WO2024176698A1 - クラッチ装置 - Google Patents

クラッチ装置 Download PDF

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Publication number
WO2024176698A1
WO2024176698A1 PCT/JP2024/002005 JP2024002005W WO2024176698A1 WO 2024176698 A1 WO2024176698 A1 WO 2024176698A1 JP 2024002005 W JP2024002005 W JP 2024002005W WO 2024176698 A1 WO2024176698 A1 WO 2024176698A1
Authority
WO
WIPO (PCT)
Prior art keywords
output shaft
clutch
side rotating
center
rotating plate
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2024/002005
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
克 吉本
嘉彦 小澤
恒香 曾
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FCC Co Ltd
Original Assignee
FCC Co Ltd
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 FCC Co Ltd filed Critical FCC Co Ltd
Priority to EP24760005.9A priority Critical patent/EP4671559A1/en
Priority to CN202480006135.0A priority patent/CN120380261A/zh
Publication of WO2024176698A1 publication Critical patent/WO2024176698A1/ja
Priority to US19/254,357 priority patent/US20250327496A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/06—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like
    • F16D43/08—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces
    • F16D43/10—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces the centrifugal masses acting directly on the pressure ring, no other actuating mechanism for the pressure ring being provided
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/74—Features relating to lubrication
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
    • F16D2013/565—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only with means for releasing the clutch pressure in case of back torque
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2200/00—Materials; Production methods therefor
    • F16D2200/0004—Materials; Production methods therefor metallic
    • F16D2200/0026—Non-ferro
    • F16D2200/003—Light metals, e.g. aluminium
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/06—Lubrication details not provided for in group F16D13/74

Definitions

  • the present invention relates to a clutch device.
  • Patent Document 1 discloses a clutch device having an input member (hereinafter referred to as input shaft) connected to the engine side, an output member (hereinafter referred to as output shaft) connected to the driving wheel side, a clutch member (hereinafter referred to as clutch center) connected to the output shaft, and a pressure member (hereinafter referred to as pressure plate) that can approach or move away from the clutch center.
  • the clutch center is fixed to the output shaft in order to transmit the rotational driving force input from the input shaft to the output shaft.
  • the clutch center has an output shaft holding portion to which the output shaft is connected, and the output shaft holding portion is formed with an insertion hole into which the output shaft is inserted.
  • clutch oil flows inside the output shaft, and the clutch oil flows to the outside from a specified part of the output shaft.
  • components such as washers and auxiliary clutch plates can be placed on the end face of the output shaft holding portion of the clutch center opposite the side on which the pressure plate is placed. For this reason, this end face is often machined to be flat.
  • the flattened end face and components such as washers come into close contact with each other, there is a problem in that the clutch oil circulating inside the output shaft cannot be sufficiently supplied to components located radially outward from the output shaft holding portion.
  • the present invention was made in consideration of these points, and its purpose is to provide a clutch device that can supply clutch oil circulating inside the output shaft to a member located radially outward from the output shaft holding portion.
  • the clutch device is a clutch device that transmits or cuts off the rotational driving force of an input shaft to an output shaft, and includes a clutch center that is accommodated in a clutch housing that holds a plurality of input side rotating plates that are rotationally driven by the rotational drive of the input shaft, holds a plurality of output side rotating plates that are arranged alternately with the input side rotating plates, and is rotationally driven together with the output shaft, and a pressure plate that is arranged to be able to approach or move away from the clutch center and to rotate relatively thereto, and is able to press the input side rotating plates and the output side rotating plates, and the clutch center is
  • the clutch has an output shaft holding portion to which the output shaft is connected, and the output shaft holding portion has an insertion hole into which the output shaft is inserted.
  • an oil groove is formed on the end face of the output shaft holding portion in the first direction, the oil groove communicates with the insertion hole, extends in the radial direction of the output shaft and from the insertion hole to the radial outer edge of the end face in the first direction, and through which clutch oil flowing out from the output shaft flows.
  • the oil groove formed on the end face of the output shaft holding part in the first direction communicates with the insertion hole and extends in the radial direction of the output shaft and from the insertion hole to the radial outer edge of the end face in the first direction. Therefore, even if a member such as a washer is disposed on the end face in the first direction of the output shaft holding part, the clutch oil flowing out from the output shaft via the oil groove can be supplied to the outside (e.g., the input side rotating plate or the output side rotating plate) from the radial outer edge of the end face in the first direction of the output shaft holding part.
  • the outside e.g., the input side rotating plate or the output side rotating plate
  • the present invention provides a clutch device that can supply clutch oil circulating within the output shaft to a member located radially outward of the output shaft holding portion.
  • FIG. 1 is a cross-sectional view of a clutch device according to one embodiment.
  • FIG. 2 is an enlarged cross-sectional view of a portion of the clutch device according to the embodiment.
  • FIG. 3 is a perspective view of the first clutch center according to the embodiment.
  • FIG. 4 is a perspective view of the first clutch center according to one embodiment.
  • FIG. 5 is a plan view of the first clutch center according to one embodiment.
  • FIG. 6 is a bottom view of the first clutch center according to one embodiment.
  • FIG. 7 is a perspective view of the second clutch center according to one embodiment.
  • FIG. 8 is a plan view of the second clutch center according to one embodiment.
  • FIG. 9 is a perspective view of a pressure plate according to one embodiment.
  • FIG. 10 is a plan view of a pressure plate according to one embodiment.
  • FIG. 11 is a cross-sectional view of a centrifugal clutch mechanism according to one embodiment.
  • FIG. 12 is a partially cutaway perspective view of a centrifugal clutch mechanism according to one embodiment.
  • FIG. 13 is a perspective view of an auxiliary clutch plate according to one embodiment.
  • FIG. 14 is a perspective view of an auxiliary clutch plate according to one embodiment.
  • FIG. 15A is a schematic diagram for explaining the action of the center side assist cam surface and the pressure side assist cam surface.
  • FIG. 15B is a schematic diagram for explaining the action of the center-side slipper cam surface and the pressure-side slipper cam surface.
  • FIG. 1 is a cross-sectional view of a clutch device 10 according to this embodiment.
