JP7339909B2 - Driven pulley device - Google Patents

Description

The present invention relates to a driven pulley device for a continuously variable transmission.

As a device of this type, there is conventionally known a device in which a torque cam mechanism is provided in a driven pulley to which torque output from a driving pulley is transmitted via an endless power transmission member (see, for example, Patent Document 1). ).

Japanese Patent No. 6605745

However, in the device described in Patent Document 1, the torque cam mechanism causes a differential in the rotational direction between the movable pulley half and the fixed pulley half, which constitute the driven pulley, at the time of shifting, causing slippage in the power transmission member. do.

A driven pulley device, which is one aspect of the present invention, includes a first pulley half supported by a rotating shaft so as to be relatively rotatable and axially movable; a driven pulley to which torque output from the drive pulley is transmitted via an endless power transmission member; a biasing member that biases the pulley half toward the second pulley half; a first cam mechanism that restricts axial relative movement and relative rotation of the first pulley half with respect to the rotating shaft; A second cam mechanism that restricts relative movement and relative rotation of the two pulley halves, and a third cam that permits axial relative movement of the first and second pulley halves and prohibits relative rotation. a mechanism; The first cam mechanism includes a first cam groove provided in the first pulley half and extending in a direction inclined to the axial direction, and a first cam mechanism provided so as to rotate integrally with the rotating shaft and engaged with the first cam groove. The second cam mechanism is provided on the second pulley half and extends in a first direction inclined to the axial direction and a second direction symmetrical to the first direction with respect to the axial direction. and a second cam pin provided to rotate integrally with the rotating shaft and engaged with the second cam groove, and the third cam mechanism is attached to one of the first pulley half and the second pulley half. A third cam groove is provided and extends axially, and a third cam pin engages with the third cam groove.

ADVANTAGE OF THE INVENTION According to this invention, the slip of an endless power transmission member at the time of a gearshift can be suppressed.

1 is a skeleton diagram showing an example of a schematic configuration of a drive system of a vehicle to which a driven pulley device according to an embodiment of the invention is applied; FIG. The figure which shows roughly the principal part structure of the driven pulley apparatus which concerns on embodiment of this invention. FIG. 3 is a top view of the first torque cam mechanism and the second torque cam mechanism in FIG. 2 ; 4 is a view showing the first torque cam mechanism of FIG. 3; FIG. FIG. 4 is a diagram showing the second torque cam mechanism of FIG. 3; FIG. 3 is a top view of the grooved cam mechanism in FIG. 2 ; 1 is a skeleton diagram showing an example of a schematic configuration of a vehicle drive system to which a modified example of a driven pulley device according to an embodiment of the invention is applied; FIG. The figure which shows the principal part structure of the driven pulley apparatus based on the modification of this embodiment.

An embodiment of the present invention will be described below with reference to FIGS. 1 to 5. FIG. FIG. 1 is a skeleton diagram showing an example of a schematic configuration of a vehicle drive system to which a driven pulley device according to an embodiment of the invention is applied. As shown in FIG. 1 , torque from an engine (ENG) 1 is input to a continuously variable transmission (also called CVT) 3 via a torque converter 2 . The continuously variable transmission 3 includes a drive pulley 50 to which torque is input from the torque converter 2 via the input shaft 4, a driven pulley 60 radially spaced from the drive pulley 50, and the drive pulley 50. It has an endless V-belt (power transmission member) 7 that is wound between the drive pulley 50 and the driven pulley 60 to transmit torque from the driving pulley 50 to the driven pulley 60 . The torque transmitted to driven pulley 60 is transmitted to drive wheels 10 via output shaft 8 and gear mechanism 9, thereby causing the vehicle to run.

