JPH037822B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a V-belt type continuously variable transmission for a vehicle, which performs continuously variable transmission using a V-belt in a vehicle such as an automobile.

[Prior Art] Generally, a V-belt type continuously variable transmission includes an input pulley, an output pulley, and an endless V-belt that is wound between these two pulleys and transmits torque. Continuously variable speed is achieved by continuously changing the effective diameter of the position where the pulley frictionally engages with each pulley.

In such a V-belt continuously variable transmission,
Conventionally, when performing continuously variable transmission, changing the speed ratio (or reduction ratio) and increasing/decreasing the squeezing force between the pulley and the V-belt have been performed using hydraulic pressure.

[Problems to be Solved by the Invention] However, this hydraulic control is limited by the volume of the cylinder of the hydraulic servo and the minimum hydraulic pressure required in other parts of the hydraulic circuit.
It has been difficult to precisely change the belt clamping force in response to changes in the transmitted torque. For this reason, when a V-belt type continuously variable transmission is used as a transmission for an automobile or the like where transmission torque fluctuates rapidly, excessive clamping force tends to always occur on the friction surface between the pulley and the V-belt, and this excessive clamping force This has been the cause of a decrease in the durability of pulleys and V-belts, and a decrease in power transmission efficiency.

Therefore, in order to change the effective diameter and control the belt clamping force of the pulley without using such hydraulic pressure, a pressing force is applied to move the movable flange of the pulley in the axial direction and press the movable flange in the axial direction. In addition to the required member, a support member is also required to support the reaction force when the pressing member presses the movable flange. however,
If the support member supports the reaction force of the force that presses the movable flange, a frictional force will be generated between the pressing member and the support member. By the way, in order to improve the durability and power transmission efficiency of the V-belt mentioned above, it is necessary to set the clamping force of the V-belt to an appropriate level. To this end, it is conceivable to generate a clamping force corresponding to the transmission torque applied to the V-belt. In that case, the clamping force will be controlled in relation to the transmission torque, but the transmission torque requires that the torque applied to the V-belt be transmitted to the pressing member and the support member as directly as possible. However, when frictional force occurs between the pressing member and the supporting member as described above, a part of the transmission torque applied to the belt is consumed by the frictional force, resulting in torque loss. The torque applied to the V-belt is smaller than the transmission torque actually applied to the V-belt. Therefore, the pressing member generates a smaller clamping force than the clamping force corresponding to the transmission torque, resulting in slippage between the V-belt and the pulley.

The present invention has been made in view of the above circumstances, and an object of the present invention is to enable precise control of the squeezing force of the V-belt by the pulley in accordance with the transmitted torque. V that can improve the durability and power transmission efficiency of
An object of the present invention is to provide a belt type continuously variable transmission.

Another object of the present invention is to reduce the frictional force generated between the pressing member of the movable flange and its axial support member to reduce torque loss, thereby increasing the clamping force as much as possible corresponding to the transmitted torque. To provide a V-belt type continuously variable transmission which can reliably prevent V-belt slippage.

[Means for Solving the Problems] In order to solve the above-mentioned problems, the present invention provides an input shaft and an output shaft arranged parallel to each other, and a fixed flange and a fixed flange, respectively. an input pulley and an output pulley, each comprising a movable flange that is movable in the axial direction and rotates integrally with the fixed flange;
By converting rotational motion into axial motion and transmitting it to at least one of the movable flanges, the V-belt that transmits transmission between the input pulley and the output pulley, and the relative rotation with the at least one movable flange. said at least one movable flange comprising a motion converting means for axially displacing the movable flange and a driving means for axially moving said movable flange by locking said motion converting means to a stationary member to limit rotation of said motion converting means; a servo mechanism of the input/output pulley, which is provided between at least one of the input shaft and the output shaft and between the motion conversion means and a support member that supports the motion conversion means in the axial direction; A V-belt type continuously variable transmission for a vehicle comprising a clamping force generating means that generates clamping force according to the transmission torque of the V belt, wherein a support member supporting the motion converting means is provided in the clamping force generating means. and a thrust bearing is provided between the motion conversion means and the support member.

