JPS6011733A - Transmission device for vehicle - Google Patents

Abstract

PURPOSE:To enable parking without providing an exclusive parking mechanism, by furnishing a starting unit with a spring mechanism, an interlocking means for transmitting the urging force of the spring mechanism to a direct driving unit, and a servomechanism. CONSTITUTION:A starting unit 1 is provided with a diaphragm spring 197 for applying spring load to engage a motive power cutoff clutch 13 and a high gear clutch 15, and with a servomechanism 19, which causes a servo-force countering the spring load, so that the clutches 13, 15 are engaged by the spring load of the diaphragm spring 197 if the servomechanism 19 is not operated during the stoppage of an engine. For this reason, a vehicle is put in a parked state due to the frictional torque of the engine. Parking is thus enabled without providing an exclusive parking mechanism.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vehicle starting transmission device (hereinafter referred to as a transmission device) that combines a fluid coupling such as a torque converter or a fringe coupling and a fluid-phase direct coupling clutch.

Conventionally, in this type of transmission device, the driving side element (pump impeller) and the driven side element (turbine run t) are not mechanically connected during stop 1, so when parking the vehicle with the engine stopped, the engine The vehicle could not be parked due to the 1-lux of friction. Therefore, in a vehicle using such a vehicle transmission device, it is necessary to separately provide a dedicated parking mechanism, which requires installation space, resulting in a large size, resulting in an increase in weight and cost.

[1] The first object of the present invention is to reduce engine wear and tear during parking when the engine is stopped, without the need for a separate parking-dedicated mechanism.
! ] ~ To provide a transmission device that can perform parking using torque.

The transmission device of the present invention includes an input shaft for transmitting engine drive, an output shaft disposed concentrically with the human power shaft, and an output shaft disposed concentrically between the input shaft and the output shaft. A pump to be connected, a fluid coupling having a turbine directly connected to the output shaft, a case, and a direct connection device that can freely connect and control the input shaft and the output shaft are connected to the starting 1A position, and to the output shaft. In a vehicle transmission device comprising a transmission device that is directly coupled to the transmission device and maintains the directly coupled state when the engine is stopped, the starting device includes a spring mechanism that applies a bias μ to the directly coupled device;
A servo mechanism including an interlocking means for transmitting force to the direct connection device to maintain the direct connection state by the spring mechanism, and a servo force generating means for opposing the force urged by the spring mechanism. , the engine stop mechanism controls the direct connection device to the second lever of IB.
At one time, the direct coupling device is engaged and the parking state is maintained.

The present invention will now be illustrated and explained based on poly-examples.

FIG. 1 shows a three-shaft small dual-purpose transmission according to a first embodiment of the present invention, in which a transmission device 1 according to the present invention used as a starting device, a gear shift m6 for 4 forward speeds and 1 reverse speed are shown. It consists of a differential 7 and a range torque mechanism, and a transmission case 10 that houses them.

In the transmission case 10, the engine fastening surface 10Δ is opened and the gear shift Ia6 side (outer side shown, hereinafter referred to as outer side)
has a shell-like starting device case 10G formed with a side wall 10[3 and housing the transmission device 1; and a cylindrical starting device case 10G having one end surface fastened to the side wall 10B of the starting device case 10C and housing a gear transmission. gear transmission case 10D; and gear transmission case 10. A gear transmission tars cover 10E fastened to the left end surface of D, and a differential case 10F (second
(Illustrated in FIG. 2), and a differential differential force bar 10G (illustrated in FIG. 2) that covers the left side opening of the gear transmission case and is integrally formed with the gear transmission case 10D.
It consists of

The transmission 1 PII device 1 is provided in the starting device case 10C, and is a transmission device case 1 in which a transmission device is kicked inside.
A, a free unit coupling (hereinafter referred to as a coupling) 11 installed on the outer periphery of the transmission case 1A, and a power supply installed inside the transmission case 1A in the radial direction. A disconnection clutch (hereinafter referred to as the clutch) 13, a direct coupling clutch 15 installed on the outer periphery of the coupling 11 (hereinafter referred to as the right side) where the engine is located in this embodiment, and 1
An oil pump 17 is installed between the input member and the output member of the clutch 13, and the oil pump 17 is installed on the left side of the clutch 13 inside the transmission case 1A. A diaphragm spring 197 that applies a spring load (pressing force) for engagement, and a side wall 101 of the transmission case 1Δ and the starting device case 10C outside.
3, the link v of the die Al flamm spring generates a servo force that opposes the spring load applied to the clutch 13 and the direct coupling clutch 15.
Servo mechanism 1 of clutch 13 that shifts 1'f619o to the right
It consists of 9.