  • the clutch device 10 is provided, for example, on a saddle-type vehicle such as a motorcycle.
  • the clutch device 10 is, for example, a device that transmits or cuts off the rotational driving force of an input shaft (crankshaft) of an engine, which is the power source of the motorcycle, to an output shaft 15.
  • the clutch device 10 is a device that transmits or cuts off the rotational driving force of the input shaft to a driving wheel (rear wheel) via the output shaft 15.
  • the clutch device 10 is disposed between the engine and the transmission.
  • first direction D1 the direction in which the pressure plate 70 of the clutch device 10 approaches and moves away from the clutch center 40
  • second direction D2 the direction in which the pressure plate 70 approaches the clutch center 40
  • the circumferential direction of the clutch center 40 and the pressure plate 70 is referred to as circumferential direction S
  • first circumferential direction S1 the direction from one pressure side cam portion 90 to the other pressure side cam portion 90 in relation to the circumferential direction S
  • first circumferential direction S1 see FIG.
  • second circumferential direction S2 the direction from the other pressure side cam portion 90 to one pressure side cam portion 90 (the direction from the other center side cam portion 60 to one center side cam portion 60) is referred to as second circumferential direction S2 (see FIG. 3).
  • the axial direction of the output shaft 15 is the same as the direction D.
  • the pressure plate 70 and the clutch center 40 rotate in a first circumferential direction S1 (i.e., the direction from the center-side assist cam surface 60A of one center-side cam portion 60 toward the center-side slipper cam surface 60S).
  • first circumferential direction S1 i.e., the direction from the center-side assist cam surface 60A of one center-side cam portion 60 toward the center-side slipper cam surface 60S.
  • the above direction is merely determined for the convenience of explanation, and does not limit the installation mode of the clutch device 10 or the present invention in any way.
  • the clutch device 10 includes an output shaft 15, a plurality of input side rotating plates 20, a plurality of output side rotating plates 22, a clutch housing 30, a clutch center 40, a pressure plate 70, a stopper plate 100, a centrifugal clutch mechanism 120, and an auxiliary clutch plate 150.
  • the output shaft 15 is a hollow shaft body.
  • One end of the output shaft 15 rotatably supports an input gear 35 and a clutch housing 30 (described later) via a needle bearing 28A.
  • the output shaft 15 fixedly supports a clutch center 40 via a nut 28B.
  • the output shaft 15 rotates integrally with the clutch center 40.
  • the other end of the output shaft 15 is connected to, for example, a transmission (not shown) of a motorcycle.
  • the output shaft 15 has a main body 15A extending in direction D and a communication hole 15B formed in the main body 15A.
  • the main body 15A has an oil flow passage 15H through which clutch oil flows.
  • the oil flow passage 15H is formed between the main body 15A and a sleeve 16C that fits around the push rod 16A (described later).
  • the clutch oil flows through the output shaft 15, i.e., through the oil flow passage 15H of the main body 15A.
  • the communication hole 15B extends in the radial direction of the output shaft 15 (hereinafter referred to as the radial direction.
  • the radial direction is a direction perpendicular to direction D).
  • the communication hole 15B communicates with the oil flow passage 15H.
  • one or two communication holes 15B are formed in the main body 15A. As shown in FIG. 2, at least a portion of the communication hole 15B is located between the end face 42D1 in the first direction D1 of the output shaft holding portion 42 (described later) and the end face 47D1 in the first direction D1 of the mating teeth 47 (described later) in relation to the axial direction of the output shaft 15 (i.e., direction D).
  • the oil flow passage 15H of the output shaft 15 is provided with a push rod 16A and a push member 16B adjacent to the push rod 16A.
  • the push rod 16A and the push member 16B are provided so as to be slidable within a sleeve 16C.
  • One end (the end on the left side in the figure) of the push rod 16A is connected to a clutch operating lever (not shown) of the motorcycle, and the push rod 16A slides within the sleeve 16C and presses the push member 16B in the second direction D2 by operating the clutch operating lever.
  • a part of the push member 16B protrudes outward from the output shaft 15 (in this case, the second direction D2) and is connected to a release bearing 18 provided on the pressure plate 70.
  • the sleeve 16C and the push member 16B are formed to be narrower than the inner diameter of the main body 15A, ensuring the flow of clutch oil within the oil flow passage 15H.
  • the clutch housing 30 is made of an aluminum alloy.
  • the clutch housing 30 is formed in a cylindrical shape with a bottom. As shown in FIG. 1, the clutch housing 30 has a bottom wall 31 formed in a substantially circular shape, and a side wall 33 extending from an edge of the bottom wall 31 in the second direction D2.
  • the clutch housing 30 holds a plurality of input side rotating plates 20.
  • an input gear 35 is provided on the bottom wall 31 of the clutch housing 30.
  • the input gear 35 is fixed to the bottom wall 31 by rivets 35B via a torque damper 35A.
  • the input gear 35 meshes with a drive gear (not shown) that rotates due to the rotational drive of the input shaft of the engine.
  • the input gear 35 rotates integrally with the clutch housing 30, independent of the output shaft 15.
  • the input side rotating plate 20 is rotated by the rotational drive of the input shaft. As shown in FIG. 1, the input side rotating plate 20 is held on the inner peripheral surface of the side wall 33 of the clutch housing 30. The input side rotating plate 20 is held in the clutch housing 30 by spline fitting. The input side rotating plate 20 is provided so that it can be displaced along the axial direction of the clutch housing 30 (i.e., direction D). The input side rotating plate 20 is provided so that it can rotate integrally with the clutch housing 30.
  • the input side rotating plate 20 is a member that is pressed against the output side rotating plate 22.
  • the input side rotating plate 20 is a flat plate formed into an annular shape.
  • the input side rotating plate 20 is formed by casting an aluminum alloy. Friction material (not shown) made of multiple pieces of paper is attached to the front and back surfaces of the input side rotating plate 20. Grooves several ⁇ m to several tens of ⁇ m deep are formed between the friction materials to hold clutch oil.
  • the clutch center 40 is accommodated in the clutch housing 30.
  • the clutch center 40 is arranged concentrically with the clutch housing 30.