The drive pulley 50 includes a fixed pulley half 51 supported by the input shaft 4 so as not to rotate relative to and axially unmovable, and a drive pulley 50 that is unrotatable relative to the input shaft 4 and axially movable relative to the fixed pulley half 51 . and a movable pulley half 52 supported on the . The fixed pulley half 51 and the movable pulley half 52 have substantially conical surfaces 51a and 52a facing each other. . The distance between the conical surface 51a of the fixed pulley half 51 and the conical surface 52a of the movable pulley half 52 gradually decreases from the outer diameter side to the inner diameter side, and the fixed pulley half 51 and the movable pulley half 52 are separated from each other. The groove between is formed in a substantially V shape.

The driven pulley 60 has a first pulley half 61 provided coaxially with the output shaft (rotating shaft) 8 and a second pulley half 62 coaxially arranged to face the first pulley half 61 . . The first pulley half 61 is supported by the output shaft 8 so as to be relatively rotatable and axially movable. . The first pulley half 61 and the second pulley half 62 have substantially conical conical surfaces 61a and 62a that face each other, and the width direction side surfaces of the V-belt 7 are aligned with these conical surfaces 61a and 62a. abut. The distance between the conical surface 61a of the first pulley half 61 and the conical surface 62a of the second pulley half 62 gradually decreases from the outer diameter side to the inner diameter side, and the first pulley half 61 and the second pulley The groove between the half bodies 62 is formed in a substantially V shape.

An actuator (not shown) is provided on the side of the movable pulley half 52 of the drive pulley 50 to move the movable pulley half 52 in the axial direction. The actuator is composed of, for example, a hydraulic piston chamber, and the movable pulley half 52 moves in the axial direction according to the hydraulic pressure of hydraulic oil supplied to the piston chamber. As the movable pulley half 52 moves in the axial direction, the relative distance from the fixed pulley half 51 changes, and the winding radius of the V-belt 7 that contacts the conical surfaces 51a and 52a changes. This causes the V-belt 7 to move radially.

A biasing member (not shown) is provided on the side of the first pulley half 61 of the driven pulley 60 to bias the first pulley half 61 toward the second pulley half 62 in the axial direction. The biasing member is, for example, a spring member such as a coil spring, and the first pulley half 61 moves in the axial direction against or due to the biasing force of the spring member. As the first pulley half 61 moves in the axial direction, the relative distance from the second pulley half 62 changes, and the winding radius of the V-belt 7 contacting the conical surfaces 61a and 62a changes. This causes the V-belt 7 to move radially.

For example, when the relative distance between the fixed pulley half 51 and the movable pulley half 52 of the drive pulley 50 is shortened, the V-belt 7 on the drive pulley 50 side is moved radially outward. The V-belt 7 is pulled toward the drive pulley 50 side. When the V-belt 7 on the side of the driven pulley 60 is pulled toward the drive pulley 50, the first pulley half 61 moves away from the second pulley half 62 against the biasing force of the spring member. The relative distance between the half body 61 and the second pulley half body 62 is increased. As a result, the V-belt 7 on the side of the driven pulley 60 is moved to the inner diameter side. Thus, in the continuously variable transmission 3, the gear ratio can be changed steplessly.

By the way, the first torque cam mechanism 63 moves the first pulley half 61 in the axial direction while rotating the first pulley half 61 relative to the output shaft 8 in order to move the first pulley half 61 smoothly. Therefore, when the second pulley half 62 is provided so as not to rotate relative to the output shaft 8 and not to move in the axial direction, a differential occurs between the first pulley half 61 and the second pulley half 62 during gear shifting. This causes the V-belt 7 to slip. Therefore, the driven pulley device according to the embodiment of the present invention is configured as follows so that the V-belt 7 does not slip.

FIG. 2 is a diagram schematically showing the main configuration of the driven pulley device 6 according to the embodiment of the present invention. As shown in FIG. 2, the driven pulley device 6 includes a driven pulley 60, an inner cylinder 66 and an outer cylinder 67, a spring member (biasing member) 68, a first torque cam mechanism (first cam mechanism) 63, A second torque cam mechanism (second cam mechanism) 64 and a groove cam mechanism (third cam mechanism) 65 are provided.

