JPS6011735A - Transmission device - Google Patents

Abstract

PURPOSE:To decrease the cost and weight of a transmission device and make it compact, by providing a centrifugal high hear clutch beside a fluid coupling in the case of the transmission device which is shaped as a thick disk. CONSTITUTION:A centrifugal high gear clutch 16 is provided beside a fluid coupling 11 in the case 1A of a transmission device, which is shaped as a thick disk. A motive power cutoff clutch 13 is provided in the case 1A, radially inside the high gear clutch 16. As a result, a servomechanism for controlling the high gear clutch 16 is not needed. For this reason, the cost and weight of the transmission device are decreased and it is made compact.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission device that is a combination of a direct-coupled tarlage fluid coupling and a gludge for use in a glitch.

Conventionally, this type of transmission device has either a fluid coupling with a direct coupling clutch and a clutch for power (power supply) arranged face-to-face in the axial direction in an 11-toe case, or installed in separate cases and arranged in series in the axial direction. This has the disadvantage that the axial dimension becomes long, making it difficult to mount when used as a transmission device for a small automobile.Furthermore, engagement and disengagement may be difficult depending on the flow direction of the working fluid in the fluid coupling. When a vehicle transmission device is purchased using a piston-type direct coupling clutch, there are the following drawbacks.

b) A special lever mechanism is required to operate the direct coupling clutch. Since the structure is complicated, it is difficult to miniaturize the structure, and the vertical portion and manufacturing cost also increase.

(Example) If you brake suddenly on a slippery road surface and the tire slips, it is very dangerous because the lock-up clutch release controller cannot be activated in time and the upper engine is likely to stop.

The purpose of the present invention is to directly connect Clara 1-(=j fluid coupling and dynamic)
[In combination with the required clutch, it is possible to shorten the axial direction X1 method, making it smaller and lighter, making it easier to install in small cars! The present invention provides an l1lI device.

Another object of the present invention is to use a centrifugal automatic clutch as a direct-coupling clutch, and to install the centrifugal clutch between a turbine and an input member of a fluid coupling, thereby eliminating the need for a one-node mechanism of a direct-coupling clutch. The structure is simple and the direct clutch can be engaged with a torque capacity that corresponds to the turbine rotation speed at low - 1st stroke, so it can be used to prevent tire locking in sudden lugs.
; It is possible to prevent entrancing stops.

The transmission device of the present invention includes a transmission device case that has a flat 4T circular shape, an Iζ fluid coupling provided on the outer periphery of the case, and a fluid coupling provided on the side of the fluid coupling in the transmission device case. It consists of a centrifugal direct-coupling clutch of the joint and a vJ force interrupter gradi located radially inwardly within the transmission case.

Next, the present invention will be explained based on one embodiment shown in the drawings.

FIG. 1 shows a three-shaft dual-purpose transmission according to a first embodiment of the present invention, including a transmission device 1 according to the present invention used as a starting device, and a gear transmission 6 for four forward speeds and one reverse speed. , a 5"-r7 arrangement (not shown), a full mechanism, and a 5"-r7 arrangement (not shown), and a 1-piece housing 10 that accommodates these.

The transmission case 10 has a side wall 1013 formed on the side where the engine fastening surface 1()△ is open and the gear transmission 6 is located. Device 1
The end face of the shell-shaped starting device case 10C houses the starting device case IOc, and the cylindrical gear transmission 7HID, K ( 'AI! Transmission'/' 7
．． 101) (7) IF lfi J) Gear transmission case cover 1 fastened to the end face and differential case 10 integrally formed on the side of the starting device case (shown in FIG. 2). ), and cover the left side 1-1 of the differential case and insert the gear transmission case I.
Differential cover 10 formed integrally with OD
G (shown in Figure 2).

