JPS6372964A - Belt type continuously variable transmission - Google Patents

Abstract

PURPOSE:To achieve the shortening in the axial dimension by supporting the bosses of fixed sheaves on supporting members via radial bearings, and moving movable sheaves in the axial directions by means of screw devices. CONSTITUTION:On shafts 30a and 30b, a primary pulley 31 and a secondary pulley 32 consisting of movable sheaves 31b, 32b and fixed sheaves 31a, 32a respectively are provided. The boss parts b of fixed sheaves are supported on supporting members 1, 2 provided integrally to a case 15 via radial bearings 3, 4. In the respective supporting members 1, 2, between the inside diameter holes of screw devices 35, 36 to be fitted with male screw parts 35a, 36a and the boss parts d, e of movable sheaves, a prescribed clearance c is provided. Thus, even the relative rotation between the male screw part and the movable sheave can be absorbed, and the number of bearings can be reduced, and further the dimension in the axial direction can be shortened.

Description

Detailed Description of the Invention (a) Industrial Application Field The present invention relates to a V-belt type continuously variable transmission suitable for use in a belt type continuously variable transmission, particularly an automatic continuously variable transmission installed in an automatic vehicle. The present invention relates to a transmission, and more particularly to a belt-type continuously variable transmission in which a pulley is variably controlled by an actuator consisting of a screw device.

(b) The most important type of conventional technology is the belt-type continuously variable transmission (CVT).
Each pulley is equipped with a primary and secondary pulley consisting of a movable sheave and a fixed sheave, and is constructed by wrapping a belt made by Imaha around both of these pulleys, and the movable sheave is moved by a hydraulic actuator to perform appropriate speed change operations. (For example, see Japanese Patent Application Laid-open No. 129953/1983).

Therefore, since the continuously variable transmission uses hydraulic pressure, it requires an oil pump and a hydraulic circuit, resulting in a very complicated and large device. This is disadvantageous in terms of efficiency and belt durability.Furthermore, if the oil pressure decreases for some reason, the belt clamping pressure becomes insufficient and transmission becomes impossible.

Therefore, instead of a hydraulic actuator, it is possible to variably control the boob with an actuator such as a ball screw device, but in the case of B, one of the members of the screw device that rotates relatively, usually on the outside. In order to control the rotation of the internally located female threaded part, it is necessary to connect the internally located male threaded part to a fixing member in a non-rotatable manner. The usual method is to interpose a bearing, such as a needle bearing, between the shaft or movable sheave to absorb relative rotation.

＆→ Problems that the invention is trying to solve By the way, in recent years, due to the adoption of F-F (front engine/front drive), etc., especially in small cars, the mounting space for gearboxes etc. has tended to be limited, and belt There is also a demand for further compactness in type continuously variable transmissions, especially reduction in the axial dimension, but in the above configuration, the radial bearing and needle bearing are arranged side by side in the axial direction. The axial dimension becomes longer,
The above requirements cannot be fully met.

Therefore, the present invention supports the shaft (or movable sheave boss part) with a member that restricts the rotation of the male threaded part of the screw device, and thereby serves as both the needle bearing and the radial bearing, thereby reducing the axial dimension. One object of the present invention is to provide a belt-type continuously variable transmission device which is designed to improve the speed of transmission.

(b) Means for Solving the Problems The present invention has been made in view of the above-mentioned circumstances.For example, as shown in FIG.
), (30a) and can move relative to each other in the axial direction.

A primary pulley (31) and a secondary pulley consisting of (32b) and fixed sheaves (31a) and (32a)
(32), movable sheave (31b) of both pulleys, (32
b) Externally threaded portions (35a) and (35b) that move in the axial direction
) and a female threaded portion (35b).

A belt-type continuously variable transmission (3) comprising a screw device (for example, a ball screw device structure) (35), (36) consisting of (36b) and a belt (33) wound around both pulleys.
Regarding 1).

Then, radial bearings (3), (
4) supports the boss part (b) of the mJ fixed sheave or the shirt 1-(30a), and supports the supporting member (1), (
At 21 are the male threaded parts (3) of the screw devices (35) and (36).
5a) and (36a) are supported non-rotatably with a predetermined gap (C) between their inner diameter holes and movable sheave bosses (d) and (e).

