JPS6011734A - Transmission device - Google Patents

Abstract

PURPOSE:To simplify the construction of a transmission device and make it compact, by housing a fluid coupling, a motive power cutoff clutch and the diaphragm spring of a servomechanism side by side in the axial direction of the device in its case. CONSTITUTION:A fluid coupling 11 is provided in the peripheral portion of the interior of the case 1A of a transmission device. A motive power cutoff clutch 13 is provided in the case 1A, radially inside the fluid coupling 11. The diaphragm spring 197 of a servomechanism 19 is provided in the case 1A, beside the motive power cutoff clutch 13. This results in decreasing the axial dimension of the transmission device, simplifying its construction and making the device compact.

Description

[Detailed description of the invention]

The present invention relates to a transmission device in which a fluid coupling and a power cutoff clutch are arranged side by side in the axial direction in a transmission case. The lever (a number of elements that apply a spring load to the clutch for clutch engagement (=J release spring) are arranged in series in the axial direction in the same transmission case, or Since each of them is mounted in a separate transmission case and arranged in series in the axial direction, it becomes large and has a multiple structure, which has the disadvantage of poor mountability when used as a transmission for a small automobile, for example. An object of the present invention is to store a fluid coupling, a power cutoff clutch, and several die/I flam springs of the power cutoff clutch in parallel in the axial direction in one transmission HiFt cage. An object of the present invention is to provide a transmission device which allows for shortening of the axial dimension and simplification of the structure. a coupling, and a power cutoff clutch connected in series with the fluid coupling and installed on the 4' radially inner side of the fluid coupling in the transmission case; a die/no flamm spring J3 installed on the side of the power cutoff clutch for applying a spring load for engagement of the power cutoff clutch; and a die 7 flam installed outside the transmission case. It is composed of a one-node-bom structure for operating a spring.Next, the present invention will be explained with reference to the drawings and an embodiment thereof.FIG. 1 shows a three-axle vehicle according to a first embodiment. Transmission device 1 according to the present invention used as a starting device
, a gear transmission 6 for four forward speeds, one reverse speed, a differential mechanism (not shown), and a transmission case 10 housing these. The transmission case 10 has a shell-like shape in which the engine fastening surface 10A is open and the gear transmission 6 is located, and a side wall 1013 is formed on the side wall 1i'- (hereinafter referred to as the left side), in which the transmission device 1 is housed. The starting device N case IOC and one end surface are fastened to the side wall 10 [3 of the starting device case 10C and the gear transmission is housed.
and a gear transmission 9-spring force bar 10" fastened to the left end surface of the gear transmission 9-s 101". , a power transmission case 1 with a power transmission device installed inside.
Δ, a free coupling (hereinafter referred to as F coupling) 11 provided on the outer periphery of the transmission device 6 gear 1Δ, and a coupling 1 in the transmission device i hill f case.
A power cutoff clutch (
g, lower clutch) 13, and a direct coupling clutch 15, which is installed on the outer periphery of the coupling 11. The air pump 17 provided between the input member and the output member is located on the left side of the clutch 13 inside the transmission case 1A.

[The installed guyaflam spring 197, iJ3 J: and the link of the Dai V noram spring installed between the transmission case 1Δ and the side wall 10 [3 of the starting device case 10G outside] The coupling 11 is connected to the engine crank 11 and the clutch 13 has a diameter of 4M 190.
A drive play 1 is connected to the input shaft 101 of the overlapping transmission device.
~ Via 102! ! Freon 1 to cover 1 tied together
11. The transmission case 1Δ consists of an annular plate-shaped rear cover 110 welded on the outer periphery of the left side of the cover 111, and the outer side of the inner peripheral wall surface of the rear cover. An annular pump shell 112 having the same name as the circumference, a pump blade 113 provided around the inner wall of the pump housing 112, a turbine blade 114 disposed opposite to the pump blade, etc., holding the turbine blade 114. A turbine shell 115 is provided. In the center of the front cover 111, the engine housing part is installed at the center of the end face of the input shaft 101. The tip is the drive shaft 1 () 6 of the oil pump 17, and the middle is a holding shaft 107 that supports and covers the clutch play 1 and the case 134 of the clutch 13 so as to be slidable in the rotational direction.