The driven pulley 60 is coaxially opposed to a first pulley half 61 supported by the output shaft 8 so as to be rotatable relative to the output shaft 8 and movable in the axial direction CL. and a second pulley half 62 supported rotatably and movably in the axial direction CL. Since the first pulley half 61 and the second pulley half 62 have the same configuration as described above, the description thereof is omitted.

The inner cylinder 66 has a substantially cylindrical shape coaxial with the output shaft 8 and is supported by the output shaft 8 so as to be rotatable relative to it and movable in the axial direction CL. A second pulley half body 62 is integrally provided at one end of the inner cylinder 66 in the axial direction CL. It is supported so as to be able to move in the axial direction CL.

The outer cylinder 67 has a substantially cylindrical shape coaxial with the inner cylinder 66 and is supported by the inner cylinder 66 so as to be relatively rotatable and movable in the axial direction CL. That is, the outer cylinder 67 is supported by the output shaft 8 via the inner cylinder 66 so as to be relatively rotatable and movable in the axial direction CL. A first pulley half body 61 is integrally provided at one end of the outer cylinder 67 in the axial direction CL. It is supported so as to be able to move in the axial direction CL. That is, the outer cylinder 67 and the first pulley half 61 are integrally supported by the output shaft 8 via the inner cylinder 66 so as to be relatively rotatable and movable in the axial direction CL.

The spring member 68 has a substantially cylindrical shape coaxial with the outer cylinder 67 and is arranged on the outer peripheral side of the outer cylinder 67 . The spring member 68 has one end in contact with the first pulley half 61 and the other end in contact with a stopper (not shown) provided at the other end of the outer cylinder 67 . , to bias the first pulley half 61 to one side.

FIG. 3 is a top view of the first torque cam mechanism 63 and the second torque cam mechanism 64 of FIG. As shown in FIG. 3, a first torque cam mechanism 63 for restricting the relative movement and relative rotation of the first pulley half 61 with respect to the output shaft 8 in the axial direction CL, and the axial direction of the second pulley half 62 with respect to the output shaft 8. A second torque cam mechanism 64 that regulates relative movement and relative rotation of CL is provided so as to operate by a common cam pin. That is, each of the first torque cam mechanism 63 and the second torque cam mechanism 64 is provided with a cam groove so as to operate with a common cam pin. By providing the first torque cam mechanism 63 and the second torque cam mechanism 64 so as to operate with a common cam pin, the length of the driven pulley device 6 in the axial direction CL can be shortened, and the size of the driven pulley device 6 can be reduced. be possible. The first torque cam mechanism 63 and the second torque cam mechanism 64 may each have a cam pin and a cam groove, and may be configured to be operated by the respective cam pins.

4A is a diagram showing the first torque cam mechanism 63 of FIG. 3. FIG. As shown in FIG. 4A, the first torque cam mechanism 63 is provided in an outer cylinder 67 integral with the first pulley half body 61, and includes a first cam groove 631 extending in the axial direction CL and the inclined direction C0. and a first cam pin 632 provided to rotate integrally with. The first cam groove 631 is formed in a substantially linear shape with which the first cam pin 632 can be engaged, and the first cam pin 632 protrudes radially outward from the output shaft 8 . That is, the first torque cam mechanism 63 is formed so that the first cam pin 632 can move linearly along the first cam groove 631 in the direction C0 that is inclined in the axial direction CL. By providing such a first torque cam mechanism 63, part of the thrust force acting on the first pulley half 61 becomes a rotational force, and the first pulley half 61 can be moved smoothly.

