JPS60179534A - Power transmission device - Google Patents

Abstract

PURPOSE:To reduce the amount of trail brought about in a power cut-off clutch, by using a conical clutch as the power cut-off clutch. CONSTITUTION:In a power transmission device 100 composed of a fluid coupling 110, a power cut-off clutch 130, a direct coupling clutch 10 and an oil pump, the power cut-off clutch 130 further comprises a pressing conical member 145 and a counter conical member 146 which are splinedly fitted into a clutch drum 134, and a torque transimitting conical member 147 which is splinedly fitted into the clutch hub 137. With this arrangement trail may be prevented between the conical engaging surfaces 145A, 146A of the pressing and counter conical members 145, 146 and frictional engaging members 147C, 147D on the conical engaging surfaces 147A, 147B of the torque transmitting conical member 147. Thereby the amount of trail brought about in the power cut-off clutch may be made small.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field] The present invention relates to a power transmission device that engages an input shaft and an output shaft.

[Prior art] This #! P revision application applicant f! fi Showa 58-240588
In No. 1, as shown in Fig. 1, there is an input shaft 101, an output shaft 103 coaxially disposed on the input shaft 1. A fluid coupling 110 disposed between a front cover 111 and a rear cover 11OA of the transmission device +00, the input shaft 101 and the output shaft 103, and provided on the outer periphery of the front cover Ill and rear cover 11OA;
An oil pump 170 is provided in parallel to the fluid coupling 110 at the center of the front cover 111 and the rear cover 11OA, and is driven by relative rotation between the input shaft 101 and the output shaft 103, and the front cover 11
1. The oil pump cover 177 and the output shaft 103 are arranged in the center of the fluid stepper, 110A, and the oil pump 170 in the rear cover 110A, and are located on the inner periphery of the clutch disc flap 1/158A of the power cutoff clutch 130. The output shaft 103 is connected to the input shaft 10 in a detachable manner.
a power cutoff clutch 130 that is engaged by being pushed in the axial direction toward the input shaft 101; and a direct coupling clutch 1o that connects the input shaft 101 and the power cutoff clutch 130 in a detachable manner.
A thrust belt is disposed between the oil pump cover 177 and the inner walls of the front cover 111 and the rear cover 11OA, and supports an axial pressing force for engagement of the power cutoff clutch 130. A power transmission device 100 comprising a ring 18 is proposed. This power cutoff clutch 130 is composed of a plate clutch, and if the load applying means is a disc spring or a coil spring, it is not possible to apply a large load, so the required torque capacity is achieved by increasing the number of plate clutches. It was secured. However, there is a problem in that increasing the number of plate clutches increases the amount of drag of adjacent plate clutches when the plate clutches are disengaged.

[Eleventh aspect of the invention 1] The object of the invention is to reduce the drag generated in the power cutoff clutch by replacing the plate clutch with a conical clutch.
The purpose of the present invention is to provide a power transmission device that can provide a large amount of power.

Configuration 1 of the Invention The power transmission device of the present invention includes a human power shaft, an output shaft coaxially disposed on the human power shaft, and a power transmission device case connected to the input shaft and rotatable around the output shaft. a pump impeller provided on the inner circumferential portion of the power transmission device case; 11 turbine blades driven by receiving fluid from the turbine inside the power transmission device case; and the turbine blades. It is comprised of a power cutoff conical clutch that removably connects the vehicle to the output shaft and is pressed into engagement, and a servo mechanism that applies a pressing force to the power cutoff conical clutch.

[Effects of the Invention 1] With the above configuration, the power transmission device of the present invention has the following effects.

b) By configuring the power cutoff clutch as a conical clutch, the amount of drag generated by the power cutoff clutch can be reduced.

Mouth) By configuring the power cutoff clutch as a conical clutch, a large amount of torque can be transmitted.

c) By configuring the power cutoff clutch as a conical clutch, the number of parts can be reduced compared to the conventional plate clutch, and assembly can be facilitated, thereby reducing production costs.

Embodiment J The power transmission device of the present invention will be explained based on an embodiment shown in FIG.