A central shaft 108 is provided through the center shaft 108. Also Freon 1
- A cylindrical portion 111C in which an annular direct-coupled clutch face 111A and 111J extending perpendicularly to the axis and an inner circumferential spline 111B are formed is connected to the outer peripheral portion of the inner wall of the cover 111. The turbine shell 115 is connected to the output horn shaft 103 of the transmission via a clutch 13 disposed on the inside in the radial direction l) within substantially the same axial section as the turbine shell 115. . 2. The hub-shaped part 1 is provided on the inner periphery of the turbine shell 11!1 with a flange part 131 extending in the diametrical direction on the left side.
The supporting wall 132 is slidably fitted to the 16, and is radially squeezed at the right end.The supporting wall 132 is welded to the disc plates 1 to 158 of the direct coupling clutch 15, which will be described later, and has an inner circumferential line 1 on the inner periphery. :(Tubular clutch play 1 with 3 formed
a hub portion 135 spline-fitted to the output @103 of the transmission device, and the clutch plays 1 to 134;
A clutch disk wheel 139 includes a ramp-drum portion 137 in which an outer circumferential spline 136 is formed at a position corresponding to the inner spline 133 of the case 134 and λ/j, and a disk portion 138 that connects the hub portion 135 and the drum portion 137; The outer periphery is the clutch plate (- a plurality of clutch plates 141 spline-fitted to the case 134, and the inner periphery is the clutch disc wheel 13).
Clutch disks 143 are spline-fitted to the drum portion of No. 9 and alternately overlapped with the clutch plates 141.
It is done from. The direct coupling clutch 15 has the freon 1 to the cover 11 on the outer periphery.
A plurality of clutch plates 1 151 are spline-fitted to the inner peripheral spline 111B of the cylindrical portion of 1, an annular direct coupling clutch pressing plate 152 fixed to the outer peripheral part of the turbine shell 115, and a circular shape of the pressing plate 152. A large number of clutch disc holding arms 1 protruding circumferentially in the axial direction! i3, and a plurality of clap disks 154 whose inner peripheries are spline-fitted to the holding arm 153 and stacked on the clutch plates 151 and q, the central hub portion 155 is connected to the center li.
It is rotatably supported on the disk plate holding shaft 107 of t 108 via a metal bearing, and the outer periphery 156 is connected to the holding arm 153 via a damper 151 with a line 94291.
The thrust bearing 1
60 toward the gear transmission. In this embodiment, the oil pump 17 is an internal two-wheel pump, and is installed between the disc plate 1 and the disc portion 138 of the clutch disc wheel 139. This oil pump 17 has an L13 on its outer circumference and is fixed to the disk plates 1 to 158, and an A oil seal 1 on its inner circumference is attached to a small diameter portion 103B at the tip of the output J shaft 103 of the transmission device.
The gauging 170 is loosely fitted through the casing 175 and is in contact with the disk portion 138 of the clutch disk ear via the thrust bearing 116, and the gauging 170 is installed in the casing 170 on the ground side of the casing 170. An internal gear 112 fitted into a rotating white stone, an external gear 171 fitted with a spline 101 at the tip of the central shaft 108, and an oil passage 103Δ formed in the center of the output till 103 connected to the casing 170. The suction D 174 formed on the disk plate 1-158 and the f disk brake
1 to 158 and a discharge IJ 173 communicating with the front cover 111. The servo mechanism 19 of the clutch 13 consists of the above-mentioned 7 flam spring 197 provided inside the transmission case and the link mechanism 190 provided outside the transmission case. The link I structure 190 includes a connecting rod 191 connected to a servo mechanism (not shown) operated by a clutch pedal located in the driver's seat or an automatic supply IJI such as intake pipe negative pressure or oil pressure, and a connecting rod 191 connected to the rear end. is a hole 1011 connected to the connecting rod and formed in the peripheral wall of the starting device case 10C.