4B is a diagram showing the second torque cam mechanism 64 of FIG. 3. FIG. As shown in FIG. 4B, the second torque cam mechanism 64 is provided on an outer cylinder 67 integral with the second pulley half 62, and is formed in a shape capable of correcting misalignment occurring in the second pulley half 62. It comprises two cam grooves 641 and a first cam pin 632 that engages with the second cam groove 641 . The second cam groove 641 is formed in a bent shape with which the first cam pin 632 can be engaged, and the first cam pin 632 is a cam pin common to the cam pin of the first torque cam mechanism 63 . By forming the second cam groove 641 into a bent shape (for example, a doglegged shape) that serves as a misalignment correction shape, misalignment due to the provision of the second torque cam mechanism 64 can be corrected.

More specifically, the second cam groove 641 includes a first groove portion 641a extending in a first direction C1 inclined with respect to the axial direction CL, and a second cam groove portion 641a extending in a second direction C2 symmetrical to the first direction C1 with respect to the axial direction CL. and a groove portion 641b. Each of the first groove portion 641a and the second groove portion 641b is formed in a substantially linear shape with which the first cam pin 632 can be engaged. Construct glyphs. That is, the second cam groove 641 is formed in a substantially V shape centered on the axial direction CL, with the central portion located on one side in the axial direction CL and both ends located on the other side in the axial direction. In other words, the second cam groove 641 is formed in a dogleg shape.

The length in the axial direction CL of the first groove portion 641a (the length in the axial direction CL of the second groove portion 641b) is the amount of misalignment correction. That is, the length of the first cam groove 631 in the axial direction CL is the stroke amount of the first pulley half 61 in the axial direction CL, and the rotation of the second pulley half 62 is restricted by the grooved cam mechanism 35. . Therefore, by reciprocating the second pulley half 62 in the axial direction CL within the stroke amount of the first pulley half 61, misalignment correction becomes possible.

The axial CL length of the first groove portion 641a (the axial CL length of the second groove portion 641b) is about 1 mm, which is about 1 mm of the axial CL length of the first cam groove 631 (about 10 mm). /10 length. The circumferential length (rotational length) of the second cam groove 641 is substantially the same as the circumferential length (rotational length) of the first cam groove 631 . By making the circumferential length of the second cam groove 641 and the circumferential length of the first cam groove 631 the same, the amounts of rotation of the first pulley half 61 and the second pulley half 62 are the same. Slippage of the V-belt 7 can be suppressed.

FIG. 5 is a top view of the grooved cam mechanism 65 of FIG. As shown in FIG. 5, the grooved cam mechanism 65 is formed to allow relative movement of the first pulley half 61 and the second pulley half 62 in the axial direction CL and prohibit relative rotation. . More specifically, the grooved cam mechanism 65 is provided on the outer cylinder 67 integral with the first pulley half 61 , and includes a third cam groove 651 extending in the axial direction CL and a third cam groove 651 that engages with the third cam groove 651 . and a cam pin 652 . The third cam groove 651 is formed substantially linearly, and the length in the axial direction CL of the third cam groove 651 is formed to be equal to or longer than the length in the axial direction CL of the first cam groove 631 . The third cam pin 652 protrudes radially outward from the inner cylinder 66 integral with the second pulley half 62 . In the grooved cam mechanism 65, the third cam groove is provided in the inner cylinder 66 integrated with the second pulley half 62, and the third cam pin extends from the outer cylinder 67 integrated with the first pulley half 61 to the third cam groove. You may make it protrude towards.

In the continuously variable transmission 3 configured as described above, the V-belt 7 is positioned radially inside the drive pulley 50 and positioned radially outside the driven pulley 60 in a low speed running state. In this state, the first cam pin 632 of the first torque cam mechanism 63 is positioned at the end of the first cam groove 631 on the low speed side (upper right end of the first cam groove 631 shown in FIG. 4A), and the second torque cam mechanism 63 The first cam pin 632 of the mechanism 64 is located at the end of the second cam groove 641 on the low speed side (the upper right end of the second cam groove 641 shown in FIG. 4B).

