JPH0650127B2 - Power transmission device - Google Patents

Description

The present invention relates to a power transmission device mainly used as a starting device for a vehicle, and more particularly to a power transmission device having a fluid coupling and a power cutoff clutch arranged in series. .

[Conventional technology]

2. Description of the Related Art Conventionally, a power transmission device having a fluid coupling has been used as a starting device for a vehicle, and one example of such a power transmission device is disclosed in Japanese Patent Laid-Open No. 55-69355. In this device, the output member of the fluid coupling, which supports the fluid coupling and the disc spring for engaging the power cutoff clutch, and the pressure plate are connected so as not to rotate relative to each other. Therefore, no friction occurs between the pressure plate and the disc spring.

[Problems to be solved by the invention]

However, in the above-mentioned conventional device, since the fluid coupling and the power cutoff clutch are arranged in series with each other, the axial dimension is large, and the axial dimension is limited as in the case of mounting on a front engine front drive vehicle, for example. When it is severe, it is disadvantageous in terms of vehicle mountability. From this point of view, when the power cut-off clutch is incorporated in the fluid coupling to reduce the axial dimension, the disc spring must be supported by the fluid coupling case. By adopting such a configuration, unlike a normal clutch, the fluid is always connected between the power cutoff clutch and the disc spring not only when the clutch is engaged and disengaged but also when the clutch is engaged. Produces a relative rotation based on the rotation difference between the input and output elements of the joint
Friction due to sliding is generated on both the contact surfaces of the clutch and the disc spring and the pressure plate, resulting in slippage and burning due to a decrease in clutch engaging force.

Therefore, the present invention, by absorbing the relative rotation difference between the power cut-off clutch and the disc spring in the pressure plate arrangement portion, by preventing slipping or burning of the power cut-off clutch due to a decrease in the engaging force, An object of the present invention is to realize a power transmission device in which a power cutoff clutch is incorporated in a fluid coupling.

[Means for solving problems]

To achieve the above object, the present invention comprises an input shaft, an output shaft, a fluid coupling and a power cutoff clutch interposed in series in a power transmission flow between the input shaft and the output shaft. In the power transmission device, the fluid coupling includes a case connected to the input shaft, a pump blade provided in the case, and a turbine blade for transmitting power via the pump blade and fluid, and the power cutoff clutch is The disc spring is disposed in the case of the fluid coupling and is connected between the turbine blade and the output shaft to be engaged by applying a biased load of the disc spring via a pressure plate, and the disc spring is opposed to the case. A bearing is disposed between the pressure plate and the power cutoff clutch so as to be non-rotatably supported. Rate side race is characterized in that the locked so as not to rotate relative to the pressure plate by detent means.

[Operation and effect of the invention]

In the power transmission device of the present invention thus configured,
A bearing arranged between the pressure plate and the power cutoff clutch absorbs a relative rotation difference between the two. At that time, the relative rotation between the pressure plate and the race on the pressure plate side of the bearing, which is caused by the co-rotation with the bearing, is prevented by the detent means between the two. As a result, the engagement and disengagement operation of the power cutoff clutch and the engagement maintenance are performed without causing the sliding operation due to the relative rotation between them.

Therefore, according to the present invention, it is possible to realize a power transmission device in which a power cut-off clutch is incorporated in a fluid coupling, and in which a slip and a burn of the clutch due to the clutch do not occur, and particularly a compact size in the axial direction is achieved.

〔Example〕

FIG. 1 shows a front engine front drive vehicle transmission using a power transmission device according to an embodiment of the present invention, and FIG. 2 shows a main part thereof.

This vehicle transmission includes a power transmission device 1, a gear transmission 200 for four forward speeds and one reverse speed, a differential mechanism (not shown), and a transmission case 300 housing these.

The power transmission device 1 includes a fluid coupling (hereinafter referred to as “coupling”) 11, a power cutoff clutch (hereinafter referred to as “clutch”) 13 of a power cutoff device provided inside thereof, and a coupling 11. A direct coupling clutch 15 provided on the right side of the drawing (hereinafter, right side of the figure), an oil pump 17 provided between an input member and an output member of the coupling 11, and a clutch 13 are released and engaged. And a servo mechanism 19 for.

The coupling 11 is a front cover 111 connected to an input shaft 101 of a power transmission device 1 connected to a crankshaft of an engine via a drive plate 102, and an annular plate shape welded to the front cover 111 at the outer circumference. Rear cover 110,
The rear cover 110 includes a pump blade 113 provided around an inner wall surface of the rear cover 110, a turbine blade 114 arranged to face the pump blade 113, and a turbine shell 115 holding the turbine blade 114. At the center of the front cover 111, the large diameter portion of the engine is a pilot boss 105 that fits into a pilot hole 104 provided at the center of the end surface of the input shaft 101, and the gear transmission 200 is a gear The left end is the drive shaft 106 of the oil pump 17, and the middle is the cover 1 of the oil pump 17.
A central shaft 108, which is a disc plate holding shaft 107 that slidably supports the 77 in both directions of the rotating shaft, is provided through. Further, a cylindrical portion 111B having a frictional engagement surface 111A parallel to the shaft is continuously provided on the outer peripheral portion of the inner wall of the front cover 111.

