JPH07259883A - Wet clutch device - Google Patents

Abstract

PURPOSE:To smoothly perform a speed change by mounting a damper spring built in a hydraulic piston of interposing a clutch plate from before and after, so as to suppress a turn together of an output shaft according to generating drag torque. CONSTITUTION:In order to disconnect a power interrupting clutch 5, an oil pressure applied to an oil chamber 60 is decreased, to displace a damper piston 51 energized by a return spring and hydraulic piston 50, toward the oil chamber 60, and the damper piston 51 is separated from a clutch plate 23, so that a turbine wheel 13 and a clutch disk 40 can be relatively displaced. At the time of disconnecting this clutch 5, since a side of the turbine wheel 13 is driven by an engine, operating oil in a clutch chamber is stirred by damper piston 51, 53, etc., of receiving a damper spring 6, but in the clutch disk 40, since both side surfaces are almost flatly formed without irregularity of the damper spring or the like, drag torque can be reduced, and a speed change of a transmission can be smoothly performed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a wet clutch device adopted in an automatic transmission or the like.

[0002]

2. Description of the Related Art As a conventional automatic transmission, a torque converter 3 having a lockup clutch 4 and a power cutoff clutch 95 in series is interposed between an engine 1 and a transmission 2 as shown in FIG. 2, a valve mechanism 8 for driving the lock lever clutch 4 and the power cut-off clutch 95 of the torque converter 3 with hydraulic pressure from the oil pump 7, an engine 1, a shift lever mechanism 6, and a valve mechanism. There is known one provided with an operation unit 9 for controlling 8 (Japanese Utility Model Publication No. 2-6850).

As shown in FIG. 7, the torque converter 3 includes a pump shell 10, a turbine shell 11 and a stator 12.
In addition to the lock-up clutch 4 for connecting / disconnecting the turbine wheel 13 and the input disk 14, the power cut-off clutch 95 for connecting / disconnecting the turbine wheel 13 and the output shaft 15 is a turbine. It is arranged on the wheel 13.

When the lockup clutch 4 is in the non-operating state, the driving force of the engine 1 is transmitted as shown by the solid line arrow in the figure, and is transmitted from the input disk 14 through the pump shell 10, turbine shell 11 and turbine wheel 13 to the power source. It is transmitted from the disconnect clutch 95 to the output shaft 15. On the other hand, when the lock-up clutch 4 is in the operating state, it is transmitted as shown by the broken line arrow in the figure, and is directly transmitted from the input disk 14 to the output shaft 15 via the power cut-off clutch 95.

The power cut-off clutch 95 interposed between the turbine wheel 13 and the output shaft 15 is
The power to the output shaft 15 is shut off when the transmission 2 shifts.

The power cut-off clutch 95 is supported by the turbine wheel 13 via the pin 25, and is in the axial direction of the output shaft 15 (hereinafter, simply referred to as the axial direction).
Driven by a piston 20, a pressure plate 21 fixed to the turbine wheel 13, a pressure plate 22 also supported by the turbine wheel 13 so as to be axially displaceable, and a clutch disc 24 so as to be axially displaceable. The clutch plates 23 and 23 are supported, and the pressure plates 21 and 22 and the clutch plates 23 and 23 are in sliding contact so as to sandwich them.

When pressure oil is supplied to the oil chamber 20A defined between the turbine wheel 13 and the piston 20, the piston 20 causes the clutch plate 23 to engage the pressure plate 2
By pressing toward 1, the power cut-off clutch 95
Are connected to connect the turbine wheel 13 and the output shaft 15. On the other hand, when the pressure oil is released from the oil chamber 20A, the pressing of the clutch plate 23 is released and the power cutoff clutch 95 is cut off.

The clutch disc 24 comprises a hub flange 27 connected to the output shaft 15 and a cushion plate 28 which is displaceable in the circumferential direction with respect to the hub flange 27. The hub flange 27 and the cushion plate 28 are connected to each other. Cushion plate 2 between
A damper spring 26 that urges 8 in the circumferential direction is interposed, and the clutch plate 23, the pressure plate 21,
Absorption of rotation fluctuation due to the intermittent connection of 22.

[0009]

However, in the above-mentioned conventional example, since the power cutoff clutch 95 integrated with the torque converter 3 is configured as a wet clutch, the power cutoff clutch 95 is cut off according to the viscosity of the hydraulic oil. Drag torque is sometimes generated, and the gear of the transmission 2 is rotated by the drag torque at the time of starting the vehicle, so that gear shifting may not be performed smoothly.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a wet clutch device capable of smoothly changing gears by suppressing the output shaft from rotating around due to the generation of drag torque.