The transmission device 1 is installed in the starting device case 100, and the transmission device case 1Δ has a transmission device installed therein.
and a solid coupling (hereinafter referred to as a blade coupling) 1 provided on the outer periphery of the transmission case 1Δ.
1, a power cutoff clutch (hereinafter referred to as the clutch) 13 provided on the radially inner side of the coupling 11 in the transmission case, and the outer periphery of the coupling 11 (in this embodiment, the engine is A centrifugal direct coupling clutch 1 installed on the right side in the figure (hereinafter referred to as the right side) and an A installed between the input member and the output member of the coupling 11.
A die
7 Fram Spring 191, J3 and the i! Measurement of the length of the lJ device 1A and the starting device case 10C outside! 1t! I
The lever 1It of the clutch 13 that rightly connects the link mechanism 190 of the Daire flam spring provided between the OB and
f619.

The coupling 11 connects the drive shaft 101 to the input shaft 101 of the transmission, which is coupled to the crank shaft 1 of the engine.
A sword connected via 102, 1-piece cover 111
, and the transmission case 1△ consisting of an annular plate-shaped rear cover 110 welded on the outer periphery of the front 1 to the cover 111, and fixed circumferentially to the outer side of the inner peripheral wall surface of the rear cover. A pump blade 113 disposed around the inner wall of the pump blade 112, a turbine blade 114 disposed opposite to the pump blade, and a turbine blade 114 that holds the turbine blade 114. Terahinge! 115. The engine side large diameter part is provided in the center of the end face of the human power 11i11101 in the core 41 of the front 1 to cover 111. ~
The boss is 105, and the tip of the left side is the A-il i1 ring 17.
The drive shaft 10G is a drive shaft 10G, and the intermediate portion is a disk drive 1-holding shaft 107 that rotatably and slidably supports the clutch plate worm 134 of the clutch 13.
The central axis 108 is set to L1 stage. Further, a cylindrical portion 111C on which a cylindrical direct clutch friction surface 111A is formed is connected to the outer periphery of the inner wall of the Noron 1-cover 111. The turbine shell 115 is connected to the transmission mJ+V-neck output @103 via a clutch 13 disposed radially inwardly within substantially the same axial section as the turbine shell 115.

A flange portion 131 extending in the I'' direction at the left end of the clap 13 is slidably fitted into a hub-shaped portion 116 provided on the inner periphery of the turbine shell 115, and the right end The disc plate h1 of the direct coupling clutch 16 has a supporting wall 132 stepped in the radial direction 21' at the other end as described later. i8, a cylindrical clutch plate case 134 with an inner spline 133 formed on its inner periphery, a hub portion 135 spline-fitted to the output shaft 103 of the transmission, and an inner wall of the gangway brake 1-case 134. A clutch disc wheel 139 includes a clap drum part 137 in which an outer circumferential spline 13G is formed at a position corresponding to the spline 133, an f-isk part 138 that connects the hub part 135 and the drum part 137, and - A plurality of gangway plays 1-141 are spline-fitted to the case 134, and the inner periphery is spline-fitted to the drum portion of the clutch plate 11\eel 139. This is done from the IC clap desk 143 etc.

The centrifugal direct-coupling Clara "flG has a friction surface 111A of the cylindrical direct-coupling clutch 1g in the mount cover 111, and a hub portion 1!15 at the center of the disc plate 1 of the central shaft 108.
~ Disc plays 1 to 158 rotatably supported on the holding shaft 107 via metal bearings, and plays 1 to 1
The outer circumferential surface 162 of the centrifugal weight 161 is an Iv friction surface, and the cylindrical friction surface 111A of the F [J seat cover 111
A cylindrical friction surface 160 is formed between the two.

Since this centrifugal clutch 16 is connected to the turbine shell 115 through the disk-h 158 and clutch-1-case 134 fc, it rotates integrally with the turbine, and the turbine rotational speed is A transmission of 1-lux is made in accordance with the .