A gangway lever 192 is inserted into the left side of the transmission case 1A and rotated around a fulcrum 193 protruding from the side wall 1, and the tip of the clutch lever 192.
A bearing case 194 having a flange 194A engaged with 1!12Δ, a bearing 195 fitted in the bearing case 194, and a stone ring part (like the rear cover 110) fitted in the ring 195. A slide-r leg sleeve 196 is inserted into the transmission case 1A from the gap between the inner circumference and the output shaft 103, and the inner circumference is locked to the right end of the slide-a-inge sleeve 19G, and the transmission case is inserted into the transmission case 1A. The diaphragm spring 197 disposed on the left side of the clap 13 in 1A is engaged with the outer peripheral edge of the diaphragm spring 197, and the ramp 13 is pressed through the thrust ring 198. Clutch 13
The release and sliding (half-sliding) can be done manually or automatically. In addition, the lever mechanism 1 of this clutch 13
Numeral 9 of the direct coupling clutch 15 is bent, and the spring ?i?I weight of the die A2 frame blink 197 is transmitted through the clutch play 1 to the flange portion 13 of the case 134 and the turbine shell 115. The direct coupling clutch suppressing plate 152 is pressed and the direct coupling clamp 15 is engaged. 1 to 1 to 61, a dog clutch 62 for switching between 1st and 2nd speeds, a dog clutch 63 for switching between 3rd and 4th speeds, and a reverse gear (not shown) arranged in parallel with ~. This transmission device operates as follows: Revo mechanism 1
When 9 is not operated and the diaphragm spring 197 is applying a spring load to the clutch 13 and the direct coupling clutch 15, the clutch 13 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 starting fluid transmission device Jp and the gear transmission 6, the vehicle is driven by the engine J1! Parking condition is obtained by friction torque. Ribo mechanism 1 of clutch 13 and direct coupling clutch 1j)
9 indicates that when the connecting rod 191 is operated manually or automatically to the left in the figure, the clutch lever 192 is moved to the fulcrum 19.
3 to the left to displace the sliding sleeve 196 through the bearing 195 in the L engine direction. This allows the sliding sleeve 19 G I
J, Die~7 The center of the phragm spring 197 bulges out towards the engine l゛, Diaphragm spring 197
A press ring 199 connected to the outer periphery of the press ring 199 is displaced leftward in the drawing. This action releases the multi-disc clutch 13. In addition, the pressing force applied to the clutch by this diaphragm spring 197 is released by releasing the pressing force applied to the clutch plate case 134, turbine shell 115, and direct clutch pressing plate brake h152. Since it is released, it is directly connected and the latch 15 is also released. In this state, the moving horn is cut off by the clutch 13, so that when the vehicle is running, the gear shift operation rA6 becomes possible, and when the vehicle is stopped, the engine can be started. . 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 restoring force of the diaphragm spring 197, and the suppression ring 199 is pressed against the engine and the multi-disc clutch 13
are engaged, and the input shaft 101 and output shaft 103 of the transmission are connected via the coupling 11. At this time, the direct coupling clutch 15 operates as follows. Clara''r-13
When the turbine shell 115 is connected to the output shaft 103 due to engagement, power is transmitted to the coupling 11, and if the relative rotation between the pump and the turbine is large, the turbine shell A thrust force is generated to the left 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 diaphragm spring 197. Then, as the relative rotation between the pump and the turbine becomes smaller, the thrust force and the discharge pressure of the oil pump become smaller, and the die 4<y engages with the flamm spring 197 as J:. Table 1 As shown in Table 1 and FIG.
