JPH07122452B2 - V-belt type continuously variable transmission - Google Patents

Description

TECHNICAL FIELD The present invention relates to a V-belt type continuously variable transmission, and more particularly to a V-belt type continuously variable transmission suitable for being mounted on an automobile.

(B) Conventional Technology Generally, this type of V-belt type continuously variable transmission (CVT) is provided with a primary sheave and a secondary pulley each of which is a movable sheave and a fixed sheave, and is constructed by winding the V-belt around these pulleys. And the movable sheave is moved by a hydraulic piston to perform an appropriate shift operation.

Therefore, since the continuously variable transmission uses hydraulic pressure, it requires an oil pump and a hydraulic circuit, has a very complicated structure and becomes a large-sized device, and exerts a belt clamping pressure more than necessary and transmits it. It is also disadvantageous in terms of efficiency and belt durability. Further, if the hydraulic pressure is lowered for some reason, the belt clamping pressure becomes insufficient and transmission becomes impossible.

Therefore, as disclosed in Japanese Patent Laid-Open No. 60-8558, recently, a movable cam of both primary and secondary pulleys is provided with a pressure adjusting cam mechanism that applies an axial force according to a load,
Further, the link mechanism is connected so that the axial force generated by the pressure adjusting cam mechanism acts on both pulleys, and the ratio selector mechanism is connected to the movable sheave of the primary pulley.
A belt type continuously variable transmission that selects a predetermined gear ratio has been devised.

(C) Problems to be Solved by the Invention By the way, the continuously variable transmission is excellent in that axial force corresponding to the transmission torque is not generated and the belt clamping pressure is not applied more than necessary. Since the pressure adjusting cam mechanism of both pulleys is connected by the link mechanism, the structure is very complicated. Especially, since the link mechanism is used, the axial force for holding the belt acts on the bearing, and the bearing is supported by the fixed member that does not rotate, so that it is necessary to support a high relative speed that is the rotational speed of the pulley. However, the structure is extremely disadvantageous in terms of durability.

Therefore, the present applicant has filed Japanese Patent Application No. 60-153132 (Japanese Unexamined Patent Publication No.
13854), a ball screw mechanism is used as an actuator mechanism for moving the movable sheaves of both pulleys in the axial direction, and both the primary and secondary side ball screw mechanisms are interlocked via a power transmission device to realize a continuous transmission. We proposed a continuously variable transmission in which the female and male threads of both actuator mechanisms rotate together with the pulley shaft during constant speed rotation, thus reducing the rotational load on the bearings.

By the way, the above-mentioned continuously variable transmission performs a gear shifting operation by relatively rotating the male screw portion and the female screw portion of both ball screw mechanisms. The gear shifting operation involves screwing a primary movable sheave with a motor. The transmission moves axially through the roller (A), or a hydraulic motor is installed on a counter shaft composed of double shafts constituting the power transmission device, and the double shafts rotate relative to each other (B). It is done by

For this reason, in the case of the above-mentioned A, a large peripheral speed always acts on the roller and a balance axial force of the speed change and the pulley axial force acts on the roller, which is extremely disadvantageous in terms of durability. Since it acts on the case via the screw transmission device, it is necessary to configure the case with a robust one. Further, in the above-mentioned B, it is necessary to form an oil passage in the counter shaft and to pipe up to the oil passage, the configuration becomes extremely complicated, a large reduction ratio cannot be obtained, and fine shift operation is difficult. However, it cannot be mechanically fixed to the gear ratio like a screw, and it is difficult to maintain the gear ratio at a predetermined position.

Therefore, the present invention intervenes a planetary gear mechanism in the power transmission device, and makes it possible to easily perform a gear shifting operation by providing relative rotation to the two power transmission systems by the planetary gear mechanism, thereby eliminating the above-mentioned drawbacks. An object of the present invention is to provide a gear transmission.

(D) Means for solving problems.