  • the clutch center 40 holds the input side rotating plate 20 and a plurality of output side rotating plates 22 arranged alternately in the direction D.
  • the clutch center 40 is driven to rotate together with the output shaft 15.
  • the clutch center 40 includes a first clutch center 41 and a second clutch center 51.
  • the first clutch center 41 and the second clutch center 51 are assembled to each other.
  • the second clutch center 51 is located radially outside the first clutch center 41.
  • the second clutch center 51 fits around the first clutch center 41.
  • the first clutch center 41 includes an output shaft holding portion 42, an annular base wall 43 located radially outside the output shaft holding portion 42, and a plurality of center side cam portions 60.
  • the output shaft 15 is connected to the output shaft holding portion 42.
  • the output shaft holding portion 42 is formed in a cylindrical shape.
  • the output shaft holding portion 42 has an insertion hole 45 into which the output shaft 15 is inserted and spline-fitted.
  • the insertion hole 45 is formed penetrating the output shaft holding portion 42.
  • a plurality of mating teeth 47 extending in the axial direction of the output shaft 15 (i.e., direction D) are formed on an inner wall 45A of the output shaft holding portion 42 that defines the insertion hole 45. The mating teeth 47 are mated with the output shaft 15.
  • an oil groove 42P through which clutch oil flows is formed on the end face 42D1 of the output shaft holding portion 42 in the first direction D1.
  • the oil groove 42P extends in the radial direction of the output shaft 15.
  • the oil groove 42P communicates with the insertion hole 45.
  • the oil groove 42P extends from the insertion hole 45 to the radial outer edge 42DO of the end face 42D1 in the first direction D1.
  • the oil groove 42P is recessed from the end face 42D1 in the second direction D2.
  • two oil grooves 42P are formed on the end face 42D1, but the number of oil grooves 42P is not limited to two.
  • the two oil grooves 42P are provided in positions facing each other. As shown in FIG. 2, the oil groove 42P is located radially outside the communication hole 15B of the output shaft 15.
  • At least a portion of the end face 42D1 in the first direction D1 of the output shaft holding portion 42 is located closer to the first direction D1 than the end face 47D1 in the first direction D1 of the mating tooth 47.
  • the entire end face 42D1 is located closer to the first direction D1 than the end face 47D1.
  • a step portion 48 is formed between the end face 42D1 in the first direction D1 of the output shaft holding portion 42 and the end face 47D1 in the first direction D1 of the mating tooth 47.
  • the step portion 48 is formed around the entire circumference of the output shaft holding portion 42 (around the entire circumference of the insertion hole 45). Clutch oil is temporarily held in the step portion 48. As shown in FIG.
  • the diameter R1 of the portion of the insertion hole 45 defined by the inner edge 42I of the end face 42D1 of the output shaft holding portion 42 in the first direction D1 is larger than the diameter R2 of the portion of the insertion hole 45 defined by the radially inner edge 47I of the mating teeth 47 (a virtual circle passing through the edge 47I).
  • the center cam portion 60 is formed in a platform shape having a cam surface made of an inclined surface constituting an Assist & Slipper (registered trademark) mechanism that generates an assist torque, which is a force that increases the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22, or a slipper torque, which is a force that reduces the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22 and transitions to a half-clutch state.
  • the center cam portion 60 is formed so as to protrude in the second direction D2 from the surface 43D2 on the second direction D2 side of the base wall 43.
  • the center cam portions 60 are arranged at equal intervals in the circumferential direction S of the first clutch center 41.
  • the first clutch center 41 has three center cam portions 60, but the number of center cam portions 60 is not limited to three.
  • the center side cam portion 60 is located radially outside the output shaft holding portion 42.
  • the center side cam portion 60 has a center side assist cam surface 60A (see also FIG. 6) and a center side slipper cam surface 60S.
  • the center side assist cam surface 60A is configured to generate a force in a direction that moves the pressure plate 70 closer to the clutch center 40 when rotating relative to the pressure plate 70 in order to increase the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22.
  • the position of the pressure plate 70 relative to the clutch center 40 does not change, and the pressure plate 70 does not need to physically approach the clutch center 40.
  • the pressure plate 70 may be physically displaced relative to the clutch center 40.
  • the center-side slipper cam surface 60S is configured to move the pressure plate 70 away from the clutch center 40 in order to reduce the pressing force (pressure contact force) between the input-side rotating plate 20 and the output-side rotating plate 22 when rotating relative to the pressure plate 70.
  • the center-side assist cam surface 60A of one center-side cam portion 60L and the center-side slipper cam surface 60S of the other center-side cam portion 60M are arranged opposite each other in the circumferential direction S.
  • the first clutch center 41 has a plurality of boss portions 62 (three in this embodiment).
  • the boss portions 62 are members for fixing the pressure plate 70.
  • the plurality of boss portions 62 are arranged at equal intervals in the circumferential direction S.
  • the boss portions 62 are formed in a cylindrical shape.
  • the boss portions 62 are located radially outward from the output shaft holding portion 42.
  • the boss portions 62 extend toward the pressure plate 70 (i.e., toward the second direction D2).
  • the boss portions 62 are provided on the center side cam portion 60.
  • the boss portions 62 are provided between the center side assist cam surface 60A and the center side slipper cam surface 60S in the circumferential direction S.
  • the boss portions 62 have a screw hole 62H formed therein, into which the bolt 28 (see FIG. 1) is inserted.
  • the screw hole 62H extends in the axial direction of the clutch center 40 (i.e., in the direction D).
  • the first clutch center 41 has a center-side cam hole 43H that penetrates a portion of the base wall 43.
  • the center-side cam hole 43H penetrates the base wall 43 in direction D.
  • the center-side cam hole 43H is located between adjacent center-side cam portions 60 in the circumferential direction S.
  • FIG. 6 when viewed from the axial direction of the clutch center 40, the center-side assist cam surface 60A and a portion of the center-side cam hole 43H overlap.
  • the first clutch center 41 has a plurality of engagement grooves 49.
  • the engagement grooves 49 are formed on the outer peripheral surface of the base wall 43.
  • the engagement grooves 49 are recessed radially inward from the outer peripheral surface of the base wall 43.