The coupling 11 is connected to a front control cover 111 connected to an input shaft 101 of a transmission device connected to an engine crankshaft via a drive plate 102, and on the outer periphery of the front cover 111 on the left side. The transmission case 1Δ is made up of welded annular plate-shaped rear covers 110 to 4, an annular pump seal 112 circumferentially fixed to the outer side of the inner peripheral wall surface of the rear cover, and an inner wall of the pump shell 112. A pump blade 113 disposed around the pump blade, a turbine blade 114 disposed opposite to the pump blade, and a turbine shell 115 holding the turbine blade 114 are included. Said sword cover 1
At the center of 11 (the large diameter part near the engine is the pyrower 1-boss 105 that fits into the pilot hole 104 installed in the center of the end face of the input shaft 101, and the left one has the tip of the oil pump 17). A drive @ 106 is provided, and the intermediate shaft holds the clutch plate shaft 134 of the clutch 13.
The center axis 108 that has been returned to 07 is now [t]. Furthermore, a cylindrical portion 111C in which an annular direct coupling clutch face 111Ac15 and an inner circumferential spline 111B are formed is connected to the outer periphery of the inner wall of the flon 1 to the cover 111. The turbine shell 115 is connected to the output horn shaft 103 of the transmission via a clutch 13 disposed radially inwardly within substantially the same axial section as the turbine shell 115. teeth,
A flange portion 131 extending in the radial direction fj at the left end is slidably fitted into a hub-like portion 116 provided on the inner periphery of the turbine shell 115, and a flange portion 131 is extended in the radial direction at the right end. A cylindrical clutch plate 1 with an inner circumferential line 133 formed on the inner periphery, with a narrow support wall 132 welded to a disk plate 158 of a cross-coupling clutch 15 (to be described later), a case 134, etc., and an output of the transmission device. a hub portion 135 spline-fitted to the clutch plate 1; a clutch drum portion 137 having an outer peripheral spline 13θ formed at a position corresponding to the inner cylinder line 133 of the case 134;
J5, a clutch disc wheel 139 consisting of a disc part 138 that connects the hub part 135 and the drum part 137, and the outer periphery of the clutch disc wheel 139 that connects the clutch plate 1-coos 134.
A plurality of clap plates 141 spline-fitted to the
The inner periphery is spline-fitted to the drum portion of the clutch disc wheel 139, and the clutch plate 14
It is made up of clutch disks 143 that are stacked alternately.

The direct coupling clutch 15 has the Freon 1-cover 11 on the outer periphery.
A plurality of clutch plates 151 are joined to the spline 1 on the inner periphery spline 111B of the cylindrical part of 1, an annular direct clutch press plate 152 fixed to the outer circumference of the turbine shell 115, and a circumferential portion from the press plate 152. a large number of clutch disc holding arms 153 protruding in the axial direction in a shape;
A plurality of clutch disks 154 whose inner peripheries are spline-fitted to the holding arm 153 and alternately overlapped with the clutch plates 151, and a central hub portion 155 are connected to the central shaft 10.
It is rotatably supported by the disc plate holding shaft 107 of No. 8 via a metal bearing, and the outer periphery 156 is attached to the damper 15.
A disk plate 158 is spline-fitted to the holding arm 153 via a disk plate 158 via a thrust bearing 160 by a spring 159 inserted into the center of the front cover 111. Become.

In this embodiment, an internal gear pump is used as the oil pump 17, and is installed between the disk plate and the disk portion 138 of the disk wheel in the Taratsuji disk boiler 139.

This A-il pump 17 is fixed to the disk plate 158 with a3 on the outer periphery, and the thrust bearing 17 is loosely fitted into the tip small diameter part 103 F'3 of the output +11+ 103 of the transmission device via the Δ-il seal 115 on the inner periphery.
Disc part 13 of the clutch disc wheel via 6
8, the casing 170, etc.
0 engine is equipped with internal teeth l'!!1JTJ, 172, which are rotatably fitted into the pulled gear 1 flume, and external teeth c, which are spline-fitted to the tip of the central shaft 108.
! an inlet II 114 connected to the oil passage 103Δ formed in the center of the output shaft 103 and provided in the casing 170; ~Cover 11
1 and a discharge port 174 communicating with the discharge port 174.