The present invention has been made in view of the above circumstances, and as shown in FIG. 1, for example, a primary and secondary pulley 5 including two sheaves 7, 9, 33, 35 that can move relative to each other in the axial direction. In the V-belt type continuously variable transmission 1 having both pulleys and a belt wound around these pulleys, a pressure adjusting mechanism 11 for directly applying an axial force corresponding to a transmission torque to at least one of the pulleys, 43 and first and second members 22 and 23 that can rotate relative to each other, and the first member 22 is integrated with the movable sheave 7 of either one of the primary and secondary pulleys (for example, the primary pulley 5). Is provided in the first member with respect to the second member 23 based on relative rotation of the first and second members.
A first actuator mechanism that moves the movable sheave of the one pulley in the axial direction by moving 22 in the axial direction.
21 and a first and second member 46, 45 that can rotate relative to each other, and the first member 46 is the movable sheave of the other of the primary and secondary pulleys (for example, the secondary pulley 6).
33 is rotatably and integrally movable in the axial direction, and the first member 46 is axially moved with respect to the second member 45 based on the relative rotation of the first and second members. A second actuator mechanism 50 that moves the movable sheave of the other pulley in the axial direction by moving the second pulley, and a first power transmission device that interlocks the second members 23 and 45 of the two actuator mechanisms. A second power transmission device for interlocking the first members 22, 46 of the two actuator mechanisms with each other; and a planetary gear mechanism 70 interposed between the first and second power transmission devices. The transmission device includes a first shaft 63, first power transmission members 26 and 65 connecting the first shaft 63 and the second member 23 of the first actuator mechanism, and the first shaft 63. And a second member 45 of the second actuator mechanism for connecting the second member The power transmission members 51, 66 of
And the second power transmission member has the same rotation ratio, and the second power transmission device includes a second shaft 57, the second shaft and the first member 22 of the first actuator mechanism. And third power transmission members 19 and 61 for connection, and fourth power transmission members 52 and 62 for connection between the second shaft 57 and the first member 46 of the second actuator mechanism, And the third
And the fourth power transmission member have the same rotation ratio, the planetary gear mechanism 70 has at least first, second and third elements, and the first element S is interlocked with the speed change operation means 75, and Second and third elements R and CR are connected to the first and second shafts 63 and 57, respectively, and the first and second power transmission members having the same rotation ratio and the third and third power transmission members are formed. The rotation ratio with the power transmission member of No. 4 is such that the rotation ratio of the first and second shafts in the state where the first and second members of both actuator mechanisms rotate in the same manner fixes the first element of the planetary mechanism. In the V-belt type continuously variable transmission, the rotation ratios of the second and third elements of the planetary gear mechanism in the above-described state are set to be the same.

(E) Operation Based on the above configuration, the rotation of the primary shaft 2 is transmitted to the primary pulley 5 via the pressure adjusting (cam) mechanism 11, further transmitted to the secondary pulley 6 via the belt B, and then the pressure adjusting (cam). ) It is transmitted to the secondary shaft 3 via the mechanism 43 (the pressure adjusting cam mechanism may be either the primary or the secondary). At this time, the pressure adjusting (cam) mechanism 11,43 applies an axial force Fp, Fs corresponding to the transmission torque to both pulleys 5,6, and these axial forces are applied to both actuator mechanisms (for example, ball screw mechanism) 21,50. And the pulleys 5 and 6 interact with each other via the power transmission device, whereby the belt B is clamped by a proper belt clamping pressure corresponding to the transmission torque, and power is transmitted between the pulleys. Further, at this time, the belt clamping pressure Fs acts on the ball screw mechanism 50 via the thrust bearing 47 and further on the shaft bulging portion 3a via the thrust bearing 53, but the pulley 6 and the shaft 3 and the ball screw mechanism 50 rotate relative to each other. Is 0 (for a gear ratio of 1: 1) or extremely small, and thrust bearing
The rotational load on 47 and 53 is small.

On the other hand, the rotation of the second member (for example, the female screw portion) 23 of the primary side ball screw mechanism 21 is caused by the rotation of the first power transmission device.
Secondary side ball screw mechanism 50 through 26,65,63,66,51
The rotation of the second member (for example, female screw portion) 45 and the rotation of the first member (for example, male screw portion) 22 of the primary side ball screw mechanism 21 in the second power transmission device 19, 61, 57, 62, It is transmitted to the first member (for example, male screw portion) 46 of the secondary side ball screw mechanism 50 via 65, but when the transmission 1 is rotating at a constant speed, the first element of the planetary gear mechanism 70 (for example, The sun gear) S is in a fixed state, the other second and third elements R and CR are maintained at a predetermined rotation ratio, and these elements are set to the predetermined rotation ratio, respectively.
Power transmission members (26 and 65, 66 and 51 and
19 and 61, 62 and 52), the female and male thread portions 23 and 22, 45 and 46 of both the primary and secondary ball screw mechanisms 21 and 50 rotate integrally. From this state, when the shift operation driving means 75 is operated based on each traveling signal to rotate the first element S of the planetary gear mechanism 70, the rotation ratios of the second and third elements R and CR are changed. As a result, the female screw portions and the male screw portions 23, 22, 45, and 46 of the ball screw mechanisms 21 and 50 are relatively rotated to move both movable sheaves 7 and 33, and a gear shift operation is performed.