[Operations and Effects of the Invention] According to the V-belt type continuously variable transmission for vehicles of the present invention configured as described above, rotational motion is converted into axial motion, and at least one of the movable flanges is moved. a motion converting means for displacing the movable flange in the axial direction by relative rotation with the at least one movable flange; Since the at least one movable flange is provided with a servo mechanism consisting of a drive means for moving it in the axial direction, the rotation limit control amount of the motion conversion means is controlled by controlling the force that locks the motion conversion means to the stationary member. can be changed as desired.

Therefore, the amount and speed of movement of the movable flange in the axial direction, that is, the amount and speed of shifting, can be controlled to change as desired. As a result, it is possible to perform a smooth shift without a shift shock, and also to perform continuous shift control. Moreover, since the shift amount and shift speed can be controlled as desired, torque transmission efficiency is significantly improved.

Furthermore, by being able to change the speed change, for example, when the vehicle suddenly stops, the V-belt can be quickly returned to the maximum deceleration state to reliably restart the vehicle.

Further, according to the present invention, the input/output pulley is provided with a Since the belt clamping force is provided with a clamping force generating means that generates the clamping force of the belt according to the transmission torque of the V-belt, the clamping force of the V-belt can be precisely controlled according to the transmission torque. This improves the durability of the V-belt and further improves the torque transmission efficiency.

Furthermore, according to the present invention, a support member that supports the motion converting means is provided in the squeezing force generating means, and a thrust bearing is provided between the motion converting means and the support member, so that the It becomes possible to reduce the frictional force generated between the motion conversion means and the support member. Therefore, the transmission torque applied to the V-belt can be transmitted to the support member of the clamping force generating means without suffering almost any torque loss due to the friction.
Thereby, the clamping force generating means can more reliably generate the clamping force of the V-belt in accordance with the transmission torque.

Further, according to the present invention, since the above-mentioned motion conversion means and the above-mentioned clamping force generation means are provided, there is no need to use a hydraulic servo for speed change and belt clamping force as in the past. This eliminates the need for complicated oil passages. Therefore, the structure becomes extremely simple.

[Example] Hereinafter, an example of the present invention will be described using the drawings.

FIG. 1 is a sectional view showing an embodiment of a V-belt type continuously variable transmission according to the present invention. In the figure, 1 is the input shaft of the V-belt type continuously variable transmission, 2 is the output shaft of the V-belt type continuously variable transmission arranged parallel to the input shaft, and 3
is an input pulley provided on the input shaft 1; 4 is an output pulley provided on the output shaft 2; 5 is a V-belt that transmits power between the input pulley 3 and the output pulley 4;
6 is a servo mechanism that changes the effective diameter of the input pulley 3, 7 is a servo mechanism that changes the effective diameter of the output pulley 4, and 8 is a cam mechanism provided on the input pulley.

The input shaft 1 is rotatably supported by a V-belt type continuously variable transmission case 10 by bearings 11 and 12, and is also supported by a stage 13 and an outer peripheral spline 14.
and a tip screw 15 are formed.

In this embodiment, the output shaft 2 is formed integrally with a sleeve portion of a fixed flange, which will be described later, and has a bearing 21.
and 22, V-belt continuously variable transmission case 1
0 and is rotatably supported.

The input pulley 3 includes a sleeve-shaped portion 33 whose one end (the right end in the figure) is brought into contact with the step 13 of the input shaft via a thrust bearing 16, and whose outer periphery is provided with an outer circumferential spline 31 and a keyway 32; A fixed flange 3A consisting of a flange portion 35 formed integrally with a sleeve-shaped portion 33 and having a slit 34 around the outer periphery for detecting the rotational speed of the input shaft, the fixed flange 3A being axially displaced in the sleeve portion 33. a sleeve-shaped hub portion 38 which is freely fitted onto the outside and has a keyway 36 formed in its inner circumferential wall that corresponds to the keyway 32 of the fixed flange, and a driven screw 37 that is a first screw provided in its outer circumferential wall; A movable flange 3B consisting of a flange portion 39 integrally formed with the hub portion 38, and a movable flange 3B that is inserted into key grooves 32 and 36 to allow displacement in the axial direction of the fixed flange 3A and movable flange 3B, and It consists of a ball key 30 for integrally performing rotation.

