WO2023171241A1 - Pulley device - Google Patents

Pulley device Download PDF

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Publication number
WO2023171241A1
WO2023171241A1 PCT/JP2023/004616 JP2023004616W WO2023171241A1 WO 2023171241 A1 WO2023171241 A1 WO 2023171241A1 JP 2023004616 W JP2023004616 W JP 2023004616W WO 2023171241 A1 WO2023171241 A1 WO 2023171241A1
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WO
WIPO (PCT)
Prior art keywords
fixed
pulley
movable
intervening member
driven pulley
Prior art date
Application number
PCT/JP2023/004616
Other languages
French (fr)
Japanese (ja)
Inventor
諭 川頭
英紀 永坂
友太 横道
克 吉本
達也 北山
Original Assignee
株式会社エフ・シー・シー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社エフ・シー・シー filed Critical 株式会社エフ・シー・シー
Publication of WO2023171241A1 publication Critical patent/WO2023171241A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable

Definitions

  • the present invention relates to a pulley device that transmits the driving force of a driving source such as an engine.
  • Patent Document 1 describes a fixed side driven plate (hereinafter referred to as a fixed side driven pulley) and a movable side driven plate (hereinafter referred to as a movable side driven pulley) that are rotationally driven by receiving the driving force of the engine via a belt.
  • a centrifugal clutch is disclosed that includes a pulley device having a. In this case, the driving force (rotational driving force) received by the movable driven pulley is transmitted to the fixed driven pulley via the cylindrical cam-formed cylinder that fits into the movable driven pulley and the fixed driven pulley, respectively. be done.
  • the present invention has been made in view of the above, and its object is to provide a pulley device in which the burden of ensuring rigidity against torsion when transmitting the driving force received by the movable driven pulley to the fixed driven pulley is reduced.
  • the goal is to provide the following.
  • a pulley device includes a fixed driven pulley and a movable driven pulley that are rotationally driven by a driving force from a drive source transmitted via a belt, and the fixed driven pulley has a cylindrical shape.
  • a fixed sleeve formed in the shape of a fixed sleeve, a fixed pulley positioned radially outside of the fixed sleeve, and a plurality of fixed side driven pulleys arranged in the rotational direction when the direction in which the fixed driven pulley rotates is the rotational direction.
  • the movable-side driven pulley is formed in a cylindrical shape, and has a movable-side sleeve that fits onto the fixed-side sleeve; and a radially outer side of the movable-side sleeve.
  • a movable pulley located at and sandwiching the belt together with the fixed pulley and configured to be able to approach and separate from the fixed pulley; and a plurality of movable cam portions lined up in the rotation direction.
  • the fixed side cam part is inserted into the through hole, and further includes an intervening member interposed between the fixed driven pulley and the movable driven pulley, and the intervening member is inserted into the through hole.
  • the member is located between the fixed cam part and the movable cam part with respect to the rotational direction, and is configured to be slidable with respect to the movable cam part, and the movable cam part is located between the fixed cam part and the movable cam part.
  • the stationary cam portion is configured to be pressable via an intervening member.
  • the movable cam portion is configured to be able to press the fixed cam portion via the intervening member configured to be slidable with respect to the movable cam portion. Therefore, the rotational driving force received by the movable driven pulley is indirectly transmitted to the stationary driven pulley via the intervening member. At this time, since no torsional stress is generated in the intervening member, the burden of ensuring rigidity against torsion is reduced.
  • FIG. 1 is a sectional view showing a power transmission mechanism including a pulley device and a centrifugal clutch according to a first embodiment.
  • FIG. 2 is a partially enlarged sectional view showing a power transmission mechanism including a pulley device and a centrifugal clutch according to the first embodiment.
  • FIG. 3 is an exploded perspective view of the driven pulley according to the first embodiment.
  • FIG. 4 is an exploded perspective view of the driven pulley according to the first embodiment.
  • FIG. 5 is a perspective view showing the configuration of a wall portion of the stationary driven pulley and its surroundings according to the first embodiment.
  • FIG. 6 is a perspective view showing a state in which an intervening member is in contact with a wall portion of the stationary driven pulley according to the first embodiment.
  • FIG. 7 is a plan view showing a state in which the intervening member is in contact with the wall portion of the stationary driven pulley according to the first embodiment.
  • FIG. 8A is a perspective view of an intermediate sleeve including an intervening member according to the first embodiment.
  • FIG. 8B is a perspective view of an intermediate sleeve with an intervening member according to the first embodiment.
  • FIG. 9A is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley approaches the fixed driven pulley.
  • FIG. 9B is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley is spaced apart from the fixed driven pulley.
  • FIG. 10 is a cross-sectional view showing a state in which the fixed cam section presses the movable cam section.
  • FIG. 11 is a partially enlarged sectional view showing a power transmission mechanism including a pulley device and a centrifugal clutch according to the second embodiment.
  • FIG. 12 is an exploded perspective view of the driven pulley according to the second embodiment.
  • FIG. 13 is an exploded perspective view of the driven pulley according to the second embodiment.
  • FIG. 14 is a perspective view of the stationary driven pulley according to the second embodiment.
  • FIG. 15 is a perspective view showing a state in which an intervening member is in contact with a wall according to the second embodiment.
  • FIG. 16 is a plan view showing a state in which an intervening member is in contact with a wall according to the second embodiment.
  • FIG. 17 is a side view of the stationary driven pulley according to the second embodiment.
  • FIG. 18 is a rear view showing a state in which the intervening member according to the second embodiment is attached to the stationary driven pulley.
  • FIG. 19A is a perspective view of an intervening member according to the second embodiment.
  • FIG. 19B is a perspective view of an intervening member according to the second embodiment.
  • FIG. 20 is a rear view showing a state in which the washer and circlip for preventing the intervening member from falling off according to the second embodiment are attached to the stationary driven pulley.
  • FIG. 21A is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley approaches the fixed driven pulley.
  • FIG. 22B is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley is spaced apart from the fixed driven pulley.
  • FIG. 22 is a sectional view showing a state in which the fixed side cam part presses the movable side cam part.
  • FIG. 1 is a sectional view showing a power transmission mechanism 100 including a pulley device 130 and a centrifugal clutch 200 according to the present embodiment.
  • FIG. 2 is a partially enlarged sectional view showing the power transmission mechanism 100 including the pulley device 130 and the centrifugal clutch 200.
  • the movable driven pulley 150 located above the center line CL is closest to the fixed driven pulley 140
  • the movable driven pulley 150 located above the center line CL is closest to the fixed driven pulley 140.
  • the movable driven pulley 150 is shown in a state farthest away from the fixed driven pulley 140.
  • the direction in which the movable pulley 151 moves away from the fixed pulley 141 is referred to as a first direction D1
  • the direction in which the movable pulley 151 approaches the fixed pulley 141 is referred to as a second direction D2.
  • the direction in which the fixed driven pulley 140 and the movable driven pulley 150 rotate is defined as a rotation direction L (see FIG. 3).
  • the power transmission mechanism 100 is mainly provided in a motorcycle such as a scooter between an engine as a drive source and a rear wheel as a drive wheel.
  • the power transmission mechanism 100 is a device that transmits or cuts off rotational driving force to the rear wheels while automatically changing the gear ratio with respect to the rotational speed of the engine.
  • the power transmission mechanism 100 includes a transmission 101 and a centrifugal clutch 200.
  • the transmission 101 is a device that continuously changes the speed of rotational driving force from an engine (not shown) and transmits it to the centrifugal clutch 200.
  • the transmission 101 includes a drive pulley 110, a V-belt 120, and a pulley device 130.
  • the transmission 101 has a diameter across the V-belt 120 defined by the spacing between a fixed drive pulley 112 and a movable drive pulley 113, which will be described later, and a V diameter defined by the spacing between a fixed driven pulley 140 and a movable driven pulley 150.
  • the rotational speed of the drive shaft 146 is varied steplessly depending on the size relationship with the diameter of the belt 120.
  • the drive pulley 110 is provided on a crankshaft 111 extending from the engine.
  • the drive pulley 110 is a device that is directly rotationally driven by the rotational driving force of the engine.
  • Drive pulley 110 includes a fixed drive pulley 112 and a movable drive pulley 113.
  • the fixed drive pulley 112 and the movable drive pulley 113 sandwich the V-belt 120.
  • the fixed drive pulley 112 is fixed to the crankshaft 111 with its convex surface facing toward the movable drive pulley 113 (that is, toward the engine). That is, the fixed drive pulley 112 is always driven to rotate integrally with the crankshaft 111.
  • the movable drive pulley 113 is attached to the crankshaft 111 with its convex surface facing the fixed drive pulley 112.
  • the movable drive pulley 113 is mounted on a sleeve bearing 114 fixed to the crankshaft 111 via an impregnated bush.
  • the movable drive pulley 113 is configured to be slidable in the axial direction and rotational direction L with respect to the sleeve bearing 114.
  • a plurality of roller weights 115 are provided on the concave side surface of the movable drive pulley 113 while being pressed by a ramp plate 116.
  • the roller weight 115 is a member that is displaced radially outward in response to an increase in the number of rotations of the movable drive pulley 113.
  • the roller weight 115 is a member that cooperates with the ramp plate 116 to press the movable drive pulley 113 toward the fixed drive pulley 112.
  • the ramp plate 116 is a member that presses the roller weight 115 toward the movable drive pulley 113.
  • the V-belt 120 is a member for transmitting the rotational driving force of the drive pulley 110 to the driven pulley 131 of the pulley device 130.
  • the V-belt 120 is formed into an endless ring shape.
  • the V-belt 120 is disposed between the fixed drive pulley 112 and the movable drive pulley 113 and between the fixed driven pulley 140 and the movable driven pulley 150 of the driven pulley 131, and is arranged between the fixed drive pulley 112 and the movable driven pulley 131. wrapped between.
  • a V-belt is an example of a belt.
  • the pulley device 130 is a device that is rotationally driven by the rotational driving force from the engine transmitted via the drive pulley 110 and the V-belt 120.
  • the pulley device 130 includes a driven pulley 131.
  • the driven pulley 131 includes a fixed driven pulley 140, a movable driven pulley 150, and an intervening member 161 interposed between the fixed driven pulley 140 and the movable driven pulley 150.
  • the driven pulley 131 includes an intermediate sleeve 160 with an intervening member 161.
  • the fixed driven pulley 140 and the movable driven pulley 150 are rotationally driven by the driving force from the engine transmitted via the V-belt 120.
  • the fixed driven pulley 140 and the movable driven pulley 150 sandwich the V-belt 120.
  • the stationary driven pulley 140 is made of a metal material such as aluminum material.
  • the fixed driven pulley 140 includes a fixed pulley 141, a fixed sleeve 142, a through hole 143, and a fixed cam portion 144.
  • the stationary pulley 141, the stationary sleeve 142, and the stationary cam part 144 are integrally molded from the same material, but they are molded as separate parts and welded together. May be connected.
  • the fixed pulley 141 and the movable pulley 151 sandwich the V-belt 120.
  • the fixed pulley 141 is formed in an annular shape.
  • the fixed pulley 141 is located on the outer side of the fixed sleeve 142 in the radial direction.
  • the fixed sleeve 142 is a member that rotates integrally with the fixed pulley 141.
  • the fixed sleeve 142 is formed into a cylindrical shape.
  • One end of the stationary sleeve 142 (the right end in FIGS. 1 and 2) is connected to the stationary pulley 141 via a stationary cam portion 144.
  • the other end of the stationary sleeve 142 (the left end in FIGS. 1 and 2) is connected to the drive plate 210 of the centrifugal clutch 200 via a connector 148.
  • the connector 148 has a plurality of through holes formed in its outer peripheral portion, and is cast into the stationary sleeve 142 when the stationary driven pulley 140 is die-cast. As shown in FIG.
  • an escape groove 143A is formed in one end of the stationary sleeve 142 and is concave toward the inside in the radial direction and is spaced apart from the intervening member 161.
  • the escape groove 143A is formed with a depth and a width such that the intervening member 161 does not come into contact with it.
  • the fixed cam portion 144 is located between the fixed sleeve 142 and the fixed pulley 141 in the radial direction.
  • three fixed side cam parts 144 are lined up at equal intervals in the rotation direction L.
  • the fixed cam portion 144 is a portion on which the movable cam portion 153 (see FIG. 4) slides via the intervening member 161.
  • the fixed cam portion 144 has a fixed contact surface 144M with which the intervening member 161 or the movable cam portion 153 comes into contact.
  • the fixed side contact surface 144M is formed at the fixed side contact surface 144MA formed at one end of the fixed side cam part 144 in the rotation direction L, and at the other end of the fixed side cam part 144 in the rotation direction L.
  • the fixed side contact surface 144MA is located on the downstream side of the intervening member 161 in the rotation direction L.
  • Fixed side sliding surface 144MB is located upstream of intervening member 161 in rotation direction L.
  • the fixed-side sliding surface 144MB is a surface on which the movable-side cam portion 153 can slide.
  • the fixed side contact surface 144MA and the fixed side sliding surface 144MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotation direction L.
  • the fixed side contact surface 144MA is a cam surface that receives rotational driving force from the engine from the movable cam portion 153 via the intervening member 161.
  • the fixed side sliding surface 144MB is a cam surface that applies back torque from the driving wheel side to the movable side cam portion 153.
  • a portion of the fixed cam portion 144 is located closer to the movable pulley 151 (on the first direction D1 side) than the through hole 143 is.
  • the through-hole 143 is formed between the fixed-side cam parts 144 adjacent to each other in the rotation direction L in the fixed-side driven pulley 140.
  • three through holes 143 are arranged at equal intervals in the rotation direction L.
  • the through hole 143 is formed in a long hole shape.
  • An intervening member 161 and a movable cam portion 153, which will be described later, are inserted into the through hole 143.
  • the stationary driven pulley 140 includes a wall portion 145 that partitions a portion of the through hole 143.
  • the wall portion 145 is a part of the fixed cam portion 144.
  • the wall portion 145 is an example of a suppressing member.
  • the wall portion 145 is located on the outer side of the intervening member 161 in the radial direction.
  • the wall portion 145 is continuous with the fixed side contact surface 144MA.
  • the wall portion 145 is located on the outer side in the radial direction than the fixed side contact surface 144MA.
  • the wall portion 145 is formed along the fixed side contact surface 144MA.
  • the wall portion 145 is in contact with the intervening member 161 (here, surface contact).
  • the wall portion 145 suppresses radially outward deformation of the intervening member 161. That is, when the stationary driven pulley 140 rotates in the rotation direction L, the centrifugal force acting on the intervening member 161 causes the intervening member 161 to spread outward in the radial direction; Since the wall portion 145 is disposed, radially outward deformation of the intervening member 161 is suppressed.
  • a drive shaft 146 is arranged within the fixed sleeve 142 of the fixed driven pulley 140.
  • the drive shaft 146 is an axis for driving the rear wheel of the motorcycle on which the power transmission mechanism 100 is mounted via a transmission.
  • the rear wheel of the motorcycle is indirectly attached to one end (not shown) of the drive shaft 146 (on the right side in FIG. 2).
  • the drive shaft 146 supports the stationary driven pulley 140 via bearings 147a and 147b.
  • a clutch outer 230 is attached to the left end of the drive shaft 146 in FIG.
  • the drive shaft 146 is shown by a two-dot chain line.
  • the movable driven pulley 150 and the fixed driven pulley 140 sandwich the V-belt 120.
  • the movable driven pulley 150 is made of a metal material such as aluminum.
  • the movable driven pulley 150 includes a movable pulley 151, a movable sleeve 152 (see FIG. 3), and a movable cam portion 153.
  • the movable pulley 151, the movable sleeve 152, and the movable cam part 153 are integrally molded from the same material, but they are molded as separate parts and are welded together. May be connected.
  • the movable pulley 151 and the fixed pulley 141 sandwich the V-belt 120.
  • the movable pulley 151 is formed in an annular shape.
  • the movable pulley 151 is located on the outer side of the movable sleeve 152 in the radial direction.
  • the movable pulley 151 is configured to be able to approach and separate from the fixed pulley 141.
  • the movable sleeve 152 is a member that rotates integrally with the movable pulley 151.
  • the movable sleeve 152 is formed into a cylindrical shape.
  • the movable sleeve 152 is fitted onto the fixed sleeve 142 . More specifically, the movable sleeve 152 is externally fitted onto the fixed sleeve 142 via the intermediate sleeve 160. That is, the intermediate sleeve 160 and the fixed sleeve 142 are inserted into the movable sleeve 152.
  • One end of the movable sleeve 152 (the right end in FIGS. 1 and 2) is connected to the movable pulley 151.
  • the movable cam portion 153 extends from the movable pulley 151 toward the fixed pulley 141 (that is, in the direction D2).
  • the movable cam portion 153 is a protrusion.
  • the three movable cam parts 153 are arranged at equal intervals in the rotation direction L.
  • the movable cam portion 153 is inserted into the through hole 143 of the fixed driven pulley 140.
  • the movable cam portion 153 is a portion that slides on the fixed cam portion 144 via the intervening member 161.
  • the movable cam portion 153 is configured to be able to press the fixed cam portion 144 via the intervening member 161.
  • the movable cam portion 153 has a movable sliding surface 153M on which the intervening member 161 or the fixed cam portion 144 slides.
  • the movable sliding surface 153M includes a first movable sliding surface 153MA formed at one end of the movable cam section 153 in the rotational direction L, and the other end of the movable cam section 153 in the rotational direction L. It has a second movable side sliding surface 153MB formed in .
  • the first movable sliding surface 153MA is located upstream of the intervening member 161 in the rotation direction L.
  • the second movable sliding surface 153MB is located upstream of the first movable sliding surface 153MA in the rotation direction L.
  • the first movable sliding surface 153MA and the second movable sliding surface 153MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotational direction L.
  • the first movable sliding surface 153MA is a cam surface that applies rotational driving force from the engine to the fixed cam portion 144 via the intervening member 161.
  • the second movable sliding surface 153MB is a cam surface that receives back torque from the driving wheel side from the fixed cam portion 144.
  • the movable sliding surface 153M and the fixed contact surface 144M are formed parallel to each other.
  • the first movable side sliding surface 153MA and the fixed side contact surface 144MA are formed parallel to each other.
  • the second movable sliding surface 153MB and the fixed sliding surface 144MB are formed parallel to each other.
  • the intermediate sleeve 160 is arranged between the fixed driven pulley 140 and the movable driven pulley 150. As shown in FIGS. 8A and 8B, the intermediate sleeve 160 includes an intervening member 161, a cylindrical member 163, and a hook member 162.
  • the cylindrical member 163 is a member for guiding the movable driven pulley 150 in the axial direction.
  • the cylindrical member 163 is arranged between the fixed sleeve 142 and the movable sleeve 152.
  • the cylindrical member 163 is slidably fitted on the outside of the stationary sleeve 142 and slidably fitted on the inside of the movable sleeve 152.
  • the cylindrical member 163 has a longer length in the axial direction than the movable sleeve 152.
  • the cylindrical member 163 has substantially the same length in the axial direction as the stationary sleeve 142. As shown in FIG.
  • the cylindrical member 163 has a contact portion 163A that restricts the intervening member 161 from moving in the second direction D2.
  • the contact portion 163A is an example of a second regulating member.
  • the contact portion 163A is configured to be able to come into contact with a surface 144A (see FIG. 3) of the fixed side cam portion 144 in the first direction D1.
  • the intervening member 161 extends from the end of the cylindrical member 163 toward the fixed pulley 141.
  • three intervening members 161 are arranged at equal intervals in the rotation direction L.
  • the intervening member 161 is inserted into the through hole 143 of the stationary driven pulley 140 and attached to the stationary driven pulley 140.
  • the intervening member 161 is located between the fixed cam part 144 and the movable cam part 153 in the rotation direction L.
  • the intervening member 161 is provided between the fixed side contact surface 144MA of the fixed side cam part 144 and the first movable side sliding surface 153MA of the movable side cam part 153, and Although it is not provided between the moving surface 144MB and the second movable sliding surface 153MB of the movable cam portion 153, it is provided between the fixed sliding surface 144MB and the second movable sliding surface 153MB. You can leave it there.
  • the intervening member 161 is configured to be slidable with respect to the movable cam portion 153. As shown in FIG. 9A, when the intervening member 161 is sandwiched between the movable cam portion 153 and the fixed contact surface 144MA, there is a gap between the movable cam portion 153 and the fixed sliding surface 144MB. It is formed.
  • the intervening member 161 has an intervening contact surface 161M that is arranged opposite to the fixed contact surface 144M.
  • the intervening side contact surface 161M is a surface that comes into contact with the fixed side cam portion 144.
  • the intervening contact surface 161M is a surface on which the movable cam portion 153 slides.
  • the intervening contact surface 161M is configured to slide in surface contact with the movable sliding surface 153M.
  • the intervening side contact surface 161M includes an intervening side contact surface 161MA formed at one end of the intervening member 161 in the rotation direction L, and an intervening side slide formed at the other end of the intervening member 161 in the rotation direction L. It has a moving surface of 161MB.
  • the intervening side contact surface 161MA faces the fixed side contact surface 144MA.
  • the intervening side contact surface 161MA makes surface contact with the stationary side contact surface 144MA.
  • the intervening sliding surface 161MB faces the fixed sliding surface 144MB via the movable cam portion 153.
  • the intervening sliding surface 161MB faces the first movable sliding surface 153MA.
  • the intervening sliding surface 161MB slides in surface contact with the first movable sliding surface 153MA.
  • the intervening side contact surface 161MA and the intervening side sliding surface 161MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotational direction L.
  • the hook member 162 is formed at the tip of the intervening member 161 (the end on the second direction D2 side).
  • the hook member 162 is an example of a first regulating member.
  • the hook member 162 restricts the intervening member 161 from moving in the first direction D1.
  • the hook member 162 is hooked on a part of the stationary driven pulley 140 (for example, the stationary cam portion 144).
  • the intervening member 161, the cylinder member 163, and the hook member 162 are integrally formed from the same material.
  • the intervening member 161, the cylindrical member 163, and the hook member 162 are made of a different material from the material forming the fixed cam portion 144 and the movable cam portion 153.
  • the intervening member 161 is made of, for example, a material with lower wear resistance than the fixed cam part 144 and the movable cam part 153.
  • the intervening member 161, the cylinder member 163, and the hook member 162 have a lower water absorption rate (for example, 0.1% to 2.0%) than the water absorption rate (for example, 3.0%) of the polyamide resin (for example, polyamide 46). formed from material.
  • the intervening member 161, the cylinder member 163, and the hook member 162 are made of, for example, resin material, paper, carbon fiber, carbon nanotubes, metal, or the like.
  • resin material for example, a thermoplastic resin or a thermosetting resin having heat resistance and wear resistance can be used, and engineering plastics or super engineering plastics are preferable.
  • the thermoplastic resin includes polyamide resin, polyetheretherketone resin (PEEK), polyphenylene sulfide resin (PPS), polyamideimide resin (PAI), fluororesin (PTFE), polyimide resin (PI), etc. Can be mentioned.
  • the thermosetting resin include diallyl phthalate resin (PDAP), epoxy resin (EP), polyimide resin, phenol resin, and silicone resin (SI).
  • a torque spring 170 is provided on the outside of the movable sleeve 152 in the radial direction. Torque spring 170 is provided between movable pulley 151 and drive plate 210. Torque spring 170 presses movable driven pulley 150 toward fixed driven pulley 140.
  • the torque spring is, for example, a coil spring.
  • the centrifugal clutch 200 is a device that transmits or interrupts the rotational driving force of the engine transmitted via the transmission 101 to the drive shaft 146.
  • the centrifugal clutch 200 interrupts transmission of rotational driving force to the drive shaft 146 until the engine reaches a predetermined rotational speed, and transmits the rotational driving force to the drive shaft 146 when the engine reaches a predetermined rotational speed. It is a device that transmits information to The centrifugal clutch 200 is provided at the distal end of the stationary sleeve 142 and the drive shaft 146.
  • the centrifugal clutch 200 includes a drive plate 210, three clutch weights 220, and a clutch outer 230.
  • the drive plate 210 is driven to rotate integrally with the stationary sleeve 142.
  • a through hole is formed in the center of the bottom 211 of the drive plate 210, into which the connector 148 is inserted.
  • a flange-shaped flange portion 212 is formed on the radially outer side of the bottom portion 211 .
  • a torque spring 170 is provided at the boundary between the bottom 211 and the flange 212 of the drive plate 210.
  • the collar portion 212 is provided with three swing support pins 213 and three weight presser support portions 215 at equal intervals along the rotation direction L.
  • the swing support pin 213 rotatably supports one end of a clutch weight 220, which will be described later, and swings the other end.
  • the swing support pin 213 is fixed to the collar portion 212 by a caulking portion 213a.
  • the swing support pin 213 passes through the pin sliding hole 222 of the clutch weight 220.
  • the swing support pin 213 and a side plate 214 attached to the tip of the swing support pin 213 support the clutch weight 220 in a sandwiched state.
  • the side plate 214 prevents the clutch weight 220 from coming off the swing support pin 213 by a circlip (not shown).
  • the weight pressing body support section 215 rotatably supports the weight pressing body 216.