(F) Example Hereinafter, an example of the present invention will be described with reference to the drawings.

As shown in FIG. 1, the belt type continuously variable transmission 1 according to the present embodiment has a primary shaft that is interlocked with the engine side and a secondary shaft 3 that is interlocked with the wheel side. Has a primary pulley 5
, A secondary pulley 6 is mounted on the secondary shaft 3, and an endless belt B is wound between these pulleys 5, 6. The primary pulley 5 is composed of a movable sheave 7 and a fixed sheave 9 that move relative to each other in the axial direction. The boss portion 9a of the fixed sheave 9 is rotatably and slidably fitted to the shaft 2 and the movable sheave 7 The boss portion 7a is slidably fitted through the ball spline 10 only. A pressure adjusting cam mechanism 11 is interposed between the rear surface of the flange portion 9b of the fixed sheave 9 and the stepped portion 2a of the shaft 2. The pressure adjusting cam mechanism 11 includes a movable race 12, a fixed race 13 and a plurality of taper rollers 15,
The movable race 12 is spline-coupled to the fixed sheave 9, and the disc spring 14 is interposed on the back surface of the flange portion 9b of the movable sheave 9, and the fixed race 13 is rotatable only through a bearing 16 in a case (not shown). It is supported. Further, the opposite end faces of both races 12 and 13 are formed in a corrugated shape, and a taper roller 15 is sandwiched between the end faces, so that the shaft acting on the sheave 9 is acted on by the transmission torque between the races 12 and 13. Generate force Fp.

Further, a gear 19 having a stepped boss portion 19a is retained by a nut 17 at a tip portion of the shaft 2 and fixed and supported, and a bearing 20 supports the boss portion 19a and the shaft tip portion. A ball screw mechanism 21 which constitutes an actuator mechanism is interposed between the gear 19 and the rear surface of the flange portion 7b of the sheave 7. The ball screw mechanism 21 has a male screw portion 22, a female screw portion 23 and a large number of balls 25. The male screw portion 22 is a boss portion of the movable sheave 7.
The female screw portion 23 is integrally formed with the 7a, and also has a gear 26 having a larger diameter than the gear 19 integrally. A thrust bearing 31 is interposed between the gears 19 and 26, and the gear 19 and the female screw portion 23 are combined with the bearing 20 on the basis of the force of the belt B which acts on the movable sheave 7 in the expanding direction. The gear 26 integral with is prevented from moving in the axial direction and is rotatably supported.

On the other hand, the secondary pulley 6 is also composed of two sheaves 33 and 35, the boss portion 33a of the movable sheave 33 is fitted to the shaft 3 so as to be rotatable and slidable, and the boss portion 35a of the fixed sheave 35 is connected to the ball spline. It is slidably fitted through 36. Then, like the primary pulley 5, on the rear surface of the flange portion 35b of the fixed sheave 35, a fixed race 39 fixed to the tip of the shaft 3 with a nut 38, a movable race 40 splined to the fixed sheave 35, and A pressure adjusting cam mechanism 43 including a taper roller 41 and a disc spring 42 is interposed between the wavy end surfaces of both rails. A ball screw mechanism 50 including a female screw portion 45, a male screw portion 46, and a ball 48 is interposed between the rear surface of the flange portion 33b of the movable sheave 33 and the stepped bulging portion 3a of the shaft 3. Furthermore,
The female screw portion 45 integrally has a gear 51 having the same number of teeth as the gear 26 of the primary side male screw portion 23, and one end of the male screw portion 46 of the movable sheave 33 has a thrust bearing 47 interposed therebetween. It is in contact with the back surface and is slidably connected to the boss portion 52a of the gear 52 at its inner diameter portion via a ball spline 54. Further, the gear 52 has the same number of teeth as the gear 19 that rotates integrally with the primary side male screw portion 25, is rotatably supported by the shaft 3 through a needle in its inner diameter hole, and has a bulging portion. The thrust bearing 53 is interposed between the gear 52 and the male screw portion 45a, and the thrust bearing 55 is interposed between the thrust bearing 53 and the male screw portion 46. Therefore, the gear 52 and the male screw portion 45 are caused by the axial force Fs from the pressure adjusting cam mechanism 43. Gear with
51 is positioned at a predetermined position in the axial direction.

