JPH03194215A - Hydraulic press type clutch - Google Patents

Abstract

PURPOSE:To prevent clutch dragging at the time of low temperature by providing a spring made of a shape memory alloy on a stopper installed diagonally against a cylinder of a hydraulic press type clutch, making stroke of a piston smaller at the time of high temperature and making it larger at the time of low temperature. CONSTITUTION:A cylinder 15 of a hydraulic press type clutch is formed in a round shape, fixed on a main body and made capable of rotating. A stopper 50 is installed on a protruded part 15j in the circumferential direction of the cylinder 15. The stopper 50 becomes diagonal against the side surface of the cylinder 15 and makes contact with a side surface 6b on the side of a transmission of a piston 16. The stopper 50 is retreated with a compression spring 51 and expanded with a compression spring 52 made of a shape memory alloy. As the compression spring 52 loses a force to reverse to a memory type and pressurizing force of the compression spring 51 excels, the stopper 50 retreats and stroke of the piston 16 becomes larger. Accordingly, a gap between a pressure plate and a clutch disc becomes larger and prevents clutch dragging at the time of low temperature.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a hydraulic compression type clutch, and in particular uses a compression spring made of a shape memory alloy to operate a stopper that limits the stroke of a piston for pressing a pressure plate. When the temperature is high, the stroke of the piston is reduced to quickly engage and disengage the clutch, and when the temperature is low, the stroke of the piston is increased to prevent the clutch from dragging due to increased oil viscosity. The present invention relates to a hydraulic pressure bonding type clutch.

BACKGROUND OF THE INVENTION Conventionally, in manual transmissions or transmissions in which the manual transmission is automatically changed by an actuator using a fluid pressure cylinder, a mechanical clutch such as a dry or wet type is required. Hydraulic compression clutches are used to improve durability and to quickly connect and disconnect the clutch.

However, in conventional hydraulic pressure-type clutches, the distance between the thalassochikaher and the clutch disc was always constant, and as a result of the constant stroke of the piston for pressing the pressure plate, the viscosity of the oil became extremely low at low temperatures. As the size increases, the clutch becomes difficult to disengage, causing so-called clutch drag, and the l-lux caused by this clutch drag increases, making it difficult to engage the gear (
There were some problems such as it was hard to come out even if it was inserted.

In order to solve this problem, it is conceivable to increase the stroke of the piston, but this causes the problem that the clutch engages and disengages slowly at high temperatures, making it impossible to perform speed change operations.

Purpose The present invention has been made in order to eliminate the disadvantages of the prior art as stated in the following. In a hydraulic pressure bonding clutch equipped with a hydraulic device consisting of a cylinder in which a ring-shaped piston for pressing a plate is slidably housed and a hydraulic pump that supplies oil to the cylinder, the cylinder is attached to the side of the cylinder on the transmission side. a stopper that is slidably mounted diagonally on the piston and whose tip abuts against the side of the piston on the transmission side to limit the stroke of the piston; and a bias compressor that presses the stopper in the backward direction. a spring, and a compression spring made of shape memory alloy, which is memorized so that it presses the stopper in the forward direction and expands due to a change in temperature.At high temperatures, the stopper By returning to that memory form, the piston moves forward and the stroke of the piston becomes smaller.
By configuring the shape memory alloy compression spring to be compressed by the bias compression spring at low temperatures, the strike collar retreats, and the stroke of the piston is increased, thereby preventing the clutch from dragging at low temperatures. This also allows for easy gear engagement and gear disengagement at low temperatures. Another object is to enable the clutch to be quickly connected and disconnected at high temperatures with the above configuration.

Configuration: In short, the present invention comprises a main body fixed to the crankshaft of an engine, a cylinder fixed to the main body and having a ring-shaped piston for pressing a pressure plate slidably housed inside the main body, and a hydraulic pressure supplying oil to the cylinder. In a hydraulic compression type clutch equipped with a hydraulic device consisting of a pump, the clutch is attached to the side surface of the cylinder on the transmission side so as to be slidable diagonally with respect to the cylinder, and the tip thereof is in contact with the side surface of the piston on the transmission side. a stopper configured to limit the stroke of the piston;
a bias compression spring that presses and urges the stopper in the backward direction; a shape memory alloy compression spring that presses and urges the stopper in the forward direction and is marked so that it expands due to temperature changes; When the temperature is high, the stopper moves forward as the shape memory alloy compression spring returns to its memorized state, reducing the stroke of the piston, and when the temperature is low, the bias compression spring causes the shape memory alloy compression spring to move forward. The piston is characterized in that it is configured such that the stopper moves back when compressed, thereby increasing the stroke of the piston.

