JP7434661B2 - pulley device - Google Patents

Description

The present invention relates to a pulley device.

Conventionally, vehicles such as scooter-type saddle-riding vehicles are equipped with belt-type continuously variable transmissions. In continuously variable transmissions, a pulley device driven by a belt is provided. The pulley device includes a fixed sheave, a movable sheave, a spring that urges the movable sheave toward the fixed sheave, and a spring seat that rotates together with the fixed sheave and supports one end of the spring (for example, Patent Document (see 1). In Patent Document 1, the movable sheave includes a disc-shaped sheave portion and a movable sheave shaft portion extending in the axial direction from the sheave portion, and controls relative rotation of the movable sheave with respect to the spring seat in the axial direction of the movable sheave. A cam mechanism is provided that converts thrust into thrust. The belt is sandwiched between the movable sheave and the fixed sheave by the spring load and the thrust of the cam mechanism.

JP2017-61967A

By the way, in the cam mechanism of the conventional pulley device described above, torque due to relative rotation of the movable sheave acts as a load.
The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to reduce the load acting on the cam mechanism in a pulley device.

The pulley device includes a fixed sheave, a movable sheave that is movable toward and away from the fixed sheave in the axial direction, a spring that urges the movable sheave toward the fixed sheave in the axial direction, and a spring that biases the movable sheave toward the fixed sheave in the axial direction. a cylindrical member that rotates together with the sheave; the movable sheave includes a disc-shaped sheave portion; and a movable sheave shaft portion extending in the axial direction from the sheave portion; In a pulley device provided with a cam mechanism that converts relative rotation of a movable sheave into an axial thrust force of the movable sheave, the movable sheave shaft section has a cylindrical outer shaft extending in the axial direction with respect to the sheave section. and an inner shaft portion extending in the axial direction from the sheave portion inside the outer shaft portion, and the cylindrical member includes a cylindrical member disposed between the outer shaft portion and the inner shaft portion. The cam mechanism is characterized in that the cam mechanism is provided on both an inner circumferential side and an outer circumferential side of the cylindrical portion.

Further, in the above configuration, the cam mechanism includes an inner cam receiving part provided on the inner circumferential surface of the cylindrical part, and an inner cam provided on the inner shaft part and abutting on the inner cam receiving part. An inner cam mechanism may be provided.
In the above configuration, the cam mechanism includes an outer cam receiving portion provided on the outer peripheral surface of the cylindrical portion, and an outer cam provided on the outer shaft portion and abutting the outer cam receiving portion. An outer cam mechanism may also be provided.

Further, in the above configuration, the movable sheave is movable in an opening direction in which the movable sheave moves away from the fixed sheave and in a closing direction in which it approaches the fixed sheave, and the inner cam mechanism The thrust may be generated during movement in one of the opening direction and the closing direction, and the outer cam mechanism may generate the thrust during movement in the other of the opening direction and the closing direction.

Further, in the above configuration, a plurality of the inner cam receivers are provided in the circumferential direction on the inner circumferential surface, and a plurality of the outer cam receivers are provided in the circumferential direction on the outer circumferential surface, and the inner cam receivers are provided in a plurality in the circumferential direction on the outer circumferential surface. The outer cam receiving portions may be arranged out of phase with each other in the circumferential direction of the cylindrical portion.
In the above configuration, the inner cam receiving part and the outer cam receiving part are cam receiving parts, the inner cam and the outer cam are cams, and in the inner cam mechanism, the cam receiving part and the outer cam receiving part are cam receiving parts. One of the cams is inclined with respect to the axial direction of the movable sheave shaft, and in the outer cam mechanism, the cam receiving portion and the other of the cams are provided with an inclination with respect to the axial direction of the movable sheave shaft. It may also be provided.

Furthermore, in the above configuration, the state of the inclination of the inner cam mechanism and the state of inclination of the outer cam mechanism may be different.
Furthermore, in the above configuration, the cylindrical member may be a spring seat that supports one end of the spring.
In the above configuration, the spring seat includes a flange portion extending radially outward from the cylindrical portion and supporting the one end of the spring, the spring being a coil spring, and the flange portion extending radially outward from the cylindrical portion and supporting the movable spring. The sheave shaft portion may be arranged radially inside the spring.
Further, in the above configuration, the spring seat is made of resin, and the fixed sheave includes a fixed sheave part that faces the sheave part, and a fixed sheave shaft part that extends in the axial direction from the fixed sheave part. The movable sheave has a self-lubricating property, the movable sheave shank fits into the fixed sheave shank, and the movable sheave is disposed between the movable sheave shank and the fixed sheave shank. It may be supported on bearings made of material.

The pulley device includes a fixed sheave, a movable sheave that is movable toward and away from the fixed sheave in the axial direction, a spring that urges the movable sheave toward the fixed sheave in the axial direction, and a fixed sheave that is integrated with the fixed sheave. The movable sheave includes a disk-shaped sheave portion and a movable sheave shaft portion extending in the axial direction from the sheave portion, and the movable sheave is configured to control relative rotation of the movable sheave with respect to the cylindrical member. A cam mechanism is provided that converts the thrust force in the axial direction of the sheave. The cylindrical member includes a cylindrical portion disposed between the outer axial portion and the inner axial portion, and the cam mechanism is arranged on both the inner and outer peripheral sides of the cylindrical portion. established in
According to this configuration, since the cam mechanism is provided on both the inner circumferential side and the outer circumferential side of the cylindrical portion of the cylindrical member, the load acting on the cam mechanism is effectively dispersed and the load is reduced. More cam mechanisms can be arranged in the radial direction than in a structure with one layer of cam mechanisms.

Further, in the above configuration, the cam mechanism includes an inner cam receiving part provided on the inner circumferential surface of the cylindrical part, and an inner cam provided in the inner shaft part and contacting the inner cam receiving part. may be provided.
According to this configuration, the inner cam mechanism can be provided compactly by the inner cam receiving portion on the inner peripheral surface of the cylindrical portion and the inner cam of the inner shaft portion provided inside the cylindrical portion.
Furthermore, in the above configuration, the cam mechanism includes an outer cam receiving part provided on the outer circumferential surface of the cylindrical part, and an outer cam provided on the outer shaft part and contacting the outer cam receiving part. It's good to be prepared.
According to this configuration, the outer cam mechanism can be provided compactly by the outer cam receiving part on the outer peripheral surface of the cylindrical part and the outer cam of the outer shaft part provided on the outside of the cylindrical part.

Furthermore, in the above configuration, the movable sheave is movable in the opening direction, in which it moves away from the fixed sheave, and in the closing direction, in which it approaches the fixed sheave, and the inner cam mechanism moves the movable sheave in the opening and closing directions. The thrust force may be generated during one movement, and the outer cam mechanism may generate thrust force during the other movement in the opening direction and the closing direction.
According to this configuration, the cam mechanism is provided separately into the cam mechanism that corresponds to the movement of the movable sheave in the opening direction and the cam mechanism that corresponds to the movement of the movable sheave in the closing direction, so that the load acting on the cam mechanism is direction becomes constant. As a result, the number and shape of the cam mechanisms can be optimized to correspond to the load, so the load can be reduced and durability can be improved, and it is also possible to cope with higher loads.

