WO2015045847A1

WO2015045847A1 - Movable sheave support structure for stepless transmission, and driven pulley device with same

Info

Publication number: WO2015045847A1
Application number: PCT/JP2014/073767
Authority: WO
Inventors: 今井　隆敏; 真希橋本; 弘司米山
Original assignee: 株式会社エクセディ
Priority date: 2013-09-24
Filing date: 2014-09-09
Publication date: 2015-04-02
Also published as: JP2015064014A; CN105531504A; JP5791678B2

Abstract

A driven pulley for a stepless transmission is configured so that the driven pulley does not require grease, and consequently the slipping of a clutch, etc. is prevented and cost is reduced by a reduction in the number of seal parts. This movable sheave structure is provided with: a boss (5) for a stationary sheave; a boss (6) for a movable sheave; a cam mechanism (7); first and second resinous members (16, 17); and a resinous collar (21). The cam mechanism (7) is provided to the boss (5) for a stationary sheave and to the boss (6) for a movable sheave and applies axial thrust force to the boss (6) for a movable sheave. The first and second resinous members (16, 17) constitute slide sections located between the boss (5) for a stationary sheave and the boss (6) for a movable sheave. The resinous collar (21) constitutes the slide section of the cam mechanism (7).

Description

Movable sheave support structure for continuously variable transmission and driven pulley device having the same

The present invention relates to a movable sheave support structure, and in particular, a movable for a continuously variable transmission for supporting a movable sheave opposed to a fixed sheave and movable in an axial direction with respect to the fixed sheave on a rotating shaft. The present invention relates to a sheave support structure. The present invention also relates to a driven pulley device for a continuously variable transmission.

In a scooter type motorcycle or the like, a belt type continuously variable transmission is employed (for example, Patent Document 1). This continuously variable transmission includes a drive pulley fixed to the crankshaft of the engine, a driven pulley, and a belt that is stretched between these pulleys. Each of the drive pulley and the driven pulley has a fixed sheave and a movable sheave that is disposed to face the fixed sheave and is movable in the axial direction.

In the continuously variable transmission as described above, the driven pulley device has a driven pulley and a centrifugal clutch. As described above, the driven pulley has a fixed sheave and a movable sheave. The fixed sheave is fixed to one end of a cylindrical fixed sheave boss, and the movable sheave is similarly fixed to one end of the cylindrical movable sheave boss. The movable sheave boss is axially slidably disposed on the outer periphery of the fixed sheave boss.

Also, a cam mechanism is provided between the fixed sheave boss and the movable sheave boss. The cam mechanism includes a torque pin fixed to the fixed sheave boss and a cam groove formed on the movable sheave boss. The torque pin is slidably inserted into the cam groove of the movable sheave boss.

JP 2008-256122 A

As described above, the driven pulley of the continuously variable transmission has a sliding portion between the torque pin and the cam groove or on the inner peripheral surface of the movable sheave boss. Therefore, in the conventional driven pulley, grease is filled between the sliding portion and the fixed sheave boss and the output shaft that transmits torque to the rear wheel side.

Here, as a centrifugal clutch in a scooter type motorcycle, a dry type clutch is generally adopted. Therefore, when the grease filled in each sliding portion of the driven pulley leaks to the centrifugal clutch side, the clutch slips. The same applies to the case where grease leaks to the belt side, and slip occurs between the belt and each pulley.

Also, in the conventional driven pulley, a sealing member such as an O-ring or an oil seal is necessary so that the filled grease does not leak, which hinders cost reduction.

An object of the present invention is to eliminate the need for grease in a driven pulley of a continuously variable transmission, to suppress slippage of a clutch or the like, and to reduce costs by reducing seal parts.

A movable sheave support structure for a continuously variable transmission according to a first aspect of the present invention is arranged to face a fixed sheave and support a movable sheave that is movable in the axial direction with respect to the fixed sheave on a rotating shaft. The structure includes a cylindrical fixed sheave boss, a cylindrical movable sheave boss, a cam mechanism, a resin sheave sliding portion, and a resin cam sliding portion. The fixed sheave boss is fixed to the inner periphery of the fixed sheave. The movable sheave boss is fixed to the inner periphery of the movable sheave and is slidably disposed in the axial direction on the outer periphery of the fixed sheave boss. The cam mechanism is provided on the fixed sheave boss and the movable sheave boss, and applies axial thrust to the movable sheave boss. The resin sheave sliding part constitutes a sliding part between the fixed sheave boss and the movable sheave boss. The resin cam sliding portion constitutes the sliding portion of the cam mechanism.

