JP2017096352A - Pulley device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pulley device which inhibits falling of a movable sheave.SOLUTION: A pulley device 100 includes a fixed sheave 1, a fixed boss 2, a movable sheave 3, a movable boss 4, and a cam mechanism 5. The cam mechanism 5 is configured to convert rotation of the movable sheave 3 relative to the fixed sheave 1 into axial thrust force of the movable sheave 3. The cam mechanism 5 has a cam part 51 and a cam receiving part 52. The cam part 51 is disposed at a radial outer side of the movable boss 4 and rotates integrally with the movable sheave 3. The cam receiving part 52 rotates integrally with the fixed sheave 1.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a pulley apparatus.

  A scooter type motorcycle or the like employs a belt-type continuously variable transmission (for example, Patent Document 1). This continuously variable transmission includes a drive pulley device, a driven pulley device, and a belt. The belt is suspended between the drive pulley device and the driven pulley device.

  The driven pulley device holds the belt between the movable sheave and the fixed sheave. During sudden acceleration such as when starting, the belt may not be firmly clamped by the movable sheave and the fixed sheave. In order to prevent this, the pulley apparatus of Patent Document 1 includes a cam mechanism. This cam mechanism has a cam part and a cam receiving part. The cam portion is provided at the tip of a movable boss extending in the axial direction from the movable sheave, and the cam receiving portion is provided on the drive plate. When the movable sheave rotates relative to the fixed sheave, the cam mechanism converts the rotation into axial thrust and moves the movable sheave toward the fixed sheave. As a result, the belt is firmly held between the movable sheave and the fixed sheave.

JP 10-318342 A

  In the pulley apparatus as described above, there is a problem that a loss of power transmission occurs when the movable sheave is tilted by the load from the belt. Then, the subject of this invention is providing the pulley apparatus which can suppress the fall of a movable sheave.

  A pulley apparatus according to an aspect of the present invention includes a fixed sheave, a fixed boss, a movable sheave, a movable boss, and a cam mechanism. The fixed boss extends from the fixed sheave to the first side in the axial direction. The movable sheave is movable so as to approach and move away from the fixed sheave in the axial direction. The movable boss is disposed radially outside the fixed boss and extends from the movable sheave to the first side in the axial direction. The cam mechanism is configured to convert the relative rotation of the movable sheave relative to the fixed sheave into the axial thrust of the movable sheave. The cam mechanism has a cam portion and a cam receiving portion. A cam part is arrange | positioned at the radial direction outer side of a movable boss | hub, and rotates integrally with a movable sheave. The cam receiver rotates integrally with the fixed sheave.

  In the conventional pulley apparatus, the cam part is formed in the 1st side edge part of the axial direction of a movable boss | hub. The cam portion at the first side end in the axial direction of the movable boss engages with the cam receiving portion. For this reason, the internal peripheral surface of the 1st side edge part in which the cam part was formed among the internal peripheral surfaces of a movable boss | hub is not supported by the fixed boss | hub. On the other hand, in the pulley device according to the present invention, the cam portion is disposed on the radially outer side of the movable boss and is not formed at the first side end portion in the axial direction of the movable boss. For this reason, the axial direction length of the part which a fixed boss | hub and a movable boss contact | abut can be lengthened. As a result, the movable sheave can be prevented from falling.

  Preferably, the pulley device further includes a drive plate fixed to the first axial end portion of the fixed boss. The cam portion extends from the movable sheave to the first side in the axial direction. The cam receiving portion extends from the drive plate to the second side in the axial direction.

  Preferably, the pulley apparatus further includes an elastic body that biases the movable sheave toward the fixed sheave. The cam portion has a first cylindrical portion and a first flange portion. The first cylindrical portion extends in the axial direction on the radially outer side of the movable boss. The first flange portion extends radially outward from the first cylindrical portion. The elastic body biases the movable sheave through the first flange portion.

  According to this configuration, the elastic body biases the movable sheave through the first flange portion, and thus does not contact the movable sheave. For this reason, for example, when a spring is used as the elastic body, it is possible to prevent the movable sheave from being damaged by the spring.