Furthermore, in the above configuration, a plurality of inner cam receivers are provided in the circumferential direction on the inner circumferential surface, and a plurality of outer cam receivers are provided in the circumferential direction on the outer circumferential surface, and the inner cam receiver and the outer cam receiver are provided in a plurality in the circumferential direction. may be arranged so as to be out of phase with each other in the circumferential direction of the cylindrical portion.
According to this configuration, the load acting on the inner cam receiving part and the outer cam receiving part can be effectively distributed to a plurality of locations in the circumferential direction of the cylindrical part, and the load can be reduced.
Further, in the above configuration, the inner cam receiving part and the outer cam receiving part are cam receiving parts, the inner cam and the outer cam are cams, and in the inner cam mechanism, one of the cam receiving part and the cam is movable. The movable sheave shaft may be provided to be inclined relative to the axial direction of the sheave shaft, and in the outer cam mechanism, the other of the cam receiving portion and the cam may be provided to be inclined relative to the axial direction of the movable sheave shaft.
According to this configuration, the portions of the cam receiving portion and the cam that are inclined with respect to the axial direction of the movable sheave shaft portion can be distributed and provided in the inner cam mechanism and the outer cam mechanism. Therefore, the load on the cam mechanism can be reduced.

Furthermore, in the above configuration, the state of inclination of the inner cam mechanism and the state of inclination of the outer cam mechanism may be different.
According to this configuration, the characteristics of the thrust generated by the cam mechanism can be made different between those generated by the inner cam mechanism and those generated by the outer cam mechanism.
Furthermore, in the above configuration, the cylindrical member may be a spring seat that supports one end of the spring.
According to this configuration, the cam mechanism can be provided with a simple structure using the spring seat.
Further, in the above configuration, the spring seat includes a flange portion extending radially outward from the cylindrical portion and supporting one end of the spring, the spring is a coil spring, and the cylindrical portion and the movable sheave shaft portion are connected to the spring. It may be arranged radially inward.
According to this configuration, the cam mechanism constituted by the cylinder portion and the movable sheave shaft portion can be provided compactly by utilizing the space inside the spring in the radial direction.
Further, in the above configuration, the spring seat is made of resin, and the fixed sheave includes a fixed sheave part facing the sheave part, and a fixed sheave shaft part extending in the axial direction from the fixed sheave part, and the fixed sheave is movable. The sheave may have a movable sheave shaft that fits into a fixed sheave shaft, and the movable sheave may be supported by a bearing made of a self-lubricating material that is disposed between the movable sheave shaft and the fixed sheave shaft. .
According to this configuration, since the spring seat constituting the cam mechanism is made of resin, lubricant such as grease for the cam mechanism can be omitted. Furthermore, since the movable sheave shaft is supported by the fixed sheave shaft via a bearing made of a self-lubricating material, it is possible to omit lubricant such as grease for the movable sheave shaft.

FIG. 1 is a left side view of a motorcycle according to an embodiment of the present invention. FIG. 2 is a sectional view of the power unit. FIG. 3 is a sectional view of the driven pulley device and clutch mechanism. FIG. 4 is an exploded perspective view of the driven pulley device. FIG. 5 is a perspective view showing the cam mechanism. FIG. 6 is a sectional view showing a state in which the movable sheave has moved in the opening direction. FIG. 7 is a sectional view of the driven pulley device and clutch mechanism in the second embodiment. FIG. 8 is an enlarged cross-sectional view of the structure that receives one end in FIG. 7. FIG. 9 is a perspective view showing a cam mechanism in the third embodiment. FIG. 10 is a cross-sectional view of the cam mechanism viewed in the axial direction.

Hereinafter, one embodiment of the present invention will be described with reference to the drawings. In addition, in the description, directions such as front, rear, left, right, and top and bottom are the same as directions with respect to the vehicle body unless otherwise specified. Further, the symbol FR shown in each figure indicates the front of the vehicle body, the symbol UP indicates the upper side of the vehicle body, and the symbol LH indicates the left side of the vehicle body.

[First embodiment]
FIG. 1 is a left side view of a motorcycle 1 according to a first embodiment of the present invention.
The motorcycle 1 is a vehicle that includes a body frame 10, a power unit 11 supported by the body frame 10, a front fork 12 that supports the front wheel 2 in a steerable manner, a rear wheel 3, and a seat 14 for a passenger. .
The motorcycle 1 is a scooter-type saddle-riding vehicle in which a rider is seated astride a seat 14. The seat 14 is provided above the rear part of the vehicle body frame 10. A step floor 15 on which an occupant places his or her feet is provided below the front of the seat 14.

The motorcycle 1 includes a body cover 16 that covers a body made up of a body frame 10 and the like.
The front fork 12 is supported by a head pipe 17 provided at the front end of the vehicle body frame 10. A steering handle 18 is provided at the upper end of the front fork 12.

FIG. 2 is a sectional view of the power unit 11. FIG. 2 is a cross section passing through the crankshaft 25 and the output shaft 31.
Referring to FIGS. 1 and 2, the power unit 11 is a unit swing type engine that has the function of an engine (internal combustion engine) that is a driving source and the function of a swing arm that supports the rear wheel 3. The power unit 11 is located directly below the seat 14 when viewed from the side of the vehicle. The rear wheel 3 is supported by an axle 3a provided at the rear end of the power unit 11.
The power unit 11 is connected to the vehicle body frame 10 via a link member 19 connected to the front part of the power unit 11, and swings up and down about the link member 19.

The power unit 11 includes a crankcase 26 that houses a crankshaft 25 and the like, a cylinder section 27 that extends forward from the front surface of the crankcase 26, and a transmission case section that extends rearward from one of the left and right sides of the crankcase 26. 28.

The crankshaft 25 extends inside the crankcase 26 in the vehicle width direction (left-right direction). The crankshaft 25 is supported by a pair of left and right side walls 26a and 26b of the crankcase 26.
A piston 29 that reciprocates within the cylinder portion 27 is connected to the crankshaft 25 via a connecting rod 30.
One axial end of the crankshaft 25 is a pulley support shaft portion 25a that extends into the transmission case portion 28 through one side wall 26a.

The transmission case portion 28 has a hollow case shape that extends long in the longitudinal direction of the vehicle.
The pulley support shaft portion 25a is located at the front inside the transmission case portion 28.
An output shaft 31 arranged parallel to the crankshaft 25 is provided at the rear inside the transmission case portion 28 . The output shaft 31 is supported by an inner side wall in the vehicle width direction of the transmission case portion 28 via a bearing.

Inside the transmission case part 28, there is a transmission 35 that changes the speed of the rotation of the crankshaft 25 and transmits it to the rear wheels 3, a centrifugal clutch mechanism 36, and a speed reduction mechanism 37 composed of a plurality of gears. provided.
The driving force of the crankshaft 25 is transmitted to the rear wheels 3 via a transmission 35, a clutch mechanism 36, and a speed reduction mechanism 37.

The transmission 35 is a belt-type continuously variable transmission.
The transmission 35 includes a drive-side pulley device 40 supported by the pulley support shaft portion 25a of the crankshaft 25, a driven-side pulley device 41 (pulley device) supported by the output shaft 31, and a drive-side pulley device 40 and the driven pulley device 40. A V-belt 42 is provided to connect the side pulley device 41.