(Herc) T13 and J: and 1 and 15 are clutch 13
When the same lever load Φ is applied to the direct-coupled clutch 15, the change will be as shown in a, but if the 1-lux capacity of the direct-coupled clutch is reduced as in this embodiment, the result will be as shown in (). Decrease. FIG. 2 shows a second embodiment. In this embodiment, a continuously variable transmission for a vehicle is constructed by combining the transmission device of the present invention and a V-belt type continuously variable 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 70-inch F cover, and a direct coupling clutch 15 is provided between the rear cover 110 and the turbine shell 115. Also in this embodiment, the air pump 1 is supplied between the rear cover 110 and the disc plates 1 to 158.
7, the turbine thrust by the turbine, and the return spring 159 inserted in the center between the rear cover 110 and the disc plate 1-158, the torque load of the direct coupling clutch 15 is reduced. 2 is a V-belt continuously variable transmission, 3 is a clutch servo mechanism,
4 is a forward/reverse switching mechanism, and 5 is a differential mechanism. ■ Pell 1 to afterglow gear shift 1 and 2 are hollow input shafts 21 arranged in series on the same axis as the engine output shaft, and V-belt continuously variable transmissions arranged in parallel with the input shafts. Hollow output shaft 22, stepped input pulley 2 on input @21
3. Output pulley 24 installed on hollow output shaft 22
, the V-bells 1 to 25 that transmit power between the human pulleys 23 dl-, J, and the output pulley 24, and the Nervo machine that changes the effective diameter of the human pulley 23 (Tom 26, which changes the effective diameter of the output pulley 24). The input shaft 21 has a hollow shaft center and a bevel 7 ring 211a.
3 and 212 J: Belt type continuously variable transmission case 10
It is rotatably supported by the
13. On the other side, an outer peripheral spline 214 and a threaded end 215 are 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 attached to the bearings 221 and 222 to the continuously variable transmission case 10. Supported. The human pulley 23 has one end (the right end in the figure) in contact with the step 213 of the input shaft via a thrust bearing 216.
On the outer periphery of the other end, there is a sleeve-shaped part 233 provided with an outer circumferential spline 231 and a keyway 232, and a sleeve l-234, which is formed integrally with the sleeve-shaped part 233 and is used to detect the rotational speed of the input shaft, is provided around the outer periphery. A fixed flange 23Δ consisting of a flange portion 235 etc., which is displaceably displaceable in the axial direction on the sleeve portion 233 of the fixed flange 23Δ, and a key groove 2 corresponding to the key groove '232 of the fixed flange on the inner peripheral wall.
36 and a driven screw 237, which is a first screw, is provided on the outer circumferential wall of the sleeve-shaped hub portion 278; and a flange portion 239 formed integrally with the hub portion 278.
A movable flange 23B1 consisting of
It consists of a ball key 230 that allows displacement in the axial direction with the ffiJl flange 23B and integrally rotates around @. The output pulley 24 has a key Fj 241, a spline 242, a screw 243, and a spline 249 formed on the outer periphery, and has a sleeve-shaped portion 244 formed integrally with the output shaft 22.
and a flange portion 245 integrally formed with the sleeve-shaped portion 244, the fixed flange 24A 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 24A. ) A sleeve-shaped hub part 247 is provided with a keyway 254 covering M241, and a driven screw 24G, which is a first screw, is formed on the outer periphery, and a flange part 248 is integrally formed with the hub part 247. A movable flange 2413 consisting of a movable flange 2413, and a movable flange 2413, which is inserted into the key grooves 241 and 254, and which accommodates displacement in the axial direction of the fixed flange 24A and the movable flange 24B and rotates around the axis integrally. Consists of a ball key 240. ■ Bell 1 to 25 is connected to the input pulley 23iJ3, respectively.