Specifically, the support members (1) and (2) have flanges (la), (1b), and (2a) on the inner diameter side and outer diameter side, respectively.
, (2b), the supporting member is concentrically supported on the case (15) by its outer diameter steel flange (la), (2a), and its inner diameter side flange ( lb), (
The radial bearings (3) and (4) are located on the inner diameter side of the
), and the external diameter steel (lc), (2c) of the inner diameter side flanges (lb), (2b) are attached to the male threaded part (35a).
, (36a) are supported non-rotatably.

(e) Primary shirt due to the above structure! - The rotation of (30b) is caused by the primary pulley (31) having a predetermined effective diameter.
is further transmitted to the secondary pulley (32) via the belt (33), and is further transmitted to the secondary shaft (3
0a). Then, based on the signal from the control section, the screw device (35).

The female threaded portions (35b) and (36b) of (36) are fixed to the male threaded portion (
35a) and (36a), thereby causing the female threaded portion to retract in the axial direction and move the movable sheaves (31b) and (36a).
32b) in the same direction, and both boos 9 (31) and (3
2) Change the effective diameter and change the speed appropriately. At this time, the fixed sheave boss part fitted to the primary shaft 30b is supported by the radial bearing 3 attached to the support member l, and the at threaded part 35a also leaves a predetermined gap C between it and the movable sheave boss part d. and is supported by the support member 1.

Similarly, the secondary shaft 30a is supported by a radial bearing 3 mounted on the support member 2, and the male threaded portion 36b is also provided with a predetermined gap C between it and the movable sheave boss portion e.
, and is supported by the support member 2.

Note that the above-mentioned reference numerals in parentheses refer to #1 fllJ, and do not limit the equivalent configuration.

(F) Example First, an outline of an automatic continuously variable transmission to which the present invention can be applied will be explained.As shown in FIG. Continuously variable transmission 30,1. In addition to the output member 70 consisting of a transfer device 80, an input shaft 60, a reduction gear device 71, and a differential gear device 72, a lock-up clutch CL is provided.
A forward/reverse switching device 90 consisting of a fluid coupling 13 having a dual planetary gear mechanism and a dual planetary gear mechanism is provided. and,
Single planetary gear mechanism Qi 20 reduces it by 8!
The element 2OS (or 2OR), which becomes a reaction force support member when used as a structure, is transferred to the locking means F and Bl via the transfer device 8o. I am moving, and the high clutch C2 is still working.
It is connected to and disconnected from the input shaft 6o through 1q.

More specifically, planetary gear 8J NIt2 o
The ring gear 20R is interlocked with the output part 3a of the non-speed transmission 3o, the carrier 20C is interlocked with the output member 7o, and the sun gear 203 constitutes a locking means via a transfer device a80. It is interlocked with clutch F, p-coast and reverse brake B1, and also interlocked with Zζ high clutch C21.

Note that the dual planetary gear mechanism 90 has a sun gear 903 connected to the input shaft 60, a carrier 90C connected to the input shaft 60 via a forward clutch C1,
Further, 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 present automatic continuously variable transmission 12 operate as shown in FIG. 3 at each position. Note that * indicates that the lock-up clutch CL can operate as appropriate.

To be more specific, on the low speed side (3) in the D range, the forward clutch CI is connected and the row one-way clutch F is activated. In this state, the rotation of the engine crankshaft is transmitted to the input shaft 60 via the lock-up clutch CL or the fluid coupling 13, and is further transmitted directly to the sun gear 903 of the dual plane gear machine MIt90 and via the forward clutch C1. The signal is transmitted to the C carrier 90C. Therefore, the dual planetary gear mechanism 90 rotates integrally with the input shaft 60, and transmits forward rotation to the primary shaft 1-30 of the belt type continuously variable transmission 30.
b, and furthermore, the continuously variable transmission 30 (the rotation which is continuously variable as appropriate) is transmitted from the secondary shaft 30a to one element of the single planetary gear mechanism 20, specifically the ring gear 2OR.On the other hand, in this state Specifically, the sun gear 203 is stopped by the row one-way clutch F via the transfer device 80, and the rotation of the ring gear 2OR is taken out from the carrier 20C as a decelerated rotation, and further The signal is transmitted to the axle shaft 73 via a reduction gear group 71 and a differential gear device 72.

Furthermore, in the D range, on the high speed side 11, the high clutch C2 is connected in addition to the forward clutch C1.

In this state, the continuously variable transmission g! At step 130, the forward rotation, which has been appropriately changed in speed, is taken out from the seven-candle shaft 30a and input to the ring gear 20R of the single planetary gear mechanism 20.

