JPH0833170B2 - Belt type continuously variable transmission - Google Patents

Description

The present invention relates to a belt type continuously variable transmission, and more particularly to a V belt type continuously variable transmission suitable for use in an automatic continuously variable transmission mounted on an automobile. More specifically, the present invention relates to a belt type continuously variable transmission in which a pulley is variably controlled by an actuator including a screw device.

(B) Conventional technology Generally, this type of V-belt type continuously variable transmission (CVT) is
Each of the pulleys has a primary pulley and a secondary pulley that are composed of a movable sheave and a fixed sheave, and is constructed by winding a metal belt around these pulleys, and the movable sheave is moved by a hydraulic actuator to perform an appropriate shift operation ( See, for example, JP-A-57-129953).

Therefore, the continuously variable transmission requires an oil pump and a hydraulic circuit because of the use of hydraulic pressure, has a very complicated structure, is a large-sized device, and exerts excessive belt clamping pressure to transmit the transmission. This is disadvantageous in terms of efficiency and belt durability, and further, if the hydraulic pressure drops for any reason, transmission becomes impossible due to insufficient belt clamping pressure.

Therefore, it is conceivable to variably control the pulley with a mechanical actuator such as a ball screw device instead of the hydraulic actuator. In this case, one of the members of the relatively rotating screw device, usually a female member located outside is used. In order to control the rotation of the screw portion, it is necessary to non-rotatably connect the male screw portion located on the inner side to the fixing member, and therefore, the outside of the radial bearing that supports the shaft, the fixing member or the male screw member and the shaft or It is a usual method to interpose a bearing such as a needle bearing that absorbs relative rotation between the movable sheave and the movable sheave.

(C) Problems to be solved by the invention By the way, recently, due to the adoption of FF (front engine / front drive), there is a tendency that the mounting space for a transmission or the like is limited especially in a small automobile. Even in the continuously variable transmission, there is a demand for further downsizing, especially for shortening the axial dimension, but in the above-mentioned configuration, the radial bearing and the needle bearing are arranged side by side in the axial direction, so The direction dimension becomes longer,
The above-mentioned demand cannot be sufficiently satisfied.

Therefore, according to the present invention, the shaft (or the movable sheave boss portion) is supported by a member that restricts the rotation of the male screw portion of the screw device, and thus the needle bearing and the radial bearing are used in combination to reduce the axial dimension. It is an object of the present invention to provide a belt type continuously variable transmission designed to achieve the above.

(D) Means for Solving the Problems The present invention has been made in view of the above circumstances, and, for example, as shown with reference to FIG.
b), movable sheaves (31b), (32b) and fixed sheaves (31a), (3) supported by (30a) and capable of relative movement in the axial direction.
2a) primary pulley (31) and secondary pulley (32), and movable sheaves (31b), (32b) of both pulleys.
A screw device (for example, ball screw mechanism) (35), (36) consisting of male screw parts (35a), (35b) and female screw parts (35b), (36b) that moves in the axial direction and is wound around both pulleys. A belt type continuously variable transmission (31) including the belt (33).

Then, the radial bearings (3), (2) are attached to the support members (1), (2) integrally provided in the case (15).
The boss (b) or the shaft (30a) of the fixed sheave is supported via (4), and the supporting members (1), (2)
To the screw devices (35), (36) male screw parts (35a), (3
6a), its inner diameter hole and movable sheave bosses (d), (e)
It is characterized in that there is a predetermined gap (c) between them and they are non-rotatably supported.

Specifically, the support members (1) and (2) have flange portions (1a), (1b), (2a), respectively on the inner diameter side and the outer diameter side.
(2b) consisting of an annular member, the outer diameter side flange (1
a) and (2a) support the support member concentrically in the case (15), and the radial bearings (3), (on the inner diameter side of the inner diameter side flange portions (1b), (2b). Put on 4),
Then, the outer diameter side (1c) of the inner diameter side flange portions (1b), (2b),
The male screw portions (35a) and (36a) are non-rotatably supported by (2c).

