JPH0743014B2 - V-belt type continuously variable transmission - Google Patents

Description

The present invention relates to a V-belt type continuously variable transmission, and more particularly to a V-belt type continuously variable transmission that is suitable for being mounted on an automobile. The present invention relates to the structure of a shift operation actuator mechanism of a multi-speed transmission.

(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, the applicant has arranged a pressure adjusting cam mechanism that applies an axial force corresponding to the transmission torque to at least one of the primary pulley and the secondary pulley, and a screw mechanism that moves the movable sheaves of both pulleys in the axial direction. There has been proposed a V-belt type continuously variable transmission that is installed and moves the movable sheaves of both pulleys by shifting the primary and secondary side screw mechanisms by the same amount.
(See Japanese Patent Application Laid-Open No. 62-13853; not yet published at the time of application) (C) Problems to be Solved by the Invention By the way, the above-mentioned continuously variable transmission has a simple structure, but has an axial force corresponding to the transmission torque. It is excellent in that it does not apply more belt pressure than necessary, but the movable sheaves of both pulleys move the same amount during a gear shift operation, so the movable sheave has the same amount of movement as the movable sheave originally defined by the belt. It makes a difference. More specifically, when the rotation ratio is 1: 1, the pitch circle radii in both pulleys are the same, so if this is r ₀ and the axial distance is, then the belt length L ₀ at this time is L ₀ = 2 + 2πr ₀ , but if the sheave spacing in one pulley is widened and narrowed in the other, the pitch radius becomes r ₀ + a on the one hand and r ₀ −a on the other hand, and the required V-belt length at this time L is L = 2 + π (r ₀ + a + r ₀ −a) + (r ₀ + a−r ₀ + a) ² / = 2 + 2πr ₀ + (4a ² /). Therefore, compared with the case where the rotation ratio is 1: 1. Therefore, it needs to be 4a ² / long. However, since the length of the belt is constant, if the movable sheave moves linearly as described above, it will deviate from the original amount of movement of the pulley in contact with the belt. That is, as shown in FIG. 9, the stroke A of the primary side movable sheave defined by the belt and the stroke B of the secondary side movable sheave differ at each torque ratio position, and the difference amount d is the torque. It becomes the maximum at ratio 1 and gradually decreases toward the acceleration position O / D and the deceleration position U / D, but the movable sheave in both pulleys of the above-mentioned continuously variable transmission moves by the same amount, so the original movable sheave movement There is a difference with the position.

For this reason, in the above-mentioned continuously variable transmission, the above difference is absorbed by the stroke of the pressure adjusting cam mechanism. However, this type of continuously variable transmission for vehicle uses not only the transmission of the positive torque from the engine but also the engine brake. When negative torque is transmitted,
The pressure adjustment cam mechanism makes a large stroke when switching between positive and negative torque transmission. That is, for example, when positive torque is transmitted, the pressure adjustment cam mechanism is in a state where the fixed race and the movable race are relatively rotated to absorb the difference as described above, but the torque transmission is switched in this state. Then, the fixed race and the movable race relatively rotate in opposite directions, and the pressure adjusting cam mechanism makes a large stroke. As a result, torque fluctuations may occur due to abrupt changes in relative rotation in the pressure adjusting cam mechanism, which may reduce the durability and performance of the pressure adjusting cam mechanism.

Therefore, the present invention reduces the stroke of the pressure adjusting cam mechanism by configuring the actuator mechanism that moves the movable sheave in the axial direction so that the movable sheave matches the original movement amount of the movable sheave, thereby improving reliability and performance. The purpose is to improve.

(D) Means for solving problems.

The present invention has been made in view of the above circumstances, and for example, as shown in FIG. 1, a pressure adjusting cam mechanism or the like that applies axial forces Fp, Fs corresponding to the transmission torque to at least one of the pulleys 5 and 6. Pressure regulating mechanism 11, 43 and two members 22, which can rotate relative to each other,
23, which comprises a primary-side actuator mechanism 21 for axially moving the movable sheave 7 of the primary pulley 5 based on the relative rotation of these members, and two relatively rotatable members 44, 45. A secondary side actuator mechanism 50 that moves the movable sheave 33 of the secondary pulley 6 in the axial direction based on the rotation. Further, both the primary and secondary actuator mechanisms 21 and 50 are connected to the power transmission device 6
These two actuator mechanisms are rotated by interlocking with the shift operation drive means (67) via 1,62,63,65,66. Then, at least one of these actuator mechanisms, for example, the secondary side actuator mechanism 50 is configured by the unequal stroke cam mechanisms 44, 45, 46 in which the axial movement amount changes non-linearly with respect to the rotation angle. Movable sheave 7,33
Is different from each other and is matched with the original moving amount of the movable sheave defined by the belt B.