Meanwhile, at the same time, the rotation of the input shaft 60 is transmitted to the sun gear 203 of the single planetary gear mechanism 20 via the high clutch C2 and the transfer device 80, so that the torque of the ring gear 2OR and the sun gear 203 is combined in the planetary gear mechanism 20. output from carrier 20C. At this time, since the rotation against the reaction force is transmitted to the sun gear 205 via the transfer device 80, a predetermined plus torque is transmitted via the transfer device 80 without causing torque circulation. The combined torque from the carrier 20C is transmitted to the axle shaft 73 via the reduction gear device 71 and the differential gear bag M72.

In addition, in operation in D range, it becomes free when reverse torque is applied (during engine braking) based on one-way clutch F, but in S range, in addition to low 12 clutch F, low cost 1, & reverse brake B
1 is activated and power is transmitted even when reverse torque is applied.

Furthermore, in the N range, the reverse brake B2 operates together with the low coast and reverse brake B1. In this state, 60 degrees of rotation at the input 11 is input to the belt type continuously variable transmission 30 from the carrier 90C as a reverse rotation based on the ring gear 90R being fixed by the dual planetary gear 8M structure 90. On the other hand, the sun gear 208 of the single planetary gear mechanism 20 is fixed based on the operation of the low coast and reverse brake B1, so that the reverse rotation from the continuously variable transmission 30 is decelerated by the planetary gear mechanism 20 and taken out to the output member 70. Ru.

Further, in the P range and the N range, the low coast and reverse brake B1 is operated.

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

This automatic continuously variable transmission 12 has a transmission case 15 that is divided into three parts, and the input shaft 60 and the primary shaft 30b of the belt type continuously variable transmission 30 are coaxially rotatable on the case 15. The secondary shaft 30a and the gear shaft 70a of the belt type continuously variable transmission 30 are coaxially and rotatably supported to constitute a first shaft A, and constitute a second shaft B. Furthermore, on the same axis of the first shaft A, there are a fluid coupling 13 equipped with a lock one-piece clutch CL, a forward clutch C1, and a high clutch C2.
, a low coast and reverse brake B1, a reverse brake B2, and an n-one-way clutch F.
0. A dual planetary gear mechanism 90 and a hydraulic pump 17 constituting a forward/reverse switching device are disposed, and a single planetary gear mechanism 2 is disposed coaxially with the second shaft B.
0 is placed.

Further explaining the control section 40 and the input section, the input shaft 60 has one end engaged with the mouth/aquatub clutch CI and the output member of the fluid coupling 13, and the other end engaged with the sun gear of the dual planetary gear mechanism 90. 90
A case 15 is engaged with the input shaft 60, and a case 15 is also disposed on the input shaft 60.
To 17! ] A sleeve portion 15a is provided. A sprocket 81 is connected to the sleeve portion 15a via a one-way clutch F, and a sleeve shaft 41 connected to the input shaft 60 is rotatably supported. Furthermore, the seven flange portion 41a rising from the sleeve shaft 41 has a forward clutch C1 installed together with its hydraulic actuator 42 on one side, and a high clutch C2 installed together with its hydraulic actuator 43 on the other side. There is. The driven side of the high clutch C2 is connected to the boss portion of the sprocket 81, and the boss portion is disposed in the case 15 together with the hydraulic actuator 45.
It is connected to reverse brake B1. On the other hand, the wave side of the forward clutch C1 is connected to the carrier 90C of the dual planetary gear mechanism 90, and the ring gear 90R of the dual planetary gear mechanism 90 engages with the reverse brake B2 disposed in the case 15 together with the hydraulic actuator 46. ing. Note that the carriers 90C are in mesh with each other and the pinions 9 are in mesh with the sun gear 903.
Pinion 9 meshing with 0PI and ring gear 90R
Supports 0P2.

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 both pulleys, and both pulleys have fixed sheaves 31a, 32n and a movable sheave 31b, respectively. , 32b.