(E) Action With the above configuration, the rotation of the primary shaft (30b) is transmitted to the primary pulley (31) having a predetermined effective diameter, and further, the secondary pulley (3) is passed through the belt (33).
2) and then to the secondary shaft (30a). Then, based on a signal from the control section, the female screw sections (35b) and (36b) of the screw devices (35) and (36) are not rotatable by the support members (1) and (2). It rotates with respect to the screw parts (35a) and (36a), whereby the female screw part moves back and forth in the axial direction to move the movable sheaves (31b) and (32b) in the same direction, and the pulleys (31), Change the effective diameter of (32) and change gears appropriately. At this time, the fixed sheave boss part b fitted to the primary shaft 30b is supported by the radial bearing 3 mounted on the support member 1, and the male screw part
35a is also supported by the support member 1 with a predetermined gap c between it and the movable sheave boss d. Similarly, the secondary shaft 30a is supported by the radial bearing 3 mounted on the support member 2, and the male screw portion 36b is also supported by the support member 2 with a predetermined gap c between it and the movable sheave boss portion e. To be done.

The reference numerals in parentheses above refer to those in FIG. 1 and do not limit the configuration in any way.

(F) Embodiments First, an outline of an automatic continuously variable transmission to which the present invention can be applied will be described. The automatic continuously variable transmission 12 includes a single planetary gear mechanism 20 and a belt type gear mechanism as shown in FIG. An output member 70 including a continuously variable transmission device 30, a transfer device 80, an input shaft 60, a reduction gear device 71, and an operating gear device 72.
In addition to the above, a forward / reverse rotation switching device 90 including a fluid coupling 13 having a lockup clutch CL and a dual planetary gear mechanism is provided. Further, in the single planetary gear mechanism 20, the element 20S (or 20R) that serves as a reaction force supporting member when using it as a reduction mechanism is interlocked with the locking means F, B1 via the transfer device 80, and the high clutch C2
Can be connected to and disconnected from the input shaft 60 via.

More specifically, the ring gear of the planetary gear mechanism 20.
20R is interlocked with the output part 30a of the continuously variable transmission 30, the carrier 20C is interlocked with the output member 70, and the sun gear 20S is a locking means via the transfer device 80. Reverse brake
It is linked to B1 and high clutch C2.

In the dual planetary gear mechanism 90, the sun gear 90S is connected to the input shaft 60, the carrier 90C is connected to the input shaft 60 via the forward clutch C1, and the ring gear 90R is connected to the reverse brake B2.

Based on the above configuration, each clutch, brake and one-way clutch in the automatic continuously variable transmission 12 operate as shown in FIG. 3 at each position. It should be noted that * indicates that the lockup clutch CL can be operated appropriately.

More specifically, on the low speed side L in the D range, the low one-way clutch F is operated in addition to the connection of the forward clutch C1. In this state, the rotation of the engine crankshaft causes the lockup clutch CL or the fluid coupling 13 to rotate.
Is transmitted to the input shaft 60 via the input shaft 60, is further transmitted directly to the sun gear 90S of the dual planetary gear mechanism 90, and is transmitted to the carrier 90C via the forward clutch C1.
Therefore, the dual planetary gear mechanism 90 rotates integrally with the input shaft 60, transmits positive rotation to the primary shaft 30b of the belt type continuously variable transmission 30, and is further continuously steplessly changed by the continuously variable transmission 30. The rotation is transmitted from the secondary shaft 30a to one element of the single planetary gear mechanism 20, specifically, the ring gear 20R. On the other hand, in this state, the reaction force supporting element that receives the reaction force, specifically, the sun gear 20S is stopped by the low one-way clutch F via the transfer device 80, so that the rotation of the ring gear 20R is decelerated from the carrier 20C. Taken out, and further reduction gear device 7
It is transmitted to the axle shaft 73 via 1 and the differential gear device 72.