  • the second clutch center 51 has an annular outer peripheral wall 52, a flange 68 extending radially outward from the outer peripheral wall 52, and a center-side fitting portion 54.
  • the second clutch center 51 holds an input side rotating plate 20 and a plurality of output side rotating plates 22 arranged alternately in direction D.
  • a splined engagement portion 56 is provided on the outer peripheral surface of the outer peripheral wall 52.
  • the splined engagement portion 56 has a plurality of center side engagement teeth 57 extending in the axial direction of the second clutch center 51 (i.e., direction D) along the outer peripheral surface of the outer peripheral wall 52, a plurality of spline grooves 58 formed between adjacent center side engagement teeth 57 and extending in the axial direction of the second clutch center 51 (i.e., direction D), and an oil discharge hole 59.
  • the center side engagement teeth 57 hold the output side rotating plate 22.
  • the center side engagement teeth 57 are aligned in the circumferential direction S.
  • the center side engagement teeth 57 are formed at equal intervals in the circumferential direction S.
  • the center side engagement teeth 57 are formed in the same shape.
  • the center side engagement teeth 57 protrude radially outward from the outer peripheral surface of the outer peripheral wall 52.
  • the oil discharge hole 59 is formed penetrating the outer peripheral wall 52 in the radial direction.
  • the oil discharge hole 59 is formed between adjacent center side mating teeth 57. That is, the oil discharge hole 59 is formed in the spline groove 58.
  • the oil discharge hole 59 is formed in the center side mating portion 54.
  • the oil discharge hole 59 connects the inside and outside of the second clutch center 51.
  • the oil discharge hole 59 is a hole that discharges clutch oil and the like that has flowed out from the output shaft 15 into the clutch center 40 to the outside of the clutch center 40.
  • the clutch oil discharged from the oil discharge hole 59 is supplied to the input side rotating plate 20 and the output side rotating plate 22 that are located radially outside the oil discharge hole 59.
  • the output side rotating plate 22 is held by the splined engagement portion 56 of the second clutch center 51 and the pressure plate 70. A part of the output side rotating plate 22 is held by the center side engagement teeth 57 and the spline grooves 58 of the second clutch center 51 through spline engagement. Another part of the output side rotating plate 22 is held by the pressure side engagement teeth 77 (see FIG. 9) of the pressure plate 70, which will be described later.
  • the output side rotating plate 22 is provided so as to be displaceable along the axial direction of the clutch center 40 (i.e., direction D).
  • the output side rotating plate 22 is provided so as to be rotatable integrally with the clutch center 40.
  • the output side rotating plate 22 is a member that is pressed against the input side rotating plate 20.
  • the output side rotating plate 22 is a flat plate formed in an annular shape.
  • the output side rotating plate 22 is formed by casting an aluminum alloy.
  • the friction material provided on the input side rotating plate 20 may be provided on the output side rotating plate 22 instead of the input side rotating plate 20, or may be provided on both the input side rotating plate 20 and the output side rotating plate 22.
  • the center side fitting portion 54 is formed on the inner peripheral surface of the outer peripheral wall 52.
  • the center side fitting portion 54 is configured to be slidably fitted onto the pressure side fitting portion 88 (see FIG. 9), which will be described later.
  • the inner diameter of the center side fitting portion 54 is formed with a fitting tolerance that allows the flow of clutch oil flowing out from the tip end 15T (see FIG. 1) of the output shaft 15 relative to the pressure side fitting portion 88. In other words, a gap is formed between the center side fitting portion 54 and the pressure side fitting portion 88.
  • the second clutch center 51 has multiple engagement protrusions 55.
  • the engagement protrusions 55 engage with the engagement grooves 49 (see Figure 3) of the first clutch center 41.
  • the engagement protrusions 55 are formed on the inner circumferential surface of the outer circumferential wall 52.
  • the engagement protrusions 55 protrude radially inward from the inner circumferential surface of the outer circumferential wall 52.
  • the engagement protrusions 55 are located on the first direction D1 side of the oil discharge hole 59.
  • the pressure plate 70 is provided so as to be able to approach or separate from the clutch center 40 and to rotate relative to it.
  • the pressure plate 70 is configured so as to be able to press the input side rotating plate 20 and the output side rotating plate 22.
  • the pressure plate 70 is arranged concentrically with the clutch center 40 and the clutch housing 30.
  • the pressure plate 70 has a main body 72 and a flange 98 that is connected to the outer periphery of the main body 72 on the second direction D2 side and extends radially outward.
  • the main body 72 protrudes in the first direction D1 beyond the flange 98.
  • the flange 98 is located radially outward beyond the cylindrical portion 80 described later.
  • the pressure plate 70 holds a plurality of output side rotating plates 22 arranged alternately with the input side rotating plates 20.
  • the flange 98 is configured so as to be able to press the input side rotating plate 20 and the output side rotating plate 22.
  • the main body 72 includes a cylindrical portion 80, a plurality of pressure side cam portions 90, a pressure side fitting portion 88, and a spring accommodating portion 84 (see FIG. 1).
  • the tubular portion 80 is formed in a cylindrical shape.
  • the tubular portion 80 is formed integrally with the pressure side cam portion 90.
  • the tubular portion 80 accommodates the tip portion 15T (see FIG. 1) of the output shaft 15.
  • the tubular portion 80 accommodates the release bearing 18 (see FIG. 1).
  • the tubular portion 80 is a portion that receives a pressing force from the push member 16B (see FIG. 1) via the release bearing 18.
  • the tubular portion 80 is a portion that receives the clutch oil that flows out from the tip portion 15T of the output shaft 15.
  • the pressure side cam portion 90 is formed in a platform shape having a cam surface made of an inclined surface that constitutes an Assist & Slipper (registered trademark) mechanism that slides against the center side cam portion 60 to generate an assist torque or a slipper torque. As shown in FIG. 9, the pressure side cam portion 90 is formed so as to protrude in the first direction D1 beyond the flange 98. As shown in FIG. 10, the pressure side cam portions 90 are disposed at equal intervals in the circumferential direction S of the pressure plate 70. In this embodiment, the pressure plate 70 has three pressure side cam portions 90, but the number of pressure side cam portions 90 is not limited to three.
