JP2010101458A - Clutch device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch device capable of accurately and easily controlling half clutch control and eliminating energy loss in an engaged state. <P>SOLUTION: This clutch device includes a spring 16 for pressing friction plates 7, 8 for performing friction welding via a pressing member 12, a first actuator 13 for operating the pressing member 12 in the direction opposite from the spring force via a release member 11 and releasing pressing force to the friction plates 7, 8, an operating member 17 slidably penetrating the pressing member 12 in the axial direction and capable of pressing the friction plates 7, 8 independently from the pressing member 12, a second actuator 20 provided to an external stationary member 1 for applying pressing force in the axial direction to the operating member 17, and a thrust bearing 19 interposed between the second actuator 20 and the operating part 17 for transmitting pressing force in the axial direction while permitting relative rotation between the second actuator 20 and the operating member 17. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

The present invention relates to a clutch device, and more particularly to a clutch device that can easily achieve a half-clutch state.

Conventionally, a wet multi-plate clutch has been known as a starting clutch for an automobile transmission. FIG. 3 shows an example of a wet multi-plate clutch, where the upper half is when released and the lower half is when engaged. An input shaft 51 and an output shaft 52 are coaxially arranged, a clutch drum 53 is connected to the input shaft 51, and a clutch hub 54 is connected to the output shaft 52. A plurality of clutch plates 55 are engaged with the inner periphery of the clutch drum 53 so as to be integrally rotatable by splines, and a plurality of clutch disks 56 are engaged with the outer periphery of the clutch hub 54 so as to be integrally rotatable by splines. . The clutch plates 55 and the clutch disks 56 are alternately arranged. Inside the clutch drum 53, a piston 57 that applies an axial load to the clutch plate 55 and the clutch disk 56 from one side is disposed, and a hydraulic chamber 58 is formed between the clutch drum 53 and the piston 57. Yes. A snap ring 59 is attached to the inner periphery of the clutch drum 53, and prevents the terminal side clutch plate (end plate) 55a from coming off. A return spring 61 is disposed between the piston 57 and a spring retainer 60 attached to the input shaft 51.

In the case of the wet multi-plate clutch having the above-described structure, the half-clutch control can be easily performed by controlling the hydraulic pressure supplied to the hydraulic chamber 58. On the other hand, since the clutch plate 55 and the clutch disk 56 are fastened during traveling, the hydraulic pressure must be continuously supplied to the hydraulic chamber 58, resulting in a large energy loss. In addition, when the hydraulic pressure in the hydraulic chamber 58 is released, the return spring 61 pushes the piston 57 back to the position where it abuts the clutch drum 53, so there is a problem that there is an invalid stroke before the next engagement and it takes time. The invalid stroke varies with wear of the clutch disk 56.

Patent Document 1 proposes a clutch device that engages a clutch plate and a clutch disk by a spring force, transmits torque, and pushes a release rod to release the engagement between the clutch plate and the clutch disk. In this case, there is an advantage that no external force for engaging the clutch is required during traveling and there is no energy loss. However, since the engagement between the clutch plate and the clutch disk is released at once by pushing the release rod, there is a drawback that half-clutch control is difficult.

In Patent Document 2, two types of multi-plate clutches having a large diameter and a small diameter are provided between the friction body on the driving side and the driven side, and a spring for pressing each multi-plate clutch is provided. A clutch device has been proposed in which the pressing positions are shifted in the axial direction to give a two-stage spring characteristic. In this case, half clutch can be performed at the first stage spring portion, but there is a problem that variation in fastening force of the half clutch increases due to variation in spring length. Further, in order to maintain the fastening state, one friction body must be continuously pressed against the other friction body, and there is a problem that energy loss occurs when this is performed by hydraulic pressure. Furthermore, since the multi-plate clutch must be configured in two stages, the structure is complicated and the space is disadvantageous.
JP-A-56-10828 JP 7-42757 A

An object of the present invention is to provide a clutch device that can perform half-clutch control precisely and easily and eliminates energy loss in the engaged state.