The servo mechanism 19 of the gangway 13 is connected to the A7 noram spring 197 and J provided in the transmission device U case.
: and the link mechanism 19 provided outside the transmission gear.
Consists of 0. The link mechanism 190 is a clutch pedal installed in the driver's seat, or a servo mechanism (1' shown in the figure) that operates in response to the automatic supply and discharge of intake pipe negative pressure or oil pressure.
a connecting rod 191 connected to the connecting rod, and a hole 10) whose rear end is connected to the connecting rod and formed in the peripheral wall of the starting device case IOC.
-1 to the left side of the transmission case 1A and side wall 1
A clutch lever 192 rotated around a fulcrum 193 protruding from 0B, and a tip 19 of the clutch lever 192.
a bearing case 194 having a flange 194A engaged with the bearing case 194; a bearing 195 fitted into the bearing case 194; and a right side portion fitted into the bearing 195 that is connected to the inner periphery of the rear cover 110 and the output shaft 103.
The sliding sleeve 196 is inserted into the transmission case 1Δ from the gap between the sliding sleeve 196 and the inner peripheral edge thereof is locked to the right end of the sliding sleeve 19G, and the left side of the clutch 13 in the transmission case 1A is inserted into the transmission case 1A. The diaphragm spring 197 disposed on the side has a pressing ring 199 that is engaged with the outer circumferential edge of the diaphragm spring 197 and presses the glitch 13 via a thrust bearing 198, and the clutch 13 is released. J3
and sliding (half-clutch) are performed manually or automatically.

Further, the 1/1 small mechanism 19 of this clutch 13 also serves as a servo mechanism of the direct coupling clutch 15, and the spring cart of the die A7 flamm spring 197 is connected to the flange portions 13J3 of the clutch plates 1 to 134 and the turbine shell 115.
When the ζ double-coupled clutch suppression plate 152 is pressed through the ζ, the direct-coupling clutch 15 is engaged.

The gear transmission 6 has a known configuration, and connects the output shaft of the transmission device to input shafts V71 and 61 to shafts 1 and 1, which are parallel to the input shafts 1 and 1, respectively.
, a dog clutch 62 for switching between first speed and second speed, a dog clutch 63 for switching between third speed and fourth speed, and a reverse gear (not shown).

This transmission operates as follows. 1noichibo mechanism 1
9 is not operated and the diaphragm spring 197 applies a spring load to the clutch 13 and the direct coupling clutch 15, the clutch 13J3 and the direct coupling clutch 15 are engaged by the spring load of the diaphragm spring 197.

Therefore, since the engine is mechanically connected to the wheels via the transmission and the gear transmission 6, the vehicle can be brought into a parking state by the engine's friction of 1 to 1 lux.

Servo mechanism 19 for clutch 13 and direct clutch 15
When the connecting rod 191 is operated manually or automatically to the left in the figure, the clutch lever 192 rotates to the left about the fulcrum 193, thereby displacing the sliding sleeve 19G toward the engine via the bearing 195. In addition, the resliding sleeve 196 bulges out the center of the die A7 flamm spring 197 toward the engine, and the die
7 Pressing ring 1 connected to the outer periphery of the flamm spring 197
99 is displaced to the left in the drawing. This action releases the multi-disc clutch 13.

Also, the release of the pressing force on the clutch by this diaphragm spring 191 is applied to the gangway play 1 of the clutch, the case 134, the turbine shell 115, and the direct-coupled clutch press plate 152. Clutch 15 is also released. In this state, the power is connected and disconnected by the clutch 13, so that when the vehicle is running, the gear shift operation (gear shift operation) is possible in J5 (gear gear shift operation is possible in gear 6), and when the vehicle is at a standstill, the engine can be started in J3.

When the connecting rod 191 is operated manually or automatically to the right in the drawing, the sliding sleeve 196 is displaced to the left in the drawing by the return force of the die 17 flamm spring 197, and the pressing ring 199 is pressed against the engine and the C multi-plate clutch 1
3 are engaged, and the input shaft 101 and output shaft 103 of the transmission are connected via the coupling 11. The direct coupling clutch 15 operates as follows. When the turbine shell 115 and the output shaft 103 are connected as the clutch 13 is engaged, power is transmitted by the coupling 11. A thrust force is generated in the bin shell to the right in the figure, and a discharge hydraulic pressure of the oil pump 17 is also generated, so that the direct coupling clutch 15 is released against the force of the die 17 flamm spring 197. Then, as the relative rotation between the pump and the turbine becomes smaller, the thrust horn and the discharge pressure of the oil pump become smaller and engage with the die N7 flamm spring 197.

Table 1 As shown in Table 1 and FIG.
When the same 1-stroke load is applied to the direct-coupled clutch 15, the change is reversed as shown in a, but when the torque capacity of the direct-coupled clutch is reduced by t-7 as in this embodiment, it decreases as shown in (). do.

FIG. 2 shows a second embodiment of the invention.