Here, the movable sheave boss is slidably disposed on the outer periphery of the fixed sheave boss, and when the movable sheave boss slides in the axial direction, the distance between the movable sheave and the fixed sheave in the axial direction is increased. Be changed. Further, when the movable sheave boss slides with respect to the fixed sheave boss, an axial thrust is applied to the movable sheave boss by the cam mechanism.

In the above structure, the sliding part is composed of a resin sliding part. Therefore, it has the following effects compared to the conventional structure.

(1) In the sliding part, resin and metal or between resins slide, and seal members such as grease and oil seal are not required, reducing sliding resistance and smooth shifting. become.

(2) Sealing members such as O-rings and oil seals can be abolished, the number of parts can be reduced, the number of assembly steps can be reduced, and the cost can be reduced.

(3) Space for filling grease is not required, and it is possible to reduce the size and weight.

(4) The grease injection and wiping process and equipment for it can be abolished.

(5) The belt slippage due to the adhesion of grease to the sheave is eliminated, and the grease adhesion check process can be abolished.

(6) Since there is no grease leakage, it is not necessary to strictly manage the processing tolerance of the seal part.

(7) Easy to disassemble and reassemble.

The movable sheave support structure for a continuously variable transmission according to the second aspect of the present invention is the sliding structure between the fixed sheave boss and the movable sheave boss in the first side support structure. And a sheave sliding resin member that slides with at least one of both bosses.

Here, since the resin member that slides with at least one of the two bosses is disposed at the sliding portion between the two bosses, the effects such as smooth shifting can be obtained as described above.

In the movable sheave support structure for a continuously variable transmission according to the third aspect of the present invention, the resin member for sliding the sheave is fixed to each inner peripheral surface at both axial ends of the movable sheave boss.

The movable sheave support structure for a continuously variable transmission according to the fourth aspect of the present invention is the first side support structure, in which at least one of the fixed sheave boss and the movable sheave boss is a resin. It is formed and configured.

Here, since at least one of both bosses is formed of resin, it is not necessary to provide a resin member different from these both bosses.

The movable sheave support structure for a continuously variable transmission according to the fifth aspect of the present invention is the support structure according to any one of the first to fourth aspects, wherein the cam mechanism includes a plurality of torque pins and a plurality of cam grooves. It is configured. The plurality of torque pins are provided on the outer periphery of the fixed sheave boss so as to protrude radially outward. The plurality of cam grooves are formed in the movable sheave boss, and each of the plurality of torque pins is movably inserted. The cam sliding portion is disposed in a sliding portion between the plurality of torque pins and the cam groove, and has a cam resin member that slides with at least one of the torque pin and the cam groove.

Here, the torque pin slides while being guided by the cam groove. At this time, the torque pin smoothly slides in the cam groove by the cam resin member provided in these sliding portions. Therefore, the same effects as those described above, such as smooth shifting, can be obtained.

The movable sheave support structure for a continuously variable transmission according to the sixth aspect of the present invention is the support structure of the fifth side, wherein the cam resin member is provided on a portion that slides with the cam groove on the outer peripheral surface of the torque pin. Yes.

The movable sheave support structure for a continuously variable transmission according to the seventh aspect of the present invention further includes a spring and a cylindrical spring support member in the support structure of the fifth side. The spring is provided on the outer periphery of the movable sheave boss and biases the movable sheave toward the fixed sheave. The spring support member is disposed between the movable sheave boss and the spring and supports the spring. The cam resin member is formed in a cylindrical shape having a portion that slides with the cam groove on the outer peripheral surface of the torque pin and a portion that slides with the inner peripheral surface of the spring support member.

Here, since the torque pin is provided with the cylindrical cam resin member, when the torque pin slides in the cam groove, the head of the cam resin member slides with the inner peripheral surface of the spring support member. . Therefore, the sliding between the torque pin and the spring support member is also smooth.

The driven pulley device of the continuously variable transmission for motorcycles according to the eighth aspect of the present invention is a device for transmitting torque from the driving pulley via the belt, and includes a fixed sheave and a movable sheave that sandwich the belt, A cylindrical fixed sheave boss with one end fixed to the inner periphery of the fixed sheave, and a cylinder fixed to the inner periphery of the movable sheave and axially slidable on the outer periphery of the fixed sheave boss Between the fixed sheave boss and the movable sheave boss, and the fixed sheave boss and the movable sheave boss between the fixed sheave boss and the movable sheave boss. Resin sheave sliding portion constituting the sliding portion, resin cam sliding portion constituting the sliding portion of the cam mechanism, a spring for biasing the movable sheave toward the fixed sheave, and a fixed sheave boss Provided at the other end of Includes a centrifugal clutch dry, was.

