JP2022092483A - Continuously variable transmission - Google Patents

Abstract

To achieve simplification of the structure to achieve reduction of manufacturing cost and electrical power consumption and downsizing in a continuously variable transmission.SOLUTION: Each of first and second movable side pulley half bodies 28, 72 in a drive pulley 16 and a driven pulley 18 includes: a piston chamber 40a, 40b and a centrifugal compensation pressure chamber 42a, 42b which are separated by a partition wall 36 and to which a working fluid is supplied; a first communication passage 48 which is formed at the partition wall 36 and allows the piston chamber 40a, 40b and the centrifugal compensation pressure chamber 42a, 42b to communicate with each other; a second communication passage 62 which allows the centrifugal compensation pressure chamber 42a, 42b and an exterior part of each of the first and second movable side pulley half bodies 28, 72 to communicate with each other; a first selector valve 54 which opens the first communication passage 48 with a centrifugal force generated by rotation of each of the drive pulley 16 and the driven pulley 18; and a second selector valve 64 which closes the second communication passage 62.SELECTED DRAWING: Figure 3

Description

The present invention relates to a continuously variable transmission mounted on a vehicle and shifting and outputting a driving force from a drive source such as an internal combustion engine.

Conventionally, a continuously variable transmission has been used as a transmission for shifting the driving force from an internal combustion engine and transmitting it to an axle in a vehicle, and this continuously variable transmission consists of a set of pulley pieces and faces each other. A belt is interposed between the arranged drive pulley and the driven pulley, and the driving force transmitted to the drive pulley is transmitted to the driven pulley to which the output shaft is connected via the belt, and the hydraulic oil is used. By moving one of the pulley pieces in the drive pulley and the driven pulley in the axial direction under the supply action, the distance between the shafts between the set of pulley pieces is changed, and the distance is transmitted from the drive pulley to the driven pulley accordingly. The gear ratio of the driving force to be applied is continuously changed.

In such a continuously variable transmission, one of the pulley pieces is moved in the axial direction by using the hydraulic pressure of the hydraulic oil. Therefore, for example, the drive pulley and the driven pulley rotate under the driving action of the internal combustion engine. When centrifugal force acts on the hydraulic oil, the pressure of the hydraulic oil rises and the pulley piece is pressed, which may cause the hydraulic oil to move in the axial direction from a predetermined position.

In order to solve such a problem, for example, in the continuously variable transmission disclosed in Patent Document 1, the fixed pulley portion piece fixed to the rotating shaft and the fixed pulley portion piece are approached in the axial direction. A movable pulley piece provided so as to be separable, a movable cylinder provided on the outer wall of the movable pulley piece, and a liquid provided on the inside of the movable cylinder and fixed to the rotating shaft and liquid on the movable cylinder. It is provided with a tightly fitted fixed cylinder portion.

Further, a hydraulic chamber is formed between the movable pulley portion piece and the fixed cylinder body to supply hydraulic oil for urging the movable pulley portion piece to one side of the fixed pulley portion, and is fixed to the movable cylinder portion. An adjusting oil chamber separated from the hydraulic chamber and to which the adjusting oil is supplied is formed between the cylinder and the cylinder, and a rotating side tubular member is provided on the outer peripheral side of the fixed cylinder so as to face the adjusting oil chamber. It is provided.

Then, the hydraulic oil is supplied to the hydraulic chamber through the oil passage, so that the movable pulley portion piece is hydraulically urged to one side of the fixed pulley portion, and the stepless transmission rotates at high speed to cause centrifugal force in the hydraulic chamber. When the pressure rises, the adjusting oil is introduced into the adjusting oil chamber from an adjusting oil flow path separate from the oil passage through an oil introduction groove formed between the fixed cylinder and the rotary side tubular member. .. As a result, the pressure in the adjusting oil chamber rises due to the supplied adjusting oil, and the movable cylinder is urged in the direction away from the fixed pulley piece, so that the movable pulley piece is fixed by the pressure increase of the hydraulic oil. The movement is prevented by being offset by the urging force to one side of the pulley portion, and the movable pulley portion piece is maintained in a predetermined position.

On the other hand, the continuously variable transmission disclosed in Patent Document 2 includes a drive side pulley, a driven side pulley, and an endless V-belt wound between the drive side pulley and the driven side pulley, and the drive side pulley. Includes a fixed sheave fixed to the drive shaft and a movable sheave movable with respect to the drive shaft. A hydraulic cylinder chamber to which hydraulic oil is supplied is provided on the back side of the movable sheave, and centrifugal force generated when the stepless transmission rotates is provided on the inner peripheral side and the back side of the hydraulic cylinder chamber. Each hydraulic balance chamber is provided for canceling the hydraulic pressure generated in the hydraulic cylinder chamber, and the hydraulic balance chamber is formed so that hydraulic oil can be supplied from an oil pump via a lubricating oil passage.

When the stepless transmission rotates at high speed and the hydraulic pressure in the hydraulic cylinder chamber rises due to centrifugal force, the hydraulic pressure in the hydraulic balance chamber and the hydraulic cylinder chamber provided on the inner peripheral side is fixed to the movable sheave. On the other hand, the hydraulic pressure of the hydraulic balance chamber provided on the back side acts on the movable sheave on the opposite side of the fixed sheave. Therefore, the sum of the hydraulic pressures in the hydraulic balance chamber and the hydraulic cylinder chamber provided on the inner peripheral side balances with the hydraulic pressure in the hydraulic balance chamber provided on the rear side, so that the movable sheave is fixed on the sheave side due to the increase in hydraulic pressure due to centrifugal force. It is prevented from moving to.

Jitsufuku No. 6-12271 Japanese Unexamined Patent Publication No. 61-45166

However, in the continuously variable transmission of Patent Document 1 described above, since it is necessary to separately provide a adjusting oil chamber capable of storing the adjusting oil on the outer peripheral side of the hydraulic chamber, the size becomes large in the radial direction and the hydraulic chamber is operated. Since the passage for supplying oil (oil passage) and the passage for supplying adjusting oil to the adjusting oil chamber (adjusting oil passage) have different configurations, the structure becomes complicated and the size of the device is increased and manufactured. There is a problem that it causes an increase in cost.