The power transmission device 100 includes a fluid coupling +10 provided in a power transmission device case 109, a power cutoff clutch 130 provided inside the power transmission device case 109, a direct coupling clutch 10, and an input member and an output member of the fluid coupling 110. and an oil pump 170 provided in between.

The fluid coupling 110 includes a front cover III, a, which is connected to the input shaft 101 of the power transmission device 100, which is connected to the crankshaft of the engine.
A pump impeller 113 disposed around the inner wall of the rear cover 11OA, a turbine impeller 114 disposed opposite to the pump impeller 113, and a turbine shell 115 holding the turbine impeller 14 are provided. The tip of the gear transmission 200 at the center of the front cover II+ is the drive shaft +08 of the oil pump 170, and the middle part is the oil pump cover 17 of the oil pump 170.
An input shaft 101 serving as an oil pump housing holding shaft 107 supporting the oil pump housing 7 is provided through the input shaft 101 . Further, the cylindrical portion 11 is formed with an annular direct-coupled flange frictional engagement surface 111A parallel to the axis on the outer circumference of the inner wall of the front cover 111.
1B are installed in series.

In the power cutoff clutch 130, the hub-shaped portion 116 of the turbine shell 115 is welded to the outer circumference, a guide ring 144 for centering the rear damper drive plate 158B is press-fitted, and an inner spline 1 is attached to the inner circumference.
A cylindrical clutch drum 134 is formed with 33 and is a backing plate of the power cutoff clutch 130, and the clutch drum is welded together. Front damper drive plate 1-158c: has the rear damper drive plate 158B to which power is transmitted from the direct clutch 10 on the left side, and a thrust bearing 19 and bearing race 19A on the right side.
A damper driven plate 158A is rotatably supported on the front cover 111 via a damper driven plate 158A whose inner peripheral portion is welded to the oil pump body 17OA of the oil pump 170, and an output (not shown) to the power transmission device 100. A hub portion 135 spline-fitted to the shaft, and a clutch hub portion 137 having an outer circumferential spline 13B formed at a position corresponding to the inner spline 133 of the clutch drum 134. and the hub portion 135 and the clutch hub portion +
A flanch disk wheel 138 consisting of a disk portion 138 connecting to the clutch drum +3, the outer periphery of which is connected to the clutch drum +3
4 and a power cutoff conical clutch 130A spline-fitted to the clutch hub portion 137. The power cutoff conical clutch 130A has a pressing cone 145 fitted into the clutch drum 134 and a reaction inner t10.
46 and a torque transmission cone 147 spline-fitted to the clutch hub portion 137, ) 1 (j) The pressing cone 145 and the reaction inner portion 3114e are conical engagement surfaces having moderately inclined surfaces facing each other on the inner circumferential side. 145A and 14
6A is formed, and the torque transmission conical engagement surface 145A and the conical engagement surface 148 of the reaction cone 14B
Two conical engagement surfaces 147A and 147B corresponding to ^
are formed, and friction materials 147C and 147 are formed on the conical engagement surfaces 147A and 147B to increase the frictional force during engagement.
D is provided. Suppression cone 145 and reaction cone 14E
As shown in FIG. 3, a wave ring 148 is interposed between the outer peripheries of i, which is a ring exhibiting a bent wave shape and has elasticity in the axial direction of the ring.
8 is arranged to push apart the suppression cone 145 in the axial direction when the power cutoff conical clutch 130A is disengaged, and the conical engagement surface 145A of the pressure cone 1'45 and the reaction cone 146, 1
46A and a conical engagement surface 147A of the torque transmission cone 147.
, 147B from dragging with the friction materials 147G, 147D.

The direct coupling clutch 10 has the front cover I11 on the outer periphery.
Frictional engagement surface 11 formed on the inner circumferential surface of the cylindrical portion 1118 of
1A, and a friction retainer 11 supported on the outer periphery of the rear damper drive plate 158B.