On the high-speed side H in the D range, the high clutch C2 is connected in addition to the forward clutch C1. In this state, in the same manner as described above, the forward rotation appropriately changed by the continuously variable transmission 30 is taken out from the secondary shaft 30a and input to the ring gear 20R of the single planetary gear mechanism 20. On the other hand, at the same time, the rotation of the input shaft 60 is transmitted to the sun gear 20S of the single planetary gear mechanism 20 via the high clutch C2 and the transfer device 80, whereby the torque of the ring gear 20R and the sun gear 20S is combined in the planetary gear mechanism 20. Is output from the carrier 20C. At this time, since rotation against the reaction force is transmitted to the sun gear 20S via the transfer device 80, a predetermined positive torque is transmitted via the transfer device 80 without causing torque circulation. The combined torque from the carrier 20C is applied to the reduction gear device 71 and the differential gear device 7
It is transmitted to the axle shaft 73 via 2.

In the operation in the D range, the reverse torque is applied (when the engine is braked) based on the one-way clutch F (when the engine is braked). However, in the S range, the low cost & reverse brake B1 operates in addition to the low one-way clutch F, and Power is transmitted even when torque is applied.

Further, in the R range, the reverse brake B2 operates together with the low coast & reverse brake B1. In this state, the rotation of the input shaft 60 is input to the belt type continuously variable transmission 30 as reverse rotation from the carrier 90C because the ring gear 90R is fixed by the dual planetary gear mechanism 90. On the other hand, the sun gear of the single planetary gear mechanism 20 based on the operation of the low coast & reverse brake B1.
Since 20S is fixed, the reverse rotation from the continuously variable transmission 30 is reduced by the planetary gear mechanism 20, and the output member 70
Taken out.

In the P range and the N range, the low coast & reverse brake B1 operates.

Next, one embodiment of the present invention will be described with reference to FIG.

The automatic continuously variable transmission 12 has a transmission case 15 composed of three divisions, and an input shaft 60 and a primary shaft 30b of a belt type continuously variable transmission 30 are coaxially and rotatably supported in the case 15. And the secondary shaft of the belt type continuously variable transmission 30
30a and the gear shaft 70a are coaxially and rotatably supported to form a second shaft B. Further, on the same axis as the first axis A, a control unit 40 including a fluid coupling 13 having a lockup clutch CL, a forward clutch C1, a high clutch C2, a low coast & reverse brake B1, a reverse brake B2, and a low one-way clutch F. A dual planetary gear mechanism 90, which constitutes a forward / reverse switching device, and a hydraulic pump 17 are provided, and a single planetary gear mechanism 20 is provided coaxially with the second axis B.

Explaining the control unit 40 and the input portion further, the input shaft 60 has the lockup clutch CL and the output member of the fluid coupling 13 engaged at one end thereof, and the sun gear 20S of the dual planetary gear mechanism 90 engaged at the other end thereof. Further, a sleeve portion 15a fixed to the case 15 is disposed on the input shaft 60. Also, the sleeve portion 15a
A sprocket 81 is connected to the shaft via a one-way clutch F, and a sleeve shaft 41 connected to the input shaft 60 is rotatably supported. Further, the sleeve shaft
A forward clutch C1 is installed with its hydraulic actuator 42 on one side of the flange 41a rising from 41, and a high clutch C2 is installed with its hydraulic actuator 43 on the other side. The driven side of the high clutch C2 is connected to a boss of the sprocket 81, and the boss is connected to a low coast and reverse brake B1 disposed in the case 15 together with the hydraulic actuator 45. On the other hand, the forward clutch C1
The driven side of the carrier 90 of the dual planetary gear mechanism 90
It is connected to C and has dual planetary gear mechanism 90.
Ring gear 90R of Case 1 with hydraulic actuator 46
It engages with the reverse brake B2 arranged at 5. The carrier 90C supports the pinion 90P1 meshing with each other and the sun gear 90S, and the pinion 90P2 meshing with the ring gear 90R.