  • the weight pressing member support portion 215 is formed to protrude from the collar portion 212 in a pin shape.
  • the weight pressing body 216 has a function of controlling the timing of swinging of the clutch weight 220.
  • the weight pressing body 216 has a function of reducing the pounding noise generated when the clutch shoe 221 contacts the clutch outer 230.
  • the clutch weight 220 contacts or separates from the clutch outer 230 via the clutch shoe 221 depending on the rotation speed of the drive plate 210. This transmits or blocks the rotational driving force from the engine to the drive shaft 146.
  • the clutch shoe 221 is a member for increasing the frictional force against the inner peripheral surface of the clutch outer 230.
  • Clutch shoe 221 is made of a friction material.
  • the clutch shoe 221 is attached to the outer peripheral surface of the clutch weight 220.
  • Adjacent clutch weights 220 are connected by a connection spring 223 and pulled toward the inside of the drive plate 210 in the radial direction. That is, the clutch weight 220 is supported on the drive plate 210 via the swing support pin 213 and the pin sliding hole 222 so that the portion where the clutch shoe 221 is provided swings relative to the clutch outer 230. There is.
  • connection spring 223 is a member that pulls the clutch weight 220 in a direction away from the clutch outer 230.
  • the connection springs 223 are provided between the clutch weights 220 adjacent to each other along the rotation direction L of the drive plate 210.
  • a pressing body accommodating portion 224 is formed on the inner surface of each clutch weight 220 facing the drive plate 210.
  • the pressing body accommodating portion 224 accommodates the weight pressing body 216.
  • a pressing body receiving portion 224a against which the weight pressing body 216 is pressed is formed in the pressing body accommodating portion 224.
  • the pressing body receiving portion 224a is formed by cutting out a concave shape on the inner surface of the clutch weight 220.
  • the pressing body receiving portion 224a is a portion that generates a resistance force when the clutch weight 220 is displaced toward the clutch outer 230 side by being pressed against the weight pressing body 216.
  • the clutch outer 230 is rotationally driven integrally with the drive shaft 146.
  • Clutch outer 230 is formed into a cup shape that covers drive plate 210 and clutch weight 220.
  • Clutch outer 230 has a cylindrical surface 231 that contacts clutch shoe 221 of clutch weight 220.
  • the centrifugal clutch 200 interrupts transmission of driving force between the engine and the drive shaft 146 when the engine is stopped or idling, as shown in FIG.
  • the fixed side driven pulley 140 and the movable side driven pulley 150 are rotationally driven by the rotational driving force of the engine transmitted via the V-belt 120.
  • the movable cam portion 153 presses the fixed cam portion 144 via the intervening member 161.
  • the drive plate 210 is driven to rotate at the same rotational speed as the fixed driven pulley 140 and the movable driven pulley 150.
  • the clutch weight 220 provided on the drive plate 210 is rotated at the same rotation speed as the drive plate 210.
  • the centrifugal force acting on the clutch weight 220 is smaller than the elastic force (tensile force) of the connection spring 223, so the clutch shoe 221 does not contact the cylindrical surface 231 of the clutch outer 230. Therefore, in the centrifugal clutch 200, the rotational driving force of the engine is not transmitted to the drive shaft 146, and the clutch is in an off state.
  • the movable driven pulley 150 In the clutch-off state, the movable driven pulley 150 is pushed by the elastic force of the torque spring 170 and the cam thrust to a position closest to the stationary driven pulley 140 or a position in the vicinity thereof. Therefore, as shown in FIG. 9A, when the movable cam portion 153 has entered deeply into the through hole 143, the first movable sliding surface 153MA is connected to the fixed contact surface 144MA via the intervening member 161. The rotational driving force is transmitted to the stationary driven pulley 140.
  • the contact area between the first movable sliding surface 153MA and the fixed contact surface 144MA via the intervening member 161 has a maximum value or a value close to the maximum value.
  • the movable driven pulley 150 can stably transmit rotational driving force to the stationary driven pulley 140 even at low engine speeds where the engine speed tends to be unstable, such as when the engine is idling.
  • the intervening member 161 is placed between the movable cam portion 153 and the fixed cam portion 144. Therefore, the pressing force from the movable cam portion 153 is transmitted in the thickness direction of the intervening member 161 and then to the fixed cam portion 144. That is, since a large torsional stress is not applied to the intervening member 161 when the pressing force from the movable cam part 153 is transmitted to the fixed cam part 144, it is not necessary to have high torsional rigidity.
  • the centrifugal clutch 200 transmits the rotational driving force of the engine to the drive shaft 146.
  • the centrifugal force acting on the clutch weight 220 becomes larger than the elastic force (tensile force) of the connection spring 223.
  • the clutch weight 220 is rotationally displaced radially outward about the swing support pin 213. That is, the clutch weight 220 is rotationally displaced toward the cylindrical surface 231 of the clutch outer 230 while resisting the elastic force (tensile force) of the connection spring 223, and the clutch shoe 221 comes into contact with the cylindrical surface 231.
  • the clutch shoe 221 is then pressed against the cylindrical surface 231.
  • the centrifugal clutch 200 enters a clutch-on state in which the rotational driving force of the engine is completely transmitted to the drive shaft 146. Therefore, the motorcycle runs with the rear wheels rotationally driven by the rotational driving force of the engine.
  • the driven pulley 131 moves in a direction (in which the movable driven pulley 150 moves away from the fixed driven pulley 140 against the elastic force of the torque spring 170 and the cam thrust as the engine speed increases). That is, it moves in the direction D1). That is, the movable cam portion 153 of the movable driven pulley 150 slides in a direction away from the fixed cam portion 144 of the fixed driven pulley 140.
  • the contact area between the first movable sliding surface 153MA and the fixed contact surface 144MA via the intervening member 161 becomes the minimum or a value close to the minimum, but the intervening member 161
  • the state of contact between the fixed side cam part 144 and the movable side cam part 153 via the contact state is maintained. That is, the transmission of the rotational driving force from the movable driven pulley 150 to the fixed driven pulley 140 is maintained.
  • the movable side cam portion 153 of the movable side driven pulley 150 is exposed on the V-belt 120 side (see FIG. 2). Thereby, the heat generated in the bearings 147a, 147b can be released to the outside through the space around the exposed movable cam portion 153.
  • the pressing force from the movable cam portion 153 is transmitted in the thickness direction of the intervening member 161 to the fixed-side cam portion 144, as in the clutch-off state. That is, since a large torsional stress is not applied to the intervening member 161 when the pressing force from the movable cam part 153 is transmitted to the fixed cam part 144, it is not necessary to have high torsional rigidity.
  • the centrifugal clutch 200 cuts off the transmission of the rotational driving force of the engine to the drive shaft 146. Specifically, as the engine speed decreases, the centrifugal force acting on the clutch weight 220 becomes smaller than the elastic force (tensile force) of the connection spring 223, and the clutch weight 220 expands in diameter around the swing support pin 213. rotational displacement toward the inside of the direction.
  • the clutch shoe 221 separates from the cylindrical surface 231 of the clutch outer 230 and returns to its original position (the above-mentioned idling position). That is, the centrifugal clutch 200 is in a clutch-off state in which the clutch shoe 221 does not contact the clutch outer 230 and does not transmit rotational driving force.
  • the movable driven pulley 150 moves in the direction closer to the fixed driven pulley 140 (that is, the direction D2) due to the elastic force of the torque spring 170 and the cam thrust.
  • the amount of exposure of the movable cam portion 153 of the movable driven pulley 150 to the V-belt 120 side is reduced, and the amount of fitting (insertion amount) with the fixed cam portion 144 is increased.
  • the centrifugal force acting on the intervening member 161 causes the intervening member 161 to spread outward in the radial direction.
  • the wall portion 145 is disposed on the radially outer side of the intervening member 161, radially outward deformation of the intervening member 161 is suppressed. This suppresses damage to the intervening member 161.
  • the movable cam portion 153 presses the fixed cam portion 144 via the intervening member 161 configured to be slidable with respect to the movable cam portion 153. configured to be possible. Therefore, the rotational driving force received by the movable driven pulley 150 is indirectly transmitted to the fixed driven pulley 140 via the intervening member 161. At this time, since no torsional stress is generated in the intervening member 161, the burden of ensuring rigidity against torsion is reduced.
  • the movable cam portion 153 extends from the movable pulley 151 toward the fixed pulley 141 and is inserted into the through hole 143. According to the above aspect, the rotational driving force received by the movable driven pulley 150 can be effectively transmitted to the fixed driven pulley 140.
  • the stationary cam portion 144 is located between the stationary sleeve 142 and the stationary pulley 141 in the radial direction. According to the above aspect, the rotational driving force received by the movable driven pulley 150 can be effectively transmitted to the fixed driven pulley 140.
  • the pulley device 130 of this embodiment includes a hook member 162 that restricts movement of the intervening member 161 in the first direction D1. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
  • the hook member 162 is formed at the tip of the intervening member 161 and hooks on a part of the stationary driven pulley 140. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
  • the pulley device 130 of this embodiment has a contact portion 163A that restricts the intervening member 161 from moving in the second direction D2. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
  • the contact portion 163A is configured to be able to contact the surface 144A of the fixed side cam portion 144 in the first direction D1. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
  • the movable sliding surface 153M and the fixed contact surface 144M are formed parallel to each other. According to the above aspect, the rotational driving force received by the movable driven pulley 150 can be effectively transmitted to the fixed driven pulley 140 via the intervening member 161.
  • the intervening member 161 is made of, for example, a material with lower wear resistance than the fixed cam portion 144 and the movable cam portion 153. According to the above aspect, wear of the fixed cam portion 144 and the movable cam portion 153 can be suppressed.
  • the intervening member 161 in a state where the intervening member 161 is sandwiched between the movable cam portion 153 and the fixed side contact surface 144MA, there is no space between the movable cam portion 153 and the fixed side sliding surface 144MB. A gap is formed. According to the above aspect, the intervening member 161 can be easily assembled to the stationary driven pulley 140. Furthermore, even if the intervening member 161 thermally expands, it does not pinch the movable cam portion 153, so it is possible to suppress the occurrence of sliding failures of the movable driven pulley 150.
  • the pulley device 130 of this embodiment includes a cylindrical member 163 that is disposed between the fixed sleeve 142 and the movable sleeve 152 and into which the movable sleeve 152 is slidably fitted. According to the above aspect, since the fixed sleeve 142 and the movable sleeve 152 do not directly slide, wear and seizure can be suppressed.
  • a portion of the fixed cam portion 144 is located closer to the movable pulley 151 (on the first direction D1 side) than the through hole 143 is. According to the above aspect, since the contact area between the stationary cam portion 144 and the intervening contact surface 161M of the intervening member 161 becomes large, the surface pressure can be reduced. That is, the durability of the stationary cam portion 144 and the intervening member 161 is improved.
  • the stationary sleeve 142 is formed with an escape groove 143A that is recessed toward the inside in the radial direction and is spaced apart from the intervening member 161. According to the above aspect, the stationary sleeve 142 can be easily molded.
  • the intervening member 161 tends to deform outward in the radial direction due to centrifugal force, but the fixed driven pulley 140 A wall portion 145 is provided that is located on the outer side of the intervening member 161 in the radial direction and suppresses deformation of the intervening member 161 to the outside in the radial direction.
  • excessive stress is not applied to the intervening member 161 attached to the stationary driven pulley 140, and damage to the intervening member 161 is suppressed.
  • the wall portion 145 partitions a part of the through hole 143.
  • the wall portion 145 that partitions a portion of the through hole 143 can suppress deformation of the intervening member 161 toward the outside in the radial direction. That is, there is no need to provide a separate member, and an increase in the number of parts of the pulley device 130 can be suppressed.
  • the fixed side cam portion 144 has a fixed side contact surface 144M with which the intervening member 161 contacts, and the wall portion 145 is continuous with the fixed side contact surface 144M and has a fixed side contact surface 144M. It is located radially outward. According to the above aspect, radially outward deformation of the intervening member 161 can be more reliably suppressed.
  • the fixed side contact surface 144M is located downstream of the intervening member 161 in the rotational direction L and is in contact with the intervening member 161.
  • the wall portion 145 is continuous with and fixed to the fixed side contact surface 144MA. It is located on the outer side in the radial direction than the side contact surface 144MA.
  • the wall portion 145 is Since it is continuous with the abutment surface 144MA and is located radially outward from the fixed side abutment surface 144MA, deformation of the intervening member 161 radially outward can be more reliably suppressed.
  • the wall portion 145 may be continuous with the fixed-side sliding surface 144MB and may be located on the outer side of the fixed-side sliding surface 144MB in the radial direction.
  • the fixed side contact surface 144M formed in a spiral shape and the intervening side contact surface 161M formed in a spiral shape are configured to make surface contact. According to the above aspect, the driving force can be transmitted from the movable driven pulley 150 to the fixed driven pulley 140 more efficiently.
  • the intervening member 161 is formed from a material having a water absorption rate lower than that of polyamide resin. According to the above aspect, the function of the intervening member 161 can be more reliably exhibited.
  • FIG. 11 is a partially enlarged sectional view showing a power transmission mechanism 300 including a pulley device 330 and a centrifugal clutch 200 according to the second embodiment.
  • the power transmission mechanism 300 differs from the power transmission mechanism 100 according to the first embodiment in that it includes a pulley device 330 instead of the pulley device 130.
  • the pulley device 330 includes a driven pulley 331.
  • the driven pulley 331 includes a fixed driven pulley 340, a movable driven pulley 150, and an intervening member 361 interposed between the fixed driven pulley 340 and the movable driven pulley 150.
  • the fixed driven pulley 340 and the movable driven pulley 150 are rotationally driven by the driving force from the engine transmitted via the V-belt 120.
  • the fixed driven pulley 340 and the movable driven pulley 150 sandwich the V-belt 120.
  • the stationary driven pulley 340 is made of a metal material such as aluminum material.
  • the fixed driven pulley 340 includes a fixed pulley 341, a fixed sleeve 342, a through hole 343, and a fixed cam portion 344.
  • the stationary pulley 341, the stationary sleeve 342, and the stationary cam part 344 are integrally molded from the same material, but they are molded as separate parts and are welded together. May be connected.
  • the fixed pulley 341 and the movable pulley 151 sandwich the V-belt 120.
  • the fixed pulley 341 is formed in an annular shape.
  • the fixed pulley 341 is located radially outside the fixed sleeve 342.
  • the fixed sleeve 342 is a member that rotates integrally with the fixed pulley 341.
  • the fixed sleeve 342 is formed into a cylindrical shape.
  • One end of the stationary sleeve 342 (the right end in FIG. 11) is connected to the stationary pulley 341 via a stationary cam portion 344.
  • the other end of the stationary sleeve 342 (the left end in FIG. 11) is connected to the drive plate 210 of the centrifugal clutch 200 via a connector 148.
  • the fixed cam portion 344 is located between the fixed sleeve 342 and the fixed pulley 341 in the radial direction.
  • the three fixed side cam parts 344 are lined up at equal intervals in the rotation direction L.
  • the fixed cam portion 344 is a portion on which the movable cam portion 153 slides via the intervening member 361.
  • the fixed side cam portion 344 has a fixed side contact surface 344M with which the intervening member 361 comes into contact.
  • the fixed side contact surface 344M includes a first fixed side contact surface 344MA formed at one end of the fixed side cam section 344 in the rotation direction L, and a first fixed side contact surface 344MA formed at the other end of the fixed side cam section 344 in the rotation direction L.
  • a formed second fixed side contact surface 344MB (see FIG. 14) is included.
  • the first fixed side contact surface 344MA is located downstream of the intervening member 361 in the rotation direction L.
  • the second fixed side contact surface 344MB is located upstream of the intervening member 361 in the rotation direction L.
  • the first fixed-side contact surface 344MA and the second fixed-side contact surface 344MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotation direction L.
  • the first fixed side contact surface 344MA is a cam surface that receives rotational driving force from the engine from the movable cam portion 153 via the intervening member 361.
  • the second fixed side contact surface 344MB is a cam surface that applies back torque from the driving wheel side to the movable side cam portion 153 via the intervening member 361.
  • the through hole 343 is formed between the fixed side cam parts 344 adjacent to each other in the rotation direction L.
  • three through holes 343 are arranged at equal intervals in the rotation direction L.
  • the through hole 343 is formed in a long hole shape. The intervening member 361 and the movable cam portion 153 are inserted into the through hole 343 .
  • the stationary driven pulley 340 includes a wall portion 345 that partitions a portion of the through hole 343.
  • the wall portion 345 is a part of the fixed cam portion 344.
  • the wall portion 345 is an example of a suppressing member.
  • the wall portion 345 is located radially outside of the intervening member 361 (more specifically, a second intervening member 361B to be described later).
  • the wall portion 345 is continuous with the second fixed side contact surface 344MB.
  • the wall portion 345 is located on the outer side in the radial direction than the second fixed side contact surface 344MB.
  • the wall portion 345 is formed along the second fixed side contact surface 344MB.
  • the wall portion 345 is in contact with the intervening member 361 (here, surface contact). Note that there may be a slight gap between the wall portion 345 and the intervening member 361.
  • the wall portion 345 suppresses radially outward deformation of the intervening member 361 (particularly the second intervening member 361B). That is, when the stationary driven pulley 340 rotates in the rotation direction L, the centrifugal force acting on the intervening member 361 causes the intervening member 361 to spread outward in the radial direction; Since the wall portion 345 is disposed, radially outward deformation of the intervening member 361 is suppressed.
  • the stationary driven pulley 340 is located closer to the first direction D1 than the intervening member 361, and includes a regulating wall 346 that restricts the movement of the intervening member 361.
  • the regulation wall 346 is an example of a first regulation member. As shown in FIG. 18, the regulating wall 346 extends in the rotation direction L and in the radial direction. The regulating wall 346 is continuous with the first fixed side contact surface 344MA. The regulating wall 346 is configured to be able to come into contact with the intervening member 361 (here, the first intervening member 361A). Since the regulation wall 346 is located closer to the first direction D1 than the intervening member 361, the intervening member 361 cannot move beyond the regulation wall 346 in the first direction D1.
  • the intermediate sleeve 360 is arranged between the fixed driven pulley 340 and the movable driven pulley 150. As shown in FIG. 12, the intermediate sleeve 360 is formed into a cylindrical shape. The intermediate sleeve 360 is a member for guiding the movable driven pulley 150 in the axial direction. The intermediate sleeve 360 is press-fitted inside the movable sleeve 152 and crimped. The intermediate sleeve 360 is slidably fitted onto the stationary sleeve 342. The intermediate sleeve 360 has a longer axial length than the movable sleeve 152. The cylindrical member 163 has a shorter length in the axial direction than the stationary sleeve 342.
  • the intervening member 361 is made of the same material as the intervening member 161 of the first embodiment described above. As shown in FIG. 18, the intervening member 361 is inserted into the through hole 343 of the stationary driven pulley 340 from the surface side of the stationary pulley 341 in the second direction D2. The intervening member 361 is inserted into the through hole 343 and attached to the stationary driven pulley 340. In this embodiment, three intervening members 361 are arranged at equal intervals in the rotation direction L. The intervening member 361 is located between the first fixed side contact surface 344MA and the second fixed side contact surface 344MB of the fixed side cam portion 344 in the rotation direction L. As shown in FIGS.
  • the intervening member 361 includes a first intervening member 361A that contacts the first fixed-side contact surface 344MA, and a second interposed member 361B that contacts the second fixed-side contact surface 344MB. , a connecting member 361C that connects the radially outer portion of the first intervening member 361A and the radially outer portion of the second intervening member 361B.
  • the first intervening member 361A is located between the first fixed side contact surface 344MA and the movable side cam portion 153.
  • the second intervening member 361B is located between the second fixed side contact surface 344MB and the movable side cam portion 153.
  • the first intervening member 361A and the second intervening member 361B are configured to be slidable with respect to the movable cam portion 153.
  • the intervening member 361 has an intervening contact surface 361M disposed opposite to the fixed contact surface 344M or the movable sliding surface 153M.
  • the intervening side contact surface 361M is a surface that comes into contact with the fixed side cam portion 344.
  • the intervening contact surface 361M is a surface on which the movable cam portion 153 slides.
  • the intervening contact surface 361M is configured to slide in surface contact with the movable sliding surface 153M.
  • the intervening side contact surface 361M is formed between a first intervening side contact surface 361MA (see FIG. 19A) formed at one end of the first intervening member 361A in the rotational direction L and a second intervening member 361B in the rotational direction L.
  • a second intervening side contact surface 361MB (see FIG. 19B) formed at the other end and a first intervening side sliding surface 361MC formed at the other end in the rotational direction L of the first intervening member 361A ( (see FIG. 19B), and a second intervening side sliding surface 361MD (see FIG. 19A) formed at one end of the second intervening member 361B in the rotation direction L.
  • the first intervening side contact surface 361MA faces the first fixed side contact surface 344MA.
  • the first intervening side contact surface 361MA makes surface contact with the first fixed side contact surface 344MA.
  • the second intervening side contact surface 361MB faces the second fixed side contact surface 344MB.
  • the second intervening side contact surface 361MB makes surface contact with the second fixed side contact surface 344MB.
  • the first intervening sliding surface 361MC faces the first movable sliding surface 153MA.
  • the first intervening sliding surface 361MC slides in surface contact with the first movable sliding surface 153MA.
  • the second intervening side sliding surface 361MD faces the second movable side sliding surface 153MB.
  • the second intervening sliding surface 361MD slides in surface contact with the second movable sliding surface 153MB.
  • the first intervening side contact surface 361MA, the second intervening side contact surface 361MB, the first intervening side sliding surface 361MC, and the second intervening side sliding surface 361MD have a spiral shape extending in the axial direction while being twisted in the rotational direction L. It is a curved surface.
  • the stationary driven pulley 340 has a deformation suppressing wall 347 that is formed on the stationary pulley 341 and that suppresses radially outward deformation of the connecting member 361C of the intervening member 361.
  • the deformation suppressing wall 347 is formed in a ring shape.
  • the deformation suppressing wall 347 is arranged on the outside of the stationary cam portion 344 in the radial direction. Note that when the drive source is stopped, a gap is formed between the connecting member 361C and the deformation suppressing wall 347 in the radial direction.
  • the connecting member 361C is slightly displaced radially outward and comes into contact with the deformation suppressing wall 347. Note that positioning of the intervening member 361 with respect to the fixed driven pulley 340 in the radial direction and rotational direction L is performed by bringing the fixed side contact surface 344M and the intervening side contact surface 361M into surface contact, and by deforming the connecting member 361C. This is not done by hitting the restraining wall 347.
  • the stationary driven pulley 340 is equipped with a washer 370 for preventing the intervening member 361 from falling off and a server.
  • a clip 371 is attached.
  • the washer 370 is provided closer to the direction D2 than the intervening member 361.
  • the washer 370 overlaps the connecting member 361C of the intervening member 361 when viewed from the axial direction.
  • the washer 370 is provided so as to be able to come into contact with the connecting member 361C.
  • the circlip 371 is a member for holding the washer 370 on the fixed pulley 341.
  • the circlip 371 is provided closer to the direction D2 than the washer 370.
  • the circlip 371 is held in a circlip holding groove 347A provided in the deformation suppressing wall 347.
  • the circlip 371 is an example of a second regulating member. That is, the circlip 371 restricts the intervening member 361 from moving in the second direction D2.
  • the movable driven pulley 150 is pressed by the torque spring 170 to a position closest to the stationary driven pulley 340 or a position in the vicinity thereof. Therefore, as shown in FIG. 21A, when the movable cam portion 153 has entered deeply into the through hole 343, the first movable sliding surface 153MA is connected to the first fixed abutting surface 344MA by the intervening member 361. are in close contact with each other via the first intervening member 361A, and transmit rotational driving force to the stationary driven pulley 140.
  • the contact area between the first movable sliding surface 153MA and the first fixed contact surface 344MA via the intervening member 361 is at a minimum or a value close to the minimum.
  • the state of contact between the stationary cam portion 344 and the movable cam portion 153 via the intervening member 361 is maintained. That is, the transmission of the rotational driving force from the movable driven pulley 150 to the fixed driven pulley 340 is maintained.
  • the centrifugal force acting on the intervening member 361 causes the intervening member 361 to spread outward in the radial direction.
  • the wall portion 345 and the deformation suppressing wall 347 are arranged on the outside of the intervening member 361 in the radial direction, deformation of the intervening member 361 toward the outside in the radial direction is suppressed. This suppresses damage to the intervening member 361.
  • the movable cam portion 153 presses the fixed cam portion 344 via the intervening member 361 configured to be slidable with respect to the movable cam portion 153. configured to be possible. Therefore, the rotational driving force received by the movable driven pulley 150 is indirectly transmitted to the fixed driven pulley 340 via the intervening member 361. At this time, since no torsional stress is generated in the intervening member 361, the burden of ensuring rigidity against torsion is reduced.
  • the regulating wall 346 is provided on the stationary driven pulley 340 and is located closer to the first direction D1 than the intervening member 361. According to the above aspect, falling of the intervening member 361 from the through hole 343 is suppressed.
  • the circlip 371 is attached to the stationary driven pulley 340. According to the above aspect, falling of the intervening member 361 from the through hole 343 is suppressed.