The present invention will be explained below based on embodiments shown in the drawings. 1st
6 to 6, a hydraulic pressure clutch 1 according to the present invention includes a main body 14 fixed to a crankshaft 6 of an engine (not shown), and a pressure plate fixed to the main body and provided with a pressure ring. The hydraulic device 12 includes a cylinder 15 in which a shaped piston 16 is slidably housed, and a vane pump I8, which is an example of a hydraulic pump that supplies oil to the cylinder.
, a bias compression spring 51, and a shape memory alloy compression spring 52.

First, to explain the basic configuration of the hydraulic pressure bonding type clutch 1, an engine (not shown) is installed in the clutch housing 5.
A crankshaft 6 is slidably fitted and protrudes into the clutch housing 5, and a flex plate 9 is attached to one end of the crankshaft 6 by a bolt 8.
is fixed to the flex plate 9, and a hydraulic bag WI2 for press-fitting the pressure plate IO to the clutch disk 11 is fixed by a bolt 13.

The hydraulic device 12 includes a main body 14, a cylinder 15, 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, and is fixed to the flex plate 9 with bolts 13. An input shaft 20 is rotatably attached to the center of the main body 14 via a bearing 19, and the input shaft 20 is rotatably mounted to the center of the main body 14, and is rotatable with the flex plate 9. A friction member 21 is fixed to the opposing surface 14a on the disk 11 side.

The cylinder 15 is formed into a circular shape so as to be rotatable together with the main body 14, is fixed to the main body 14 by a bolt 22, and has a cylinder chamber 15b inside and an oil passage 15C communicating with the cylinder chamber 15b.
is formed. Cylinder chamber 15b and oil passage 15
C is connected to the oil passage 1 through the communication hole 15d.
Reference numeral 5c denotes an oil passage of a retainer 26 rotatably supported by the sleeve 18a of the vane pump 18 via a bearing 23 and rotatably fitted into the boss portion 18b of the vane pump 18 via a plurality of seal members 24 and 25. 26a, and the retainer 26 connects the seal member 2 to the cylinder 15.
It is fixed via 7.

The oil passage 26a of the retainer 26 is connected to a solenoid valve housing portion 18f fixed to the boss portion 18b of the vane pump 18.
The oil gear 18d is connected to the oil discharge port 18C of the vane pump IB through a solenoid valve (not shown) housed in the vane pump IB, and the oil discharged from the vane pump is controlled by the solenoid valve to the boss portion. The oil is supplied under high pressure from a high-pressure side oil gearing 18g formed in the retainer 26 through a communication vent 26d formed in the retainer 26. Note that the end of the oil passage 15c is sealed by a steel ball 15e.

Further, an oil passage 15f is formed in the cylinder 15 at a circumferential position different from that of the oil passage 15c, and the oil passage is connected to a space 12a in the hydraulic device 12 through a communication hole 15.
g, and communicates with an oil passage 26C formed at a different position in the circumferential direction from the oil passage 26a, and the oil passage 26c is connected to the oil passage 26C via another electromagnetic valve (not shown). The oil discharged from the vane pump 18 is controlled by the electromagnetic valve and communicated with the oil gear lary 18d, and the oil flows from the low-pressure side oil gear lary 18h formed in the boss portion 18b through the communication hole 26e formed in the retainer 26 to the space in a low pressure state. 12a to obtain hydraulic pressure for disengaging 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 in a ring shape, has a pressure plate 10 fixed to its side surface 16a on the side of the clutch disc 11, and is slidable horizontally into the cylinder chamber 15b via a seal portion tA''17. is housed in
The pressure plate 10 is configured to be pressed against the clutch disc 11 by moving to the left in the figure.

Note that the countershaft 42 is rotatably supported by the transmission case 41 via a bearing 43.

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 connected by bolts 29, and a rotor 30 is rotatably housed inside the sleeve 18a through a bush 31. Further, the rotor 30 is housed in a ring 32, and the rotor 30 is disposed on the inner surface 32a of the ring.
A vane 33, which is slidably housed in a plurality of radial grooves 30a formed in the radial grooves 30a, slides in contact with each other due to the centrifugal force generated by rotation, thereby compressing the oil while maintaining confidentiality. . In addition, notches 30b for power transmission are formed at two locations on the inner circumferential surface of the rotor 30, and the ends 26b of the retainer 2G are engaged with the notches, so that power is transmitted from the retainer to the rotor 30. ing.