and the fixed flannon 23Δ of the output pulley 24, the fixed flange 24A, and the movable flange 23Bd: (and contact the V-shaped working surface of the movable flange 24B,
Forming working surfaces 251J5 and 252 are provided on both sides. The V-bow mechanism 2G of the input pulley has a drive screw 261 formed on the inner periphery, which is a second screw that engages with the driven screw 237 of the movable flannon 23B of the input pulley, and one end has a thrust bearing 265. A sleeve 262, which is a driver of a movable flange, is brought into contact with a cam race 287 of a cam mechanism described later, and a wet multi-plate is installed between the sleeve 262 and the case 10 to brake the sleeve 262. Electromagnetic downshift 1 to brake 263. sleeve 262
A cylindrical spring guide 264 is disposed on the outer periphery of the spring guide 264, and the engine side end is connected to the movable flange 23B between the spring guide 264 and the sleeve 262, and the other end is connected to the other end of the cylindrical spring guide 264. The first upshift 1 to 1 hexagonal cord connected to the side end
The spring 26G is arranged around the outer periphery of the spring guide, and the four ends of the engine are connected to the spring end of the spring guide 264, and the other end is connected to the spring end of the sleeve 2. 2 upshift/for 1~-
Jiyoung] Ill Spring 267 growls. The output boolean servo mechanism 274, the movable flange 2
Sleeve 2, which is a driver, has a drive screw 271, which is a second screw, screwed into the driven screw 246 of 4B, formed on the inner periphery.
12, a wet-type multi-plate electromagnetic brake 273 for fixing the sleeve 272 and the case 10, etc., and a down with both ends connected between the sleeve 212 and the movable flange 2413. The torsion coil spring 274 for shifting is formed with a spline that fits with the spline 242 of the output shaft, and the one on the movable flange 24B side is in contact with the end surface of the sleeve 272 via a bearing 275, and the other side is in contact with the end surface of the sleeve 272 through a bearing 275. The surface is connected to the inner race of the bearing 221 by a support ring 277 which is locked by a jet 27G and supports the sleeve 272 in the axial direction. The snap ring 218 externally fitted on the input shaft 21 and the spline 21 of the input @ 21 are fixed in the axial direction by the snap ring 218 screwed onto the screw 215 formed at the input shaft 21 and b.
4 and spline-fitted inner periphery szoller in 281 are formed -h cam race 282, etc.
l! ! one cam race 287 , a Daverd roller 288 interposed between these cam races, and a cover ring 289 of the roller 288 .
8 is sandwiched between the working surfaces 292 and 286 of the races 282 and 287, and changes the pressing force that presses the movable flange 23B in the right direction in the figure in response to the rotational displacement of the input shaft 21 and the fixed flange 23A. . Next, we will explain the operation of this belt type continuously variable transmission. (a) Play when driving at constant speed: i: 263, J, and 27
3 will be released together. Torque is transmitted through the input shaft 21-) one race 282 of the cam mechanism → the Daverd roller 288 → the other race 2
87→input switch 23-) V bells 1 to 25->output switch 24-) output shaft 22. ■Bell 1-25
The magnitude of the transmitted torque is proportional to the clamping force applied to the V-bells 1 to 25, and the clamping force contacts the other cam race 287 via the movable pulley 23B and the sleeve 262 screwed with the movable pulley. The input boom moves slightly in the rotational direction due to the principle of the cam mechanism, and
The clamping force Fc acting in the axial direction by 88 changes in proportion to 1 Herc of transmission as shown in Fig. 4.