In this embodiment, the air pump 11 is an internal notification pump, and is installed in the clutch disk wheel 139 between the disk plates 1 to 1 and the disk portion 138 of the clutch disk wheel.

This oil pump 17 is fixed to the disk plate 158 at its outer circumference, and its inner circumference is connected to the small diameter end portion 103B of the transmission 'aH output +11+103 via an oil seal 175 (31f) to a thrust bearing 176.
Via eff latch disc wheel de 129 part 13
8 and the casing 17
0 engine is installed (internal tooth width 172 rotatably fitted in the gear room), external gear 171 spline-fitted to the tip of the center @ 108, and the center of the output shaft 103. It consists of a suction port 174 provided in the casing 170 connected to the formed oil passage 103Δ, and a discharge port 173 formed in the ice cream 1-1 circle and communicating between the disc plate 158 and the freon 1 to the cover 111. .

The servo mechanism 19 of the clutch 13 consists of the die 17, the frame ring 197, and the link mechanism 190 provided outside the transmission gear. The link (Ikuyoko 1909) is installed in the driver's seat and is connected to the IC clutch pedal or the intake pipe (11f or self-help supply/discharge of hydraulic pressure, etc.). ) connecting rod 191 connected to
The rear end is connected to the connecting rod, and the starting device case IOC
A fulcrum 1 is inserted into the left side of the Buddha movement Il-su 1Δ through a hole 101-1 formed in the peripheral wall of the fulcrum 1 and protrudes from the side wall 10B.
The ramp lever 192 is rotated around the bearing case 194, the bevel 7 link 9-spring 194, etc., which connects the flange 194A engaged with the tip 192Δ of the clutch lever 192, and the bevel 7 ring fitted inside the bearing case 194. 195
The inner circumferential edge of the bearing 195 is connected to the sliding sleeve 196 inserted into the transmission case 1△ through the gap between the inner periphery of the rear cover 110 and the output shaft 1()3, and the inner peripheral edge. The right side of the sliding sleeve 19G is locked in the gap, and the transmission MP'? The diaphragm spring 197 arranged on the arm side of the clutch 13 in the Kusuke is engaged with the outer peripheral edge of the spring 197 and presses the clutch 13 via the thrust bearing 198. Press I to
EN''; r 109, and the clutch 13 is released and operated manually or automatically.

l'141rIj The transmission 6 has a known configuration, and the output of the transmission device ? Let +I+ be Impra 1 ~ Shirefu 1 ~,
Ara 1 to Butu I arranged in parallel to Inbutsu 1 to Shafu 1
- A shift V-shift 61, 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 device is ft1FJI as follows. .

In the 1-no-vo mechanism 19 of the gangway ~13, the clutch lever 192, which is operated manually or automatically C' connecting rod 1≦)1 in the outward direction as shown in the figure, rotates counterclockwise from the fulcrum 193j and rotates the bearing 195. Sliding sleeve 19G through
is displaced one carrot direction. In addition to this, the Usriding Sleeve 196 is Dai 17 Novumsoring 19
A press ring 199 is connected to the outer periphery of the die \7 flamm spring 197, with the center side of the ring bulging out along the side of the engine 1.
t change to the left as shown f1/? 5. This action releases the multi-disc clutch 13. In this state, the power is cut off by the power supply 13, and the engine can be started during the gear shift operation in the engine 6.

When the connecting rod 191 is operated manually or automatically in the right direction in the drawing, the sliding sleeve 19G is displaced in the direction C (in the drawing) by the return force of the die 1/flamm mesh ring 197, and the pressing ring 199 +; The multi-disc clutch 13 is engaged by being pressed by the four discs, and the input shaft 10 of the transmission [Vi]
1 and the output @103 are connected to each other via the coupling 11.

FIG. 2 shows a second embodiment of the invention.