  • the intervening member 361 tends to deform outward in the radial direction due to centrifugal force, but the fixed driven pulley 340 A wall portion 345 is provided that is located on the outer side of the intervening member 361 in the radial direction and suppresses deformation of the intervening member 361 to the outside in the radial direction. As a result, excessive stress is not applied to the intervening member 361 attached to the stationary driven pulley 340, and damage to the intervening member 361 is suppressed.
  • the wall portion 345 partitions a part of the through hole 343.
  • the wall portion 345 that partitions a portion of the through hole 343 can suppress deformation of the intervening member 361 to the outside in the radial direction. That is, there is no need to provide a separate member, and an increase in the number of parts of the pulley device 330 can be suppressed.
  • the wall portion 345 is continuous with the fixed side contact surface 344M and is located on the outer side of the fixed side contact surface 344M in the radial direction. According to the above aspect, radially outward deformation of the intervening member 361 can be more reliably suppressed.
  • the intervening member 361 is inserted into the through hole 343 from the surface side of the fixed pulley 341 in the second direction D2. According to the above aspect, the intervening member 361 can be easily inserted into the through hole 343 when assembling the pulley device 330.
  • the stationary driven pulley 340 is located on the first direction D1 side with respect to the intervening member 361, and includes a regulating wall 346 that restricts movement of the intervening member 361. According to the above aspect, it is possible to prevent the intervening member 361 inserted into the through hole 343 from falling out in the first direction D1.
  • the regulation wall 346 is continuous with the first fixed side contact surface 344MA. According to the above aspect, it is possible to more reliably prevent the intervening member 361 inserted into the through hole 343 from falling out in the first direction D1.
  • the intervening member 361 includes a first intervening member 361A that contacts the first fixed side contact surface 344MA, a second interposed member 361B that contacts the second fixed side contact surface 344MB, It is equipped with According to the above aspect, it is possible to suppress direct sliding between the fixed side cam part 144 and the movable side cam part 153.
  • the intervening member 361 includes a connecting member 361C that connects the radially outer portion of the first intervening member 361A and the radially outer portion of the second intervening member 361B. . According to the above aspect, the ease of assembling the intervening member 361 is improved.
  • the fixed driven pulley 340 has a deformation suppressing wall 347 formed on the fixed pulley 341 and suppressing radially outward deformation of the connecting member 361C, and has a drive source.
  • a gap is formed between the connecting member 361C and the deformation suppressing wall 347 in the radial direction.
  • the connecting member 361C comes into contact with the deformation suppressing wall 347.
  • the deformation suppressing wall 347 suppresses radially outward deformation of the intervening member 361.
  • the intervening member 361 is positioned relative to the fixed driven pulley 340 in the radial direction and rotational direction L by bringing the fixed side contact surface 344M and the intervening side contact surface 361M into surface contact. According to the above aspect, the intervening member 361 can be arranged more appropriately.
  • the wall portion 145 which is a part of the stationary cam portion 144, suppresses the radially outward deformation of the intervening member 161, but the present invention is not limited thereto.
  • a suppressing member separate from the fixed cam portion 144 may be used to suppress radially outward deformation of the intervening member 161.
  • the wall portion 345 that is a part of the fixed side cam portion 344 suppresses the deformation of the intervening member 361 toward the outside in the radial direction, but the present invention is not limited thereto.
  • a suppressing member separate from the fixed cam portion 344 may be used to suppress radially outward deformation of the intervening member 361.
  • the through hole 143 is formed between the fixed cam parts 144 adjacent to each other in the rotation direction L in the fixed driven pulley 140, and the movable cam part 153 is inserted into the through hole 143. It is not limited to this.
  • the through hole 143 may be formed between adjacent movable cam parts 153 in the rotation direction L in the movable driven pulley 150, and the fixed cam part 144 may be inserted into the through hole 143. That is, the through hole 143 may be formed in the fixed driven pulley 140 or the movable driven pulley 150. The same applies to the through hole 343.
  • the pulley devices 130, 330 are applied to the centrifugal clutch 200, but the invention is not limited thereto.
  • the pulley devices 130, 330 can be widely applied to devices that transmit driving force from a drive source such as an engine or an electric motor to an output shaft such as the drive shaft 146.
  • the pulley devices 130 and 330 can be used in an electric vehicle (for example, an electric vehicle or an electric two-wheeled vehicle) that runs on its own using an electric motor as a drive source.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

The purpose of the present invention is to reduce the burden of ensuring rigidity against torsion when a driving force received by a movable-side driven pulley is transmitted to a fixed-side driven pulley. This pulley device (130) has an interposed member (161) interposed between a fixed-side driven pulley (140) and a movable-side driven pulley (150). The interposed member (161) is inserted into a through-hole (143) in the fixed-side driven pulley (140), positioned between a fixed-side cam part (144) of the fixed-side driven pulley (140) and a movable-side cam part (153) of the movable-side driven pulley (150) with respect to a rotation direction (L), and configured to be capable of sliding in relation to the movable-side cam part (153). The movable-side cam part (153) is configured to be capable of pressing against the fixed-side cam part (144) via the interposed member (161).

Description

プーリ装置pulley device
　本発明は、エンジン等の駆動源の駆動力を伝達するプーリ装置に関する。 The present invention relates to a pulley device that transmits the driving force of a driving source such as an engine.
　従来から、エンジン等の駆動源の駆動力を伝達するプーリ装置が知られている。例えば、特許文献１には、ベルトを介してエンジンの駆動力を受けて回転駆動する固定側ドリブンプレート（以下固定側ドリブンプーリとする）と可動側ドリブンプレート（以下可動側ドリブンプーリとする）とを有するプーリ装置を備えた遠心クラッチが開示されている。この場合、可動側ドリブンプーリが受けた駆動力（回転駆動力）は、可動側ドリブンプーリと固定側ドリブンプーリとにそれぞれ嵌合する円筒状のカム形成筒体を介して固定側ドリブンプーリに伝達される。 Conventionally, pulley devices that transmit the driving force of a driving source such as an engine have been known. For example, Patent Document 1 describes a fixed side driven plate (hereinafter referred to as a fixed side driven pulley) and a movable side driven plate (hereinafter referred to as a movable side driven pulley) that are rotationally driven by receiving the driving force of the engine via a belt. A centrifugal clutch is disclosed that includes a pulley device having a. In this case, the driving force (rotational driving force) received by the movable driven pulley is transmitted to the fixed driven pulley via the cylindrical cam-formed cylinder that fits into the movable driven pulley and the fixed driven pulley, respectively. be done.
特開２０２１－６７２７８号公報JP2021-67278A
　ところで、特許文献１に記載されたプーリ装置において、可動側ドリブンプーリが受けた駆動力をカム形成筒体を介して固定側ドリブンプーリに伝達する際に、カム形成筒体には比較的大きなねじり応力が発生する。ここで、カム形成筒体は薄肉の円筒体であるため、カム形成筒体のねじりに対する剛性の確保が困難という問題があった。 By the way, in the pulley device described in Patent Document 1, when the driving force received by the movable driven pulley is transmitted to the stationary driven pulley via the cam-forming cylinder, a relatively large twist is applied to the cam-forming cylinder. Stress occurs. Here, since the cam-forming cylindrical body is a thin-walled cylindrical body, there is a problem in that it is difficult to ensure rigidity against torsion of the cam-forming cylindrical body.
　本発明はかかる点に鑑みてなされたものであり、その目的は、可動側ドリブンプーリが受けた駆動力を固定側ドリブンプーリに伝達する際のねじりに対する剛性を確保する負担が低減されたプーリ装置を提供することである。 The present invention has been made in view of the above, and its object is to provide a pulley device in which the burden of ensuring rigidity against torsion when transmitting the driving force received by the movable driven pulley to the fixed driven pulley is reduced. The goal is to provide the following.
　本発明に係るプーリ装置は、ベルトを介して伝達された駆動源からの駆動力によって回転駆動する固定側ドリブンプーリおよび可動側ドリブンプーリを有するプーリ装置であって、前記固定側ドリブンプーリは、円筒状に形成された固定側スリーブと、前記固定側スリーブよりも径方向の外側に位置する固定側プーリと、前記固定側ドリブンプーリが回転する方向を回転方向としたとき、前記回転方向に並ぶ複数の固定側カム部と、を有し、前記可動側ドリブンプーリは、円筒状に形成され、かつ、前記固定側スリーブに外嵌する可動側スリーブと、前記可動側スリーブよりも前記径方向の外側に位置し、かつ、前記固定側プーリと共に前記ベルトを挟み、かつ、前記固定側プーリに対して接近および離隔可能に構成された可動側プーリと、前記回転方向に並ぶ複数の可動側カム部と、を有し、前記固定側ドリブンプーリにおいて前記回転方向に関して隣り合う前記固定側カム部の間、もしくは、前記可動側ドリブンプーリにおいて前記回転方向に関して隣り合う前記可動側カム部の間には、前記回転方向に並ぶ複数の貫通孔が形成され、前記固定側ドリブンプーリに前記貫通孔が形成されている場合には、前記可動側カム部が前記貫通孔に挿入され、前記可動側ドリブンプーリに前記貫通孔が形成されている場合には、前記固定側カム部が前記貫通孔に挿入され、前記固定側ドリブンプーリと前記可動側ドリブンプーリとの間に介在する介在部材をさらに有し、前記介在部材は、前記回転方向に関して前記固定側カム部と前記可動側カム部との間に位置し、かつ、前記可動側カム部に対して摺動可能に構成され、前記可動側カム部は、前記介在部材を介して前記固定側カム部を押圧可能に構成されている。 A pulley device according to the present invention includes a fixed driven pulley and a movable driven pulley that are rotationally driven by a driving force from a drive source transmitted via a belt, and the fixed driven pulley has a cylindrical shape. a fixed sleeve formed in the shape of a fixed sleeve, a fixed pulley positioned radially outside of the fixed sleeve, and a plurality of fixed side driven pulleys arranged in the rotational direction when the direction in which the fixed driven pulley rotates is the rotational direction. a fixed-side cam portion, the movable-side driven pulley is formed in a cylindrical shape, and has a movable-side sleeve that fits onto the fixed-side sleeve; and a radially outer side of the movable-side sleeve. a movable pulley located at and sandwiching the belt together with the fixed pulley and configured to be able to approach and separate from the fixed pulley; and a plurality of movable cam portions lined up in the rotation direction. , and between the fixed side cam parts adjacent in the rotation direction in the fixed side driven pulley, or between the movable side cam parts adjacent in the rotation direction in the movable side driven pulley, the When a plurality of through holes arranged in the rotational direction are formed and the fixed side driven pulley is formed with the through hole, the movable side cam portion is inserted into the through hole, and the movable side driven pulley is formed with the through hole. When a through hole is formed, the fixed side cam part is inserted into the through hole, and further includes an intervening member interposed between the fixed driven pulley and the movable driven pulley, and the intervening member is inserted into the through hole. The member is located between the fixed cam part and the movable cam part with respect to the rotational direction, and is configured to be slidable with respect to the movable cam part, and the movable cam part is located between the fixed cam part and the movable cam part. The stationary cam portion is configured to be pressable via an intervening member.
　本発明に係るプーリ装置によると、可動側カム部は、可動側カム部に対して摺動可能に構成された介在部材を介して固定側カム部を押圧可能に構成されている。このため、可動側ドリブンプーリが受けた回転駆動力は、介在部材を介して固定側ドリブンプーリに間接的に伝達される。このとき、介在部材にはねじり応力が発生しないため、ねじりに対する剛性を確保する負担が低減される。 According to the pulley device according to the present invention, the movable cam portion is configured to be able to press the fixed cam portion via the intervening member configured to be slidable with respect to the movable cam portion. Therefore, the rotational driving force received by the movable driven pulley is indirectly transmitted to the stationary driven pulley via the intervening member. At this time, since no torsional stress is generated in the intervening member, the burden of ensuring rigidity against torsion is reduced.
　本発明によれば、可動側ドリブンプーリが受けた駆動力を固定側ドリブンプーリに伝達する際のねじりに対する剛性を確保する負担が低減されたプーリ装置を提供することができる。 According to the present invention, it is possible to provide a pulley device in which the burden of ensuring rigidity against torsion when transmitting the driving force received by the movable driven pulley to the fixed driven pulley is reduced.
図１は、第１実施形態に係るプーリ装置および遠心クラッチを備えた動力伝達機構を示す断面図である。FIG. 1 is a sectional view showing a power transmission mechanism including a pulley device and a centrifugal clutch according to a first embodiment. 図２は、第１実施形態に係るプーリ装置および遠心クラッチを備えた動力伝達機構を示す部分拡大断面図である。FIG. 2 is a partially enlarged sectional view showing a power transmission mechanism including a pulley device and a centrifugal clutch according to the first embodiment. 図３は、第１実施形態に係るドリブンプーリの分解斜視図である。FIG. 3 is an exploded perspective view of the driven pulley according to the first embodiment. 図４は、第１実施形態に係るドリブンプーリの分解斜視図である。FIG. 4 is an exploded perspective view of the driven pulley according to the first embodiment. 図５は、第１実施形態に係る固定側ドリブンプーリの壁部およびその周辺の構成を示す斜視図である。FIG. 5 is a perspective view showing the configuration of a wall portion of the stationary driven pulley and its surroundings according to the first embodiment. 図６は、第１実施形態に係る固定側ドリブンプーリの壁部に介在部材が接触した状態を示す斜視図である。FIG. 6 is a perspective view showing a state in which an intervening member is in contact with a wall portion of the stationary driven pulley according to the first embodiment. 図７は、第１実施形態に係る固定側ドリブンプーリの壁部に介在部材が接触した状態を示す平面図である。FIG. 7 is a plan view showing a state in which the intervening member is in contact with the wall portion of the stationary driven pulley according to the first embodiment. 図８Ａは、第１実施形態に係る介在部材を備えた中間スリーブの斜視図である。FIG. 8A is a perspective view of an intermediate sleeve including an intervening member according to the first embodiment. 図８Ｂは、第１実施形態に係る介在部材を備えた中間スリーブの斜視図である。FIG. 8B is a perspective view of an intermediate sleeve with an intervening member according to the first embodiment. 図９Ａは、可動側ドリブンプーリが固定側ドリブンプーリに対して接近した状態における固定側カム部と可動側カム部と介在部材との位置関係を示す断面図である。FIG. 9A is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley approaches the fixed driven pulley. 図９Ｂは、可動側ドリブンプーリが固定側ドリブンプーリに対して離隔した状態における固定側カム部と可動側カム部と介在部材との位置関係を示す断面図である。FIG. 9B is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley is spaced apart from the fixed driven pulley. 図１０は、固定側カム部が可動側カム部を押圧する状態を示す断面図である。FIG. 10 is a cross-sectional view showing a state in which the fixed cam section presses the movable cam section. 図１１は、第２実施形態に係るプーリ装置および遠心クラッチを備えた動力伝達機構を示す部分拡大断面図である。FIG. 11 is a partially enlarged sectional view showing a power transmission mechanism including a pulley device and a centrifugal clutch according to the second embodiment. 図１２は、第２実施形態に係るドリブンプーリの分解斜視図である。FIG. 12 is an exploded perspective view of the driven pulley according to the second embodiment. 図１３は、第２実施形態に係るドリブンプーリの分解斜視図である。FIG. 13 is an exploded perspective view of the driven pulley according to the second embodiment. 図１４は、第２実施形態に係る固定側ドリブンプーリの斜視図である。FIG. 14 is a perspective view of the stationary driven pulley according to the second embodiment. 図１５は、第２実施形態に係る壁部に介在部材が接触した状態を示す斜視図である。FIG. 15 is a perspective view showing a state in which an intervening member is in contact with a wall according to the second embodiment. 図１６は、第２実施形態に係る壁部に介在部材が接触した状態を示す平面図である。FIG. 16 is a plan view showing a state in which an intervening member is in contact with a wall according to the second embodiment. 図１７は、第２実施形態に係る固定側ドリブンプーリの側面図である。FIG. 17 is a side view of the stationary driven pulley according to the second embodiment. 図１８は、第２実施形態に係る介在部材が固定側ドリブンプーリに取り付けられた状態を示す背面図である。FIG. 18 is a rear view showing a state in which the intervening member according to the second embodiment is attached to the stationary driven pulley. 図１９Ａは、第２実施形態に係る介在部材の斜視図である。FIG. 19A is a perspective view of an intervening member according to the second embodiment. 図１９Ｂは、第２実施形態に係る介在部材の斜視図である。FIG. 19B is a perspective view of an intervening member according to the second embodiment. 図２０は、第２実施形態に係る介在部材の抜け止め防止用のワッシャーとサークリップが固定側ドリブンプーリに取り付けられた状態を示す背面図である。FIG. 20 is a rear view showing a state in which the washer and circlip for preventing the intervening member from falling off according to the second embodiment are attached to the stationary driven pulley. 図２１Ａは、可動側ドリブンプーリが固定側ドリブンプーリに対して接近した状態における固定側カム部と可動側カム部と介在部材との位置関係を示す断面図である。FIG. 21A is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley approaches the fixed driven pulley. 図２２Ｂは、可動側ドリブンプーリが固定側ドリブンプーリに対して離隔した状態における固定側カム部と可動側カム部と介在部材との位置関係を示す断面図である。FIG. 22B is a cross-sectional view showing the positional relationship between the fixed cam part, the movable cam part, and the intervening member in a state where the movable driven pulley is spaced apart from the fixed driven pulley. 図２２は、固定側カム部が可動側カム部を押圧する状態を示す断面図である。FIG. 22 is a sectional view showing a state in which the fixed side cam part presses the movable side cam part.
　以下、図面を参照しながら、本発明に係るプーリ装置およびプーリ装置を備えた動力伝達機構の実施形態について説明する。なお、ここで説明される実施形態は、当然ながら特に本発明を限定することを意図したものではない。また、同じ作用を奏する部材・部位には同じ符号を付し、重複する説明は適宜省略または簡略化する。 Hereinafter, embodiments of a pulley device and a power transmission mechanism equipped with the pulley device according to the present invention will be described with reference to the drawings. Note that the embodiments described here are, of course, not intended to particularly limit the present invention. In addition, the same reference numerals are given to members and parts that have the same function, and redundant explanations are omitted or simplified as appropriate.
＜第１実施形態＞
　図１は、本実施形態に係るプーリ装置１３０および遠心クラッチ２００を備えた動力伝達機構１００を示す断面図である。図２は、プーリ装置１３０および遠心クラッチ２００を備えた動力伝達機構１００を示す部分拡大断面図である。なお、図１および図２では、中心線ＣＬに対して上側に位置する可動側ドリブンプーリ１５０は固定側ドリブンプーリ１４０に対して最も接近した状態を示し、中心線ＣＬに対して下側に位置する可動側ドリブンプーリ１５０は固定側ドリブンプーリ１４０に対して最も離隔した状態を示している。以下の説明では、可動側プーリ１５１が固定側プーリ１４１に対して離隔する方向を第１の方向Ｄ１、可動側プーリ１５１が固定側プーリ１４１に対して接近する方向を第２の方向Ｄ２とする。また、固定側ドリブンプーリ１４０および可動側ドリブンプーリ１５０が回転する方向を回転方向Ｌ（図３参照）とする。 <First embodiment>
FIG. 1 is a sectional view showing a power transmission mechanism 100 including a pulley device 130 and a centrifugal clutch 200 according to the present embodiment. FIG. 2 is a partially enlarged sectional view showing the power transmission mechanism 100 including the pulley device 130 and the centrifugal clutch 200. In FIGS. 1 and 2, the movable driven pulley 150 located above the center line CL is closest to the fixed driven pulley 140, and the movable driven pulley 150 located above the center line CL is closest to the fixed driven pulley 140. The movable driven pulley 150 is shown in a state farthest away from the fixed driven pulley 140. In the following description, the direction in which the movable pulley 151 moves away from the fixed pulley 141 is referred to as a first direction D1, and the direction in which the movable pulley 151 approaches the fixed pulley 141 is referred to as a second direction D2. . Further, the direction in which the fixed driven pulley 140 and the movable driven pulley 150 rotate is defined as a rotation direction L (see FIG. 3).
　動力伝達機構１００は、主としてスクータなどの自動二輪車において、駆動源としてのエンジンと駆動輪である後輪との間に設けられている。動力伝達機構１００は、エンジンの回転数に対する変速比を自動的に変更しながら、回転駆動力を後輪に伝達または遮断する装置である。図１に示すように、動力伝達機構１００は、変速機１０１および遠心クラッチ２００を備えている。 The power transmission mechanism 100 is mainly provided in a motorcycle such as a scooter between an engine as a drive source and a rear wheel as a drive wheel. The power transmission mechanism 100 is a device that transmits or cuts off rotational driving force to the rear wheels while automatically changing the gear ratio with respect to the rotational speed of the engine. As shown in FIG. 1, the power transmission mechanism 100 includes a transmission 101 and a centrifugal clutch 200.
　変速機１０１は、図示しないエンジンからの回転駆動力を無段階で変速して遠心クラッチ２００に伝達する装置である。図１に示すように、変速機１０１は、ドライブプーリ１１０、Ｖベルト１２０およびプーリ装置１３０を備えている。変速機１０１は、後述する固定ドライブプーリ１１２と可動ドライブプーリ１１３との間隔で規定されるＶベルト１２０を挟む直径と、固定側ドリブンプーリ１４０と可動側ドリブンプーリ１５０との間隔で規定されるＶベルト１２０を挟む直径との大小関係によってドライブシャフト１４６の回転数を無段階で変速する。 The transmission 101 is a device that continuously changes the speed of rotational driving force from an engine (not shown) and transmits it to the centrifugal clutch 200. As shown in FIG. 1, the transmission 101 includes a drive pulley 110, a V-belt 120, and a pulley device 130. The transmission 101 has a diameter across the V-belt 120 defined by the spacing between a fixed drive pulley 112 and a movable drive pulley 113, which will be described later, and a V diameter defined by the spacing between a fixed driven pulley 140 and a movable driven pulley 150. The rotational speed of the drive shaft 146 is varied steplessly depending on the size relationship with the diameter of the belt 120.
　図１に示すように、ドライブプーリ１１０は、エンジンから延びるクランク軸１１１上に設けられている。ドライブプーリ１１０は、エンジンの回転駆動力によって直接回転駆動する装置である。ドライブプーリ１１０は、固定ドライブプーリ１１２および可動ドライブプーリ１１３を備えている。 As shown in FIG. 1, the drive pulley 110 is provided on a crankshaft 111 extending from the engine. The drive pulley 110 is a device that is directly rotationally driven by the rotational driving force of the engine. Drive pulley 110 includes a fixed drive pulley 112 and a movable drive pulley 113.
　図１に示すように、固定ドライブプーリ１１２は、可動ドライブプーリ１１３とともにＶベルト１２０を挟む。固定ドライブプーリ１１２は、凸側の面が可動ドライブプーリ１１３側（即ちエンジン側）に向いた状態でクランク軸１１１に固定されている。すなわち、固定ドライブプーリ１１２は、常にクランク軸１１１と一体的に回転駆動する。 As shown in FIG. 1, the fixed drive pulley 112 and the movable drive pulley 113 sandwich the V-belt 120. The fixed drive pulley 112 is fixed to the crankshaft 111 with its convex surface facing toward the movable drive pulley 113 (that is, toward the engine). That is, the fixed drive pulley 112 is always driven to rotate integrally with the crankshaft 111.
　図１に示すように、可動ドライブプーリ１１３は、凸側の面が固定ドライブプーリ１１２に対向する向きでクランク軸１１１に取り付けられている。可動ドライブプーリ１１３は、クランク軸１１１に固定されたスリーブ軸受１１４上に含浸ブッシュを介して取り付けられている。可動ドライブプーリ１１３は、スリーブ軸受１１４に対して軸方向および回転方向Ｌに摺動自在に構成されている。 As shown in FIG. 1, the movable drive pulley 113 is attached to the crankshaft 111 with its convex surface facing the fixed drive pulley 112. The movable drive pulley 113 is mounted on a sleeve bearing 114 fixed to the crankshaft 111 via an impregnated bush. The movable drive pulley 113 is configured to be slidable in the axial direction and rotational direction L with respect to the sleeve bearing 114.
　図１に示すように、可動ドライブプーリ１１３の凹側の面には、複数のローラウエイト１１５がランププレート１１６によって押圧された状態で設けられている。ローラウエイト１１５は、可動ドライブプーリ１１３の回転数の増加に応じて径方向の外側に変位する部材である。ローラウエイト１１５は、ランププレート１１６と協働して可動ドライブプーリ１１３を固定ドライブプーリ１１２側に押圧する部材である。ランププレート１１６は、ローラウエイト１１５を可動ドライブプーリ１１３側に押圧する部材である。 As shown in FIG. 1, a plurality of roller weights 115 are provided on the concave side surface of the movable drive pulley 113 while being pressed by a ramp plate 116. The roller weight 115 is a member that is displaced radially outward in response to an increase in the number of rotations of the movable drive pulley 113. The roller weight 115 is a member that cooperates with the ramp plate 116 to press the movable drive pulley 113 toward the fixed drive pulley 112. The ramp plate 116 is a member that presses the roller weight 115 toward the movable drive pulley 113.