The transmission case 10 has a frontage of 10Δ before the J carrot is fastened, and a side wall 103 is formed on the gear transmission 6 (there are four not shown, hereinafter referred to as "ganes"). A shell-like starting station case 10C in which the device 1 is housed, one end surface of which is fastened to the side wall 10B of the starting device case IOC, and a cylindrical gear transmission case 10C in which a gear transmission is housed.
D, a gear transmission case cover 1 () fastened to the left end of the gear transmission case IOD, a differential case 10F integrally formed on the side force of the starting device case, and The left side of the differential is covered with a frontage and is formed integrally with the gear transmission case 10D, and the starting device case 10C and the gear transmission case 10 [) It consists of an intermediate side wall 101 interposed therebetween, and an A-il pump cover 101 fastened to the right side wall of the intermediate side wall 10H. Flange 13 of clutch plate case 134
The clutch plate case 134 is slidably fitted into a hub-like portion 116 provided on the inner periphery of the turbine shell 115 on one side, and the supporting wall 132 of the clutch plate case 134 is fitted on the right end of the output shaft 103. It is supported so as to be freely rotatable and axially movable, and is welded to the outer periphery of a turbine disk 145 disposed between the front cover 111 and the first disk plate 139.

The oil pump 17' is an internal gear pump in this embodiment, and is welded to the center of the cover 110 as described above.
A hollow oil positive drive shaft 171 inserted into the oil pump cover 1OI from between the inner circumference of the oil pump cover 10I and the output @103, and an oil shaft formed on the left wall surface of the oil pump cover 10I. Internal gear 17 slidably and rotatably fitted into Bonplume IOJ
3. The inner periphery consists of an external gear 175 spline-fitted to the left end of the pump drive @ 171 and meshed with the internal gear, and a stage (pulled suction 1
179, and discharges hydraulic oil to a discharge port 180 formed in the oil pump cover 101, after which the hydraulic oil is supplied to a control circuit (not shown).

Reference numeral 65 denotes a differential shaft in which output shafts 651 and 652 are arranged parallel to the input shafts 17) and 1 to 1 of the gear transmission.

The hydraulic servo mechanisms 7 are arranged in four positions in the radial direction of the coupling 11 within the transmission case 1△.

This hydraulic lever mechanism 7 includes an annular cylinder 71 installed between the clutch drum section 137 on the left side of the disk section 138 of the clutch disk boiler 139 and the hub section 135, and an annular cylinder 71 installed within the cylinder 71. It consists of an annular piston 72 fitted in a slidable manner, and a hydraulic servo 70 generates a servo force opposing the spring load applied to the gangway 13J3 and the direct coupling clutch 15, and a comb-like slit is formed on the inner periphery. The piston 72 is engaged with the comb tooth-shaped protrusion 147 protruding from the disk portion 138 to the left, and the inner circumferential end is engaged with the left side of the piston 72, and the outer circumference is in contact with the right side of the clutch 13. The stacked pressing plates 73, etc., the spring retainer 74 engaged with the outer periphery of the left end of the comb-shaped protrusion 147, the spring retainer 7, etc.
4 and the suppression plate 73, and a return spring 75 that applies a spring load for engagement of the clutch 13J3 and the direct coupling clutch 15.

The actions of this hydraulic knurl (1! mechanism 1, clutch 13, and direct coupling clutch 15) will be explained.

When the hydraulic knurl 70 is depressurized, the spring load of the return spring 75 is applied to the clutch 13 via the press plate 73, and the clutch 13 is engaged, and the direct coupling clutch 15 is applied with the spring load of the return spring 75 to the clutch 13. Plate case 132, turbine shell 115, pressing plate 1
52 and is therefore engaged. As a result, since the engine is mechanically connected to the wheels via the transmission and the gear shift 81!6, the vehicle can be brought into a parking state by the frictional torque of the engine. When pressure oil is supplied from the oil passage formed in the output shaft of the hydraulic pressure 1 nervo 70, the screw 1 heng 72 is displaced to the left, displacing the pressing plate 73 to the left, so that the clutch 13 is released. Then, the direct coupling clutch 15 is also released.

In this state, the power is cut off by the clutch 13, so that the gear transmission 6 can perform a speed change operation.

Further, when the hydraulic servo 7 is disengaged, the direct coupling clutch 15 operates as follows.