When the continuously variable transmission 3 starts shifting from the low-speed running state to the high-speed running state, an actuator (not shown) moves the movable pulley half 52 of the driving pulley 50 to one side in the axial direction CL. As a result, the relative distance between the movable pulley half 52 and the fixed pulley half 51 is shortened, and the V-belt 7 on the drive pulley 50 side moves from the radially inner side to the radially outer side. When the V-belt 7 on the drive pulley 50 side moves radially outward, the V-belt 7 on the driven pulley 60 side is pulled toward the drive pulley 50 side.

When the V-belt 7 on the side of the driven pulley 60 is pulled toward the drive pulley 50, the first pulley half 61 of the driven pulley 60 starts moving to the other side in the axial direction CL against the biasing force of the spring member 68. do. At this time, the first pulley half 61 is relatively rotated with respect to the output shaft 8 by the first torque cam mechanism 63 and relatively moved to the other side in the axial direction CL. When the first pulley half 61 rotates relative to the output shaft 8 , the groove cam mechanism 65 rotates the second pulley half 62 together with the first pulley half 61 . When a force in the rotational direction is applied to the second pulley half 62 by the grooved cam mechanism 65 , the second pulley half 62 rotates relative to the output shaft 8 by the second torque cam mechanism 64 while the second cam groove 641 is rotated. After relatively moving to one side in the axial direction CL along, relatively moving to the other side in the axial direction CL.

When the first cam pin 632 of the first torque cam mechanism 63 moves to the high-speed end of the first cam groove 631 (lower left end of the first cam groove 631 shown in FIG. 4A), the first pulley half 61 and the second The relative rotation of the pulley half 62 with respect to the output shaft 8 stops. That is, the first pulley half 61 and the second pulley half 62 (driven pulley 60 ) rotate together with the output shaft 8 . At this time, the first cam pin 632 of the second torque cam mechanism is positioned at the high-speed end of the second cam groove 641 (lower right end of the second cam groove 641 shown in FIG. 4B). When the continuously variable transmission 3 shifts from the high-speed running state to the low-speed running state, the operations opposite to those described above are executed.

According to this embodiment, the following effects can be obtained.
(1) A first pulley half 61 supported by the output shaft 8 so as to be rotatable relative to the output shaft 8 and movable in the axial direction CL, which is coaxially opposed to the first pulley half 61 and is rotatable relative to the output shaft 8 A driven pulley 60 (FIG. 1) to which torque output from the drive pulley 50 is transmitted via an endless V-belt 7. a spring member 68 that biases the first pulley half 61 toward the second pulley half 62; A 1-torque cam mechanism 63, a second torque cam mechanism 64 that regulates the relative movement and relative rotation of the second pulley half 62 with respect to the output shaft 8, and the first pulley half 61 and the second pulley half 62 in the axial direction CL. and a grooved cam mechanism 65 that permits relative movement of and prohibits relative rotation (FIG. 2).

With this configuration, even when the first pulley half 61 is rotated and relatively moved with respect to the output shaft 8 by the first torque cam mechanism 63 , the second torque cam mechanism 64 and the groove cam mechanism 65 operate to rotate the second pulley half 61 . Since the body 62 is rotated together with the first pulley half 61, the occurrence of a differential between the first pulley half 61 and the second pulley half 62 can be suppressed. Therefore, slippage of the V-belt 7 can be reduced. As a result, wear of the V-belt 7 can be suppressed, and reduction in torque transmission efficiency from the V-belt 7 to the driven pulley device 6 can be suppressed.