Similarly, in the continuously variable transmission of Patent Document 2, a passage (oil passage) for supplying hydraulic oil to the hydraulic cylinder chamber and a passage (lubricating oil) for supplying oil to a set of hydraulic balance chambers. Since the road) is provided as a separate system with respect to the driven shaft, there is a problem that the processing of the driven shaft becomes complicated and the manufacturing cost increases. Furthermore, in order to prevent the movable sheave from being pressed toward the fixed sheave side due to centrifugal force at high rpm, oil is supplied to the hydraulic balance chamber by an oil pump, which causes a problem of increased power consumption. There is.

The present invention has been made in consideration of the above-mentioned problems, and an object of the present invention is to provide a continuously variable transmission capable of reducing manufacturing cost and power consumption by simplifying the configuration and reducing the size. do.

In order to achieve the above object, an embodiment of the present invention includes a drive pulley and a driven pulley having a movable side pulley half body that can move relative to the fixed side pulley half body and the fixed side pulley half body in the axial direction. It is equipped with an endless member wound between the drive pulley and the driven pulley, and the gear ratio is changed by changing the groove width of the drive pulley and the groove width of the driven pulley with the hydraulic pressure of the hydraulic oil. In the transmission
The movable side pulley half body is separated in the axial direction by a partition wall and is supplied with hydraulic oil in a hydraulic chamber and a centrifugal compensating pressure chamber.
The first communication passage formed in the partition wall and communicating the hydraulic chamber and the centrifugal compensation pressure chamber,
A second communication passage that communicates the centrifugal compensation pressure chamber with the outside of the movable pulley half body,
The first switching valve that opens the first passage by the centrifugal force generated by the rotation of the drive pulley or driven pulley,
A second switching valve that closes the second passage by the centrifugal force generated by the rotation of the drive pulley or driven pulley,
To prepare for.

According to the present invention, the movable side pulley half body of the drive pulley and the driven pulley constituting the stepless transmission is provided with a hydraulic chamber and a centrifugal compensation pressure chamber separated in the axial direction by a partition wall and supplied with hydraulic oil. A first communication passage connecting the hydraulic chamber and the centrifugal compensation pressure chamber is formed in this partition wall, and the first communication passage is opened by the first switching valve by the centrifugal force generated by the rotation of the drive pulley or the driven pulley. , It has a second communication passage that communicates the centrifugal compensation pressure chamber and the outside of the movable side pulley, and the second communication passage is closed by the second switching valve by centrifugal force.

Therefore, when the drive pulley and the driven pulley are rotating at high speed, the pressure of the hydraulic oil in the hydraulic chamber rises due to the centrifugal force, and a pressing force is generated to urge the movable side pulley half body toward the fixed side pulley half body side. Even if there is, a part of the hydraulic oil in the hydraulic chamber is supplied to the centrifugal compensation pressure chamber side through the open first communication passage, the pressure of the hydraulic oil in the centrifugal compensation pressure chamber is increased, and the centrifugal compensation pressure chamber by centrifugal force is used. By pressing the movable side pulley half body in the direction opposite to the fixed side pulley half body by the pressing force generated by the pressure rise of the hydraulic oil in, the fixed side with respect to the movable side pulley half body by centrifugal force. It can be preferably offset by the pressing force acting on the pulley half body side.

As a result, compared to the conventional continuously variable transmission, which supplies hydraulic oil to each of the two hydraulic chambers through the two passages to prevent the movement of the pulley piece due to centrifugal force, it has a simple structure and is used at high speeds. Since it is possible to prevent the pressing force on the fixed side pulley half body side acting on the movable side pulley half body due to the centrifugal force, it is possible to reduce the size of the continuously variable transmission and the manufacturing cost. .. In addition, since the hydraulic oil is supplied to the centrifugal compensation pressure chamber at high rpm, the power consumption is higher than that of the conventional continuously variable transmission that supplies the hydraulic oil from the oil pump. Can be reduced.

According to the present invention, the following effects can be obtained.

That is, at the time of high rotation of the stepless transmission, the pressure of the hydraulic oil in the hydraulic chamber rises due to the centrifugal force, and a pressing force for urging the movable side pulley half body toward the fixed side pulley half body side is generated. However, by supplying the hydraulic oil in the hydraulic chamber to the centrifugal compensation pressure chamber through the open first communication passage, the pressure of the hydraulic oil in the centrifugal compensation pressure chamber is increased, and the hydraulic oil in the centrifugal compensation pressure chamber is increased by centrifugal force. The pressing force on the movable side pulley half body in the direction opposite to the fixed side pulley half body can be preferably offset by the pressing force on the fixed side pulley half body side acting on the movable side pulley half body.

As a result, compared to the conventional continuously variable transmission, which supplies hydraulic oil to each of the two hydraulic chambers through the two passages to prevent the movement of the pulley piece due to centrifugal force, the centrifugal force is reduced with a simple configuration. It is possible to prevent the movable side pulley half body from moving to the fixed side pulley half body side, and it is possible to reduce the size of the continuously variable transmission and the manufacturing cost.

It is an overall sectional view of the continuously variable transmission which concerns on embodiment of this invention. It is an enlarged sectional view of the drive pulley in the continuously variable transmission of FIG. FIG. 3 is an enlarged cross-sectional view showing a state in which the continuously variable transmission of FIG. 2 is rotated at a high speed.

A suitable embodiment of the continuously variable transmission according to the present invention will be described, and will be described in detail below with reference to the accompanying drawings.

As shown in FIG. 1, the continuously variable transmission 10 is mounted on, for example, a vehicle equipped with an engine (not shown), and includes a drive shaft 12 and a driven shaft 14 arranged in parallel with each other, and the drive shaft 12 is provided. The driving force from the engine is transmitably connected, the driven shaft 14 is connected so as to be able to transmit the driving force to the drive wheels of the vehicle, and the drive pulley 16 provided on the drive shaft 12 and the driven shaft are connected. An endless metal belt (endless member) 20 is wound around a driven pulley 18 provided on the shaft 14.

As shown in FIGS. 1 to 3, the drive shaft 12 is composed of a shaft body extending along the axial direction (directions of arrows A and B), and an oil supply extending along the axial direction is inside the drive shaft 12. A passage 22a is formed, and hydraulic oil is supplied from a hydraulic supply device (for example, an oil pump) (not shown) to circulate. Further, the drive shaft 12 has a connecting path 24 extending radially outward from the oil supply path 22a at a position facing the first movable side pulley half body 28, which will be described later, and the connecting path 24 is the drive shaft 12. It penetrates to the outer peripheral surface and communicates with the piston chamber 40a of the first movable side pulley half body 28, which will be described later.