The drive-side pulley device 40 is provided on the crankshaft 25 and rotates together with the crankshaft 25.
The drive-side pulley device 40 includes a disk-shaped drive-side fixed sheave 40a fixed to the shaft end of the pulley support shaft 25a, and a drive-side movable sheave 40b that is movable in the axial direction on the pulley support shaft 25a. Equipped with. The drive side movable sheave 40b is located between the drive side fixed sheave 40a and the side wall 26a in the axial direction.
The drive-side movable sheave 40b moves in the axial direction of the crankshaft 25 by being pushed by a roller weight 40c that moves due to centrifugal force caused by the rotation of the crankshaft 25. As a result, the distance between the drive-side fixed sheave 40a and the drive-side movable sheave 40b changes in accordance with the rotation of the crankshaft 25. The V-belt 42 is held between a driving-side fixed sheave 40a and a driving-side movable sheave 40b.

The driven pulley device 41 includes a fixed sheave 51 that rotatably fits on the outer periphery of the output shaft 31, a movable sheave 52 that is movable in the axial direction of the fixed sheave 51 with respect to the fixed sheave 51, and a movable sheave 52 that connects the movable sheave 52 to the fixed sheave. A spring 53 that urges toward the 51 side is provided.
The V-belt 42 is held between a fixed sheave 51 and a movable sheave 52.
In the transmission 35, the drive-side movable sheave 40b and the movable sheave 52 are displaced in the axial direction, so that the pulley diameter of the drive-side pulley device 40 and the pulley diameter of the driven-side pulley device 41 change with respect to the V-belt 42. The gear ratio is changed steplessly.

When the rotation of the driven pulley device 41 exceeds a predetermined rotation speed, the clutch mechanism 36 becomes connected due to centrifugal force and transmits the rotation of the driven pulley device 41 to the output shaft 31.
The rotation of the output shaft 31 is transmitted to the rear wheels 3 via the speed reduction mechanism 37.

FIG. 3 is a sectional view of the driven pulley device 41 and the clutch mechanism 36. FIG. 4 is an exploded perspective view of the driven pulley device 41.
Referring to FIGS. 3 and 4, the driven pulley device 41 includes, in addition to the above-described fixed sheave 51, movable sheave 52, and spring 53, a support plate 54 fixed to the shaft end of the output shaft 31, and a spring 53. A spring seat 55 supports one end 53a of the movable sheave 52, and a bearing 56 supports the movable sheave 52 on the fixed sheave 51.

The fixed sheave 51 includes a disk-shaped fixed sheave part 58 and a fixed sheave shaft part 59 extending from the center of the fixed sheave part 58 in the axial direction of the fixed sheave 51. The fixed sheave shaft portion 59 has a cylindrical shape that extends outward in the vehicle width direction from the fixed sheave portion 58 toward the support plate 54 side.
The fixed sheave 51 is supported by the output shaft 31 by fitting the fixed sheave shaft portion 59 to the outer periphery of the output shaft 31 . The fixed sheave 51 is connected to the output shaft 31 via a plurality of fixed sheave bearings 60a (ball type) and 60b (needle type) arranged between the inner circumference of the fixed sheave shaft portion 59 and the outer circumference of the output shaft 31. Supported.
The fixed sheave 51 is rotatable around the output shaft 31 and is immovable in the axial direction of the output shaft 31. The axial direction of the output shaft 31 is the axial direction of the fixed sheave 51 and coincides with the axial direction of the driven pulley device 41.

The support plate 54 is fixed to the shaft end of the fixed sheave shaft portion 59. The support plate 54 has a disk shape that extends radially outward with respect to the fixed sheave shaft portion 59. The fixed sheave portion 58 is provided at one end of the fixed sheave shaft portion 59, and the support plate 54 is provided at the other end of the fixed sheave shaft portion 59.
The support plate 54 includes a through hole 54a in the center. The support plate 54 has a through hole 54a that fits into the shaft end of the fixed sheave shaft section 59, is abutted against a stepped portion 59a of the fixed sheave shaft section 59, and is fastened to the shaft end of the fixed sheave shaft section 59 with a nut 61. be done. The support plate 54 rotates together with the fixed sheave 51.
The support plate 54 includes a plurality of fixing holes 54b at positions radially outward from the through holes 54a.

The spring seat 55 includes a cylindrical tube portion 55a extending in the axial direction of the fixed sheave 51, and an annular flange portion 55b extending radially outward from the axial end of the tube portion 55a.
The cylindrical portion 55a has a cylindrical shape with a larger diameter than the fixed sheave shaft portion 59, and the fixed sheave shaft portion 59 is inserted into the cylindrical portion 55a.
The spring seat 55 is disposed between the support plate 54 and the movable sheave 52 in the axial direction of the fixed sheave 51, and is fixed to the support plate 54.

The flange portion 55b is provided at an end portion 55c on the support plate 54 side at an axial end portion of the cylindrical portion 55a.
The flange portion 55b is provided with a plurality of protrusions 55d that protrude toward the support plate 54 in the axial direction of the cylinder portion 55a.
The spring seat 55 is fixed to the support plate 54 by the end portion 55c abutting against the support plate 54 in the axial direction and by the protrusion 55d engaging with the fixing hole 54b.
Since the spring seat 55 is fixed to the support plate 54, it rotates together with the fixed sheave 51.

The movable sheave 52 is arranged between the fixed sheave 51 and the spring seat 55 in the axial direction of the output shaft 31.
The movable sheave 52 includes a disk-shaped sheave portion 65 and a movable sheave shaft portion 66 extending from the center of the sheave portion 65 in the axial direction of the movable sheave 52.
The movable sheave shaft portion 66 has a cylindrical shape extending outward in the vehicle width direction from the sheave portion 65 toward the support plate 54 side.

The movable sheave 52 is supported by the fixed sheave shaft 59 by fitting the movable sheave shaft 66 to the outer periphery of the fixed sheave shaft 59 . The movable sheave 52 is supported by the fixed sheave shaft 59 via the bearing 56, which is disposed between the inner periphery of the movable sheave shaft 66 and the outer periphery of the fixed sheave shaft 59.
The movable sheave 52 is rotatable relative to the fixed sheave shaft 59 on the fixed sheave shaft 59 and movable in the axial direction of the fixed sheave shaft 59 . That is, the movable sheave 52 is rotatable relative to the spring seat 55 fixed to the fixed sheave 51.
The axial direction of the fixed sheave shaft portion 59 coincides with the axial direction of the driven pulley device 41.

The V-belt 42 is held between the sheave portion 65 and the stationary sheave portion 58. In the axial direction of the fixed sheave shaft portion 59, the distance between the sheave portion 65 and the fixed sheave portion 58 increases as it goes radially outward of the sheave portion 65.

The movable sheave shaft portion 66 includes a cylindrical outer shaft portion 70 that extends in the axial direction of the movable sheave 52 with respect to the sheave portion 65, and a cylindrical outer shaft portion 70 that extends from the sheave portion 65 in the axial direction of the movable sheave 52 inside the outer shaft portion 70. A cylindrical inner shaft portion 71 is provided. The outer shaft portion 70 and the inner shaft portion 71 are arranged coaxially.
Since the inner shaft portion 71 has a smaller diameter than the outer shaft portion 70, a space 72 is formed between the outer shaft portion 70 and the inner shaft portion 71 in the radial direction.