Further, counter shafts 57, 63 consisting of double shafts are arranged between the primary and secondary shafts 2, 3, and a planetary gear mechanism 70 is coaxially arranged at one end portion thereof. Further, the primary gear mechanism 70
The ring gear R is an outer shaft of the double counter shaft.
A gear 65 is formed integrally with 63, and a gear 65 that meshes with the primary-side female screw gear 26 is formed on the outer peripheral portion thereof. The carrier CR that rotatably supports the planetary pinion P is integrally connected to the inner shaft 57 of the double counter shaft, and is also connected to the gear 61 that meshes with the primary gear 19. Further, a worm wheel 76 is fixed to a gear shaft 73 extending from the sun gear S, and the wheel 76 is rotatably supported by a bearing 59 and meshes with a worm gear 75. Is driven by a motor controlled by traveling signals such as vehicle speed and throttle opening, and constitutes a gear shift operation means. On the other hand, at the other end portion of the counter shaft, a gear 62 is fixed to the inner shaft 57 and an outer shaft 63 and a gear 66 are fixedly arranged, and the gear 62 is connected to the secondary side male screw part interlocking gear 52. ,
Further, the gears 66 mesh with the female screw integrated gear 51, respectively. Then, gears 65, 66 that rotate integrally with the outer shaft 63,
Further, the gears 61 and 62 that rotate integrally with the inner shaft 57 have the same number of teeth, so that the female screw portions 23 and 45 and the male screw portions 22 and 46 in both the primary and secondary ball screw mechanisms 21 and 50 are The counter shaft always rotates at the same speed, and the inner shaft 57 and outer shaft 63 of the counter shaft are geared.
They are rotating at different speeds based on the difference in the number of teeth of 61,65 and 62,66. Furthermore, the number of teeth of each element R, CR, S of the planetary gear mechanism 70 is such that the ring gear R and the carrier CR are the outer shaft 63 and the inner shaft 63 of the counter shaft with the sun gear S fixed.
The predetermined rotation ratio is set so as to match the rotation of 57. That is, the gears 65, 26 and 6 that connect the female screw portions 23 and 45 to each other.
6,51 and the outer shaft 63 constitute the first power transmission device,
Further, the gears 61, 19 and 62, 52 connecting the male screw portions 22, 46 together constitute a second power transmission device, and the gears 61, 65 and 6 are provided.
The rotation ratios of the first and second power transmission devices, which are determined based on the difference in the number of teeth of 2,66, are the male screw portions 22, 46 and the second member which are the first members of both actuator mechanisms. The other two of the planetary gear mechanism 70 in the state where the rotation ratio of the inner shaft 57 and the outer shaft 63 of the counter shaft in the state where the female screw portions 23 and 46 rotate in the same manner fixes the sun gear S which is a predetermined element of the planetary gear mechanism 70. It is set to be the same as the rotation ratio of the ring gear R and the carrier CR, which are elements. In the figure, 60 is a bearing that supports the other end of the counter shaft, and 64 is a bearing that supports the gear 61.