The transmission case 10 is a shell-shaped start support case 1 in which the engine fastening surface 10A is open, a side 'F1013 is formed on the gear shift 1ift e side, and the transmission device 1 is housed.
0C, and one end face is the side wall 10 of the starting device case 10C.
A cylindrical tooth width transmission case 10D that is fastened to B and houses the WI medium transmission, and a gear transmission case cover IOI3 that is fastened to the left side end face of the float transmission case IOD.
A differential woofer 101 is formed integrally with the side force of the starting device case, and the left side of the differential 1 full case covers the opening and connects the gear transmission case IO.
Differential 1 full cover 10 integrally formed with D
0, the starting device case 10C and the gear transmission case 1
00, and an oil pump cover 1or fastened to the right side of the intermediate side wall i o +-+.

The flanges 131 of the clutch plate 1 to the case 134 are slidably fitted to the hub-shaped part 116 stepped on the inner circumference of the turbine shell 115, and the support wall 132 of the tardage plate case 134 is Disc plates 1 to 145 are rotatably supported at the right end of the output shaft 103 and slidably in the axial direction, and are disposed between the freon 1 to cover 111 and the clutch disc boiler 139.
The 1° mail pump 17' is welded to the outer periphery of the
In this embodiment, an internal gear pump is used, and is welded to the center of the rear cover 110, and the oil pump cover 1 is welded to the center of the rear cover 110.
A hollow oil pump lower pipe il'1ll171 is inserted into the oil pump cover 1tII from between the inner circumference and the output shaft 103 of the oil pump cover 107; R' in plume IOJ! 1 movement freely rotatable 1 inset) L internal teeth Jl 1
73, an outer 1 whose inner circumference is fitted with a spline 1 at the left end of the pump dry shaft 111 and meshed with the internal gear;
- The gear 175 absorbs oil from the suction D 179 provided on the intermediate side wall 10H, and the haul pump cover 1 (
) The hydraulic oil is discharged to the discharge port 180 formed in ().

Reference numeral 65 denotes a differential gear whose output shafts 651 and 652 are disposed parallel to the input shaft J5 and the rear wheels of the gear transmission.

The hydraulic servomechanism 1 is arranged in the transmission worm 1Δ on the radially inner side of the coupling ring 11.

This hydraulic pressure (the nervo mechanism 7 is installed between the clutch drum part 131 and the hub part 135 on the left side of the disc part 138 of the clutch disc wheel 139) is inserted into the annular cylinder 71J3 and slides into the cylinder 71. A hydraulic servo 70 which generates a servo force opposing the ponne load applied to the clutch 13 is composed of an annular screw I~n 72 which is freely fitted, and the inner periphery is formed into a comb-tooth shape, and the disk part The inner circumferential end is engaged with a comb tooth-like protrusion 147 protruding from the piston 7 to the left side.
a suppressing plate 73 that is engaged with the left side of the clutch 13 and whose outer periphery is in contact with the right side of the clutch 13; A return spring 75 is interposed between the blink rear knob 4, the spring retape 74, and the pressing plates 73 and 9, and applies a spring load for engagement of the clutch 13 and the direct coupling clutch 15.
What does it consist of?

The functions of the hydraulic revolving mechanism 1, a5 and the clutch 13 will be explained.

The spring load of the return spring 75 is applied to the clutch 13 via the pressure plate 73 when the pressure of the hydraulic nervo 70 is exhausted.
, and the clutch 13 is engaged. In the hydraulic servo 10, when pressure oil is supplied from the oil passage formed on the output shaft, the piston 72 is displaced into four left pistons, and the suppression plate 13 is displaced to the left, so that the gangway 13 is released. . In this state, the power by the clutch 13 is disconnected, so that the gear transmission 6 can perform a gear shift operation, and the J-engine can be started when the engine is stopped.

Further, the direct coupling clutch 16 operates in the same manner as in the first embodiment.

FIG. 3 shows a third embodiment. Embodiment C constitutes a continuously variable transmission for a vehicle by combining the transmission device of the present invention and the V-Pel 1 to Valorous Gear transmission. The same reference numerals as in FIG. 1 indicate the same functional parts.