The drive pulley 16 is a disk-shaped first fixed-side pulley half body (fixed-side pulley half body) 26 fixed to the drive shaft 12, and the drive for the first fixed-side pulley half body 26. It has a disc-shaped first movable side pulley half body (movable side pulley half body) 28 slidable in the axial direction (arrows A and B directions) of the shaft 12, and the first fixed side pulley half body 26. Is on one side in the axial direction of the drive shaft 12 (direction of arrow A), and the first movable side pulley half body 28 is on the other side in the axial direction (direction of arrow B) with respect to the first fixed side pulley half body 26. Placed in. The first movable side pulley half body 28 has a groove width (groove width of the drive pulley 16) between the first fixed side pulley half body 26 and the first fixed side pulley half body 26 due to the hydraulic pressure of the hydraulic oil supplied to the piston chamber 40a described later. It is provided so as to be variable.

The first movable side pulley half body 28 includes a boss portion 30 that is in sliding contact with the outer peripheral surface of the drive shaft 12, a disk-shaped pulley piece 32 extending toward the outer peripheral side with respect to the boss portion 30, and the pulley. The tubular portion 34 extending in the axial direction (arrow B direction) from the vicinity of the outer edge portion of the piece 32, the partition wall 36 housed inside the tubular portion 34, and the tubular portion 34 provided substantially parallel to the partition wall 36. It has a cover portion 38 that closes the other end in the axial direction of the above.

Further, in the first movable side pulley half body 28, a piston chamber (hydraulic chamber) 40a facing the pulley piece 32 and being supplied with hydraulic oil, and a centrifugal compensation pressure chamber 42a adjacent to the piston chamber 40a with the partition wall 36 interposed therebetween. And prepare. The piston chamber 40a is formed in an annular shape on the outer peripheral side of the drive shaft 12 by being surrounded by the pulley piece 32, the boss portion 30, the tubular portion 34, and the partition wall 36, and has a connection path 24 opened on the outer peripheral surface of the drive shaft 12. It communicates with the oil supply path 22a via the oil supply path 22a.

The centrifugal compensation pressure chamber 42a is provided on the outer peripheral side of the drive shaft 12, is surrounded by a tubular portion 34, a partition wall 36, and a cover portion 38 to form an annular shape, and is formed in an annular shape with respect to the piston chamber 40a in the axial direction of the drive shaft 12. It is separated by a partition wall 36 adjacent to the side (direction of arrow B). A predetermined amount of hydraulic oil, which is the same as the hydraulic oil supplied to the piston chamber 40a, is stored inside the centrifugal compensation pressure chamber 42a.

The partition wall 36 is formed, for example, in a disk shape from a plate material having a constant thickness, is provided so as to be orthogonal to the axis of the drive shaft 12, and its inner peripheral surface abuts on the outer peripheral surface of the drive shaft 12. It is positioned in the axial direction by the locking ring 44, and the outer peripheral surface is arranged so as to be in sliding contact with the inner peripheral surface of the tubular portion 34. A seal ring 46 is attached to the outer peripheral surface of the partition wall 36 via an annular groove and is in contact with the inner peripheral surface of the tubular portion 34. That is, the partition wall 36 is fixed to the drive shaft 12 and does not move together with the first movable side pulley half body 28.

Further, between the partition wall 36 and the first movable side pulley half body 28, the pulley piece 32 is attached in the direction of separating from the partition wall 36, that is, toward the first fixed side pulley half body 26 side (arrow A direction). A spring 47 is provided to force the spring 47. The spring 47 is composed of, for example, a coil spring, and is arranged so as to be on the outer peripheral side of the boss portion 30. Then, the elastic force of the spring 47 urges the first movable side pulley half body 28 toward the first fixed side pulley half body 26, so that the first movable side pulley half body 28 and the first fixed body 28 are fixed. The metal belt 20 is held between the side pulley half body 26 and the metal belt 20.

Further, the partition wall 36 has a first communication passage 48 penetrating in the axial direction (arrows A and B directions), and the first communication passage 48 is formed, for example, with a constant diameter along the axial direction and has a piston chamber. The 40a and the centrifugal compensation pressure chamber 42a are communicated with each other, and are formed at a position closer to the inner peripheral surface than the central portion between the inner peripheral surface and the outer peripheral surface of the partition wall 36, that is, on the drive shaft 12 side. There is.

Then, inside the first connecting passage 48, an orifice 50 capable of adjusting the flow rate of the hydraulic oil flowing inside the first connecting passage 48 is provided. The orifice 50 is formed in a cylindrical shape having a hole having a diameter smaller than the passage cross-sectional area of the first continuous passage 48. It is not necessary to provide the orifice 50 in the first continuous passage 48, and the shape of the orifice 50 is the hydraulic oil to be circulated from the piston chamber 40a to the centrifugal compensation pressure chamber 42a side through the first continuous passage 48. It is set appropriately according to the flow rate.

Further, the partition wall 36 is provided with a valve accommodating portion 52 formed on the end surface facing the centrifugal compensation pressure chamber 42a and recessed toward the piston chamber 40a side (direction of arrow A) and a first valve accommodating portion 52 facing the valve accommodating portion 52. It is provided with a first switching valve 54 capable of switching the communication state of the communication passage 48.

The valve accommodating portion 52 is formed, for example, in a substantially triangular cross section formed deeply toward the piston chamber 40a side (direction of arrow A) gradually from the inner peripheral side to the outer peripheral side of the partition wall 36, and is near the inner peripheral side thereof. The other end of the first communication passage 48 in the axial direction is open. The maximum depth of the valve accommodating portion 52 is formed so as to be, for example, ½ or more of the axial thickness of the partition wall 36.

For the first switching valve 54, for example, a leaf spring formed of an elastic plate material is used so that one end (inner peripheral end) thereof is the inner peripheral side of the partition wall 36 and the other end (outer peripheral end) is the outer peripheral side. Is arranged substantially parallel to the partition wall 36, and is fixed by, for example, a rivet 56 penetrating in the thickness direction of the partition wall 36 in a state where one end of the partition wall 36 is in contact with the end surface of the partition wall 36. In other words, the first switching valve 54 has a cantilever structure in which only one end along the extending direction thereof is fixed.

Further, the first switching valve 54 is formed so as to bend from one end supported by the partition wall 36 toward the other end toward the piston chamber 40a side (direction of arrow A) by a predetermined angle, and from one fixed end to the other. A portion on the end side is accommodated in the valve accommodating portion 52, and a weight 58 having a predetermined weight is attached to the other end. That is, the first switching valve 54 is preformed in a shape inclined by a predetermined angle with respect to the partition wall 36 so that the other end side is accommodated in the valve accommodating portion 52 together with the weight 58.