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 18a of the Hoehn pump 8, there is a compression spring 3 for pressure setting that presses and biases the ring pressing pin 47.
4 is housed in a cover 36 fixed to the main body with bolts 35, and the compression spring 34 is compressed by the ring 32, thereby reducing eccentricity. Further, a stopper 37 is identified on the inner peripheral surface 32a of the ring 32,
The vertical position of the ring 32 is set by the stopper.

1 Next, the shape memory alloy compression spring 5 which forms the main part of the present invention
2, the stopper 50 is attached to the side surface 15i of the cylinder 15 on the transmission side so as to be slidable obliquely with respect to the cylinder, and its tip 50a is attached to the transmission side of the piston 16. The stroke of the piston is limited by coming into contact with the side surface 16b of the cylinder 15. Tunnel-shaped protrusions 15j are formed at three locations in the circumferential direction of the cylinder 15, and one stopper is attached to each of the protrusions. 50 is installed. Further, the stopper 50 is formed hollow, and has a hole 50b.
, a flange portion 50c, a large diameter portion 50d, and a small diameter portion 50.
e and the tapered portion 50f are formed continuously. The flange portion 50C and the large diameter portion 50d are inserted into the large diameter hole of the protrusion 15j, and the small diameter portion 50e is inserted into the small diameter hole 15N of the protrusion 15j.
They are designed to fit into each other.

The bias compression spring 5I moves the stopper 50 in the backward direction (
4 to left in Figure 6), and is a normal metal compression spring that does not use shape memory alloy, and its spring constant is The compression force is weaker than the force for returning the spring 52 to its memory state (stretched state), and the compression spring 52 is made of a shape memory alloy.
The value is set such that the shape memory alloy compression spring can be compressed when returning to the secondary permanently deformed state (compressed state). It is fitted into the small diameter portion 50e of the stopper 50, and one end 51a is brought into contact with the large diameter portion 50d.

The shape memory alloy compression spring 52 presses and urges the stopper 50 in the forward direction, and is memorized so that it expands due to a change in temperature, that is, a temperature rise above a certain value,
It is manufactured with the stretched state as a memory form and the compressed state as a secondary permanent deformation form. That is, when the temperature exceeds a certain value, the shape memory alloy compression spring 52 tries to expand by generating a very strong stretching force in order to return to its memorized state.
When the temperature drops below a certain value, the force to maintain the stretched state is lost so that it may return to the secondary permanently deformed state. And shape memory alloy compression spring 52
is accommodated in the hole 50b of the stopper 50, and is prevented from being removed by a plug member 53 in which a guide F portion 53a having a smaller diameter than the inner diameter of the plug member 53 is formed.
It is fixed to the protruding part 15j by.

Shape memory alloys are broadly classified into Ni-Ti alloys and CuZn-A1 alloys, but Cu-ZnA1 alloys are cheaper than Ni-Ti alloys, can quickly follow temperature changes, have small hysteresis, and Nj-Ti alloy has the advantage of a wide transformation temperature range, and has a large shape recovery amount.
It is said to have 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 52.

Then, the shape memory alloy compression spring 52 returns to its memorized state and moves forward, reducing the stroke of the piston 16. At low temperatures, the bias compression spring 51 compresses the shape memory alloy compression spring 52 and the stopper 50 retreats. 3 4 , and is configured to increase the stroke of the piston 16.

Function The present invention is constructed as described above, and its function will be explained below. First, the basic operation of the hydraulic pressure bonding type clutch 1 will be explained. When the engine rotates, the crankshaft 6, flex plate 9, hydraulic system 12
The main body 14, 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 1.

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

When the clutch is connected, the solenoid valve is operated to communicate the discharge port 18C of the vane pump 18 with the oil passage 26a, and the high pressure is supplied to the oil passage 26a from the high-pressure side oil gallery 'J4' 8g through the communication hole 26d. The high-pressure oil is supplied from the oil passage 26a to the oil passage 15C. Then, oil flows into the cylinder chamber 15b through the communication hole 15b, high pressure oil pressure is generated in the cylinder chamber, and the piston 16 moves to the left in the figure along 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 connected.

In addition, 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 disappears, and the pressure plate 10 and the piston 16 are moved by the low pressure hydraulic pressure in the space 12a. You can release the clutch by pushing it back to the center right.