(2) The first torque cam mechanism 63 is provided in the first pulley half body 61 and is provided so as to rotate integrally with the first cam groove 631 extending in the direction C0 that is inclined with respect to the axial direction CL and the output shaft 8, The second torque cam mechanism 64 has a first cam pin 632 that engages with the first cam groove 631 (FIG. 4A), and the second torque cam mechanism 64 is provided on the second pulley half 62 and is inclined in the first direction C1 and A second cam groove 641 extending in a second direction C2 symmetrical to the first direction C1 with respect to the axial direction CL, and a second cam pin provided to rotate integrally with the output shaft 8 and engaged with the second cam groove 641. (first cam pin 632) (FIG. 4B), and the grooved cam mechanism 65 is provided in the first pulley half body 61 and is engaged with a third cam groove 651 extending in the axial direction CL and the third cam groove 651. and a mating third cam pin 652 (FIG. 5). As a result, the second torque cam mechanism 64 is formed in a shape capable of correcting misalignment that occurs in the second pulley half 62, so misalignment can be suppressed, and torque is transmitted from the V-belt 7 to the driven pulley device 6. Efficiency and durability of the V-belt 7 can be improved. For example, the second torque cam mechanism 64 causes the second pulley half 62 to relatively rotate while reciprocating in the axial direction CL, so misalignment can be corrected.

(3) The cam pin of the first torque cam mechanism 63 and the cam pin of the second torque cam mechanism 64 are configured by a common first cam pin 632 (FIGS. 2 and 3). As a result, the length of the driven pulley device 6 in the axial direction CL can be shortened, and the size of the driven pulley device 6 can be reduced.

(4) The first cam pin 632 of the first torque cam mechanism 63 and the second torque cam mechanism 64 projects radially outward from the output shaft 8 (FIG. 2). As a result, for example, the cam pin of the first torque cam mechanism 63, the cam pin of the second torque cam mechanism 64, or the first cam pin 632 common to the first and second torque cam mechanisms 63, 64 can be supported by the output shaft 8.

FIG. 6 is a skeleton diagram showing an example of a schematic configuration of a vehicle drive system to which a modification of the driven pulley device according to the embodiment of the invention is applied. A driven pulley device according to a modification of the present embodiment can be applied to, for example, a drive system of a two-wheeled vehicle. As shown in FIG. 6, the torque of the engine (ENG) 1A is input via the input shaft 4 to the continuously variable transmission 3A. Torque input to the drive pulley 50 of the continuously variable transmission 3A is transmitted to the driven pulley 60 via the endless V-belt 7 . The torque transmitted to driven pulley 60 is transmitted to output shaft 8 and gear mechanism 9 via clutch 69, thereby causing the vehicle to run. That is, in one example of the drive system of the vehicle according to the modification, torque transmission is turned on and off using the clutch 69 instead of the torque converter 2 (see FIG. 1).

A driven pulley device 6</b>A according to the modification of the present embodiment differs from the driven pulley device 6 in that the torque transmitted to the driven pulley 60 is transmitted to the output shaft 8 via the clutch 69 . In the following, differences from the driven pulley device 6 will be mainly described, and the same components as those of the driven pulley device 6 will be denoted by the same reference numerals, and description thereof will be omitted.

FIG. 7 is a diagram showing the main configuration of a driven pulley device 6A according to a modification of the present embodiment. As shown in FIG. 7, the driven pulley device 6A includes a driven pulley 60, an inner cylinder 66 and an outer cylinder 67, a spring member 68, a first torque cam mechanism (first cam mechanism) 63A, and a second torque cam mechanism ( A second cam mechanism) 64A, a grooved cam mechanism (third cam mechanism) 65, and a clutch 69 are provided.

The first torque cam mechanism 63A includes a first cam groove 631 and a first cam pin 632A that engages with the first cam groove 631. As shown in FIG. The second torque cam mechanism 64A includes a second cam groove 641 and a first cam pin 632A that engages with the second cam groove 641, which is common to the cam pin of the first torque cam mechanism 63A. The first cam pin 632A does not protrude from the output shaft 8, but is slidably supported by the first cam groove 631 and the second cam groove 641. As shown in FIG. That is, the first pulley half 61 (outer cylinder 67 ) and the second pulley half 62 (inner cylinder 66 ) are configured to rotate integrally when coupled with the output shaft 8 by the clutch 69 .

