JP2003048443A - Transfer for toroidal cvt - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transfer for a toroidal CVT for improving vehicle mountability by shortening the whole length including the toroidal CVT. SOLUTION: This transfer 2 for the toroidal CVT is applied to the toroidal CVT 1 having a toroidal shift part for transmitting driving force inputted from an engine to an input shaft 10 to a counter shaft 15 by friction engagement, inputs driving force from the counter shaft 15 via an auxiliary transmission 5 having a plurality of selectable shift ratios, and transmits the inputted driving force to an output shaft 3 for a rear wheel and an output shaft 4 for a front wheel at a prescribed distribution ratio by a clutch 31. The output shaft 3 for the rear wheel is provided rotatably for the input shaft 10 and on the same axis as that of the input shaft 10. Subsequently, the auxiliary transmission 5 is provided on an outer periphery of the output shaft 3 for the rear wheel.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is applied to a four-wheel drive vehicle and has a toroidal CVT (ContinuouslyVariableTransmi).
ssion) transfer, especially toroidal CV
The present invention relates to a transfer for a toroidal CVT that has a shorter overall length including T to improve vehicle mountability.

[0002]

2. Description of the Related Art FIG. 5 shows a conventional transfer for a toroidal CVT. The transfer 2 for the toroidal CVT is transmitted from the engine to the toroidal CVT 1.
A steplessly-shifted driving force is accelerated and decelerated by the auxiliary transmission 5, and the accelerated and decelerated driving force is distributed to the rear wheel output shaft 3 and the front wheel output shaft 4 at a predetermined distribution ratio. Is.

The toroidal CVT1 is a double-cavity toroidal type continuously variable transmission that has two toroidal speed change parts (only one of which is shown in the figure) to increase the transmission torque, and is generated in the engine. An input shaft 10 into which driving force is input via a torque converter and a forward / reverse switching device (not shown), and an input disk 12 provided around the input shaft 10 and holding a power roller 11 therebetween.
And a toroidal speed changer composed of the output disc 13 and the output disc 13 provided in parallel with the input shaft 10.
Is rotatably supported with respect to the input shaft 10 by the needle shaft 17 and the roller bearing 18 and the counter shaft 15 whose driving force is transmitted through the gears 14A and 14B from the counter shaft 15. Idler gear not shown,
And the drive shaft 16 transmitted via the drive gear 16a. In the figure, 19 is a slide bearing.

The transfer 2 for toroidal CVT is
A rear wheel output shaft 3 rotatably provided on the same axis as the drive shaft 16 of the toroidal CVT 1;
The front wheel output shaft 4 provided in parallel with the rear wheel output shaft 3
An auxiliary transmission 5 provided on the CVT 1 side of the rear wheel output shaft 3, a hydraulic unit 6 that applies a predetermined hydraulic pressure to a multi-disc clutch 31 described later via a pipe 6a, and a hydraulic unit 6
And a control circuit 7 for controlling the hydraulic pressure generated by. The rear wheel output shaft 3 and the front wheel output shaft 4 are supported by a case 9 by ball bearings 8.

A drive sprocket 30 rotatably provided on the rear wheel output shaft 3 by a needle bearing 17 on the outer periphery of the rear wheel output shaft 3, a clutch housing 32 for accommodating a multi-plate clutch 31, and a multi-plate. Clutch 31
A pressing member 33 that presses or releases the pressing member 33 and a piston 34 that presses the pressing member 33 are provided. Multi-plate clutch 31
Is composed of a plurality of clutch disks 31a and pusher plates 31b that transmit driving torque by making surface contact with each other. The clutch housing 32 includes an outer housing 32a that accommodates the clutch disc 31a and is coupled to and supported by the drive sprocket 30, and an inner housing 32b that accommodates the pusher plate 31b and is coupled to and supported by the rear wheel output shaft 3.
It consists of and. A clutch spring 35 is arranged between the inner housing 32b and the pressing member 33 in order to bring the clutch disc 31a and the pusher plate 31b into a non-contact state when the multi-plate clutch 31 is released. In order that the piston 34 can transmit the pressing force to the rotating pressing member 33, the pressing member 33 and the piston 34
The needle bearing 17 is arranged between the two.

A driven sprocket 40 is provided on the outer periphery of the front wheel output shaft 4, and a chain 41 is wound around the driven sprocket 40 and the drive sprocket 30.