The discharge oil pressure of the oil pump 17 is regulated by a control device to be described later, and is passed from the right end of the output shaft 103 through an oil passage 88 in a sleeve 107 that is fitted in a center hole 106 formed at the center of the output shaft 103. ) When supplied between the L1 channel 1~cover 111 and the disc plate h158, the Freon 1
The hydraulic pressure between the cover 111 and the disc plate 158 increases, and the hydraulic oil expands the connection between the clutch plate 151 and the clutch disc 154 of the direct coupling clutch 15 and flows from the gap A to the left side inside the transmission case 1A. flow,
The oil is provided between the oil pump drive shaft 171 and the output shaft 103 and flows out into the oil passage 87. Therefore, the direct coupling clutch 15 is released against the force of the return spring 75.

ff13 shows a third embodiment.'7Io In this embodiment, a continuously variable transmission for a vehicle is constructed by combining the transmission device of the present invention and a V-pel 1 to afterglow speed transmission. The same reference numerals as in FIG. 1 indicate the same functional parts.

In this embodiment, the transmission device 1 is composed of the same functional elements as in the first embodiment. A pump blade 113 is provided on the outer peripheral inner wall of the freon 1 to the cover, and a direct coupling clutch 15 is provided between the rear cover 110 and the turbine shell 115. Also in this embodiment, the oil pump 17 is supplied between the rear cover 110 and the disc plate 1-158.
The torque capacity of the direct coupling clutch 15 is reduced by the discharge oil pressure of the turbine, the turbine shell 1 through the turbine, and the return spring 159 inserted in the center between the rear cover 110 and the disk plate 1-158.

2 is a belt-type continuously variable transmission, 3 is a clutch servo (multilateral, 4 is a forward/reverse switching mechanism, and 5 is a differential differential mechanism.

■Pell 1 to afterglow stage transmission 2 is a hollow input shaft 21 arranged in series on the same axis as the engine output shaft, and parallel to the input shaft ■Pell 1 to afterglow stage transmission hollow output shaft 22, input shaft 21. J-, iQ FJ input pulley 23, output pulley 2 set on hollow output Q1+22, input pulley 23J5J: V-belt 25 that transmits power between the protruding horn pulley 24, and the input horn pulley 23.
Servo mechanism 26 that changes the effective diameter of the output pulley 24
It consists of a servo mechanism 27 that changes the effective diameter of the input pulley, and a cam mechanism 28 provided on the input pulley.

The input shaft 21 has a hollow shaft center and is rotatably supported by the V-pel 1 to afterglow gear transmission case 10 by bearings 211 and 212.
, the other side has an alligator outer peripheral spline 21413 and a tip screw 2
15 is formed.

The output shaft 22 has a hollow shaft center, and in this embodiment is formed integrally with a sleeve of a fixed flange, which will be described later, and is rotatably supported in the belt type continuously variable transmission case 10 by bearings 221 and 222.

The input horn pulley 23 includes a sleeve-shaped portion 233 whose one end (the right end in the figure) is brought into contact with the step 213 of the input shaft via a thrust bearing 216, and the outer periphery of the other end is provided with an outer peripheral spline 231 and a key groove 232. Sleeve-shaped part 233
A fixed flange 23A1 consisting of a flange portion 235 integrally formed with a flange portion 235 having a slit 234 around its outer circumference for detecting the rotational speed of the input shaft; and a key groove 236 corresponding to the key groove 232 of the fixed flange on the inner peripheral wall.
A movable flange 23B1 consisting of a sleeve-shaped hub part 278 in which a driven screw 237, which is a first screw, is formed on the outer peripheral wall thereof, and a flange part 239 formed integrally with the hub part 278, and a keyway. 232 and 2
Fixed flange 23△ and movable flange 2 placed in 3G
It consists of a ball key 230 that allows displacement in the axial direction with respect to 3B and integrally rotates around the axis.

The output pulley 24 has a key tF8241, a spline 242, a screw 243, a J5, and a spline 249 formed on the outer periphery, and a sleeve-shaped portion 2 formed integrally with the output shaft 22.
44, a fixed flange 24Δ consisting of a flange portion 245 formed integrally with the sleeve-shaped portion 244, and a fixed flange 24Δ that is fitted onto the sleeve portion 244 of the fixed flange 24A so as to be freely displaceable in the axial direction, and the key is attached to the inner periphery of the fixed flange 24Δ. fF+ 241 and a sleeve-shaped hub part 247 in which a key groove 254 corresponding to the fF+ 241 is provided and a driven screw 246 as a first screw formed on the outer periphery, and a flange part 248 formed integrally with the hub part 247. Movable flange 24F3183 and keyway 241
and a ball key 24 which is inserted into the interior of the fixed flange 24A and the movable flange 24B and which accommodates the axial displacement h'1 of the fixed flange 24A and the movable flange 24B and integrally rotates the fixed flange 24A and the movable flange 24B about the axis.
Consists of 0.