The bearing 56 is attached to the movable sheave 52 by fitting into the inner circumference of the inner shaft portion 71.
The outer shaft portion 70 is formed separately from the inner shaft portion 71. The outer shaft portion 70 fits into the base end portion of the inner shaft portion 71 and is fixed to the inner shaft portion 71 by a coupling method such as press fitting or welding. Note that the outer shaft portion 70 and the inner shaft portion 71 may be formed integrally.
The movable sheave 52 includes an annular spring receiving portion 73 extending radially outward from the outer periphery of the base end portion of the movable sheave shaft portion 66 .

The cylindrical portion 55a of the spring seat 55 has a smaller diameter than the outer shaft portion 70 and a larger diameter than the inner shaft portion 71.
The cylindrical portion 55a of the spring seat 55 overlaps the outer shaft portion 70 and the inner shaft portion 71 of the movable sheave shaft portion 66 in the axial direction of the driven pulley device 41. That is, a portion of the cylindrical portion 55a is located in the space 72 between the outer shaft portion 70 and the inner shaft portion 71.

The spring 53 is a coil spring that extends in the axial direction of the driven pulley device 41.
The spring 53 has a larger diameter than the movable sheave shaft portion 66, and the movable sheave shaft portion 66 and the cylindrical portion 55a of the spring seat 55 pass inside the spring 53 in the radial direction.
One end 53a of the spring 53 is supported by the flange portion 55b of the spring seat 55, and the other end 53b of the spring 53 is supported by the spring receiving portion 73 of the movable sheave 52.
The spring 53 is compressed between the flange portion 55b and the spring receiving portion 73, and urges the movable sheave 52 toward the fixed sheave 51 in the axial direction of the driven pulley device 41. Further, the spring 53 urges the spring seat toward the support plate 54 in the axial direction.

In the axial direction of the driven pulley device 41, the movable sheave 52 is movable in an opening direction A in which it moves away from the fixed sheave 51 and in a closing direction B in which it approaches the fixed sheave 51.
The spring 53 urges the movable sheave 52 in the closing direction B.

The driven pulley device 41 includes a cam mechanism 80 that converts the relative rotation of the movable sheave 52 with respect to the spring seat 55 into a thrust force F in the axial direction of the movable sheave 52. The thrust force F is a force that moves the movable sheave 52 in the axial direction of the driven pulley device 41.
FIG. 5 is a perspective view showing the cam mechanism 80. FIG. 5 shows an axis 41a extending in the axial direction of the driven pulley device 41. As shown in FIG. Further, FIG. 5 shows the rotational direction R of the movable sheave 52 and the fixed sheave 51 that are driven by the crankshaft 25 via the V-belt 42.
Referring to FIGS. 3 to 5, the cam mechanism 80 includes an inner cam mechanism 81 provided on the inner circumferential side of the cylindrical portion 55a of the spring seat 55, and an outer cam mechanism 81 provided on the outer circumferential side of the cylindrical portion 55a of the spring seat 55. 82.

The inner cam mechanism 81 includes an inner cam receiving portion 83 provided on the inner circumferential surface 55e of the cylindrical portion 55a, and an inner cam 71a provided on the inner shaft portion 71 of the movable sheave 52.
The inner cam receiving portion 83 is a protrusion that protrudes radially inward from the inner circumferential surface 55e.
The inner cam receiving portion 83 extends long in the axial direction of the driven pulley device 41 in a rail shape.
The inner cam receiving portion 83 is obliquely inclined so as to shift toward the rotation direction R side as it goes toward the sheave portion 65 side in the axial direction. That is, the inner cam receiving portion 83 is provided to be inclined with respect to the axis 41a of the driven pulley device 41.

The inner cam receiving portion 83 has a pair of side surfaces in the circumferential direction of the cylindrical portion 55a. A side surface of the inner cam receiving portion 83 that faces the rotational direction R is an inner contact surface 83a that contacts the inner cam 71a. Although the side surface 83b on the side of the rotation direction R of the inner cam receiving part 83 does not contact the inner cam 71a in this embodiment, the shapes of the inner cam 71a and the inner cam receiving part 83 are adjusted so that the side surface 83b contacts the inner cam 71a. It's okay.
The inner contact surface 83a is obliquely inclined so as to shift toward the rotation direction R side as it goes toward the sheave portion 65 side in the axial direction.
A plurality of inner cam receiving portions 83 (three in this embodiment) are provided at equal intervals in the circumferential direction of the cylindrical portion 55a on the inner circumferential surface 55e.

The inner cam 71a is provided by cutting out a part of the inner shaft portion 71 in the axial direction of the driven pulley device 41.
Specifically, the inner shaft portion 71 is provided with a cutout portion 71b that is cut out in the axial direction from the tip of the inner shaft portion 71 toward the sheave portion 65 side. A plurality of notches 71b are provided at equal intervals in the circumferential direction of the inner shaft portion 71.
In the inner shaft portion 71, the portion remaining after being cut out by each notch portion 71b is an inner cam 71a. A plurality of inner cams 71a (three in this embodiment) are provided at equal intervals in the circumferential direction of the inner shaft portion 71.

The inner cam 71a extends in the axial direction inside the cylindrical portion 55a of the spring seat 55. The inner cam 71a is located between a pair of inner cam receivers 83 adjacent to the inner cam 71a in the circumferential direction of the cylindrical portion 55a.
The tip of the inner cam 71a is an inner cam surface 71c that slides in contact with the inner cam receiving portion 83 within the cylinder portion 55a. The inner cam surface 71c is formed into a curved shape so as to slide smoothly on the inner abutment surface 83a of the inner cam receiving portion 83.

The outer cam mechanism 82 includes an outer cam receiving portion 84 provided on the outer peripheral surface 55f of the cylindrical portion 55a, and an outer cam 70a provided on the outer shaft portion 70 of the movable sheave 52.
The outer cam receiving portion 84 is a protrusion that protrudes radially outward from the outer circumferential surface 55f. The outer cam receiving portion 84 is a substantially semicircular protrusion when viewed from the radially outer side of the cylindrical portion 55a.
The outer cam receiving portion 84 is provided at the end of the cylindrical portion 55a on the sheave portion 65 side in the axial direction. A plurality of outer cam receivers 84 (in this embodiment, two locations) are provided at equal intervals in the circumferential direction of the cylindrical portion 55a on the outer circumferential surface 55f.

The outer cam 70a is provided by cutting out a part of the outer shaft portion 70 in the axial direction of the driven pulley device 41.
Specifically, the outer shaft portion 70 is provided with a cutout portion 70b that is cut out in the axial direction from the tip of the outer shaft portion 70 toward the sheave portion 65 side. A plurality of cutout portions 70b are provided at equal intervals in the circumferential direction of the outer shaft portion 70.
In the outer shaft portion 70, the portion remaining after being cut out by each notch portion 70b is an outer cam 70a. A plurality of outer cams 70a (two in this embodiment) are provided at equal intervals in the circumferential direction of the outer shaft portion 70.

An edge portion of the outer cam 70a facing in the rotational direction R is an outer cam surface 70c that slides in contact with the outer cam receiving portion 84.
The outer cam surface 70c extends in the axial direction of the driven pulley device 41.
The outer cam surface 70c is obliquely inclined so as to shift toward the rotation direction R side as it goes toward the sheave portion 65 side in the axial direction. That is, the outer cam surface 70c is provided to be inclined with respect to the axis 41a of the driven pulley device 41.