In the present invention as described above, grease is not required in the driven pulley of the continuously variable transmission, and slippage of the clutch or the like can be suppressed, and cost reduction can be achieved by reducing seal parts.

Sectional drawing of the driven side action mechanism for continuously variable transmission provided with the movable sheave support structure by one Embodiment of this invention. Sectional drawing of the boss | hub for movable sheaves. The development of the outer peripheral surface of the movable sheave boss. Sectional drawing which shows other embodiment of a cam sliding part. Sectional drawing which shows other embodiment of a cam sliding part. FIG. 6 is a sectional view taken along line VI-VI in FIG. 5. Sectional drawing which shows other embodiment of a cam sliding part. VIII-VIII sectional view taken on the line of FIG.

[overall structure]
FIG. 1 shows a pulley device 1 on the driven side of a continuously variable transmission. Torque is transmitted to the driven pulley apparatus 1 via a belt 2 from a driving pulley apparatus (not shown) including a driving pulley. The driven pulley device 1 includes a fixed sheave 3 and a movable sheave 4, a cylindrical fixed sheave boss 5 and a movable sheave boss 6, a cam mechanism 7, a spring 8, and a dry centrifugal clutch 9, respectively. Have.

[Fixed sheave 3 and fixed sheave boss 5]
The fixed sheave 3 is a disk-shaped member and has a through hole 3a at the center. The surface of the fixed sheave 3 on the side facing the movable sheave 4 is formed in a tapered shape that is inclined so as to move away from the movable sheave 4 toward the outer peripheral side, and forms a V-groove together with the surface facing the movable sheave 4. Yes.

The fixed sheave boss 5 is formed in a cylindrical shape, and has a fixed flange 5a formed at one end (the right end in FIG. 1), a cylindrical portion 5b extending in the axial direction, and an engaging portion 5c formed at the other end. have.

The fixed flange 5a is formed to have a larger diameter than other portions, and is inserted into the through hole 3a of the fixed sheave 3 and fixed. The cylindrical portion 5b extends to the engaging portion 5c on the other end side with the same outer diameter, and has a plurality of (for example, three) holes 5d penetrating in the radial direction at the central portion in the axial direction. The engaging portion 5c is a portion to which the centrifugal clutch 9 is attached and is formed in an oval shape when viewed in the axial direction.

Note that an output shaft (not shown) for transmitting torque to the rear wheel side passes through the inner peripheral portion of the cylindrical portion 5b. A needle bearing 12, an oil seal 13, and a roller bearing 14 are provided between the inner peripheral surface of the cylindrical portion 5b and the output shaft.

[Moveable sheave 4 and movable sheave boss 6]
The movable sheave 4 is a disk-shaped member and has a through hole 4a at the center. The surface of the movable sheave 4 on the side facing the fixed sheave 3 is formed in a tapered shape that is inclined so as to move away from the fixed sheave 3 toward the outer peripheral side, and forms a V-groove together with the surface facing the fixed sheave 3. Yes.

As shown in FIGS. 1 to 3, the movable sheave boss 6 is formed in a cylindrical shape, and has a fixed flange 6a formed at one end (the right end in FIG. 1), and a cylindrical portion 6b extending in the axial direction. is doing. 2 shows only the movable sheave boss 6 and FIG. 3 is a developed view showing the outer peripheral surface thereof.

The fixed flange 6a has a larger diameter than the other part, and is inserted into the through hole 4a of the movable sheave 4 and fixed. The cylindrical portion 6b has the same outer diameter and extends to the other end, and has a plurality of (for example, three) cam grooves 6d extending in the axial direction.

At one end and the other end of the movable sheave boss 6, a first resin member (sheave sliding portion) 16 is provided in a portion where the cam groove 6 d is not formed (sliding portion with the fixed sheave boss 5). And a second resin member (sheave sliding portion) 17 are provided. Each of the

resin members

16 and 17 is formed in a cylindrical shape. The

resin members

16 and 17 are bonded to the inner peripheral surface of the movable sheave boss 6. The method of fixing the

resin members

16 and 17 to the movable sheave boss 6 is not limited to adhesion, and various configurations such as press-fitting and fitting of engagement protrusions and engagement recesses are employed. It is possible.