- The belt 25 has a working surface that comes into contact with the V-shaped working surfaces formed by the fixed flange 23Δ'tJ3J, the fixed flange 24A, the movable flange 2313, and the movable flange 24B of the input horn pulley 23 and the output pulley 24, respectively, and forms a friction surface. 251 and 252 are provided on both sides.

The input pulley's nervo 'a' R26 is a second screw threaded into the driven screw 231 of the movable flange 233 of the input pulley.
A drive screw 261, which is a screw of
31 A sleeve 262, which is a driver of a movable flange, is brought into contact with the other cam race 287 of the cam lit structure, which will be described later, through a thrust bearing 265, and the sleeve 26
2 and the case 10 and brakes the sleeve 262]・brake 263;
A cylindrical spring guide 264 arranged around the outer periphery of the sleeve 262, and the spring guide 264 and the sleeve 262
One end of the engine is connected to the movable flange 23B, and the other end is connected to a cylindrical spring guide 264.
The first upshift coil spring 26G is connected to the other end of the spring guide, and the first upshift coil spring 26G is arranged around the outer periphery of the spring guide.
The engine is connected to one end of the engine, and the other end is
The second upshift 1 connected to the other end of 262
T-th ~ - Consists of John coil spring 267.

The output pulley 1-axis mechanism 27 is the front iiL! 'ir
e A sleeve 272 that is a driver having a drive screw 271 that is a second screw that is screwed into the driven screw 246 of the flange 243 formed on the inner periphery, and the sleeve 272 and the case 10.
and 4 fixed covering wet multi-plate electromagnetic upshift brake 213, downshift 1~ torsion coil spring 274 whose both ends are connected and installed between sleeve 212 and movable flange 24B, and output shaft spline. 242 is formed, one side of the movable flange 24B side is in contact with the end surface of the sleeve 272 via the bearing 275, and the other side is connected to the bearing 242.
It is locked with a nut 27G via the inner race of 21,
A support ring 2 that supports the sleeve 272 in the axial direction
Consisting of 77.

As shown in FIG. 4, the cam mechanism 28 is fixed in the axial direction by a snap ring 218 fitted onto the input shaft 21 and a nut l-217 screwed into the screw 215 formed at the end of the input shaft. One cam race 282 is formed with an inner circumferential spline 281 which is spline-fitted with the spline 214 of the input shaft 21, and the other cam race 28.
7. A tapered roller 288 interposed between these cam races and a cover ring 289 of the roller 288.
The roller 288 is sandwiched between the working surfaces 292 and 286 of the races 282 and 287, and presses the movable flange 23B to the right in the figure in response to the rotational displacement of the input shaft 21 and the fixed flange 23A. Change the pressing force.

Next, the operation of this V-belt type continuously variable transmission will be explained.

(a) When traveling at constant speed, both brakes 263 and 273 are released.

Torque is transmitted in the following order: input 1hb 21 → one race 282 of the power ram mechanism → taper roller 288 → other race 287 → input coupler 23), V-bell 1 to 25 → output pulley 24 → output shaft 22. Ru. ■Bell l-2
! The magnitude of the torque transmitted by i is proportional to the clamping force applied to the V-pel 1 25, and the clamping pressure is applied to the movable pulley 23B and the sleeve 262 screwed with the movable pulley.
The input boom is brought into contact with the cam race 287 of No., and the input boob moves slightly in the rotational direction due to the principle of the cam ljI4M, and the pincer force FC exerted in the axial direction by the large pad roller 288 is
As shown in Fig. 5, the clamping force applied to the movable flange 23B that clamps the bells 1 to 25 is changed in proportion to the transmitted torque, as shown in FIG. Working surface of V-belt 25 and 1iI dynamic flange 23Bi1
3 and the working surface of the fixed flange 23A change, thereby avoiding a change in the clamping force for the time being. In Figure 5, Fl is the necessary clamping force to prevent the V-belt from slipping at the highest reduction ratio, 2 is the necessary clamping force to prevent the V-belt from slipping at the lowest reduction ratio, and 0 is the required clamping force for the V-belt to prevent it from slipping at the lowest reduction ratio. The clamping force when using the [S] indicates the clamping force exerted on the spring.
From the graph in the figure, it can be seen that in a V-belt continuously variable transmission using the cam mechanism 28, the clamping force and the transmitted torque are directly proportional even if the transmission 1-lux is less than 5 kgm, and unnecessary clamping force is generated between the V-belt and the pulley. It can be seen that the reduction is significant.

(b) Upshift 1- engages the brake 273 (
It will be done.