In this embodiment, an internal gear pump is used as the oil pump 170, and is provided on the inner peripheral side of the clutch disc wheel 138. In this oil pump 170, the oil pump cover 177 and the oil pump body 170A are fixed at the outer peripheral portion with ribs 178,
The inner periphery of the power transmission device 100 is 7. Oil is brought into contact with the disk portion 138 of the clutch disk wheel 139 via a thrust bearing 176 that is loosely fitted to a small diameter portion at the tip of an output shaft (not shown) via an oil seal 175. Pump body 170A and the oil pump body 17
An oil pump internal gear 172 is rotatably fitted into a gear room provided next to the 0A engine, and an oil pump external gear 171 is fitted to the tip of the human power shaft 101.
and an oil suction port 174 connected to an oil passage formed at the center of an output shaft (not shown) and communicating between the oil pump cover 177 and the front cover 111.

FIG. 4 shows the power transmission device 100 of the above embodiment as a front-engine, front-drive vehicle transmission consisting of a gear transmission 200 for five forward speeds and one reverse speed, a differential mechanism, and a transmission case 300 housing these. This is an example used in

The transmission case 300 has an engine fastening surface 301 open 1.
A gear transmission 200 has a side wall 302 formed thereon and a shell-shaped starting device case 303 in which the power transmission device 100 is housed, and one end surface is fastened to the side wall 302 of the starting device case 303. A gear transmission case cover 305 is fastened to the left end surface of a cylindrical gear transmission case 304 in which the gear transmission case 200 is housed, and the starting device case 30
3, and a differential cover 307 that covers the left side opening of the differential case 308 and is formed integrally with the gear transmission case 304.

The gear transmission 200 has a known configuration, with the output shaft 103 of the power transmission device 100 being an input shaft, and an output shaft parallel to the input shaft.
201. Dog clutch 20 for switching between 1st speed and 2nd speed
2. Dog clutch 203 for switching between 3rd speed and 4th speed
, and a fifth speed switching dog clutch 204.

A servo mechanism 190 that engages and disconnects the power cutoff conical clutch 130A is connected to a clutch pedal provided in the driver's seat or a transmission mechanism 191A that operates according to automatic supply and discharge of intake negative pressure or oil pressure. connecting rod 191
a pressing rod 182 rotated around a fulcrum 1113 by the connecting rod 191; a bearing 195 supported by a flange 194 abutting the tip of the pressing rod 182;
A sliding sleeve 19B fitted into the bearing 195 and an inner peripheral edge of the sliding sleeve 186
Diaphragm spring 187 locked on the right end of
and a suppression ring 193 that is engaged with the outer circumferential edge of the diaphragm spring 197 to press the suppression cone 145 in the axial direction via a thrust bearing 198 and supports the pressing force of the diaphragm spring 197, and the outer circumference of the oil pump cover 177. A bearing race support 19A attached to the damper driven plate 158A attached to the side 12J, a bearing race 19G supported by the bearing race support 19A, and the front cover 11
1, and is held by an L-shaped bearing race 19D, and the bearing race 190 is held by an annular plate-shaped bearing holding member 19B. 1
The release and sliding (half-clutch) of 30 is achieved by manually or automatically driving the transmission mechanism.

205 is a differential mechanism in which front wheel drive shafts 20B and 207 are arranged in 41 rows on the input shaft and output shaft 201 of the gear transmission 200.

In the servo a mechanism 1110 of the power transmission device 100, when the connecting rod 191 is moved to the left in the drawing manually or automatically, the pressing rod 182 rotates to the left around the fulcrum 193, and the sliding sleeve 19fi is moved to the engine via the bearing 185. direction. As a result, the sliding sleeve 196 causes the center of the diaphragm spring 187 to bulge out toward the engine, and the suppression ring 199 connected to the outer periphery of the diaphragm spring 187 becomes freely displaceable to the left in the figure. This action causes the wave ring 14 to rebound in the axial direction, the suppression cone 145 and the reaction cone 146 are separated, and the power cutoff conical clutch 130A is released. In this state, the power is cut off by the power cutoff clutch 130, so that the gear transmission 200 can perform a speed change operation.