[0011]

According to the present invention, in a wet type clutch device for cutting off a power transmission path, an annular oil chamber formed on a drive shaft side and an annular member are provided, and the annular oil chamber is formed. The first that can be axially displaced and accommodated in
Of the first piston, a guide member that is disposed on the drive shaft side, and restricts the displacement of the first piston in the circumferential direction, and the first member.
A second piston that is axially coupled to the first piston and that engages in a relatively displaceable manner in the circumferential direction; a friction member that is provided on the driven side facing the second piston;
And an elastic member interposed between the second piston and the second piston to urge the second piston in the circumferential direction.

[0012]

Therefore, the supply and discharge of the pressure oil to and from the annular oil chamber displaces the first and second pistons in the axial direction, and the second piston comes into contact with and separates from the friction member to engage and disengage the wet clutch. When connecting the wet clutch, the guide member on the drive shaft side
The drive shaft and the driven shaft are coupled via the piston, the elastic member, and the second piston. When there is a change in the number of revolutions between the driven shaft and the drive shaft, the second piston urged by the elastic member is displaced relative to the first piston in the circumferential direction so that the number of revolutions changes. Can be relaxed.

[0013]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

1 to 5 show an example in which the present invention is applied to a torque converter 3 which constitutes an automatic transmission similar to the conventional example, and the power cutoff clutch 5 is similar to the power cutoff clutch 95 of the conventional example. 5, and the same parts as those shown in FIGS. 5 and 6 shown as the conventional example are designated by the same reference numerals and the description thereof will be omitted.

An annular oil chamber 60, which communicates with a hydraulic oil passage 70, is provided on the inner circumference of a turbi wheel 13 serving as a drive shaft having a substantially cylindrical shape with a clutch plate 18 of the lockup clutch 4 on the outer circumference. 14, the oil chamber 60 is formed of an annular member in the oil chamber 60 and can be displaced in the axial direction of the output shaft 15 (hereinafter, simply referred to as the axial direction). A hydraulic piston 50 serving as a first piston is accommodated.

The hydraulic piston 50 is the input disk 1
4, projecting a convex portion 50A at a predetermined position on the circumference facing
The convex portion 50A is housed in the oil chamber 60 with the input disk 14 side facing.

The hydraulic piston 50 is a turbine wheel 13.
While the displacement in the circumferential direction is restricted by a pin 53 as a guide member that is provided so as to project from the oil chamber 60 to the oil chamber 60 in the axial direction, the pin 53 is guided in the axial direction.

A damper piston 51 formed of an annular member is engaged with the hydraulic piston 50 on the input disk 14 side.

As shown in FIGS. 3 and 4, the damper piston 51 facing the hydraulic piston 50 is formed with a recess 51A having a substantially U-shaped cross section in a predetermined arc shape.
By engaging the convex portion 50A of the hydraulic piston 50 with the concave portion 51A, the hydraulic piston 50 and the damper piston 51 are coupled in the axial direction, while being relatively displaceable within a predetermined range in the circumferential direction.

As shown in FIG. 2, damper springs 6, 6 are provided on the inner periphery of the recess 51A so as to sandwich the protrusion 50A, and the damper piston 51 is protruded by the damper springs 6, 6. The damper piston 51 is constantly urged so that the 50A is located substantially in the center of the recess 51A.
When is rotated with respect to the hydraulic piston 50, the damper spring 6 urges in the direction opposite to this rotating direction.

As shown in FIGS. 3 and 4, the damper piston 51 is urged toward the hydraulic piston 50 by a return spring 54 provided at the open end of the oil chamber 60,
The damper piston 51 is always coupled with the hydraulic piston 50 in the axial direction and is integrally displaced in the axial direction.

An output shaft 1 as a driven shaft between the turbine wheel 13 and the input disk 14.
A clutch plate 23 is provided on the outer periphery of a disc-shaped clutch disc 40 connected to the clutch 5 at a position facing the damper piston 51. The clutch disc 40
Is formed so that both side surfaces are substantially smooth.

A fixed piston 52 and a damper piston 53, which have the same construction as the hydraulic piston 50 and the damper piston 51, are arranged on the input disk 14 side of the clutch plate 23.
It is clamped by the damper pistons 51 and 53 according to the hydraulic pressure applied to zero. The fixed piston 52 is fixed to the inner circumference of the end portion of the turbine wheel 13, and the fixed piston 52 and the damper piston 53 are axially coupled to each other, while the fixed piston 52 and the damper piston 53 are circumferentially arranged in a predetermined range via the damper springs 6 and 6. Relative displacement is possible.