In this exemplary embodiment, the transmission 1 is made up of functional elements of a first embodiment. A pump blade 113 is provided on the outer peripheral inner wall of the Freon 1-cover, and the rear cover 110
A direct coupling clutch 16 is provided between the turbine lever 115 and the turbine lever 115. In this embodiment as well, the rear cover 110
An air pump 17 is provided between the disk plate 158 and the disk plate 158. 2 is a V-bell 1 set continuously variable transmission, 3 is a clutch servo mechanism, 4 is a forward/reverse switching mechanism, and 5 is a differential mechanism.

■Pel 1-stage transmission 2 is a hollow input @21 arranged in series on the same axis as the engine output shaft, and a belt-type continuously variable transmission parallel to the input shaft. Hollow output @ 22, turnip with numbered number on input shaft 21 - IJ
23. Output pulley 2 installed on the hollow output shaft 2211
4. V-bell transmitted between the human pulley 23J3 and the output 1-reel 24] ~ 25. Changing the effective diameter of the input pulley 23 - 1-bore mechanism 2G, avoiding changing the effective diameter of the output horn pulley 24 4. It consists of a novo Ia mechanism 21 and a cam mechanism 28 provided on the input pulley.

The human power shaft 21 has a hollow shaft center and is rotatably supported by the V-pel 1 to valor stage transmission case 10 by bearings 211 and 212, and the engine is connected to the alligator stage 213.
For use, an outer peripheral spline 214J3J and a tip screw 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 supported by the bearings 221ct3 and 222, and by the transmission case 10. has been done.

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 21G,
On the outer periphery of the other end, there is a sleeve-shaped part 233 provided with an outer peripheral spline 231 and a keyway 232, and the sleeve-shaped part 233 is formed integrally with the outer periphery of the sleeve 1 to 234 for detecting the rotational speed of the human-powered shaft. A fixed flange 23Δ consisting of a fixed flange portion 235 is externally fitted onto the sleeve portion 233 of the fixed flange 23A so as to be freely displaceable in the @IJ direction, and a key groove 23G corresponding to the :1 knee groove 232 of the fixed clutch is formed on the inner peripheral wall. A sleeve-shaped hub portion 278 is formed and provided with a driven screw 237, which is a first screw, on the outer peripheral wall.
and a flange portion 23 integrally formed with the hub portion 278.
Movable flange 23 consisting of 9 parts, B1 and J: key groove 23
2d5 and 236, the ball key 2 is used to integrally rotate the fixed flange 23△ and the movable flange 2313 about their axes by displacing them in the axial direction.
Consists of 30.

The output pulley 24 has a keyway 241 and a spline 2 on the outer periphery.
42, a screw 243, and a spline 249, and a fixed flange 24△ consisting of a sleeve-shaped part 244 formed integrally with the output shaft 22, a flange part 245 formed integrally with the sleeve-shaped part 244, etc.; A key groove 25 is fitted on the sleeve portion 244 of the fixed flange 24A so as to be freely displaceable in the axial direction, and a key groove 25 corresponding to the key groove 241 is provided on the inner periphery.
4 is provided, and a driven screw 246 which is the first screw is provided on the outer periphery.
The sleeve-shaped hub portion 247 is formed with a
A movable flange 24B1 consisting of a flange portion 248 integrally formed with a It consists of a ball key 240 for integral operation.

■The bells 1 to 25 are in contact with the V-shaped working surfaces formed by the fixed flanges 23Δ and 24A of the input convertible 23a3 and the output pulley 24, the movable flange 23[3, and the square cut flange 24B, respectively! Working surfaces 251 and 252 forming V719 surfaces are provided on both sides.
There is.