When the connecting rod 11111 is operated manually or automatically to the right in the figure, the sliding sleeve 198 is displaced to the left in the figure by the return force of the diaphragm spring 197.
The suppression ring 199 is pressed against the engine, the wave ring 148 contracts in the axial direction, and the conical engagement surfaces 145A, 148A of the suppression cone 1H45 and the reaction cone 146, and the conical engagement surface 147^ of the torque transmission cone 147, The input shaft 101 and the output shaft 103 of the power transmission device +00 are engaged with the friction materials 1470 and 1470 provided on the 147B, and the input shaft 101 and the output shaft 103 of the power transmission device
connected via.

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

The power cutoff conical clutch 130A of the power transmission device 10 (l) of this embodiment is spline-fitted to the clutch drum 134 on the outer side, and has a moderately inclined conical engagement surface 145A on the right side of the inner periphery in the figure. a pressing cone 145; a reaction port @ 14Ei whose inner peripheral side is fixed to the damper driven plate 15nA and whose outer periphery has a conical engaging surface 14bA corresponding to the conical engaging surface 145A of the pressing inner fi 145; and the suppressing cone 145. A conical engagement surface 14 is disposed between the reaction cone 14B, has an inner peripheral edge spline-fitted to the clutch disc wheel 139, and corresponds to the conical engagement surface 145A of the suppression cone 145 and the conical engagement surface 146A of the reaction cone !46.
7A and 147B, and a friction material 147C is formed on the conical engagement surfaces 147A and 147B formed on the inner and outer peripheries of the torque transmission port M 147.
1147D is provided. 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 the drawing]

FIG. 1 is a sectional view of a conventional power transmission device, FIG. 2 is a side sectional view of an embodiment of the power transmission device of the present invention, FIG. 3 is a side view of a wave ring, and FIG. 4 is a power transmission device of the present invention. FIG. 5 is a side sectional view of a vehicle transmission incorporating an embodiment of the transmission device. FIG. 5 is a side sectional view of a vehicle transmission according to another embodiment of the power transmission device of the present invention. In the diagram 101... Input shaft 103... Output shaft lo9
・Power transmission case 113...Pump impeller +1
4...Turbine impeller 130A...Conical clutch for power cutoff 145...Suppression cone 14B...Reaction cone 1
．． 47... Torque transmission cone 148... Wave ring 180... Servo mechanism agent Kenji Ishiguro Figure 3

Claims (1)

[Scope of Claims] l) An input shaft, an output shaft disposed coaxially with the input shaft, a power transmission device case connected to the input shaft and rotatable around the output shaft, and the power transmission case. a pump impeller provided on the inner circumference of the device case; a turbine impeller driven by receiving fluid transmitted from the turbine inside the power transmission device case; and the turbine impeller and the output shaft. A power transmission device comprising a power cutoff conical clutch which is detachably connected to the power cutoff conical clutch and is pressed into engagement, and a servo mechanism which applies a pressing force to the power cutoff conical clutch. 2) The power cutoff conical clutch includes a suppression cone and a reaction cone that receive the relative rotation of the fluid coupling, a torque transmission cone that receives rotational torque of the fluid coupling due to the pressing force of the suppression cone and the reaction cone, and 2. The power transmission device according to claim 1, comprising a cone and a wave ring that is a resilient member that separates from each other when no pressing force is applied to the reaction cone. 3) The pressure cone and the reaction cone each form a conical engagement surface having moderately inclined surfaces facing each other on their inner peripheries, and the cone engagement surface of the suppression cone and the reaction cone are formed on the outer periphery of the torque transmission cone. Claim 2, characterized in that two conical engagement surfaces corresponding to the conical engagement surfaces of the cone are formed.
The power transmission device described in section. 4) The pressing cone has a conical engagement surface having a moderately inclined surface on the inner periphery, and a conical engaging surface having an inclined surface corresponding to the conical engaging surface of the pressing cone on the outer periphery of the reaction cone. and a conical retaining surface corresponding to a conical retaining surface of the pressing cone and a conical engaging surface of the reaction cone is formed on the outer periphery and the inner periphery of the torque transmission cone. The power transmission device according to item 1. 5) The servo mechanism engages a sliding sleeve, a diaphragm spring whose end is engaged with the sliding sleeve, and the tire flam spring in order to operate the power cutoff clutch from outside the power transmission case. 2. The power transmission device according to claim 1, further comprising a suppression ring which is brought together to press the power cutoff clutch.