The other end of the first switching valve 54 is tiltably provided with one end supported by the rivet 56 as a fulcrum, and is accommodated in the valve accommodating portion 52 to close the other end in the axial direction of the first communication passage 48. The communication between the piston chamber 40a and the centrifugal compensation pressure chamber 42a through the first communication passage 48 is blocked.

The cover portion 38 covers the other end in the axial direction of the tubular portion 34, is provided substantially parallel to the partition wall 36 in the axial direction (arrow B direction) by a predetermined distance, and is substantially orthogonal to the tubular portion 34. The inner peripheral surface thereof is provided so as to be in sliding contact with the outer peripheral surface of the drive shaft 12.

Further, the cover portion 38 is provided with a second communication passage 62 penetrating in the thickness direction (axial direction) in the vicinity of the outer peripheral portion close to the cylinder portion 34, and is formed inside the cover portion 38 through the second communication passage 62. The centrifugal compensation pressure chamber 42a and the outside are in communication with each other. The second passage 62 is arranged so as to be radially outside, that is, on the tubular portion 34 side as compared with the first passage 48 provided in the partition wall 36.

Further, on the outside of the cover portion 38, a second switching valve 64 capable of switching the communication state of the second communication passage 62 so as to face the second communication passage 62 is provided.

Similar to the first switching valve 54, the second switching valve 64 uses, for example, a leaf spring formed of an elastic plate material, and one end (inner peripheral end) thereof is the inner circumference with respect to the second connecting passage 62. It is arranged substantially parallel to the cover portion 38 so that it is on the side and the other end (outer peripheral end) is on the outer peripheral side. Then, the second switching valve 64 is fixed by, for example, a rivet 66 penetrating in the thickness direction of the cover portion 38 in a state where one end thereof is in contact with the end surface of the cover portion 38. In other words, the second switching valve 64 has a cantilever structure in which only one end along the extending direction thereof is fixed.

Further, the second switching valve 64 is formed so as to bend by a predetermined angle from one end supported by the cover portion 38 toward the other end in a direction away from the cover portion 38 (direction of arrow B). A weight 68 having a predetermined weight is attached to the end. That is, the second switching valve 64 is preliminarily formed in a shape in which the other end side is inclined by a predetermined angle with respect to the cover portion 38 together with the weight 68.

The other end side of the second switching valve 64 is tiltably provided with one end supported by the rivet 66 as a fulcrum, and the other end side is separated from the cover portion 38 so that the other end side in the axial direction of the second communication passage 62 is provided. It is opened and the centrifugal compensation pressure chamber 42a and the outside communicate with each other through the second communication passage 62. The second switching valve 64 is arranged so as to be radially outside the first switching valve 54.

In the drive pulley 16 described above, the first movable side pulley half body 28 is urged toward the first fixed side pulley half body 26 side (arrow A direction) by the hydraulic oil supplied to the piston chamber 40a, and the drive shaft 12 is used. It moves along the first fixed side pulley half body 26 side so as to approach. On the other hand, by reducing the supply amount of the hydraulic oil to the piston chamber 40a, the first movable side pulley half body 28 moves in the direction away from the first fixed side pulley half body 26 (direction of arrow B). ..

As a result, the axial distance (groove width) between the first movable side pulley half body 28 and the first fixed side pulley half body 26 changes, and the metal belt 20 wound between the two changes accordingly. Moves in the radial direction to change the turning radius, so that the gear ratio of the driving force from the drive pulley 16 to the driven pulley 18 is changed.

On the other hand, as shown in FIG. 1, the driven pulley 18 includes a disk-shaped second fixed side pulley half body (fixed side pulley half body) 70 fixed to the driven shaft 14, and the second fixed side pulley. It has a disk-shaped second movable side pulley half body (movable side pulley half body) 72 that is slidable in the axial direction (arrows A and B directions) of the driven shaft 14 with respect to the half body 70. 2 The fixed side pulley half body 70 is on the other side in the axial direction of the driven shaft 14 (in the direction of arrow B), and the second movable side pulley half body 72 is on one side in the axial direction with respect to the second fixed side pulley half body 70 (in the direction of arrow B). It is arranged so as to be in the direction of the arrow A).

Further, the second movable side pulley half body 72 has a groove width (groove width of the driven pulley 18) between the second fixed side pulley half body 70 and the second fixed side pulley half body 70 due to the hydraulic pressure of the hydraulic oil supplied to the piston chamber 40b described later. It is provided so as to be variable.

As shown in FIG. 1, the driven pulley 18 has the same configuration as the drive pulley 16 and is arranged so as to be symmetrical in the axial direction. Therefore, the same reference numerals are given to the same components. A detailed description thereof will be omitted.

The second movable side pulley half body 72 includes a piston chamber 40b facing the pulley piece 32 and supplying hydraulic oil, and a centrifugal compensation pressure chamber 42b adjacent to the piston chamber 40b with the partition wall 36 interposed therebetween. The chamber 40b is formed in an annular shape on the outer peripheral side of the driven shaft 14 by being surrounded by the pulley piece 32, the boss portion 30, the tubular portion 34, and the partition wall 36, and provides a connection path 24 opened on the outer peripheral surface of the driven shaft 14. It communicates with the oil supply path 22b via the oil supply path 22b.

The partition wall 36 has a valve accommodating portion 52 formed on the end surface facing the centrifugal compensation pressure chamber 42b and recessed toward the piston chamber 40b, and the valve accommodating portion 52 is provided with a communication state of the first communication passage 48. A switchable first switching valve 54 is provided.

Further, the cover portion 38 of the second movable side pulley half body 72 is provided with a second communication passage 62 penetrating in the thickness direction (axial direction) in the vicinity of the outer edge portion close to the cylinder portion 34, and the second communication passage. The centrifugal compensation pressure chamber 42b formed inside the cover portion 38 and the outside communicate with each other through 62, and the communication state of the second communication passage 62 is switched to the outside of the cover portion 38 facing the second communication passage 62. It is equipped with a possible second switching valve 64.

