JPH0368248B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a power transmission device used as a starting device for a vehicle, and more particularly to a power transmission device that combines a fluid transmission device and a power cutoff clutch.

[Conventional technology]

Since manual transmissions commonly used in vehicles require complicated operations including clutch operation for each gear shift, semi-automatic transmissions that do not require clutch operation have been proposed.

In semi-automatic transmissions, the starting device that should replace the clutch is a combination of a fluid coupling and a power cut-off clutch, which are arranged axially in series in a single case or are , Automotive Engineering Complete Book Volume 9 Power Transmission Device, Sankaido Co., Ltd., December 20, 1981, p. 254), each is housed in a separate case and arranged in series in the same axial direction. There is.

However, the launching device with this arrangement is
The axial dimension is long, and it cannot be placed as is in the clutch housing space of a conventional manual transmission.

Therefore, in order to solve the above-mentioned problems, the applicant has proposed a power transmission device disclosed in Japanese Patent Application No. 58-240568 (Japanese Patent Application Laid-open No. 132132-1982).

As shown in FIG. 1, this device includes a front cover 111 and a rear cover 1 of a power transmission device 100.
10A, the power cutoff clutch 130 is arranged on the inner circumference side of the fluid coupling 110, which is disposed on the outer circumference side of the 10A. Although they are arranged in series in terms of power transmission flow, they are structurally arranged in parallel in the radial direction, and the device can be accommodated in the clutch housing space of a conventional manual transmission.

[Problem that the invention seeks to solve]

However, in the power transmission device proposed by the applicant, the power cutoff clutch 130 is configured as a multi-disc clutch in order to ensure sufficient torque transmission capacity, so the number of clutch discs is reduced when the clutch is released. This includes the potential for a proportionate amount of clutch drag.

The present invention was devised in view of the above circumstances, and an object of the present invention is to provide a power transmission device that can reduce the amount of clutch drag while maintaining a sufficiently large torque transmission capacity of the power cutoff clutch. shall be.

[Means for solving problems]

In order to achieve the above object, the power transmission device of the present invention includes an input shaft connected to a power source, an output shaft arranged concentrically with the input shaft, and a pump connected to the input shaft. A turbine that transmits power through the fluid of the pump, a power cutoff conical clutch that is disposed between the turbine and the output shaft and disconnects the drive connection between the input shaft and the output shaft, and an engagement of the conical clutch. The conical clutch includes a servo mechanism for controlling engagement and release, and the conical clutch has a driving member connected to the turbine and a driven member connected to the output shaft, and the driving member is rotatably supported by the input shaft. , the driven member is rotatably supported by the output shaft, and the conical clutch is disposed radially inside the pump.

[Action and effect of the invention]

According to the power transmission device of the present invention having the above configuration, it is possible to utilize the fastening force due to the wedge action between the driving member and the driven member of the conical clutch when the clutch is engaged. Not only can the transmission torque capacity of the clutch be increased without increasing the number of elements, but when the clutch is released, the clutch can be released smoothly with less drag compared to a multi-disc clutch.
Furthermore, the number of parts can be reduced by simplifying the clutch structure and assembly can be facilitated, thereby reducing production costs.

〔Example〕

The power transmission device of the present invention will be explained based on an embodiment shown in FIGS. 2 to 4.

As shown in FIG. 2, the power transmission device 100 includes:
An input shaft 101 connected to a power source such as an engine (not shown), an output shaft 103 (see FIG. 4) arranged concentrically with the input shaft 101, a pump connected to the input shaft 101, and the pump. A fluid coupling 11 consisting of a turbine that transmits power via fluid.
0, a power cutoff conical clutch 130 disposed between the turbine and the output shaft 103 to cut off the driving connection between the input shaft 101 and the output shaft 103, and a servo mechanism to control engagement and release of the conical clutch 130. 190 (see FIG. 4), the conical clutch 130 has a driving member connected to the turbine and a driven member connected to the output shaft 103. The driving member is rotatably supported by the input shaft 101 and the driven member is connected to the turbine. The member is rotatably supported on the output shaft 103, and the conical clutch 130 is disposed radially inwardly of the pump. Furthermore, this power transmission device 100 includes:
A diameter clutch 10 and an oil pump 170 are provided.