  Preferably, the cam receiving portion includes a second cylindrical portion and a second flange portion. The second cylindrical portion extends in the axial direction. The second flange portion extends radially outward from the second cylindrical portion. The first axial side end portion of the elastic body is supported by the second flange portion.

  Preferably, the pulley device further includes a sliding member. The sliding member is attached to the inner peripheral surface of the movable boss and has a lower coefficient of friction than the movable boss.

  Preferably, the first axial side end of the movable boss is disposed closer to the first axial side than the first axial end of the cam portion.

  Preferably, a friction coefficient of a portion of the cam portion that comes into contact with the cam receiving portion is lower than a friction coefficient of the cam receiving portion.

  Preferably, the friction coefficient of the cam contact portion in contact with the cam portion is lower than the friction coefficient of the cam portion.

  According to the pulley device of the present invention, it is possible to suppress the falling of the movable sheave.

Side surface sectional drawing of a pulley apparatus. Schematic for demonstrating operation | movement of a cam mechanism.

  Hereinafter, embodiments of a pulley device according to the present invention will be described with reference to the drawings. The pulley device 100 according to the present embodiment is a driven-side pulley device 100. Torque is transmitted to the driven pulley device 100 from the driving pulley device (not shown) via the belt 101. The belt 101 is a member for transmitting torque.

  FIG. 1 is a side sectional view of the pulley device 100. In the following description, the rotation axis O means the rotation axis of the pulley device 100. The radial direction means the radial direction of a circle around the rotation axis O. The outer side in the radial direction means the side away from the rotation axis O in the radial direction, and the inner side in the radial direction means the side closer to the rotation axis O in the radial direction. The axial direction means a direction along the rotation axis O. The first side in the axial direction means the left side of FIG. 1, and the second side in the axial direction means the right side of FIG. The circumferential direction means the circumferential direction of a circle around the rotation axis O.

  As shown in FIG. 1, the pulley device 100 includes a fixed sheave 1, a fixed boss 2, a movable sheave 3, a movable boss 4, a cam mechanism 5, a spring (an example of an elastic body) 6, and a centrifugal clutch 7. And. The pulley apparatus 100 further includes a sliding member 8 and first and second seal members 9a and 9b. The first and second seal members 9a and 9b are specifically dust seals. In the following description, the first seal member 9a is referred to as a first dust seal 9a, and the second seal member 9b is referred to as a second dust seal 9b.

  The fixed sheave 1 is arranged so as to rotate about the rotation axis O. The central axis of the fixed sheave 1 is arranged substantially coaxially with the rotation axis O. The fixed sheave 1 is disposed on the second side of the movable sheave 3 in the axial direction. The fixed sheave 1 is fixed so as not to move in the axial direction.

  The fixed sheave 1 has a disk shape. The facing surface 11 of the fixed sheave 1 is inclined so as to move away from the movable sheave 3 as it goes outward in the radial direction. That is, the opposing surface 11 is inclined toward the second side in the axial direction toward the outer side in the radial direction. Note that the facing surface 11 of the fixed sheave 1 is a surface facing the movable sheave 3. That is, the facing surface 11 of the fixed sheave 1 faces the first side in the axial direction.

  The fixed boss 2 rotates integrally with the fixed sheave 1. In the present embodiment, the fixed boss 2 and the fixed sheave 1 are formed of a single member. Note that the fixed boss 2 and the fixed sheave 1 are formed by separate members, and may be integrally rotated by being fixed to each other. The fixed boss 2 is cylindrical and extends from the fixed sheave 1 to the first side in the axial direction. The central axis of the fixed boss 2 is arranged substantially coaxially with the rotation axis O.

  The centrifugal clutch 7 is attached to the first side end 21 of the fixed boss 2. Further, the fixed sheave 1 extends radially outward from the second side end 22 of the fixed boss 2. The first side end portion 21 is an end portion on the first side in the axial direction, and the second side end portion 22 is an end portion on the second side in the axial direction. The first side end portion 21 has a mounting surface extending in parallel with each other on the outer peripheral surface. Since the first side end portion 21 has an outer diameter smaller than that of other portions, a shoulder portion 23 is formed.

  The output shaft (not shown) extends in the axial direction inside the fixed boss 2. The output shaft is a shaft for transmitting torque to the rear wheels, for example. The output shaft and the fixed boss 2 are relatively rotatable. Note that bearings 102 and 103 are disposed between the output shaft and the fixed boss 2.