Further, the belt type continuously variable transmission 30 according to the present invention includes a primary pulley 31, a secondary pulley 32, and a belt 33 wound around these pulleys, and both pulleys are fixed sheaves 31a, 32a and movable sheave 31b, respectively. , 32b.

Further, a thrust holding member 34a and a fixed sheave 31a, which are supported by the radial roller bearing 8 and are connected to the primary shaft 30b so as to rotate integrally with the primary pulley 31, with a plurality of disc springs 38 interposed therebetween. A pressure adjusting cam mechanism 34 for applying an axial force corresponding to the transmission torque is disposed between the movable sheave 31b and the movable sheave 31b which is slidably supported by a boss portion b of the fixed sheave 31a via a ball spline. In addition, a ball screw device 35 including a male screw portion 35a and a female screw portion 35b is disposed on the back side thereof. On the other hand, the support member 1 is fitted into the hole 15d formed in the case 15 so as not to move in the radial and rotational directions, and the cover member 15
By attaching e to the case 15 with bolts, it is attached and secured. The support member 1 is made of an annular member having flanges 1a and 1b on the outer diameter side and the inner diameter side, respectively.
The outer diameter side flange portion 1a is concentrically fitted in the case hole portion 15d, and the rotational movement is blocked by a spline formed in a part of the flange portion 1a. Further, the collar portion 1b on the inner diameter side of the support member 1
A radial roller bearing 3 is mounted in the inner diameter hole of the bearing 3, and the bearing 3 supports the boss portion b of the fixed sheave 31a, holds the concentricity of the primary shaft 30b, and carries a radial load. . Further, a spline 1c is formed on the outer diameter side of the inner diameter side collar portion 1b, and the spline 1c
The one end on the inner diameter side of the male screw portion 35a is fitted to the male screw portion 35a, and the male screw portion 35a is separated from the boss portion d of the movable sheave 31b by a predetermined gap c.
It is supported so that it cannot rotate. Further, in the ball screw device 35, the male screw portion 35a is axially immovable to the flange portion 7 fixed to the primary shaft 30b via the thrust bearing, and the female screw portion 35b thereof does not move the thrust bearing to the movable sheave 31b. It is connected so as to move integrally in the axial direction.

On the other hand, in the secondary pulley 32, the fixed sheave 32a is rotatably supported by the radial roller bearing 9 in the case 15 integrally with the secondary shaft 30a, and the movable sheave 32b only slides on the secondary shaft 30a via the ball spline. It is supported freely. Further, on the back surface of the movable sheave 32b, a male screw portion 36a and a female screw portion 36b are provided.
Is provided with a ball screw device 36. Further, the support member 2 is fitted in the hole 15f formed in the case 15 so as not to move in the radial direction and the rotation direction, and is attached by being prevented from being pulled out by the step portion and the snap ring. The support member 2 is composed of an annular member having flange portions 2a and 2b on the outer diameter side and the inner diameter side, respectively, and the outer diameter side flange portion 2a has a case hole 15
Rotational movement is blocked by a spline fitted concentrically with f and formed on a part of the collar portion 2a. Further, a radial roller bearing 4 is mounted in the inner diameter hole of the inner diameter side flange portion 2b of the support member 2, and the bearing 4 holds the secondary shaft 30a with its concentricity and carries a radial load. . Further, a spline 2c is formed on the outer diameter side of the inner diameter side flange portion 2b, and the inner diameter side end of the male screw portion 36a is fitted to the spline 2c, and the male screw portion 36a is movable sheave 32b. A non-rotatable member is supported with a predetermined gap c between the boss portion e and the boss portion e. Further, in the ball screw device 36, its male screw portion 36a is axially immovably connected to a flange 30d fixed to the secondary shaft 30a via a thrust bearing, and its female screw portion 36b is also movable via a thrust bearing to a movable sheave 32b. And are connected so as to move integrally in the axial direction.