　Ｖベルト１２０は、ドライブプーリ１１０の回転駆動力をプーリ装置１３０のドリブンプーリ１３１に伝達するための部材である。Ｖベルト１２０は、無端のリング状に形成されている。Ｖベルト１２０は、固定ドライブプーリ１１２と可動ドライブプーリ１１３との間、および、ドリブンプーリ１３１の固定側ドリブンプーリ１４０と可動側ドリブンプーリ１５０との間に配置され、ドライブプーリ１１０とドリブンプーリ１３１との間に巻き掛けられている。Ｖベルトは、ベルトの一例である。 The V-belt 120 is a member for transmitting the rotational driving force of the drive pulley 110 to the driven pulley 131 of the pulley device 130. The V-belt 120 is formed into an endless ring shape. The V-belt 120 is disposed between the fixed drive pulley 112 and the movable drive pulley 113 and between the fixed driven pulley 140 and the movable driven pulley 150 of the driven pulley 131, and is arranged between the fixed drive pulley 112 and the movable driven pulley 131. wrapped between. A V-belt is an example of a belt.
　図２に示すように、プーリ装置１３０は、ドライブプーリ１１０およびＶベルト１２０を介して伝達されるエンジンからの回転駆動力によって回転駆動する装置である。プーリ装置１３０は、ドリブンプーリ１３１を備えている。ドリブンプーリ１３１は、固定側ドリブンプーリ１４０と、可動側ドリブンプーリ１５０と、固定側ドリブンプーリ１４０と可動側ドリブンプーリ１５０との間に介在する介在部材１６１と、を備えている。本実施形態では、ドリブンプーリ１３１は、介在部材１６１を備えた中間スリーブ１６０を備えている。固定側ドリブンプーリ１４０および可動側ドリブンプーリ１５０は、Ｖベルト１２０を介して伝達されたエンジンからの駆動力によって回転駆動する。 As shown in FIG. 2, the pulley device 130 is a device that is rotationally driven by the rotational driving force from the engine transmitted via the drive pulley 110 and the V-belt 120. The pulley device 130 includes a driven pulley 131. The driven pulley 131 includes a fixed driven pulley 140, a movable driven pulley 150, and an intervening member 161 interposed between the fixed driven pulley 140 and the movable driven pulley 150. In this embodiment, the driven pulley 131 includes an intermediate sleeve 160 with an intervening member 161. The fixed driven pulley 140 and the movable driven pulley 150 are rotationally driven by the driving force from the engine transmitted via the V-belt 120.
　図２に示すように、固定側ドリブンプーリ１４０は、可動側ドリブンプーリ１５０とともにＶベルト１２０を挟む。固定側ドリブンプーリ１４０は、アルミニウム材などの金属材料から形成されている。図３に示すように、固定側ドリブンプーリ１４０は、固定側プーリ１４１と、固定側スリーブ１４２と、貫通孔１４３と、固定側カム部１４４と、を備えている。本実施形態では、固定側プーリ１４１と、固定側スリーブ１４２と、固定側カム部１４４とは互いに同じ材料から一体的に成形されているが、互いに別部品で成形されて溶接などを介して互いに連結されていてもよい。 As shown in FIG. 2, the fixed driven pulley 140 and the movable driven pulley 150 sandwich the V-belt 120. The stationary driven pulley 140 is made of a metal material such as aluminum material. As shown in FIG. 3, the fixed driven pulley 140 includes a fixed pulley 141, a fixed sleeve 142, a through hole 143, and a fixed cam portion 144. In this embodiment, the stationary pulley 141, the stationary sleeve 142, and the stationary cam part 144 are integrally molded from the same material, but they are molded as separate parts and welded together. May be connected.
　図２に示すように、固定側プーリ１４１は、可動側プーリ１５１とともにＶベルト１２０を挟む。固定側プーリ１４１は、円環状に形成されている。固定側プーリ１４１は、固定側スリーブ１４２よりも径方向の外側に位置する。 As shown in FIG. 2, the fixed pulley 141 and the movable pulley 151 sandwich the V-belt 120. The fixed pulley 141 is formed in an annular shape. The fixed pulley 141 is located on the outer side of the fixed sleeve 142 in the radial direction.
　固定側スリーブ１４２は、固定側プーリ１４１と一体的に回転駆動する部材である。固定側スリーブ１４２は、円筒状に形成されている。固定側スリーブ１４２の一方の端部（図１および図２の右側の端部）は、固定側カム部１４４を介して固定側プーリ１４１と接続している。固定側スリーブ１４２の他方の端部（図１および図２の左側の端部）は、連結具１４８を介して遠心クラッチ２００のドライブプレート２１０に連結されている。なお、連結具１４８は、外周部に複数の貫通孔が形成されており、固定側ドリブンプーリ１４０のダイカスト成形時に固定側スリーブ１４２内に鋳込まれる。図３に示すように、固定側スリーブ１４２の一方の端部には、径方向の内側に向けて凹みかつ介在部材１６１から離隔した逃げ溝１４３Ａが形成されている。逃げ溝１４３Ａは、介在部材１６１が接触しない深さおよび幅で形成されている。 The fixed sleeve 142 is a member that rotates integrally with the fixed pulley 141. The fixed sleeve 142 is formed into a cylindrical shape. One end of the stationary sleeve 142 (the right end in FIGS. 1 and 2) is connected to the stationary pulley 141 via a stationary cam portion 144. The other end of the stationary sleeve 142 (the left end in FIGS. 1 and 2) is connected to the drive plate 210 of the centrifugal clutch 200 via a connector 148. The connector 148 has a plurality of through holes formed in its outer peripheral portion, and is cast into the stationary sleeve 142 when the stationary driven pulley 140 is die-cast. As shown in FIG. 3, an escape groove 143A is formed in one end of the stationary sleeve 142 and is concave toward the inside in the radial direction and is spaced apart from the intervening member 161. The escape groove 143A is formed with a depth and a width such that the intervening member 161 does not come into contact with it.
　図３に示すように、固定側カム部１４４は、径方向に関して固定側スリーブ１４２と固定側プーリ１４１との間に位置する。ここでは、３つの固定側カム部１４４が回転方向Ｌに等間隔で並ぶ。固定側カム部１４４は、介在部材１６１を介して可動側カム部１５３（図４参照）が摺動する部分である。固定側カム部１４４は、介在部材１６１または可動側カム部１５３が接触する固定側接触面１４４Ｍを有している。固定側接触面１４４Ｍは、固定側カム部１４４の回転方向Ｌの一方の端部に形成された固定側当接面１４４ＭＡと、固定側カム部１４４の回転方向Ｌの他方の端部に形成された固定側摺動面１４４ＭＢと、を含む。固定側当接面１４４ＭＡは、介在部材１６１よりも回転方向Ｌの下流側に位置する。固定側摺動面１４４ＭＢは、介在部材１６１よりも回転方向Ｌの上流側に位置する。固定側摺動面１４４ＭＢは、可動側カム部１５３が摺動可能な面である。固定側当接面１４４ＭＡおよび固定側摺動面１４４ＭＢは、回転方向Ｌに捩じれながら軸方向に延びるらせん状の曲面である。固定側当接面１４４ＭＡは、エンジンからの回転駆動力を介在部材１６１を介して可動側カム部１５３から受けるカム面である。固定側摺動面１４４ＭＢは、駆動輪側からのバックトルクを可動側カム部１５３に与えるカム面である。固定側カム部１４４の一部は、貫通孔１４３よりも可動側プーリ１５１側（第１の方向Ｄ１側）に位置する。 As shown in FIG. 3, the fixed cam portion 144 is located between the fixed sleeve 142 and the fixed pulley 141 in the radial direction. Here, three fixed side cam parts 144 are lined up at equal intervals in the rotation direction L. The fixed cam portion 144 is a portion on which the movable cam portion 153 (see FIG. 4) slides via the intervening member 161. The fixed cam portion 144 has a fixed contact surface 144M with which the intervening member 161 or the movable cam portion 153 comes into contact. The fixed side contact surface 144M is formed at the fixed side contact surface 144MA formed at one end of the fixed side cam part 144 in the rotation direction L, and at the other end of the fixed side cam part 144 in the rotation direction L. and a fixed side sliding surface 144MB. The fixed side contact surface 144MA is located on the downstream side of the intervening member 161 in the rotation direction L. Fixed side sliding surface 144MB is located upstream of intervening member 161 in rotation direction L. The fixed-side sliding surface 144MB is a surface on which the movable-side cam portion 153 can slide. The fixed side contact surface 144MA and the fixed side sliding surface 144MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotation direction L. The fixed side contact surface 144MA is a cam surface that receives rotational driving force from the engine from the movable cam portion 153 via the intervening member 161. The fixed side sliding surface 144MB is a cam surface that applies back torque from the driving wheel side to the movable side cam portion 153. A portion of the fixed cam portion 144 is located closer to the movable pulley 151 (on the first direction D1 side) than the through hole 143 is.
　図３および図４に示すように、貫通孔１４３は、固定側ドリブンプーリ１４０において回転方向Ｌに関して隣り合う固定側カム部１４４の間に形成されている。ここでは、３つの貫通孔１４３が回転方向Ｌに等間隔に並ぶ。貫通孔１４３は、長孔状に形成されている。貫通孔１４３には、介在部材１６１および後述する可動側カム部１５３が挿入される。 As shown in FIGS. 3 and 4, the through-hole 143 is formed between the fixed-side cam parts 144 adjacent to each other in the rotation direction L in the fixed-side driven pulley 140. Here, three through holes 143 are arranged at equal intervals in the rotation direction L. The through hole 143 is formed in a long hole shape. An intervening member 161 and a movable cam portion 153, which will be described later, are inserted into the through hole 143.
　図５に示すように、固定側ドリブンプーリ１４０は、貫通孔１４３の一部を区画する壁部１４５を備えている。壁部１４５は、固定側カム部１４４の一部である。壁部１４５は、抑制部材の一例である。図６および図７に示すように、壁部１４５は、介在部材１６１よりも径方向の外側に位置する。壁部１４５は、固定側当接面１４４ＭＡに連続する。壁部１４５は、固定側当接面１４４ＭＡよりも径方向の外側に位置する。壁部１４５は、固定側当接面１４４ＭＡに沿って形成されている。壁部１４５は、介在部材１６１に接触（ここでは面接触）している。なお、壁部１４５と介在部材１６１との間にはわずかな隙間が空いていてもよい。壁部１４５は、介在部材１６１の径方向の外側への変形を抑制する。即ち、固定側ドリブンプーリ１４０が回転方向Ｌに回転するとき、介在部材１６１に作用する遠心力によって介在部材１６１は径方向の外側に広がろうとするが、介在部材１６１の径方向の外側には壁部１４５が配置されているため、介在部材１６１の径方向の外側への変形は抑制される。 As shown in FIG. 5, the stationary driven pulley 140 includes a wall portion 145 that partitions a portion of the through hole 143. The wall portion 145 is a part of the fixed cam portion 144. The wall portion 145 is an example of a suppressing member. As shown in FIGS. 6 and 7, the wall portion 145 is located on the outer side of the intervening member 161 in the radial direction. The wall portion 145 is continuous with the fixed side contact surface 144MA. The wall portion 145 is located on the outer side in the radial direction than the fixed side contact surface 144MA. The wall portion 145 is formed along the fixed side contact surface 144MA. The wall portion 145 is in contact with the intervening member 161 (here, surface contact). Note that there may be a slight gap between the wall portion 145 and the intervening member 161. The wall portion 145 suppresses radially outward deformation of the intervening member 161. That is, when the stationary driven pulley 140 rotates in the rotation direction L, the centrifugal force acting on the intervening member 161 causes the intervening member 161 to spread outward in the radial direction; Since the wall portion 145 is disposed, radially outward deformation of the intervening member 161 is suppressed.
　図２に示すように、固定側ドリブンプーリ１４０の固定側スリーブ１４２内には、ドライブシャフト１４６が配置されている。ドライブシャフト１４６は、動力伝達機構１００が搭載される自動二輪車両の後輪をトランスミッションを介して駆動するための軸である。自動二輪車両の後輪は、ドライブシャフト１４６の一方（図２の右側）の端部（図示せず）に間接的に取り付けられている。 As shown in FIG. 2, a drive shaft 146 is arranged within the fixed sleeve 142 of the fixed driven pulley 140. The drive shaft 146 is an axis for driving the rear wheel of the motorcycle on which the power transmission mechanism 100 is mounted via a transmission. The rear wheel of the motorcycle is indirectly attached to one end (not shown) of the drive shaft 146 (on the right side in FIG. 2).
　ドライブシャフト１４６は、軸受け１４７ａ、１４７ｂを介して固定側ドリブンプーリ１４０を支持している。ドライブシャフト１４６の図２の左側の端部には、クラッチアウタ２３０が取り付けられている。なお、図１および図２においては、ドライブシャフト１４６を二点鎖線で示している。 The drive shaft 146 supports the stationary driven pulley 140 via bearings 147a and 147b. A clutch outer 230 is attached to the left end of the drive shaft 146 in FIG. In addition, in FIG. 1 and FIG. 2, the drive shaft 146 is shown by a two-dot chain line.
　図２に示すように、可動側ドリブンプーリ１５０は、固定側ドリブンプーリ１４０とともにＶベルト１２０を挟む。可動側ドリブンプーリ１５０は、アルミニウム材などの金属材料から形成されている。図４に示すように、可動側ドリブンプーリ１５０は、可動側プーリ１５１と、可動側スリーブ１５２（図３参照）と、可動側カム部１５３と、を備えている。本実施形態では、可動側プーリ１５１と、可動側スリーブ１５２と、可動側カム部１５３とは互いに同じ材料から一体的に成形されているが、互いに別部品で成形されて溶接などを介して互いに連結されていてもよい。 As shown in FIG. 2, the movable driven pulley 150 and the fixed driven pulley 140 sandwich the V-belt 120. The movable driven pulley 150 is made of a metal material such as aluminum. As shown in FIG. 4, the movable driven pulley 150 includes a movable pulley 151, a movable sleeve 152 (see FIG. 3), and a movable cam portion 153. In this embodiment, the movable pulley 151, the movable sleeve 152, and the movable cam part 153 are integrally molded from the same material, but they are molded as separate parts and are welded together. May be connected.
　図２に示すように、可動側プーリ１５１は、固定側プーリ１４１とともにＶベルト１２０を挟む。可動側プーリ１５１は、円環状に形成されている。可動側プーリ１５１は、可動側スリーブ１５２よりも径方向の外側に位置する。可動側プーリ１５１は、固定側プーリ１４１に対して接近および離隔可能に構成されている。 As shown in FIG. 2, the movable pulley 151 and the fixed pulley 141 sandwich the V-belt 120. The movable pulley 151 is formed in an annular shape. The movable pulley 151 is located on the outer side of the movable sleeve 152 in the radial direction. The movable pulley 151 is configured to be able to approach and separate from the fixed pulley 141.
　可動側スリーブ１５２は、可動側プーリ１５１と一体的に回転駆動する部材である。可動側スリーブ１５２は、円筒状に形成されている。可動側スリーブ１５２は、固定側スリーブ１４２に外嵌する。より詳細には、可動側スリーブ１５２は、中間スリーブ１６０を介して固定側スリーブ１４２に外嵌する。即ち、可動側スリーブ１５２には、中間スリーブ１６０および固定側スリーブ１４２が挿入される。可動側スリーブ１５２の一方の端部（図１および図２の右側の端部）は、可動側プーリ１５１と接続している。 The movable sleeve 152 is a member that rotates integrally with the movable pulley 151. The movable sleeve 152 is formed into a cylindrical shape. The movable sleeve 152 is fitted onto the fixed sleeve 142 . More specifically, the movable sleeve 152 is externally fitted onto the fixed sleeve 142 via the intermediate sleeve 160. That is, the intermediate sleeve 160 and the fixed sleeve 142 are inserted into the movable sleeve 152. One end of the movable sleeve 152 (the right end in FIGS. 1 and 2) is connected to the movable pulley 151.
　図４に示すように、可動側カム部１５３は、可動側プーリ１５１から固定側プーリ１４１に向けて（即ち方向Ｄ２に向けて）延びる。可動側カム部１５３は、突起である。ここでは、３つの可動側カム部１５３が回転方向Ｌに等間隔で並ぶ。可動側カム部１５３は、固定側ドリブンプーリ１４０の貫通孔１４３に挿入される。可動側カム部１５３は、介在部材１６１を介して固定側カム部１４４に摺動する部分である。可動側カム部１５３は、介在部材１６１を介して固定側カム部１４４を押圧可能に構成されている。可動側カム部１５３は、介在部材１６１または固定側カム部１４４が摺動する可動側摺動面１５３Ｍを有している。可動側摺動面１５３Ｍは、可動側カム部１５３の回転方向Ｌの一方の端部に形成された第１可動側摺動面１５３ＭＡと、可動側カム部１５３の回転方向Ｌの他方の端部に形成された第２可動側摺動面１５３ＭＢと、を有する。第１可動側摺動面１５３ＭＡは、介在部材１６１よりも回転方向Ｌの上流側に位置する。第２可動側摺動面１５３ＭＢは、第１可動側摺動面１５３ＭＡよりも回転方向Ｌの上流側に位置する。第１可動側摺動面１５３ＭＡおよび第２可動側摺動面１５３ＭＢは、回転方向Ｌに捩じれながら軸方向に延びるらせん状の曲面である。第１可動側摺動面１５３ＭＡは、エンジンからの回転駆動力を介在部材１６１を介して固定側カム部１４４に与えるカム面である。第２可動側摺動面１５３ＭＢは、駆動輪側からのバックトルクを固定側カム部１４４から受けるカム面である。可動側摺動面１５３Ｍと固定側接触面１４４Ｍとは互いに平行に形成されている。第１可動側摺動面１５３ＭＡと固定側当接面１４４ＭＡとは互いに平行に形成されている。第２可動側摺動面１５３ＭＢと固定側摺動面１４４ＭＢとは互いに平行に形成されている。 As shown in FIG. 4, the movable cam portion 153 extends from the movable pulley 151 toward the fixed pulley 141 (that is, in the direction D2). The movable cam portion 153 is a protrusion. Here, the three movable cam parts 153 are arranged at equal intervals in the rotation direction L. The movable cam portion 153 is inserted into the through hole 143 of the fixed driven pulley 140. The movable cam portion 153 is a portion that slides on the fixed cam portion 144 via the intervening member 161. The movable cam portion 153 is configured to be able to press the fixed cam portion 144 via the intervening member 161. The movable cam portion 153 has a movable sliding surface 153M on which the intervening member 161 or the fixed cam portion 144 slides. The movable sliding surface 153M includes a first movable sliding surface 153MA formed at one end of the movable cam section 153 in the rotational direction L, and the other end of the movable cam section 153 in the rotational direction L. It has a second movable side sliding surface 153MB formed in . The first movable sliding surface 153MA is located upstream of the intervening member 161 in the rotation direction L. The second movable sliding surface 153MB is located upstream of the first movable sliding surface 153MA in the rotation direction L. The first movable sliding surface 153MA and the second movable sliding surface 153MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotational direction L. The first movable sliding surface 153MA is a cam surface that applies rotational driving force from the engine to the fixed cam portion 144 via the intervening member 161. The second movable sliding surface 153MB is a cam surface that receives back torque from the driving wheel side from the fixed cam portion 144. The movable sliding surface 153M and the fixed contact surface 144M are formed parallel to each other. The first movable side sliding surface 153MA and the fixed side contact surface 144MA are formed parallel to each other. The second movable sliding surface 153MB and the fixed sliding surface 144MB are formed parallel to each other.
　図２に示すように、中間スリーブ１６０は、固定側ドリブンプーリ１４０と可動側ドリブンプーリ１５０との間に配置されている。図８Ａおよび図８Ｂに示すように、中間スリーブ１６０は、介在部材１６１と、筒部材１６３と、引掛け部材１６２と、を備えている。 As shown in FIG. 2, the intermediate sleeve 160 is arranged between the fixed driven pulley 140 and the movable driven pulley 150. As shown in FIGS. 8A and 8B, the intermediate sleeve 160 includes an intervening member 161, a cylindrical member 163, and a hook member 162.
　筒部材１６３は、可動側ドリブンプーリ１５０を軸方向に案内するための部材である。筒部材１６３は、固定側スリーブ１４２と可動側スリーブ１５２との間に配置されている。筒部材１６３は、固定側スリーブ１４２に対して摺動自在に外嵌すると共に、可動側スリーブ１５２に対して摺動自在に内嵌する。筒部材１６３は、可動側スリーブ１５２よりも軸方向の長さが長い。筒部材１６３は、固定側スリーブ１４２と軸方向の長さが略同じである。図８Ａに示すように、筒部材１６３は、介在部材１６１が第２の方向Ｄ２に移動することを規制する当接部１６３Ａを有している。当接部１６３Ａは、第２規制部材の一例である。当接部１６３Ａは、固定側カム部１４４の第１の方向Ｄ１の面１４４Ａ（図３参照）に当接可能に構成されている。 The cylindrical member 163 is a member for guiding the movable driven pulley 150 in the axial direction. The cylindrical member 163 is arranged between the fixed sleeve 142 and the movable sleeve 152. The cylindrical member 163 is slidably fitted on the outside of the stationary sleeve 142 and slidably fitted on the inside of the movable sleeve 152. The cylindrical member 163 has a longer length in the axial direction than the movable sleeve 152. The cylindrical member 163 has substantially the same length in the axial direction as the stationary sleeve 142. As shown in FIG. 8A, the cylindrical member 163 has a contact portion 163A that restricts the intervening member 161 from moving in the second direction D2. The contact portion 163A is an example of a second regulating member. The contact portion 163A is configured to be able to come into contact with a surface 144A (see FIG. 3) of the fixed side cam portion 144 in the first direction D1.
　介在部材１６１は、筒部材１６３の端部から固定側プーリ１４１に向けて延びる。ここでは、３つの介在部材１６１が回転方向Ｌに等間隔で並ぶ。介在部材１６１は、固定側ドリブンプーリ１４０の貫通孔１４３に挿入されて固定側ドリブンプーリ１４０に取り付けられている。介在部材１６１は、回転方向Ｌに関して固定側カム部１４４と可動側カム部１５３との間に位置する。介在部材１６１は、固定側カム部１４４の固定側当接面１４４ＭＡと可動側カム部１５３の第１可動側摺動面１５３ＭＡとの間に設けられており、固定側カム部１４４の固定側摺動面１４４ＭＢと可動側カム部１５３の第２可動側摺動面１５３ＭＢとの間には設けられていないが、固定側摺動面１４４ＭＢと第２可動側摺動面１５３ＭＢとの間に設けられていてもよい。介在部材１６１は、可動側カム部１５３に対して摺動可能に構成されている。図９Ａに示すように、介在部材１６１が可動側カム部１５３と固定側当接面１４４ＭＡとに挟まれた状態において、可動側カム部１５３と固定側摺動面１４４ＭＢとの間には隙間が形成されている。 The intervening member 161 extends from the end of the cylindrical member 163 toward the fixed pulley 141. Here, three intervening members 161 are arranged at equal intervals in the rotation direction L. The intervening member 161 is inserted into the through hole 143 of the stationary driven pulley 140 and attached to the stationary driven pulley 140. The intervening member 161 is located between the fixed cam part 144 and the movable cam part 153 in the rotation direction L. The intervening member 161 is provided between the fixed side contact surface 144MA of the fixed side cam part 144 and the first movable side sliding surface 153MA of the movable side cam part 153, and Although it is not provided between the moving surface 144MB and the second movable sliding surface 153MB of the movable cam portion 153, it is provided between the fixed sliding surface 144MB and the second movable sliding surface 153MB. You can leave it there. The intervening member 161 is configured to be slidable with respect to the movable cam portion 153. As shown in FIG. 9A, when the intervening member 161 is sandwiched between the movable cam portion 153 and the fixed contact surface 144MA, there is a gap between the movable cam portion 153 and the fixed sliding surface 144MB. It is formed.