The servo machine 142G of the Heka pulley is a second motor which is screwed into the driven screw 237 of the movable flange 23B of the Heka pulley.
A drive screw 261 is formed on the inner periphery, and one end is connected to a sleeve 262, which is a driver of a movable flange, which is brought into contact with a cam race 287 (which will be described later) through a thrust bearing 265. A wet multi-plate electromagnetic downshift 1 to brake gear 263 is provided between the 2G2 and the case 10 to brake the sleeve 1262, and a cylindrical spring guide 264 is arranged around the outer periphery of the sleeve 262.
．． The engine end is connected to the movable flange 23B arranged 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. A compression coil spring 266 is disposed around the outer periphery of the spring guide, and has one end connected to the engine side of the spring guide 264, and the other end of the spring guide 264 connected to the engine side end of the sleeve 262. It consists of a torsion coil spring 267 for 2-7 springs 71-.

The servo mechanism 21 that comes out of the way is connected to the movable flange 2
A sleeve 272, which is a driver, has a drive screw 271, which is a second screw, which is screwed into the driven screw 246 of No. Brake 273 for formula 7p shift 1~,
The sleeve 272 and the movable flange 243 are connected at both ends to the downshift 1. The sleeve 272 and the movable flange 243 are connected to each other, and the spring 274 has a spline that fits with the spline 242 of the output shaft. A certain force surface is connected to the sleeve 2 via the bearing 275.
The support ring 277 is in contact with the end surface of the sleeve 72, and the other surface is locked by a put 276 via the inner race of the bearing 221, supporting the sleeve 272 in the direction of the axis Ij.

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 buttons 1 to 217 screwed into the screws 215 formed at the end of the input shaft. One cam race 282 is formed with an inner peripheral tin line 281 which is connected to the spline 214 of the input shaft 21 and the spline 1, and the other cam race 2
87, a tapered roller 288 interposed between these cam races, and a cover ring 28 of the roller 288.
9, the roller 288 has races 282 and 287
The input shaft 2 is sandwiched between the input shaft 292 and 286.
The pressing force for pressing the movable flange 23[3 in the right direction in the figure is changed depending on the rotational direction of the constant flange 23Δ.

Next, the operation of the bottomless variable speed change to this V-bell 1 will be explained.

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

(The transmission of torque is done by the human power shaft 21) Cam mechanism σ or one race 282 → Taper roller 288 → The other race 287 → Inlet pulley 23 -,) To V bell 1 25 → Output pulley 24 → Output shaft 22 done in order. ■Bell 1-25
The human nature of Luk is proportional to the clamping force applied to the bells 1 to 2j), and the clamping pressure is applied via the movable pulley 2313 and the sleeve 262 screwed with the movable boot. The tapered roller is brought into contact with the other cam race 287, and due to the principle of the cam mechanism, the tapered roller moves slightly in the rotational direction.
The clamping force Fc acting in the axial direction by 288 is transmitted from transmission 1 to
As shown in FIG. 5, the clamping force applied to the movable flange 233 that clamps the V-bell 1 to the 25 is changed in accordance with the transmitted torque.
The blood pressure between the working surface of the movable flange 238 and the working surface of the fixed flange 23A changes, thereby changing the clamping force on the contact surface. In Fig. 5, [1 is the necessary clamping force to prevent V-bell 1~ from slipping at the highest reduction ratio, [=2 is the necessary clamping force to prevent V-bell 1~ from slipping at the lowest reduction ratio, I-' 0 is the grip when using a conventional hydraulic press)
■Force, "S" indicates the clamping force due to the spring 1. In the V-pel 1 - bottomless continuously variable transmission using the cam mechanism 28 shown in Figure 5, the clamping force is not felt even if the transmission 1 - torque is less than 5 kgm. It can be seen that the transmission 1 herk is directly proportional, and that the occurrence of unnecessary jambs at the bells 1 and 1 can be reduced.

(Mouth) I Tubushifu 1 ~ is done with P1 No 2 F, 273 engaged with jJ.