Furthermore, the primary pulley 31 includes 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 through a plurality of disc springs 38 so as to rotate together with the primary shaft 30b. A pressure regulating cam mechanism 34 that applies an axial force corresponding to the transmitted torque is disposed between the movable sheave 31b and the movable sheave 31b. At the same time, a ball screw device 35 consisting of a male threaded portion 35a and a female threaded portion 35b is disposed on the back thereof. On the other hand, the support member 1 is fitted into the hole 15d formed in the case 15 so as to be immovable in the radial and rotational directions, and the cover member 15e is attached to the case 15 with bolts so as to be prevented from coming out. ing. The support member 1 is made of an annular member having an outer diameter steel and flanges 1a and lb on the inner diameter side, respectively, and the outer diameter steel collar 1a fits concentrically into the case hole 15d.
Rotational movement is prevented by a spline formed in a part of a. Further, a radial roller bearing 3 is attached to the inner diameter 6F of the support member 1 + the inner diameter hole of the collar 1b, and the bearing 3 supports the boss of the fixed sheave 31a and maintains the concentricity of the primary shaft 30b. It holds and carries radial loads. Further, a spline IC is formed in the outer diameter steel of the inner diameter side collar portion 1b, and one end of the inner diameter side of the male threaded portion 35a is fitted into the spline 1c, and the male threaded portion 35a is connected to the movable sheave 31b. It is unrotatably supported with a predetermined gap C between it and the boss part d.

Second, the male screw part 35a of the ball screw device 35 is smooth! - The flange portion 7 is fixed to the primary shaft 30b via a bearing, and cannot be moved in the axial direction.
Also, the female threaded portion 35b slides into the movable sheave 31b!
・They are connected through bearings so that they move together in the axial direction.

On the other hand, the secondary pulley 32 has its fixed lap 32a rotatably supported by a radial roller bearing 9 on the case 15 together with the secondary shaft 30a, and the movable sheave 32b is connected to the secondary shaft 30a.
It is supported so that it can only slide freely via a ball spline. Further, on the back surface of the movable sheave 32b, there is a ball screw device [3] consisting of a male screw portion 36a and a female screw portion 36b.
6 are arranged. Further, the support member 2 is fitted into the hole 15f formed in the case 15 so as not to be movable in the radial and rotational directions, and is attached to the support member 2 so as to be prevented from coming out by means of a stepped portion and a snap ring. The support member 2 has a flange portion 2a on the outer diameter steel side and on the inner diameter side, respectively.

2b, the outer diameter steel flange 2a of which fits concentrically into the case hole 15f, and whose rotational movement is prevented by a spline formed in a part of the flange 2a. . Further, a radial roller bearing 4 is installed in the inner diameter hole of the inner diameter side collar portion 2b of the support member 2, and the bearing 4 holds the secondary shaft 30a at an angle of 8 degrees and carries a radial load. Further, a spline 2c is formed on the outer diameter steel of the inner diameter side collar portion 2b, and one end of the inner diameter side of the male threaded portion 36a is fitted into the spline 2C, and the male threaded portion 36a is connected to the movable sheave 32b. It is unrotatably supported with a predetermined gap C between it and the boss e. Further, the ball screw device 36 has a male threaded portion 36a.
is a flange 30 fixed to the secondary shaft 30a.
d via a thrust bearing so that it cannot move in the axial direction, and its female threaded portion 36b is connected to the movable sheave 32b via a thrust bearing so as to move together in the axial direction.

Then, the primary pulley 31 and the secondary pulley 3
2, an operating shaft 37 is rotatably supported. Note that since FIG. 3 is a developed view, the operating shaft 37 is drawn upward, but in reality, the operating shaft 37 is located at an intermediate portion between the primary shaft 30b and the secondary shaft 30a when viewed from the front. A circular gear 37a, a non-circular gear 37b1, and a worm wheel 37c are fixed to the operating shaft 37, and the wheel 37c is connected to a worm 37d connected to an electric motor controlled by an electric signal from a control unit. are meshing. Further, the circular gear 37a is a wide circular gear 35C1L1. fixed to the male threaded portion 35b on the primary pulley 31 side. The non-circular gear 37b is in mesh with the wide non-circular gear 3 fixed to the female threaded portion 36b on the secondary pulley 32 side.
It meshes with 6c.

Also, things? Is the Brinetari Gear machine $420 a gear shaft that constitutes the second shaft B? The ring gear 2OR is connected to the secondary shaft 30a of the belt type continuously variable transmission 30 adjacent to the flange 30d. Further, a sprocket 82 is rotatably supported on the gear shaft 70a integrally with the sun gear 208, and a carrier 20C rotatably supporting the pinion 20P is fixed to the gear shaft 70a.

On the other hand, between the sprocket 82 integrated with the sun gear 203 on the second shaft B and the sprocket 81 supported by the row one-way clutch F disposed on the sleeve portion 15 a coaxial with the first shaft A. is silent chain 8
3 is wound around the sprocket and chain, and these sprockets and chains constitute the transfer equipment M80.