[Cam mechanism 7]
The cam mechanism 7 includes a plurality of torque pins 20, a cam groove 6d formed in the movable sheave boss 6, and a resin collar 21 (cam sliding portion).

The torque pin 20 is mounted in the hole 5d of the fixed sheave boss 5 and is formed to project radially outward from the outer peripheral surface of the fixed sheave boss 5. As shown in FIG. 3, the cam groove 6d is a groove that is long in the axial direction and is inclined at a predetermined angle with respect to the axial direction. The resin collar 21 is provided between the torque pin 20 and the wall surface of the cam groove 6d, and is provided so as to cover the entire outer peripheral surface of the portion protruding from the outer peripheral surface of the fixed sheave boss 5 of the torque pin 20. . The outer peripheral surface of the resin collar 21 slides with the wall surface of the cam groove 6d. The head of the resin collar 21 slides on the inner peripheral surface of the first support member 24 described later.

[Spring 8]
The spring 8 is provided between the centrifugal clutch 9 and the movable sheave 4 and biases the movable sheave 4 toward the fixed sheave 3. The spring 8 is supported by the first support member 24 and the second support member 25.

Specifically, the first support member 24 is formed in a cylindrical shape and disposed on the inner peripheral portion of the spring 8. A flange is formed at one end of the first support member 24 (end portion on the movable sheave side) to support one end of the spring 8. Further, like the first support member 24, the second support member 25 is formed in a cylindrical shape and disposed on the inner peripheral portion of the spring 8. A flange is formed at the other end (end portion on the centrifugal clutch side) of the second support member 25 to support the other end of the spring 8. One end of the second support member 25 is disposed so as to overlap in the radial direction on the outer periphery of the other end of the first support member 24. The first support member 24 and the second support member 25 are slidable in the axial direction.

[Centrifuge clutch 9]
The centrifugal clutch 9 has a drive plate 30, a plurality of weights 31, and a clutch housing 32. The centrifugal clutch 9 is fixed to the other end of the fixed sheave boss 5 by a lock nut 33.

The drive plate 30 is a disk-shaped plate having a hole 30a at the center. The hole 30a is formed in an oval shape and engages with the engaging portion 5c of the fixed sheave boss 5. Therefore, the drive plate 30 rotates integrally with the fixed sheave boss 5 and the fixed sheave 3. Further, the flange of the second support member 25 is in contact with the side surface of the drive plate 30. A stepped portion 30b is formed in the drive plate 30, and the flange of the second support member 25 is supported by the stepped portion 30b, thereby positioning the second support member 25 and the spring 8 supported thereby in the radial direction. Has been made.

Each of the plurality of weights 31 is rotatably attached to the drive plate 30 at one end in the circumferential direction. A friction material 34 is fixed to the outer peripheral surface of the weight 31. A return spring 35 is provided at the other end of the weight 31 to urge the weight 31 toward the inner peripheral side.

The clutch housing 32 is disposed so as to cover the weight 31 from the outer periphery. The friction material 34 of the weight 31 can be brought into and out of contact with the inner peripheral surface of the clutch housing 32.

A hole is formed in the center of the clutch housing 32, and a boss member 36 is fixed to the hole. A spline hole 36a is formed on the inner peripheral surface of the boss member 36, and the tip of the output shaft can be engaged with the spline hole 36a.

[Operation]
For example, when the groove width of both sheaves on the drive side becomes narrow, the winding diameter of the belt increases and the gear ratio shifts to the high speed side. In addition, when the groove width of both sheaves on the drive side is widened, the winding diameter of the belt is reduced and the gear ratio is shifted to the low speed side.

On the other hand, the groove width of the

sheaves

3 and 4 on the driven side operates in the opposite direction to that on the drive side as the groove width of the drive-side sheave changes. That is, when the engine speed increases and the centrifuge of the driving pulley device moves to the outer peripheral side, and the force for pressing the movable sheave toward the fixed sheave increases, the winding diameter of the belt increases. Then, on the driven side, the belt bites into the groove between the

sheaves

3 and 4, and the movable sheave 4 moves away from the fixed sheave 3 against the urging force of the cam mechanism 7 and the spring 8. For this reason, the groove width between the

sheaves

3 and 4 on both sides of the driven side is increased, and the winding diameter of the belt is reduced. Thereby, the gear ratio between the driving side and the driven side becomes small.