(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 to the secondary pressure adjusting mechanism 43. Is transmitted to the secondary shaft 3 (the pressure adjusting mechanism may be either the primary or the secondary). At this time, the pressure adjusting mechanisms 11 and 43 apply axial forces Fp and Fs corresponding to the transmission torque to the pulleys 5 and 6 to hold the belt B. In addition, the power transmission device is driven by driving the shift operation drive means such as a motor controlled based on the traveling signal.
When both actuator mechanisms 21 and 50 rotate via 61, 27, 62, 26, 63, 49, 65 and 48, a screw mechanism (or an equal stroke cam mechanism that moves linearly in the axial direction with respect to the rotation angle) The secondary side actuator mechanism 50 composed of the unequal stroke cam mechanisms 44, 45, 46 moves in an unequal stroke with respect to the uniform stroke movement of the primary side actuator mechanism 21 composed of. absorbs d.
As a result, the movable sheaves 7, 33 are adjusted to the original moving position of the movable sheave defined by the belt B, and the belt effective diameter is set to a predetermined gear ratio.

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

(He-1) First Embodiment A belt type continuously variable transmission 1 according to the first embodiment is, as shown in FIG. 1, interlocked with a primary shaft 2 which is interlocked with an engine side and a wheel side. Secondary shaft 3
The primary shaft 2 is fitted with the primary pulley 5, the secondary shaft 3 is fitted with the secondary pulley 6, and
The endless belt B is wound between 5 and 6. And
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.
Is rotatably and slidably fitted on the shaft 2, and the boss portion 9a of the fixed sheave 9 is slidably fitted via the ball spline 10. 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 bulging portion 2a of the shaft 2. The pressure adjusting cam mechanism 11
Is a movable race 12, a fixed race 13 and many taper rollers 15
The movable race 12 is spline-coupled to the fixed sheave 9, and is pressed against the back surface of the flange portion 9b via a disc spring 14, and the fixed race 13 is fixed to the bulging portion 2a. Bearing 16 in case (not shown)
It is rotatably supported via. Furthermore, both races 1
The opposing end faces of 2, 13 are corrugated in a wavy shape, and a taper roller 15 is sandwiched between the end faces, so that both races 12, 13
An axial force Fp that acts on the sheave 9 is generated based on the transmission torque between them.

A stepped collar 19 is retained and fixed by a nut 17 at the tip of the shaft 2, and is supported by the collar.
Therefore, the tip of the shaft is supported by the bearing 20. A ball screw mechanism 21 that constitutes an actuator mechanism having an equal stroke is interposed between the collar 19 and the back surface of the flange portion 7b of the movable sheave 7. The ball screw mechanism 21 has a female screw portion 22, a male screw portion 23, and a large number of balls 25, and also has two gears 26 and 27 having different numbers of teeth.
have. The one gear 26 having a large number of teeth is integrally fixed to the female screw portion 22, and the boss portion 27a of the other gear 27 having a small number of teeth is fitted and inserted into the shaft 2 via a needle. The outer periphery thereof is slidably connected to the male screw portion 23 via a ball spline 29. Further, one end surface of the male screw portion 23 is in contact with the rear surface of the flange portion 7b via the thrust bearing 30, and the other gear 27
The end side surface of the gear is in contact with the end side surface of the collar 19 via the thrust bearing 31, and the thrust bearing 32 is interposed between the facing side surfaces of the gears 26 and 27.