  • the pressure side cam portion 90 is located radially outside the cylindrical portion 80.
  • the pressure side cam portion 90 has a pressure side assist cam surface 90A (see also FIG. 9) and a pressure side slipper cam surface 90S.
  • the pressure side assist cam surface 90A is configured to be able to come into contact with the center side assist cam surface 60A.
  • the pressure side assist cam surface 90A is configured to generate a force in a direction that brings the pressure plate 70 closer to the clutch center 40 in order to increase the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22 when rotating relative to the clutch center 40.
  • the pressure side slipper cam surface 90S is configured to be able to come into contact with the center side slipper cam surface 60S.
  • the pressure side slipper cam surface 90S is configured to move the pressure plate 70 away from the clutch center 40 in order to reduce the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22 when rotating relative to the clutch center 40.
  • the pressure side assist cam surface 90A of one pressure side cam portion 90L and the pressure side slipper cam surface 90S of the other pressure side cam portion 90M are arranged opposite each other in the circumferential direction S.
  • the pressure side fitting portion 88 is located radially outward from the pressure side cam portion 90.
  • the pressure side fitting portion 88 is located on the second direction D2 side from the pressure side cam portion 90.
  • the pressure side fitting portion 88 is configured to be slidably fitted into the center side fitting portion 54 (see FIG. 7).
  • the pressure plate 70 has a pressure side cam hole 73H that penetrates the main body 72 and a part of the flange 98.
  • the pressure side cam hole 73H is located radially outward from the cylindrical portion 80.
  • the pressure side cam hole 73H extends from the side of the cylindrical portion 80 to a position radially outward from the pressure side fitting portion 88.
  • the pressure side cam hole 73H is formed between the pressure side assist cam surface 90A and the pressure side slipper cam surface 90S of the adjacent pressure side cam portion 90.
  • FIG. 10 when viewed from the axial direction of the pressure plate 70, the pressure side assist cam surface 90A and a part of the pressure side cam hole 73H overlap.
  • the boss portion 62 (see FIG. 3) of the first clutch center 41 is inserted into the pressure side cam hole 73H.
  • the pressure plate 70 has a plurality of pressure side mating teeth 77 arranged on a flange 98.
  • the pressure side mating teeth 77 hold the output side rotating plate 22.
  • the pressure side mating teeth 77 protrude from the flange 98 in a first direction D1.
  • the pressure side mating teeth 77 are located radially outward from the cylindrical portion 80.
  • the pressure side mating teeth 77 are located radially outward from the pressure side cam portion 90.
  • the pressure side mating teeth 77 are located radially outward from the pressure side mating portion 88.
  • the multiple pressure side mating teeth 77 are aligned in the circumferential direction S.
  • the multiple pressure side mating teeth 77 are arranged at equal intervals in the circumferential direction S. In this embodiment, some of the pressure side mating teeth 77 have been removed, so the spacing between those teeth is wider, but the other adjacent pressure side mating teeth 77 are spaced equally apart.
  • the spring accommodating portion 84 is formed in the pressure side cam portion 90.
  • the spring accommodating portion 84 is formed so as to be recessed from the second direction D2 to the first direction D1 (see also FIG. 15A).
  • the spring accommodating portion 84 is formed in a circular shape.
  • the spring accommodating portion 84 accommodates the pressure spring 25.
  • the pressure spring 25 is housed in the spring housing 84.
  • the pressure spring 25 biases the pressure plate 70 toward the clutch center 40 (i.e., toward the first direction D1).
  • the pressure spring 25 is, for example, a coil spring made of spring steel wound in a spiral shape.
  • the centrifugal clutch mechanism 120 is provided in the clutch housing 30.
  • the centrifugal clutch mechanism 120 is provided on the first direction D1 side of the clutch center 40.
  • the centrifugal clutch mechanism 120 is located radially outside the oil groove 42P.
  • the centrifugal clutch mechanism 120 is located on the extension line 42PL (see also FIG. 2) of the oil groove 42P.
  • the centrifugal clutch mechanism 120 is held in the clutch housing 30.
  • the centrifugal clutch mechanism 120 is provided so as to be rotatable integrally with the clutch housing 30. As shown in FIG. 11 and FIG.
  • the centrifugal clutch mechanism 120 has a weight member 122, a holding member 124, a pressure contact member 126, a support member 128, a first spherical member 131, a second spherical member 132, and a biasing member 135 (see FIG. 1).
  • the centrifugal clutch mechanism 120 presses the input side rotating plate 20 and the output side rotating plate 22 together to enable the rotational driving force of the input shaft to be transmitted to the output shaft 15.
  • the centrifugal clutch mechanism 120 When the weight member 122 is in a radially inner position, the centrifugal clutch mechanism 120 releases the pressing force between the input side rotating plate 20 and the output side rotating plate 22 to enable the rotational driving force of the input shaft to be blocked from being transmitted to the output shaft 15.
  • the centrifugal clutch mechanism 120 is configured to be able to press a disk portion 154 (see FIG. 13) of the auxiliary clutch plate 150 (see FIG. 13), which will be described later.
  • the weight member 122 is configured to be movable from a radially inner position to an outer position by the centrifugal force that accompanies the rotation of the clutch housing 30. As shown in FIG. 11, the weight member 122 is accommodated in a accommodating portion 124A (described later) of the holding member 124. The weight member 122 is held in a radially inner position when no centrifugal force is applied. When centrifugal force is applied, the weight member 122 moves radially outward against the biasing force of the biasing member 135 (see FIG. 1) and moves to the radially outer position.
  • the holding member 124 holds the weight member 122 movably between a radially inner position and a radially outer position.
  • the holding member 124 is formed in an annular shape.
  • the holding member 124 has a plurality of accommodating portions 124A formed in the circumferential direction, a sloped groove 124B formed in the accommodating portion 124A, and a pressing surface 124C.
  • the accommodating portion 124A accommodates the weight member 122.
  • the accommodating portion 124A is formed in a concave shape that matches the shape and range of movement of the weight member 122.
  • One end of the biasing member 135 (see FIG. 1) is configured to be able to abut against the outer peripheral wall surface 124AA of the accommodating portion 124A.