Conversely, when the engine speed decreases and the drive-side centrifuge returns to the inner peripheral side, the force pressing the movable sheave toward the fixed sheave becomes smaller. Then, the urging force of the cam mechanism 7 and the spring 8 is won, the groove width on the driven side is narrowed, and the winding diameter of the belt is increased. Along with this, the winding diameter of the belt on the driving side becomes smaller. As a result, the gear ratio between the driving side and the driven side increases, and the transmission torque to the rear wheel side (output side) increases.

The torque transmitted from the drive side to the driven side as described above is transmitted to the rear wheel side via the centrifugal clutch 9.

In the operation on the driven side described above, the movable sheave boss 6 and the fixed sheave boss 5 slide. Since these sliding parts are provided with the first and

second resin members

16 and 17 and the resin collar 21 is also provided on the sliding part of the cam mechanism 7, Sliding is smooth and gear shifting is performed smoothly.

Also, since the grease provided in the conventional structure is no longer necessary, seal members such as O-rings and oil seals can be eliminated, and further, belt slippage due to grease adhesion to the sheave can be eliminated, and the grease adhesion check process can be abolished. Further, the grease injection and wiping process and the equipment therefor can be abolished, and since there is no grease leakage, it is not necessary to strictly manage the processing tolerance of the seal portion. In addition, disassembly and reassembly are facilitated. Furthermore, a space for filling the grease becomes unnecessary, and the size and weight can be reduced.

[Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

(A) In the above-described embodiment, the first resin member 16 and the second resin member 17 are provided as the sheave sliding resin member. However, depending on the structure of the movable sheave boss, the resin member may be a single resin member.

(B) Although the first resin member 16 and the second resin member 17 are fixed to the inner peripheral surface of the movable sheave boss 6 in the above embodiment, they may be fixed to the outer peripheral surface of the fixed sheave boss 5.

(C) FIG. 4 shows another embodiment of the resin sheave sliding portion and the cam sliding portion. The movable sheave boss 46 shown in the embodiment of FIG. 4 is entirely formed by resin molding. That is, the movable sheave boss 6 and the first and

second resin members

16 and 17 in the embodiment shown in FIG. 1 are formed of an integral resin. In this case, since the portion (cam groove inner wall) that slides with the torque pin 20 is also made of resin, the resin collar 21 in the embodiment is not necessary.

(D) The shape and structure of the cam resin member (resin collar) provided in the cam mechanism 7 are not limited to the above embodiment.

(E) FIG. 5 and FIG. 6 show still another embodiment of the cam sliding portion. 6 is a cross-sectional view taken along line VI-VI in FIG. In this embodiment, three cam resin members 57 made of resin are fixed to the inner wall of the cam groove 6 d and a part of the inner peripheral surface of the movable sheave boss 56. That is, each cam resin member 57 has an arc portion 57a attached to the inner peripheral surface of the movable sheave boss 56, and a protruding portion 57b protruding from the arc portion 57a to the outer peripheral side.

The arc portion 57a extends in the circumferential direction over an angle range of 120 degrees, and the circumferential ends of the adjacent cam resin members 57 are in contact with each other. The protrusion 57b has a shape that covers the entire circumference of the inner wall surface of the cam groove 6d. And the groove | channel where the torque pin 20 slides is formed in the protrusion part 57b. In this case, the first resin member 16 ′ and the second resin member 17 ′ are shorter in the axial direction than in the embodiment.

(F) FIGS. 7 and 8 show still another embodiment of the sheave sliding portion and the cam sliding portion. 8 is a cross-sectional view taken along line VIII-VIII in FIG. The resin member 67 of this embodiment is formed by integrally forming the cam resin member 57 and the first and second resin members 16 ′ and 17 ′ in the embodiment shown in FIGS. 5 and 6. Also in this embodiment, three resin members 67 made of resin are fixed to the inner wall of the cam groove 6d and the inner peripheral surface of the movable sheave boss 66, as in the embodiment of FIGS. Each resin member 67 has an arc portion 67a attached to the inner peripheral surface of the movable sheave boss 66, and a protruding portion 67b protruding from the arc portion 67a to the outer peripheral side.

The circular arc portion 67a extends in the circumferential direction over an angle range of 120 degrees, and the circumferential ends of the adjacent resin members 67 are in contact with each other. In this embodiment, unlike the embodiment of FIGS. 7 and 8, the arc portion 67 a is provided over the entire inner peripheral surface of the movable sheave boss 66. The protruding portion 67b has a shape that covers the entire circumference of the inner wall surface of the cam groove 6d. And the groove | channel where the torque pin 20 slides is formed in the protrusion part 67b.