　図８Ａおよび図８Ｂに示すように、介在部材１６１は、固定側接触面１４４Ｍに対向して配置される介在側接触面１６１Ｍを有している。介在側接触面１６１Ｍは、固定側カム部１４４に当接する面である。介在側接触面１６１Ｍは、可動側カム部１５３が摺動する面である。介在側接触面１６１Ｍは、可動側摺動面１５３Ｍと面接触して摺動するように構成されている。介在側接触面１６１Ｍは、介在部材１６１の回転方向Ｌの一方の端部に形成された介在側当接面１６１ＭＡと、介在部材１６１の回転方向Ｌの他方の端部に形成された介在側摺動面１６１ＭＢと、を有する。介在側当接面１６１ＭＡは、固定側当接面１４４ＭＡに対向する。介在側当接面１６１ＭＡは、固定側当接面１４４ＭＡと面接触する。介在側摺動面１６１ＭＢは、可動側カム部１５３を介して固定側摺動面１４４ＭＢに対向する。介在側摺動面１６１ＭＢは、第１可動側摺動面１５３ＭＡに対向する。介在側摺動面１６１ＭＢは、第１可動側摺動面１５３ＭＡと面接触して摺動する。介在側当接面１６１ＭＡおよび介在側摺動面１６１ＭＢは、回転方向Ｌに捩じれながら軸方向に延びるらせん状の曲面である。 As shown in FIGS. 8A and 8B, the intervening member 161 has an intervening contact surface 161M that is arranged opposite to the fixed contact surface 144M. The intervening side contact surface 161M is a surface that comes into contact with the fixed side cam portion 144. The intervening contact surface 161M is a surface on which the movable cam portion 153 slides. The intervening contact surface 161M is configured to slide in surface contact with the movable sliding surface 153M. The intervening side contact surface 161M includes an intervening side contact surface 161MA formed at one end of the intervening member 161 in the rotation direction L, and an intervening side slide formed at the other end of the intervening member 161 in the rotation direction L. It has a moving surface of 161MB. The intervening side contact surface 161MA faces the fixed side contact surface 144MA. The intervening side contact surface 161MA makes surface contact with the stationary side contact surface 144MA. The intervening sliding surface 161MB faces the fixed sliding surface 144MB via the movable cam portion 153. The intervening sliding surface 161MB faces the first movable sliding surface 153MA. The intervening sliding surface 161MB slides in surface contact with the first movable sliding surface 153MA. The intervening side contact surface 161MA and the intervening side sliding surface 161MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotational direction L.
　図８Ａおよび図８Ｂに示すように、引掛け部材１６２は介在部材１６１の先端部（第２の方向Ｄ２側の端部）に形成されている。引掛け部材１６２は、第１規制部材の一例である。図９Ａおよび図９Ｂに示すように、引掛け部材１６２は、介在部材１６１が第１の方向Ｄ１に移動することを規制する。引掛け部材１６２は、固定側ドリブンプーリ１４０の一部（例えば固定側カム部１４４）に引っ掛かる。 As shown in FIGS. 8A and 8B, the hook member 162 is formed at the tip of the intervening member 161 (the end on the second direction D2 side). The hook member 162 is an example of a first regulating member. As shown in FIGS. 9A and 9B, the hook member 162 restricts the intervening member 161 from moving in the first direction D1. The hook member 162 is hooked on a part of the stationary driven pulley 140 (for example, the stationary cam portion 144).
　介在部材１６１および筒部材１６３および引掛け部材１６２は、同じ材料から一体的に形成されている。介在部材１６１および筒部材１６３および引掛け部材１６２は、固定側カム部１４４および可動側カム部１５３を形成する材料とは異なる材料から形成されている。介在部材１６１は、例えば、固定側カム部１４４および可動側カム部１５３よりも耐摩耗性が低い材料から形成されている。介在部材１６１および筒部材１６３および引掛け部材１６２は、ポリアミド樹脂（例えばポリアミド４６）の吸水率（例えば３．０％）よりも低い吸水率（例えば０．１％～２．０％）を有する材料から形成されている。介在部材１６１および筒部材１６３および引掛け部材１６２は、例えば、樹脂材料、紙、カーボンファイバー、カーボンナノチューブ、金属等から形成されている。樹脂材料としては、例えば、耐熱性および耐摩耗性を有する熱可塑性樹脂または熱硬化性樹脂を用いることができ、エンジニアリングプラスチックまたはスーパーエンジニアリングプラスチックが好適である。具体的には、熱可塑性樹脂としては、ポリアミド樹脂、ポリエーテルエーテルケトン樹脂（ＰＥＥＫ）、ポリフェニレンサルファイド樹脂（ＰＰＳ）、ポリアミドイミド樹脂（ＰＡＩ）、フッ素樹脂（ＰＴＦＥ）またはポリイミド樹脂（ＰＩ）等が挙げられる。熱硬化性樹脂としては、ジアリルフタレート樹脂（ＰＤＡＰ）、エポキシ樹脂（ＥＰ）、ポリイミド樹脂、フェノール樹脂またはシリコン樹脂（ＳＩ）等が挙げられる。 The intervening member 161, the cylinder member 163, and the hook member 162 are integrally formed from the same material. The intervening member 161, the cylindrical member 163, and the hook member 162 are made of a different material from the material forming the fixed cam portion 144 and the movable cam portion 153. The intervening member 161 is made of, for example, a material with lower wear resistance than the fixed cam part 144 and the movable cam part 153. The intervening member 161, the cylinder member 163, and the hook member 162 have a lower water absorption rate (for example, 0.1% to 2.0%) than the water absorption rate (for example, 3.0%) of the polyamide resin (for example, polyamide 46). formed from material. The intervening member 161, the cylinder member 163, and the hook member 162 are made of, for example, resin material, paper, carbon fiber, carbon nanotubes, metal, or the like. As the resin material, for example, a thermoplastic resin or a thermosetting resin having heat resistance and wear resistance can be used, and engineering plastics or super engineering plastics are preferable. Specifically, the thermoplastic resin includes polyamide resin, polyetheretherketone resin (PEEK), polyphenylene sulfide resin (PPS), polyamideimide resin (PAI), fluororesin (PTFE), polyimide resin (PI), etc. Can be mentioned. Examples of the thermosetting resin include diallyl phthalate resin (PDAP), epoxy resin (EP), polyimide resin, phenol resin, and silicone resin (SI).
　図２に示すように、可動側スリーブ１５２の径方向の外側には、トルクスプリング１７０が設けられている。トルクスプリング１７０は、可動側プーリ１５１とドライブプレート２１０との間に設けられている。トルクスプリング１７０は、可動側ドリブンプーリ１５０を固定側ドリブンプーリ１４０側に押圧する。トルクスプリングは、例えば、コイルスプリングである。 As shown in FIG. 2, a torque spring 170 is provided on the outside of the movable sleeve 152 in the radial direction. Torque spring 170 is provided between movable pulley 151 and drive plate 210. Torque spring 170 presses movable driven pulley 150 toward fixed driven pulley 140. The torque spring is, for example, a coil spring.
　図２に示すように、遠心クラッチ２００は、変速機１０１を介して伝達されたエンジンの回転駆動力をドライブシャフト１４６に伝達または遮断する装置である。遠心クラッチ２００は、エンジンが所定の回転数に達するまでの間は回転駆動力のドライブシャフト１４６への伝達を遮断するとともに、エンジンが所定の回転数に達したときに回転駆動力をドライブシャフト１４６に伝達する装置である。遠心クラッチ２００は、固定側スリーブ１４２およびドライブシャフト１４６の先端部に設けられている。遠心クラッチ２００は、ドライブプレート２１０、３つのクラッチウエイト２２０およびクラッチアウタ２３０を備えている。 As shown in FIG. 2, the centrifugal clutch 200 is a device that transmits or interrupts the rotational driving force of the engine transmitted via the transmission 101 to the drive shaft 146. The centrifugal clutch 200 interrupts transmission of rotational driving force to the drive shaft 146 until the engine reaches a predetermined rotational speed, and transmits the rotational driving force to the drive shaft 146 when the engine reaches a predetermined rotational speed. It is a device that transmits information to The centrifugal clutch 200 is provided at the distal end of the stationary sleeve 142 and the drive shaft 146. The centrifugal clutch 200 includes a drive plate 210, three clutch weights 220, and a clutch outer 230.
　ドライブプレート２１０は、固定側スリーブ１４２と一体的に回転駆動する。ドライブプレート２１０の底部２１１の中央部には、連結具１４８が貫通した状態で嵌合する貫通孔が形成されている。底部２１１の径方向の外側にはフランジ状に張り出した鍔部２１２が形成されている。 The drive plate 210 is driven to rotate integrally with the stationary sleeve 142. A through hole is formed in the center of the bottom 211 of the drive plate 210, into which the connector 148 is inserted. A flange-shaped flange portion 212 is formed on the radially outer side of the bottom portion 211 .
　ドライブプレート２１０の底部２１１と鍔部２１２の境界部分にはトルクスプリング１７０が設けられている。鍔部２１２には、回転方向Ｌに沿ってそれぞれ３つの揺動支持ピン２１３およびウエイト押圧体支持部２１５が等間隔で設けられている。 A torque spring 170 is provided at the boundary between the bottom 211 and the flange 212 of the drive plate 210. The collar portion 212 is provided with three swing support pins 213 and three weight presser support portions 215 at equal intervals along the rotation direction L.
　揺動支持ピン２１３は、後述するクラッチウエイト２２０の一方の端部を回動可能に支持しかつ他方の端部を揺動させる。揺動支持ピン２１３は、カシメ加工部２１３ａによって鍔部２１２に固定されている。揺動支持ピン２１３は、クラッチウエイト２２０のピン摺動孔２２２内を貫通する。揺動支持ピン２１３は、揺動支持ピン２１３の先端部に取り付けられるサイドプレート２１４と共に、クラッチウエイト２２０を挟んだ状態で支持している。サイドプレート２１４は、図示しないサークリップによってクラッチウエイト２２０が揺動支持ピン２１３から抜けることを防止する。 The swing support pin 213 rotatably supports one end of a clutch weight 220, which will be described later, and swings the other end. The swing support pin 213 is fixed to the collar portion 212 by a caulking portion 213a. The swing support pin 213 passes through the pin sliding hole 222 of the clutch weight 220. The swing support pin 213 and a side plate 214 attached to the tip of the swing support pin 213 support the clutch weight 220 in a sandwiched state. The side plate 214 prevents the clutch weight 220 from coming off the swing support pin 213 by a circlip (not shown).
　ウエイト押圧体支持部２１５は、ウエイト押圧体２１６を回転自在な状態で支持する。ウエイト押圧体支持部２１５は、鍔部２１２上にピン状に突出して形成されている。ウエイト押圧体２１６は、クラッチウエイト２２０の揺動のタイミングを制御する機能を有する。ウエイト押圧体２１６は、クラッチシュー２２１がクラッチアウタ２３０に接触するときに発生する打音を軽減する機能を有する。 The weight pressing body support section 215 rotatably supports the weight pressing body 216. The weight pressing member support portion 215 is formed to protrude from the collar portion 212 in a pin shape. The weight pressing body 216 has a function of controlling the timing of swinging of the clutch weight 220. The weight pressing body 216 has a function of reducing the pounding noise generated when the clutch shoe 221 contacts the clutch outer 230.
　クラッチウエイト２２０は、ドライブプレート２１０の回転数に応じて、クラッチシュー２２１を介してクラッチアウタ２３０に接触または離隔する。これにより、エンジンからの回転駆動力をドライブシャフト１４６に伝達または遮断する。 The clutch weight 220 contacts or separates from the clutch outer 230 via the clutch shoe 221 depending on the rotation speed of the drive plate 210. This transmits or blocks the rotational driving force from the engine to the drive shaft 146.
　クラッチシュー２２１は、クラッチアウタ２３０の内周面に対する摩擦力を増大させる
ための部材である。クラッチシュー２２１は、摩擦材から形成されている。クラッチシュー２２１は、クラッチウエイト２２０の外周面に張り付けられている。 The clutch shoe 221 is a member for increasing the frictional force against the inner peripheral surface of the clutch outer 230. Clutch shoe 221 is made of a friction material. The clutch shoe 221 is attached to the outer peripheral surface of the clutch weight 220.
　隣接するクラッチウエイト２２０は、連結スプリング２２３によって連結され、ドライブプレート２１０の径方向の内側に向かって引っ張られている。すなわち、クラッチウエイト２２０は、クラッチシュー２２１が設けられた部分がクラッチアウタ２３０に対して揺動するように、揺動支持ピン２１３およびピン摺動孔２２２を介してドライブプレート２１０上に支持されている。 Adjacent clutch weights 220 are connected by a connection spring 223 and pulled toward the inside of the drive plate 210 in the radial direction. That is, the clutch weight 220 is supported on the drive plate 210 via the swing support pin 213 and the pin sliding hole 222 so that the portion where the clutch shoe 221 is provided swings relative to the clutch outer 230. There is.
　連結スプリング２２３は、クラッチウエイト２２０をクラッチアウタ２３０に対して離隔する方向に引っ張る部材である。連結スプリング２２３は、ドライブプレート２１０の回転方向Ｌに沿って互いに隣接し合うクラッチウエイト２２０間にそれぞれ設けられている。 The connection spring 223 is a member that pulls the clutch weight 220 in a direction away from the clutch outer 230. The connection springs 223 are provided between the clutch weights 220 adjacent to each other along the rotation direction L of the drive plate 210.
　各クラッチウエイト２２０のドライブプレート２１０に対向する内側面には、押圧体収容部２２４がそれぞれ形成されている。押圧体収容部２２４は、ウエイト押圧体２１６を収容する。押圧体収容部２２４には、ウエイト押圧体２１６が押し付けられる押圧体受け部２２４ａが形成されている。押圧体受け部２２４ａは、クラッチウエイト２２０の内側面に凹状に切り欠かれて形成されている。 A pressing body accommodating portion 224 is formed on the inner surface of each clutch weight 220 facing the drive plate 210. The pressing body accommodating portion 224 accommodates the weight pressing body 216. A pressing body receiving portion 224a against which the weight pressing body 216 is pressed is formed in the pressing body accommodating portion 224. The pressing body receiving portion 224a is formed by cutting out a concave shape on the inner surface of the clutch weight 220.
　押圧体受け部２２４ａは、ウエイト押圧体２１６に押し付けられることでクラッチウエイト２２０がクラッチアウタ２３０側に変位する際の抵抗力を発生させるための部分である。 The pressing body receiving portion 224a is a portion that generates a resistance force when the clutch weight 220 is displaced toward the clutch outer 230 side by being pressed against the weight pressing body 216.
　クラッチアウタ２３０は、ドライブシャフト１４６と一体的に回転駆動する。クラッチアウタ２３０は、ドライブプレート２１０およびクラッチウエイト２２０を覆うカップ状に形成されている。クラッチアウタ２３０は、クラッチウエイト２２０のクラッチシュー２２１に接触する円筒面２３１を有している。 The clutch outer 230 is rotationally driven integrally with the drive shaft 146. Clutch outer 230 is formed into a cup shape that covers drive plate 210 and clutch weight 220. Clutch outer 230 has a cylindrical surface 231 that contacts clutch shoe 221 of clutch weight 220.
　次に、プーリ装置１３０および遠心クラッチ２００の作動について説明する。遠心クラッチ２００は、エンジンが停止状態またはアイドリング状態では、図１に示すように、エンジンとドライブシャフト１４６との間の駆動力の伝達を遮断する。 Next, the operation of the pulley device 130 and the centrifugal clutch 200 will be explained. The centrifugal clutch 200 interrupts transmission of driving force between the engine and the drive shaft 146 when the engine is stopped or idling, as shown in FIG.
　ここで、Ｖベルト１２０を介して伝達されたエンジンの回転駆動力により固定側ドリブンプーリ１４０および可動側ドリブンプーリ１５０が回転駆動する。このとき、可動側カム部１５３が介在部材１６１を介して固定側カム部１４４を押圧する。これにより、ドライブプレート２１０は、固定側ドリブンプーリ１４０および可動側ドリブンプーリ１５０と同じ回転数で回転駆動する。ドライブプレート２１０に設けられたクラッチウエイト２２０は、ドライブプレート２１０と同じ回転数で回転駆動する。 Here, the fixed side driven pulley 140 and the movable side driven pulley 150 are rotationally driven by the rotational driving force of the engine transmitted via the V-belt 120. At this time, the movable cam portion 153 presses the fixed cam portion 144 via the intervening member 161. As a result, the drive plate 210 is driven to rotate at the same rotational speed as the fixed driven pulley 140 and the movable driven pulley 150. The clutch weight 220 provided on the drive plate 210 is rotated at the same rotation speed as the drive plate 210.
　ところが、エンジンがアイドリング状態では、クラッチウエイト２２０に作用する遠心力が連結スプリング２２３の弾性力（引張力）よりも小さいため、クラッチシュー２２１がクラッチアウタ２３０の円筒面２３１に接触しない。したがって、遠心クラッチ２００において、エンジンの回転駆動力がドライブシャフト１４６に伝達されることはなく、クラッチオフの状態となっている。 However, when the engine is idling, the centrifugal force acting on the clutch weight 220 is smaller than the elastic force (tensile force) of the connection spring 223, so the clutch shoe 221 does not contact the cylindrical surface 231 of the clutch outer 230. Therefore, in the centrifugal clutch 200, the rotational driving force of the engine is not transmitted to the drive shaft 146, and the clutch is in an off state.
　クラッチオフの状態において、可動側ドリブンプーリ１５０は、トルクスプリング１７０の弾性力およびカム推力によって固定側ドリブンプーリ１４０に最も接近する位置またはその近傍の位置に押圧されている。このため、図９Ａに示すように、可動側カム部１５３が貫通孔１４３内に奥深くまで進入した状態で第１可動側摺動面１５３ＭＡが固定側当接面１４４ＭＡに対して介在部材１６１を介して密着し、回転駆動力を固定側ドリブンプーリ１４０に伝達する。 In the clutch-off state, the movable driven pulley 150 is pushed by the elastic force of the torque spring 170 and the cam thrust to a position closest to the stationary driven pulley 140 or a position in the vicinity thereof. Therefore, as shown in FIG. 9A, when the movable cam portion 153 has entered deeply into the through hole 143, the first movable sliding surface 153MA is connected to the fixed contact surface 144MA via the intervening member 161. The rotational driving force is transmitted to the stationary driven pulley 140.
　この場合、介在部材１６１を介した第１可動側摺動面１５３ＭＡと固定側当接面１４４ＭＡとの接触面積は、最大または最大に近い値となる。これにより、可動側ドリブンプーリ１５０は、エンジンのアイドリングなどの回転数が不安定になりがちな低回転時においても、安定的に回転駆動力を固定側ドリブンプーリ１４０に伝達することができる。 In this case, the contact area between the first movable sliding surface 153MA and the fixed contact surface 144MA via the intervening member 161 has a maximum value or a value close to the maximum value. As a result, the movable driven pulley 150 can stably transmit rotational driving force to the stationary driven pulley 140 even at low engine speeds where the engine speed tends to be unstable, such as when the engine is idling.
　また、この場合、介在部材１６１は、可動側カム部１５３と固定側カム部１４４とに挟まれた状態で配置されている。従って、可動側カム部１５３からの押圧力は、介在部材１６１の厚さ方向に伝達されて固定側カム部１４４に伝達される。すなわち、介在部材１６１には、可動側カム部１５３からの押圧力が固定側カム部１４４に伝達される際に、大きなねじり応力が掛かることがないため、高いねじり剛性を備える必要はない。 Furthermore, in this case, the intervening member 161 is placed between the movable cam portion 153 and the fixed cam portion 144. Therefore, the pressing force from the movable cam portion 153 is transmitted in the thickness direction of the intervening member 161 and then to the fixed cam portion 144. That is, since a large torsional stress is not applied to the intervening member 161 when the pressing force from the movable cam part 153 is transmitted to the fixed cam part 144, it is not necessary to have high torsional rigidity.
　次に、運転者のアクセル操作によってエンジンの回転数が所定の値よりも大きくなると、遠心クラッチ２００はエンジンの回転駆動力をドライブシャフト１４６に伝達する。エンジンの回転数が増加するに従ってクラッチウエイト２２０に作用する遠心力が連結スプリング２２３の弾性力（引張力）よりも大きくなる。これにより、クラッチウエイト２２０が揺動支持ピン２１３を中心として径方向の外側に向かって回動変位する。すなわち、クラッチウエイト２２０が連結スプリング２２３の弾性力（引張力）に抗しながらクラッチアウタ２３０の円筒面２３１側に回動変位し、クラッチシュー２２１が円筒面２３１に接触する。そして、クラッチシュー２２１が円筒面２３１に押し付けられる。これにより、遠心クラッチ２００は、エンジンの回転駆動力を完全にドライブシャフト１４６に伝達するクラッチオンの状態となる。したがって、自動二輪車は、エンジンの回転駆動力によって後輪が回転駆動して走行する。 Next, when the engine rotational speed becomes larger than a predetermined value due to the driver's accelerator operation, the centrifugal clutch 200 transmits the rotational driving force of the engine to the drive shaft 146. As the engine speed increases, the centrifugal force acting on the clutch weight 220 becomes larger than the elastic force (tensile force) of the connection spring 223. As a result, the clutch weight 220 is rotationally displaced radially outward about the swing support pin 213. That is, the clutch weight 220 is rotationally displaced toward the cylindrical surface 231 of the clutch outer 230 while resisting the elastic force (tensile force) of the connection spring 223, and the clutch shoe 221 comes into contact with the cylindrical surface 231. The clutch shoe 221 is then pressed against the cylindrical surface 231. As a result, the centrifugal clutch 200 enters a clutch-on state in which the rotational driving force of the engine is completely transmitted to the drive shaft 146. Therefore, the motorcycle runs with the rear wheels rotationally driven by the rotational driving force of the engine.
　クラッチオンの状態において、ドリブンプーリ１３１は、エンジンの回転数が増加するに従って可動側ドリブンプーリ１５０がトルクスプリング１７０の弾性力およびカム推力に抗して固定側ドリブンプーリ１４０に対して離隔する方向（即ち方向Ｄ１）に移動する。すなわち、可動側ドリブンプーリ１５０の可動側カム部１５３は、固定側ドリブンプーリ１４０の固定側カム部１４４に対して離隔する方向に摺動する。 In the clutch-on state, the driven pulley 131 moves in a direction (in which the movable driven pulley 150 moves away from the fixed driven pulley 140 against the elastic force of the torque spring 170 and the cam thrust as the engine speed increases). That is, it moves in the direction D1). That is, the movable cam portion 153 of the movable driven pulley 150 slides in a direction away from the fixed cam portion 144 of the fixed driven pulley 140.
　これにより、図９Ｂに示すように、介在部材１６１を介した第１可動側摺動面１５３ＭＡと固定側当接面１４４ＭＡとの接触面積は、最少または最少に近い値となるが、介在部材１６１を介した固定側カム部１４４と可動側カム部１５３との接触状態は維持される。すなわち、可動側ドリブンプーリ１５０から固定側ドリブンプーリ１４０への回転駆動力の伝達は維持される。 As a result, as shown in FIG. 9B, the contact area between the first movable sliding surface 153MA and the fixed contact surface 144MA via the intervening member 161 becomes the minimum or a value close to the minimum, but the intervening member 161 The state of contact between the fixed side cam part 144 and the movable side cam part 153 via the contact state is maintained. That is, the transmission of the rotational driving force from the movable driven pulley 150 to the fixed driven pulley 140 is maintained.
　また、可動側ドリブンプーリ１５０の可動側カム部１５３は、Ｖベルト１２０側に露出する（図２参照）。これにより、軸受け１４７ａ、１４７ｂに生じた熱を、露出した可動側カム部１５３の周囲の空間を介して外部に逃がすことができる。 Further, the movable side cam portion 153 of the movable side driven pulley 150 is exposed on the V-belt 120 side (see FIG. 2). Thereby, the heat generated in the bearings 147a, 147b can be released to the outside through the space around the exposed movable cam portion 153.
　また、クラッチオンの状態においても、クラッチオフの状態と同様に、可動側カム部１５３からの押圧力は、介在部材１６１の厚さ方向に伝達されて固定側カム部１４４に伝達される。すなわち、介在部材１６１には、可動側カム部１５３からの押圧力が固定側カム部１４４に伝達される際に大きなねじり応力が掛かることがないため、高いねじり剛性を備える必要はない。 Further, even in the clutch-on state, the pressing force from the movable cam portion 153 is transmitted in the thickness direction of the intervening member 161 to the fixed-side cam portion 144, as in the clutch-off state. That is, since a large torsional stress is not applied to the intervening member 161 when the pressing force from the movable cam part 153 is transmitted to the fixed cam part 144, it is not necessary to have high torsional rigidity.
　なお、クラッチオンの状態においては、自動二輪車車の走行状態によってはドリブンプーリ１３１に駆動輪側（即ちドライブシャフト１４６側）からバックトルクが掛かる場合がある。ここで、固定側カム部１４４と可動側カム部１５３との間には、介在部材１６１が設けられていない。このため、図１０に示すように、固定側カム部１４４の固定側摺動面１４４ＭＢは、第２可動側摺動面１５３ＭＢに直接接触して可動側カム部１５３を押圧し、バックトルクが可動側カム部１５３に伝達される。 Note that in the clutch-on state, back torque may be applied to the driven pulley 131 from the drive wheel side (that is, the drive shaft 146 side) depending on the running state of the motorcycle. Here, no intervening member 161 is provided between the fixed cam section 144 and the movable cam section 153. Therefore, as shown in FIG. 10, the fixed side sliding surface 144MB of the fixed side cam section 144 directly contacts the second movable side sliding surface 153MB and presses the movable side cam section 153, causing back torque to move. The signal is transmitted to the side cam portion 153.
　一方、エンジンの回転数が減少していく場合においては、遠心クラッチ２００は、エンジンの回転駆動力のドライブシャフト１４６への伝達を遮断する。具体的には、エンジンの回転数が減少するに従ってクラッチウエイト２２０に作用する遠心力が連結スプリング２２３の弾性力（引張力）よりも小さくなり、クラッチウエイト２２０が揺動支持ピン２１３を中心として径方向の内側に向かって回動変位する。 On the other hand, when the engine speed decreases, the centrifugal clutch 200 cuts off the transmission of the rotational driving force of the engine to the drive shaft 146. Specifically, as the engine speed decreases, the centrifugal force acting on the clutch weight 220 becomes smaller than the elastic force (tensile force) of the connection spring 223, and the clutch weight 220 expands in diameter around the swing support pin 213. rotational displacement toward the inside of the direction.