The auxiliary transmission 5 is connected to a drive shaft 16 and is rotatably supported by a needle bearing 17 on a rear wheel output shaft 3, a hollow shaft 50, a sun gear 50a formed on the hollow shaft 50, and a sun gear. A planetary gear 51 that meshes with 50a, a planetary gear support plate 53 that supports the planetary gear 51 by a support shaft 52, an inner gear 54 that is connected to the support shaft 52 of the planetary gear 51, and a rear wheel output shaft 3 are slidable. And a slide gear 55 supported by.

In the transfer 2 for toroidal CVT constructed as described above, the drive force transmitted from the drive shaft 16 of the toroidal CVT 1 to the hollow shaft 50 of the transfer 2 is selected by the position of the slide gear 55 of the auxiliary transmission 5. The gear ratio is changed and transmitted to the rear wheel output shaft 3. On the other hand, the piston 34 applies a predetermined pressing force to the multi-plate clutch 31 via the pressing member 33 by the hydraulic pressure from the hydraulic unit 6 under the control of the control circuit 7. The driving force transmitted to the rear wheel output shaft 3 is distributed by the multi-plate clutch 31 at a predetermined distribution ratio to the rear wheel output shaft 3 and the front wheel output shaft 4.
Be distributed to.

[0009]

However, according to the conventional transfer for toroidal CVT, the driving force is temporarily applied to the drive shaft 16 coaxial with the input shaft 10 of the CVT 1 via the counter gear 15a, the idler gear and the drive gear 16a. After the transmission of the CV, the auxiliary transmission 5 arranged coaxially with the drive shaft 16 shifts to a predetermined gear ratio.
There is a problem that the total length including T1 becomes very long. Further, since the CVT 1 and the transfer 2 are connected by the drive shaft 16 and the hollow shaft 50 provided on the same axis, there is a problem that the total length becomes longer and the mountability on the vehicle is poor. In addition, since the number of parts is increased, the mass is increased and the cost is increased.

Therefore, an object of the present invention is toroidal CV.
An object of the present invention is to provide a transfer for a toroidal CVT, which has a shorter overall length including T to improve vehicle mountability.

[0011]

In order to achieve the above object, the present invention is provided in parallel with a first shaft to which a driving force is input from a prime mover, and the first shaft. Is provided on the outer periphery of the first shaft and a second shaft to which the driving force is transmitted from, and transmits the driving force input to the first shaft to the second shaft by frictional engagement. Applied to a toroidal CVT having a toroidal transmission,
The driving force transmitted to the shaft of the rear wheel is input through the auxiliary transmission having a plurality of selectable gear ratios, and the input driving force is applied to the first wheel for the rear wheels or the front wheels at a predetermined distribution ratio by the clutch. In the transfer for a toroidal CVT, which transmits the output shaft of the first output shaft and the second output shaft for the front wheels or the rear wheels, the first output shaft is rotatably the same as the first shaft with respect to the first shaft. The auxiliary transmission is provided on an axis, and the auxiliary transmission includes an auxiliary shaft provided in parallel with the first output shaft, and is configured by using the first output shaft and the auxiliary shaft. Provide transfer for toroidal CVT.

In order to achieve the above object, the present invention is provided in parallel with a first shaft to which a driving force is input from a prime mover, and the driving force is transmitted from the first shaft. A second shaft, and a toroidal speed changer provided on the outer periphery of the first shaft and transmitting the driving force input to the first shaft to the second shaft by frictional engagement. The driving force applied to the toroidal CVT and transmitted to the second shaft is input through an auxiliary transmission having a plurality of selectable gear ratios, and the input driving force is applied to a predetermined distribution ratio by a clutch. In a toroidal CVT transfer for transmitting to a first output shaft for rear wheels or front wheels and a second output shaft for front wheels or rear wheels, the auxiliary transmission is provided on the outer periphery of the second shaft. Toroidal CV characterized by To provide a use transfer.

[0013]

1 shows a transfer for a toroidal CVT according to a first embodiment of the present invention. The toroidal CVT transfer 2 is transmitted from the engine and steplessly changed in speed by the toroidal CVT 1 is accelerated and decelerated by the auxiliary transmission 5, and the increased and decelerated driving force is rearranged at a predetermined distribution ratio. It is distributed to the wheel output shaft 3 and the front wheel output shaft 4.