The outer cam 70a surrounds the cylindrical portion 55a of the spring seat 55 from the outer peripheral side. The outer cam receiving portion 84 is located between a pair of outer cams 70a adjacent to the outer cam receiving portion 84 in the circumferential direction of the cylindrical portion 55a.
The outer peripheral surface of the semicircular outer cam receiving portion 84 is an outer contact surface 84a that contacts the outer cam surface 70c of the outer cam 70a. The outer contact surface 84a is formed into a curved shape so as to slide smoothly on the outer cam surface 70c.

In the cylindrical portion 55a of the spring seat 55, inner cam receivers 83 are provided at three locations at 120° intervals in the circumferential direction, and outer cam receivers 84 are provided at two locations at 180° intervals in the circumferential direction. .
Further, the inner cam receiving portion 83 and the outer cam receiving portion 84 are arranged with phases shifted from each other in the circumferential direction of the cylindrical portion 55a. That is, the inner cam receiving part 83 and the outer cam receiving part 84 are staggered so that the inner cam receiving part 83 and the outer cam receiving part 84 are not located at the same position in the circumferential direction.

The inner cam receiving part 83 and the outer cam receiving part 84 of the spring seat 55 are cam receiving parts.
The inner cam 71a and the outer cam 70a of the movable sheave shaft portion 66 are cams that slide on the cam receiving portion.
In the inner cam mechanism 81, an inner cam receiving part 83, which is one of a cam receiving part and a cam, is provided to be inclined with respect to the axis 41a extending in the axial direction of the movable sheave shaft part 66.
In the outer cam mechanism 82, the outer cam 70a, which is the other of the cam receiving portion and the cam, is provided to be inclined with respect to the axis 41a extending in the axial direction of the movable sheave shaft portion 66.
Although the inclination angle of the inner cam receiving portion 83 and the inclination angle of the outer cam 70a are substantially the same, the shapes of the inclinations are different. Specifically, only the outer cam 70a has a V-shape with an apex.

The clutch mechanism 36 includes a plurality of clutch shoes 36a supported by a support plate 54, a clutch spring 36b that biases the clutch shoes 36a, and a clutch outer 36c surrounding the support plate 54 and the clutch shoes 36a from the outer circumferential side.
The clutch shoe 36a is disposed on the support plate 54 at a radially outer position with respect to the spring 53, and is erected from the support plate 54 toward the sheave portion 65 side. The clutch spring 36b urges the clutch shoe 36a in the direction of disconnecting the clutch mechanism 36.
The clutch outer 36c is a cup-shaped member that extends radially outward from the output shaft 31.
The clutch outer 36c is spline-fitted to the shaft end of the output shaft 31. The clutch outer 36c is fixed by a nut 75 fastened to the output shaft 31. The clutch outer 36c rotates together with the output shaft 31.

Here, the operation of the driven pulley device 41 and the clutch mechanism 36 will be explained.
When the driving force is transmitted to the driven pulley device 41 via the V-belt 42, the driven pulley device 41 rotates on the output shaft 31 via the fixed sheave bearings 60a, 60b.
The support plate 54 of the clutch mechanism 36 rotates together with the driven pulley device 41. The clutch shoe 36a is displaced radially outward against the clutch spring 36b due to the centrifugal force of this rotation, and comes into contact with the inner periphery of the clutch outer 36c. The friction of this contact connects the clutch mechanism 36. When the clutch mechanism 36 is connected, rotation is transmitted from the clutch shoe 36a to the output shaft 31 via the clutch outer 36c.

In the driven pulley device 41, the movable sheave 52 is urged in the closing direction B by a spring 53.
Further, the movable sheave 52 is moved in the axial direction of the driven pulley device 41 by the action of the cam mechanism 80. The cam mechanism 80 is operated by fluctuations in torque acting on the movable sheave 52.

When the torque in the rotational direction R input from the V-belt 42 to the driven pulley device 41 increases, the movable sheave 52 is rotated in the rotational direction R with respect to the fixed sheave 51 by the V-belt 42 . Then, in the inner cam mechanism 81, the inner cam 71a of the inner shaft portion 71 slides against the inner cam receiving portion 83 of the spring seat 55, and the movable sheave 52 moves in the direction D1 in FIG. Direction D1 includes a component of closing direction B.
That is, when the movable sheave 52 rotates relative to the fixed sheave 51 in the rotation direction R, the movable sheave 52 moves in the closing direction B as shown in FIG. 3 due to the action of the inner cam mechanism 81. Due to the thrust F in the closing direction B, the V-belt 42 is more strongly sandwiched between the movable sheave 52 and the fixed sheave 51.

For example, when the rider widens the accelerator in an attempt to accelerate the motorcycle 1, the torque of the power unit 11 increases, and the torque in the rotation direction R transmitted from the V-belt 42 to the driven pulley device 41 also increases. Then, the movable sheave 52 moves in the closing direction B by the action of the inner cam mechanism 81. As a result, the V-belt 42 is strongly sandwiched between the movable sheave 52 and the fixed sheave 51, and is pushed outward in the radial direction of the driven pulley device 41, resulting in a substantial pulley diameter of the driven pulley device 41. increases, and the gear ratio of the transmission 35 becomes higher. Therefore, the motorcycle 1 can be effectively accelerated.

FIG. 6 is a sectional view showing a state in which the movable sheave 52 has moved in the opening direction A.
Furthermore, when the movable sheave 52 rotates in the opposite direction to the rotational direction R with respect to the fixed sheave 51 due to fluctuations in the torque acting on the movable sheave 52, the outer cam 70a of the outer shaft portion 70 in the outer cam mechanism 82 55, the movable sheave 52 moves in the direction D2 in FIG. Direction D2 includes a component of opening direction A.
That is, when the movable sheave 52 rotates relative to the fixed sheave 51 in the direction opposite to the rotational direction R, the movable sheave 52 moves in the opening direction A as shown in FIG. 6 due to the action of the outer cam mechanism 82. Due to the thrust force F in the opening direction A, the V-belt 42 is more weakly sandwiched between the movable sheave 52 and the fixed sheave 51. In this case, the V-belt 42 moves radially inward of the driven pulley device 41, the substantial pulley diameter of the driven pulley device 41 becomes smaller, and the gear ratio of the transmission 35 becomes smaller.

When the movable sheave 52 is moved in the closing direction B by the inner cam mechanism 81, a clearance is secured in the circumferential direction between the outer cam receiving part 84 of the outer cam mechanism 82 and the outer cam 70a, and the outer cam The receiving portion 84 and the outer cam 70a do not come into contact with each other.
When the movable sheave 52 is moved in the opening direction A by the outer cam mechanism 82, a clearance is secured in the circumferential direction between the inner cam receiving part 83 of the inner cam mechanism 81 and the inner cam 71a, and the inner cam The receiving portion 83 and the inner cam 71a do not come into contact with each other.
That is, the inner cam mechanism 81 functions as a cam mechanism only when moving in the closing direction B when the movable sheave 52 moves in the closing direction B and the opening direction A.
Further, the outer cam mechanism 82 functions as a cam mechanism only when the movable sheave 52 moves in the closing direction B and the opening direction A, and only when moving in the opening direction A.

The cam mechanism 80 of the driven pulley device 41 is divided into an inner cam mechanism 81 on the inner circumferential side of the cylindrical portion 55a of the spring seat 55 and an outer cam mechanism 82 on the outer circumferential side of the cylindrical portion 55a. Therefore, the load acting on the cam mechanism 80 can be distributed between the inner circumferential side and the outer circumferential side of the cylindrical portion 55a of the spring seat 55.