The fluid coupling 110 is connected to the front cover 11 connected to the input shaft 101 of the power transmission device 100.
1. An annular plate-shaped rear cover 110A welded to the front cover 111 at the outer periphery, the rear cover 110
It includes a pump impeller 113 disposed around the inner wall of A, a turbine impeller 114 disposed opposite to the pump impeller 113, and a turbine shell 115 holding the turbine impeller 114. At the center of the front cover 111 is a gear transmission 200.
(See Figure 4) The end of the side is the drive shaft 106 of the oil pump 170, and the middle part is the oil pump 1.
An input shaft 101 serving as an oil pump housing holding shaft 107 that supports an oil pump cover 177 of 70 is provided through the input shaft 101 . Further, on the inner wall of the outer circumferential cylindrical portion 111B of the front cover 111, an annular direct clutch friction engagement surface 111A parallel to the axis is formed.

The conical clutch 130 has a hub-shaped portion 116 of the turbine shell 115 welded to its outer periphery as a driving member, and a rear damper drive plate 158.
A cylindrical clutch drum 134 is press-fitted with a guide ring 144 for centering B, and has an inner spline 133 formed on its inner periphery. A damper spring 157 is disposed, and on the right side there is a front damper drive plate 158C, and on the left side there is a rear damper drive plate 15 to which power is transmitted from the direct coupling clutch 10.
8B, the right end surface is rotatably supported by the front cover 111 via the sliced bearing 19 and its bearing races 19A, 19D, the inner peripheral part is welded to the oil pump body 170A of the oil pump 170, and the conical clutch 130
The hub part 135 is spline-fitted to the output shaft 103 to the power transmission device 100 as a driven member, and the outer circumferential spline is provided at a position corresponding to the inner spline 133 of the clutch drum 134. The clutch disc wheel 139 includes a clutch hub part 137 formed with a 136 and a disc part 138 connecting the hub part 135 and the clutch hub part 137, and has an outer circumference and an inner circumference spline-fitted to the clutch drum 134 and the clutch hub part 137, respectively. A conical clutch element 130A is provided.

The conical clutch element 130A includes a pressure cone 145 and a reaction cone 146 splined to the clutch drum 134 as driving members, and a torque transmission cone 147 splined to the clutch hub portion 137 as a driven member. . The pressing cone 145 and the reaction cone 146 are formed with conical engagement surfaces 145A and 146A having moderately inclined surfaces facing each other on the inner circumferential side. On the outer peripheral side of the torque transmission cone 147, there are two conical engagement surfaces 147 corresponding to the conical engagement surface 145A of the pressure cone 145 and the conical engagement surface 146A of the reaction cone 146.
A, 147B are formed, and these conical engagement surfaces 1
47A and 147B are provided with friction materials 147C and 147D, respectively, to increase the frictional force during engagement. A wave ring 148 is interposed between the outer peripheral end surfaces of the pressing cone 145 and the reaction cone 146, and is a ring having a bent wave shape as shown in FIG. 3 and having elasticity in the axial direction of the ring. This wave ring 148 is arranged to push apart the push cone 145 in the axial direction when the conical clutch element 130A is disengaged, and the conical engagement surfaces 147A, 147 of both the push cone 145 and the reaction cone 146
This prevents dragging between B and the friction materials 147C and 147D.

The direct coupling clutch 10 has a friction engagement surface 111A formed on the inner peripheral surface of the cylindrical portion 111B of the front cover 111, and a rear damper drive plate 158.
A frictional engager 11 is supported on the outer periphery of B.