-25, the clamping force applied to the movable flange 23 [3] is changed in accordance with the transmitted torque, and thereby V-bells 1 to 2
The surface pressure between the working surface of 5 and the working surface of the movable flange 23[3 and the fixed flange 23A changes to change the clamp loca for the time being. F2 is the necessary clamping force to prevent V-bell 1- from slipping at the lowest reduction ratio, B
：Force, ゛ indicates the clamping force using a conventional hydraulic pressure pump, and Fs indicates the clamping force using a meso ring. In the V-bell 1 continuously variable transmission using the cam IWJ 4R2g from Grano shown in Fig. 4, the clamping horn and the transmission 1-lux are directly proportional even if the transmission 1-luke is less than 5 kgm, and there is no need for belt sagging. It can be seen that the generation of clamping force can be reduced. (['') Upshift is made with U engaging play 1273. The sleeves 262J and 272 rotate relative to the sleeve portions 27B and 241 of the movable flange, and the movable flange 23
B is displaced in a direction (to the right in the figure) that extends the effective diameter of the input pulley 23, and the movable flange 24B is
4 in the direction of decreasing the right diameter (toward the right in the figure),
A reduction in the gear ratio is performed. Brakes 2G3 and 273 are released when the gear ratio reaches the control set value. This 19f 1~ time output boolean 1-bo mechanism 1-
The spring 274 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, the movable flange 23B is displaced toward the left in the figure in the direction of decreasing the effective diameter of the coupler pulley 23, and the torsion spring 274
rotates the sleeve 212 and returns, moving the movable flange 2
4] Displace 3 in the direction of increasing the effective diameter of the output boob (to the left in the figure). Movable flange 23B of this person Kapuli 23
The displacement is made against the pressing force of the movable flange 2313 by the cam mechanism. When the gear ratio reaches the control setting hook, the brake 263 is released and turned over. During this downshift 1~, the first and second shift springs 266 and 267 of the human power 1-reservoir mechanism 26 are twisted to accumulate energy. This ■ Pel 1 - Martial stage gear 1 is a3 and brake 2
63. If the electromagnetic brake of 273 has failed and the brake cannot be engaged, the vehicle can run with the same gear ratio as before the failure.Therefore, the gear ratio can be changed using the hydraulic lever.Pel 1~ The clutch servo machine WJ3 has excellent safety because it prevents the gear ratio from being changed inadvertently, such as when oil leaks in the case of a martial arts gear transmission. 33, consisting of a pusher J inserted into the hollow of the input horn shaft 21, a clutch pedal 3G, and a clutch pedal link (37). The other of the bushing lever 331, the sliding knob 333 provided on the transmission case, and the bushing rod 35 is brought into contact with the spring end 352, and the release bearing 33!i
The bearing race 337 is rotatably supported on the inner wall of the sliding knob 333 via a bearing race 337. 4)--When the lift mechanism 3 is not operated by J3, the guille flamm spring 312 (more than the latch 1)
When engaged by pressing 3, the direct coupling clutch 1 is connected via the clutch plate case 134 and the turbine seal 115. I engaged! ing. When the bushing lever 331 is rotated around the fulcrum in the direction shown in the illustration by manual operation using the foot or LL q=, the sliding kit t/tube is slid across the J-engine. lever 3j
] towards the engine, displace the center of the guilleaf flamm spring 312 in the direction of the engine lJ, move the IC pressure plays 1 to 1 towards the engine, and press the clamp 13
J: Release the direct coupling clutch 15. The clutch pedal link mechanism 37 includes a link lever 361 that is housed together with the push lever 331 and is disposed outside the transmission case 10, and a cable 362 that connects the free end of the link lever 361 to the clutch pedal 3G. . In this embodiment, when the driver depresses the clutch pedal 36, the clutch lever mechanism 3
62, put silver 331 via link lever 361
is driven to rotate around the fulcrum, and the clutch release J3 and sliding (half-clutch) are performed manually as described above. Note that it is also possible to control the clutch automatically as in the first embodiment. The forward/reverse switching mechanism 4 includes a dog clutch 41, a first simple planetary gear 1/43, and second simple planetary gears 1-45. Dog Clara'f41 (linked to the control lever)
A-ri 411, a brake sleeve 413 that is engaged with the A-ri and slides in the axial direction, and a first gear 415 (
spline piece), second gear 417 (spline piece), sleeve 413, etc. (sink 1 = 1 gear 419 (synchronizer
The 3° first gear set 1 to 43 consisting of a ring) is connected to the sub-input 24 installed at the output @22 of the Pel 1 to Valorous gear transmission.
A sun gear 431 is formed on a lean gear shaft 430 which is connected to a spline 1 and connected to a second gear 417 of a dog clutch 41, and a second gear set 1 is connected to a second gear 417 of a dog clutch 41.