  The movable sheave 3 is arranged so as to rotate about the rotation axis O. The central axis of the movable sheave 3 is arranged substantially coaxially with the rotation axis O. The movable sheave 3 is arranged so as to move along the rotation axis O. That is, the movable sheave 3 is disposed so as to move in the axial direction. The movable sheave 3 moves toward and away from the fixed sheave 1 by moving in the axial direction. The movable sheave 3 is disposed on the first side of the fixed sheave 1 in the axial direction.

  The movable sheave 3 has a disk shape. The facing surface 31 of the movable sheave 3 is inclined so as to move away from the fixed sheave 1 as it goes outward in the radial direction. That is, the facing surface 31 is inclined toward the first side in the axial direction toward the outer side in the radial direction.

  The facing surface 31 of the movable sheave 3 is a surface facing the fixed sheave 1. That is, the facing surface 31 of the movable sheave 3 faces the second side in the axial direction. The facing surface 11 of the fixed sheave 1 and the facing surface 31 of the movable sheave 3 are opposed to each other with an interval. A V groove is formed by the facing surface 11 of the fixed sheave 1 and the facing surface 31 of the movable sheave 3. As the movable sheave 3 moves in the axial direction, the groove width of the V groove changes. A belt 101 is disposed in the V groove. The belt 101 is sandwiched between the facing surface 11 of the fixed sheave 1 and the facing surface 31 of the movable sheave 3.

  The movable sheave 3 has a plurality of first mounting holes 32. The first mounting holes 32 are arranged at intervals in the circumferential direction. Each first attachment hole 32 may or may not penetrate in the axial direction. Each first attachment hole 32 is formed in the inner periphery of the movable sheave 3.

  The movable boss 4 rotates integrally with the movable sheave 3. The movable boss 4 moves in the axial direction integrally with the movable sheave 3. In the present embodiment, the movable boss 4 and the movable sheave 3 are formed of a single member. Note that the movable boss 4 and the movable sheave 3 are formed by separate members, and may be integrally rotated and moved in the axial direction by being fixed to each other.

  The movable boss 4 is cylindrical and extends from the movable sheave 3 to the first side in the axial direction. That is, the movable boss 4 extends in a direction away from the fixed sheave 1. The central axis of the movable boss 4 is arranged substantially coaxially with the rotation axis O. The movable boss 4 is disposed on the radially outer side of the fixed boss 2. That is, the fixed boss 2 extends in the movable boss 4.

  The movable boss 4 is made of metal, for example. Specifically, the movable boss 4 is made of steel or aluminum alloy. More specifically, the movable boss 4 is formed of at least one selected from the group consisting of carbon steel and alloy steel.

  The sliding member 8 is attached to the inner peripheral surface of the movable boss 4. A metal layer and a sintered body layer may be interposed between the sliding member 8 and the movable boss 4. The sliding member 8 slides in the axial direction integrally with the movable boss 4. Further, the sliding member 8 rotates integrally with the movable boss 4. The sliding member 8 has a cylindrical shape. The inner peripheral surface of the sliding member 8 is in contact with the outer peripheral surface of the fixed boss 2.

  The sliding member 8 has a lower coefficient of friction than the movable boss 4. For example, the sliding member 8 is formed of at least one selected from the group consisting of a nylon resin, a fluororesin, a polyether ether ketone resin, and a polyphenylene sulfide resin. Thus, since the sliding member 8 has a smaller coefficient of friction than the movable boss 4, the sliding member 8 can slide smoothly on the fixed boss 2.

  The first and second dust seals 9 a and 9 b are attached to the inner peripheral surface of the movable boss 4. Specifically, the first dust seal 9 a is attached to the inner peripheral surface of the movable boss 4 at the first side end 41 of the movable boss 4. The second dust seal 9 b is attached to the inner peripheral surface of the movable boss 4 at the second side end portion 42 of the movable boss 4. The first side end portion 41 of the movable boss 4 is an end portion on the first side in the axial direction, and the second side end portion 42 of the movable boss 4 is an end portion on the second side in the axial direction. The first and second dust seals 9 a and 9 b are in contact with the outer peripheral surface of the fixed boss 2. For this reason, the space between the fixed boss 2 and the movable boss 4 is hermetically sealed by the first and second dust seals 9a and 9b, thereby preventing dust from entering. The cross-sectional shape of the first and second dust seals 9a and 9b is, for example, a rectangular shape. The first and second dust seals 9a and 9b are, for example, fiber composites. Specifically, the first and second dust seals 9a and 9b are configured by fusing resin fibers with a rubber elastic body.