  • the pressure contact member 126 is configured to be able to move in the second direction D2 by the weight member 122 moving from a radially inner position to an outer position, thereby pressing the input side rotating plate 20 and the output side rotating plate 22.
  • the pressure contact member 126 is formed in an annular shape.
  • the pressure contact member 126 has a plurality of gradient grooves 126A formed around the circumference, grooves 126B formed at the positions where the gradient grooves 126A are formed, and a pressing surface 126C.
  • the gradient grooves 126A are formed at positions corresponding to the weight members 122.
  • the gradient grooves 126A are inclined so as to face the first direction D1 from the radially inner side toward the radially outer side.
  • the weight member 122 When the clutch housing 30 is stopped, the weight member 122 is held radially inward by the biasing force of the biasing member 135 (see FIG. 1).
  • the clutch housing 30 rotates and centrifugal force is applied to the weight member 122, the weight member 122 moves along the gradient groove 126A, and the pressing member 126 moves in a direction away from the holding member 124 (i.e., in the second direction D2).
  • the pressing surface 126C of the pressing member 126 presses the flange 68 (see FIG. 1) of the second clutch center 51 in the second direction D2.
  • the holding member 124 and the pressing member 126 have a plurality of protrusions 127 formed in the circumferential direction.
  • the holding member 124 and the pressing member 126 are held by the inner peripheral surface of the side wall 33 of the clutch housing 30 via the protrusions 127, similar to the input side rotating plate 20.
  • the holding member 124 and the pressing member 126 are held by fitting into the clutch housing 30.
  • the holding member 124 and the pressure contact member 126 are provided so as to be displaceable along the axial direction of the clutch housing 30 (i.e., direction D).
  • the holding member 124 and the pressure contact member 126 are provided so as to be rotatable integrally with the clutch housing 30.
  • the support member 128 is attached to the holding member 124.
  • the support member 128 is fixed to the surface of the holding member 124 facing the second direction D2.
  • the support member 128 holds the weight member 122 so that it can move in the radial direction.
  • a friction material 175 is provided between the support member 128 and the clutch center 40 (here, the first clutch center 41).
  • the friction material 175 is an example of another friction material.
  • the first spherical member 131 is attached to the weight member 122.
  • the first spherical member 131 is, for example, a steel ball.
  • a portion of the first spherical member 131 protrudes from one opening of a through hole formed in the weight member 122 and contacts the gradient groove 126A of the pressure contact member 126.
  • the second spherical member 132 is attached to the weight member 122.
  • the second spherical member 132 is, for example, a steel ball.
  • a portion of the second spherical member 132 protrudes from the other opening of a through hole formed in the weight member 122 and contacts the gradient groove 124B of the holding member 124.
  • the biasing member 135 is disposed radially outward of the weight member 122.
  • the biasing member 135 biases the weight member 122 radially inward.
  • the biasing member 135 is, for example, a coil spring.
  • the auxiliary clutch plate 150 is provided in the clutch housing 30.
  • the auxiliary clutch plate 150 is fixed to the output shaft 15.
  • the auxiliary clutch plate 150 is disposed on the first direction D1 side of a portion of the centrifugal clutch mechanism 120.
  • the auxiliary clutch plate 150 is adjacent to the end surface 42D1 in the first direction D1 of the output shaft holding portion 42 of the first clutch center 41. At least a portion of the auxiliary clutch plate 150 and at least a portion of the end surface 42D1 in the first direction D1 of the output shaft holding portion 42 are in surface contact.
  • a member such as a washer may be provided between the auxiliary clutch plate 150 and the end surface 42D1.
  • the auxiliary clutch plate 150 is configured to be pressed by the centrifugal clutch mechanism 120 (here, the pressing surface 124C of the holding member 124) when the input side rotating plate 20 and the output side rotating plate 22 are pressed together (i.e., when the weight member 122 of the centrifugal clutch mechanism 120 is located at the radially outer position) to enable the rotational driving force of the input shaft to be transmitted to the output shaft 15.
  • the auxiliary clutch plate 150 is configured to be released from the pressure of the centrifugal clutch mechanism 120 (here, the pressing surface 124C of the holding member 124) when the pressing force between the input side rotating plate 20 and the output side rotating plate 22 is released (i.e., when the weight member 122 is located at the radially inner position) to interrupt the transmission of the rotational driving force of the input shaft to the output shaft 15.
  • the auxiliary clutch plate 150 has an engagement portion 152 and a disk portion 154.
  • the fitting portion 152 and the disk portion 154 are formed integrally.
  • the fitting portion 152 fits onto the output shaft 15.
  • the fitting portion 152 is formed with an insertion hole 152H (see also FIG. 13) into which the output shaft 15 is inserted and spline-fitted.
  • the insertion hole 152H is formed penetrating the fitting portion 152.
  • the length L1 of the fitting portion 152 in direction D i.e., the axial direction of the output shaft 15
  • the disk portion 154 is located radially outward from the fitting portion 152.
  • the disk portion 154 is an end face on the second direction D2 side, and has an abutment surface 154F that is pressed against the centrifugal clutch mechanism 120.
  • the abutment surface 154F is pressed against the pressing surface 124C of the retaining member 124 of the centrifugal clutch mechanism 120.
  • a friction material 170 (see also FIG. 14) is provided between the abutment surface 154F and the centrifugal clutch mechanism 120. That is, the abutment surface 154F is indirectly pressed against the pressing surface 124C via the friction material 170.
  • the disk portion 154 is located on the second direction D2 side from the center 152C of the fitting portion 152 in the direction D.
  • the stopper plate 100 is provided so as to be able to come into contact with the pressure plate 70.
  • the stopper plate 100 is a member that prevents the pressure plate 70 from moving away from the clutch center 40 in the second direction D2 by more than a predetermined distance.
  • the stopper plate 100 is fixed to the boss portion 62 of the first clutch center 41 by the bolt 28.
  • the pressure plate 70 is attached by tightening the bolt 28 to the boss portion 62 via the stopper plate 100 with the pressure spring 25 disposed in the spring accommodating portion 84.
  • the stopper plate 100 is formed in a substantially triangular shape in a plan view.
  • a predetermined amount of clutch oil is supplied into the clutch device 10.