In this way, the power cut-off clutch 5 constitutes a wet clutch with the hydraulic oil filled between the turbine wheel 13 and the input disk 14, and the hydraulic piston 50
While the damper piston 51 and the damper piston 51 are integrally coupled in the axial direction,
Permitting relative displacement in the circumferential direction through the damper spring 6 within a predetermined range absorbs rotational fluctuations, and the damper piston 51 is brought into and out of contact with the clutch plate 23 supported by the clutch disc 40 to disconnect the power. I do.

With the above construction, the operation will be described below.

To connect the power cut-off clutch 5, pressure oil is supplied from the hydraulic oil passage 70 to the oil chamber 60, and the hydraulic piston 50 is displaced integrally with the damper piston 51 in the axial direction toward the input disk 14. Let

The damper piston 51 is the clutch plate 2
3 while pressing the clutch plate 23 against the damper piston 53 to connect the turbine wheel 13 and the clutch disc 40,
Is transmitted to the output shaft 15.

On the other hand, in order to disengage the power cut-off clutch 5, the hydraulic pressure applied to the oil chamber 60 is lowered, and the damper piston 51 and the hydraulic piston 50 urged by the return spring 54 are displaced toward the oil chamber 60, and the damper Piston 5
1 is separated from the clutch plate 23 so that the turbine wheel 13 and the clutch disc 40 can be displaced relative to each other.

Since the turbine wheel 13 side is driven by the engine when the power cut-off clutch 5 is disengaged, the damper pistons 51 and 53 housing the damper spring 6, the hydraulic piston 50, and the fixed piston 52 are filled with hydraulic oil. However, since the clutch disc 40 is formed so that both side surfaces thereof are substantially smooth, the drag torque due to the stirred working oil can be reduced as compared with the conventional example, and the transmission can be smoothly shifted. It will be possible.

As shown in FIG. 5, the damper spring 6 accommodated in the hydraulic piston 50 and the damper piston 51 which rotate together with the turbine wheel 13, when the rotational speeds of the turbine wheel 13 and the clutch disc 40 are different, The displacement of the hydraulic piston 50 in the circumferential direction is regulated by the pin 53, and the damper piston 51 causes the damper spring 6 to move.
The impact can be alleviated by compressing the oil, and the rotational fluctuation of the turbine wheel 13 and the output shaft 15 can be absorbed as in the conventional example.

As described above, since the damper spring 6 for absorbing the rotation fluctuation is provided on the turbine wheel 13 side, both side surfaces of the clutch disc 40 can be formed substantially smooth and the drag torque can be reduced. Therefore, the gear shift operation of the transmission can be smoothly performed.

[0032]

As described above, according to the present invention, in a wet type clutch device that cuts off a power transmission path, an annular oil chamber formed on the drive shaft side and an annular member are provided, and the annular oil is formed. The first that is housed in the chamber and can be displaced in the axial direction
Of the first piston, a guide member that is disposed on the drive shaft side, and restricts the displacement of the first piston in the circumferential direction, and the first member.
A second piston that is axially coupled to the first piston and that engages in a relatively displaceable manner in the circumferential direction; a friction member that is provided on the driven side facing the second piston;
And an elastic member that is interposed between the second piston and the second piston to urge the second piston in the circumferential direction, and the elastic member that absorbs the fluctuation in rotation is disposed on the drive shaft side. The clutch disc on the side can be formed in a shape capable of reducing the agitation resistance of the hydraulic oil, and the drag torque can be reduced to promote smooth gear shift operation.

[Brief description of drawings]

FIG. 1 is a sectional view of a torque converter showing an embodiment of the present invention.

FIG. 2 is a front view of a clutch disc.

3 is a cross-sectional view taken along the line AA of FIG.

FIG. 4 is a sectional view taken along line BB of FIG.

FIG. 5 is a front view of the clutch disc showing a differential state.

FIG. 6 is a block diagram of an automatic transmission showing a conventional example.

FIG. 7 is a sectional view of a torque converter showing a conventional example.

[Explanation of symbols]

 3 Torque Converter 5 Power Shut-off Clutch 6 Damper Spring 13 Turbine Wheel 23 Clutch Plate 40 Clutch Disc 50 Hydraulic Piston 51 Damper Piston 53 Pin 60 Oil Chamber

Claims (1)

[Claims] 1. A wet clutch device for cutting off a power transmission path, which is formed of an annular oil chamber formed on a drive shaft side and an annular member, and is housed in the annular oil chamber to be axially moved. A displaceable first piston, a guide member that is disposed on the drive shaft side and that restricts the displacement of the first piston in the circumferential direction, and that is coupled to the first piston in the axial direction, A second piston that engages so as to be relatively displaceable in the circumferential direction, a friction member that is provided on the driven side facing the second piston, and is interposed between the first piston and the second piston. A wet clutch device, comprising: an elastic member that is mounted to urge the second piston in the circumferential direction.