  The cam mechanism 5 is configured to convert relative rotation of the movable sheave 3 with respect to the fixed sheave 1 into axial thrust of the movable sheave 3. That is, when the movable sheave 3 rotates at a faster speed than the fixed sheave 1, the cam mechanism 5 moves the movable sheave 3 toward the fixed sheave 1. The cam mechanism 5 has a cam portion 51 and a cam receiving portion 52.

  The cam portion 51 has a cylindrical shape and is disposed on the radially outer side of the movable boss 4. The central axis of the cam portion 51 is disposed substantially coaxially with the rotation axis O. The inner peripheral surface of the cam portion 51 is in contact with the outer peripheral surface of the movable boss 4. The cam portion 51 is detachably attached to the movable sheave 3 and rotates integrally with the movable sheave 3.

  The cam portion 51 extends from the movable sheave 3 to the first side in the axial direction. The first side tip in the axial direction of the cam portion 51 is disposed on the second side in the axial direction with respect to the first side tip in the axial direction of the movable boss. The cam portion 51 may be formed of the same material as the movable boss 4 or may be formed of a material different from that of the movable boss 4. For example, the cam portion 51 is made of metal. Specifically, the cam portion 51 is made of steel or aluminum alloy. More specifically, the cam portion 51 is formed of at least one selected from the group consisting of carbon steel and alloy steel.

  The cam portion 51 includes a first cylindrical portion 511, a first flange portion 512, and a plurality of first convex portions 513. The 1st cylindrical part 511, the 1st flange part 512, and the some 1st convex part 513 are formed of one member. The first cylindrical portion 511 has a cylindrical shape and is disposed on the radially outer side of the movable boss 4. The first cylindrical portion 511 extends in the axial direction along the movable boss 4. The inner peripheral surface of the first cylindrical portion 511 is in contact with the outer peripheral surface of the movable boss 4.

  The first flange portion 512 extends radially outward from the second side end portion in the axial direction of the first cylindrical portion 511. The first flange portion 512 is urged toward the second side in the axial direction by the spring 6. The first flange portion 512 is in contact with the movable sheave 3. Thus, since the 1st flange part 512 is urged | biased by the spring 6 at the movable sheave 3 side, it can prevent that the cam part 51 remove | deviates from the movable sheave 3. FIG. Note that the second side end surface of the spring 6 in the axial direction is in contact with the washer 104, but may be in direct contact with the first flange portion 512.

  Each first protrusion 513 protrudes to the second side in the axial direction. Each 1st convex part 513 is arrange | positioned at intervals in the circumferential direction. The first convex portion 513 is fitted into the first mounting hole 32. As a result, the cam portion 51 rotates integrally with the movable sheave 3. Further, the cam portion 51 can be detached from the movable sheave 3.

  Preferably, the cam part 51 further has a support part 514. The support portion 514 is cylindrical and extends in the axial direction. The support portion 514 extends from the first flange portion 512 to the first side in the axial direction. Between the support portion 514 and the first cylindrical portion 511, the second side end portion in the axial direction of the spring 6 is disposed.

  The cam receiver 52 rotates integrally with the fixed sheave 1. Specifically, the cam receiving portion 52 rotates integrally with the drive plate 71 that rotates integrally with the fixed sheave 1 and the fixed boss 2. The cam receiving portion 52 is detachably attached to the drive plate 71. The cam receiving portion 52 is cylindrical and extends in the axial direction. Specifically, the cam receiving portion 52 extends from the drive plate 71 to the second side in the axial direction. The central axis of the cam receiving portion 52 is disposed substantially coaxially with the rotation axis O.