　これにより、クラッチシュー２２１がクラッチアウタ２３０の円筒面２３１から離隔して元の位置（上述のアイドリング時の位置）に復帰する。すなわち、遠心クラッチ２００は、クラッチシュー２２１がクラッチアウタ２３０に接触せず回転駆動力を伝達しないクラッチオフの状態となる。 As a result, the clutch shoe 221 separates from the cylindrical surface 231 of the clutch outer 230 and returns to its original position (the above-mentioned idling position). That is, the centrifugal clutch 200 is in a clutch-off state in which the clutch shoe 221 does not contact the clutch outer 230 and does not transmit rotational driving force.
　なお、エンジンの回転数が減少するに従って可動側ドリブンプーリ１５０がトルクスプリング１７０の弾性力およびカム推力によって固定側ドリブンプーリ１４０に接近する方向（即ち方向Ｄ２）に移動する。これにより、可動側ドリブンプーリ１５０の可動側カム部１５３は、Ｖベルト１２０側への露出量が減少するとともに固定側カム部１４４との嵌合量（挿入量）が増加する。 Note that as the rotational speed of the engine decreases, the movable driven pulley 150 moves in the direction closer to the fixed driven pulley 140 (that is, the direction D2) due to the elastic force of the torque spring 170 and the cam thrust. As a result, the amount of exposure of the movable cam portion 153 of the movable driven pulley 150 to the V-belt 120 side is reduced, and the amount of fitting (insertion amount) with the fixed cam portion 144 is increased.
　上述のように、クラッチオフの状態やクラッチオンの状態のときに、固定側ドリブンプーリが回転方向Ｌに回転すると、介在部材１６１に作用する遠心力によって介在部材１６１は径方向の外側に広がろうとする。ここで、介在部材１６１の径方向の外側には壁部１４５が配置されているため、介在部材１６１の径方向の外側への変形は抑制される。これにより、介在部材１６１の破損が抑制される。 As described above, when the stationary driven pulley rotates in the rotational direction L in the clutch-off state or clutch-on state, the centrifugal force acting on the intervening member 161 causes the intervening member 161 to spread outward in the radial direction. try to Here, since the wall portion 145 is disposed on the radially outer side of the intervening member 161, radially outward deformation of the intervening member 161 is suppressed. This suppresses damage to the intervening member 161.
　以上のように、本実施形態のプーリ装置１３０によると、可動側カム部１５３は、可動側カム部１５３に対して摺動可能に構成された介在部材１６１を介して固定側カム部１４４を押圧可能に構成されている。このため、可動側ドリブンプーリ１５０が受けた回転駆動力は、介在部材１６１を介して固定側ドリブンプーリ１４０に間接的に伝達される。このとき、介在部材１６１にはねじり応力が発生しないため、ねじりに対する剛性を確保する負担が低減される。 As described above, according to the pulley device 130 of the present embodiment, the movable cam portion 153 presses the fixed cam portion 144 via the intervening member 161 configured to be slidable with respect to the movable cam portion 153. configured to be possible. Therefore, the rotational driving force received by the movable driven pulley 150 is indirectly transmitted to the fixed driven pulley 140 via the intervening member 161. At this time, since no torsional stress is generated in the intervening member 161, the burden of ensuring rigidity against torsion is reduced.
　本実施形態のプーリ装置１３０では、可動側カム部１５３は、可動側プーリ１５１から固定側プーリ１４１に向けて延び、かつ、貫通孔１４３に挿入されている。上記態様によれば、可動側ドリブンプーリ１５０が受けた回転駆動力を固定側ドリブンプーリ１４０に効果的に伝達させることができる。 In the pulley device 130 of this embodiment, the movable cam portion 153 extends from the movable pulley 151 toward the fixed pulley 141 and is inserted into the through hole 143. According to the above aspect, the rotational driving force received by the movable driven pulley 150 can be effectively transmitted to the fixed driven pulley 140.
　本実施形態のプーリ装置１３０では、固定側カム部１４４は、径方向に関して固定側スリーブ１４２と固定側プーリ１４１との間に位置する。上記態様によれば、可動側ドリブンプーリ１５０が受けた回転駆動力を固定側ドリブンプーリ１４０に効果的に伝達させることができる。 In the pulley device 130 of this embodiment, the stationary cam portion 144 is located between the stationary sleeve 142 and the stationary pulley 141 in the radial direction. According to the above aspect, the rotational driving force received by the movable driven pulley 150 can be effectively transmitted to the fixed driven pulley 140.
　本実施形態のプーリ装置１３０は、介在部材１６１が第１の方向Ｄ１に移動することを規制する引掛け部材１６２を有する。上記態様によれば、介在部材１６１が貫通孔１４３から脱落することが抑制される。 The pulley device 130 of this embodiment includes a hook member 162 that restricts movement of the intervening member 161 in the first direction D1. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
　本実施形態のプーリ装置１３０では、引掛け部材１６２は、介在部材１６１の先端部に形成され、かつ、固定側ドリブンプーリ１４０の一部に引っ掛かる。上記態様によれば、介在部材１６１が貫通孔１４３から脱落することが抑制される。 In the pulley device 130 of this embodiment, the hook member 162 is formed at the tip of the intervening member 161 and hooks on a part of the stationary driven pulley 140. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
　本実施形態のプーリ装置１３０は、介在部材１６１が第２の方向Ｄ２に移動することを規制する当接部１６３Ａを有している。上記態様によれば、介在部材１６１が貫通孔１４３から脱落することが抑制される。 The pulley device 130 of this embodiment has a contact portion 163A that restricts the intervening member 161 from moving in the second direction D2. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
　本実施形態のプーリ装置１３０では、当接部１６３Ａは、固定側カム部１４４の第１の方向Ｄ１の面１４４Ａに当接可能に構成されている。上記態様によれば、介在部材１６１が貫通孔１４３から脱落することが抑制される。 In the pulley device 130 of this embodiment, the contact portion 163A is configured to be able to contact the surface 144A of the fixed side cam portion 144 in the first direction D1. According to the above aspect, falling of the intervening member 161 from the through hole 143 is suppressed.
　本実施形態のプーリ装置１３０では、可動側摺動面１５３Ｍと固定側接触面１４４Ｍとは互いに平行に形成されている。上記態様によれば、可動側ドリブンプーリ１５０が受けた回転駆動力を、介在部材１６１を介して固定側ドリブンプーリ１４０に効果的に伝達することができる。 In the pulley device 130 of this embodiment, the movable sliding surface 153M and the fixed contact surface 144M are formed parallel to each other. According to the above aspect, the rotational driving force received by the movable driven pulley 150 can be effectively transmitted to the fixed driven pulley 140 via the intervening member 161.
　本実施形態のプーリ装置１３０では、介在部材１６１は、例えば、固定側カム部１４４および可動側カム部１５３よりも耐摩耗性が低い材料から形成されている。上記態様によれば、固定側カム部１４４および可動側カム部１５３の摩耗を抑制することができる。 In the pulley device 130 of the present embodiment, the intervening member 161 is made of, for example, a material with lower wear resistance than the fixed cam portion 144 and the movable cam portion 153. According to the above aspect, wear of the fixed cam portion 144 and the movable cam portion 153 can be suppressed.
　本実施形態のプーリ装置１３０では、介在部材１６１が可動側カム部１５３と固定側当接面１４４ＭＡとに挟まれた状態において、可動側カム部１５３と固定側摺動面１４４ＭＢとの間には隙間が形成されている。上記態様によれば、介在部材１６１を固定側ドリブンプーリ１４０に容易に組み付けることができる。また、介在部材１６１が熱膨張した場合であっても、可動側カム部１５３を挟み込まないため、可動側ドリブンプーリ１５０の摺動不良の発生を抑制することができる。 In the pulley device 130 of the present embodiment, in a state where the intervening member 161 is sandwiched between the movable cam portion 153 and the fixed side contact surface 144MA, there is no space between the movable cam portion 153 and the fixed side sliding surface 144MB. A gap is formed. According to the above aspect, the intervening member 161 can be easily assembled to the stationary driven pulley 140. Furthermore, even if the intervening member 161 thermally expands, it does not pinch the movable cam portion 153, so it is possible to suppress the occurrence of sliding failures of the movable driven pulley 150.
　本実施形態のプーリ装置１３０は、固定側スリーブ１４２と可動側スリーブ１５２との間に配置され、かつ、可動側スリーブ１５２が摺動自在に嵌合する筒部材１６３を有している。上記態様によれば、固定側スリーブ１４２と可動側スリーブ１５２とが直接摺動しないため、摩耗や焼き付きを抑制することができる。 The pulley device 130 of this embodiment includes a cylindrical member 163 that is disposed between the fixed sleeve 142 and the movable sleeve 152 and into which the movable sleeve 152 is slidably fitted. According to the above aspect, since the fixed sleeve 142 and the movable sleeve 152 do not directly slide, wear and seizure can be suppressed.
　本実施形態のプーリ装置１３０では、固定側カム部１４４の一部は、貫通孔１４３よりも可動側プーリ１５１側（第１の方向Ｄ１側）に位置する。上記態様によれば、固定側カム部１４４と介在部材１６１の介在側接触面１６１Ｍとの接触面積が大きくなるため、面圧を低減させることができる。即ち、固定側カム部１４４および介在部材１６１の耐久性が向上する。 In the pulley device 130 of the present embodiment, a portion of the fixed cam portion 144 is located closer to the movable pulley 151 (on the first direction D1 side) than the through hole 143 is. According to the above aspect, since the contact area between the stationary cam portion 144 and the intervening contact surface 161M of the intervening member 161 becomes large, the surface pressure can be reduced. That is, the durability of the stationary cam portion 144 and the intervening member 161 is improved.
　本実施形態のプーリ装置１３０では、固定側スリーブ１４２には、径方向の内側に向けて凹みかつ介在部材１６１から離隔した逃げ溝１４３Ａが形成されている。上記態様によれば、固定側スリーブ１４２を容易に成形することができる。 In the pulley device 130 of this embodiment, the stationary sleeve 142 is formed with an escape groove 143A that is recessed toward the inside in the radial direction and is spaced apart from the intervening member 161. According to the above aspect, the stationary sleeve 142 can be easily molded.
　本実施形態のプーリ装置１３０では、固定側ドリブンプーリ１４０および可動側ドリブンプーリ１５０が回転するときには、介在部材１６１が遠心力によって径方向の外側に変形しようとするが、固定側ドリブンプーリ１４０は、介在部材１６１よりも径方向の外側に位置し、かつ、介在部材１６１の径方向の外側への変形を抑制する壁部１４５を備えている。これにより、固定側ドリブンプーリ１４０に取り付けられた介在部材１６１に過度な応力が加わることがなく、介在部材１６１が破損することが抑制される。 In the pulley device 130 of this embodiment, when the fixed driven pulley 140 and the movable driven pulley 150 rotate, the intervening member 161 tends to deform outward in the radial direction due to centrifugal force, but the fixed driven pulley 140 A wall portion 145 is provided that is located on the outer side of the intervening member 161 in the radial direction and suppresses deformation of the intervening member 161 to the outside in the radial direction. As a result, excessive stress is not applied to the intervening member 161 attached to the stationary driven pulley 140, and damage to the intervening member 161 is suppressed.
　本実施形態のプーリ装置１３０では、壁部１４５は、貫通孔１４３の一部を区画する。上記態様によれば、貫通孔１４３の一部を区画する壁部１４５によって、介在部材１６１の径方向の外側への変形を抑制することができる。即ち、別途部材を設ける必要がなく、プーリ装置１３０の部品点数の増加を抑制することができる。 In the pulley device 130 of this embodiment, the wall portion 145 partitions a part of the through hole 143. According to the above aspect, the wall portion 145 that partitions a portion of the through hole 143 can suppress deformation of the intervening member 161 toward the outside in the radial direction. That is, there is no need to provide a separate member, and an increase in the number of parts of the pulley device 130 can be suppressed.
　本実施形態のプーリ装置１３０では、固定側カム部１４４は、介在部材１６１が接触する固定側接触面１４４Ｍを有し、壁部１４５は、固定側接触面１４４Ｍに連続しかつ固定側接触面１４４Ｍよりも径方向の外側に位置する。上記態様によれば、介在部材１６１の径方向の外側への変形をより確実に抑制することができる。 In the pulley device 130 of this embodiment, the fixed side cam portion 144 has a fixed side contact surface 144M with which the intervening member 161 contacts, and the wall portion 145 is continuous with the fixed side contact surface 144M and has a fixed side contact surface 144M. It is located radially outward. According to the above aspect, radially outward deformation of the intervening member 161 can be more reliably suppressed.
　本実施形態のプーリ装置１３０では、固定側接触面１４４Ｍは、介在部材１６１よりも回転方向Ｌの下流側に位置し、かつ、介在部材１６１に当接する固定側当接面１４４ＭＡと、介在部材１６１よりも回転方向Ｌの上流側に位置し、かつ、可動側カム部１５３が摺動する固定側摺動面１４４ＭＢと、を含み、壁部１４５は、固定側当接面１４４ＭＡに連続しかつ固定側当接面１４４ＭＡよりも径方向の外側に位置する。上記態様によれば、固定側ドリブンプーリ１４０が回転方向Ｌに回転するときには、固定側当接面１４４ＭＡに接触している介在部材１６１にはより大きな遠心力が加わるが、壁部１４５は固定側当接面１４４ＭＡに連続しかつ固定側当接面１４４ＭＡよりも径方向の外側に位置するため、介在部材１６１の径方向の外側への変形をより確実に抑制することができる。なお、壁部１４５は、固定側摺動面１４４ＭＢに連続しかつ固定側摺動面１４４ＭＢよりも径方向の外側に位置してもよい。 In the pulley device 130 of this embodiment, the fixed side contact surface 144M is located downstream of the intervening member 161 in the rotational direction L and is in contact with the intervening member 161. The wall portion 145 is continuous with and fixed to the fixed side contact surface 144MA. It is located on the outer side in the radial direction than the side contact surface 144MA. According to the above aspect, when the stationary side driven pulley 140 rotates in the rotation direction L, a larger centrifugal force is applied to the intervening member 161 that is in contact with the stationary side contact surface 144MA, but the wall portion 145 is Since it is continuous with the abutment surface 144MA and is located radially outward from the fixed side abutment surface 144MA, deformation of the intervening member 161 radially outward can be more reliably suppressed. Note that the wall portion 145 may be continuous with the fixed-side sliding surface 144MB and may be located on the outer side of the fixed-side sliding surface 144MB in the radial direction.
　本実施形態のプーリ装置１３０では、らせん状に形成された固定側接触面１４４Ｍとらせん状に形成された介在側接触面１６１Ｍとは面接触するように構成されている。上記態様によれば、可動側ドリブンプーリ１５０から固定側ドリブンプーリ１４０に駆動力をより効率よく伝達することができる。 In the pulley device 130 of this embodiment, the fixed side contact surface 144M formed in a spiral shape and the intervening side contact surface 161M formed in a spiral shape are configured to make surface contact. According to the above aspect, the driving force can be transmitted from the movable driven pulley 150 to the fixed driven pulley 140 more efficiently.
　本実施形態のプーリ装置１３０では、介在部材１６１は、ポリアミド樹脂の吸水率よりも低い吸水率を有する材料から形成されている。上記態様によれば、介在部材１６１の機能をより確実に発揮することができる。 In the pulley device 130 of this embodiment, the intervening member 161 is formed from a material having a water absorption rate lower than that of polyamide resin. According to the above aspect, the function of the intervening member 161 can be more reliably exhibited.
＜第２実施形態＞
　図１１は、第２実施形態に係るプーリ装置３３０および遠心クラッチ２００を備えた動力伝達機構３００を示す部分拡大断面図である。動力伝達機構３００はプーリ装置１３０に代えてプーリ装置３３０を備える点において第１実施形態に係る動力伝達機構１００と異なる。 <Second embodiment>
FIG. 11 is a partially enlarged sectional view showing a power transmission mechanism 300 including a pulley device 330 and a centrifugal clutch 200 according to the second embodiment. The power transmission mechanism 300 differs from the power transmission mechanism 100 according to the first embodiment in that it includes a pulley device 330 instead of the pulley device 130.
　図１１に示すように、プーリ装置３３０は、ドリブンプーリ３３１を備えている。ドリブンプーリ３３１は、固定側ドリブンプーリ３４０と、可動側ドリブンプーリ１５０と、固定側ドリブンプーリ３４０と可動側ドリブンプーリ１５０との間に介在する介在部材３６１と、を備えている。固定側ドリブンプーリ３４０および可動側ドリブンプーリ１５０は、Ｖベルト１２０を介して伝達されたエンジンからの駆動力によって回転駆動する。 As shown in FIG. 11, the pulley device 330 includes a driven pulley 331. The driven pulley 331 includes a fixed driven pulley 340, a movable driven pulley 150, and an intervening member 361 interposed between the fixed driven pulley 340 and the movable driven pulley 150. The fixed driven pulley 340 and the movable driven pulley 150 are rotationally driven by the driving force from the engine transmitted via the V-belt 120.
　図１１に示すように、固定側ドリブンプーリ３４０は、可動側ドリブンプーリ１５０とともにＶベルト１２０を挟む。固定側ドリブンプーリ３４０は、アルミニウム材などの金属材料から形成されている。図１２に示すように、固定側ドリブンプーリ３４０は、固定側プーリ３４１と、固定側スリーブ３４２と、貫通孔３４３と、固定側カム部３４４と、を備えている。本実施形態では、固定側プーリ３４１と、固定側スリーブ３４２と、固定側カム部３４４とは互いに同じ材料から一体的に成形されているが、互いに別部品で成形されて溶接などを介して互いに連結されていてもよい。 As shown in FIG. 11, the fixed driven pulley 340 and the movable driven pulley 150 sandwich the V-belt 120. The stationary driven pulley 340 is made of a metal material such as aluminum material. As shown in FIG. 12, the fixed driven pulley 340 includes a fixed pulley 341, a fixed sleeve 342, a through hole 343, and a fixed cam portion 344. In this embodiment, the stationary pulley 341, the stationary sleeve 342, and the stationary cam part 344 are integrally molded from the same material, but they are molded as separate parts and are welded together. May be connected.
　図１１に示すように、固定側プーリ３４１は、可動側プーリ１５１とともにＶベルト１２０を挟む。固定側プーリ３４１は、円環状に形成されている。固定側プーリ３４１は、固定側スリーブ３４２よりも径方向の外側に位置する。 As shown in FIG. 11, the fixed pulley 341 and the movable pulley 151 sandwich the V-belt 120. The fixed pulley 341 is formed in an annular shape. The fixed pulley 341 is located radially outside the fixed sleeve 342.
　固定側スリーブ３４２は、固定側プーリ３４１と一体的に回転駆動する部材である。固定側スリーブ３４２は、円筒状に形成されている。固定側スリーブ３４２の一方の端部（図１１の右側の端部）は、固定側カム部３４４を介して固定側プーリ３４１と接続している。固定側スリーブ３４２の他方の端部（図１１の左側の端部）は、連結具１４８を介して遠心クラッチ２００のドライブプレート２１０に連結されている。 The fixed sleeve 342 is a member that rotates integrally with the fixed pulley 341. The fixed sleeve 342 is formed into a cylindrical shape. One end of the stationary sleeve 342 (the right end in FIG. 11) is connected to the stationary pulley 341 via a stationary cam portion 344. The other end of the stationary sleeve 342 (the left end in FIG. 11) is connected to the drive plate 210 of the centrifugal clutch 200 via a connector 148.
　図１２に示すように、固定側カム部３４４は、径方向に関して固定側スリーブ３４２と固定側プーリ３４１との間に位置する。ここでは、３つの固定側カム部３４４が回転方向Ｌに等間隔で並ぶ。固定側カム部３４４は、介在部材３６１を介して可動側カム部１５３が摺動する部分である。固定側カム部３４４は、介在部材３６１が接触する固定側接触面３４４Ｍを有している。固定側接触面３４４Ｍは、固定側カム部３４４の回転方向Ｌの一方の端部に形成された第１固定側当接面３４４ＭＡと、固定側カム部３４４の回転方向Ｌの他方の端部に形成された第２固定側当接面３４４ＭＢ（図１４参照）と、含む。第１固定側当接面３４４ＭＡは、介在部材３６１よりも回転方向Ｌの下流側に位置する。第２固定側当接面３４４ＭＢは、介在部材３６１よりも回転方向Ｌの上流側に位置する。第１固定側当接面３４４ＭＡおよび第２固定側当接面３４４ＭＢは、回転方向Ｌに捩じれながら軸方向に延びるらせん状の曲面である。第１固定側当接面３４４ＭＡは、エンジンからの回転駆動力を介在部材３６１を介して可動側カム部１５３から受けるカム面である。第２固定側当接面３４４ＭＢは、駆動輪側からのバックトルクを介在部材３６１を介して可動側カム部１５３に与えるカム面である。 As shown in FIG. 12, the fixed cam portion 344 is located between the fixed sleeve 342 and the fixed pulley 341 in the radial direction. Here, the three fixed side cam parts 344 are lined up at equal intervals in the rotation direction L. The fixed cam portion 344 is a portion on which the movable cam portion 153 slides via the intervening member 361. The fixed side cam portion 344 has a fixed side contact surface 344M with which the intervening member 361 comes into contact. The fixed side contact surface 344M includes a first fixed side contact surface 344MA formed at one end of the fixed side cam section 344 in the rotation direction L, and a first fixed side contact surface 344MA formed at the other end of the fixed side cam section 344 in the rotation direction L. A formed second fixed side contact surface 344MB (see FIG. 14) is included. The first fixed side contact surface 344MA is located downstream of the intervening member 361 in the rotation direction L. The second fixed side contact surface 344MB is located upstream of the intervening member 361 in the rotation direction L. The first fixed-side contact surface 344MA and the second fixed-side contact surface 344MB are spiral curved surfaces that extend in the axial direction while being twisted in the rotation direction L. The first fixed side contact surface 344MA is a cam surface that receives rotational driving force from the engine from the movable cam portion 153 via the intervening member 361. The second fixed side contact surface 344MB is a cam surface that applies back torque from the driving wheel side to the movable side cam portion 153 via the intervening member 361.
　図１３に示すように、貫通孔３４３は、回転方向Ｌに関して隣り合う固定側カム部３４４の間に形成されている。ここでは、３つの貫通孔３４３が回転方向Ｌに等間隔に並ぶ。貫通孔３４３は、長孔状に形成されている。貫通孔３４３には、介在部材３６１および可動側カム部１５３が挿入される。 As shown in FIG. 13, the through hole 343 is formed between the fixed side cam parts 344 adjacent to each other in the rotation direction L. Here, three through holes 343 are arranged at equal intervals in the rotation direction L. The through hole 343 is formed in a long hole shape. The intervening member 361 and the movable cam portion 153 are inserted into the through hole 343 .
　図１４に示すように、固定側ドリブンプーリ３４０は、貫通孔３４３の一部を区画する壁部３４５を備えている。壁部３４５は、固定側カム部３４４の一部である。壁部３４５は、抑制部材の一例である。図１５および図１６に示すように、壁部３４５は、介在部材３６１（より詳細には後述する第２介在部材３６１Ｂ）よりも径方向の外側に位置する。壁部３４５は、第２固定側当接面３４４ＭＢに連続する。壁部３４５は、第２固定側当接面３４４ＭＢよりも径方向の外側に位置する。壁部３４５は、第２固定側当接面３４４ＭＢに沿って形成されている。壁部３４５は、介在部材３６１に接触（ここでは面接触）している。なお、壁部３４５と介在部材３６１との間にはわずかな隙間が空いていてもよい。壁部３４５は、介在部材３６１（特に第２介在部材３６１Ｂ）の径方向の外側への変形を抑制する。即ち、固定側ドリブンプーリ３４０が回転方向Ｌに回転するとき、介在部材３６１に作用する遠心力によって介在部材３６１は径方向の外側に広がろうとするが、介在部材３６１の径方向の外側には壁部３４５が配置されているため、介在部材３６１の径方向の外側への変形は抑制される。 As shown in FIG. 14, the stationary driven pulley 340 includes a wall portion 345 that partitions a portion of the through hole 343. The wall portion 345 is a part of the fixed cam portion 344. The wall portion 345 is an example of a suppressing member. As shown in FIGS. 15 and 16, the wall portion 345 is located radially outside of the intervening member 361 (more specifically, a second intervening member 361B to be described later). The wall portion 345 is continuous with the second fixed side contact surface 344MB. The wall portion 345 is located on the outer side in the radial direction than the second fixed side contact surface 344MB. The wall portion 345 is formed along the second fixed side contact surface 344MB. The wall portion 345 is in contact with the intervening member 361 (here, surface contact). Note that there may be a slight gap between the wall portion 345 and the intervening member 361. The wall portion 345 suppresses radially outward deformation of the intervening member 361 (particularly the second intervening member 361B). That is, when the stationary driven pulley 340 rotates in the rotation direction L, the centrifugal force acting on the intervening member 361 causes the intervening member 361 to spread outward in the radial direction; Since the wall portion 345 is disposed, radially outward deformation of the intervening member 361 is suppressed.