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, between the back surface of the flange portion 35b of the fixed sheave 35 and the fixed race 39 fixed to the tip of the shaft 3 with the nut 38, the movable race 40, the tapered roller 41, and the disc spring 42 The pressure regulating cam mechanism 43 is interposed. Similarly, between the rear surface of the flange portion 33b of the movable sheave 33 and the stepped bulge portion 3a of the shaft 3, an unequal stroke cam mechanism 50 constituting an actuator having unequal strokes is interposed. As shown in detail in FIG. 2, the unequal stroke cam mechanism 50 comprises a movable side end surface cam 44, a supporting side end surface cam 45, and a plurality of rollers 46 sandwiched between these cams. The rollers 46 are held in a predetermined phase by a holding ring 47, and the movable side end cams 44 have unequal strokes based on the relative rotation of the both end face cams 44, 45. More specifically, as shown in FIG. The opposing surface of the front end surface cam is a curved surface, and the primary side actuator mechanism 21 moves with an unequal stroke composed of a curve E that absorbs the difference amount d (FIG. 9) with respect to an equal stroke composed of a straight line D. To do. Further, a large-diameter gear 48 is formed integrally with the support-side end surface cam 45, and a boss portion of a small-diameter gear 49 rotatably supported by the shaft 3 is provided inside the boss portion of the movable-side end surface cam 44. It is connected via a ball spline 29. In addition, 51 and 52 are shafts 3
Bearings, 53,55,56 are axial forces from sheave 33
It is a thrust bearing that receives Fs.

A counter shaft 57 is arranged between the primary and secondary shafts 2 and 3, and both ends thereof are rotatably supported by bearings 59 and 60. Further, a large-diameter gear 61 and a small-diameter gear 62 are spline-coupled to one end of the shaft 57.
Reference numerals 1 and 62 respectively mesh with a small diameter gear 27 and a large diameter gear 26 of the primary side actuator mechanism (ball screw mechanism) 21. A large-diameter gear 63 and a small-diameter gear 65 are also spline-coupled to the other part of the shaft 57.
63 and 65 are the small diameter gear 49 and the large diameter gear 48 of the secondary side actuator mechanism (unequal stroke cam mechanism) 50, respectively.
Meshes with. Further, a worm wheel 66 is spline-coupled to the shaft 57, and a worm 67 which is interlocked with a gear shifting operation means such as a motor is meshed with the wheel 66.

Since the present embodiment is configured as described above, the rotation of the primary shaft 2 based on the engine output is transmitted from the expanded diameter portion 2a to the fixed race 13 of the pressure adjusting cam mechanism 11, and further the tapered roller 15 and the movable race. It is transmitted to the sheave 9 of the primary pulley 5 via 12. At this time, the pressure adjustment cam mechanism
Transmission torque between the fixed race 13 and the movable race 12 of 11,
That is, 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, while the other sheave 7 has a ball screw mechanism 21 having a length corresponding to a predetermined gear ratio. Therefore, the same reaction force Fp acts on the back surface of the sheave 7 via the thrust bearing 30. As a result, the primary pulley 5 moves the belt B with the holding force Fp corresponding to the input torque. Hold in.
Then, the torque of the pulley 5 that rotates integrally via the ball spline 10 is transferred to the secondary pulley 6 via the belt B.
Is transmitted to the secondary shaft 3 via the pressure adjusting cam mechanism 43. At this time, based on the pressure adjusting cam mechanism 43, the axial force Fs corresponding to the output torque transmitted to the secondary shaft 3 acts on the sheave 35 via the disc spring 42, while being fixed also on the back surface of the other sheave 33. The reaction force Fs acts from the unequal stroke cam mechanism 50 in FIG. 2 and the secondary pulley 6 also holds the belt B with the holding force Fs corresponding to the output torque. However, in the torque transmission state described above, the disc springs 14 and 42 are respectively moved to the movable race 12 and the sheave 9, and the movable race 40 and the sheave 35 by the axial forces Fp and Fs generated by the pressure adjusting cam mechanisms 11 and 43, respectively. It is in close contact.