  The cam receiver 52 is disposed outside the movable boss 4 in the radial direction. The cam receiving portion 52 is aligned with the cam portion 51 in the axial direction. The cam receiving portion 52 includes a second cylindrical portion 521, a second flange portion 522, and a plurality of second convex portions 523.

  The cam receiver 52 is made of metal, for example. Specifically, the cam receiving part 52 is made of steel or aluminum alloy. More specifically, the cam receiving portion 52 is formed of at least one selected from the group consisting of carbon steel and alloy steel. In addition, it is preferable that the part which contact | abuts the cam part 51 among the cam receiving parts 52 is formed with the material whose friction coefficient is lower than the cam part 51. FIG. For example, a portion of the cam receiving portion 52 that contacts the cam portion 51 is made of resin. Specifically, the portion of the cam receiving portion 52 that comes into contact with the cam portion 51 is at least one selected from the group consisting of nylon resin, fluororesin, polyether ether ketone resin, and polyphenylene sulfide resin. .

  The second cylindrical portion 521, the second flange portion 522, and the plurality of second convex portions 523 are integrally formed by one member. The second cylindrical portion 521 is cylindrical and extends in the axial direction. The second cylindrical portion 521 is disposed on the radially outer side of the movable boss 4.

  The second flange portion 522 extends outward in the radial direction from the first side end portion in the axial direction of the second cylindrical portion 521. The second flange portion 522 supports the first axial side end portion of the spring 6 in the axial direction. Since the spring 6 biases the second flange portion 522 toward the drive plate 71, the cam receiving portion 52 does not come off the drive plate 71. The first side end surface of the spring 6 in the axial direction is in contact with the washer 105, but may be in direct contact with the second flange portion 522.

  Each second protrusion 523 protrudes on the first side in the axial direction. Each 2nd convex part 523 is arrange | positioned at intervals in the circumferential direction. This 2nd convex part 523 fits in the 2nd attachment hole 711 formed in the drive plate 71 mentioned later. As a result, the cam receiving portion 52 rotates integrally with the drive plate 71. Further, the cam receiving portion 52 can be detached from the drive plate 71.

  The cam portion 51 and the cam receiving portion 52 are in contact with each other in the axial direction. Specifically, the first axial end portion of the cam portion 51 is in contact with the second axial end portion of the cam receiving portion 52. As shown in FIG. 2, the cam portion 51 has a cam surface 515. The cam surface 515 is inclined so as to face the rotation direction and to the first side in the axial direction. This cam surface 515 comes into contact with the cam receiving portion 52. The direction of rotation is the direction in which the movable boss 4 rotates when the vehicle moves forward.

  As shown in FIG. 1, the spring 6 urges the movable sheave 3 toward the fixed sheave 1 in the axial direction. That is, the spring 6 urges the movable sheave 3 toward the second side in the axial direction. Specifically, the spring 6 urges the movable sheave 3 to the fixed sheave 1 side via the first flange portion 512 of the cam portion 51. As a result, the fixed sheave 1 and the movable sheave 3 sandwich the belt 101. The spring 6 can be a coil spring, for example. The spring 6 is disposed on the radially outer side of the cam portion 51 and the cam receiving portion 52 so as to surround the cam portion 51 and the cam receiving portion 52.

  The centrifugal clutch 7 has a drive plate 71, a plurality of clutch shoes 72, and a clutch housing 73. The centrifugal clutch 7 is configured to transmit or block the rotation of the fixed sheave 1 and the movable sheave 3 to the output shaft. Specifically, the centrifugal clutch 7 is configured to transmit or block the rotation of the fixed boss 2 to the output shaft.

  The drive plate 71 is attached to the first side end 21 of the fixed boss 2. The drive plate 71 rotates integrally with the fixed boss 2. The drive plate 71 has a plurality of second mounting holes 711. The second mounting holes 711 are arranged at intervals in the circumferential direction. Each of the second mounting holes 711 may or may not penetrate in the axial direction. Each second attachment hole 711 is formed in the inner peripheral portion of the drive plate 71. The second convex portion 523 of the cam receiving portion 52 described above is fitted into the second mounting hole 711.

  The drive plate 71 has a disk shape and has a through hole 712 at the center. The through hole 712 is shaped to engage with the first side end 21 of the fixed boss 2. Specifically, the outer peripheral edge of the through hole 712 has substantially the same shape as the outer peripheral edge of the fixed boss 2.