The toroidal CVT1 is a double-cavity toroidal type continuously variable transmission which has two toroidal speed change parts (only one of which is shown in the figure) to increase the transmission torque. An input shaft 10 into which driving force is input via a torque converter and a forward / reverse switching device (not shown), and an input disk 12 provided around the input shaft 10 and holding a power roller 11 therebetween.
And a toroidal speed changer composed of the output disc 13 and the output disc 13 provided in parallel with the input shaft 10.
And a counter shaft 15 from which the driving force is transmitted via gears 14A and 14B.

The power roller 11 transmits power from the input disk 12 to the output disk 13 by frictional engagement. The input disk 12 is provided so as to rotate integrally with the input shaft 10, and is provided so as to be movable along the axis of the input shaft 10 by a slide bearing 19. The output disk 13 is rotatably provided with respect to the input shaft 10 by a needle bearing 17. Input disk 12 and output disk 1
3 has toroidal curved surfaces 12a and 13a,
The power roller 11 is sandwiched and pressed between the input disk 12 and the output disk 13,
The gear ratio is continuously changed by continuously changing the inclination angle of.

The transfer 2 for toroidal CVT is
A rear wheel output shaft 3 rotatably provided on the same axis as the input shaft 10 of the toroidal CVT 1.
A front wheel output shaft 4 provided in parallel with the rear wheel output shaft 3; an auxiliary transmission 5 provided on the CVT 1 side of the rear wheel output shaft 3; It has a hydraulic unit 6 that gives a predetermined hydraulic pressure via the control unit 7 and a control circuit 7 that controls the hydraulic pressure generated by the hydraulic unit 6.
The rear wheel output shaft 3 and the front wheel output shaft 4 are supported by a case 9 by ball bearings 8.

A drive sprocket 30 rotatably provided on the rear wheel output shaft 3 by a needle bearing 17 on the outer periphery of the rear wheel output shaft 3, a clutch housing 32 for accommodating a multi-plate clutch 31, and a multi-plate. Clutch 31
A pressing member 33 that presses or releases the pressing member 33 and a piston 34 that presses the pressing member 33 are provided. Multi-plate clutch 31
Is composed of a plurality of clutch disks 31a and pusher plates 31b that transmit driving torque by making surface contact with each other. The clutch housing 32 includes an outer housing 32a that accommodates the clutch disc 31a and is coupled to and supported by the drive sprocket 30, and an inner housing 32b that accommodates the pusher plate 31b and is coupled to and supported by the rear wheel output shaft 3.
It consists of and. A clutch spring 35 is arranged between the inner housing 32b and the pressing member 33 in order to bring the clutch disc 31a and the pusher plate 31b into a non-contact state when the multi-plate clutch 31 is released. In order that the piston 34 can transmit the pressing force to the rotating pressing member 33, the pressing member 33 and the piston 34
The needle bearing 17 is arranged between the two.

A driven sprocket 40 is provided on the outer periphery of the front wheel output shaft 4, and a chain 41 is wound around the driven sprocket 40 and the drive sprocket 30.

The sub-transmission 5 is rotatably mounted on the sub-shaft 56 provided in parallel with the rear wheel output shaft 3 and the rear-wheel output shaft 3 by a needle bearing 17, and the counter gear 15a of the counter shaft 15 is provided. A small gear 57A that meshes with an idler gear (not shown), a large gear 57B that is also rotatably provided on the rear wheel output shaft 3 by a needle bearing 17, and a secondary shaft 56. A large gear 57C that meshes with the third small gear 57A,
Similarly, the large gear 5 of the rear wheel output shaft 3 is provided on the sub shaft 56.
7B, and a slide gear 58 that is slid to selectively connect the small gear 57A or the large gear 57B of the rear wheel output shaft 3 to the rear wheel output shaft 3.