Then, in order to perform the gear shift operation of the V-belt type continuously variable transmission 1, the rotation of the motor linked with the worm 67 is controlled based on the traveling signals such as the vehicle speed, the throttle opening, and the engine speed. For example, when the worm 67 is rotated in the clockwise direction, that is, the upshift direction, the worm wheel 66 is rotated in the clockwise direction when viewed from the right side of the drawing (the same applies hereinafter), and the gears 61, 62, 63, 65 via the counter shaft 57. Also rotates in the same direction. Then, the gears 26, 2 of the primary side ball screw mechanism 21.
Although 7 rotates counterclockwise, the number of rotations of the small diameter gear 27 is higher than that of the large diameter gear 26 based on the difference in the number of teeth. As a result, the male screw portion 23 that rotates integrally with the gear 27 via the ball spline 29 becomes larger than the rotation of the female screw portion 22 that rotates integrally with the gear 26, and the ball screw consisting of the right screw moves to the right. It is extended with an equal stroke, and the movable sheave is moved via the strut bearing 30 so that the distance between the movable sheave and the fixed sheave 9 becomes smaller, so that the effective diameter of the belt B becomes larger. Similarly, the rotation of the counter shaft 57 is transmitted to the gears 49 and 48 of the secondary side unequal stroke cam mechanism 50 via the gears 63 and 65, and is integrated with the gear 49 based on the counterclockwise relative rotation of these gears. The movable side end cam 44 that rotates to the right and the support side end cam 45 that rotates integrally with the gear 48 are prevented from moving in the axial direction through the thrust bearings 56 and 55, so that the strokes are uneven in the right direction. And the movable sheave 33 is moved so that the distance between the movable sheave 33 and the fixed sheave 35 is increased. As a result, the primary side movable sheave having an equal stroke and the secondary side movable sheave 33 having an unequal stroke are combined to absorb the difference amount d (FIG. 9) in the predetermined gear ratio, and the difference is defined by the belt B. Both movable sheaves 7, 33 are moved and adjusted to their original movable sheave movement positions.

When the worm 67 is rotated counterclockwise, that is, in the downshift direction, the worm 67 rotates in the opposite direction to that in the upshift, and the primary side ball screw mechanism 21 contracts to the left with an equal stroke and the unequal stroke on the secondary side. The cam mechanism 50 extends to the left with unequal strokes,
The movable sheaves 7, 33 of 5, 6 are adjusted to the movement position defined by the belt B, and change the belt B in the deceleration direction.

In the above description, the positive torque transmission in which torque is transmitted from the engine to the wheel direction is described.
The belt type continuously variable transmission 1 also generates a negative torque transmission state in which torque is transmitted from the wheels to the engine during engine braking. When the positive torque transmission is switched to the negative torque transmission or vice versa, the pressure adjustment cam mechanisms 11 and 43 are rotated in the opposite direction, but the movable sheaves 7 and 33 of the pulleys 5 and 6 are moved. Is in the original position defined by the belt B, and therefore, the pressure adjusting cam mechanisms 11 and 43 have taper rollers 15 and 41 located in the vicinity of the valley position, and the moving stroke thereof is extremely short. In addition, even the extremely slight stroke can cause disc springs 14,4
It is absorbed by the existence of 2 and maintains the belt clamping pressure even when switching between positive and negative torque transmission. Also, during negative torque transmission, the secondary side becomes the input side and the primary side becomes the output side, and as in the case of positive torque transmission, the belt is crushed by the axial force corresponding to the transmitted torque, and power is transmitted. .

(He-2) Second Embodiment Next, a second embodiment of the present invention will be described with reference to FIGS. 4 and 5. The same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

In the V-belt type continuously variable transmission 1'of this embodiment, as shown in FIG. 4, the primary side actuator mechanism 21 'is composed of an equal stroke cam mechanism, and the secondary side actuator mechanism 50' is composed of an unequal stroke cam mechanism. Consists of. The unequal stroke cam mechanism 50 ', as shown in detail in FIG.
An end cam 70 having a saw-toothed cam surface 70a having a predetermined curved surface on one end surface and a roller 71 abutting on the cam surface 70a are provided, and the other side surface of the cam 70 has a movable sheave 33 via a thrust bearing 53. The guide part 70
b is integrally formed, and the guide portion 70b is guided by the case 73 via the ball spline 72 while being prevented from rotating. Further, each roller 71 is rotatably supported by a pin 75, and is mounted on the gear 48 via an arm 76. On the other hand, the equal-stroke cam mechanism 21 'is also the same as the above-described unequal-stroke cam mechanism 50', except that the cam surface of the end face cam has a shape with an equal stroke. That is,
The cam mechanism 21 'is provided with an end surface cam 77 having a saw-teeth-shaped cam surface 77a and a roller 79 that abuts on the cam surface. The cam 77 has its other side surface facing the movable sheave 7 via a thrust bearing 30. While being in contact with each other, the guide portion 77b is guided by the case 73 via the ball spline 80 to prevent rotation. The roller 79 is rotatably supported by a pin 83 at the tip of an arm 82 extending from the gear 26. The primary-side gear 26 and the secondary-side gear 48 have the same number of teeth and mesh with the gears 62 and 65 fixed to the counter shaft 57. In this embodiment, the ball splines 10,36 connecting the movable sheaves 7,33 and the fixed sheaves 9,35 are connected to the actuator 2
It is located on the inner diameter side of 1 ', 50'.