The spring seat 55 including the inner cam receiver 83 and the outer cam receiver 84 is made of resin material.
The movable sheave shaft portion 66 including the inner cam 71a and the outer cam 70a is made of metal, for example, made of iron-based material. In the cam mechanism 80, the metal movable sheave shaft portion 66 slides against the resin spring seat 55, so the cam mechanism 80 can operate well without applying lubricant such as grease to the cam mechanism 80. be able to.
Further, the bearing 56 that supports the movable sheave 52 on the fixed sheave 51 is made of a self-lubricating material. Therefore, no lubricant such as grease is required between the movable sheave 52 and the fixed sheave 51.
That is, in the driven pulley device 41, the cam mechanism 80 and the movable sheave 52 do not require a lubricant such as grease. Therefore, lubricant such as grease is prevented from adhering to the clutch mechanism 36, the stationary sheave portion 58, and the sheave portion 65.

As described above, according to the first embodiment to which the present invention is applied, the driven pulley device 41 is movable toward and away from the fixed sheave 51 in the axial direction. The movable sheave 52 includes a movable sheave 52, a spring 53 that urges the movable sheave 52 toward the fixed sheave 51 in the axial direction, and a spring seat 55 as a cylindrical member that rotates together with the fixed sheave 51. It includes a disk-shaped sheave portion 65 and a movable sheave shaft portion 66 extending in the axial direction from the sheave portion 65, and converts the relative rotation of the movable sheave 52 with respect to the spring seat 55 into an axial thrust force F of the movable sheave 52. A converting cam mechanism 80 is provided, and the movable sheave shaft portion 66 includes a cylindrical outer shaft portion 70 extending axially from the sheave portion 65 and a cylindrical outer shaft portion 70 extending axially from the sheave portion inside the outer shaft portion 70. The spring seat 55 includes a cylindrical portion 55a disposed between the outer axial portion 70 and the inner axial portion 71, and the cam mechanism 80 extends from the inner peripheral side of the cylindrical portion 55a. Provided on both outer peripheral sides.
According to this configuration, since the cam mechanism 80 is provided on both the inner and outer circumferential sides of the cylindrical portion 55a of the spring seat 55, the load acting on the cam mechanism 80 is effectively dispersed and reduced. However, more cam mechanisms can be arranged in the radial direction than in a structure with one layer of cam mechanisms.

The cam mechanism 80 also includes an inner cam receiving part 83 provided on the inner peripheral surface 55e of the cylindrical part 55a, and an inner cam 71a provided on the inner shaft part 71 and abutting on the inner cam receiving part 83. A cam mechanism 81 is provided.
According to this configuration, the inner cam mechanism 81 can be provided compactly by the inner cam receiving part 83 on the inner peripheral surface 55e of the cylindrical part 55a and the inner cam 71a of the inner shaft part 71 provided inside the cylindrical part 55a. I can do it.
The cam mechanism 80 also includes an outer cam receiving part 84 provided on the outer circumferential surface 55f of the cylindrical part 55a, and an outer cam 70a provided on the outer shaft part 70 and abutting on the outer cam receiving part 84. A mechanism 82 is provided.
According to this configuration, the outer cam mechanism 82 can be provided compactly by the outer cam receiving portion 84 on the outer peripheral surface 55f of the cylindrical portion 55a and the outer cam 70a of the outer shaft portion 70 provided on the outside of the cylindrical portion 55a. can.

Furthermore, the movable sheave 52 is movable in an opening direction A in which it moves away from the fixed sheave 51 and in a closing direction B in which it approaches the fixed sheave 51. The outer cam mechanism 82 generates a thrust force F when moving in the closing direction B, which is one of the closing directions B, and the outer cam mechanism 82 generates a thrust force F when moving in the opening direction A, which is the other of the opening direction A and the closing direction B. let
According to this configuration, the cam mechanism 80 is divided into an outer cam mechanism 82 that corresponds to the movement of the movable sheave 52 in the opening direction A, and an inner cam mechanism 81 that corresponds to the movement of the movable sheave 52 in the closing direction B. Therefore, the direction of the load acting on the cam mechanism 80 is constant. As a result, the number and shape of the cam mechanisms 80 can be optimized in accordance with the load, so that durability can be improved by reducing the load, and it is also possible to cope with higher loads.

Further, a plurality of inner cam receivers 83 are provided in the circumferential direction on the inner circumferential surface 55e, and a plurality of outer cam receivers 84 are provided in the circumferential direction on the outer circumferential surface 55f. and are arranged out of phase with each other in the circumferential direction of the cylindrical portion 55a.
According to this configuration, the load acting on the inner cam receiving portion 83 and the outer cam receiving portion 84 can be effectively dispersed to a plurality of locations in the circumferential direction of the cylindrical portion 55a, and the load can be reduced.

Further, the inner cam receiving part 83 and the outer cam receiving part 84 are cam receiving parts, the inner cam 71a and the outer cam 70a are cams, and in the inner cam mechanism 81, the inner cam receiving part 83 and the outer cam receiving part 84 are cams. The cam receiving portion 83 is provided to be inclined with respect to the axial direction of the movable sheave shaft portion 66, and in the outer cam mechanism 82, the outer cam 70a, which is the other of the cam receiving portion and the cam, is inclined in the axial direction of the movable sheave shaft portion 66. It is installed at an angle to the
According to this configuration, the portions of the cam receiving portion and the cam that are inclined with respect to the axial direction of the movable sheave shaft portion 66 can be distributed and provided in the inner cam mechanism 81 and the outer cam mechanism 82. Therefore, the load on the cam mechanism 80 can be reduced.
Furthermore, in the above configuration, the cylindrical member may be a spring seat 55 that supports one end 53a of the spring 53.
According to this configuration, the cam mechanism 80 can be provided with a simple structure by using the spring seat 55.
Further, the spring seat 55 includes a flange portion 55b extending radially outward from the cylindrical portion 55a and supporting one end 53a of the spring 53. The spring 53 is a coil spring, and the cylindrical portion 55a and the movable sheave shaft portion 66 are , are arranged radially inside the spring 53.
According to this configuration, the cam mechanism 80 constituted by the cylinder portion 55a and the movable sheave shaft portion 66 can be provided compactly by utilizing the space inside the spring 53 in the radial direction.
Further, the spring seat 55 is made of resin, and the fixed sheave 51 includes a fixed sheave part 58 facing the sheave part 65 and a fixed sheave shaft part 59 extending in the axial direction from the fixed sheave part 58, The movable sheave 52 has a movable sheave shaft portion 66 fitted into a fixed sheave shaft portion 59, and the movable sheave 52 is made of a self-lubricating material and is disposed between the movable sheave shaft portion 66 and the fixed sheave shaft portion 59. It is supported by a bearing 56.
According to this configuration, since the spring seat 55 constituting the cam mechanism 80 is made of resin, a lubricant such as grease for the cam mechanism 80 can be omitted. Further, since the movable sheave shaft portion 66 is supported by the fixed sheave shaft portion 59 via the bearing 56 made of a self-lubricating material, a lubricant such as grease for the movable sheave shaft portion 66 can be omitted.