Next, the operation of the transfer 2 of the first embodiment will be described. The driver operates the shift lever (not shown) to move the slide gear 58 to the H side or the L side. When the slide gear 58 is moving to the H side, the small gear 57A on the rear wheel output shaft 3 is connected to the rear wheel output shaft 3, so that the driving force from the CVT 1 is generated by the counter gear 15a and the small gear. It is transmitted to the rear wheel output shaft 3 through the gear 57A at a constant speed, for example. When the slide gear 58 is moving to the L side, the small gear 57A on the rear wheel output shaft 3 is disconnected from the rear wheel output shaft 3, and the large gear 57B is connected to the rear wheel output shaft 3. Therefore, the driving force from the CVT 1 is the counter gear 15a, the small gear 57A, and the countershaft 56.
It is transmitted to the rear wheel output shaft 3 at a predetermined reduction ratio via the upper large gear 57C, the small gear 57D, and the large wheel 57B on the rear wheel output shaft 3. In addition, the driver operates a mode selection lever portion (not shown) to select a mode such as 4WD mode or 2WD mode. The mode selection lever unit outputs a mode selection signal indicating the selected mode to the control circuit 7. The control circuit 7 controls the hydraulic unit 6 so as to supply the hydraulic oil having the pressure corresponding to the mode selection signal to the piston 34.
To control. The hydraulic unit 6 supplies the hydraulic oil having a pressure corresponding to the mode selection signal to the piston 34. The piston 34 presses the pressing member 33 against the spring force of the clutch spring 35 by the hydraulic oil, and the clutch disc 31 a and the pusher plate 31 of the multi-plate clutch 31.
Press b. The multi-plate clutch 31 distributes the driving force to the front wheel output shaft 4 via the drive sprocket 30 and the chain 41 at a distribution ratio according to the pressing force.

According to the first embodiment, the rear wheel output shaft 3 is directly connected to the input shaft 10 of the CVT 1 without using the conventional drive shaft 16 and hollow shaft 50 shown in FIG. , The total length including CVT1 is shortened, and the mountability on the vehicle can be improved. Therefore, it is possible to mount the system on a vehicle with a small space. Further, since the number of gears used is smaller than in the conventional case, it is possible to reduce the mass and the cost. Also, the CVT 1 and the transfer 2 can be manufactured as one unit, and various expenses can be reduced.

FIG. 2 shows a toroidal CVT transfer according to a second embodiment of the present invention. This second embodiment differs from the first embodiment in that the auxiliary transmission 5
Is provided on the count shaft 15 and the multi-disc clutch 31 is provided on the front wheel output shaft 4.

A driven gear 36 is provided on the outer periphery of the rear wheel output shaft 3, and a driven gear 42, a clutch housing 32 for accommodating the multiple disc clutch 31, and a multiple disc clutch are provided on the outer periphery of the front wheel output shaft 4. A pressing member 33 that presses or releases 31 and a piston 34 that presses the pressing member 33 are provided.

The sub transmission 5 includes a small gear 57A rotatably provided on the counter shaft 15 by a needle bearing 17, a large gear 57B rotatably provided on the counter shaft 15 by a needle bearing 17, and a counter shaft. 15 and a large gear 57C which is provided on the auxiliary shaft 56 and meshes with the small gear 57A of the counter shaft 15, and a large gear 57C which is also provided on the auxiliary shaft 56 and is arranged on the large gear 57B of the counter shaft 15. It has a small gear 57D that meshes with it, and a slide gear 58 that selectively connects the small gear 57A or the large gear 57B of the counter shaft 15 to the counter shaft 15. As shown in FIG. 3, the small gear 57D meshes with the driven gear 42 at a phase position different from the phase position meshing with the large gear 57B, and also meshes with the driven gear 36 at a different phase position. The large gear 57B and the driven gear 36 are arranged so as to overlap each other in the axial direction.

Next, the operation of the transfer 2 of the second embodiment will be described. The driver operates the shift lever (not shown) to move the slide gear 58 to the H side or the L side. When the slide gear 58 is moving to the H side, the large gear 57B on the counter shaft 15 is connected to the counter shaft 15, so the driving force from the CVT 1 is the large gear 57B and the small gear on the counter shaft 56. It is transmitted to the rear wheel output shaft 3 at a constant speed, for example, via 57D and the driven gear 36. When the slide gear 58 is moving to the L side, the small gear 57 on the counter shaft 15
Since A is connected to the counter shaft 15, CVT
The driving force from 1 is transmitted to the rear wheel output shaft 3 at a predetermined reduction ratio via the small gear 57A, the large gear 57C on the auxiliary shaft 56, the small gear 57D and the driven gear 36. In addition, the driver operates a mode selection lever portion (not shown) to select a mode such as 4WD mode or 2WD mode. The mode selection lever unit outputs a mode selection signal indicating the selected mode to the control circuit 7. The control circuit 7 controls the hydraulic unit 6 to supply the hydraulic oil having a pressure corresponding to the mode selection signal to the piston 34. Hydraulic unit 6
Supplies the hydraulic oil having a pressure corresponding to the mode selection signal to the piston 34. The piston 34 presses the pressing member 33 against the spring force of the clutch spring 35 with hydraulic oil, and presses the clutch disc 31a and the pusher plate 31b of the multi-plate clutch 31. The multi-plate clutch 31 distributes the driving force transmitted via the small gear 57D on the auxiliary shaft 56 and the driven gear 42 to the front wheel output shaft 4 at a distribution ratio according to the pressing force.