  The drive plate 71 is made of metal. Specifically, the drive plate 71 is made of steel or aluminum alloy. More specifically, the drive plate 71 is at least one selected from the group consisting of carbon steel and alloy steel. The drive plate 71 is restricted from moving toward the second side in the axial direction by contacting the shoulder 23 of the fixed boss 2. Moreover, the drive plate 71 is restricted from moving in the axial direction to the first side by the retaining ring 106 attached to the first side end portion 21.

  Each clutch shoe 72 has a circumferential end attached to the drive plate 71 so as to be swingable. Each clutch shoe 72 has a friction material (not shown) on its outer peripheral surface. A return spring (not shown) is attached to the other end of each clutch shoe 72 so as to urge each clutch shoe 72 inward in the radial direction.

  The clutch housing 73 is disposed so as to cover each clutch shoe 72 from the outside in the radial direction. The clutch housing 73 is rotatable relative to the fixed boss 2. Specifically, the clutch housing 73 has a boss portion 731. A spline hole 7311 is formed in the boss portion 731. The output shaft can be spline-engaged with the spline hole 7311.

  When the centrifugal clutch 7 is in the transmission state, the friction material of each clutch shoe 72 is frictionally engaged with the inner peripheral surface of the clutch housing 73. Further, when the centrifugal clutch 7 is disconnected, the friction material of each clutch shoe 72 is separated from the inner peripheral surface of the clutch housing 73. The transmission state of the centrifugal clutch 7 means a state in which the centrifugal clutch 7 transmits the rotation of the fixed sheave 1 and the movable sheave 3 to the output shaft. The disconnected state of the centrifugal clutch 7 means a state in which the centrifugal clutch 7 does not transmit the rotation of the fixed sheave 1 and the movable sheave 3 to the output shaft.

  The pulley apparatus configured as described above operates as follows.

  In the pulley apparatus on the driving side, when the width of the groove formed by the fixed sheave and the movable sheave becomes narrow, the winding diameter of the belt 101 becomes large. That is, the belt 101 moves radially outward in the driving pulley apparatus.

  As shown in FIG. 1, in the driven pulley device 100, the width of the groove formed by the fixed sheave 1 and the movable sheave 3 operates in the opposite direction to the groove width in the driving pulley device. That is, when the belt 101 moves outward in the radial direction in the driving pulley apparatus, the belt 101 moves inward in the radial direction in the driven pulley apparatus 100.

  When the belt 101 moves inward in the radial direction, the movable sheave 3 moves away from the fixed sheave 1 against the biasing force of the spring 6. That is, the movable sheave 3 moves to the first side in the axial direction. As a result, the width of the groove between the fixed sheave 1 and the movable sheave 3 increases.

  Further, in the driving-side pulley device, when the width of the groove formed by the fixed sheave and the movable sheave increases, the winding diameter of the belt 101 decreases. That is, the belt 101 moves inward in the radial direction in the pulley apparatus on the driving side.

  When the belt 101 moves radially inward in the driving pulley apparatus, the belt 101 moves radially outward in the driven pulley apparatus 100. Then, the movable sheave 3 moves in a direction approaching the fixed sheave 1 by the urging force of the spring 6. As a result, the width of the groove between the fixed sheave 1 and the movable sheave 3 is reduced.

  Next, the operation of the cam mechanism 5 will be described. When rapidly accelerating, such as when starting, the movable sheave 3 rotates at a faster speed than the fixed sheave 1. That is, the movable sheave 3 rotates relative to the fixed sheave 1 in the rotation direction. Then, the movable sheave 3 rotates at a faster speed than the drive plate 71. As a result, the cam mechanism 5 applies axial thrust to the movable sheave 3, and the movable sheave 3 moves to the second side in the axial direction.

  Specifically, as shown in FIG. 2, the cam portion 51 rotates relative to the cam receiving portion 52 in the rotation direction. Then, the cam surface 515 receives a reaction force from the cam receiving portion 52 to the second side in the axial direction, and the cam portion 51 moves to the second side in the axial direction. As a result, the movable sheave 3 is pushed by the cam portion 51 and moves to the fixed sheave 1 side, and firmly holds the belt 101.