In order to achieve the above object, the present invention provides a spring that presses a friction plate that is friction-welded through a pressing member, and operates the pressing member in a direction opposite to the spring force through a release member to press the friction plate. A first actuator that releases pressure, and an operating member that penetrates the pressing member in an axially slidable manner and can press the friction plate independently of the pressing member; A second actuator provided on an external stationary member, and interposed between the second actuator and the actuating member to apply an axial pressing force to the member; the second actuator and the actuating member; And a thrust bearing that transmits an axial pressing force while allowing relative rotation of the clutch device.

When the first actuator is operated, the pressing member is pressed in the direction opposite to the spring force via the release member, and the friction plate is released. In this state, when the second actuator is operated and the friction plate is pressed via the thrust bearing and the operating member, a transmission torque proportional to the pressing force generated by the second actuator is generated, so half-clutch control is easily performed. it can. Next, when the first actuator is deactivated, the pressing force by the release member is released, so that the pressing member presses the friction plate by the spring force. Therefore, the friction plate can maintain the fastening state without applying any force from the outside, and energy loss can be eliminated.

There is no need to provide a gap between the second actuator and the actuating member, or between the actuating member and the friction plate, and the contact state may be obtained when the friction plate is released. Therefore, if the second actuator is operated, the friction plate immediately starts to engage, and half-clutch control can be started. That is, since the invalid stroke for obtaining the half clutch state can be reduced, the time loss can be shortened. Since the maximum generated pressing force of the second actuator may be lower than the spring force, fine half-clutch control can be performed.

Since the second actuator is provided on the stationary member and the actuating member rotates integrally with the pressing member, a relative rotation occurs between the second actuator and the actuating member. Etc. can be suppressed. Since the second actuator is provided on a stationary member such as a case, the configuration is simplified, and subtle hydraulic control can be performed without being affected by centrifugal hydraulic pressure.

At the initial stage of engagement, the first actuator is operated to release the pressing force to the friction plate by the spring. The pressing force generated by the second actuator brings the friction plate into a half-clutch state, and the pressing force by the second actuator is reduced. A control device may be provided that, after exceeding a predetermined value, releases the first actuator and fastens the friction plate with a spring. That is, when the vehicle is stopped, the first actuator is ON (spring force OFF), the second actuator is OFF, and the clutch is released. If the second actuator is raised while controlling the pressing force while the first actuator is in the ON state (spring force OFF), the vehicle can start smoothly in a half-clutch state. Then, when the pressing force by the second actuator exceeds a predetermined value and approaches the fastening state, the first actuator is turned off (spring force ON) and the friction plate is completely fastened by the spring force. Thereafter, by turning off the second actuator, it is possible to smoothly shift to the running state.

The first actuator is composed of a hydraulic device having a piston, the piston is connected to a release member, and the second actuator is composed of a hydraulic device having a piston, and the piston cooperates with the actuating member via a thrust bearing. It is good also as composition which has. The first actuator and the second actuator can be configured by a linear motion mechanism such as a combination of an electric motor and a ball screw. However, when a hydraulic device is used, the operation can be freely switched by controlling the hydraulic pressure. There is an advantage that can be. The supply hydraulic pressure of the first actuator is ON / OFF two-stage switching, whereas the supply hydraulic pressure of the second actuator is preferably variable continuously.

A clutch drum connected to one of the input rotating member or the output rotating member and a clutch hub connected to the other of the input rotating member or the output rotating member, and the friction plate is spline fitted to the inner periphery of the clutch drum It is composed of a clutch plate and a clutch disk that is spline-fitted to the outer periphery of the clutch hub. The spring is disposed between the clutch drum and the pressing member, and the operating member slidably penetrates the clutch drum and protrudes to the outside. It is good also as composition which has. In the case of such a wet multi-plate clutch, it is easy to control the half-clutch. The friction plate of the present invention may be either a single plate or multiple plates, and may be either dry or wet.

According to the present invention, when the first actuator is in the non-operating state, the pressing member presses the friction plate by the spring force, so that the friction plate can maintain the fastening state without applying any force from the outside, and the energy loss. Can be reduced. When the first actuator is activated and the friction plate is disengaged, the second actuator is actuated, so that a transmission torque proportional to the pressing force generated by the second actuator is generated. Can be implemented. In particular, since the half-clutch control is not affected by the spring force, fine half-clutch control can be performed by the second actuator.