According to the second embodiment, the transfer 2 is connected through the counter shaft 15 without using the conventional drive shaft 16 and hollow shaft 50 shown in FIG. 5, so that the entire length including the CVT 1 is connected. Can be shortened, and the vehicle mountability can be improved. In particular, the gear 36 and the gear 42
Since the gear 57 and the gear 57 mesh with the different phases of the gear 57D and the input gear and the output gear of the driving force are performed by one gear, the number of parts can be reduced. Further, the total length can be shortened. 2A, the large gear 57B and the driven gear 3
6 and the driven gear 42 are arranged so as to overlap each other in the axial direction, the overall length can be further shortened.

FIG. 4 shows a toroidal CVT transfer according to a third embodiment of the present invention. In the third embodiment, instead of the counter shaft 15 in the first embodiment, the rear wheel output shaft 3 and the front wheel output shaft 4 are arranged on the same axis, and the rear wheel output shaft 3 is arranged. 3, an auxiliary transmission 5 that performs the same planetary motion as in the conventional example is provided, and a multi-disc clutch 31 is provided on the front wheel output shaft 4.

A drive sprocket 20 is provided on the input shaft 10 of the toroidal CVT 1, and an auxiliary transmission 5 that makes a planetary motion and a driven sprocket 40 are provided on the outer periphery of the rear wheel output shaft 3. And winding the chain 41 around the drive sprocket 20,
A clutch housing 32 that accommodates the multi-plate clutch 31, a pressing member 33 that presses or releases the multi-plate clutch 31, and a piston 34 that presses the pressing member 33 are provided on the outer periphery of the front wheel output shaft 4.

Next, the operation of the transfer 2 of the third embodiment will be described. The driver operates the shift lever (not shown) to move the slide gear 55 to the H side or the L side. Since the slide gear 55 does not mesh with the inner gear 54 when the slide gear 55 is moving to the H side, the driving force transmitted from the input shaft 10 of the CVT 1 to the driven sprocket 40 via the drive sprocket 20 and the chain 41 is , Is transmitted to the rear wheel output shaft 3 at a constant speed, for example. When the slide gear 55 is moving to the L side, the slide gear 55 meshes with the inner gear 54, and the planet gear 51 makes a planetary motion around the sun gear 50a. Therefore, the drive sprocket 20 and the chain 41 are separated from the input shaft 10 of the CVT 1. The driving force transmitted to the driven sprocket 40 via the above is transmitted to the rear wheel output shaft 3 at a predetermined reduction ratio. In addition, the driver operates the mode selection lever portion (not shown) to select the 4WD mode, the 2W mode.
Select a mode such as D mode. The mode selection lever unit outputs a mode selection signal indicating the selected mode to the control circuit 7. The control circuit 7 controls the hydraulic unit 6 to supply the hydraulic oil having a pressure corresponding to the mode selection signal to the piston 34. The hydraulic unit 6 supplies the hydraulic oil having a pressure corresponding to the mode selection signal to the piston 34.
The piston 34 presses the pressing member 33 against the spring force of the clutch spring 35 with hydraulic oil, and presses the clutch disc 31a and the pusher plate 31b of the multi-plate clutch 31. The multi-plate clutch 31 distributes the driving force transmitted from the rear wheel output shaft 3 to the front wheel output shaft 4 at a distribution ratio according to the pressing force.

According to the third embodiment, the rear wheel output shaft 3 and the front wheel output shaft 4 are input shafts without using the conventional drive shaft 16, hollow shaft 50 and counter shaft 15 shown in FIG. Since it is provided in parallel with 10, the total length including the CVT 1 is shortened, and the vehicle mountability can be improved. In addition, the number of parts is reduced compared to other embodiments,
The mass can be reduced, and the vehicle mountability is further improved.

[0031]

As described above, according to the toroidal CVT transfer of the present invention, the auxiliary transmission is provided with the first output shaft or the second shaft rotatably provided with respect to the first shaft. By installing it on the outer circumference of the toroidal CV
The total length including T is shortened, and the mountability on the vehicle can be improved.

[Brief description of drawings]

FIG. 1 is a toroidal C according to a first embodiment of the present invention.
It is a block diagram of the transfer for VTs.