Clutch 69 is constituted by a centrifugal clutch. The clutch 69 has a clutch plate 661 fixed to the inner cylinder 66 and an outer plate 662 fixed to the output shaft 8 and arranged to face the clutch plate 661 . In the clutch 69, when the clutch plate 661 rotates, the clutch plate 661 is coupled to the outer plate 662 due to centrifugal force. As a result, torque is transmitted from the first pulley half 61 and the second pulley half 62 to the output shaft 8 via the clutch 69 .

The driven pulley device 6A according to the modified example of the present embodiment can be suitably applied to, for example, the drive system of a two-wheeled vehicle. In particular, by configuring the cam pin of the first torque cam mechanism 63A and the cam pin of the second torque cam mechanism 64A by the common first cam pin 632A, the size of the driven pulley device 6A can be reduced. It can also be suitably used for vehicles.

In the above embodiment, the grooved cam mechanism 65 has the third cam groove 651 provided in the outer cylinder 67 integrated with the first pulley half 61 and the third cam pin 652 that engages with the third cam groove 651. However, it may be configured by a third cam groove provided in the inner cylinder 66 integrated with the second pulley half 62 and a third cam pin engaged with the third cam groove. In this case, the third cam pin may be provided on the outer cylinder 67 so as to protrude from the outer cylinder 67 toward the inner cylinder 66 .

In the above embodiment, the spring member 68 is used to bias the first pulley half 61 toward one side (the second pulley half 62 side), but an elastic member such as rubber may be used to bias it. It may be configured to be hydraulically biased.

The above description is merely an example, and the present invention is not limited by the above-described embodiments and modifications as long as the features of the present invention are not impaired. It is also possible to arbitrarily combine one or more of the above embodiments and modifications, and it is also possible to combine modifications with each other.

Reference Signs List 1 engine 3 continuously variable transmission 4 input shaft 6 driven pulley device 7 V-belt (power transmission member) 8 output shaft 50 drive pulley 60 driven pulley 61 first pulley half body 62 second pulley half body 63 first torque cam mechanism (first cam mechanism) 64 second torque cam mechanism (second cam mechanism) 65 groove cam mechanism (third cam mechanism) 68 spring member (biasing member) 631 first cam groove 632 first cam pin 641 second cam groove 651 third cam groove 652 third cam pin

Claims (3)

A first pulley half supported to be rotatable relative to the rotating shaft and movable in the axial direction; a second pulley half supported by a driven pulley to which torque output from the drive pulley is transmitted via an endless power transmission member;
a biasing member that biases the first pulley half toward the second pulley half;
a first cam mechanism that regulates axial relative movement and relative rotation of the first pulley half with respect to the rotating shaft;
a second cam mechanism that regulates the relative movement and the relative rotation of the second pulley half with respect to the rotating shaft;
a third cam mechanism that allows the relative movement of the first pulley half and the second pulley half in the axial direction and prohibits the relative rotation ;
The first cam mechanism includes a first cam groove provided in the first pulley half body and extending in an axial direction and an inclined direction, and a first cam mechanism provided so as to rotate integrally with the rotating shaft. a first cam pin for engagement;
The second cam mechanism is provided in the second pulley half body and includes a second cam groove extending in a first direction inclined with respect to the axial direction and a second direction symmetrical with the first direction with respect to the axial direction; a second cam pin provided to rotate integrally with the shaft and engaged with the second cam groove;
The third cam mechanism is provided in one of the first pulley half and the second pulley half, and includes a third cam groove extending in the axial direction and a third cam pin engaged with the third cam groove. A driven pulley device comprising : In the driven pulley device according to claim 1,
A driven pulley device, wherein the first cam pin and the second cam pin are configured by a common cam pin. In the driven pulley device according to claim 1 or 2,
A driven pulley device, wherein the first cam pin and the second cam pin protrude radially outward from the rotating shaft.

Images