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
FIG. 1 shows a first embodiment of a clutch device according to the present invention. This clutch device A is an example used as a starting clutch of an automobile transmission, and includes an input shaft 3 that is rotatably supported via a bearing 2 at the center of a case 1. Power is transmitted to the input shaft 3 from an engine or motor which is a power source. A clutch drum 4 is fixed to the shaft end of the input shaft 3. A cylindrical output shaft 5 is disposed so as to face the input shaft 3, and a clutch hub 6 is fixed to the output shaft 5 by a spline 5a so as to be integrally rotatable. An inner spline 4a is formed on the inner periphery of the clutch drum 4, an outer spline 6a is formed on the outer periphery of the clutch hub 6, and the outer periphery of the clutch plate 7 constituting the friction plate and the clutch disk are formed on both the splines 4a and 6a. Each of the inner peripheral portions of 8 is spline-fitted. The clutch plates 7 and the clutch disks 8 are alternately arranged in the axial direction, and the outer side of the terminal side (left end) clutch plate 7 is prevented from coming off by a snap ring 9 fitted to the inner periphery of the clutch drum 4.

A release rod 11 is slidably inserted into the shaft portion of the output shaft 5 through a sleeve 10. A pressing member 12 is connected to the right end portion of the release rod 11 so as to be relatively rotatable. The left end portion of the release rod 11 is connected to a piston 14 of a first hydraulic device 13 that is a first actuator. An oil chamber 15 is formed in the first hydraulic device 13, and hydraulic pressure is supplied to the oil chamber 15 via an ON / OFF switching valve 34 described later. The maximum pressing force generated by the first hydraulic device 13 is larger than the spring force of the spring 16 described later. In the above description, the release rod 11 and the pressing member 12 are connected so as to be relatively rotatable. However, the release rod 11 and the pressing member 12 are fixed, and relative rotation between the release rod 11 and the piston 14 is allowed. However, a rotation support member such as a bearing that transmits axial force may be provided.

A spring receiving portion 12a protrudes from the side surface of the pressing member 12, and a spring 16 is inserted through the spring receiving portion 12a. The spring 16 is interposed between the side surface of the pressing member 12 and the inner surface of the clutch drum 4 in a compressed state, and always urges the pressing member 12 in the left direction in FIG. The spring 16 is not limited to a coil spring, and may be a plate spring such as a disc spring or other spring means. A pressing portion 12b extending in the radial direction is integrally formed on the outer peripheral portion of the pressing member 12 up to a position facing the friction plates (7, 8). The clutch plate 7a on the front end side (right end) also serves as a pressure plate. The pressure plate 7a can be pressed by the pressing portion 12b of the pressing member 12. When the pressing member 12 is pressed leftward by the spring force of the spring 16, the pressing portion 12b of the pressing member 12 presses the clutch plate 7 and the clutch disk 8 in the axial direction via the pressure plate 7a and fastens them.

One end of a pin-like actuating member 17 is fitted to the pressure plate 7a so as to be movable in the axial direction. A plurality of actuating members 17 are arranged at predetermined pitch intervals in the circumferential direction. In addition, the end surface of the operation member 17 may be in contact with the side edge of the pressure plate 7a. The operating member 17 penetrates the clutch drum 4 and the pressing member 12 so as to be slidable in the axial direction, and the other end projects from the side surface of the clutch drum 4 to the outside. A ring-shaped washer 18 is fixed to the protruding portion on the other end side of the operating member 17. Note that the pressure plate 7a is not limited to a configuration in which one end portion of the operating member 17 is fitted in an axially movable manner and the washer 18 is fixed to the protruding portion on the other end side of the operating member 17, and vice versa. Both may be unfixed. The washer 18 is in contact with a piston 21 of a second hydraulic device 20 that is a second actuator provided in the case 1 via a thrust bearing 19. Since the piston 21 is a stationary piston, the thrust bearing 19 can absorb the relative rotational difference between the piston 21 and the washer 18 (actuating member 17). The thrust bearing 19 is not limited to a needle bearing as shown in the figure, and any bearing such as a ball bearing or a roller bearing can be used. An oil chamber 22 is formed in the second hydraulic device 20, and hydraulic pressure is supplied to the oil chamber 22 via a control valve 35 described later. When the piston 21 moves to the left in the axial direction, the actuating member 17 is pushed through the thrust bearing 19 and the washer 18, and further the pressure plate 7a is pushed. Therefore, the clutch plate 7 and the clutch disk 8 can be engaged with each other with a pressing force corresponding to the oil pressure of the oil chamber 22. The maximum pressing force generated by the second hydraulic device 20 is smaller than the spring force generated by the spring 16.