FIG. 2 is a toroidal C according to a second embodiment of the present invention.
It is a block diagram of the transfer for VTs.

FIG. 3 is a diagram showing a meshed state of the gears in FIG.

FIG. 4 is a toroidal C according to a third embodiment of the invention.
It is a block diagram of the transfer for VTs.

FIG. 5 is a configuration diagram of a conventional toroidal CVT transfer.

[Explanation of symbols]

1 Toroidal CVT 2 Toroidal CVT transfer 3 Output shaft for rear wheels Output shaft for 4 front wheels 5 Sub transmission 6 hydraulic unit 6a pipe 7 control circuit 8 ball bearings 9 cases 9a opening 10 input axes 11 Power roller 12 input disks 12a, 13a curved surface 13 Output disc 14A, 14B gear 15 counter shaft 15a counter gear 16a drive gear 16 drive shaft 17 Needle Bearing 18 Roller bearing 19 Slide bearing 20 drive sprocket 30 drive sprocket 31 Multi-disc clutch 31a clutch disc 31b Pusher plate 32 clutch housing 32a outer housing 32b inner housing 33 Pressing member 34 Piston 35 clutch spring 36 Driven Gear 40 Driven Sprocket 41 chains 42 Driven Gear 50 hollow shaft 50a sun gear 51 planetary gears 52 Support shaft 53 Planetary gear support plate 54 Inner Gear 55 slide gear 56 Secondary axis 57A small gear 57B large gear 57C large gear 57D small gear 58 slide gear

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Kazutoshi Murakami             Fuji Co., Ltd. 2418 Washizu, Kosai City, Shizuoka Prefecture             In Univance (72) Inventor Akira Yagi             Fuji Co., Ltd. 2418 Washizu, Kosai City, Shizuoka Prefecture             In Univance F-term (reference) 3D043 AA06 AB17 EA02 EA18 EA35                       EA40 EB06 EB12 EB14 EC01                       EC03 EF06

Claims (6)

[Claims] 1. A first shaft to which a driving force is input from a prime mover, a second shaft which is provided parallel to the first shaft, and to which the driving force is transmitted from the first shaft, The present invention is applied to a toroidal CVT that is provided on the outer periphery of a first shaft and has a toroidal speed change unit that transmits the driving force input to the first shaft to the second shaft by frictional engagement. The driving force transmitted to the shaft of the rear wheel is input through the auxiliary transmission having a plurality of selectable gear ratios, and the input driving force is applied to the first wheel for the rear wheels or the front wheels at a predetermined distribution ratio by the clutch. In the transfer for a toroidal CVT, which transmits to the second output shaft for front wheels or rear wheels, the first output shaft is the same as the first shaft so as to be rotatable with respect to the first shaft. Is provided on the axis, and the auxiliary transmission is The output shaft comprises a countershaft disposed parallel to, the first transfer for a toroidal CVT, characterized in that the output shaft and the constructed using the auxiliary axis. 2. A first shaft to which a driving force is input from a prime mover, a second shaft which is provided in parallel with the first shaft and which transmits the driving force from the first shaft, and The present invention is applied to a toroidal CVT that is provided on the outer periphery of a first shaft and has a toroidal speed change unit that transmits the driving force input to the first shaft to the second shaft by frictional engagement. The driving force transmitted to the shaft of the rear wheel is input through the auxiliary transmission having a plurality of selectable gear ratios, and the input driving force is applied to the first wheel for the rear wheels or the front wheels at a predetermined distribution ratio by the clutch. Of the toroidal CVT for transmitting the output shaft of the vehicle to the second output shaft for the front wheels or the rear wheels, wherein the auxiliary transmission is provided on the outer periphery of the second shaft. . 3. The toroidal according to claim 2, wherein the auxiliary transmission includes an auxiliary shaft parallel to the second shaft, and is configured by using the second shaft and the auxiliary shaft. Transfer for CVT. 4. The sub transmission includes a sub shaft parallel to the second shaft, the sub shaft including gears provided on the first and second output shafts, and the second shaft. 3. The toroidal CVT transfer according to claim 2, wherein gears for transmitting the driving force from the gears are provided with gears that mesh with each other in different phases. 5. The toroidal C according to claim 2, wherein the sub transmission is configured by using a planetary gear mechanism.
Transfer for VT. 6. The toroidal CVT transfer according to claim 2, wherein the clutch and the auxiliary transmission are provided on the outer circumference of the first output shaft and the second output shaft.