  • the clutch oil absorbs heat and prevents wear of the friction material.
  • the clutch device 10 of this embodiment is a so-called wet-type multi-plate friction clutch device.
  • the clutch oil flows through the oil flow path 15H of the output shaft 15 into the clutch center 40 and the pressure plate 70, and is supplied to the input side rotating plate 20 and the output side rotating plate 22.
  • the clutch oil flowing through the oil flow path 15H also flows toward the oil groove 42P through the communication hole 15B, as shown by the arrow FL in FIG. 2.
  • a step portion 48 (see also FIG. 4) is formed around the entire circumference of the output shaft holding portion 42 at the end of the output shaft holding portion 42 on the first direction D1 side.
  • the clutch oil flows more reliably through the step portion 48 into the oil groove 42P.
  • the end face 42D1 of the output shaft holding portion 42 in the first direction D1 and the auxiliary clutch plate 150 are in surface contact, but since the end face 42D1 has an oil groove 42P formed therein, the clutch oil flowing out of the communication hole 15B flows to the radial outside of the first clutch center 41 through the oil groove 42P.
  • the clutch oil flowing to the radial outside of the first clutch center 41 is supplied to, for example, the friction material 170 provided between the contact surface 154F of the auxiliary clutch plate 150 and the centrifugal clutch mechanism 120, the friction material 175 provided between the support member 128 and the first clutch center 41, the weight member 122 of the centrifugal clutch mechanism 120, the input side rotating plate 20, and the output side rotating plate 22.
  • the oil groove 42P formed on the end face 42D1 of the output shaft holding portion 42 in the first direction D1 communicates with the insertion hole 45 and extends in the radial direction of the output shaft 15 from the insertion hole 45 to the radial outer edge 42DO of the end face 42D1 in the first direction D1.
  • the clutch oil flowing out of the output shaft 15 via the oil groove 42P can be supplied to the outside (e.g., the input side rotating plate 20 or the output side rotating plate 22) from the radial outer edge 42DO of the end face 42D1 in the first direction D1 of the output shaft holding portion 42.
  • the clutch device 10 of this embodiment has a weight member 122 that is configured to be movable from a radially inner position to an outer position by the centrifugal force accompanying the rotation of the clutch housing 30, and is equipped with a centrifugal clutch mechanism 120 that presses the input side rotating plate 20 and the output side rotating plate 22 together when the weight member 122 is in the outer position, making it possible to transmit the rotational driving force of the input shaft to the output shaft 15, and that releases the pressing force between the input side rotating plate 20 and the output side rotating plate 22 when the weight member 122 is in the inner position, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15.
  • the centrifugal clutch mechanism 120 is located radially outside the oil groove 42P and on the extension line 42PL of the oil groove 42P. According to the above aspect, the centrifugal clutch mechanism 120 can be supplied with clutch oil that flows out from the output shaft 15 via the oil groove 42P.
  • the clutch device 10 of this embodiment is equipped with an auxiliary clutch plate 150 which is configured to be pressed by the centrifugal clutch mechanism 120 when the input side rotating plate 20 and the output side rotating plate 22 are pressed together, thereby enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15, and which is released from the pressure by the centrifugal clutch mechanism 120 when the pressing force between the input side rotating plate 20 and the output side rotating plate 22 is released, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15.
  • the auxiliary clutch plate 150 is fixed to the output shaft 15 and is adjacent to the end face 42D1 in the first direction D1 of the output shaft holding portion 42, and at least a portion of the auxiliary clutch plate 150 is in surface contact with at least a portion of the end face 42D1 in the first direction D1 of the output shaft holding portion 42.
  • the auxiliary clutch plate 150 is adjacent to the end face 42D1 of the output shaft holding part 42 in the first direction D1, and at least a part of the auxiliary clutch plate 150 is in surface contact with at least a part of the end face 42D1 of the output shaft holding part 42 in the first direction D1, but the clutch oil that flows out of the output shaft 15 through the oil groove 42P can be supplied to the outside from the radial outer edge of the end face 42D1 of the output shaft holding part 42 in the first direction D1.
  • the auxiliary clutch plate 150 has an engagement portion 152 that engages with the output shaft 15, and a disk portion 154 that is located radially outward of the engagement portion 152, and the length L1 in the direction D1 of the engagement portion 152 is longer than the length L2 in the direction D1 of the disk portion 154. According to the above aspect, the auxiliary clutch plate 150 is reliably engaged with the output shaft 15, and the auxiliary clutch plate 150 can be arranged compactly.
  • the centrifugal clutch mechanism 120 is configured to be able to press the disk portion 154, and the disk portion 154 is located on the second direction D2 side of the axial center 152C of the fitting portion 152. According to the above aspect, the centrifugal clutch mechanism 120 can be made smaller.
  • the disk portion 154 is an end face on the second direction D2 side and has an abutment surface 154F that is pressed against the centrifugal clutch mechanism 120.
  • the centrifugal clutch mechanism 120 can press the entire auxiliary clutch plate 150 by pressing the abutment surface 154F.
  • the clutch device 10 of this embodiment includes a friction material 170 provided between the contact surface 154F and the centrifugal clutch mechanism 120. According to the above aspect, the rotational driving force is reliably transmitted by the friction material 170 to the auxiliary clutch plate 150 via the centrifugal clutch mechanism 120. In addition, since the friction material 170 can be supplied with clutch oil flowing out from the output shaft 15, wear of the friction material 170 can be suppressed.
  • the inner wall 45A of the output shaft holding portion 42 that defines the insertion hole 45 is formed with a plurality of mating teeth 47 that extend in the axial direction of the output shaft 15 and mating with the output shaft 15, and at least a portion of the end face 42D1 in the first direction D1 of the output shaft holding portion 42 is located closer to the first direction D1 than the end face 47D1 in the first direction D1 of the mating teeth 47, and a step portion 48 is formed between the end face 42D1 in the first direction D1 of the output shaft holding portion 42 and the end face 47D1 in the first direction D1 of the mating teeth 47.
  • the clutch oil that flows out of the output shaft 15 is once held in the step portion 48 before flowing into the oil groove 42P, so that more clutch oil can flow from the oil groove 42P to the outside.