FIG. 1 also shows a hydraulic control device 30 for operating the first and second hydraulic devices 13 and 20. The hydraulic control device 30 is configured to control the hydraulic device 13 by ON / OFF controlling the output hydraulic pressure of the oil pump 32 that sucks oil from the oil reservoir 31, the pressure adjustment valve 33 that adjusts the discharge hydraulic pressure of the oil pump 32 to a predetermined hydraulic pressure, and the pressure adjustment valve 33. An ON / OFF switching valve 34 supplied to the oil chamber 15, a control valve 35 that finely controls the output hydraulic pressure of the pressure regulating valve 33 and supplies it to the oil chamber 22 of the hydraulic device 20, and an electronic control device 36 are provided. A general ON / OFF solenoid valve can be used as the ON / OFF switching valve 34, and a duty solenoid valve or a linear solenoid valve can be used as the control valve 35. Various signals (for example, accelerator opening, vehicle speed, gear position, etc.) indicating the running state are input to the electronic control device 36, and the ON / OFF switching valve 34 and the control valve 35 are controlled according to these signals.

The operation of the clutch device A having the above structure will be described. The following table shows each operation of the first hydraulic device 13 and the second hydraulic device 20 in each traveling state.

[When the vehicle is stopped]
When the vehicle is stopped, the first hydraulic device 13 is turned on (spring released) and the second hydraulic device 20 is turned off. Therefore, the spring 16 is compressed, and the axial pressing force does not act on the clutch plate 7 and the clutch disc 8 to be released. For this reason, the torque of the input shaft 3 is not transmitted to the output shaft 5.
[When starting]
At the time of start, the first hydraulic device 13 is turned on (spring release), and the second hydraulic device 20 is controlled. That is, the hydraulic pressure in the oil chamber 22 is gradually raised while being finely controlled by the control valve 35, and half-clutch control is performed. Therefore, the pressure contact force between the clutch plate 7 and the clutch disk 8 gradually increases, the torque of the input shaft 3 is transmitted to the output shaft 5, and the vehicle can start smoothly. Since the half clutch control is performed not by the first hydraulic device 13 but by the second hydraulic device 20 whose maximum generated pressure is lower than the spring force of the spring 16, a delicate half clutch control can be performed.
〔Running〕
When the hydraulic pressure of the second hydraulic device 20 rises and the transmission torque exceeds a certain value (half-clutch region), the first hydraulic device 13 is turned off and the compression of the spring 16 is released, and the clutch plate 7 and the clutch are released by the spring force. The disk 8 is fastened. At this time, the second hydraulic device 20 may be in any of the ON / OFF / control states, but in order to avoid energy loss, the second hydraulic device 20 should be in the OFF state. In this way, during traveling that occupies most of the traveling state, the clutch device maintains the engaged state by the spring force, so there is no energy loss due to hydraulic pressure, and fuel efficiency can be improved.