~ Ring gear 433 connected to sun gear 451 of 45
, knee 7 rear 4 connected to the first gear 415 of the dog clutch 41 and connected to the second ring gear 453
35, consists of a planetary gear 437, and the second planetary gearlets 1 to 4j) have a spline attached to a spline 459 provided on the output sleeve 450 connected to the ring gear 451, the ring gear 453, and the gear box of the differential 111M. 1■ combined -1-+-lip 455
J3J: Consists of 457 planetary gears. This forward/reverse switching mechanism 41 is configured such that when the sleeve 413 of the dog clutch 41 is manually or automatically meshed with the second gear 417 and the ring gear 433 and sun gear 451 are fixed to the case 10, the forward movement of the set gear ratio is performed. At 43, the sleeve 413 is meshed with the first gear 415 and locked.
! When the ring gear 453 and the ring gear 453 are fixed to the case 10, there is a backward movement at the set gear ratio. The differential mechanism 5 includes an output sleeve 450, which is the output shaft of the forward/reverse switching mechanism 4, and an input shaft, a gear box 52 integrally connected to the input shaft 450, a small differential gear 53, 54, and the differential A large differential gear 55.56 meshed with a small moving gear, one output @ 57J: iJ: and an output shaft box 1 of the Pel 1 to Valorous gear transmission, which was spline fitted to the differential man gear. f 2 ring gear 431.451,
FIG. 6 shows a third embodiment. This embodiment has a configuration in which the direct coupling clutch 15 is removed from the first embodiment d3 and the second embodiment. As described above, the transmission 1 of the present invention (J, a transmission case and G provided on the outer periphery inside the transmission case), and the fluid coupling connected in series with the fluid coupling and inside the transmission case. a power cutter clutch 1 provided on the radially inner side of the fluid coupling; and a power cutter clutch 1 provided on the side of the power cutoff clutch in the transmission worm for engagement of the power cutoff clutch. It consists of a die A7 flamm spring that applies a spring load, and a lever mechanism that is installed outside the transmission case and operates the diaphragm ring. The disconnection clutch's ribo 1m structure GUY .Spring type pusher structure (tie) 7Fram springs are used, so the number of parts is smaller than when using coil springs, and the phase characteristics are excellent, and the rotation of the clutch acts on the spring. Prevents the reduction in engagement force caused by force.
Therefore, the internal dimensions of the shaft can be made smaller. Also, for the same torque capacity, the clutch operating force is smaller than that of a coil spring. Furthermore, the pressing mechanism can be controlled with a small operating force by changing the lever ratio of the lever for operating the die V-flag spring, and the operating mechanism can be made simple.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of an FF type automatic medium transmission (a cross-sectional view,
Fig. 2 is a sectional view of an Fl: type automatic intermediate transmission which combines the transmission device according to the second embodiment of Ming 1 and a V-belt type continuously variable transmission, and Fig. 3 is a sectional view of a cam machine 'IM'. Fig. 4 is a graph for explaining its operation, and Fig. 5 is a graph showing the relationship between the clutch for power m and ii: and the 1-to-luk capacity ratio of the gangway and the 1-to-bo load ratio. , vtX6 diagram shows the transmission according to the fourth embodiment. In the picture 11...Free'', It Katsuno Blade 13
...Power connection clutch 15...Direct connection graph 1
-17...Auxiliary oil pump 3.19...Clutch revo IHM 197.312...Diaphragm spring Fig. 3 28 Fig. 4 shows 9 Iyandatsu Torreg Fig. 5 □□□□□-1 3.0 l-fFrt response Fig. 6 103 101

Claims (1)

[Scope of Claims] 1) A transmission device case, a fluid coupling provided on the outer periphery inside the 1FII device coupe, and a fluid coupling connected in series with the fluid coupling, and the transmission! ζ A power cutoff clutch installed on the radially inner side of the fluid coupling in the field case, and a power cutoff clutch provided on the side of the moving horn cutoff clutch in the transmission case. A transmission device comprising a dial ram spring for applying a spring load for connection, and a lever mechanism provided outside the transmission case for operating the die to seven flamm springs. 2> The transmission device according to claim 1, wherein the power cutoff clutch is a multi-plate clutch C.