Then, the primary pulley 31 and the secondary pulley 32
An operation shaft 37 is rotatably supported between them. In addition,
Since FIG. 3 is a developed view, the operating shaft 37 is drawn upward, but in actuality, the operating shaft 37 is located at an intermediate portion between the primary shaft 30b and the secondary shaft 30a in a front view. A circular gear 37a, a non-circular gear 37b, and a worm wheel 37c are fixed to the operation shaft 37,
The wheel 37c is meshed with a worm 37d connected to an electric motor controlled by an electric signal from the control unit. Further, the circular gear 37a meshes with the wide circular gear 35c fixed to the male screw portion 35b on the primary pulley 31 side, and the non-circular gear 37b is the secondary pulley 32b.
Wide non-circular gear 36c fixed to the female thread 36b on the side
Is engaged.

Further, the single planetary gear mechanism 20 is disposed on the gear shaft 70a that constitutes the second shaft B, and its ring gear 20R is adjacent to the flange 30d and the belt type continuously variable transmission 30.
Is connected to the secondary shaft 30a. A sprocket 82 is rotatably supported on the gear shaft 70a integrally with the sun gear 20S, and the pinion 2 is attached to the gear shaft 70a.
A carrier 20C that rotatably supports 0P is fixed.

On the other hand, between the sprocket 82 integrated with the sun gear 20S on the second shaft B and the sprocket 81 supported by the low one-way clutch F disposed on the sleeve portion 15a coaxial with the first shaft A. A silent chain 83 is wound, and the sprocket and chain constitute a transfer device 80.

The gear shaft 70a integrally forms a gear 71a to form an output member 70, and the gear 71a is engaged with a gear 71c fixed to an intermediate shaft 71b. Further, a small gear 71d is formed on the intermediate shaft 71b, and the gear 71d meshes with a ring gear 72a fixed to the differential gear device 72,
It constitutes the speed reducer 71. Left and right front axle shafts 73 extend from the differential gear unit 72.

 Next, the operation of this embodiment will be described.

The rotation of the engine crankshaft is the lockup clutch CL
Alternatively, it is transmitted to the input shaft 60 via the fluid coupling 13, further transmitted to the sun gear 90S of the dual planetary gear mechanism 90, and further transmitted to the sleeve shaft 41. In the D range and the S range, since the forward clutch C1 is connected and the reverse brake B2 is released, the dual planetary gear mechanism 90 causes the sun gear 90S and the carrier 90C to integrally rotate, and the ring gear 90R also integrally rotates. It is transmitted to the primary shaft 30b of the belt type continuously variable transmission 30.

The rotation of the primary shaft 30b is transmitted to the pressure adjusting cam mechanism 34 via the thrust holding member 34a, and further transmitted to the movable sheave 31b via the fixed sheave 31a of the primary pulley 31 and the ball spline. At this time, in the pressure adjusting cam mechanism 34, an axial force corresponding to the input torque acting on the input shaft 30b acts on the back surface of the sheave 31a via the disc spring 38,
On the other hand, the other sheave 31b is in a state in which the ball screw device 35 is fixed in the longitudinal direction corresponding to the predetermined gear ratio, and therefore an equivalent reaction force acts on the back surface of the sheave 31b via the thrust bearing, Thus, the primary pulley 31 holds the belt 33 with a holding force corresponding to the input torque.
Further, the rotation of the belt 33 is transmitted to the secondary pulley 32 and further to the secondary shaft 30a. Also,
When the belt is transmitted, the motor is controlled based on signals from sensors such as throttle opening and vehicle speed, and the operating shaft 37 is rotated via the worm 37d and the worm wheel 37c. Then, the female screw portion 35b of the primary pulley 31 side ball screw device 35 rotates via the circular gears 37a and 35c, and the female screw portion 36b of the secondary pulley 32 side ball screw mechanism 36 rotates via the non-circular gears 37b and 36c. To do.
As a result, the male screw portion 35 that is prevented from rotating on the case 15 is
The female screw portions 36a, 36b rotate relative to a, 36a, and the ball screw devices 35, 36 move the movable sheaves 31b, 32b via thrust bearings to move the primary pulley 31 and the secondary pulley 32 to a predetermined effective diameter. To obtain the set torque ratio. At this time, since both ball screw devices move linearly, a difference occurs with the original moving amount of the movable sheave defined by the belt 33, but since the secondary pulley 32 side rotates via the non-circular gears 37b, 36c. , The movable sheave is moved by an amount that matches the original amount of movement. Further, the belt clamping pressure by both sheaves 31a, 31b and 32a, 32b acts to pull the primary shaft 30b via the thrust bearing on the primary pulley 31 side, and the case 1
5 does not act on the secondary pulley 32 side, nor does it act on the case 15 by pulling the secondary shaft 30a on the secondary pulley 32 side.