Since the present embodiment is configured as described above, the rotation of the primary shaft 2 based on the engine output is transmitted to the fixed race 13 of the pressure adjusting cam mechanism 11, and further, via the taper roller 15 and the movable race 12, the primary pulley. 5 sheaves 9
Be transmitted to. At this time, the fixed race 13 of the pressure adjusting cam mechanism 11
Based on the relative rotation between the movable race 12 and the movable race 12, an axial force Fp corresponding to the input torque acting on the shaft 2 acts on the back surface of the sheave 9 via the disc spring 14. Also, Ball Spline 10
The torque of the pulley 5 that rotates integrally via the secondary shaft 6 is transmitted to the secondary pulley 6 via the belt B, and is transmitted to the secondary shaft 3 to the dish via the pressure adjusting cam mechanism 43. At this time, based on the pressure adjusting cam mechanism 43, the secondary shaft 3
The axial force Fs corresponding to the output torque transmitted to the sheave 35 acts on the sheave 35 via the disc spring 42. However, in the torque transmission state described above, the axial force Fp, Fs generated by the pressure adjusting cam mechanism 11, 43 compresses the disc springs 14, 42 to a predetermined height, and the movable races 12, 40 directly move to the sheave flange portions 9b, 35b. Adheres to and acts on the back of the.

On the other hand, the rotation of the primary shaft 2 is transmitted as the same-speed rotation to the male screw portion 22 of the ball screw mechanism via the pressure adjusting cam 11 and the pulley 5, and the gears 19 and 61 and the planetary gear mechanism 7 are also transmitted.
0 carrier CR, counter shaft inner shaft 57, gear 62,
The same speed rotation is transmitted to the male screw portion 46 of the second-side ball screw mechanism 50 via 52 and the ball spline 54.
At the same time, the rotation of the female screw 23 on the primary side is prevented by rotating the gears 26, 6
5, the ring gear R of the planetary gear mechanism 70, the outer shaft 63 of the counter shaft, and the gears 66 and 51 are transmitted to the secondary side female screw portion 45 as the same speed rotation. Therefore, when the gear ratio is not changed, that is, when the female screw portion and the male screw portion of the ball screw mechanism do not rotate relative to each other and do not move in the axial direction, the female screw portion and the male screw portion of both ball screw mechanisms are the same as those of the primary shaft 2. Rotate at speed. Further, the axial force Fp based on the pressure adjusting cam mechanism 11 on the primary side is the belt B,
A torque acting in one direction, for example, a counterclockwise direction when viewed from the right side in the drawing, is applied to the male screw portion 23 via the movable sheave 7 and the male screw portion 22, while the axial force Fs based on the pressure adjusting cam mechanism 43 on the secondary side is Through the belt B, the movable sheave 33, the thrust bearing 47, and the male screw portion 46, a torque in another direction, for example, a clockwise direction, acts on the female screw portion 45. Therefore, the axial forces Fp and Fs generated by the two pressure adjusting cam mechanisms 11 and 43 are controlled by the two ball screw mechanisms 21 and 50 that are interlocked with each other via the power transmission device.
Interact with each other.

As a result, both pulleys 5 and 6 have
A proper belt clamping pressure corresponding to the transmission torque is applied, and power is transmitted in a state in which excessive belt clamping pressure does not act on the belt B and belt slip does not occur. Further, at this time, the belt clamping pressure Fs acts on the ball screw mechanism 50 via the thrust bearing 47, and is further received by the bulging portion 3a of the shaft 3 via the thrust bearing 53. By the way, as described above, since the secondary side ball screw mechanism 50 rotates at the same speed as the primary shaft 2, when the gear ratio is 1: 1, the primary pulley 6
Also, the shaft 3 and the ball screw mechanism 50 rotate at the same speed, the thrust bearings 47 and 53 do not rotate,
It only receives a static load and has a gear ratio of 1: 1.
Even if it is not, the relative rotation between the primary pulley 6 and the shaft 3 and the ball screw mechanism 50 is small compared to the relative rotation with the stationary fixing member, and the thrust bearings 47 and 53 have the axial force at a small rotation speed. It is enough to maintain.