The clutch 13 has an inner spline 133 formed on the inner circumference thereof, and the hub-shaped portion 1 of the turbine shell 115 on the left end in the drawing on the outer circumference thereof.
16 is welded, and a clutch drum 134 to which a guide sleeve 144 that slidably centers a damper drive plate 158B that is an output member of the direct coupling clutch 15 is press-fitted and fixed, and an output shaft 103 of the power transmission device 1. A clutch hub portion 137 having a hub portion 135 spline-fitted to the outer peripheral spline 136 at a position corresponding to the inner spline 133 of the clutch drum 134.
And a plurality of clutch plates 141 each having an outer periphery spline-fitted to the clutch drum 134, and an inner periphery having a clutch disc wheel 139. The clutch disc wheel 139 has a disc portion 138 for connecting the hub portion 135 and the clutch hub portion 137. Clutch hub part 1
A clutch disc 143 is spline-fitted to 37, and includes clutch plates 141 and clutch discs 143 alternately stacked.

The direct coupling clutch 15 includes a friction engagement surface 111A formed on the inner peripheral surface of the front cover 111 and a friction engagement element 150 supported by the damper drive plate 158B. The damper drive plate 158B is provided with a frictional engagement element on the outer periphery, the inner periphery is fixed to the oil pump body 170, and the outer periphery is held by the front damper plate 158C.
Equipped with 57. Damper drive plate 158B
The left side of the drawing supports the pressing force of the diaphragm spring 2, and the right side of the clutch contacts the bearing race 161 of the thrust bearing 160 mounted on the front cover 111 to support the pressing force of the diaphragm spring 2. It is fixed so as to be orthogonal to the drum 134.

The oil pump 17 is an internal gear pump in this embodiment, and is provided on the inner peripheral side of the clutch hub portion of the clutch disc wheel 139. The oil pump 17 has an outer peripheral portion fixed to a cover 177 of the oil pump, and an inner peripheral portion of the output shaft 103 of the power transmission device 1 having a small tip portion 103B.
An oil pump body 170 that is loosely fitted to the disc portion 138 of the clutch disc wheel 139 via a thrust bearing 176, and an engine of the oil pump body 170 is provided in the gear room An internal gear 172 that is rotatably fitted inside, and an external gear 171 that is spline-fitted at the tip of the central shaft 108.
And an intake port 174 connected to an oil passage 103A formed at the center of the output shaft 103 and connected between the cover 177 of the oil pump and the front cover 111.

A connecting rod 191 connected to the servo mechanism 19 of the clutch 13, a clutch pedal provided in the driver's seat, or a servo mechanism operated by automatic supply / discharge of intake pipe negative pressure or hydraulic pressure.
And a pressing rod 192 that is rotated around the fulcrum 193 by the connecting rod 191 and a flange that is in contact with the tip 192A of the pressing rod 192.
Bearing 195 attached to 194 and the bearing 195
As shown in FIG. 2, the sliding sleeve 196 fitted inside the oil seal 19 and the oil seal 19 which constitutes a sealing means between the rear cover 110 and the sliding sleeve 196.
Support 197 configured as a ring as a 7A reinforcing plate
Locked to the sliding sleeve 196 via B,
One side is provided with a diaphragm spring 2 which is an annular disk-shaped disc spring through which the output shaft 103 is inserted, and a protrusion contact portion 41 which is pressed against the outer periphery 22 of the diaphragm spring 2 as shown in FIG. , The pressure plate 4 having the fitting groove portion 43 on the inner circumference 42, and the L projecting in the axial direction at one or more portions of the inner circumference 51 corresponding to the fitting groove portion 43.
An inner spline 198a of the stop ring 198 is provided at one or more locations on the outer periphery 53, which is provided with a character-shaped claw-shaped projection 52.
Rear cover 1 that has an outta spline 54 that fits with
The bearing race 5 of the thrust bearing 3 for smoothing the relative rotation between the diaphragm spring 2 and the clutch 13, which are fixed to the clutch 10, and the pressing ring 199 for pressing the clutch 13. Therefore,
When the clutch 13 is released and slid (semi-clutch) manually or automatically, the claw-shaped projection 5 of the bearing race 5 is
2 and the fitting groove portion 43 of the pressure plate 4 constitute the rotation preventing portion 6, and the pressure plate 4
And the bearing race 5 rotate integrally without any relative rotation.

The gear transmission 200 has a well-known structure, an output shaft 103 of the power transmission device 1 is an input shaft, an output shaft 201 arranged in parallel with the input shaft, and a dog clutch for switching between first speed and second speed. 202, a dog clutch 203 for switching between the third speed and the fourth speed, and a reverse gear not shown.

This power transmission device 1 operates as follows.