  As described above, the pulley apparatus 100 according to the present embodiment has the following characteristics.

  The cam portion 51 is disposed on the radially outer side of the movable boss 4, and is not formed on the first side end portion 41 in the axial direction of the movable boss 4. For this reason, the axial direction length of the part which the fixed boss | hub 2 and the movable boss | hub 4 contact | abut can be lengthened. For example, in this embodiment, the contact area between the inner peripheral surface of the sliding member 8 and the outer peripheral surface of the fixed boss 2 can be increased. As a result, the movable sheave 3 can be prevented from falling.

[Modification]
As mentioned above, although embodiment of this invention was described, this invention is not limited to these, A various change is possible unless it deviates from the meaning of this invention.

Modification 1
For example, in the above embodiment, the cam receiving portion 52 is detachably attached to the drive plate 71, but the cam receiving portion 52 may not be removable from the drive plate 71.

Modification 2
In the above embodiment, the cam portion 51 is attached to the movable sheave 3, but may be attached to the movable boss 4. Furthermore, the cam portion 51 is fixed to the movable sheave 3 or the movable boss 4 and may not be removed. The cam portion 51 may be formed integrally with the movable sheave 3 or the movable boss 4.

Modification 3
In the above-described embodiment, the portion of the cam receiving portion 52 that contacts the cam portion 51 is made of resin, but the contacting portion of the cam receiving portion 52 may be made of metal like the other portions. . In this case, it is preferable that a portion of the cam portion 51 that contacts the cam receiving portion 52 is formed of a material having a lower friction coefficient than the cam receiving portion 52. For example, the portion of the cam portion 51 that contacts the cam receiving portion 52 is preferably made of resin.

1: Fixed sheave 2: Fixed boss 21: First side end 3: Movable sheave 4: Movable boss 41: First side end 5: Cam mechanism 51: Cam portion 511: First cylindrical portion 512: First flange portion 52: Cam receiving portion 521: Second cylindrical portion 522: Second flange portion 6: Spring 8: Sliding member 71: Drive plate 100: Pulley device

Claims (8)

With fixed sheaves,
A fixed boss extending from the fixed sheave to the first side in the axial direction;
A movable sheave movable in an axial direction so as to approach and separate from the fixed sheave;
A movable boss disposed on the radially outer side of the fixed boss and extending from the movable sheave to the first side in the axial direction;
A cam mechanism configured to convert relative rotation of the movable sheave relative to the fixed sheave into an axial thrust of the movable sheave;
With
The cam mechanism includes a cam portion that is disposed on a radially outer side of the movable boss and rotates integrally with the movable sheave, and a cam receiving portion that rotates integrally with the fixed sheave.
Pulley device. A drive plate fixed to the first axial end of the fixed boss;
The cam portion extends from the movable sheave to the first side in the axial direction,
The cam receiving portion extends from the drive plate to the second side in the axial direction.
The pulley apparatus according to claim 1. An elastic body for urging the movable sheave toward the fixed sheave;
The cam portion includes a first cylindrical portion extending in the axial direction on the radially outer side of the movable boss, and a first flange portion extending radially outward from the first cylindrical portion,
The elastic body biases the movable sheave through the first flange portion.
The pulley apparatus according to claim 1 or 2. The cam receiving portion includes a second cylindrical portion extending in the axial direction, and a second flange portion extending radially outward from the second cylindrical portion,
An axial first side end portion of the elastic body is supported by the second flange portion.
The pulley apparatus according to claim 3. A sliding member attached to the inner peripheral surface of the movable boss and further having a lower coefficient of friction than the movable boss;
The pulley apparatus in any one of Claim 1 to 4. The axial first side end of the cam portion is disposed on the second axial side than the first axial end of the movable boss.
The pulley apparatus in any one of Claim 1 to 5. The cam portion has a lower friction coefficient of a portion contacting the cam receiving portion than the friction coefficient of the cam receiving portion.
The pulley apparatus in any one of Claim 1 to 6. The cam receiving portion has a lower friction coefficient of a portion contacting the cam portion than the friction coefficient of the cam portion.
The pulley apparatus in any one of Claim 1 to 6.

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