When the V-belt type continuously variable transmission 1 is in the constant speed state, the sun gear S of the planetary mechanism 70 is maintained in a fixed state by the meshing of the worm gear 75 and the worm wheel 76, so that the ring gear R and the carrier CR are set to a predetermined value. Rotating at the rotation ratio, the outer shaft 63 and inner shaft of the counter shaft
57 is held at a rotation difference based on the gears 61, 65 and 66, 62, and the ball screw mechanisms 21, 50 have their female screw portions and male screw portions integrally rotated. From this state, the V-belt type continuously variable transmission 1
In order to shift the gear, the motor is driven based on each traveling signal to rotate the worm gear 75. Then, when the sun gear S of the planetary gear mechanism 70 rotates in either the left or right direction, for example, the same direction as the rotation direction of the other elements R, CR, the rotation ratio between the ring gear R and the carrier CR changes to a smaller direction, and the change occurs. Is transmitted to the primary side ball screw mechanism 21 via the gears 61, 19 and 65, 21 and is transmitted to the secondary side ball screw mechanism 50 via the counter shafts 57, 63 and gears 62, 52 and 66, 51. The female screw portion and the male screw portion of both ball screw mechanisms 21 and 50 are relatively rotated. As a result, the movable sheaves 7, 33 of the primary and secondary pulleys 5, 6 are both moved to the right, and the belt B is moved in the upshift direction. In addition, worm gear 75 other elements
When rotating in the opposite direction of R and CR, the ring gear R
The rotation ratio between the carrier CR and the carrier CR increases, and the change is transmitted as relative rotation between the female screw portion and the male screw portion of the ball screw mechanisms 21 and 50 in the same manner as described above. Both are moved to the left and thus belt B is moved in the downshift direction. At this time, the driving force of the motor that rotates the worm gear 75, which is the gear shifting operation means, is
Only a very small force, which is the difference between the belt clamping pressures of the two pulleys 5 and 6, is sufficient and can be controlled quickly and accurately according to each running signal, and the belt B is durable without giving excessive clamping pressure. There is no loss in communication and transmission efficiency.

In the above description, the positive torque is transmitted when the torque is transmitted from the engine to the wheel direction, but the secondary side is the input side even when the negative torque is transmitted when the torque is transmitted from the wheel to the engine direction during engine braking. In addition, the primary side becomes the output side, and power can be similarly transmitted by the axial force corresponding to the transmission torque. When the positive torque is transferred to the negative torque or vice versa, since the rotating direction is different, the pressure adjusting cam mechanisms 11 and 43 momentarily play due to the reverse rotation, but due to the existence of the disc springs 14 and 42. , The belt pressure can be maintained at all times.

In the above embodiment, the pressure adjusting cam mechanisms 11 and 43 are arranged on the primary side and the secondary side, respectively, but they may be arranged on only one of them.

Further, although the gears are used to interlock the ball screw mechanisms 21 and 50, each screw mechanism and the counter shaft may be connected by a chain. As a result, each gear (sprocket) can have a small diameter and can be made compact.

Furthermore, although the ball screw mechanism is used as the actuator mechanism, it is also possible to use a cam mechanism that converts rotational movement into axial movement.

(G) Effect of the Invention As described above, according to the present invention, the pressure adjusting mechanism 11, 43
Generates axial forces Fp and Fs corresponding to the transmission torque, and these axial forces act on both pulleys via both actuator mechanisms 21 and 50 and the power transmission device, so a complicated link mechanism is also required. However, even though it has an extremely simple structure, it is possible to apply the optimum belt clamping pressure according to the gear ratio and the transmission torque, improve the belt durability and the transmission efficiency, and further, it is possible to avoid excessive movement during gear shifting. The belt pressure does not act, and the belt durability and transmission efficiency are not impaired. In particular, even when the vehicle starts with a high ratio of belt pulling pressure, it is possible to maintain an appropriate belt pulling pressure, prevent belt slip and excessive belt pulling pressure, and perform a smooth start. Further, since the actuator mechanism 50 also rotates in accordance with the rotation of the pulleys 5 and 6, the relative rotation between the pulley 6 and the shaft 3 and the actuator mechanism such as the ball screw mechanism 50 can be greatly reduced, and the thrust force that receives the axial force can be reduced. The rotational load of the bearings 47, 53 can be reduced and the life can be significantly improved. Further, even if a trouble such as a failure of the gear shift operation drive means occurs, the belt clamping pressure can be maintained and the transmission can be continued.

In addition, the planetary gear mechanism 70 is interposed in the two-system power transmission device, and the first element S of the planetary gear mechanism is provided.
By rotating the two actuator mechanisms 21,50
Since the first member and the second member in the above are configured to rotate relative to each other, a large axial force related to the gear shifting operation does not act on the case, so that the case can be made lightweight and the normal gear shifting Since the operation means 75 is stopped, there is no need for a roller or the like for receiving rotation, no complicated oil passages and piping are required, and the structure can be simplified and durability can be improved. Further, the first element S of the planetary gear mechanism 70 can be operated through a predetermined speed reducing means such as the worm gear 75, and a fine gear shift operation can be performed by a motor or the like, and the first element S can be mechanically fixed. The gear ratio can be reliably and easily held at a predetermined position.