The output pulley 4 has a keyway 41, a spline 42, and a screw 43 formed on its outer periphery, and includes a sleeve-shaped portion 44 formed integrally with the output shaft 2, and a flange portion 45 formed integrally with the sleeve-shaped portion 44. a fixed flange 4A consisting of;
A key groove 4 is fitted onto the sleeve portion 44 of A so as to be freely displaceable in the axial direction, and has a key groove 4 corresponding to the key groove 41 on the inner periphery.
1A, a movable flange 4B consisting of a sleeve-shaped hub portion 47 having a driven screw 56 as a first screw formed on the outer periphery, a flange portion 48 formed integrally with the hub portion 47, and a key groove 41. and a ball key 40 which is inserted into the flange 41A and is used to integrally rotate the fixed flange 4A and the movable flange 4B.

The V-belt 5 is connected to the fixed flange 3 of the input pulley 3.
Working surfaces 51 and 52 are in contact with the V-shaped working surfaces formed by A and the movable flange 3B and the V-shaped working surfaces formed by the fixed flange 4A and the movable flange 4B of the output pulley 4, respectively, to form friction surfaces. It is formed.

The input pulley servo mechanism 6 includes a sleeve 62, which is a driver of the movable flange, and a sleeve 62, which is a driver of the movable flange, and a drive screw 61, which is a second screw that is screwed into the driven screw 37 of the movable flange 3B of the input pulley, is formed on the inner periphery. It is provided between the sleeve 62 and the case 10 and includes a wet multi-plate electromagnetic upshift brake 63 for braking the sleeve 62, a downshift planetary gear set 64, and a wet multi-plate electromagnetic downshift brake 66. Planetary gear set 64
is a ring gear 64 connected to the sleeve 62;
R, an inner peripheral spline 83 that fits with the spline 31 of the fixed flange is formed, and one side surface on the movable flange side is formed on the end surface 6 of the sleeve 62.
A carrier 64C is connected to the other cam race 87, which is in contact with the other cam race 87 through the thrust bearing 85 and whose other side is used as the working surface 86 of the cam mechanism to be described later. Sungear 6 freely supported
4S, and ring gear 64R and sun gear 64S
It consists of a planetary gear 64P meshed with and rotatably supported by a carrier 64C,
A downshift brake 66 is provided between the sun gear 64S and the case 10.
S is braked by a downshift brake 66. It is also possible to reverse the effects of the upshift brake 63 and the downshift brake 66 by reversing the thread formation directions of the drive screw 61 of the sleeve 62 and the driven screw of the movable flange 3B.

The output pulley servo mechanism 7 includes a sleeve 72 which is a driver, and a sleeve 72 which is a driver having a drive screw 71 which is a second screw screwed into the driven screw 46 of the movable flange 4B formed on the inner periphery, and the sleeve 72 and the case 10. a wet multi-plate electromagnetic upshift brake 73 that fixes the upshift brake 73, a downshift torsion coil spring 74 whose both ends are connected and attached between the sleeve 72 and the movable flange 4B, and the spline 42 of the output shaft. A spline is formed to fit with the end surface 7 of the sleeve 72 through a thrust bearing 75, and one surface on the movable flange 4B side
The support ring 77 abuts on the sleeve 21 and is locked on the other side with a nut 76 to support the sleeve 72 in the axial direction.