Since this embodiment has the above configuration, the worm 67
The rotation of the counter shaft 57 based on
The primary and secondary gears 26, 48 rotate via the. Then, the rollers 79 and 71 rotate integrally with the gears 26 and 48 around the shafts 2 and 3, and the rollers 79 and 71 rotate relative to the end face cams 77 and 70 which are prevented from rotating by the ball splines 80 and 72. Occurs. As a result, both stroke cam mechanisms 21 ′, 5
Although the 0 ′ end surface cams 77, 70 both move in the axial direction, the primary side cam mechanism 21 ′ consisting of the equal stroke cam surface 77a moves in equal strokes, while the secondary side consisting of the unequal stroke cam surface 70a The cam mechanism 50 'moves with unequal strokes, both movable sheaves are adjusted in accordance with the original movement of the movable sheaves 7 and 33 defined by the belt B, and a predetermined gear ratio is set.

(H-3) Third Embodiment Next, a third embodiment of the present invention will be described with reference to FIGS. 6 and 7. Also in this embodiment, the same parts as those in the previous embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the V-belt type continuously variable transmission 1 ″ of this embodiment, as shown in FIG. 6, the primary side actuator mechanism 21 ″ is an unequal stroke cam mechanism, and the secondary side actuator mechanism 50 ″ is an equal stroke cam mechanism. The unequal stroke cam mechanism 21 ″, as shown in detail in FIG.
An end cam 77 'having a curved cam surface 77'a and a roller 79 abutting against the cam surface 77'a are provided, and the end cam 77' has a movable sheave with the other end surface via a thrust bearing 30. 7 and is engaged with the case 73 via the ball spline 80. Also, the roller 79
Is installed on an arm 82 fixed to the gear 26, and an axial force supporting race 90 is arranged on the opposite side of the cam surface 77'a of the roller 79. A thrust bearing 91 is interposed between them. On the other hand, the uniform stroke cam mechanism 50 ″ also has a cam surface 70 ′ with a shape that provides uniform strokes.
An end surface cam 70 'having a is in contact with the movable sheave 33 via a thrust bearing 53 and is engaged with a case 73 via a ball spline 72. Also, the roller 71
Is mounted on the gear 48 via the arm 76, and the roller 71 is provided on the side opposite to the cam surface 70'a for supporting the axial force 93
And a thrust bearing 95 is interposed between the race 93 and the gear 48.

Since the present embodiment is configured as described above, when the rollers 79 and 71 of both actuators 21 ″ and 50 ″ rotate based on the rotation of the counter shaft 57, both end surface cams 77 ′ and 70 ′ move in the axial direction. . At this time, as shown in FIG. 8, the primary-side end surface cam 77 'composed of an unequal stroke cam surface moves in an unequal stroke indicated by a predetermined curve F, and the secondary side end surface cam 71 composed of an equal-stroke cam surface. ′ Moves in equal strokes indicated by a straight line G. As a result, the movable pulleys 7 and 33 are moved in conformity with the original movement of the movable sheave defined by the belt B, and the predetermined gear ratio is set. Further, the axial force from the movable sheaves 7,33 is transmitted through the thrust bearings 30,53 and the end surface cams 77 ', 70' to the rollers 79,71.
The rollers 79, 71 are connected to the shafts 2, 3 via the support races 90, 93 and the thrust bearings 91, 95, respectively.
Since it is directly received by the gears 26, 48 that are prevented from moving in the axial direction via the thrust bearings 31, 55, no axial force acts on the arms 82, 76, and the rollers 7
No excessive force is applied to the 9,71, allowing light and accurate gear shifting.

(H-4) Other Embodiments In the above-described embodiments, the movable sheave of either one of the two pulleys 5 and 6 is moved with an equal stroke, but both movable sheaves are moved with an unequal stroke. Good. Further, although the stroke cam mechanism is rotated on the roller side and the end face cam is moved in the axial direction, it goes without saying that this relationship may be reversed.