Then, in the driven pulley 18, the second movable side pulley half body 72 is urged toward the second fixed side pulley half body 70 side (in the direction of arrow B) by the hydraulic oil supplied to the piston chamber 40b, and the driven shaft 14 is used. The second movable side pulley half body 72 is second fixed by reducing the supply amount of the hydraulic oil to the piston chamber 40b while moving so as to approach the second fixed side pulley half body 70 side along the same. It moves in the direction away from the side pulley half body 70 (direction of arrow A).

As a result, the axial distance (groove width) between the second movable side pulley half body 72 and the second fixed side pulley half body 70 changes, and the metal belt 20 wound between the two changes accordingly. Moves in the radial direction to change the turning radius, so that the gear ratio of the driving force from the drive pulley 16 to the driven pulley 18 is changed and transmitted.

The continuously variable transmission 10 according to the embodiment of the present invention is basically configured as described above, and the operation and the effect thereof will be described next. A state in which the vehicle on which the continuously variable transmission 10 is mounted is stopped will be described as an initial state.

First, in an initial state in which an engine (not shown) is already driven and the driving force is not transmitted to the drive wheels of the vehicle, the driver operates a select lever (not shown) to start the vehicle, thereby electronically controlling the vehicle. A driving force (torque) from the engine is transmitted to the drive shaft 12 of the continuously variable transmission 10 based on a command from a unit (not shown), and the drive pulley 16 rotates integrally with the drive shaft 12. ..

Further, when the vehicle is started from a stopped state, in the continuously variable transmission 10, the groove width of the drive pulley 16 is increased to reduce the turning radius of the metal belt 20, and the groove width of the driven pulley 18 is reduced. By increasing the turning radius of the metal belt 20, control is performed to increase the gear ratio.

Specifically, in the drive pulley 16, the hydraulic oil is not supplied to the piston chamber 40a filled with the hydraulic oil, and the pressure of the hydraulic oil does not rise, so that the first movable side pulley half The body 28 moves in a direction away from the first fixed-side pulley half body 26 (in the direction of arrow B). Therefore, the groove width (distance between the axes) between the first fixed side pulley half body 26 and the first movable side pulley half body 28 becomes large, and the first movable side pulley half body 28 and the first fixed side pulley half body 26 The metal belt 20 moves inward in the radial direction along the inclined surface, and the radius of gyration becomes smaller.

Further, as described above, when the vehicle is stopped or traveling at a low speed and the drive pulley 16 is rotating at a low rotation speed, the first and second switching of the first movable side pulley half body 28 is performed. Since the centrifugal force acting on the valves 54 and 64 is small, the first and second switching valves 54 and 64 do not tilt together, and the first switching valve 54 closes the first communication passage 48. The second switching valve 64 maintains the open state of the second communication passage 62.

Further, as the drive pulley 16 rotates, a centrifugal force acts on the hydraulic oil in the piston chamber 40a, and the pressure near the radial outer side in the piston chamber 40a rises. The pressure rise causes the drive pulley 16 to rotate at a high speed. It will be a little compared to the state where it was done. Therefore, the centrifugal pressing force in one axial direction (direction of arrow A) with respect to the first movable side pulley half body 28 due to the pressure increase due to the centrifugal force becomes small, and the first movable side pulley half body 28 is used. 1 The size is not large enough to push toward the fixed side pulley half body 26 side.

Further, centrifugal force also acts on the hydraulic oil in the centrifugal compensation pressure chamber 42a, but since the second communication passage 62 is opened by the second switching valve 64, the hydraulic oil flows through the second communication passage 62. By being discharged to the outside, the pressure increase in the centrifugal compensation pressure chamber 42a is avoided, and the centrifugal pressing force (also referred to as cancellation pressure) that presses the cover portion 38 toward the other side in the axial direction with the pressure increase due to the centrifugal force. ) Does not occur.

On the other hand, in the driven pulley 18, hydraulic oil is supplied from a hydraulic supply device (not shown) to the oil supply path 22b based on a command from an electronic control unit (not shown), and the second movable side pulley half body is supplied through the connection path 24. By being supplied into the piston chamber 40b of 72, the pulley piece 32 of the second movable side pulley half body 72 moves toward the second fixed side pulley half body 70 side (direction of arrow B) by the hydraulic pressure of the hydraulic oil. When pressed, the second movable side pulley half body 72 approaches the second fixed side pulley half body 70 side (direction of arrow B).

As a result, the groove width (distance between the shafts) between the second movable side pulley half body 72 and the second fixed side pulley half body 70 becomes smaller, and the metal belt 20 becomes the second movable side pulley half body 72 and the second movable side pulley half body 72. The radius of gyration increases by moving outward in the radial direction along the inclined surface of the second fixed-side pulley half body 70. As a result, the gear ratio of the driving force transmitted from the drive pulley 16 to the driven pulley 18 becomes large.

Then, the driving force transmitted from the engine to the drive shaft 12 is transmitted to the metal belt 20 sandwiched between the first fixed side pulley half body 26 and the first movable side pulley half body 28 in the drive pulley 16. By rotating the metal belt 20, the metal belt 20 is transmitted to the driven pulley 18 sandwiching the metal belt 20 between the second fixed side pulley half body 70 and the second movable side pulley half body 72 at a predetermined speed change ratio. Will be done.

At this time, when the driven pulley 18 starts to rotate and the rotation speed is low, the centrifugal force acting on the first and second switching valves 54 and 64 of the second movable side pulley half body 72 is small, so that the first And the second switching valves 54 and 64 do not tilt, the first switching valve 54 closes the first communication passage 48, and the second switching valve 64 maintains the open state of the second communication passage 62. Will be done. Therefore, the hydraulic oil supplied to the piston chamber 40b does not flow into the centrifugal compensation pressure chamber 42b side through the first communication passage 48, and the hydraulic pressure of all the hydraulic oil supplied to the piston chamber 40b prevents the second movable side. The pulley half body 72 is urged toward the second fixed side pulley half body 70 side (direction of arrow B) with a predetermined valve control pressure (pushing pressure).

Further, as the driven pulley 18 rotates, a centrifugal force acts on the hydraulic oil in the piston chamber 40b, and the pressure in the vicinity of the radial outer side in the piston chamber 40b rises, but the pressure rise is higher in the driven pulley 18. It will be slight compared to the rotated state. Therefore, the centrifugal pressing force in the other side in the axial direction (direction of arrow B) with respect to the second movable side pulley half body 72 due to the pressure increase due to the centrifugal force becomes small, and the second movable side pulley half body 72 is used. 2 The size is not large enough to push toward the fixed side pulley half body 70 side.