　図１７に示すように、固定側ドリブンプーリ３４０は、介在部材３６１よりも第１の方向Ｄ１側に位置し、かつ、介在部材３６１の移動を規制する規制壁３４６を備えている。規制壁３４６は、第１規制部材の一例である。図１８に示すように、規制壁３４６は、回転方向Ｌかつ径方向に延びる。規制壁３４６は、第１固定側当接面３４４ＭＡと連続する。規制壁３４６は、介在部材３６１（ここでは、第１介在部材３６１Ａ）と接触可能に構成されている。規制壁３４６が介在部材３６１よりも第１の方向Ｄ１側に位置するため、介在部材３６１は規制壁３４６を超えて第１の方向Ｄ１側に移動することができない。 As shown in FIG. 17, the stationary driven pulley 340 is located closer to the first direction D1 than the intervening member 361, and includes a regulating wall 346 that restricts the movement of the intervening member 361. The regulation wall 346 is an example of a first regulation member. As shown in FIG. 18, the regulating wall 346 extends in the rotation direction L and in the radial direction. The regulating wall 346 is continuous with the first fixed side contact surface 344MA. The regulating wall 346 is configured to be able to come into contact with the intervening member 361 (here, the first intervening member 361A). Since the regulation wall 346 is located closer to the first direction D1 than the intervening member 361, the intervening member 361 cannot move beyond the regulation wall 346 in the first direction D1.
　図１１に示すように、中間スリーブ３６０は、固定側ドリブンプーリ３４０と可動側ドリブンプーリ１５０との間に配置されている。図１２に示すように、中間スリーブ３６０は、筒状に形成されている。中間スリーブ３６０は、可動側ドリブンプーリ１５０を軸方向に案内するための部材である。中間スリーブ３６０は、可動側スリーブ１５２の内側に圧入して加締められている。中間スリーブ３６０は、固定側スリーブ３４２に対して摺動自在に外嵌する。中間スリーブ３６０は、可動側スリーブ１５２よりも軸方向の長さが長い。筒部材１６３は、固定側スリーブ３４２よりも軸方向の長さが短い。 As shown in FIG. 11, the intermediate sleeve 360 is arranged between the fixed driven pulley 340 and the movable driven pulley 150. As shown in FIG. 12, the intermediate sleeve 360 is formed into a cylindrical shape. The intermediate sleeve 360 is a member for guiding the movable driven pulley 150 in the axial direction. The intermediate sleeve 360 is press-fitted inside the movable sleeve 152 and crimped. The intermediate sleeve 360 is slidably fitted onto the stationary sleeve 342. The intermediate sleeve 360 has a longer axial length than the movable sleeve 152. The cylindrical member 163 has a shorter length in the axial direction than the stationary sleeve 342.
　介在部材３６１は、上述した第１実施形態の介在部材１６１と同様の材料から形成されている。図１８に示すように、介在部材３６１は、固定側プーリ３４１の第２の方向Ｄ２の面側から固定側ドリブンプーリ３４０の貫通孔３４３に挿入されている。介在部材３６１は、貫通孔３４３に挿入されて固定側ドリブンプーリ３４０に取り付けられている。本実施形態では、３つの介在部材３６１が回転方向Ｌに等間隔に配置されている。介在部材３６１は、回転方向Ｌに関して固定側カム部３４４の第１固定側当接面３４４ＭＡと第２固定側当接面３４４ＭＢとの間に位置する。図１９Ａおよび図１９Ｂに示すように、介在部材３６１は、第１固定側当接面３４４ＭＡに接触する第１介在部材３６１Ａと、第２固定側当接面３４４ＭＢに接触する第２介在部材３６１Ｂと、第１介在部材３６１Ａの径方向の外側の部分と第２介在部材３６１Ｂの径方向の外側の部分とを連結する連結部材３６１Ｃとを備えている。第１介在部材３６１Ａは、第１固定側当接面３４４ＭＡと可動側カム部１５３との間に位置する。第２介在部材３６１Ｂは、第２固定側当接面３４４ＭＢと可動側カム部１５３との間に位置する。第１介在部材３６１Ａおよび第２介在部材３６１Ｂは、可動側カム部１５３に対して摺動可能に構成されている。 The intervening member 361 is made of the same material as the intervening member 161 of the first embodiment described above. As shown in FIG. 18, the intervening member 361 is inserted into the through hole 343 of the stationary driven pulley 340 from the surface side of the stationary pulley 341 in the second direction D2. The intervening member 361 is inserted into the through hole 343 and attached to the stationary driven pulley 340. In this embodiment, three intervening members 361 are arranged at equal intervals in the rotation direction L. The intervening member 361 is located between the first fixed side contact surface 344MA and the second fixed side contact surface 344MB of the fixed side cam portion 344 in the rotation direction L. As shown in FIGS. 19A and 19B, the intervening member 361 includes a first intervening member 361A that contacts the first fixed-side contact surface 344MA, and a second interposed member 361B that contacts the second fixed-side contact surface 344MB. , a connecting member 361C that connects the radially outer portion of the first intervening member 361A and the radially outer portion of the second intervening member 361B. The first intervening member 361A is located between the first fixed side contact surface 344MA and the movable side cam portion 153. The second intervening member 361B is located between the second fixed side contact surface 344MB and the movable side cam portion 153. The first intervening member 361A and the second intervening member 361B are configured to be slidable with respect to the movable cam portion 153.
　図１９Ａおよび図１９Ｂに示すように、介在部材３６１は、固定側接触面３４４Ｍまたは可動側摺動面１５３Ｍに対向して配置された介在側接触面３６１Ｍを有している。介在側接触面３６１Ｍは、固定側カム部３４４に当接する面である。介在側接触面３６１Ｍは、可動側カム部１５３が摺動する面である。介在側接触面３６１Ｍは、可動側摺動面１５３Ｍと面接触して摺動するように構成されている。介在側接触面３６１Ｍは、第１介在部材３６１Ａの回転方向Ｌの一方の端部に形成された第１介在側当接面３６１ＭＡ（図１９Ａ参照）と、第２介在部材３６１Ｂの回転方向Ｌの他方の端部に形成された第２介在側当接面３６１ＭＢ（図１９Ｂ参照）と、第１介在部材３６１Ａの回転方向Ｌの他方の端部に形成された第１介在側摺動面３６１ＭＣ（図１９Ｂ参照）と、第２介在部材３６１Ｂの回転方向Ｌの一方の端部に形成された第２介在側摺動面３６１ＭＤ（図１９Ａ参照）と、を有する。第１介在側当接面３６１ＭＡは、第１固定側当接面３４４ＭＡに対向する。第１介在側当接面３６１ＭＡは、第１固定側当接面３４４ＭＡと面接触する。第２介在側当接面３６１ＭＢは、第２固定側当接面３４４ＭＢに対向する。第２介在側当接面３６１ＭＢは、第２固定側当接面３４４ＭＢと面接触する。第１介在側摺動面３６１ＭＣは、第１可動側摺動面１５３ＭＡに対向する。第１介在側摺動面３６１ＭＣは、第１可動側摺動面１５３ＭＡと面接触して摺動する。第２介在側摺動面３６１ＭＤは、第２可動側摺動面１５３ＭＢに対向する。第２介在側摺動面３６１ＭＤは、第２可動側摺動面１５３ＭＢと面接触して摺動する。第１介在側当接面３６１ＭＡ、第２介在側当接面３６１ＭＢ、第１介在側摺動面３６１ＭＣおよび第２介在側摺動面３６１ＭＤは、回転方向Ｌに捩じれながら軸方向に延びるらせん状の曲面である。 As shown in FIGS. 19A and 19B, the intervening member 361 has an intervening contact surface 361M disposed opposite to the fixed contact surface 344M or the movable sliding surface 153M. The intervening side contact surface 361M is a surface that comes into contact with the fixed side cam portion 344. The intervening contact surface 361M is a surface on which the movable cam portion 153 slides. The intervening contact surface 361M is configured to slide in surface contact with the movable sliding surface 153M. The intervening side contact surface 361M is formed between a first intervening side contact surface 361MA (see FIG. 19A) formed at one end of the first intervening member 361A in the rotational direction L and a second intervening member 361B in the rotational direction L. A second intervening side contact surface 361MB (see FIG. 19B) formed at the other end and a first intervening side sliding surface 361MC formed at the other end in the rotational direction L of the first intervening member 361A ( (see FIG. 19B), and a second intervening side sliding surface 361MD (see FIG. 19A) formed at one end of the second intervening member 361B in the rotation direction L. The first intervening side contact surface 361MA faces the first fixed side contact surface 344MA. The first intervening side contact surface 361MA makes surface contact with the first fixed side contact surface 344MA. The second intervening side contact surface 361MB faces the second fixed side contact surface 344MB. The second intervening side contact surface 361MB makes surface contact with the second fixed side contact surface 344MB. The first intervening sliding surface 361MC faces the first movable sliding surface 153MA. The first intervening sliding surface 361MC slides in surface contact with the first movable sliding surface 153MA. The second intervening side sliding surface 361MD faces the second movable side sliding surface 153MB. The second intervening sliding surface 361MD slides in surface contact with the second movable sliding surface 153MB. The first intervening side contact surface 361MA, the second intervening side contact surface 361MB, the first intervening side sliding surface 361MC, and the second intervening side sliding surface 361MD have a spiral shape extending in the axial direction while being twisted in the rotational direction L. It is a curved surface.
　図１８に示すように、固定側ドリブンプーリ３４０は、固定側プーリ３４１に形成され、かつ、介在部材３６１の連結部材３６１Ｃの径方向の外側への変形を抑制する変形抑制壁３４７を有する。変形抑制壁３４７は、リング状に形成されている。変形抑制壁３４７は、固定側カム部３４４の径方向の外側に配置されている。なお、駆動源が停止した状態において、径方向に関して、連結部材３６１Ｃと変形抑制壁３４７との間には、隙間が形成されている。また、固定側ドリブンプーリ３４０および可動側ドリブンプーリ１５０が回転するとき、連結部材３６１Ｃは径方向の外側にわずかに変位して変形抑制壁３４７と接触する。なお、介在部材３６１の固定側ドリブンプーリ３４０に対する径方向および回転方向Ｌの位置決めは、固定側接触面３４４Ｍと介在側接触面３６１Ｍとを面接触させることによって行われており、連結部材３６１Ｃを変形抑制壁３４７に突き当てることによって行われていない。 As shown in FIG. 18, the stationary driven pulley 340 has a deformation suppressing wall 347 that is formed on the stationary pulley 341 and that suppresses radially outward deformation of the connecting member 361C of the intervening member 361. The deformation suppressing wall 347 is formed in a ring shape. The deformation suppressing wall 347 is arranged on the outside of the stationary cam portion 344 in the radial direction. Note that when the drive source is stopped, a gap is formed between the connecting member 361C and the deformation suppressing wall 347 in the radial direction. Further, when the fixed driven pulley 340 and the movable driven pulley 150 rotate, the connecting member 361C is slightly displaced radially outward and comes into contact with the deformation suppressing wall 347. Note that positioning of the intervening member 361 with respect to the fixed driven pulley 340 in the radial direction and rotational direction L is performed by bringing the fixed side contact surface 344M and the intervening side contact surface 361M into surface contact, and by deforming the connecting member 361C. This is not done by hitting the restraining wall 347.
　図２０に示すように、固定側ドリブンプーリ３４０に取り付けられた介在部材３６１が、方向Ｄ２から脱落しないように、固定側ドリブンプーリ３４０には、介在部材３６１の抜け止め防止用のワッシャー３７０およびサークリップ３７１が取り付けられている。ワッシャー３７０は、介在部材３６１よりも方向Ｄ２側に設けられている。ワッシャー３７０は、軸方向から見て介在部材３６１の連結部材３６１Ｃと重なる。ワッシャー３７０は、連結部材３６１Ｃと接触可能に設けられている。サークリップ３７１は、ワッシャー３７０を固定側プーリ３４１に保持するための部材である。サークリップ３７１は、ワッシャー３７０よりも方向Ｄ２側に設けられている。サークリップ３７１は、変形抑制壁３４７に設けられたサークリップ保持溝３４７Ａに保持されている。サークリップ３７１は、第２規制部材の一例である。即ち、サークリップ３７１は、介在部材３６１が第２の方向Ｄ２に移動することを規制する。 As shown in FIG. 20, in order to prevent the intervening member 361 attached to the stationary driven pulley 340 from falling off in the direction D2, the stationary driven pulley 340 is equipped with a washer 370 for preventing the intervening member 361 from falling off and a server. A clip 371 is attached. The washer 370 is provided closer to the direction D2 than the intervening member 361. The washer 370 overlaps the connecting member 361C of the intervening member 361 when viewed from the axial direction. The washer 370 is provided so as to be able to come into contact with the connecting member 361C. The circlip 371 is a member for holding the washer 370 on the fixed pulley 341. The circlip 371 is provided closer to the direction D2 than the washer 370. The circlip 371 is held in a circlip holding groove 347A provided in the deformation suppressing wall 347. The circlip 371 is an example of a second regulating member. That is, the circlip 371 restricts the intervening member 361 from moving in the second direction D2.
　ここで、クラッチオフの状態において、可動側ドリブンプーリ１５０はトルクスプリング１７０によって固定側ドリブンプーリ３４０に最も接近する位置またはその近傍の位置に押圧されている。このため、図２１Ａに示すように、可動側カム部１５３が貫通孔３４３内に奥深くまで進入した状態で第１可動側摺動面１５３ＭＡが第１固定側当接面３４４ＭＡに対して介在部材３６１の第１介在部材３６１Ａを介して密着し、回転駆動力を固定側ドリブンプーリ１４０に伝達する。 Here, in the clutch-off state, the movable driven pulley 150 is pressed by the torque spring 170 to a position closest to the stationary driven pulley 340 or a position in the vicinity thereof. Therefore, as shown in FIG. 21A, when the movable cam portion 153 has entered deeply into the through hole 343, the first movable sliding surface 153MA is connected to the first fixed abutting surface 344MA by the intervening member 361. are in close contact with each other via the first intervening member 361A, and transmit rotational driving force to the stationary driven pulley 140.
　また、クラッチオンの状態において、図２１Ｂに示すように、介在部材３６１を介した第１可動側摺動面１５３ＭＡと第１固定側当接面３４４ＭＡとの接触面積は、最少または最少に近い値となるが、介在部材３６１を介した固定側カム部３４４と可動側カム部１５３との接触状態は維持される。すなわち、可動側ドリブンプーリ１５０から固定側ドリブンプーリ３４０への回転駆動力の伝達は維持される。 In addition, in the clutch-on state, as shown in FIG. 21B, the contact area between the first movable sliding surface 153MA and the first fixed contact surface 344MA via the intervening member 361 is at a minimum or a value close to the minimum. However, the state of contact between the stationary cam portion 344 and the movable cam portion 153 via the intervening member 361 is maintained. That is, the transmission of the rotational driving force from the movable driven pulley 150 to the fixed driven pulley 340 is maintained.
　なお、クラッチオンの状態においてドリブンプーリ３３１に駆動輪側（即ちドライブシャフト１４６側）からバックトルクが掛かる場合には、図２２に示すように、固定側カム部３４４の第２固定側当接面３４４ＭＢは、介在部材３６１の第２介在部材３６１Ｂを介して第２可動側摺動面１５３ＭＢに直接接触して可動側カム部１５３を押圧し、バックトルクが可動側カム部１５３に伝達される。 Note that when back torque is applied to the driven pulley 331 from the drive wheel side (that is, the drive shaft 146 side) in the clutch-on state, as shown in FIG. 344MB directly contacts the second movable sliding surface 153MB via the second intervening member 361B of the intervening member 361 to press the movable cam portion 153, and back torque is transmitted to the movable cam portion 153.
　上述のように、クラッチオフの状態やクラッチオンの状態のときに、固定側ドリブンプーリが回転方向Ｌに回転すると、介在部材３６１に作用する遠心力によって介在部材３６１は径方向の外側に広がろうとする。ここで、介在部材３６１の径方向の外側には壁部３４５や変形抑制壁３４７が配置されているため、介在部材３６１の径方向の外側への変形は抑制される。これにより、介在部材３６１の破損が抑制される。 As described above, when the stationary driven pulley rotates in the rotation direction L in the clutch-off state or clutch-on state, the centrifugal force acting on the intervening member 361 causes the intervening member 361 to spread outward in the radial direction. try to Here, since the wall portion 345 and the deformation suppressing wall 347 are arranged on the outside of the intervening member 361 in the radial direction, deformation of the intervening member 361 toward the outside in the radial direction is suppressed. This suppresses damage to the intervening member 361.
　以上のように、本実施形態のプーリ装置３３０によると、可動側カム部１５３は、可動側カム部１５３に対して摺動可能に構成された介在部材３６１を介して固定側カム部３４４を押圧可能に構成されている。このため、可動側ドリブンプーリ１５０が受けた回転駆動力は、介在部材３６１を介して固定側ドリブンプーリ３４０に間接的に伝達される。このとき、介在部材３６１にはねじり応力が発生しないため、ねじりに対する剛性を確保する負担が低減される。 As described above, according to the pulley device 330 of the present embodiment, the movable cam portion 153 presses the fixed cam portion 344 via the intervening member 361 configured to be slidable with respect to the movable cam portion 153. configured to be possible. Therefore, the rotational driving force received by the movable driven pulley 150 is indirectly transmitted to the fixed driven pulley 340 via the intervening member 361. At this time, since no torsional stress is generated in the intervening member 361, the burden of ensuring rigidity against torsion is reduced.
　本実施形態のプーリ装置３３０では、規制壁３４６は、固定側ドリブンプーリ３４０に設けられ、かつ、介在部材３６１よりも第１の方向Ｄ１側に位置する。上記態様によれば、介在部材３６１が貫通孔３４３から脱落することが抑制される。 In the pulley device 330 of the present embodiment, the regulating wall 346 is provided on the stationary driven pulley 340 and is located closer to the first direction D1 than the intervening member 361. According to the above aspect, falling of the intervening member 361 from the through hole 343 is suppressed.
　本実施形態のプーリ装置３３０では、サークリップ３７１は、固定側ドリブンプーリ３４０に取り付けられている。上記態様によれば、介在部材３６１が貫通孔３４３から脱落することが抑制される。 In the pulley device 330 of this embodiment, the circlip 371 is attached to the stationary driven pulley 340. According to the above aspect, falling of the intervening member 361 from the through hole 343 is suppressed.
　本実施形態のプーリ装置３３０では、固定側ドリブンプーリ３４０および可動側ドリブンプーリ１５０が回転するときには、介在部材３６１が遠心力によって径方向の外側に変形しようとするが、固定側ドリブンプーリ３４０は、介在部材３６１よりも径方向の外側に位置し、かつ、介在部材３６１の径方向の外側への変形を抑制する壁部３４５を備えている。これにより、固定側ドリブンプーリ３４０に取り付けられた介在部材３６１に過度な応力が加わることがなく、介在部材３６１が破損することが抑制される。 In the pulley device 330 of this embodiment, when the fixed driven pulley 340 and the movable driven pulley 150 rotate, the intervening member 361 tends to deform outward in the radial direction due to centrifugal force, but the fixed driven pulley 340 A wall portion 345 is provided that is located on the outer side of the intervening member 361 in the radial direction and suppresses deformation of the intervening member 361 to the outside in the radial direction. As a result, excessive stress is not applied to the intervening member 361 attached to the stationary driven pulley 340, and damage to the intervening member 361 is suppressed.
　本実施形態のプーリ装置３３０では、壁部３４５は、貫通孔３４３の一部を区画する。上記態様によれば、貫通孔３４３の一部を区画する壁部３４５によって、介在部材３６１の径方向の外側への変形を抑制することができる。即ち、別途部材を設ける必要がなく、プーリ装置３３０の部品点数の増加を抑制することができる。 In the pulley device 330 of this embodiment, the wall portion 345 partitions a part of the through hole 343. According to the above aspect, the wall portion 345 that partitions a portion of the through hole 343 can suppress deformation of the intervening member 361 to the outside in the radial direction. That is, there is no need to provide a separate member, and an increase in the number of parts of the pulley device 330 can be suppressed.
　本実施形態のプーリ装置３３０では、壁部３４５は、固定側接触面３４４Ｍに連続しかつ固定側接触面３４４Ｍよりも径方向の外側に位置する。上記態様によれば、介在部材３６１の径方向の外側への変形をより確実に抑制することができる。 In the pulley device 330 of this embodiment, the wall portion 345 is continuous with the fixed side contact surface 344M and is located on the outer side of the fixed side contact surface 344M in the radial direction. According to the above aspect, radially outward deformation of the intervening member 361 can be more reliably suppressed.
　本実施形態のプーリ装置３３０では、介在部材３６１は、固定側プーリ３４１の第２の方向Ｄ２の面側から貫通孔３４３に挿入されている。上記態様によれば、プーリ装置３３０を組み立てる際に容易に介在部材３６１を貫通孔３４３に挿入することができる。 In the pulley device 330 of this embodiment, the intervening member 361 is inserted into the through hole 343 from the surface side of the fixed pulley 341 in the second direction D2. According to the above aspect, the intervening member 361 can be easily inserted into the through hole 343 when assembling the pulley device 330.
　本実施形態のプーリ装置３３０では、固定側ドリブンプーリ３４０は、介在部材３６１よりも第１の方向Ｄ１側に位置し、かつ、介在部材３６１の移動を規制する規制壁３４６を備えている。上記態様によれば、貫通孔３４３に挿入された介在部材３６１が第１の方向Ｄ１に抜け落ちるのを規制することができる。 In the pulley device 330 of this embodiment, the stationary driven pulley 340 is located on the first direction D1 side with respect to the intervening member 361, and includes a regulating wall 346 that restricts movement of the intervening member 361. According to the above aspect, it is possible to prevent the intervening member 361 inserted into the through hole 343 from falling out in the first direction D1.
　本実施形態のプーリ装置３３０では、規制壁３４６は、第１固定側当接面３４４ＭＡに連続する。上記態様によれば、貫通孔３４３に挿入された介在部材３６１が第１の方向Ｄ１に抜け落ちるのをより確実に規制することができる。 In the pulley device 330 of this embodiment, the regulation wall 346 is continuous with the first fixed side contact surface 344MA. According to the above aspect, it is possible to more reliably prevent the intervening member 361 inserted into the through hole 343 from falling out in the first direction D1.
　本実施形態のプーリ装置３３０では、介在部材３６１は、第１固定側当接面３４４ＭＡに当接する第１介在部材３６１Ａと、第２固定側当接面３４４ＭＢに当接する第２介在部材３６１Ｂと、を備えている。上記態様によれば、固定側カム部１４４と可動側カム部１５３とが直接摺動することを抑制することができる。 In the pulley device 330 of this embodiment, the intervening member 361 includes a first intervening member 361A that contacts the first fixed side contact surface 344MA, a second interposed member 361B that contacts the second fixed side contact surface 344MB, It is equipped with According to the above aspect, it is possible to suppress direct sliding between the fixed side cam part 144 and the movable side cam part 153.
　本実施形態のプーリ装置３３０では、介在部材３６１は、第１介在部材３６１Ａの径方向の外側の部分と第２介在部材３６１Ｂの径方向の外側の部分とを連結する連結部材３６１Ｃを備えている。上記態様によれば、介在部材３６１の組み付け性が向上する。 In the pulley device 330 of this embodiment, the intervening member 361 includes a connecting member 361C that connects the radially outer portion of the first intervening member 361A and the radially outer portion of the second intervening member 361B. . According to the above aspect, the ease of assembling the intervening member 361 is improved.
　本実施形態のプーリ装置３３０では、固定側ドリブンプーリ３４０は、固定側プーリ３４１に形成され、かつ、連結部材３６１Ｃの径方向の外側への変形を抑制する変形抑制壁３４７を有し、駆動源が停止した状態において、径方向に関して、連結部材３６１Ｃと変形抑制壁３４７との間には、隙間が形成されている。上記態様によれば、介在部材３６１が熱膨張によって大きくなっても、介在部材３６１は過度に圧迫されず、介在部材３６１の破損が抑制される。 In the pulley device 330 of the present embodiment, the fixed driven pulley 340 has a deformation suppressing wall 347 formed on the fixed pulley 341 and suppressing radially outward deformation of the connecting member 361C, and has a drive source. In the stopped state, a gap is formed between the connecting member 361C and the deformation suppressing wall 347 in the radial direction. According to the above aspect, even if the intervening member 361 becomes larger due to thermal expansion, the intervening member 361 is not excessively compressed, and damage to the intervening member 361 is suppressed.
　本実施形態のプーリ装置３３０では、固定側ドリブンプーリ３４０および可動側ドリブンプーリ１５０が回転するとき、連結部材３６１Ｃは、変形抑制壁３４７と接触する。上記態様によれば、変形抑制壁３４７によって介在部材３６１の径方向の外側への変形が抑制される。 In the pulley device 330 of this embodiment, when the fixed driven pulley 340 and the movable driven pulley 150 rotate, the connecting member 361C comes into contact with the deformation suppressing wall 347. According to the above aspect, the deformation suppressing wall 347 suppresses radially outward deformation of the intervening member 361.