The cam mechanism 8 is fixed in the axial direction by a step 13 provided on the input shaft and a nut 17 screwed onto a screw 15 at the end of the input shaft, as shown in FIG. One cam race 8 on which a matching inner peripheral spline 81 is formed
2, the other cam race 87, and a tapered roller 88 interposed between these cam races.
and a covering ring 89 of the roller 88, the roller 88 having a working surface 8 of the races 82 and 87.
2A and 86, and changes the pressing force that presses the movable flange 3B in the right direction in the figure in response to the rotational displacement between the input shaft 1 and the fixed flange 3A. The cam mechanism may be of a type using ball bearings instead of the tapered roller 88, of a type in which the slopes 8A and 8B are in direct contact as shown in FIG. 3, or of other configurations.

In this embodiment, the cam race 87 that is locked in the axial direction of the input shaft by the nut 17 on the input shaft is an axial support member for the sleeve 62 which is the driver, and the cam race 87 on the input shaft is held in the axial direction by the nut 76. A locking ring 77 that is locked in this direction is an axial support member for the sleeve 72, which is a driver.

In this way, the servo mechanism 6 of the input and output pulleys,
7, it becomes unnecessary to use hydraulic pressure for speed change and belt clamping force.

Also, each brake 63, 66, 6 during gear shift.
7 with a predetermined engagement force, the gap between the sleeve 62 and the sleeve 38 and between the sleeve 47
By generating a predetermined relative rotation between the sleeve 72 and the sleeve 72, the gear shift can be performed at a predetermined shift speed.

Next, the operation of this V-belt type continuously variable transmission will be explained.

(a) When driving at constant speed At this time, brakes 63, 66 and 7
All 3 are released. Therefore, torque is transmitted from input shaft 1 to one race 82 of the cam mechanism.
→ Tapered roller 88 → Other race 87
→Input pulley 3→V belt 5→Output pulley 4→
This is done in the order of output shaft 2. The magnitude of the torque transmitted by the V-belt 5 is proportional to the clamping force applied to the V-belt 5, and the clamping force is applied to the other cam race 87 via the movable pulley 3B and the sleeve 62 threaded to the movable pulley. Due to the principle of the mechanism, the input pulley moves slightly in the rotational direction, and the clamping force Fc applied in the axial direction by the tapered roller 83 changes in proportion to the transmitted torque as shown in FIG. The clamping force applied to 3B is changed in accordance with the transmitted torque, thereby changing the surface pressure between the working surface of the V-belt 5 and the working surfaces of the movable flange 3B and fixed flange 3A, thereby changing the clamping force on the contact surfaces. let In Figure 4, F1 is the necessary clamping force to prevent the V-belt from slipping at the maximum reduction ratio, F
2 indicates the necessary clamping force to prevent the V-belt from slipping at the lowest reduction ratio, F0 indicates the clamping force when using a conventional hydraulic servo, and Fs indicates the clamping force due to the spring. The graph in Figure 4 shows that in the V-belt endless transmission using the cam mechanism 8 of the present invention, the clamping force and the transmitted torque are directly proportional even when the transmitted torque is 5 kg or less, and unnecessary clamping force with the V-belt pulley occurs. It is clear that it is possible to reduce the

(b) During upshift At this time, brakes 63 and 73 are operated. Therefore, sleeves 62 and 7
2 is fixed, the sleeve parts 38 and 47 of the movable flange 3B rotate relative to the sleeves 62 and 72, and the movable flange 3B is displaced in the direction (to the right in the figure) to increase the effective diameter of the input pulley 3, and the movable flange 3B is moved. The flange 4B is displaced in a direction that reduces the effective diameter of the output pulley (to the right in the figure), and the reduction ratio is reduced. Brakes 63 and 73 are released when the reduction ratio reaches the control set value.

At this time, the torsion spring 74 of the output pulley servo mechanism is twisted and energy is stored.