Further, centrifugal force also acts on the hydraulic oil in the centrifugal compensation pressure chamber 42b, but since the second communication passage 62 is opened by the second switching valve 64, the hydraulic oil is external to the hydraulic oil through the second communication passage 62. The pressure increase in the centrifugal compensation pressure chamber 42b is avoided, and the centrifugal pressing pressure (cancellation pressure) that presses the cover portion 38 to one side in the axial direction is generated along with the pressure increase due to the centrifugal force. Never.

Then, the driving force transmitted from the drive pulley 16 to the driven pulley 18 at a desired gear ratio is transmitted from the driven shaft 14 fixed to the second fixed side pulley half body 70 via a differential gear or the like (not shown) of the vehicle. It is transmitted to the drive wheels.

Next, a case will be described in which the continuously variable transmission 10 rotates at a high speed by changing the gear ratio of the driving force transmitted from the engine (not shown) to the continuously variable transmission 10 while the vehicle is running. do. While the vehicle is traveling at high speed, in the continuously variable transmission 10, the groove width of the drive pulley 16 is reduced to increase the turning radius of the metal belt 20, and the groove width of the driven pulley 18 is increased. Control is performed to reduce the gear ratio by reducing the turning radius of the metal belt 20.

First, the supply amount of hydraulic oil to the driven pulley 18 is reduced, while the supply amount of hydraulic oil to the drive pulley 16 is increased based on a command from an electronic control unit (not shown) (not shown). As a result, in the driven pulley 18, the hydraulic pressure of the piston chamber 40b in the second movable side pulley half body 72 decreases, so that the second movable side pulley half body 72 is separated from the second fixed side pulley half body 70 (arrow). It moves in the A direction), and the distance between the axes (groove width) between the two gradually increases, so that the turning radius of the metal belt 20 becomes smaller.

On the other hand, in the drive pulley 16, as shown in FIG. 3, the hydraulic oil is supplied to the piston chamber 40a of the first movable side pulley half body 28 through the oil supply path 22a, so that the first movable side pulley half body is said. 28 is urged toward the first fixed side pulley half body 26 side (direction of arrow A) and moves by a predetermined distance. As a result, the distance (groove width) between the axes of the first movable side pulley half body 28 and the first fixed side pulley half body 26 becomes smaller, and accordingly, the first movable side pulley half body 28 and the first fixed side The metal belt 20 moves radially outward along the inclined surface of the pulley half body 26 to increase the turning radius, so that the gear ratio of the driving force transmitted from the drive pulley 16 to the driven pulley 18 is changed. To.

Further, when the drive pulley 16 rotates at a high speed, a centrifugal force acts on the hydraulic oil in the piston chamber 40a, the pressure in the vicinity of the radial outer side in the piston chamber 40a rises, and the first and second switching valves 54 and 64 Centrifugal force works in the same way. Therefore, in the first and second switching valves 54 and 64, the weights 58 and 68 provided at the outer ends thereof are pulled outward in the radial direction by the centrifugal force, and the first switching valve 54 is centrifugal from the valve accommodating portion 52. The first communication passage 48 is opened by tilting toward the compensation pressure chamber 42a side (direction of arrow B), and the second switching valve 64 is tilted toward the cover portion 38 side (direction of arrow A) to open the second communication passage 62. Close the other end in the axial direction of.

As a result, the piston chamber 40a and the centrifugal compensation pressure chamber 42a communicate with each other through the first communication passage 48, and the communication between the centrifugal compensation pressure chamber 42a and the second communication passage 62 to the outside is cut off, and the operation in the piston chamber 40a is performed. A part of the oil flows into the centrifugal compensation pressure chamber 42a side through the first communication passage 48, and the hydraulic oil in the centrifugal compensation pressure chamber 42a increases. Further, since the communication between the centrifugal compensation pressure chamber 42a and the outside through the second communication passage 62 is cut off, the hydraulic oil is not discharged from the centrifugal compensation pressure chamber 42a to the outside, and the hydraulic oil is not discharged to the outside. The oil pressure will rise.

As a result, as shown in FIG. 3, in the piston chamber 40a, the first fixed side pulley half body 26 side (direction of arrow A) with respect to the pulley piece 32 of the first movable side pulley half body 28 by the supplied hydraulic oil. ) Is applied with a valve control pressure MP, and centrifugal force causes centrifugal force CP1 to be the largest in the vicinity of the outer side in the radial direction and to urge one side in the axial direction (arrow A direction). do.

On the other hand, in the centrifugal compensating pressure chamber 42a, a centrifugal force acts on the hydraulic oil in the centrifugal compensating pressure chamber 42a to generate the largest centrifugal pressing pressure CP2 in the vicinity of the outer side in the radial direction, and the centrifugal pressing pressure CP2 is generated. The cover portion 38 is applied so as to press it toward the other side in the axial direction (direction of arrow B). The centrifugal pressing force CP2 works on both sides in the axial direction so as to be maximum on the radial outer side in the piston chamber 40a, but since the partition wall 36 is fixed to the drive shaft 12, the first movable is movable. It is urged to one side in the axial direction so as to press the side pulley half body 28.

The centrifugal pressing pressure CP2 of the centrifugal compensation pressure chamber 42a introduces the hydraulic oil of the piston chamber 40a to the centrifugal compensation pressure chamber 42a side through the first continuous passage 48, so that the centrifugal pressing pressure CP1 generated in the piston chamber 40a is generated. It is set to be the same as the absolute value of (CP1 = CP2).

Specifically, by providing the orifice 50 inside the first continuous passage 48, the flow rate flows from the piston chamber 40a to the centrifugal compensation pressure chamber 42a side through the first continuous passage 48 at the time of high rotation of the continuously variable transmission 10. It controls the flow rate of hydraulic oil.

As a result, the centrifugal pressing force CP1 that presses the pulley piece 32 of the first movable side pulley half body 28 in the piston chamber 40a in one axial direction (arrow A direction) and the first movable side pulley in the centrifugal compensation pressure chamber 42a. The centrifugal pressing force CP2 that presses the cover portion 38 of the half body 28 toward the other side in the axial direction (arrow B direction) has the same size and acts in opposite directions, so that they are preferably offset. In other words, the centrifugal pressing force CP1 and the centrifugal pressing force CP2, which act on opposite sides in the axial direction, are balanced and offset.