The sleeves 262 and 272 rotate relative to the sleeve portions 218 and 247 of the movable flange, and
13 is displaced in the direction h (right side in the figure) that increases the effective diameter of the input pulley 23, and the movable flange 2413 is displaced toward the output pulley 2.
Displaced in the norah direction (to the right in the figure) to reduce the effective diameter of 4,
A reduction in the gear ratio is performed. When the gear ratio reaches the control set value, play-~=2G3a3 and 273 are released.

The torsion spring 274 of the revolving mechanism of the upshift 1 temporary 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 changed to reduce the effective diameter of the manual pulley 23 (leftward in the figure).The spring 274 rotates the sleeve 272. Then return and displace the movable flange 2413 in the direction of increasing the effective diameter of the output boob (to the left in the figure). This displacement of the movable flange 23B of the manual pulley 23 is made against the pressing force of the movable flange 23B by the twisting mechanism. When the gear ratio reaches the set value, the brake 263 is released. This downshift 1~
At this time, the first d3 and second upshift l-springs 266 and 267 of the input pulley servo machine 4ti2(3) are twisted and energy is stored.

Brake 263 in this ■ Pell 1-Memorandum gear transmission
．． If the electromagnetic brake of 213 fails and the brake is not engaged, the vehicle can still run with the same gear ratio as before. It is excellent in safety because it prevents accidental changes in the speed ratio, such as those caused by oil pressure leaks in the case of V-belt valor gear changers that change the speed ratio using hydraulic pressure.

Kuratsuji servo lj! The mechanism 3 includes an operating section 33 for operating the clutch, a bushing rod 35 inserted through the input shaft 21, a clutch pedal 3G, and a link mechanism 37 for the clutch pedal. The operation unit 33 is connected to the transmission case 1
0, the -L lever 331, the sliding cap 333 provided on the transmission case, and the bushing rod 3.
A bearing race 337 is abutted against the other end 352 of the 1U drive wheel 7 and supported by a rotating white stone on the inner wall of the 1U drive wheel 7 knob 333 via a release bearing 335.
When the bushing lever 331 is rotated around the fulcrum in the counterclockwise direction in the drawing by manual operation by hand, the sliding cap slides against the engine and presses the bushing lever 3 against the engine. The center of the diaphragm spring 312 is displaced in the direction of the engine I! then move the Zoresha plate in the "carrot" direction and release the clutch.

The clutch pedal link mechanism 37 is fixed at the same time as the bush lever 331 (a link lever 361 disposed outside the transmission case 1o, and a "pull 362" connecting the free end of the link lever 361 and the clutch pedal 3G).
What does it consist of? In this embodiment, in the clutch lever Fi3, when the driver depresses the clutch pedal 36, the bushing lever 331 is rotated around the fulcrum via the cable 362 and the link lever 361, and as described above, the clutch is released and the sliding half-clutch is operated. is done manually. Note that the clutch may be controlled automatically as in the first embodiment.

The forward/reverse switching I1 lateral 4 is comprised of a dog clutch 41, first simple planetary gears 1-43, and second simple planetary gears 1-4.

The dongle 'f41 includes a fork 411 linked to an operating lever, a brake sleeve 413 that is engaged with the fork and slid in the axial direction, a first gear 415 (spline piece), a second gear 411 (spline piece), The 3° first planetary gear set 1-43, which consists of a synchronizer gear 419 (synchronizer ring) installed between the sleeve 413 and the second gear 417, connects the V-pel 1 to the output shaft 22 of the continuously variable transmission. The Subra Inn 2 was established in
The ring gear 431 formed on the lean gear 430 is spline-fitted to the ring gear 49, and the 2-1 of the dog clutch 41.
! A ring gear 433 is connected to the Noah 417 and connected to the lean gear 451 of the second planetary gear 45, and a carrier Ay is connected to the first gear 415 of the dog clutch 41 and connected to the second ring gear 453. 435, J3 and Planetary 1! The 21st lateral gears 437 are spline-fitted to splines 459 provided on the output sleeve 450 connected to the ring gear 451, ring gear 453, and the gear box of the differential mechanism.
and 4T from planetary gear 457. This forward/reverse switching mechanism 41 is configured such that when the sleeve 413 of the dog clutch 41 is manually or automatically engaged with the second gear 417 and the ring gears 433, 433, and 451 are fixed to the case 10, the forward movement of the set gear ratio is performed. made, sleeve 4
13 is the first gear 41! i is in mesh with 17 st743
5 and the ring gear 453 are fixed to the case 10, a backward movement occurs at the set gear ratio.