(c) During downshift At this time, the brake 66 is operated.
Therefore, the sun gear 64S of the planetary gear set 64 is fixed, and the ring gear 64R increases the speed of the sleeve 62 in the rotational direction of the input shaft and moves the movable flange 3B in the direction of decreasing the effective diameter of the input pulley 3 (to the left in the figure). The torsion spring 74 rotates the sleeve 72 and returns.
The movable flange 4B is displaced in the direction of increasing the effective diameter of the output pulley (to the left in the figure). This displacement of the movable flange 3B of the input pulley 3 is performed against the pressing force of the movable flange 3B by the cam mechanism. When the reduction ratio reaches the control set value, the brake 66 is released.

When upshifting and downshifting as described above, a large pressing force is generated between the sleeves 62 and 72, which are drivers, and the cam race 87 and locking ring 77. Therefore, the rotational resistance due to friction during relative rotation is equal to the capacity of frictional resistance due to the clamping force of the V-belt, as shown in Figure 5.
Thrust bearings 85 and 75 compared to
If there is no V-belt, it will become large like F10 and slip of the V-belt will occur. By inserting the thrust bearings 85 and 75 of the present invention, rotational resistance due to frictional force during relative rotation can be reduced to F20, and slipping of the V-belt can be prevented.

FIG. 6 is a sectional view similar to FIG. 1 showing another embodiment of the present invention. It should be noted that the same components as those in the above-mentioned embodiments are given the same reference numerals, and their explanations will be omitted.

As shown in FIG. 6, in this embodiment, a servo mechanism 7A having the same configuration as the servo mechanism of the movable pulley 4B of the output pulley shown in the first embodiment is used as the drive mechanism of the movable flange 3B of the input pulley. .
The servo mechanism 7A is a drive element, and one end 621 is a sleeve 62 which is in contact with a cam race 87 via a thrust bearing 85, a wet multi-plate electromagnetic downshift brake 78 that fixes the sleeve 62 and the case 10, and one end is a It has an upshift torsion spring 79 fixed to the movable pulley 3B and the other end fixed to the sleeve 62.

The V-belt type continuously variable transmission of this embodiment releases both the downshift brake 78 and upshift brake 73 during steady driving, engages only the brake 78 during downshift, and engages only brake 73 during upshift. engage. The torsion spring 79 of the input pulley movable flange 3B is always given a predetermined twist, and is further twisted during an upshift, for example, and is returned to its original position during a downshift.

FIG. 7 shows a first embodiment showing still another embodiment of the present invention.
It is a sectional view similar to the figure. It should be noted that the same components as those in the above-mentioned embodiments are given the same reference numerals, and their explanations will be omitted.

As shown in FIG. 7, in this embodiment, the cam mechanism 8 in the second embodiment is arranged on the right side of the input pulley 3 of the input shaft 1 in the drawing. The cam mechanism 8A has an input pulley surface 19 of a flange-shaped portion 18 provided on the input shaft 1 and an end surface 33A of the sleeve portion 33 of the input pulley fixing flange 3A as working surfaces.
is slightly moved in the opposite direction to the movable flange 3B, and a clamping force corresponding to the transmitted torque is applied to the V-belt 5 between the locking ring 101 that is spline-fitted to the input shaft 1 and locked in the axial direction with a nut 17. Add.

FIG. 8 shows a first embodiment showing still another embodiment of the present invention.
It is a sectional view similar to the figure. It should be noted that the same components as those in the above-mentioned embodiments are given the same reference numerals, and their explanations will be omitted.

As shown in FIG. 8, in this embodiment, the cam mechanism 8
B is provided on the output shaft 2. The cam mechanism 8B is
One race 87 is spline-fitted to the sleeve portion 44 of the fixed flange 4A of the output pulley fitted to the output shaft 2, and the other cam race 87 is in contact with the end surface 721 of the sleeve 72 via the thrust bearing 85. , a support ring 58 that is externally fitted onto the sleeve portion 44 or the output shaft 2 and spline-fitted to the sleeve portion 44, and a thrust bearing 82.
1, the other cam race 82 is locked by a nut 59 screwed onto the sleeve portion 44 through the cam race 82;
It consists of a tapered roller 88. In this embodiment, the rotating drum 2A formed integrally with the cam race 82 serves as the output member.