Further, in the first embodiment, the ball screw mechanism 21 and the unequal stroke cam mechanism 50 are changed in speed by applying the same relative rotation. However, depending on the shape of the cam surface of the cam mechanism 50, the gear ratio from the counter shaft 57 may vary. The strokes of the two movable sheaves 7 and 33 may be adjusted so that they match. Similarly,
Also in the other second and third embodiments, the shape of the cam surface may be different and the gear ratio may be adjusted.

(G) Effect of the Invention As described above, according to the present invention, the moving amounts of the movable sheaves of both pulleys are made different from each other by the unequal stroke cam mechanism, so that at any speed ratio of the continuously variable transmission, Since the movable sheaves 7 and 33 of both pulleys 5 and 6 are set to the original shift positions defined by the belt B, when the positive torque transmission state is switched to the negative torque transmission or vice versa, the pressure adjusting mechanism is set. The movements of 11, 43 are extremely small, the power transmission becomes smooth, and it is possible to prevent a large impact force from being applied to the pressure adjusting mechanism, thereby improving the durability of the continuously variable transmission.

[Brief description of drawings]

FIG. 1 is a front sectional view showing a first embodiment of the present invention, FIG. 2 is a front view showing an unequal stroke cam mechanism thereof, and FIG. 3 is a view showing movement of an actuator mechanism on a primary side and a secondary side. is there. 4 is a front sectional view showing a second embodiment of the present invention, and FIG. 5 is a front view showing the unequal stroke cam mechanism thereof. Furthermore, FIG. 6 shows the third aspect of the present invention.
FIG. 7 is a front sectional view showing an embodiment, FIG. 7 is a front view showing the unequal stroke cam mechanism, and FIG. 8 is a view showing movements of both actuator mechanisms. FIG. 9 is a diagram showing the original strokes of both the primary and secondary movable sheaves defined by the belt. 1,1 ′, 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 mechanism (pressure adjusting cam mechanism), 21,21 ′, 21 ″, 50,50 ′, 50 ″ …… Actuator mechanism, 21 …… (ball) screw mechanism , 21 ', 50 ″…
… Equal stroke cam mechanism, 21 ″, 50 ′ …… Unequal stroke cam mechanism, 22,23,44,45,70,71,76,77,79,82 …… Two members, 70a, 77′a ...... Relative movement surface, 57,67 ...... Gear shift operation drive means.

Claims (5)

[Claims] 1. A V-belt type continuously variable transmission which has a primary pulley and a secondary pulley each of which is supported by each shaft and is capable of relatively moving in the axial direction, and which has a pulley wound around the pulleys. The pressure adjusting mechanism interposed between the shaft and the sheave of at least one of the pulleys and directly applying an axial force corresponding to the transmission torque, and two members capable of relative rotation. And a primary side actuator mechanism that moves the movable sheave of the primary pulley in the axial direction based on the relative rotation of the secondary pulley, and two members that can rotate relative to each other. In the secondary side actuator mechanism that moves to the At least one of the two members
The two actuator mechanisms include a power transmission device that interlocks so that the two members rotate in corresponding relative rotations, and a shift operation drive unit that interlocks with the power transmission device. At least one of the two
The relative movement surface of each of the members is formed of a curved surface, and includes an unequal stroke cam mechanism in which the axial movement amount changes non-linearly with respect to the relative rotation angle of these two members. V-belt type continuously variable transmission configured such that relative rotation is caused in the two members of the two actuator mechanisms based on the rotation of the actuator mechanism so that the moving amounts of the movable sheave by the two actuator mechanisms are different from each other. . 2. The V-belt type continuously variable transmission according to claim 1, wherein one of the actuator mechanisms is a screw mechanism and the other is an unequal stroke cam mechanism. 3. A V-belt type continuously variable transmission according to claim 1, wherein one of the actuator mechanisms is an equal stroke cam mechanism and the other is an unequal stroke cam mechanism. 4. The V-belt type continuously variable transmission according to claim 1, wherein both actuator mechanisms are unequal stroke cam mechanisms. 5. The V-belt type continuously variable transmission according to claim 1, wherein the pressure adjusting mechanism is a pressure adjusting cam mechanism.