc spring configured to prevent the clutch disc from separating from the main body by more than a predetermined distance when engaged. 3. A main body of a hydraulic system fixed to the crankshaft of the engine, and a cylinder chamber fixed to the main body that is slidably housed in the hydraulic system and configured to reduce the stroke when the temperature is high and increase the stroke when the temperature is low. a ring-shaped piston for pressing a pressure plate; and a clutch disc that rotates integrally with the main body when pressed by the piston and is slidably mounted on the input shaft in the axial direction thereof. ,
Disposed between the main body and the clutch disc in a state fixed to the clutch disc, and when the supply of pressure oil to the cylinder chamber is cut off, the clutch disc is quickly separated from the main body by elastic force. and a disc spring configured to prevent the clutch disc from separating from the main body by more than a predetermined distance by engaging the locking part with the stepped part of the input shaft. Crimp type clutch.