FIG. 9 shows a first embodiment showing still another embodiment of the present invention.
It is a sectional view similar to the figure. It should be noted that the same components as those in the above-mentioned embodiments are given the same reference numerals, and their explanations will be omitted.

As shown in FIG. 9, in this embodiment, the servo mechanism 7B of the movable flange 3B of the input pulley includes a downshift brake 78, an upshift torsion spring 79, and a first screw formed on the outer periphery of the cam race 87. A driving screw 87A, a driven screw 61 which is a second screw formed on the inner periphery of the sleeve 62 and screwed into the driving screw 87A, and a sleeve 62.
The end face 622 next to the movable flange and the movable flange 3
Thrust bearing 623 interposed between B
and a friction engagement 70 of the downshift brake 78 provided between the sleeve 62 and the transmission case 10.
Brake plate 78 spline fitted to 0
1. Consists of a hub drum 783 connected to the sleeve 62 and having a spline 782 formed on its outer periphery, and a friction plate 784 disposed between the brake plate 781 and spline-fitted to the hub drum 783;
displacement in the axial direction is allowed. Furthermore, the servo mechanism 7C of the movable flange 4B of the output pulley has a similar configuration, and has an upshift brake 73, a downshift spring 74, and is freely displaceable in the axial direction, and the end surface 722 next to the movable flange is thrust into the movable flange 4B. A sleeve 72 abuts through a bearing 723, and a first screw threadedly engaged with a driven screw 71, which is a second screw formed on the sleeve.
It consists of a support ring 77 on the outer periphery of which a drive screw 771 is provided.

In this embodiment, when the downshift brake 78 or the upshift brake 73 is engaged, the sleeve 62 or 72, which is a driver, is displaced in the axial direction and presses the movable flange 3B or 4B.

FIG. 10 is a sectional view similar to FIG. 1 showing still another embodiment of the present invention. In addition, by attaching the same reference numerals to the same components as in the above-mentioned embodiment,
The explanation will be omitted.

As shown in FIG. 10, in this embodiment, the servo mechanism 9 of the movable flange consists of a pair of sleeves 9 screwed together.
It consists of a drive element 90 consisting of 1 and 92 and a servo motor that rotates these sleeves 91 and 92 relative to each other. The sleeve 91 has one end in contact with a race 87 of the cam mechanism via a bearing 85 and is provided with a gear 94, and the other end of the sleeve 92 abuts on the movable flange 3B via a thrust bearing 96 and has a gear 95 at the end. The output shaft of the servo motor 93 is provided with a first drive gear 97 meshing with a gear 94 and a second drive gear 98 having a different number of teeth than the gear 97 and meshing with a gear 95. There is. The axial length of the driver 90 increases or decreases depending on the rotational direction of the motor 93, and the pressing force of the movable flange 3B is changed to increase or decrease the effective diameter of the input pulley 3. In this way, it is also possible to use a drive mechanism such as a servo motor instead of a brake as the drive mechanism for the driver.

As described above, according to the V-belt type continuously variable transmission for vehicles of the present invention, rotational motion is converted into axial motion and transmitted to at least one of the movable flanges, so that at least one of the movable flanges is A motion converting means for displacing the movable flange in the axial direction by relative rotation with the movable flange, and a driving means for restricting rotation of the motion converting means by locking the motion converting means to a stationary member and moving the movable flange in the axial direction. Since the servo mechanism for the at least one movable flange is provided,
By controlling the force that locks the motion converting means to the stationary member, it is possible to change the rotation limit control amount of the motion converting means as desired.

Therefore, the amount and speed of movement of the movable flange in the axial direction, that is, the amount and speed of shifting, can be controlled to change as desired. As a result, it is possible to perform a smooth shift without a shift shock, and also to perform continuous shift control. Moreover, since the shift amount and shift speed can be controlled as desired, torque transmission efficiency is significantly improved.