The differential machine 41i ¥5 has an output sleeve 450, which is the output shaft of the forward/reverse switching mechanism 4, as a hekari, and a gear box 5 integrally connected to the input shaft 450.
2. Universal small gear 53.54, differential man gear 55.5G meshed with the small differential gear, one output @57, spline fitted to the large differential gear, and the V-pel. 1 ~ Output IN of bottomless continuously variable transmission + 1st and 2nd number gear 431.4
51, and the other output @58 with the output sleeve 450 inserted therein.

As described above, the transmission device of the present invention includes a transmission case having the shape of a flat circular can, a fluid coupling provided on the outer periphery of the case, and a fluid coupling provided on the side of the fluid coupling within the transmission case. The centrifugal direct coupling clutch of the fluid coupling provided and the above-mentioned transmission? J
The workpiece tracer placed inside the radius surface inside the J equipment case...
Since it consists of the clutch for i, the combination V of the fluid coupling and the clutch for power '111fai is J3.
As a result, it is possible to shorten the number of directions in one direction, making it easy to install in a small vehicle.Furthermore, since a centrifugal clutch is used as a direct coupling clutch, the following effects are achieved.

a) In order to control the torque transmission capacity of the direct coupling clutch by J to the turbine rotation speed, special ]-1 to [1 -It is directly connected and released naturally without the need for a cable, which prevents engine stoppage.

b) It has a simple configuration because it does not require the Liebo machine 4M for direct clutch control, and is low weight, 1 stroke, lightweight, and compact.

C) In the case of a right-speed transmission, the torque capacity of the 2-1-1 roll clutch is controlled, and it is possible to eliminate shift shifting even with the direct coupling clutch connected. (The centrifugal lock clutch clutch engages and disengages freely according to the turbine rotation speed, so it can be freely engaged and disengaged. Shock during gear shifting is a problem with multi-stage transmissions.)

[BRIEF DESCRIPTION OF THE DRAWINGS] FIG. 1 is a cross-sectional view of an F-type gearbox transmission that combines a transmission device and a south-central transmission according to a first embodiment of the present invention.
FIG. 2 is a sectional view of an FF automobile transmission that combines a transmission device and a gear transmission according to a second embodiment of the present invention;
The figure is a cross-sectional view of the F-type automobile transmission (;1), which is a combination of the transmission device according to the third embodiment of the present invention and the V-bell type continuously variable transmission. The enlarged view and Fig. 5 are graphs for explaining the operation.
G... Centrifugal direct-coupled clutch 17.17'... Aile pump 3.1.19... Clutch servo mechanism No. 4
Figure 28 Figure 5 shows 9 a ≧ return t and 2

Claims (1)

[Scope of Claims] 1) A transmission device case having a flat solidified shape, a fluid coupling provided on the outer periphery of the case, and a fluid coupling provided on the side of the fluid coupling in the transmission VC mounting case. Transmission 1. consists of a centrifugal type direct-coupled collage f- of a fluid coupling, and a power cutoff clutch disposed radially inward within the transmission case.
IJ Soa. 2) The transmission device according to claim 1, wherein the power cutoff clutch is a wet multi-disc clutch.