The oil pump 170 is an internal gear pump in this example, and is provided on the inner peripheral side of the clutch disc wheel 139. This oil pump 170
The oil pump cover 177 and the oil pump body 170A are fixed to each other by rivets 178 at the outer periphery. Oil pump body 170A
is loosely fitted at its inner periphery to the small diameter portion at the tip of the output shaft 103 via an oil seal 175, and its left end surface is supported in contact with the disk portion 138 of the clutch disk wheel 139 via a thrust bearing 176. An oil pump internal gear 172 is rotatably fitted into a gear room provided on the engine side of the oil pump body 170A.
An oil pump external gear 171 that meshes with this is fitted to the tip of the input shaft 101. The oil pump body 170A is provided with an oil discharge port connected to an oil passage formed at the center of the output shaft 103, and an oil inlet port 174 connected between the oil pump cover 177 and the front cover 111.
is provided.

FIG. 4 shows the power transmission device 100 of the above embodiment,
This figure shows an embodiment applied to a front engine front drive type vehicle transmission in which a gear transmission 200 for five forward speeds and one reverse speed and a differential mechanism are housed in a transmission case 300.

The transmission case 300 has a fastening surface 3 to the engine.
The 01 side is open, and the partition wall 30 is on the gear transmission 200 side.
2 is formed, and a shell-shaped starting device case 303 in which the power transmission device 100 is housed, one end surface is fastened to the partition wall 302 of the starting device case 303, and a gear transmission case cover 305 is fastened to the left end surface. A cylindrical gear transmission case 304 housing the gear transmission 200, a differential case 306 integrally formed on the side of the starting device case 303, and a gear transmission case 304 integrally formed, It consists of a differential cover 307 that covers the left side opening of the differential case 306.

The gear transmission 200 has a known configuration, and includes an input shaft for the output shaft 103 of the power transmission device 100, an output shaft 201 parallel to the input shaft, and a dot clutch 202 for switching between first and second speeds. , a dog clutch 203 for switching between third and fourth speeds, and a dog clutch 204 for switching between fifth speed.

A servo mechanism 190 that engages and disconnects the conical clutch element 130A is connected to a transmission mechanism 191A that is operated by operating a clutch pedal provided at the driver's seat or by automatic supply and discharge of intake negative pressure or hydraulic pressure. a rod 191; a pressing rod 192 rotated around a fulcrum 193 by the connecting rod 191;
A bearing 195 supported by a flange 194 that comes into contact with the tip of the presser 192, and a bearing 19
Sliding sleeve 196 built into 5
and a diaphragm spring 197 whose inner peripheral edge is locked to the inner end of the sliding sleeve 196.
and a pressing ring 199 that engages with the outer peripheral edge of the diaphragm spring 197 and presses the pressing cone 145 in the axial direction via the thrust bearing 198.
and an annular plate-shaped bearing holding member attached to the front cover 111 that contacts the bearing race 19C supported by the bearing race support 19A attached to the damper driven plate 158A to support the pressing force of the diaphragm spring 197. A thrust bearing 19 is held in contact with an L-shaped bearing race 19D held by a bearing race 19B. Then, the conical clutch 130 is released and slid (half-clutched) by manually or automatically driving the transmission mechanism.

Reference numeral 205 designates a differential mechanism in which front wheel drive shafts 206 and 207 are arranged parallel to the input shaft 103 and output shaft 201 of the gear transmission 200.

Servo mechanism 190 of this power transmission device 100
works as follows. When the connecting rod 191 moves to the left in the figure, either manually or automatically, the pressing rod 19
2 rotates counterclockwise around the fulcrum 193 and the bearing 1
95 to displace the sliding sleeve 196 toward the engine. As a result, the sliding sleeve 196 causes the center side of the diaphragm spring 197 to bulge toward the engine, and the pressing ring 199 connected to the outer periphery of the diaphragm spring 197 can be freely displaced to the left in the drawing. This action causes the wave ring 148 to rebound axially, causing the push cone 145 and the reaction cone 146 to separate, releasing the cone clutch element 130A. In this state, the power is cut off by the conical clutch 130, so that the gear transmission 200 can be operated to change gears.

When the connecting rod 191 moves to the right in the figure, either manually or automatically, the sliding sleeve 196
Due to the return force of the diaphragm spring 197, it is displaced to the left in the figure, the pressing ring 199 is pressed toward the engine, the wave ring 148 is compressed in the axial direction, and the double conical engagement surfaces 145A, 146A of the pressing cone 145 and the reaction cone 146 and torque transmission cone 147
Friction materials 147C and 147D provided on both conical engagement surfaces 147A and 147B engage with each other, and the input shaft 101 and output shaft 103 of the power transmission device 100 are connected via the fluid coupling 110.