Note that the above embodiment shows one mode to which the present invention is applied, and the present invention is not limited to the above embodiment.
In the embodiment described above, an example is given in which the inner cam mechanism 81 that functions in the closing direction B and the outer cam mechanism 82 that functions in the opening direction A are provided separately on the inner circumferential side and the outer circumferential side of the cylindrical portion 55a. However, the present invention is not limited thereto. For example, a cam mechanism capable of generating thrust in both the opening direction A and the closing direction B according to the rotation of the movable sheave 52 may be provided on both the inner and outer circumferential sides of the cylindrical portion 55a.
Further, in the above embodiment, the inner cam receiving part 83 and the outer cam receiving part 84 are described as being protrusions, but the present invention is not limited to this. For example, the inner cam receiving part 83 and the outer cam receiving part 84 are made into recessed parts, the inner cam 71a is made into a protrusion that engages with the recessed part of the inner cam receiving part 83, and the outer cam 70a is made into a recessed part of the outer cam receiving part 84. It may also be a protrusion.
Further, in the above embodiment, it has been explained that the inclination angle of the inner cam receiving portion 83 and the inclination angle of the outer cam 70a are the same, but the present invention is not limited to this. For example, the inclination angle of the inner cam receiving portion 83 and the inclination angle of the outer cam 70a may be made different, so that the characteristics of the generation of the thrust force F may be made different in the opening direction A and the closing direction B. Thereby, the speed change characteristics can be changed between the opening direction A and the closing direction B. Furthermore, the characteristics of the generation of the thrust force F may be made different in the opening direction A and the closing direction B by making the shape of the inclination of the inner cam receiving portion 83 and the shape of the inclination of the outer cam 70a different. The angle of inclination of the inner cam receiving part 83 and the outer cam 70a and the shape of the inclination of the inner cam receiving part 83 and the outer cam 70a are the states of inclination of the inner cam receiving part 83 and the outer cam 70a.
Further, in the above embodiment, the inner cam receiving part 83 and the outer cam receiving part 84 are arranged with phases shifted from each other in the circumferential direction of the cylindrical part 55a, but the present invention is not limited to this. The inner cam receiving portion 83 and the outer cam receiving portion 84 may be arranged at the same position in the circumferential direction of the cylindrical portion 55a.
Further, in the above embodiment, the motorcycle 1 has been described as an example, but the present invention is not limited thereto. It is applicable to vehicles equipped with more than one wheel.

[Second embodiment]
A second embodiment to which the present invention is applied will be described below with reference to FIGS. 7 and 8. In this second embodiment, the same reference numerals are given to the same parts as in the first embodiment, and the explanation thereof will be omitted.
The second embodiment differs from the first embodiment in the structure for receiving one end 53a of the spring 53 and the like.

FIG. 7 is a sectional view of the driven pulley device 241 and the clutch mechanism 36 in the second embodiment.
The driven pulley device 241 includes a cylindrical member 255 that rotates together with the fixed sheave 51, a holder 290 supported by the support plate 54, and a spring 53 instead of the spring seat 55 of the first embodiment. A spring receiving member 291 that receives one end 53a is provided.
The cylindrical member 255 includes a cylindrical portion 55a, an end portion 55c, a protrusion 55d, and an inner circumferential surface 55e, and does not include a flange portion 55b (FIG. 3) that receives the spring 53.

FIG. 8 is an enlarged cross-sectional view of the structure that receives one end 53a in FIG. 7.
The support plate 54 includes a first disk portion 54c extending radially outward from the fixed sheave shaft portion 59, and an annular peripheral wall portion extending from the outer circumference of the first disk portion 54c toward the fixed sheave portion 58. 54d, and a second disk portion 54e extending radially outward from the axial end of the peripheral wall portion 54d.
The through hole 54a and the fixing hole 54b are provided in the first disc portion 54c. Clutch shoe 36a is supported by second disc portion 54e.
The peripheral wall portion 54d has a cylindrical shape that surrounds the cylindrical member 255 from the periphery.

Holder 290 is supported by support plate 54. The holder 290 supports one end 53a of the spring 53 via a spring receiving member 291.
The holder 290 includes a cylindrical fitting part 290a that fits into the inner periphery of the peripheral wall part 54d, and a ring-shaped collar part 290b that extends radially outward from the axial end of the fitting part 290a. . Further, the holder 290 includes an annular step portion 290c into which the spring receiving member 291 is fitted, on the inner peripheral portion of the collar portion 290b.
The holder 290 is pushed in the axial direction by the biasing force of the spring 53, and the collar portion 290b comes into contact with the second disc portion 54e. The holder 290 is fixed to the support plate 54 by press-fitting the fitting portion 290a into the inner periphery of the peripheral wall portion 54d. Therefore, as the fixed sheave 51 rotates, the holder 290 rotates together with the support plate 54.
The fitting portion 290a faces the cylindrical member 255 in the axial direction, but a gap 292 is provided in the axial direction between the fitting portion 290a and the cylindrical member 255.
The holder 290 is made of metal, for example, an aluminum alloy.

The spring receiving member 291 is sandwiched between the holder 290 and one end 53a of the spring 53, and directly receives the one end 53a.
The spring receiving member 291 includes a ring-shaped receiving plate portion 291a that follows the shape of one end 53a, an annular projection 291b that fits into the stepped portion 290c of the holder 290, and a shaft extending from the radially outer end of the receiving plate portion 291a. It includes an annular rib 291c that stands upright in the direction.
The spring receiving member 291 is positioned in the radial direction by fitting the protrusion 291b into the stepped portion 290c. The receiving plate portion 291a receives one end 53a in the axial direction. The rib 291c surrounds the one end 53a and positions the one end 53a.
The spring receiving member 291 is made of a material having a smaller coefficient of friction than the holder 290. The spring receiving member 291 is made of resin, for example.
The contact surface between the receiving plate portion 291a of the spring receiving member 291 and the collar portion 290b of the holder 290 is a sliding surface 293. The spring receiving member 291 slides on the holder 290 via the sliding surface 293.

The other end 53b (FIG. 7) of the spring 53 directly contacts the sheave portion 65 of the movable sheave 52 and is received by the sheave portion 65 in the axial direction.
The relative rotation between the movable sheave 52 and the support plate 54 also extends to the spring 53 sandwiched between the spring receiving member 291 and the sheave portion 65. At this time, the rotation applied to the spring 53 is mainly absorbed by the sliding of the spring receiving member 291 and the holder 290 on the sliding surface 293 on the one end 53a side. On the other end 53b side of the spring 53, since the other end 53b directly contacts the sheave portion 65 having a high coefficient of friction, relative rotation between the spring 53 and the sheave portion 65 is difficult to occur.

[Third embodiment]
A third embodiment to which the present invention is applied will be described below with reference to FIGS. 9 and 10. In this third embodiment, the same reference numerals are given to the same parts as in the first embodiment, and the explanation thereof will be omitted.
In the third embodiment, the shapes of the inner cam mechanism 381 and the outer cam mechanism 382 are different from the inner cam mechanism 81 and the outer cam mechanism 82 of the first embodiment, etc. The form is different from that of

FIG. 9 is a perspective view showing a cam mechanism 380 in the third embodiment.
In the third embodiment, a movable sheave 352 is provided in place of the movable sheave 52, and a spring seat 355 is provided in place of the spring seat 55.
The movable sheave 352 includes a movable sheave shaft portion 366 that extends from the sheave portion 65 in the axial direction.
The movable sheave shaft portion 366 includes an outer shaft portion 370 and an inner shaft portion 371.
The spring seat 355 includes a plurality of protrusions 355d that engage with the fixing holes 54b of the support plate 54.