  • the step portion 48 is formed around the entire circumference of the output shaft holding portion 42. According to the above aspect, even if the circumferential position (phase) of the communication hole 15B of the output shaft 15 and the oil groove 42P are misaligned, the clutch oil flowing through the oil flow path 15H of the output shaft 15 can be reliably supplied to the oil groove 42P.
  • the centrifugal clutch mechanism 120 has a support member 128 that holds the weight member 122 so that it can move radially, and is equipped with a friction material 175 provided between the support member 128 and the clutch center 40. According to the above aspect, it is possible to supply clutch oil to the friction material 175, and seizure of the friction material 175 can be suppressed.
  • the auxiliary clutch plate 150 is fixed to the output shaft 15 and is adjacent to the end face 42D1 in the first direction D1 of the output shaft holding part 42. According to the above aspect, the auxiliary clutch plate 150 is adjacent to the end face 42D1 in the first direction D1 of the output shaft holding part 42, and the clutch oil flowing out from the output shaft 15 via the oil groove 42P can be supplied to the outside from the radial outer edge 42DO of the end face 42D1 in the first direction D1 of the output shaft holding part 42.
  • the entire end face 42D1 in the first direction D1 of the output shaft holding portion 42 is located on the first direction side D1 of the end face 47D1 in the first direction D1 of the mating tooth 47.
  • the step portion 48 is formed around the entire circumference of the insertion hole 45, so that a larger amount of clutch oil can be held in the step portion 48.
  • the diameter R1 of the portion of the insertion hole 45 defined by the inner edge 42I of the end face 42D1 of the output shaft holding portion 42 in the first direction D1 is larger than the diameter R2 of the portion of the insertion hole 45 defined by the radially inner edge 47I of the mating tooth 47.
  • the radial length of the step portion 48 can be sufficiently secured, so that more clutch oil can be held in the step portion 48.
  • the output shaft 15 includes a main body 15A that extends in direction D and forms an oil flow path 15H through which clutch oil flows, and a communication hole 15B that is formed in the main body 15A, extends radially, and communicates with the oil flow path 15H.
  • the clutch oil flowing through the oil flow path 15H of the main body 15A flows into the oil groove 42P via the communication hole 15B.
  • At least a portion of the communication hole 15B is located between the end face 42D1 in the first direction D1 of the output shaft holding portion 42 and the end face 47D1 in the first direction D1 of the mating tooth 47 in direction D (i.e., the axial direction of the output shaft 15). According to the above aspect, more clutch oil flowing through the oil flow path 15H of the main body portion 15A can flow to the step portion 48.
  • the clutch center 40 includes a first clutch center 41 and a second clutch center 51, and the first clutch center 41 and the second clutch center 51 are assembled together for use, but the first clutch center 41 and the second clutch center 51 may be integrated.
  • clutch oil does not flow through the insertion hole 45 in the axial direction of the output shaft 15, but it may.
  • the clutch center 40 has a center-side assist cam surface 60A and a center-side slipper cam surface 60S, but the clutch center 40 does not have to have the center-side assist cam surface 60A and the center-side slipper cam surface 60S.
  • the pressure plate 70 has a pressure-side assist cam surface 90A and a pressure-side slipper cam surface 90S, but the pressure plate 70 does not have to have the pressure-side assist cam surface 90A and the pressure-side slipper cam surface 90S.
  • an engine is used as the power source, but the power source is not limited to an engine and may be, for example, an electric motor, etc.
  • the saddle-type vehicle refers to a vehicle on which a driver straddles and rides.
  • the saddle-type vehicle is not limited to motorcycles such as scooters.
  • the saddle-type vehicle may be, for example, a three-wheeled motor vehicle, an ATV (All Terrain vehicle), a snowmobile, etc.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
PCT/JP2024/002005 2023-02-21 2024-01-24 クラッチ装置 Ceased WO2024176698A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP24760005.9A EP4671559A1 (en) 2023-02-21 2024-01-24 CLUTCH DEVICE
CN202480006135.0A CN120380261A (zh) 2023-02-21 2024-01-24 离合器装置
US19/254,357 US20250327496A1 (en) 2023-02-21 2025-06-30 Clutch device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2023025453A JP2024118886A (ja) 2023-02-21 2023-02-21 クラッチ装置
JP2023-025453 2023-02-21

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US19/254,357 Continuation US20250327496A1 (en) 2023-02-21 2025-06-30 Clutch device

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WO2024176698A1 true WO2024176698A1 (ja) 2024-08-29

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PCT/JP2024/002005 Ceased WO2024176698A1 (ja) 2023-02-21 2024-01-24 クラッチ装置

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EP (1) EP4671559A1 (https=)
JP (1) JP2024118886A (https=)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7777262B1 (ja) * 2024-10-23 2025-11-27 株式会社エフ・シー・シー クラッチ装置
JP7651054B1 (ja) * 2024-11-18 2025-03-25 株式会社エフ・シー・シー クラッチ装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5917030A (ja) * 1982-07-19 1984-01-28 Honda Motor Co Ltd 多板摩擦クラツチ
WO2022030349A1 (ja) * 2020-08-06 2022-02-10 株式会社エフ・シー・シー 動力伝達装置
JP2022030211A (ja) 2020-08-06 2022-02-18 株式会社エフ・シー・シー 動力伝達装置
JP2022072810A (ja) * 2020-10-30 2022-05-17 ヤマハ発動機株式会社 クラッチ装置およびそれを備える鞍乗型車両

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5917030A (ja) * 1982-07-19 1984-01-28 Honda Motor Co Ltd 多板摩擦クラツチ
WO2022030349A1 (ja) * 2020-08-06 2022-02-10 株式会社エフ・シー・シー 動力伝達装置
JP2022030211A (ja) 2020-08-06 2022-02-18 株式会社エフ・シー・シー 動力伝達装置
JP2022072810A (ja) * 2020-10-30 2022-05-17 ヤマハ発動機株式会社 クラッチ装置およびそれを備える鞍乗型車両

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JP2024118886A (ja) 2024-09-02
EP4671559A1 (en) 2025-12-31
US20250327496A1 (en) 2025-10-23

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