The servo mechanism 19 of the clutch 13 is a connecting rod that is manually or automatically operated.
When 191 operates in the leftward direction in the drawing, the pressing rod 192 rotates counterclockwise around the fulcrum 193 to displace the sliding sleeve 196 in the engine direction via the bearing 195. As a result, the sliding sleeve 196 causes the center of the diaphragm spring 2 to bulge to the engine, and the outer periphery 22 of the diaphragm spring 2 is displaced leftward in the drawing. By this action, the pressing force acting on the clutch 13 disappears and the clutch 13 is released. In this state, the clutch 13 cuts off the power, so that the gear transmission 200 can perform a gear shift operation.

When the pressing force to the left in the drawing is released from the connecting rod 191 manually or automatically, the sliding sleeve 196 is displaced to the left in the drawing by the restoring force of the diaphragm spring 2, and the pressing ring 199 presses the engine to the burr. The clutch 13 is engaged, and the input shaft 101 and the output shaft 103 of the power transmission device 1 are connected via the coupling 11. At this time, the direct coupling clutch 15, which is a centrifugal clutch, starts to be engaged at a certain rotational speed or higher and transmits power. Therefore, in the low rotation speed range, the power is transmitted only by the coupling 11, and when the turbine blade is rotated beyond a certain rotation, both the direct coupling clutch 15 and the coupling 11 share and transmit the power, and the rotation is further increased. When the relative rotation of
Power is transmitted only by the direct coupling clutch 15.

Not only when the clutch 13 is engaged and disengaged during such a shift operation, but also when the clutch 13 is engaged, the relative rotational difference is between the diaphragm spring 2 and the pressing ring 199 unless the direct coupling clutch 15 is engaged. However, since the thrust bearing 3 is interposed between the thrust bearings 3 to absorb the difference in rotation between them, sliding friction does not occur between them. On the other hand, the bearing race 5 is not rotated by the thrust bearing 3 due to the engagement with the pressure plate 4,
Since the pressure plate 4 rotates at the same speed as the engine rotation accompanying the rotation of the pressure plate 4, a relative rotation difference does not occur between the diaphragm spring 2 and the pressure plate 4, and between the pressure plate 4 and the bearing race 5.

Thus, according to the power transmission device of the above embodiment,
The thrust plate 3 prevents the pressure plate 4 and the bearing race 5 from rotating together, and the engagement and disengagement operations of the power cut-off clutch and the engagement maintenance are performed without causing a sliding operation therebetween. . Therefore, by realizing such an operation, both the clutch 13 and the diaphragm spring 2 can be housed on the inner peripheral side of the fluid coupling, and the axial dimension of the entire apparatus is made compact.

4 and 5 show a second embodiment of the power transmission device of the present invention.

The rotation stopping portion 7 of this embodiment is the outer circumference of the bearing race 5.
A first outta spline 54 formed on 53 and the pressure plate 4 corresponding to the first outta spline 54.
A second outer spline 45 formed on the outer periphery 44 of the bearing race 5 and the pressure plate 4 are rotated in the same direction by spline fitting both splines 45, 54.

According to the detent means of this embodiment, the detent means is located at a position beyond the outer circumference of the diaphragm spring 2, so that the bearing race 5 is locked to the stop ring 198 and engaged to the pressure plate 4. Both of them can be stopped by the first outer spline 54, and the structure of the bearing race 5 can be simplified.

[Brief description of drawings]

1 is a sectional view of a vehicle transmission incorporating the power transmission device of the present invention, FIG. 2 is a sectional view of a main portion of a vehicle transmission incorporating the power transmission device of the present invention, and FIG. Is a front view of a pressure plate and a bearing race according to a first embodiment of the power transmission device of the present invention, and FIG. 4 is a front view of a pressure plate and a bearing race according to a second embodiment of the power transmission device of the present invention, Figure 5 is AA of Figure 4.
FIG. In the figure, 1 ... Power transmission device, 2 ... Diaphragm spring disc spring, 3 ... Thrust bearing, 4 ... Pressure plate, 5 ... Bearing race, 6, 7 ...
Non-rotating part, 15 ... Direct coupling clutch, 101 ... Input shaft, 103
...... Output shaft, 11 …… Fluid coupling

Claims (2)

[Claims] 1. A power transmission device comprising an input shaft, an output shaft, a fluid coupling and a power cutoff clutch interposed in series between the input shaft and the output shaft in a power transmission flow, wherein the fluid The joint comprises a case connected to the input shaft, a pump blade provided in the case, and a turbine blade for transmitting power via the pump blade and fluid, and the power cutoff clutch is arranged in the case of the fluid joint. The disc spring is provided between the turbine blade and the output shaft and is engaged by applying a biased load of a disc spring through a pressure plate, and the disc spring is supported by the case so as not to rotate relative to the case. A bearing is arranged between the pressure plate and the power cutoff clutch, and the race on the pressure plate side of the bearing is non-rotating. A power transmission device, wherein the power transmission device is engaged with the pressure plate by a locking means so that the pressure plate cannot rotate relative to the pressure plate. 2. The rotation preventing means comprises a groove formed in the pressure plate and a protrusion formed in the race and engaging with the groove. Power transmission device