The primary shaft 30b is supported by a radial roller bearing 8 and a radial roller bearing 3 mounted on the support member 1 concentrically held by the case 15 so as to carry a radial load, and The support member 1 blocks the rotation of the male screw portion 35a of the ball screw device 35, and the bearing 3 has a predetermined gap c between the bearing 3 and the movable sheave boss portion d so that the movable sheave 31b and the male screw portion 35a are opposed to each other. It also absorbs rotation. Similarly,
The secondary shaft 30a also supports the radial roller bearing 9 and the support member 2 which is concentrically held by the case 15.
Is supported by being supported by a radial roller bearing 4 mounted in the radial direction, and the supporting member 2
Prevents rotation of the male screw portion 36a of the ball screw device 36 and has a predetermined gap with the movable sheave boss portion e,
The bearing 4 also absorbs the relative rotation between the movable sheave 32 and the male screw portion 35a.

Further, the secondary shaft of the belt type continuously variable transmission 30
The rotation of 30a is transmitted to the ring gear 20R of the single planetary gear mechanism 20, and further via the carrier 20C to the gear shaft 70a.
Is transmitted to

In the low range L in the D range, the low one-way clutch F is in an operating state as shown in FIG. 2, and therefore, when the torque is transmitted from the ring gear 20R to the carrier 20C, the sun gear 20S receives a reaction force. The sun gear 20S is stopped in rotation by the low one-way clutch F via the transfer device 80, and the single planetary gear mechanism 20 constitutes a reduction mechanism. Therefore, the rotation of the secondary shaft 30a of the belt type continuously variable transmission 30 is simply reduced by the single planetary gear mechanism 20,
Further reduction is performed via a reduction gear device 71 including gears 71a, 71c, an intermediate shaft 71b, a gear 71d and a mount gear 72a,
Then, through the differential gear unit 72, the left and right front axle shafts
Transmitted to 73.

Also, when the throttle opening and vehicle speed reach a predetermined value,
The high clutch C2 is connected by the signal from the control unit and switched to the high speed side. Then, the rotation of the input shaft 60 is transmitted to the belt-type continuously variable transmission 30 and the sleeve shaft
It is transmitted to the sprocket 81 via 41 and the high clutch C2, and further transmitted to the sun gear 20S of the single planetary gear mechanism 20 via the silent chain 83 and the sprocket 82. At this time, since the sprocket 81 on the input side of the transfer device 80 was receiving the reaction force from the sun gear 20S of the single planetary gear mechanism by the low one-way clutch F, the shift shock due to the grip change was prevented, and the high clutch C2 was connected. The rotation starts smoothly and torque is transmitted to the sun gear 20S. Thus, the torque continuously changed by the belt type continuously variable transmission 30 and the torque via the transfer device 80 are combined by the single planetary gear mechanism 20, and the combined torque is generated by the carrier 20.
The gear shaft 70a is transmitted from C. Further, similarly to the low speed side, it is transmitted to the left and right front axle shafts 73 via the reduction gear device 71 and the differential gear device 72.