The sleeves 2G2 and 272 rotate relative to the sleeve parts 278 and 247 of the movable flange, and the movable flange 23
The movable flange 24B is displaced toward the right side in the figure to increase the effective diameter of the input pulley 23, and the movable flange 24B is
The effective diameter of the gear is shifted in the direction of decreasing (to the right in the figure), and the gear ratio is reduced. When the gear ratio reaches the control set value, plays 4.263 and 273 are released.

The first hexion spring 274 of the V-bow mechanism of this upshift first output pulley is twisted to store energy.

(c) A downshift is performed by engaging the brake 263.

When the brake 263 is engaged, the sleeve 262 is fixed and the movable flange 23B is displaced in the direction of decreasing the effective diameter of the input pulley 23 (to the left in the figure).
4 rotates and returns the sleeve 272, displacing the movable flange 24B in the direction of increasing the effective diameter of the output boob (to the left in the figure). The movable flange 23 of this input pulley 23 [
The displacement 3 is performed against the pressing force of the movable flange 23B by the cam mechanism. When the gear ratio reaches the control set value, the brake 263 is released. During this downshift, the first and second upshift members 26 - springs 266J3J and 267 are twisted and energy is accumulated.

In this V-pel 1~afterglow gear transmission-(ha pre m: 1-
If the electromagnetic player of the 263 or 273 malfunctions and the brake becomes inapplicable, the a5 can still be driven with the same gear ratio as before the malfunction. Therefore, in the case of a V-belt type continuously variable transmission in which the gear ratio is changed by hydraulic pressure 4-no-vo, careless changes in the gear ratio such as oil 11 leakage can be prevented, resulting in excellent safety.

The clutch servo IfHf 43 that generates a servo horn that opposes the spring load applied to the clutch 13 and the direct coupling clutch 15 includes an operating section 33 that operates the clutch;
A bushing rod 35 inserted through the input shaft 21, a clutch pedal 36, and a clutch pedal link mechanism 3
Consists of 7. The operating section 33 includes a bushing lever 331 pivotally connected to the transmission case 10, a sliding key/tub 333 provided on the transmission case, and a bushing rod 35 whose other end contacts a spring end 352, and a release bearing 335. It consists of a bearing race 337 rotatably supported on the inner wall of the sliding cap 333 via the bearing race 337. When no servo force is acting on the servo mechanism 3, the diaphragm spring 312 presses the clutch 13 to engage it, and also engages the direct coupling Clara'/-15 via the clutch brake 1-case 134 and turbine shell 115. I'm making it match. When the bushing lever 331 is rotated counterclockwise around the fulcrum by manual operation with the foot or hand, the sliding cap slides against the engine and pushes the bushing lever 35 against the engine. 13
The center of the diaphragm spring 312, which applies a spring load (pressing force) for engagement of J5 and the direct coupling clutch 15, is displaced in the direction of the engine, and the pressure plate is moved towards the engine, and the clutch 13 and the direct coupling clutch 15 are moved. unlock. The clutch pedal link mechanism 37 consists of a link lever 361 that is fixed together with the push lever 331 and arranged outside the transmission case 10, and a cable 362 that connects the free end of the link lever 361 and the clutch pedal 3G. In this embodiment, when the driver depresses the clutch pedal 36, the clutch servo mechanism 3 connects the cable 362 and the link lever 361.
The bushing lever 331 is rotated around the fulcrum via the lever 331, and as described above, the YR release and sliding (half-flat 'f-) of the clutch are performed manually. Note a3: The clutch may be controlled automatically as in the first embodiment.

The forward/reverse switching mechanism 4 includes a dog clutch 41, first simple planetary gearlets 1 to 43, and a second thimble planetary gear set 45.

Dog clutch 41 (linked to the operating lever)
A-ri 411, a brake sleeve 413 that is engaged with the fork and slid in the axial direction, and a first gear 415 (
spline piece), second gear 417 (spline piece), installed between sleeve 413 and second gear 417 (spline piece), second gear 417 (spline piece),
) consists of a synchronizer gear 419 (synchronizer ring).

The first planetary gear set 43 is formed on a ring gear shaft 430 that is spline-fitted to the spline 249 provided on the output shaft 22 of the belt front gear shift assembly.
Non-gear 431, second gear 417 of dog clutch 41
When connected to the second brane gear set 1 to 4
Ring gear 433 connected to lean gear 4;) 1 of 5;
, is connected to the first gear 415 of the dog clamp 41, and is also connected to the second ring gear 453. V
The second planetary gear set 45 includes the sun gear 451, the ring gear 453, and the output three 1450 connected to the gear box of the full circle mechanism, and the spline 459 has a spline. 1. Combine f and kya l no jy 45
Consists of 5 and 457 planetary gears. This forward/reverse switching mechanism 41 is manually or automatically engaged with the sleeve 413 of the lug clutch 41 or the second gear 417, and the ring gear 433 and sun gear 451 are connected to the case 1.
When it is fixed at 0, the setting changes) * A specific forward movement is made, and the sleeve 413 meshes with the first gear 415 and the key jy 1
Month? When the ring gear 435 and the ring gear 453 are fixed to the case 10, there is a backward motion at the set gear ratio.