6 Next, the shape memory alloy compression spring 5 which forms the main part of the present invention
The operation of the stopper 50 using the stopper 2 will be explained. Fifth
In the figure, at high temperatures, the shape memory alloy compression spring 52
tries to strongly return to its storage form, so the bias compression spring 51 is compressed to move the stopper 50 forward. As a result, the tip 50a of the stopper 50
Press the side surface 16b of No. 6 on the transmission side upward in the figure (toward the clutch disk side). As a result, the gap C between the pressure plate 10 and the clutch disc 11 becomes smaller, and the clutch can be quickly connected and disconnected.

Furthermore, when the temperature is low, as shown in FIG. 6, the force that tends to return the shape memory alloy compression spring 52 to its memorized state disappears, so the restoring force of the bias compression spring 51 overcomes the bias bias spring 52. The compression spring presses the stopper 50, and the shape memory alloy compression spring 52 is returned from the expanded state to the compressed state, that is, to the secondary permanent deformation state.

As a result, the stopper 50 moves backward, its tip 50a no longer presses the transmission-side side surface 16b of the piston 16, and the stroke of the piston 16 increases.
The gap C between the pressure plate 10 and the clutch disc 11 becomes larger. As a result, even if the viscosity of the oil increases at low temperatures, it is possible to prevent the clutch from dragging, the clutch is completely disengaged, gears can be engaged and removed easily, and air-based actuators, etc. The load can be reduced.

Effects As described above, the present invention comprises a main body fixed to the crankshaft of an engine, a cylinder fixed to the main body and slidably housing a ring-shaped piston for pressing a pressure plate, and an oil supply to the cylinder. In a hydraulic compression type clutch equipped with a hydraulic device consisting of a hydraulic pump, the clutch is attached to the side of a cylinder on the transmission side so as to be slidable diagonally relative to the cylinder, and its tip abuts the side of the piston on the transmission side. A stopper configured to limit the stroke of the piston, a bias compression spring that presses and biases the stopper in a backward direction, and a bias compression spring that presses and biases the stopper in a forward direction and expands due to temperature changes. The stopper is equipped with a shape memory alloy compression spring that has been memorized, and when the temperature is high, the stopper moves forward as the shape memory alloy compression spring returns to its memorized form, reducing the stroke of the piston, and when the temperature is low, the stopper is moved forward by the bias compression spring. Since the shape memory alloy compression spring is compressed and the stopper retreats to increase the stroke of the piston, this has the effect of preventing the clutch from dragging at low temperatures. The effect of being able to easily engage and disengage gears is obtained. Further, as a result of the above configuration, there is an effect that the clutch can be quickly connected and disconnected at high temperatures.

[Brief explanation of drawings]

The drawings relate to embodiments of the present invention, and FIG. 1 is a longitudinal sectional view of a hydraulic pressure clutch, FIG. 2 is a longitudinal sectional view of a vane pump, and FIG. 3 is a portion showing the state of a stopper arranged on the side of a cylinder. 4 is an exploded perspective view of stopper-related parts, FIG. 5 is a cross-sectional view showing the state of the stopper at high temperatures, and FIG. 6 is a cross-sectional view showing the state of the stopper at low temperatures. be. 1 is a hydraulic pressure bonding type clutch, 10 is a pressure play I.
, 12 is a hydraulic system, 15 is a cylinder, 15j is a side surface on the transmission side, 16 is a piston, 16b is a side surface on the transmission side, 18 is a vane pump which is an example of a hydraulic pump, 50 is a stopper, 50a is a tip, 51 is a bias compression The spring 52 is a compression spring made of shape memory alloy.

Claims (1)

[Claims] A hydraulic system consisting of a main body fixed to the engine crankshaft, a cylinder fixed to the main body and slidably housing a ring-shaped piston for pressing a pressure plate, and a hydraulic pump supplying oil to the cylinder. In a hydraulic compression type clutch, the clutch is mounted on the transmission side side of the cylinder so as to be slidable diagonally with respect to the cylinder, and its tip abuts the transmission side side of the piston to limit the stroke of the piston. A bias compression spring that presses and biases the stopper in the backward direction, and a shape memory alloy made of a shape memory alloy that presses and biases the stopper in the forward direction and is memorized to expand due to temperature changes. When the temperature is high, the stopper moves forward as the shape memory alloy compression spring returns to its memorized form, reducing the stroke of the piston, and when the temperature is low, the bias compression spring causes the shape memory alloy compression spring to move forward, reducing the stroke of the piston. A hydraulic crimp type clutch, characterized in that the compression spring is compressed and the stopper retreats to increase the stroke of the piston.