Therefore, at high rotation of the stepless transmission 10, the first movable side pulley half body 28 is moved to the first fixed side pulley half body 26 side (arrow) by the centrifugal pressing pressure CP1 in addition to the valve control pressure MP due to the influence of the centrifugal force. It is prevented from being pressed in the A direction), and is pressed in one axial direction (arrow A direction) only by the desired valve control pressure MP.

On the other hand, when the driving force from the drive pulley 16 is transmitted to the driven pulley 18 at high rotation speed via the metal belt 20, the centrifugal force generated by the rotation of the driven pulley 18 at high rotation speed causes the inside of the piston chamber 40b. As the pressure of the hydraulic oil rises near the radial outer side, the weights 58 and 68 of the first and second switching valves 54 and 64 are pulled outward by the centrifugal force, respectively, and the first switching valve 54 causes the first and second switching valves 54 to pull outward. The 1-series passage 48 is opened, and the 2nd-series passage 62 is closed by the second switching valve 64.

As a result, the piston chamber 40b and the centrifugal compensation pressure chamber 42b in the second movable side pulley half body 72 communicate with each other through the first communication passage 48, and the centrifugal compensation pressure chamber 42b communicates with the outside through the second communication passage 62. Is shut off, and a part of the hydraulic oil in the piston chamber 40b is introduced to the centrifugal compensation pressure chamber 42b side through the first communication passage 48, and the hydraulic oil in the centrifugal compensation pressure chamber 42b increases.

Then, in the piston chamber 40b, the pulley piece 32 of the second movable side pulley half body 72 is pressed toward the second fixed side pulley half body 70 side (direction of arrow B) by the centrifugal pressing force CP1 generated by the centrifugal force. In the centrifugal compensation pressure chamber 42b, the cover portion 38 is urged by the centrifugal force in the direction opposite to the second fixed side pulley half body 70 side (direction of arrow A), and has the same absolute value as the centrifugal pressing force CP1. When the cover portion 38 is pressed by the centrifugal pressing force CP2, the centrifugal pressing force CP1 and the centrifugal pressing force CP2 are suitably offset. Therefore, the second movable side pulley half body 72 does not move in the axial direction from the predetermined position.

In this way, the driving force transmitted from the engine to the drive shaft 12 at high rotation is the metal sandwiched between the first fixed side pulley half body 26 and the first movable side pulley half body 28 in the drive pulley 16. It is transmitted to the belt 20, and by rotating the metal belt 20, it is desired to be a driven pulley 18 in which the metal belt 20 is sandwiched between the second fixed side pulley half body 70 and the second movable side pulley half body 72. It is transmitted at the gear ratio of. Then, it is transmitted from the driven shaft 14 fixed to the second fixed side pulley half body 70 of the driven pulley 18 to the drive wheels of the vehicle via a differential gear or the like (not shown).

The above-mentioned first and second switching valves 54 and 64 are not limited to the case where they are composed of leaf springs, and can be opened and closed by using the centrifugal force of the drive pulley 16 and the driven pulley 18. All you need is.

As described above, in the present embodiment, in the stepless transmission 10 for shifting the driving force from the engine and transmitting it to the drive wheels of the vehicle, the first and the driven pulleys 18 are configured in the stepless transmission 10. The second movable side pulley halves 28 and 72 have piston chambers 40a and 40b and centrifugal compensating pressure chambers 42a and 42b, respectively, to which hydraulic oil is supplied and separated in the axial direction by the partition wall 36, and the partition wall 36 has. Opens the first communication passage 48 by the centrifugal force generated by the rotation of the drive pulley 16 and the driven pulley 18 and the first communication passage 48 communicating the piston chambers 40a and 40b and the centrifugal compensation pressure chambers 42a and 42b. A first switching valve 54 is provided. On the other hand, the cover portions 38 of the first and second movable side pulley half bodies 28 and 72 have a second communication passage 62 that communicates the centrifugal compensation pressure chambers 42a and 42b with the outside, and a second communication passage due to the centrifugal force. A second switching valve 64 that closes 62 is provided.

Therefore, when the drive pulley 16 and the driven pulley 18 constituting the continuously variable transmission 10 rotate at a low speed, the first switching valve 54 closes the first communication passage 48, and the second switching valve 64 opens the second communication passage 62. As a result, the first and second movable side pulley halves 28 and 72 are changed to the first and second fixed side pulley halves 26 and 70 by the pressure of the hydraulic oil (valve control pressure MP) supplied to the piston chambers 40a and 40b. It can be moved to the side by pressing it with a desired pressure. Further, by configuring the hydraulic oil in the centrifugal compensation pressure chambers 42a and 42b to be discharged to the outside, it is possible to prevent the generation of the cancel pressure (centrifugal pressing pressure CP2).

On the other hand, when the drive pulley 16 and the driven pulley 18 rotate at high speed, the first communication passage 48 is opened and the second communication passage 62 is closed, so that a part of the hydraulic oil in the piston chambers 40a and 40b is partially discharged to the centrifugal compensation pressure chamber 42a. Centrifugal compensation pressure by centrifugal force against the centrifugal pressing pressure CP1 to the first and second fixed side pulley halves 26 and 70 side generated in the hydraulic oil of the piston chambers 40a and 40b by supplying to 42b. Centrifugal pressing CP2 to the opposite side of the first and second fixed side pulley halves 26 and 70 generated in the hydraulic oil of the chambers 42a and 42b can be suitably offset by being the same.

As a result, the drive shaft 12 and driven are compared with the conventional continuously variable transmission in which the passage for supplying the hydraulic oil to the hydraulic chamber and the passage for supplying the adjusting oil to the adjusting oil chamber are different configurations. The shaft 14 is provided with a single oil supply passage 22a and 22b (connection passage 24) capable of supplying hydraulic oil to the piston chambers 40a and 40b, respectively, with a simple configuration of the first and second movable side pulley half bodies 28. The centrifugal pressing pressure CP1 applied to 72 can be suitably offset and moved at a desired valve control pressure MP. Therefore, it is possible to reduce the size and manufacturing cost of the continuously variable transmission 10, and the metal belt 20 becomes the first and the metal belt 20 due to the excessive pressing force of the first and second movable side pulley half bodies 28 and 72. It is also possible to prevent the pulley from being pinched between the second fixed side pulley halves 26 and 70 and damaged.

Further, since the piston chambers 40a and 40b for storing the hydraulic oil and the centrifugal compensation pressure chambers 42a and 42b are arranged along the axial direction of the drive shaft 12 and the driven shaft 14, the adjustment oil can be stored. Compared with the conventional continuously variable transmission in which the oil chamber is arranged on the outer peripheral side of the hydraulic chamber, the radial dimension can be suppressed and the size can be reduced.