A differential machine (in other words, the output sleeve 450 which is the output shaft of the forward/reverse switching mechanism 4 is used as an input shaft, the gear box 52 integrally connected to the input shaft 450, the differential amount gears 53 and 54, and the differential gear 53, 54, Differential amount gear 55.56 meshed with the small dynamic gear /, one output shaft 57J3J spline-fitted to the differential amount gear; and second ring gear 431, 451, and the other output shaft 58 inserted through the protrusion sleeve 450.

As described above, the vehicle transmission device of the present invention includes an input shaft that transmits engine drive, an output shaft that is disposed concentrically with the input shaft, and an output shaft that is disposed concentrically between the input shaft and the output shaft. a pump connected to the input shaft, a fluid coupling connected to the turbine directly connected to the output shaft, a case d5, a starting device connected to the direct connection device capable of freely connecting and controlling the input shaft and the output shaft, and the output shaft. The vehicle Kawaden fII consists of a transmission that is directly connected to the engine and maintains the directly connected state when the engine is stopped.
In the device, the starting device is biased by the spring mechanism, including a spring mechanism that biases the direct coupling device, and interlocking means that transmits the biasing force of the spring mechanism to the direct coupling device to maintain the direct coupling state. The engine is equipped with a servo mechanism equipped with a servo force generating means that resists the force exerted by the engine, and the servo mechanism controls the direct coupling device in a freely engaging and disengaging manner, and when the engine is stopped, the direct coupling device is engaged to maintain the parking state. By constantly engaging the direct coupling clutch,
Even without separately installing a dedicated parking mechanism, when parking with the engine stopped, the transmission device can be brought into a state where the torque can be transmitted, making it possible to park using the engine's friction of 1 to 1 lux. Furthermore, since the parking mechanism can be omitted, it can be easily acclimatized to Combat 1 and can be manufactured at low cost.

Furthermore, it is also possible to start the engine using the movement of the vehicle.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of a Fl complete gear transmission that combines a vehicle transmission device and a gear transmission according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view according to a second embodiment of the present invention. FIG. 3 is a sectional view of an FF automobile transmission that combines a vehicle transmission and a gear transmission, and shows a starting fluid transmission and a V-belt continuously variable transmission according to a third embodiment of the present invention. Union U 1-1:
2) A cross-sectional view of the automatic transmission, Fig. 4 is an enlarged view of the cam mechanism, Fig. 5 is a graph for explaining its operation, and Fig. 6 is the 1-luk displacement ratio of the power cutoff clutch and the direct coupling clutch. It is a graph which shows the relationship between and a servo load ratio. In the diagram 11... Free unit coupling 13...
・Power cutoff clutch 15...Direct clutch 17
．． 17'... Aile pump 3.7.19... Clutch servo mechanism 75.197... Spring Fig. 4 28 Fig. 5 A Toharu torque

Claims (1)

[Scope of Claims] 1) an input shaft that transmits engine drive; an output shaft that is disposed concentrically with the input shaft; and an input shaft that is disposed concentrically between the input shaft and the output shaft. A pump connected to the output shaft, a fluid coupling having a turbine directly connected to the output shaft, a case, and a starting device connected to the direct connection device that can connect and control the input shaft and the output shaft, and a starting device directly connected to the output shaft to stop the engine. In a vehicle transmission device comprising a transmission device that maintains a directly coupled state at times, the starting device includes a spring mechanism that biases the starting device and the direct coupled device, and a spring mechanism that transmits a biasing force from the spring mechanism to the directly coupled device to maintain the directly coupled state. The servo mechanism includes a servo mechanism having an interlocking means for maintaining the servo mechanism and a nervoka generating means for opposing the force urged by the spring mechanism, and the servo mechanism controls the direct coupling device in a detachable manner so that when the engine is stopped, the direct coupling device A vehicle transmission device characterized in that a parking state is maintained by engaging and closing the vehicle. 2) The direct coupling device is provided with a friction clutch disposed between the input shaft and the turbine, and the urging force by the spring mechanism is transmitted via the turbine. The vehicle transmission position described in item 1.