In this embodiment, the sheave sliding portion and the cam sliding portion can be configured by one (exactly one set of three) resin members 67.

The continuously variable transmission according to the present invention eliminates the need for grease in the driven pulley, suppresses slipping of the clutch and the like, and can reduce the cost by reducing seal parts.

DESCRIPTION OF SYMBOLS 1 Drive side action mechanism 2 Belt 3 Fixed sheave 4 Movable sheave 5

Fixed sheave bosses

6, 46, 56, 66 Movable sheave boss 6d Cam groove 7 Cam mechanism 8 Spring 9 Centrifugal clutches 16, 16 'First resin member (sheave Resin material for sliding)
17, 17 'Second resin member (resin member for sheave sliding)
20 Torque pin 21 Resin collar 57 Resin member 67 for cam Resin member

Claims

A movable sheave support structure for a continuously variable transmission for supporting a movable sheave arranged opposite to the fixed sheave and movable in the axial direction with respect to the fixed sheave on a rotating shaft,
A cylindrical fixed sheave boss fixed to the inner periphery of the fixed sheave;
A cylindrical movable sheave boss which is fixed to the inner peripheral portion of the movable sheave and is slidably disposed in the axial direction on the outer periphery of the fixed sheave boss;
A cam mechanism which is provided on the fixed sheave boss and the movable sheave boss, and applies axial thrust to the movable sheave boss;
A resin sheave sliding portion constituting a sliding portion between the fixed sheave boss and the movable sheave boss;
A resin cam sliding portion constituting the sliding portion of the cam mechanism;
A movable sheave support structure for a continuously variable transmission.
The sheave sliding portion is disposed in a sliding portion between the fixed sheave boss and the movable sheave boss, and has a sheave sliding resin member that slides with at least one of the both bosses. A movable sheave support structure for a continuously variable transmission as described in 1.
The movable sheave support structure for a continuously variable transmission according to claim 2, wherein the sheave sliding resin member is fixed to each inner peripheral surface of each axial end portion of the movable sheave boss.
The movable sheave support structure for a continuously variable transmission according to claim 1, wherein the sheave sliding portion is configured such that at least one of the fixed sheave boss and the movable sheave boss is formed of a resin. .
The cam mechanism is
A plurality of torque pins provided on the outer periphery of the fixed sheave boss and projecting radially outward;
A plurality of cam grooves formed on the movable sheave boss, wherein each of the plurality of torque pins is movably inserted;
Have
The cam sliding portion includes a cam resin member that is disposed in a sliding portion between the plurality of torque pins and the cam groove and slides with at least one of the torque pin and the cam groove.
The movable sheave support structure for a continuously variable transmission according to any one of claims 1 to 4.
The movable sheave support structure for a continuously variable transmission according to claim 5, wherein the resin member for cam is provided in a portion that slides with the cam groove on an outer peripheral surface of the torque pin.
A spring provided on an outer periphery of the movable sheave boss, and biasing the movable sheave toward the fixed sheave;
A cylindrical spring support member disposed between the movable sheave boss and the spring, for supporting the spring;
Further comprising
The cam resin member is formed in a cylindrical shape having a portion that slides with the cam groove on an outer peripheral surface of the torque pin and a portion that slides with an inner peripheral surface of the spring support member.
The movable sheave support structure for a continuously variable transmission according to claim 5.
A driven pulley device for a continuously variable transmission for a motorcycle in which torque is transmitted from a driving pulley via a belt,
A fixed sheave and a movable sheave sandwiching the belt;
A cylindrical fixed sheave boss, one end of which is fixed to the inner periphery of the fixed sheave;
A cylindrical movable sheave boss which is fixed to the inner peripheral portion of the movable sheave and is slidably disposed in the axial direction on the outer periphery of the fixed sheave boss;
A cam mechanism that is provided on the fixed sheave boss and the movable sheave boss, and that applies axial thrust to the movable sheave boss;
A resin sheave sliding portion constituting a sliding portion between the fixed sheave boss and the movable sheave boss;
A resin cam sliding portion constituting the sliding portion of the cam mechanism;
A spring for urging the movable sheave toward the fixed sheave;
A dry centrifugal clutch provided at the other end of the fixed sheave boss;
A driven pulley device for a continuously variable transmission comprising: