JP2020143758A - Centrifugal clutch and pulley device - Google Patents

Abstract

To improve a torque transmission capacity during low speed rotation.SOLUTION: A centrifugal clutch 10 includes an input member 2, a cam member 3, an output member 4, a clutch part 5, a weight member 6, and a cam mechanism 7. The cam member 3 has a first cam surface 31. The cam member 3 is disposed so as to be rotatable by torque input from the input member 2. The clutch part 5 transmits and shields torque between the cam member 3 and the output member 4. The weight member 6 rotates with the cam member 3 to receive a centrifugal force. The cam mechanism 7 moves the cam member 3 toward the clutch part 5 in an axial direction when the input member 2 and the cam member 3 rotate relative to each other. The first cam surface 31 converts the centrifugal force of the weight member 6 into a thrust force that moves the weight member 6 toward the clutch part 5.SELECTED DRAWING: Figure 1

Description

The present invention relates to a centrifugal clutch and a pulley device.

The centrifugal clutch is configured to transmit torque from the engine to the drive wheels when the rotation speed of the engine or the like exceeds a predetermined value. Such a centrifugal clutch is mainly used for a scooter type motorcycle or the like. For example, the centrifugal clutch disclosed in Patent Document 1 has a drive plate, a clutch shoe, and a housing. When the engine speed increases and the drive plate speed exceeds a predetermined value, the clutch shoe moves radially outward and frictionally engages with the housing. As a result, the torque from the drive plate is transmitted to the housing.

Japanese Unexamined Patent Publication No. 2012-229730

In recent years, a hybrid type motorcycle that uses not only an engine but also a motor as a drive source has been proposed. In such a hybrid type motorcycle, high torque can be output at low rotation speed. In addition, a motorcycle that can output high torque at low rotation speed has been proposed in order to reduce fuel consumption. With respect to a drive source capable of outputting high torque at such a low rotation speed, in a centrifugal clutch of the same size as the conventional one, the clutch shoe does not sufficiently frictionally engage with the housing at low rotation speed. By increasing the diameter of the centrifugal clutch, it is possible to transmit high torque at low rotation speeds, but there is a problem that the cost and weight of the centrifugal clutch increase.

An object of the present invention is to improve the torque transmission capacity at low rotation speed.

The centrifugal clutch according to the first aspect of the present invention includes an input member, a cam member, an output member, a clutch portion, a weight member, and a cam mechanism. Torque is input to the input member, and the input member is rotatably arranged. The cam member has a first cam surface. Torque is input from the input member of the cam member, and the cam member is rotatably arranged. The output members are rotatably arranged to output torque. The clutch portion is configured to transmit and disengage torque between the cam member and the output member. The weight member rotates together with the cam member and receives centrifugal force. The cam mechanism moves the cam member in the axial direction toward the clutch portion when the input member and the cam member rotate relative to each other. The first cam surface of the cam member converts the centrifugal force of the weight member into a thrust of the weight member toward the clutch portion.

According to this configuration, first, the torque input to the input member is transmitted to the cam member, and the cam member and the weight member rotate. The centrifugal force acting on the weight member due to this rotation is converted into a thrust toward the clutch portion by the first cam surface. As a result, the weight member presses the clutch portion, the clutch portion is in the clutch-on state, and torque is transmitted from the cam member to the output member. Here, since the input member and the cam member rotate relative to each other at low rotation, the cam member moves toward the clutch portion by the action of the cam mechanism. As a result, the thrust that the weight member presses against the clutch portion increases, so that the torque transmission capacity at low rotation speed can be improved. That is, it is possible to transmit high torque at low rotation speed without increasing the diameter of the centrifugal clutch more than necessary.

Preferably, the cam member has a restricting portion that is arranged on the outer side of the weight member in the radial direction and restricts the movement of the weight member outward in the radial direction.

Preferably, the input member has a pressure receiving surface that sandwiches the clutch portion with the weight member.

Preferably, the centrifugal clutch further comprises an elastic member disposed between the pressure receiving surface and the clutch portion.

Preferably, the input member has a drive plate into which torque is input and a support plate fixed to the drive plate. The cam member is arranged axially between the drive plate and the support plate.

Preferably, the cam mechanism has a second cam surface formed on the input member and a third cam surface formed on the cam member and facing the second cam surface.

Preferably, the clutch portion is a dry multi-plate clutch.

The pulley device according to the second aspect of the present invention includes a fixed sheave, a fixed boss, a movable sheave, a movable boss, and any of the above-mentioned centrifugal clutches. The fixed boss extends axially from the fixed sheave. The movable sheave is movably arranged so as to approach and separate from the fixed sheave in the axial direction. The movable boss extends axially from the movable sheave. The movable boss has a tubular shape and is arranged outside the fixed boss in the radial direction. Torque is input to the centrifugal clutch from the fixed boss.

According to the present invention, the torque transmission capacity at low rotation speed can be improved.

Sectional drawing which shows the pulley device. The schematic which shows the cam mechanism.

Hereinafter, an embodiment of the pulley device 100 having a centrifugal clutch according to the present invention will be described with reference to the drawings. In the following description, the axial direction means the direction in which the rotation axis O of the pulley device 100 extends. The radial direction means the radial direction of the circle centered on the rotation axis O, and the circumferential direction means the circumferential direction of the circle centered on the rotation axis O.

[Pulley device]
The pulley device 100 is used, for example, as a driven pulley device that constitutes a CVT (Continuously Variable Transmission). Torque is transmitted from the pulley device 100 on the drive side (not shown) via the belt 120. Then, the pulley device 100 transmits torque to the drive wheels (not shown) via the drive shaft (not shown).

The pulley device 100 includes a fixed sheave 101, a movable sheave 102, a fixed boss 103, a movable boss 104, and a centrifugal clutch 10. The pulley device 100 rotates about the rotation shaft O. Specifically, the pulley device 100 is attached to a drive shaft and is rotatable relative to the drive shaft.

[Fixed sheave and movable sheave]
The fixed sheave 101 and the movable sheave 102 approach and separate from each other in the axial direction. Specifically, the movable sheave 102 approaches and separates from the fixed sheave 101 by moving in the axial direction. The movable sheave 102 is urged toward the fixed sheave 101 by an urging member 108, for example, a coil spring. As the belt 120 moves inward in the radial direction, the movable sheave 102 moves so as to be separated from the fixed sheave 101 against the urging force of the urging member 108.

The fixed sheave 101 and the movable sheave 102 have disc surfaces that face each other in the axial direction. The disc surfaces of the fixed sheave 101 and the movable sheave 102 are configured so that the distance between them increases toward the outer side in the radial direction. The belt 120 is sandwiched between the disk surfaces of the fixed sheave 101 and the movable sheave 102. An opening is provided in the central portion of the fixed sheave 101 and the movable sheave 102.

[Fixed boss]
The fixed boss 103 extends from the fixed sheave 101 to the first side in the axial direction. The fixed boss 103 has a cylindrical shape. The fixed boss 103 rotates integrally with the fixed sheave 101. The fixed sheave 101 and the fixed boss 103 are each formed by separate members, and when they are fixed to each other, they rotate integrally. For example, the fixed sheave 101 and the fixed boss 103 are fixed to each other by welding or brazing. The fixed sheave 101 and the fixed boss 103 may be composed of one member.

A drive shaft extends inside the fixed boss 103. The drive shaft is a shaft for transmitting torque to the drive wheels. The drive shaft and the fixed boss 103 can rotate relative to each other. A needle bearing 105 and a ball bearing 106 are arranged between the drive shaft and the fixed boss 103.

[Movable boss]
The movable boss 104 extends from the movable sheave 102 to the first side in the axial direction. The movable boss 104 has a cylindrical shape. The movable boss 104 is arranged outside the fixed boss 103 in the radial direction. That is, the fixed boss 103 extends inside the movable boss 104. The movable boss 104 slides axially on the outer peripheral surface of the fixed boss 103.

The movable boss 104 rotates integrally with the movable sheave 102. Further, the movable boss 104 moves in the axial direction integrally with the movable sheave 102. The movable boss 104 and the movable sheave 102 are formed by separate members, and when they are fixed to each other, they integrally rotate and move in the axial direction. For example, the movable boss 104 and the movable sheave 102 are fixed to each other by welding or brazing. The movable boss 104 and the movable sheave 102 may be composed of one member. The movable boss 104 has a cylindrical shape.

[Centrifugal clutch]
The centrifugal clutch 10 has an input member 2, a cam member 3, an output member 4, a clutch portion 5, a plurality of weight members 6, and a plurality of cam mechanisms 7. The centrifugal clutch 10 is configured to transmit or shut off the torque from the fixed boss 103 to the drive shaft. The centrifugal clutch 10 is arranged on the first side of the fixed sheave 101 and the movable sheave 102 in the axial direction. The left side of FIG. 1 is the first side in the axial direction, and the right side of FIG. 1 is the second side in the axial direction.

[Input member 2]
The input member 2 is rotatably arranged around the rotation axis O. The input member 2 is attached to the tip portion 103a of the fixed boss 103. Torque from the fixed boss 103 is input to the input member 2, and the input member 2 rotates integrally with the fixed boss 103. A fixed sheave 101 is attached to the base end portion 103b of the fixed boss 103.

Since the tip portion 103a of the fixed boss 103 has a smaller outer diameter than the other portions, a step portion 103c is formed. The step portion 103c restricts the movement of the input member 2 to the second side in the axial direction. Further, the input member 2 is fastened to the tip portion 103a of the fixed boss 103 by a nut (not shown) or the like, and the movement of the input member 2 to the first side in the axial direction is restricted. As described above, the input member 2 is immovable in the axial direction.

The input member 2 has a drive plate 21 and a support plate 22. The drive plate 21 is attached to the fixed boss 103. Torque from the fixed boss 103 is input to the drive plate 21. The drive plate 21 has a disk shape.

The drive plate 21 has a plurality of first pillar portions 211 extending on the second side in the axial direction. The plurality of first pillar portions 211 are arranged at intervals in the circumferential direction. The first pillar portion 211 is, for example, cylindrical. The first pillar portion 211 has a screw hole 212 that opens on the second side in the axial direction.

The drive plate 21 has an annular protrusion 213 that projects to the second side in the axial direction. The annular protrusion 213 positions the urging member 108 from the inside in the radial direction. Further, the drive plate 21 has a plurality of positioning protrusions 214. The plurality of positioning protrusions 214 are arranged at intervals in the circumferential direction. The positioning protrusion 214 positions the disc spring 53 from the inside in the radial direction. The positioning protrusion 214 is formed at the base of the first pillar portion 211. In addition, a plurality of positioning protrusions 214 may be connected to each other to form an annular shape.

The drive plate 21 has a pressure receiving surface 215 facing the second side in the axial direction at the outer peripheral end portion. The pressure receiving surface 215 faces the weight member 6 side. The pressure receiving surface 215 is annular. The clutch portion 5 is sandwiched between the pressure receiving surface 215 and the weight member 6.

The support plate 22 is annular. The support plate 22 is arranged on the second side of the drive plate 21 in the axial direction. The support plate 22 has a plurality of second pillar portions 221 extending on the first side in the axial direction. The plurality of second pillar portions 221 are arranged at intervals in the circumferential direction. The tip surface of the second pillar portion 221 comes into contact with the tip surface of the first pillar portion 211.

The second pillar portion 221 has a through hole extending in the axial direction. The bolt 110 is screwed into the screw hole 212 of the first pillar portion 211 through the through hole. As a result, the support plate 22 is fixed to the drive plate 21. That is, the drive plate 21 and the support plate 22 rotate integrally with each other.

[Cam member 3]
The cam member 3 is rotatably arranged around the rotation axis O. Torque is input to the cam member 3 from the input member 2. Specifically, torque is input from the input member 2 to the cam member 3 via the cam mechanism 7 described later. The cam member 3 is arranged between the drive plate 21 and the support plate 22 in the axial direction. The cam member 3 is attached to the input member 2. The cam member 3 is movable in the axial direction with respect to the input member 2.

The cam member 3 has a plurality of first cam surfaces 31. The plurality of first cam surfaces 31 are arranged at intervals in the circumferential direction. The first cam surface 31 converts the centrifugal force of the weight member 6 into a thrust force of the weight member 6 toward the clutch portion 5. The first cam surface 31 faces the clutch portion 5. That is, the first cam surface 31 faces the first side in the axial direction. Further, the first cam surface 31 is inclined so as to face the first side in the axial direction and inward in the radial direction.

The cam member 3 has a regulation unit 32. The regulation unit 32 constitutes the outer wall of the cam member 3. The regulating portion 32 is arranged outside the weight member 6 in the radial direction. Then, the regulation unit 32 regulates the movement of the weight member 6 outward in the radial direction. In this way, the regulating unit 32 regulates the movement of the weight member 6 outward in the radial direction to prevent the excessive torque from being transmitted when the excessive torque is input to the centrifugal clutch 10. be able to.

The cam member 3 has a plurality of support portions 33 projecting to the first side in the axial direction. The plurality of support portions 33 are arranged at intervals in the circumferential direction. The support portion 33 slidably supports the inner disc 51 of the clutch portion 5, which will be described later, in the axial direction. The plurality of support portions 33 may be connected in an annular shape. That is, one cylindrical portion may be formed by connecting the plurality of support portions 33 to each other.

The cam member 3 has a plurality of accommodating portions 34 for accommodating the weight member 6. The plurality of accommodating portions 34 are arranged at intervals in the circumferential direction. The accommodating portion 34 is a recess formed in the cam member 3 and opens toward the first side in the axial direction. That is, the accommodating portion 34 is open toward the clutch portion 5. The accommodating portion 34 is defined by a first cam surface 31, an inner wall surface of the regulating portion 32, and the like.

The cam member 3 has a plurality of sliding portions 35. The plurality of sliding portions 35 are arranged at intervals in the circumferential direction. The second pillar portion 221 extends in the axial direction through the space between the sliding portions 35 adjacent to each other in the circumferential direction.

The sliding portion 35 is composed of a main body portion 36 of the cam member 3 and a separate member. The sliding portion 35 is attached to the main body portion 36 of the cam member 3, and rotates integrally with the main body portion 36 or moves in the axial direction. The sliding portion 35 is a portion for forming the cam mechanism 7 described later. The sliding portion 35 is made of, for example, resin. The main body 36 of the cam member 3 is made of, for example, steel or an aluminum alloy.

[Output member 4]
The output member 4 is rotatably arranged around the rotation axis O. The output member 4 outputs torque to the drive shaft. The output member 4 is arranged on the first side of the input member 2 in the axial direction.

The output member 4 has a disk portion 41, a cylindrical portion 42, and a boss portion 43. The cylindrical portion 42 extends from the outer peripheral end portion of the disc portion 41 to the second side in the axial direction. The cylindrical portion 42 is arranged outside the support portion 33 in the radial direction. The outer disc 52 of the clutch portion 5, which will be described later, is slidably attached to the cylindrical portion 42 in the axial direction.

The boss portion 43 extends from the inner peripheral end portion of the disc portion 41 to the second side in the axial direction. The boss portion 43 extends within the fixed boss 103. A spline hole 431 is formed in the boss portion 43. The drive shaft is spline-engaged with the spline hole 431.

[Clutch part 5]
The clutch portion 5 is configured to transmit and disengage torque between the cam member 3 and the output member 4. The clutch portion 5 is configured as a multi-plate clutch. That is, the clutch portion 5 has a plurality of inner discs 51 and a plurality of outer discs 52. The clutch portion 5 is a dry clutch.

The inner disc 51 is attached to the cam member 3. Specifically, the inner disc 51 is attached to the support portion 33 of the cam member 3. The inner peripheral end of the inner disk 51 is engaged with the support 33. The inner disc 51 is slidable in the axial direction. The pair of inner discs 51 arranged at both ends in the axial direction are urged in a direction away from each other by an urging member (not shown) such as a coil spring.

Of the plurality of inner discs 51, the end inner disc 51a, which is the inner disc 51 arranged on the first side in the axial direction, is in contact with the disc spring 53 (an example of an elastic member). The disc spring 53 is arranged between the pressure receiving surface 215 of the drive plate 21 and the end inner disc 51a in the axial direction.

The outer disc 52 is attached to the output member 4. Specifically, the outer disc 52 is attached to the cylindrical portion 42 of the output member 4. The outer peripheral end of the outer disc 52 is engaged with the cylindrical portion 42. The outer disc 52 is slidable in the axial direction. The outer disc 52 is arranged between the inner discs 51 in the axial direction. That is, in the axial direction, the inner disc 51 and the outer disc 52 are arranged alternately. Friction material is attached to both sides of the outer disc 52. In addition, the friction material may be attached to both sides of the inner disc 51 instead of the outer disc 52.

[Weight member 6]
The weight member 6 is arranged so as to rotate together with the cam member 3 and receive centrifugal force. Specifically, the weight member 6 is housed in the accommodating portion 34 of the cam member 3. The plurality of weight members 6 are arranged at intervals in the circumferential direction. The weight member 6 has a columnar shape. The weight member 6 is arranged so that its outer peripheral surface is in contact with the first cam surface 31. Therefore, the weight member 6 can move to the outer side in the radial direction and to the second side in the axial direction when a centrifugal force acts. The weight member 6 is configured to press the clutch portion 5 toward the first side in the axial direction. When an excessive torque is input, the weight member 6 moves radially outward and comes into contact with the regulating portion 32. When the weight member 6 comes into contact with the regulation portion 32 in this way, no further pressing force is applied to the clutch portion 5.

The weight member 6 has a main body portion 61 and a cover portion 62. The main body 61 is columnar. The cover portion 62 is configured to cover the outer peripheral surface of the main body portion 61. The cover portion 62 has a cylindrical shape. The main body 61 is made of metal or the like. For example, the main body 61 is made of iron, steel, non-ferrous metal, or the like. On the other hand, the cover portion 62 is formed of, for example, resin or aluminum.

[Cam mechanism 7]
The cam mechanism 7 is configured to move the cam member 3 in the axial direction toward the clutch portion 5 when the input member 2 and the cam member 3 rotate relative to each other. As shown in FIG. 2, the cam mechanism 7 has a first cam portion 71 and a second cam portion 72.

The first cam portion 71 functions when the torque from the input member 2 is transmitted to the cam member 3 and the input member 2 and the cam member 3 rotate relative to each other at the time of starting or accelerating. The first cam portion 71 moves the cam member 3 in the axial direction toward the clutch portion 5 when the input member 2 and the cam member 3 rotate relative to each other. The first cam portion 71 has a second cam surface 71a and a third cam surface 71b.

The second cam surface 71a is formed on the support plate 22 of the input member 2. The second cam surface 71a is composed of side surfaces of the second pillar portion 221 facing in the circumferential direction. The second cam surface 71a is inclined so as to face the rotation direction and the first side in the axial direction. The rotation direction is the direction in which the centrifugal clutch 10 rotates when the motorcycle advances. The right direction in FIG. 2 is the rotation direction.

The third cam surface 71b extends so as to face the second cam surface 71a. The third cam surface 71b is formed on the cam member 3. Specifically, the third cam surface 71b is formed on the sliding portion 35 of the cam member 3. The third cam surface 71b is inclined so as to face the opposite direction of the rotation direction and the second side in the axial direction. The distance between the third cam surface 71b and the second cam surface 71a is narrowed toward the first side in the axial direction. The distance between the third cam surface 71b and the second cam surface 71a may be substantially constant in the axial direction. The length of the third cam surface 71b is shorter than the length of the second cam surface 71a.

The second cam portion 72 functions when torque is transmitted from the cam member 3 to the input member 2 at the time of deceleration or kick start, and the input member 2 and the cam member 3 rotate relative to each other. The second cam portion 72 moves the cam member 3 in the axial direction toward the clutch portion 5 when the input member 2 and the cam member 3 rotate relative to each other. The second cam portion 72 has a fourth cam surface 72a and a fifth cam surface 72b.

The fourth cam surface 72a is formed on the support plate 22 of the input member 2. The fourth cam surface 72a is composed of side surfaces of the second pillar portion 221 facing in the circumferential direction. The fourth cam surface 72a is inclined so as to face the opposite direction of the rotation direction and the first side in the axial direction.

The fifth cam surface 72b extends so as to face the fourth cam surface 72a. The fifth cam surface 72b is formed on the cam member 3. Specifically, the fifth cam surface 72b is formed on the sliding portion 35 of the cam member 3. The fifth cam surface 72b is inclined so as to face the rotation direction and the second side in the axial direction. The distance between the fifth cam surface 72b and the fourth cam surface 72a is narrowed toward the first side in the axial direction. The distance between the fifth cam surface 72b and the fourth cam surface 72a may be substantially constant in the axial direction. The length of the fifth cam surface 72b is shorter than the length of the fourth cam surface 72a.

[Operation of centrifugal clutch 10]
Next, the operation of the centrifugal clutch 10 will be described. First, when stopped, the centrifugal clutch 10 is in the clutch-off state. That is, the centrifugal clutch 10 does not transmit torque between the fixed boss 103 and the drive shaft. Specifically, the transmission of torque is cut off at the clutch portion 5 of the centrifugal clutch 10. Therefore, the motorcycle can be easily pushed and moved.

When starting, torque is input to the input member 2 from the fixed boss 103. Here, since the input member 2 rotates relative to the cam member 3, the cam member 3 moves toward the clutch portion 5. Specifically, when the input member 2 rotates relative to the cam member 3, the second cam surface 71a and the third cam surface 71b come into contact with each other, and the first cam portion 71 of the cam mechanism 7 operates. As a result, the cam member 3 moves toward the clutch portion 5.

When the torque from the input member 2 is transmitted to the cam member 3 and the cam member 3 rotates, the weight member 6 rotating together with the cam member 3 moves radially outward due to centrifugal force. Here, the weight member 6 moves radially outward along the first cam surface 31 to move toward the clutch portion 5 and press the clutch portion 5. As a result, the clutch portion 5 is in the clutch-on state. As described above, the cam member 3 is moved to the clutch portion 5 side by the cam mechanism 7. Since the pressing force of the clutch portion 5 by the weight member 6 is increased by the amount of movement of the cam member 3 in the axial direction, the torque transmission capacity of the clutch portion 5 at low rotation is improved.

When the clutch portion 5 is turned on, the torque from the cam member 3 is transmitted to the output member 4. Then, the output member 4 outputs torque to the drive shaft. In this way, the torque input to the centrifugal clutch 10 is transmitted to the drive shaft in the order of the drive plate 21, the support plate 22, the cam member 3, the weight member 6, the clutch portion 5, and the output member 4. That is, the torque input to the centrifugal clutch 10 is once directed to the second side in the axial direction and then transmitted to the first side in the axial direction.

On the other hand, when the accelerator is loosened to decelerate or the engine is started by a kick starter, the cam member 3 rotates relative to the input member 2 in the rotational direction. As a result, the fourth cam surface 72a and the fifth cam surface 72b come into contact with each other, and the second cam portion 72 of the cam mechanism 7 operates. Then, the cam member 3 moves to the clutch portion 5 side, and the pressing force of the clutch portion 5 by the weight member 6 increases.

[Modification example]
Although the embodiments of the present invention have been described above, the present invention is not limited thereto, and various modifications can be made without departing from the spirit of the present invention.

For example, in the above embodiment, the cam mechanism 7 has two cam portions, a first cam portion 71 and a second cam portion 72, but the cam mechanism 7 does not have the second cam portion 72. You may.

2 Input member 21 Drive plate 22 Support plate 3 Cam member 31 Cam surface 32 Regulator 4 Output member 5 Clutch 6 Weight member 7 Cam mechanism 71a 2nd cam surface 71b 3rd cam surface 100 Pulley device 101 Fixed sheave 102 Movable sheave 103 Fixed boss 104 Movable boss

Claims (8)

An input member to which torque is input and is rotatably arranged,
A cam member having a first cam surface, to which torque is input from the input member, and which is rotatably arranged.
An output member that is rotatably arranged and outputs torque,
A clutch portion configured to transmit and disconnect torque between the cam member and the output member,
A weight member that rotates with the cam member and receives centrifugal force,
A cam mechanism that moves the cam member in the axial direction toward the clutch portion when the input member and the cam member rotate relative to each other.
With
The first cam surface of the cam member converts the centrifugal force of the weight member into a thrust of the weight member toward the clutch portion.
Centrifugal clutch.
The cam member is arranged outside the weight member in the radial direction and has a regulating portion that regulates the movement of the weight member outward in the radial direction.
The centrifugal clutch according to claim 1.
The input member has a pressure receiving surface that sandwiches the clutch portion with the weight member.
The centrifugal clutch according to claim 1 or 2.
An elastic member arranged between the pressure receiving surface and the clutch portion is further provided.
The centrifugal clutch according to claim 3.
The input member has a drive plate into which torque is input and a support plate fixed to the drive plate.
The cam member is arranged between the drive plate and the support plate in the axial direction.
The centrifugal clutch according to any one of claims 1 to 4.
The cam mechanism has a second cam surface formed on the input member and a third cam surface formed on the cam member and facing the second cam surface.
The centrifugal clutch according to any one of claims 1 to 5.
The clutch portion is a dry multi-plate clutch.
The centrifugal clutch according to any one of claims 1 to 6.
Fixed sheave and
A fixed boss extending axially from the fixed sheave,
A movable sheave that is movablely arranged so as to approach and separate from the fixed sheave in the axial direction.
A tubular movable boss that extends axially from the movable sheave and is arranged outside the fixed boss in the radial direction.
The centrifugal clutch according to any one of claims 1 to 6, wherein torque is input from the fixed boss.
Pulley device with.

Images