Further, when the first element S of the planetary gear mechanism 70 is operated via the worm gear, it is possible to obtain a large reduction gear ratio very easily, and it is possible to easily and surely hold it at the predetermined gear shift position.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention. 1 ... V-belt type continuously variable transmission, 2 ... Primary shaft, 3 ... Secondary shaft, 5 ... Primary pulley, 6 ... Secondary pulley, 7,33 ... Movable sheave, 9,
35 …… Fixed sheave, 11,43 …… Pressure adjusting (cam) mechanism, 21,50
...... Actuator (ball screw) mechanism, 12,40 …… Movable race, 13,39 …… Fixed race, 15,41 …… Rolling body (taper roller), 14,42 …… Biasing means (disc spring), 23,45
...... Second member (female screw part), 22,46 ...... First member (male screw part), 19,61,62,52,57 ...... Second power transmission device (third and fourth) Power transmission member, second shaft), 26,65,5
1,66,63 ... First power transmission device (first and second power transmission members, first shaft), 57,63 ... counter shaft, 4
7,53 ...... Thrust bearing, 70 ...... Planetary gear mechanism, S ...... Predetermined element (sun gear), R, CR ...... Other two elements (ring gear, carrier), 75 ...... Gear change operation drive means (worm gear), B ……belt.

Claims (3)

[Claims] 1. A primary and secondary pulley comprising two sheaves, each of which is capable of relative movement in the axial direction,
In a V-belt type continuously variable transmission in which a belt is wound around both of these pulleys, a pressure adjusting mechanism that directly applies an axial force corresponding to the transmitted torque to at least one of the pulleys, and a first and a second device that can rotate relative to each other. A second member, wherein the first member is integrally provided on one of the movable sheaves of the primary and secondary pulleys, and the first and second
A first actuator mechanism for moving the movable sheave of the one pulley in the axial direction by moving the first member in the axial direction with respect to the second member based on the relative rotation of the member in FIG. A first and a second member that can be moved, the first member being provided so as to be rotatable and axially move integrally with the movable sheave of the other one of the primary and secondary pulleys, A second actuator that axially moves the movable sheave of the other pulley with respect to the second member based on relative rotation of the first and second members to axially move the first member with respect to the second member. A mechanism, a first power transmission device that interlocks second members of both actuator mechanisms, a second power transmission device that interlocks first members of both actuator mechanisms, and the first and second power transmission devices. And a planetary gear mechanism interposed between the second power transmission device and the second power transmission device, wherein the first power transmission device includes a first shaft, the first shaft, and a second member of the first actuator mechanism. A first power transmission member that connects the first shaft and a second power transmission member that connects the first shaft and a second member of the second actuator mechanism, and the first and second power transmission members. The second power transmission device has a second shaft and a third shaft connecting the second shaft and the first member of the first actuator mechanism. A power transmission member, and a fourth power transmission member that connects the second shaft to the first member of the second actuator mechanism, and the third and fourth power transmission members are the same. The planetary gear mechanism comprises at least the first, second and third rotation ratios. The first and second elements are coupled to the first and second shafts, respectively, and have the same rotation ratio. The rotation ratio between the second power transmission member and the third and fourth power transmission members is the rotation of the first and second shafts in a state where the first and second members of the two actuator mechanisms rotate in the same direction. A V-belt continuously variable gear, characterized in that the ratio is set to be the same as the rotation ratio of the second and third elements of the planetary gear mechanism in the state where the first element of the planetary mechanism is fixed. transmission. 2. The V-belt type continuously variable transmission according to claim 1, wherein a predetermined element of the planetary gear mechanism is operated via a worm gear. 3. The first and second shafts are counter shafts composed of double shafts, and the planetary gear mechanism connects a ring gear, which is the second element, to an outer shaft of the counter shafts, 2. The V-belt type according to claim 1, wherein the carrier, which is the third element, is connected to the inner shaft of the counter shaft, and the sun gear, which is the first element, is interlocked with the gear shift operation means. Continuously variable transmission.