FIG. 10 is a cross-sectional view of the cam mechanism 380 viewed in the axial direction. In FIG. 10, a fixed sheave shaft portion 59 is also illustrated.
The cam mechanism 380 includes an inner cam mechanism 381 provided on the inner circumferential side of the cylindrical portion 55a of the spring seat 355, and an outer cam mechanism 382 provided on the outer circumferential side of the cylindrical portion 55a of the spring seat 355.

The inner cam mechanism 381 includes an inner cam receiving portion 383 provided on the inner circumferential surface 55e of the cylindrical portion 55a, and an inner cam 371a provided on the inner shaft portion 371 of the movable sheave 352.
The inner cam receiving portion 383 is configured similarly to the inner cam receiving portion 83 of the first embodiment, and the inner cam 371a is configured similarly to the inner cam 71a of the first embodiment. The inner cam receiving portions 383 and the inner cams 371a are provided at five equal intervals in the circumferential direction of the cylindrical portion 55a.

The outer cam mechanism 382 includes an outer cam receiving portion 384 provided on the outer peripheral surface 55f of the cylindrical portion 55a, and an outer cam 370a provided on the outer shaft portion 370 of the movable sheave 352.
The outer cam receiving portion 384 is configured similarly to the outer cam receiving portion 84 of the first embodiment.

The outer cam 370a is a groove extending on the outer shaft portion 370 in the axial direction of the movable sheave 352. The outer cam 370a has a long hole shape that penetrates the wall surface of the outer cam 370a. The outer cam 370a is obliquely inclined so as to shift toward the rotation direction R side as it goes toward the sheave portion 65 side in the axial direction. That is, the outer cam 370a is provided to be inclined with respect to the axis 41a of the driven pulley device 41.
The outer cam receiving portion 384 fits into the outer cam 370a. The peripheral edge of the outer cam 370a is an outer cam surface 370c that slides in contact with the outer cam receiving portion 384.

41,241 Driven pulley device (pulley device)
51 Fixed sheave 52,352 Movable sheave 53 Spring 55,355 Spring seat (cylindrical member)
55a Cylindrical portion 55b Flange portion 55e Inner circumferential surface 55f Outer circumferential surface 56 Bearing 58 Fixed side sheave portion 59 Fixed sheave shaft portion 65 Sheave portion 66, 366 Movable sheave shaft portion 70, 370 Outer shaft portion 70a, 370a Outer cam (cam receiving portion and the other side of the cam)
71,371 Inner shaft portion 71a, 371a Inner cam 80,380 Cam mechanism 81,381 Inner cam mechanism 82,382 Outer cam mechanism 83,383 Inner cam receiver (one of cam receiver and cam)
84,384 Outer cam receiving part 255 Cylindrical member A Opening direction B Closing direction F Thrust

Claims (10)

a fixed sheave (51), a movable sheave (52, 352) that is movable toward and away from the fixed sheave (51) in the axial direction, and a movable sheave (52, 352) that is movable in the axial direction The movable sheave (52, 352) includes a spring (53) that biases toward the sheave (51) and a cylindrical member (55, 255, 355) that rotates together with the fixed sheave (51). , comprising a disc-shaped sheave part (65) and a movable sheave shaft part (66, 366) extending in the axial direction from the sheave part (65), and A pulley device provided with a cam mechanism (80, 380) that converts relative rotation of the movable sheave (52, 352) into an axial thrust (F) of the movable sheave (52, 352),
The movable sheave shaft portion (66, 366) includes a cylindrical outer shaft portion (70, 370) that extends in the axial direction with respect to the sheave portion (65), and an inner side of the outer shaft portion (70, 370). and an inner shaft part (71, 371) extending in the axial direction from the sheave part (65),
The cylindrical member (55, 255, 355) includes a cylindrical portion (55a) disposed between the outer shaft portion (70, 370) and the inner shaft portion (71, 371),
The pulley device is characterized in that the cam mechanism (80, 380) is provided on both an inner circumferential side and an outer circumferential side of the cylinder portion (55a). The cam mechanism (80, 380) includes an inner cam receiving portion (83, 383) provided on the inner peripheral surface (55e) of the cylinder portion (55a) and an inner cam receiving portion (83, 383) provided on the inner shaft portion (71, 371). The pulley device according to claim 1, further comprising an inner cam mechanism (81, 381) constituted by an inner cam (71a, 371a) that abuts the inner cam receiving portion (83, 383). The cam mechanism (80, 380) includes an outer cam receiving portion (84, 384) provided on the outer peripheral surface (55f) of the cylinder portion (55a), and an outer cam receiving portion (84, 384) provided on the outer shaft portion (70, 370). The pulley device according to claim 2, further comprising an outer cam mechanism (82, 382) constituted by an outer cam (70a, 370a) that abuts an outer cam receiving portion (84, 384). The movable sheave (52, 352) is movable in an opening direction (A) in which it moves away from the fixed sheave (51) and in a closing direction (B) in which it approaches the fixed sheave (51),
The inner cam mechanism (81, 381) generates the thrust (F) when the movable sheave (52, 352) moves in one of the opening direction (A) and the closing direction (B). The pulley device according to claim 3, wherein the outer cam mechanism (82, 382) generates the thrust (F) during movement in the other of the opening direction (A) and the closing direction (B). . A plurality of the inner cam receiving portions (83) are provided in the circumferential direction on the inner peripheral surface (55e),
A plurality of the outer cam receiving portions (84) are provided in the circumferential direction on the outer peripheral surface (55f),
The inner cam receiving part (83) and the outer cam receiving part (84) are arranged so as to be out of phase with each other in the circumferential direction of the cylindrical part (55a). pulley device. The inner cam receiver (83) and the outer cam receiver (84) are cam receivers,
The inner cam (71a) and the outer cam (70a) are cams,
In the inner cam mechanism (81), one of the cam receiving portion and the cam is provided to be inclined with respect to the axial direction of the movable sheave shaft portion (66),
In the outer cam mechanism (82), the other of the cam receiving portion and the cam is provided to be inclined with respect to the axial direction of the movable sheave shaft portion (66). The pulley device described in Crab. The pulley device according to claim 6, wherein the state of inclination of the inner cam mechanism (81) and the state of inclination of the outer cam mechanism (82) are different. The pulley device according to any one of claims 1 to 7, wherein the cylindrical member (55) is a spring seat (55) that supports one end (53a) of the spring (53). The spring seat (55) includes a flange portion (55b) extending radially outward from the cylindrical portion (55a) and supporting the one end (53a) of the spring (53),
9. The spring (53) is a coil spring, and the cylindrical portion (55a) and the movable sheave shaft portion (66) are arranged radially inside the spring (53). pulley device. The spring seat (55) is made of resin,
The fixed sheave (51) includes a fixed sheave part (58) facing the sheave part (65) and a fixed sheave shaft part (59) extending in the axial direction from the fixed sheave part (58). Prepare,
The movable sheave (52) has the movable sheave shaft (66) fitted into the fixed sheave shaft (59),
The movable sheave (52) is supported by a bearing (56) made of a self-lubricating material and disposed between the movable sheave shaft (66) and the fixed sheave shaft (59). The pulley device according to claim 8 or 9.

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