On the low speed side L in the S range, negative torque due to engine braking etc. is also received, so low coast &
The reverse brake B1 is engaged, and the sprocket 81 is prevented from rotating forward and backward. The high-speed side H in the S range is the same as the high-speed side in the D range.

On the other hand, in the R range, the forward clutch C1 is released and the reverse brake B2 is engaged. Therefore, the rotation of the input shaft 60 transmitted to the sun gear 90S of the dual planetary gear mechanism 90 is transmitted as reverse rotation from the carrier 90C to the primary shaft 30b of the belt type continuously variable transmission 30 when the ring gear 90R is stopped. At this time, the reaction torque from the sun gear 20S of the single planetary gear mechanism 20 acts on the sprocket 81 as a reverse rotation via the transfer device 80, so that the low coast & reverse brake B1 is activated to stop the sprocket 81.

(G) Effect of the Invention As described above, according to the present invention, screw devices (35), (36) such as a ball screw device are used as actuators for axially moving the movable sheaves (31b), (32b). Since it is possible to eliminate the problems and disadvantages caused by the hydraulic actuator, the electric signal from the control unit can be directly actuated to the screw device by an electric motor or the like to perform quick and responsive control, Support members (1) and (2) integrally provided on the case (15) prevent rotation of the male screw parts (35a) and (36a), and the support members have radial bearings (3) and (4). ),
It carries the radial load of the shafts (30b) and (30a) and also absorbs the relative rotation between the male screw part and the movable sheaves (31b) and (32b) to reduce the number of bearings and the shaft. Belt type continuously variable transmission (3
0) can be made compact.

[Brief description of drawings]

FIG. 1 is a sectional view showing an automatic continuously variable transmission including a belt type continuously variable transmission according to the present invention. FIG. 2 is a schematic diagram showing the continuously variable transmission, and FIG. 3 is a diagram showing the operation of each element at each position. 1,2 …… Supporting member, 1a, 2a …… Outer diameter side flange part, 1b, 2b …… Inner diameter side flange part, 1c, 2c …… Outer diameter side (spline) of inner diameter side flange part, 3,4… … Radial (roller) bearings, 8,9 ……
Radial (roller) bearing, 12 …… Automatic continuously variable transmission, 13 …… Fluid coupling, 15 …… Case, 15d, 15f …… Hole, 30 …… Belt type continuously variable transmission, 30a …… Secondary shaft, 30b …… Primary shaft, 31 …… Primary pulley, 31a …… Fixed sheave, 31b …… Movable sheave,
32 …… Secondary pulley, 32a …… Fixed sheave, 32b ……
Movable sheave, 33 …… Belt, 35,36 …… (ball) screw mechanism, 35a, 36a …… Male screw part, 35b, 36b …… Female screw part.

Claims (3)

[Claims] 1. A primary pulley and a secondary pulley, each of which comprises a movable sheave and a fixed sheave supported on a shaft and capable of relative movement in the axial direction, and a male screw portion and a female screw portion which axially move the movable sheave of both pulleys. In a belt type continuously variable transmission including a screw device consisting of and a belt wound around both pulleys, a support member integrally provided in a case is provided with a support member of the fixed sheave via a radial bearing. A belt type non-supporting device that supports a boss or a shaft, and non-rotatably supports the male screw part of the screw device on the supporting member with a predetermined gap between the inner diameter hole and the movable sheave boss part. Gearbox. 2. The screw device is a ball screw device.
A belt type continuously variable transmission according to claim 1. 3. The support member comprises an annular member having a flange portion on the inner diameter side and a flange portion on the outer diameter side, and the support member is concentrically supported on the case by the outer diameter side flange portion, and The belt according to claim 1, wherein the radial bearing is mounted on the inner diameter side of the inner diameter side flange portion, and the male screw portion is non-rotatably supported on the outer diameter side of the inner diameter side flange portion. Type continuously variable transmission.