Further, the gear shaft 70a integrally constitutes a gear 71a to constitute an output member 70, and the gear 71a meshes with a gear 71C fixed to an intermediate shaft 71b. Furthermore, a small gear 71d is formed on the intermediate shaft 71b,
The gear 71d meshes with a ring gear 72a fixed to a differential gear M72, thereby forming a speed reduction device 71.

Furthermore, left and right front axle shafts 73 extend from the differential gear device 72 .

Next, the operation of this embodiment will be explained.

The rotation of the engine crankshaft is controlled by the lock-up 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 and S ranges, the forward clutch C1 is connected and the reverse brake B2 is released, so the dual planetary gear el#90 rotates forward as the sun gear 90S and carrier 90C rotate together, and the ring gear 9OR also rotates as one. 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 regulating 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, the pressure regulating cam mechanism 34 applies an axial force corresponding to the input torque acting on the input shaft 30b to the sheave 31 through the disc spring 38.
On the other hand, the other sheave 31b has a ball screw device 35 fixed in its longitudinal direction in accordance with a predetermined gear ratio, and therefore an equivalent force is applied to the back surface of the sheave 31b via a thrust bearing. A reaction force acts, and as a result, the primary pulley 31 clamps the belt 33 with a clamping force corresponding to the input torque. Further, the rotation of the belt 33 is transmitted to the secondary pulley 32, and further transmitted to the secondary shaft 30a. In addition, during the belt transmission, signals from various sensors such as throttle opening and vehicle speed are
The motor is controlled based on the worm 37d.
The operating shaft 37 is rotated via the worm wheel 37c. Then, the female screw portion 3 of the ball screw device M35 on the primary pulley 31 side is connected via the circular gears 37a and 35C.
5b rotates, and the female screw portion 36b of the ball screw mechanism 36 on the secondary pulley 32 side rotates via the non-circular gears 37b and 36c. As a result, the female threaded parts 36a and 36b rotate relative to the male threaded parts 35g and 36a which are fixed to the case 15, and the ball screw devices 35 and 36 are connected to the movable sheave 31b via the thrust bearing. , 32b are moved to set the brake pulley 31 and the secondary pulley 32 to a predetermined effective diameter, thereby obtaining the set torque ratio. At this time, since both ball screw devices move linearly, there is a difference between the original movement a of the movable sheave defined by the belt 33, but the secondary pulley 32 side rotates via the non-circular gears 37b and 36c. Therefore, the movable sheave is moved by an amount matching its original movement m. Matoko, both sheaves 31a, 31b and 32a
, 32b is applied to the belt clamping pressure by the primary pulley 31
On the side, it acts to pull the primary shaft 30b via the thrust bearing and does not act on the case 15, and similarly on the secondary pulley 32 side, it acts to pull the secondary shaft 30a and acts on the case 15. There's nothing to do.

The primary shaft 30b includes a radial roller bearing 8 and a radial roller bearing 3 mounted on the support member 1 held concentrically in the case 15.
The supporting member 1 prevents the rotation of the male screw portion 35a of the ball screw device 35, and the bearing 3 is supported by a predetermined distance VXC between the movable sheave boss portion d and the movable sheave boss portion d. Movable sheave 3
It also absorbs the relative rotation between 1b and the male threaded portion 35n.

Similarly, the secondary shaft 30a is also supported with a radial load carried by a radial roller bearing 9 and a radial roller bearing 4 attached to a support member 2 held concentrically in the case 15. ,
And the support member 2 is connected to the male threaded portion 36 of the ball screw device 36.
The bearing 4 prevents the rotation of the movable sheave 32 and the male threaded portion 35a, and also absorbs the relative rotation between the movable sheave 32 and the male threaded portion 35a, with a predetermined gap provided between the movable sheave boss portion e and the movable sheave boss portion e.

Further, the rotation of the secondary shaft 30a of the belt type continuously variable transmission 30 is transmitted to the ring gear 2OR of the single planetary gear mechanism 20, and further transmitted to the gear shaft 70a via the carrier 20C.

In the case of the low speed side in the D range (i), the row one-way clutch F is in the operating state as shown in FIG. , the sun gear 20S is stopped from rotating by a row one-way clutch F via a transfer device 80, and the single planetary gear mechanism 20 constitutes a reduction gear 4JIJR. The rotation is simply reduced by the single planetary gear mechanism 20, further reduced by the reduction gear device 71 consisting of gears 71a, 71c, intermediate shaft 71b, gear 71d, and mount gear 72a, and then by the differential gear device 72. It is transmitted to the left and right front axle shafts 73.