Furthermore, by being able to change the speed change, for example, when the vehicle suddenly stops, the V-belt can be quickly returned to the maximum deceleration state to reliably restart the vehicle.

Further, according to the present invention, the input/output pulley is provided with a Since the belt clamping force is provided with a clamping force generating means that generates the clamping force of the belt according to the transmission torque of the V-belt, the clamping force of the V-belt can be precisely controlled according to the transmission torque. This improves the durability of the V-belt and further improves the torque transmission efficiency.

Furthermore, according to the present invention, a support member that supports the motion converting means is provided in the squeezing force generating means, and a thrust bearing is provided between the motion converting means and the support member, so that the It becomes possible to reduce the frictional force generated between the motion conversion means and the support member. Therefore, the transmission torque applied to the V-belt can be transmitted to the support member of the clamping force generating means without suffering almost any torque loss due to the friction.
Thereby, the clamping force generating means can more reliably generate the clamping force of the V-belt in accordance with the transmission torque.

Further, according to the present invention, since the above-mentioned motion conversion means and the above-mentioned clamping force generation means are provided, there is no need to use a hydraulic servo for speed change and belt clamping force as in the past. This eliminates the need for complicated oil passages. Therefore, the structure becomes extremely simple.

[Brief explanation of drawings]

Figure 1 shows the first V-belt type continuously variable transmission of the present invention.
2 is a front view of the cam mechanism, FIG. 3 is a front view of another embodiment of the cam mechanism, and FIG. 4 is a graph for explaining the operating principle of the cam mechanism.
Fig. 5 is a graph showing the capacity of frictional resistance of the V-belt, Fig. 6 is a sectional view showing a second embodiment of the V-belt type continuously variable transmission of the present invention, and Fig. 7 is a graph showing the capacity of the V-belt type continuously variable transmission. Sectional view showing the third embodiment of the gear transmission, No. 8
The figure is a sectional view showing a fourth embodiment of the V-belt type continuously variable transmission of the present invention, FIG. 9 is a sectional view showing the fifth embodiment of the V-belt type continuously variable transmission of the present invention, and FIG. FIG. 7 is a sectional view showing a sixth embodiment of the V-belt type continuously variable transmission of the present invention. In the figure 1...Input shaft, 2...Output shaft, 3...Input pulley, 4...Output pulley, 5...V belt,
6, 7, 7A, 9... Servo mechanism of movable flange, 8... Cam mechanism, 62, 72... Sleeve,
75, 85... Thrust bearing.

Claims (1)

[Scope of Claims] 1. A shaft is provided on an input shaft and an output shaft that are arranged parallel to each other, and is displaceable in the axial direction with respect to a fixed flange, and is integrally formed with the fixed flange. An input pulley and an output pulley consisting of a rotating movable flange, a V-belt that transmits power between the input pulley and the output pulley, and converting rotational motion into axial motion and transmitting it to at least one of the movable flanges. The motion converting means displaces the movable flange in the axial direction by relative rotation with the at least one movable flange, and the motion converting means is locked to a stationary member to restrict the rotation of the motion converting means. a servo mechanism for the at least one movable flange comprising a drive means for moving the movable flange in the direction;
A V-belt type continuously variable transmission for a vehicle, comprising a clamping force generating means for generating a clamping force of the V-belt of the input/output pulley according to the transmission torque of the V-belt, and a support for supporting the motion converting means. A V-belt type continuously variable transmission for a vehicle, characterized in that a member is provided on the squeezing force generating means, and a thrust bearing is provided between the motion converting means and the support member. 2. The motion converting means includes a first screw formed on each movable flange or a member axially interlocked with each of these movable flanges;
and a second screw that respectively displaces the first screw in the axial direction by relative rotation with the first screw. gearbox. 3. The V-belt type continuously variable transmission for a vehicle according to claim 2, wherein the driving means is a brake that brakes the second screw. 4. The V-belt type continuously variable transmission for a vehicle according to any one of claims 1 to 3, wherein the clamping force generating means is a cam mechanism.