FIG. 2 shows the relationship between the piston stroke and the transmission torque (pressing force) in the prior art and the present invention. FIG. 3A shows the characteristics of the conventional wet multi-plate clutch shown in FIG. 3. First, there is an invalid stroke, and thereafter, the transmission torque increases in proportion to the piston stroke, and eventually the engaged state is reached. However, since the hydraulic pressure acting on the piston needs to overcome the spring force to operate the piston, the gradient of the transmission torque / stroke becomes large and fine half-clutch control is difficult. (B) shows the characteristics of the clutch device according to the present invention. In the initial region of the piston stroke, there is almost no invalid stroke, and the second hydraulic device 20 quickly raises the transmission torque. The second hydraulic device 20 does not need to overcome the spring force to operate the piston, and the generated pressure itself is low, so that the gradient of the half-clutch region can be lowered. When the upper limit value of the half-clutch region is reached, the first hydraulic device 13 is released and the spring force acts, so that the transmission torque rises in a step shape and enters the engaged state.

As described above, since the necessary transmission torque of the clutch device is obtained by the spring force, there is little energy loss during traveling. In particular, since the operation of the first hydraulic device 13 is only at the time of stopping and starting, the operation time can be shortened and the energy loss can be further reduced. Further, since the maximum pressure of the second hydraulic device 20 can be set lower than the required transmission torque, fine control of the generated torque in the half-clutch state can be facilitated. Further, since the spring force does not act during half-clutch control, there is no influence on the half-clutch control due to variations in spring force.

Although the wet multiplate clutch has been described in the above embodiment, the present invention can also be applied to a dry single plate clutch. Further, although the clutch drum is connected to the input shaft and the clutch hub is connected to the output shaft, the clutch drum may be connected to the output shaft and the clutch hub may be connected to the input shaft.
Moreover, although the first actuator and the second actuator are configured by a hydraulic device, it may be configured by using an electric device such as a combination of a solenoid or an electric motor and a ball screw mechanism. Further, when the second actuator is configured by a hydraulic device, the second hydraulic device 20 is not limited to being formed integrally with the case 1, and the second hydraulic device may be formed separately from the case 1.

It is sectional drawing of 1st Embodiment of the clutch apparatus concerning this invention. It is the characteristic figure of the piston stroke-transmission torque in the conventional clutch apparatus of this invention. It is sectional drawing of an example of the conventional wet multi-plate clutch.

Explanation of symbols

1 Case (stationary member)
3 Input shaft 4 Clutch drum 5 Output shaft 6 Clutch hub 7 Clutch plate (friction plate)
8 Clutch disc (friction plate)
11 Release rod 12 Pressing member 13 First actuator (first hydraulic device)
14 Piston 16 Spring 17 Actuating member 18 Washer 19 Thrust bearing 20 Second actuator (second hydraulic device)
21 Piston 22 Oil chamber

Claims (4)

A spring that presses the friction plate in contact with the friction pressure through a pressing member; and a first actuator that releases the pressing force to the friction plate by operating the pressing member in a direction opposite to the spring force through the release member. In the clutch device
An operating member that slidably penetrates the pressing member in the axial direction and can press the friction plate independently of the pressing member;
A second actuator provided on an external stationary member to apply an axial pressing force to the actuating member;
A clutch device comprising: a thrust bearing that is interposed between the second actuator and the actuating member and transmits axial pressing force while allowing relative rotation between the second actuator and the actuating member. In the initial stage of engagement, the first actuator is operated to release the pressing force on the friction plate by the spring, and the friction plate is brought into a half-clutch state by the pressing force generated by the second actuator,
2. The clutch device according to claim 1, further comprising: a control device that releases the first actuator and fastens the friction plate by the spring after the pressing force by the second actuator exceeds a predetermined value. 3. The first actuator is composed of a hydraulic device including a piston, and the piston is connected to the release member,
3. The clutch device according to claim 1, wherein the second actuator is configured by a hydraulic device including a piston, and the piston cooperates with the operation member via the thrust bearing. A clutch drum connected to one of the input rotating member or the output rotating member;
A clutch hub connected to the other of the input rotating member or the output rotating member,
The friction plate is composed of a clutch plate that is spline-fitted to the inner periphery of the clutch drum, and a clutch disk that is spline-fitted to the outer periphery of the clutch hub,
The spring is disposed between the clutch drum and the pressing member;
The clutch device according to claim 3, wherein the operating member slidably penetrates the clutch drum and protrudes to the outside.

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