Furthermore, when the throttle opening degree and vehicle speed reach predetermined values, the high clutch C2 is connected and switched to the high speed side by a signal from the control unit. Then, the rotation of the input shaft 60 is transmitted to the belt type continuously variable transmission 30, and the rotation of the input shaft 60 is transmitted to the sprocket 8 via the sleeve shaft 41 and the high clutch C2.
1, silent chain 83 and sprocket!・Single planetary gear mechanism 20 via 82
be transmitted to the sun gear 203. At this time, since the sprocket 81 at the input end of the transfer device 80 was receiving reaction force from the sun gear 20S of the single planetary gear mechanism at the row one-way clutch F, the shift shock caused by changing the grip was prevented and the high clutch C2 was connected. It starts rotating smoothly and transmits torque to sun gear 2O3.

Thereby, the torque continuously variable by the belt type continuously variable transmission 30 and the torque via the transfer device 80 are combined in the single planetary gear mechanism 20, and the combined torque is transmitted from the carrier 20C to the gear shaft 70a. Furthermore, similarly to the low-speed side described above, the left and right front axle shafts 7 are connected via a reduction gear device 71 and a differential gear device 72.
3 is transmitted and reached.

Further, in the S range, on the low speed side, negative torque due to engine braking etc. is also applied, so the low coast and reverse brake B1 is engaged and the sprocket 81 is prevented from rotating in both forward and reverse directions. Also, the high speed side H in the S range
is the same as the high speed side of the D range.

On the other hand, in R range, forward clutch C1 is released and! Novice brake B2 is engaged. Therefore, the rotation of the input shaft 60 transmitted to the gear 90S of the dual planetary gear mechanism 90 is reversely rotated from the carrier 90C when the ring gear 90R stops, and is transferred to the primary shaft of the belt-type continuously variable transmission 30. -30b. At this time, the reaction torque acts on the sprocket 81 as reverse rotation from the sun gear 203 of the single planetary gear mechanism 20 via the transfer device 80.
Low coast & reverse brake - key B1 operates to stop the sprocket 81.

(G) As described in detail, according to the present invention, the movable sheave (31
b), (32b) are used as actuators to move them in the axial direction.
), it is possible to eliminate problems and disadvantages caused by hydraulic actuators, and the electric signal from the control unit can be applied directly to the screw device by an electric motor, etc., allowing quick and responsive control. However,
Support member (1) integrally provided (ζ) in the case (15)
.

(2) prevents the rotation of the male threaded portions (35aJ, (36a), and radial bearings (3), (4) are attached to the support member.
) and install the shaft (30b).

It carries the radial load of (30a) and also absorbs the relative rotation between the male threaded part and the movable sheaves (31b) and (32b), reducing the number of bearings and shortening the axial dimension. Therefore, the belt type continuously variable transmission (30) can be made more compact.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing an automatic continuously variable transmission equipped with 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, la, 2a/outer diameter steel flange
, lb, 2b...inner diameter side flange, lc. 2C... Outer diameter steel (spline) of the inner diameter side flange, 3.
4...Radial (roller) bearing, 8.9...
・Radial (roller) bearing, 12...Automatic continuously variable transmission, 13...Fluid coupling, 15...Case
, 15d, ISf...hole, 30...bell)
・Continuously variable transmission, 30a... Sekangurin Yaft, 30b... Brima Marine Yaft, 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 thread part
, 35b, 3 [ib...Female screw part.

Claims (3)

[Claims] (1) A primary pulley and a secondary pulley each consisting of a movable sheave and a fixed sheave that are supported by a shaft and can move relative to each other in the axial direction, and a male threaded part and a female threaded part that move the movable sheave of both pulleys in the axial direction. In a belt-type continuously variable transmission comprising a screw device and a belt wound around both pulleys, the boss portion of the fixed sheave is attached to a support member integrally provided in the case via a radial bearing. or a belt type stepless device, which supports a shaft, and supports the male threaded portion of the screw device on the supporting member in a non-rotatable manner with a predetermined gap between the inner diameter hole and the movable sheave boss portion. gearbox. (2) The belt type continuously variable transmission according to claim 1, wherein the screw device is a ball screw device. (3) The support member is an annular member having flanges on the inner diameter side and outer diameter side, and the support member is concentrically supported on the case by the outer diameter side flanges, and the inner diameter side The belt-type bearing according to claim 1, wherein the radial bearing is mounted on the inner diameter side of the flange, and the male threaded part is supported non-rotatably by the outer diameter steel of the inner radial side flange. gear transmission.