Further, at high rotation of the continuously variable transmission 10, the cancel pressure (centrifugation) is performed by the hydraulic oil supplied from the piston chambers 40a and 40b to the centrifugal compensation pressure chambers 42a and 42b without driving the hydraulic pressure supply device such as an oil pump. Since the push pressure CP2) can be generated, the power consumption for driving the hydraulic pressure supply device can be reduced to save energy, and a plurality of passages to which hydraulic oil is supplied are provided on the pulley shaft. Compared with the conventional continuously variable transmission, the single oil supply passages 22a and 22b can be easily processed and manufactured, so that the manufacturing cost of the continuously variable transmission 10 can be reduced. ..

Furthermore, in the first and second movable side pulley half bodies 28 and 72, the first communication passage 48 and the first switching valve 54 are radially inward with respect to the second communication passage 62 and the second switching valve 64. For example, the stepless transmission 10 is rotating at a low rotation speed, and the centrifugal pressing force CP1 due to the centrifugal force is not generated in the piston chambers 40a and 40b, but in the centrifugal compensating pressure chambers 42a and 42b. When the generation of the cancel pressure (centrifugal pressing pressure CP2) is not required, it is possible to reduce the amount of hydraulic oil stored in the centrifugal compensating pressure chambers 42a and 42b.

Further, at the time of low rotation of the stepless transmission 10, the first switching valve 54 closes the first communication passage 48, and the second switching valve 64 opens the second communication passage 62, whereby the piston chambers 40a and 40b. The hydraulic oil supplied to the piston chambers 40a and 40b is prevented from flowing into the centrifugal compensation pressure chambers 42a and 42b, and the hydraulic oil supplied to the piston chambers 40a and 40b causes the first and second movable side pulley halves 28 and 72. The pulley piece 32 can be reliably pressed and moved toward the first and second fixed side pulley half bodies 26 and 70 with only the desired valve control pressure MP, and further, the centrifugal compensation pressure chambers 42a and 42b. It is possible to reliably avoid the generation of the cancel pressure (centrifugal pressing pressure CP2) due to the hydraulic oil inside.

Further, the first and second switching valves 54 and 64 are provided along the radial direction of the first and second movable side pulley halves 28 and 72, and the inner peripheral end thereof is provided along the radial direction of the first and second movable side pulley halves 28 and 72. The body 28 and 72 have a cantilever structure supported by the partition wall 36 and the cover portion 38, respectively, and the outer peripheral end side is tiltable, and weights 58 and 68 are provided on the outer peripheral end side, respectively.

Therefore, when the drive pulley 16 and the driven pulley 18 rotate at high speed, the outer peripheral ends provided with the weights 58 and 68 are suitably pulled outward in the radial direction by centrifugal force to facilitate the first and second switching valves 54 and 64. In addition, it can be tilted reliably to switch the communication state of the first and second communication passages 48 and 62, and the simple configuration can reduce the manufacturing cost, and the size can be increased in the axial direction. It is possible to suppress it.

Further, the centrifugal compensation pressure chambers 42a and 42b adjacent to the piston chambers 40a and 40b, the first communication passage 48 communicating the piston chambers 40a and 40b with the centrifugal compensation pressure chambers 42a and 42b, and the first communication passage 48 are provided. The first switching valve 54 that opens and closes, the second communication passage 62 that communicates the centrifugal compensation pressure chambers 42a and 42b with the outside, and the second switching valve 64 that opens and closes the second communication passage 62 are drive pulleys as described above. The case is not limited to the case where the 16 and the driven pulley 18 are provided respectively, and for example, the drive pulley 16 and the driven pulley 18 may be provided only in one of the drive pulleys 16 and the driven pulley 18.

It should be noted that the continuously variable transmission according to the present invention is not limited to the above-described embodiment, and of course, various configurations can be adopted without departing from the gist of the present invention.

10 ... Continuously variable transmission 16 ... Drive pulley 18 ... Driven pulley 20 ... Metal belts 22a, 22b ... Oil supply path 26 ... First fixed side pulley half body 28 ... First movable side pulley half body 36 ... Bulk partition 38 ... Cover 40a, 40b ... Piston chamber 42a, 42b ... Centrifugal compensation pressure chamber 48 ... 1st continuous passage 54 ... 1st switching valve 62 ... 2nd continuous passage 64 ... 2nd switching valve 70 ... 2nd fixed side pulley half body 72 ... 2 Movable side pulley half body

Claims (5)

A drive pulley and a driven pulley having a fixed side pulley half body and a movable side pulley half body that can move relative to the fixed side pulley half body, and winding between the drive pulley and the driven pulley. In a continuously variable transmission, which is provided with a continuously variable transmission and changes the gear ratio by changing the groove width of the drive pulley and the groove width of the driven pulley with the hydraulic pressure of the hydraulic oil, respectively.
The movable side pulley half body is separated in the axial direction by a partition wall, and is supplied with the hydraulic oil and the centrifugal compensation pressure chamber.
A first communication passage formed in the partition wall and communicating the hydraulic chamber and the centrifugal compensation pressure chamber,
A second communication passage that communicates the centrifugal compensation pressure chamber with the outside of the movable pulley half body,
A first switching valve that opens the first communication passage by centrifugal force generated by the rotation of the drive pulley or the driven pulley.
A second switching valve that closes the second passage by centrifugal force generated by the rotation of the drive pulley or the driven pulley.
A continuously variable transmission. In the continuously variable transmission according to claim 1,
The first communication passage and the first switching valve are continuously variable transmissions arranged inside the movable side pulley half body in the radial direction with respect to the second communication passage and the second switching valve. In the continuously variable transmission according to claim 1 or 2.
A continuously variable transmission in which the first switching valve closes the first passage and the second switching valve opens the second passage when the drive pulley or the driven pulley is not rotating. In the continuously variable transmission according to any one of claims 1 to 3.
The first and second switching valves are provided along the radial direction of the movable side pulley half body, and have a cantilever structure in which the inner peripheral end thereof is supported by the movable side pulley half body and the outer peripheral end side is tiltable. , A continuously variable transmission provided with a weight on the outer peripheral end side. In the continuously variable transmission according to any one of claims 1 to 4.
The first switching valve is provided inside the centrifugal compensation pressure chamber, and the second switching valve is provided outside the centrifugal compensation pressure chamber, a continuously variable transmission.

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