　本実施形態のプーリ装置では、固定側接触面３４４Ｍと介在側接触面３６１Ｍとを面接触させることによって、介在部材３６１の固定側ドリブンプーリ３４０に対する径方向および回転方向Ｌの位置決めがされている。上記態様によれば、介在部材３６１をより適切に配置することができる。 In the pulley device of this embodiment, the intervening member 361 is positioned relative to the fixed driven pulley 340 in the radial direction and rotational direction L by bringing the fixed side contact surface 344M and the intervening side contact surface 361M into surface contact. According to the above aspect, the intervening member 361 can be arranged more appropriately.
　以上、本発明の好適な実施形態について説明した。しかし、上述の実施形態は例示に過ぎず、本発明は他の種々の形態で実施することができる。 The preferred embodiments of the present invention have been described above. However, the above-described embodiments are merely illustrative, and the present invention can be implemented in various other forms.
　上述した第１実施形態では、固定側カム部１４４の一部である壁部１４５が介在部材１６１の径方向の外側への変形を抑制していたが、これに限定されない。固定側カム部１４４とは別体の抑制部材を用いて、介在部材１６１の径方向の外側への変形を抑制してもよい。また、上述した第２実施形態では、固定側カム部３４４の一部である壁部３４５が介在部材３６１の径方向の外側への変形を抑制していたが、これに限定されない。固定側カム部３４４とは別体の抑制部材を用いて、介在部材３６１の径方向の外側への変形を抑制してもよい。 In the first embodiment described above, the wall portion 145, which is a part of the stationary cam portion 144, suppresses the radially outward deformation of the intervening member 161, but the present invention is not limited thereto. A suppressing member separate from the fixed cam portion 144 may be used to suppress radially outward deformation of the intervening member 161. Further, in the second embodiment described above, the wall portion 345 that is a part of the fixed side cam portion 344 suppresses the deformation of the intervening member 361 toward the outside in the radial direction, but the present invention is not limited thereto. A suppressing member separate from the fixed cam portion 344 may be used to suppress radially outward deformation of the intervening member 361.
　上述した実施形態では、貫通孔１４３は、固定側ドリブンプーリ１４０において回転方向Ｌに関して隣り合う固定側カム部１４４の間に形成され、可動側カム部１５３が貫通孔１４３に挿入されているが、これに限定されない。貫通孔１４３は、可動側ドリブンプーリ１５０において回転方向Ｌに関して隣り合う可動側カム部１５３の間に形成され、固定側カム部１４４が貫通孔１４３に挿入されていてもよい。即ち、貫通孔１４３は、固定側ドリブンプーリ１４０に形成されていてもよいし、可動側ドリブンプーリ１５０に形成されていてもよい。貫通孔３４３についても同様である。 In the embodiment described above, the through hole 143 is formed between the fixed cam parts 144 adjacent to each other in the rotation direction L in the fixed driven pulley 140, and the movable cam part 153 is inserted into the through hole 143. It is not limited to this. The through hole 143 may be formed between adjacent movable cam parts 153 in the rotation direction L in the movable driven pulley 150, and the fixed cam part 144 may be inserted into the through hole 143. That is, the through hole 143 may be formed in the fixed driven pulley 140 or the movable driven pulley 150. The same applies to the through hole 343.
　上述の各実施形態においては、プーリ装置１３０、３３０は、遠心クラッチ２００に適用していたが、これに限定されない。例えば、プーリ装置１３０、３３０は、エンジンまたは電動モータなどの駆動源からの駆動力をドライブシャフト１４６などの出力軸に伝達する装置に広く適用することができる。また、プーリ装置１３０、３３０は、電動モータを駆動源として自走する電動車両（例えば電気自動車や電動二輪車）において用いることができる。 In each of the embodiments described above, the pulley devices 130, 330 are applied to the centrifugal clutch 200, but the invention is not limited thereto. For example, the pulley devices 130, 330 can be widely applied to devices that transmit driving force from a drive source such as an engine or an electric motor to an output shaft such as the drive shaft 146. Further, the pulley devices 130 and 330 can be used in an electric vehicle (for example, an electric vehicle or an electric two-wheeled vehicle) that runs on its own using an electric motor as a drive source.
１００　動力伝達機構
１０１　変速機
１２０　Ｖベルト
１３０　プーリ装置
１３１　ドリブンプーリ
１４０　固定側ドリブンプーリ
１４１　固定側プーリ
１４２　固定側スリーブ
１４３　貫通孔
１４４　固定側カム部
１４４Ｍ　固定側接触面
１４４ＭＡ　固定側当接面
１４４ＭＢ　固定側摺動面
１４５　壁部（抑制部材）
１５０　可動側ドリブンプーリ
１５１　可動側プーリ
１５２　可動側スリーブ
１５３　可動側カム部
１５３Ｍ　可動側摺動面
１５３ＭＡ　第１可動側摺動面
１５３ＭＢ　第２可動側摺動面
１６１　介在部材
１６１Ｍ　介在側接触面
１６１ＭＡ　介在側当接面
１６１ＭＢ　介在側摺動面
１６２　引掛け部材（第１規制部材） 100 Power transmission mechanism 101 Transmission 120 V-belt 130 Pulley device 131 Driven pulley 140 Fixed side driven pulley 141 Fixed side pulley 142 Fixed side sleeve 143 Through hole 144 Fixed side cam portion 144M Fixed side contact surface 144MA Fixed side contact surface 144MB Fixed Side sliding surface 145 wall (suppression member)
150 Movable side driven pulley 151 Movable side pulley 152 Movable side sleeve 153 Movable side cam portion 153M Movable side sliding surface 153MA 1st movable side sliding surface 153MB 2nd movable side sliding surface 161 Intervening member 161M Intervening side contact surface 161MA Interposition Side contact surface 161MB Intervening side sliding surface 162 Hook member (first regulating member)

Claims (30)

  1. 　ベルトを介して伝達された駆動源からの駆動力によって回転駆動する固定側ドリブンプーリおよび可動側ドリブンプーリを有するプーリ装置であって、
    　前記固定側ドリブンプーリは、
    　　円筒状に形成された固定側スリーブと、
    　　前記固定側スリーブよりも径方向の外側に位置する固定側プーリと、
    　　前記固定側ドリブンプーリが回転する方向を回転方向としたとき、前記回転方向に並ぶ複数の固定側カム部と、を有し、
    　前記可動側ドリブンプーリは、
    　　円筒状に形成され、かつ、前記固定側スリーブに外嵌する可動側スリーブと、
    　　前記可動側スリーブよりも前記径方向の外側に位置し、かつ、前記固定側プーリと共に前記ベルトを挟み、かつ、前記固定側プーリに対して接近および離隔可能に構成された可動側プーリと、
    　　前記回転方向に並ぶ複数の可動側カム部と、を有し、
    　前記固定側ドリブンプーリにおいて前記回転方向に関して隣り合う前記固定側カム部の間、もしくは、前記可動側ドリブンプーリにおいて前記回転方向に関して隣り合う前記可動側カム部の間には、前記回転方向に並ぶ複数の貫通孔が形成され、
    　前記固定側ドリブンプーリに前記貫通孔が形成されている場合には、前記可動側カム部が前記貫通孔に挿入され、前記可動側ドリブンプーリに前記貫通孔が形成されている場合には、前記固定側カム部が前記貫通孔に挿入され、
    　前記固定側ドリブンプーリと前記可動側ドリブンプーリとの間に介在する介在部材をさらに有し、
    　前記介在部材は、前記回転方向に関して前記固定側カム部と前記可動側カム部との間に位置し、かつ、前記可動側カム部に対して摺動可能に構成され、
    　前記可動側カム部は、前記介在部材を介して前記固定側カム部を押圧可能に構成されている、プーリ装置。     A pulley device having a fixed side driven pulley and a movable side driven pulley that are rotationally driven by a driving force from a driving source transmitted via a belt,
    The fixed side driven pulley is
    a fixed sleeve formed in a cylindrical shape;
    a fixed-side pulley located radially outside the fixed-side sleeve;
    a plurality of fixed-side cam portions arranged in the rotational direction when the direction in which the fixed-side driven pulley rotates is the rotational direction;
    The movable side driven pulley is
    a movable sleeve formed in a cylindrical shape and fitted onto the fixed sleeve;
    a movable pulley located radially outside the movable sleeve, sandwiching the belt together with the fixed pulley, and configured to be able to approach and separate from the fixed pulley;
    a plurality of movable side cam parts arranged in the rotation direction,
    Between the fixed side cam parts adjacent in the rotation direction in the fixed side driven pulley, or between the movable cam parts adjacent in the rotation direction in the movable side driven pulley, there are a plurality of cam parts arranged in the rotation direction. A through hole is formed,
    When the through hole is formed in the fixed driven pulley, the movable cam portion is inserted into the through hole, and when the through hole is formed in the movable driven pulley, the movable cam part is inserted into the through hole. A fixed side cam part is inserted into the through hole,
    further comprising an intervening member interposed between the fixed side driven pulley and the movable side driven pulley,
    The intervening member is located between the fixed cam part and the movable cam part in the rotation direction, and is configured to be slidable with respect to the movable cam part,
    The movable cam portion is configured to be able to press the fixed cam portion via the intervening member.
  2. 　前記貫通孔は、前記固定側ドリブンプーリに形成され、
    　前記可動側カム部は、前記可動側プーリから前記固定側プーリに向けて延び、かつ、前記貫通孔に挿入されている、請求項１記載のプーリ装置。     The through hole is formed in the stationary driven pulley,
    The pulley device according to claim 1, wherein the movable cam portion extends from the movable pulley toward the fixed pulley and is inserted into the through hole.
  3. 　前記固定側カム部は、前記径方向に関して前記固定側スリーブと前記固定側プーリとの間に位置する、請求項１または２記載のプーリ装置。 The pulley device according to claim 1 or 2, wherein the stationary cam portion is located between the stationary sleeve and the stationary pulley in the radial direction.
  4. 　前記可動側プーリが前記固定側プーリに対して離隔する方向を第１の方向、前記可動側プーリが前記固定側プーリに対して接近する方向を第２の方向としたとき、前記介在部材が前記第１の方向に移動することを規制する第１規制部材を有する、請求項１または２記載のプーリ装置。 When the direction in which the movable pulley moves away from the fixed pulley is a first direction, and the direction in which the movable pulley approaches the fixed pulley is a second direction, the intervening member The pulley device according to claim 1 or 2, further comprising a first regulating member that regulates movement in the first direction.
  5. 　前記第１規制部材は、前記介在部材の先端部に形成され、かつ、前記固定側ドリブンプーリの一部に引っ掛かる引掛け部である、請求項４記載のプーリ装置。 The pulley device according to claim 4, wherein the first regulating member is a hook portion that is formed at the tip of the intervening member and that is hooked on a part of the stationary driven pulley.
  6. 　前記第１規制部材は、前記固定側ドリブンプーリに設けられ、かつ、前記介在部材よりも前記第１の方向側に位置する規制壁である、請求項４に記載のプーリ装置。 The pulley device according to claim 4, wherein the first regulating member is a regulating wall provided on the stationary driven pulley and located on the first direction side with respect to the intervening member.
  7. 　前記可動側プーリが前記固定側プーリに対して離隔する方向を第１の方向、前記可動側プーリが前記固定側プーリに対して接近する方向を第２の方向としたとき、前記介在部材が前記第２の方向に移動することを規制する第２規制部材を有する、請求項１または２記載のプーリ装置。 When the direction in which the movable pulley moves away from the fixed pulley is a first direction, and the direction in which the movable pulley approaches the fixed pulley is a second direction, the intervening member The pulley device according to claim 1 or 2, further comprising a second regulating member that regulates movement in the second direction.
  8. 　前記介在部材は、前記固定側カム部の前記第１の方向側の面に当接可能な当接部を有し、
    　前記第２規制部材は、前記当接部である、請求項７に記載のプーリ装置。     The intervening member has a contact portion that can come into contact with the first direction side surface of the stationary cam portion,
    The pulley device according to claim 7, wherein the second regulating member is the contact portion.
  9. 　前記第２規制部材は、前記固定側ドリブンプーリに取り付けられたサークリップである、請求項７に記載のプーリ装置。 The pulley device according to claim 7, wherein the second regulating member is a circlip attached to the stationary driven pulley.
  10. 　前記固定側カム部は、前記介在部材が接触する固定側接触面を有し、
    　前記可動側カム部は、前記介在部材が摺動する可動側摺動面を有し、
    　前記固定側接触面と前記可動側摺動面とは、互に平行に形成されている、請求項１または２記載のプーリ装置。     The fixed side cam portion has a fixed side contact surface with which the intervening member comes into contact,
    The movable side cam portion has a movable side sliding surface on which the intervening member slides,
    The pulley device according to claim 1 or 2, wherein the fixed side contact surface and the movable side sliding surface are formed parallel to each other.
  11. 　前記介在部材は、前記固定側カム部および前記可動側カム部よりも耐摩耗性が低い材料から形成されている、請求項１または２記載のプーリ装置。 The pulley device according to claim 1 or 2, wherein the intervening member is made of a material having lower wear resistance than the fixed cam part and the movable cam part.
  12. 　前記固定側カム部は、
    　　前記駆動源からの回転駆動力を受ける固定側当接面と、
    　　駆動輪側からのバックトルクを前記可動側カム部に与える固定側摺動面と、を有し、
    　前記介在部材が前記可動側カム部と前記固定側当接面とに挟まれた状態において、前記可動側カム部と前記固定側摺動面との間には隙間が形成されている、請求項１または２に記載のプーリ装置。     The fixed side cam part is
    a fixed side contact surface that receives rotational driving force from the drive source;
    a fixed side sliding surface that applies back torque from the driving wheel side to the movable side cam part,
    Claim: A gap is formed between the movable cam portion and the fixed sliding surface in a state where the intervening member is sandwiched between the movable cam portion and the fixed contact surface. 3. The pulley device according to 1 or 2.
  13. 　前記固定側スリーブと前記可動側スリーブとの間に配置され、かつ、前記可動側スリーブが摺動自在に嵌合する筒部材を有している、請求項１または２に記載のプーリ装置。 The pulley device according to claim 1 or 2, further comprising a cylindrical member disposed between the stationary sleeve and the movable sleeve, and into which the movable sleeve is slidably fitted.
  14. 　前記固定側カム部の一部は、前記貫通孔よりも前記可動側プーリ側に位置する、請求項１または２に記載のプーリ装置。 The pulley device according to claim 1 or 2, wherein a part of the fixed cam portion is located closer to the movable pulley than the through hole.
  15. 　前記固定側スリーブには、径方向の内側に向けて凹みかつ前記介在部材から離隔した逃げ溝が形成されている、請求項１または２に記載のプーリ装置。 The pulley device according to claim 1 or 2, wherein the stationary sleeve is formed with an escape groove that is recessed toward the inside in the radial direction and is spaced apart from the intervening member.
  16. 　前記固定側ドリブンプーリは、前記介在部材よりも前記径方向の外側に位置し、かつ、前記介在部材の前記径方向の外側への変形を抑制する抑制部材を備えている、請求項１に記載のプーリ装置。 The stationary side driven pulley is provided with a suppressing member located outside the intervening member in the radial direction and suppressing deformation of the intervening member outward in the radial direction. pulley device.
  17. 　前記抑制部材は、前記貫通孔の一部を区画する壁部である、請求項１６に記載のプーリ装置。 The pulley device according to claim 16, wherein the suppressing member is a wall portion that partitions a part of the through hole.
  18. 　前記固定側カム部は、前記介在部材が接触する固定側接触面を有し、
    　前記抑制部材は、前記固定側接触面に連続しかつ前記固定側接触面よりも前記径方向の外側に位置する、請求項１７に記載のプーリ装置。     The fixed side cam portion has a fixed side contact surface with which the intervening member comes into contact,
    The pulley device according to claim 17, wherein the suppressing member is continuous with the fixed side contact surface and is located on the outer side of the fixed side contact surface in the radial direction.
  19. 　前記固定側接触面は、
    　　前記介在部材よりも前記回転方向の下流側に位置し、かつ、前記介在部材に当接する固定側当接面と、
    　　前記介在部材よりも前記回転方向の上流側に位置し、かつ、前記可動側カム部が摺動する固定側摺動面と、を含み、
    　前記抑制部材は、前記固定側当接面に連続しかつ前記固定側当接面よりも前記径方向の外側に位置する、請求項１８に記載のプーリ装置。     The fixed side contact surface is
    a fixed side contact surface that is located downstream of the intervening member in the rotational direction and abuts the intervening member;
    a fixed-side sliding surface located upstream of the intervening member in the rotational direction and on which the movable-side cam portion slides;
    The pulley device according to claim 18, wherein the suppressing member is continuous with the fixed side abutting surface and located on the outer side of the fixed side abutting surface in the radial direction.
  20. 　前記固定側接触面は、
    　　前記介在部材よりも前記回転方向の下流側に位置し、かつ、前記介在部材に当接する固定側当接面と、
    　　前記介在部材よりも前記回転方向の上流側に位置し、かつ、前記可動側カム部が摺動する固定側摺動面と、を含み、
    　前記抑制部材は、前記固定側摺動面に連続しかつ前記固定側摺動面よりも前記径方向の外側に位置する、請求項１８に記載のプーリ装置。     The fixed side contact surface is
    a fixed side contact surface that is located downstream of the intervening member in the rotational direction and abuts the intervening member;
    a fixed-side sliding surface located upstream of the intervening member in the rotational direction and on which the movable-side cam portion slides;
    The pulley device according to claim 18, wherein the suppressing member is continuous with the fixed-side sliding surface and located outside the fixed-side sliding surface in the radial direction.
  21. 　前記可動側プーリが前記固定側プーリに対して離隔する方向を第１の方向、前記可動側プーリが前記固定側プーリに対して接近する方向を第２の方向としたとき、前記介在部材は、前記固定側プーリの前記第２の方向の面側から前記貫通孔に挿入されている、請求項１６または１７に記載のプーリ装置。 When the direction in which the movable pulley moves away from the fixed pulley is a first direction, and the direction in which the movable pulley approaches the fixed pulley is a second direction, the intervening member The pulley device according to claim 16 or 17, wherein the pulley device is inserted into the through hole from the surface side of the fixed pulley in the second direction.
  22. 　前記固定側ドリブンプーリは、前記介在部材よりも前記第１の方向側に位置し、かつ、前記介在部材の移動を規制する規制壁を備えている、請求項２１に記載のプーリ装置。 The pulley device according to claim 21, wherein the stationary driven pulley is located on the first direction side with respect to the intervening member and includes a regulating wall that restricts movement of the intervening member.
  23. 　前記固定側カム部は、前記介在部材が接触する固定側接触面を有し、
    　前記固定側接触面は、
    　　前記介在部材よりも前記回転方向の下流側に位置し、かつ、前記介在部材に当接する固定側当接面と、
    　　前記介在部材よりも前記回転方向の上流側に位置し、かつ、前記可動側カム部が摺動する固定側摺動面と、を含み、
    　前記規制壁は、前記固定側当接面に連続する、請求項２２に記載のプーリ装置。     The fixed side cam portion has a fixed side contact surface with which the intervening member comes into contact,
    The fixed side contact surface is
    a fixed side contact surface that is located downstream of the intervening member in the rotational direction and abuts the intervening member;
    a fixed-side sliding surface located upstream of the intervening member in the rotational direction and on which the movable-side cam portion slides;
    The pulley device according to claim 22, wherein the regulating wall is continuous with the fixed side contact surface.
  24. 　前記固定側カム部は、前記介在部材が接触する固定側接触面を有し、
    　前記固定側接触面は、
    　　前記介在部材よりも前記回転方向の下流側に位置し、かつ、前記介在部材に当接する第１固定側当接面と、
    　　前記介在部材よりも前記回転方向の上流側に位置し、かつ、前記介在部材に当接する第２固定側当接面と、を含み、
    　前記介在部材は、
    　　前記第１固定側当接面に当接する第１介在部材と、
    　　前記第２固定側当接面に当接する第２介在部材と、を備えている、請求項１６または１７に記載のプーリ装置。     The fixed side cam portion has a fixed side contact surface with which the intervening member comes into contact,
    The fixed side contact surface is
    a first fixed-side contact surface that is located downstream of the intervening member in the rotational direction and abuts the intervening member;
    a second fixed-side contact surface located upstream of the intervening member in the rotational direction and abutting the intervening member;
    The intervening member is
    a first intervening member that abuts the first fixed side contact surface;
    The pulley device according to claim 16 or 17, further comprising a second intervening member that abuts the second fixed side contact surface.
  25. 　前記介在部材は、前記第１介在部材の前記径方向の外側の部分と前記第２介在部材の前記径方向の外側の部分とを連結する連結部材を備えている、請求項２４に記載のプーリ装置。 The pulley according to claim 24, wherein the intervening member includes a connecting member that connects the radially outer portion of the first intervening member and the radially outer portion of the second intervening member. Device.
  26. 　前記固定側ドリブンプーリは、前記固定側プーリに形成され、かつ、前記連結部材の前記径方向の外側への変形を抑制する変形抑制壁を有し、
    　前記駆動源が停止した状態において、前記径方向に関して、前記連結部材と前記変形抑制壁との間には、隙間が形成されている、請求項２５に記載のプーリ装置。     The fixed side driven pulley has a deformation suppressing wall formed on the fixed side pulley and suppressing outward deformation of the connecting member in the radial direction,
    The pulley device according to claim 25, wherein a gap is formed between the connecting member and the deformation suppressing wall in the radial direction when the drive source is stopped.
  27. 　前記固定側ドリブンプーリおよび前記可動側ドリブンプーリが回転するとき、前記連結部材は、前記変形抑制壁と接触する、請求項２６に記載のプーリ装置。 The pulley device according to claim 26, wherein when the fixed side driven pulley and the movable side driven pulley rotate, the connecting member comes into contact with the deformation suppressing wall.
  28. 　前記固定側カム部は、前記介在部材が接触するらせん状に形成された固定側接触面を有し、
    　前記介在部材は、前記固定側接触面に対向して配置され、かつ、らせん状に形成された介在側接触面を有し、
    　前記固定側接触面と前記介在側接触面とは面接触するように構成されている、請求項１６または１７に記載のプーリ装置。     The fixed side cam portion has a fixed side contact surface formed in a spiral shape with which the intervening member contacts,
    The intervening member has an intervening contact surface disposed opposite to the fixed contact surface and formed in a spiral shape,
    The pulley device according to claim 16 or 17, wherein the fixed side contact surface and the intervening side contact surface are configured to make surface contact.
  29. 　前記固定側接触面と前記介在側接触面とを面接触させることによって、前記介在部材の前記固定側ドリブンプーリに対する前記径方向および前記回転方向の位置決めがされている、請求項２８に記載のプーリ装置。 The pulley according to claim 28, wherein the intervening member is positioned in the radial direction and the rotational direction with respect to the stationary driven pulley by bringing the stationary side contact surface and the intervening side contact surface into surface contact. Device.
  30. 　前記介在部材は、ポリアミド樹脂の吸水率よりも低い吸水率を有する材料から形成されている、請求項１６または１７に記載のプーリ装置。 The pulley device according to claim 16 or 17, wherein the intervening member is made of a material having a water absorption rate lower than that of polyamide resin.
PCT/JP2023/004616 2022-03-11 2023-02-10 Pulley device WO2023171241A1 (en)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0338447U (en) * 1989-08-24 1991-04-15
JPH09287640A (en) * 1996-04-23 1997-11-04 Honda Motor Co Ltd Torque cam mechanism for automatic v-belt transmission
US20040229724A1 (en) * 2003-05-15 2004-11-18 Kalies Ken Edward Driven pulley system for use in torque converter
JP2006064121A (en) * 2004-08-27 2006-03-09 Honda Motor Co Ltd Transmission with variable pulley
JP2006322593A (en) * 2005-05-20 2006-11-30 F C C:Kk Aluminum pulley and its manufacturing method
JP2010203484A (en) * 2009-02-28 2010-09-16 Honda Motor Co Ltd V-belt type continuously variable transmission
JP2021067281A (en) * 2019-10-17 2021-04-30 株式会社エフ・シー・シー Pulley device and centrifugal clutch

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0338447U (en) * 1989-08-24 1991-04-15
JPH09287640A (en) * 1996-04-23 1997-11-04 Honda Motor Co Ltd Torque cam mechanism for automatic v-belt transmission
US20040229724A1 (en) * 2003-05-15 2004-11-18 Kalies Ken Edward Driven pulley system for use in torque converter
JP2006064121A (en) * 2004-08-27 2006-03-09 Honda Motor Co Ltd Transmission with variable pulley
JP2006322593A (en) * 2005-05-20 2006-11-30 F C C:Kk Aluminum pulley and its manufacturing method
JP2010203484A (en) * 2009-02-28 2010-09-16 Honda Motor Co Ltd V-belt type continuously variable transmission
JP2021067281A (en) * 2019-10-17 2021-04-30 株式会社エフ・シー・シー Pulley device and centrifugal clutch

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