FIG. 5 shows another embodiment of the power transmission device of the present invention.

The conical clutch element 130A of the power transmission device 100 of this embodiment has a clutch drum 134 on the outer peripheral side.
A pressing cone 1 is spline-fitted to the press cone 1 and has a moderately inclined conical engagement surface 145A on the right side of the inner periphery as shown in the figure.
45, and the inner peripheral side is the damper driven plate 158
A reaction cone 146 is fixed to A and has an outer periphery as a conical engagement surface 146A corresponding to the conical engagement surface 145A of the pressure cone 145, and the pressure cone 145 and the reaction cone 1.
46, whose inner peripheral edge is spline-fitted to the clutch disc wheel 139, and which corresponds to the conical engagement surface 145A of the push cone 145 and the conical engagement surface 146A of the reaction cone 146.
The torque transmitting cone 147 has friction materials 147C and 147D on conical engagement surfaces 147A and 147B formed on the inner and outer circumferences of the torque transmitting cone 147, respectively. Further, a wave ring 148 having elasticity in the axial direction is interposed between the outer peripheral side of the pressing cone 145 and the damper driven plate 158A.

[Brief explanation of drawings]

FIG. 1 is a sectional view of the power transmission device according to the prior application, FIG. 2 is a side sectional view of an embodiment of the power transmission device of the present invention, FIG. 3 is a perspective view of the wave ring, and FIG.
The figure is a side sectional view showing how it is incorporated into a vehicle transmission, and FIG. 5 is a side sectional view of another embodiment of the power transmission device of the present invention. 101...Human power axis, 103...Output axis, 110
... Fluid coupling, 113 ... Pump impeller (pump), 114 ... Turbine impeller (turbine), 1
30... Conical clutch for power cutoff, 145... Pressing cone (driving member), 146... Reaction cone (driving member), 147... Torque transmission cone (driven member),
190... Servo mechanism.

Claims (1)

[Claims] 1. An input shaft connected to a power source, an output shaft disposed concentrically with the input shaft, a pump connected to the input shaft, and power transmission via the pump and fluid. a power cutoff conical clutch disposed between the turbine and the output shaft to disconnect the driving connection between the input shaft and the output shaft, and a servo mechanism for controlling engagement and release of the conical clutch. The conical clutch has a driving member connected to the turbine and a driven member connected to the output shaft, the driving member being rotatably supported by the input shaft, and the driven member being connected to the output shaft. A power transmission device, characterized in that the conical clutch is rotatably supported, and the conical clutch is disposed radially inward of the pump. 2. The power transmission device according to claim 1, wherein the drive member has a hub that supports the turbine radially inward. 3. The conical clutch has a pressing cone and a reaction cone as driving members, a torque transmitting cone as a driven member,
3. The power transmission device according to claim 2, further comprising a wave ring as means for applying a load in a direction to separate the pressing cone and the reaction cone from each other. 4. The pressing cone and the reaction cone each have a conical engagement surface on their inner peripheral sides, and the torque transmission cone has a
4. The power transmission device according to claim 3, further comprising two conical engaging surfaces corresponding to the conical engaging surface of the pressing cone and the conical engaging surface of the reaction cone on the outer peripheral side. 5. The pressing cone has a conical engagement surface on the inner peripheral side,
The reaction cone has a conical engagement surface on the outer circumferential side with an inclination corresponding to the conical engagement surface of the pressure cone, and the torque transmission cone has a conical engagement surface of the press cone on the outer circumferential side and an inner circumferential side, respectively. 4. The power transmission device according to claim 3, further comprising a conical engagement surface corresponding to the conical engagement surface of the reaction cone. 6. The servo mechanism includes a sliding sleeve, a diaphragm spring whose end is locked to the sliding sleeve, and a pressing ring engaged with the diaphragm spring. The power transmission device according to item 2.