Clutch device

Abstract

To effectively transmit an axial thrust of an output shaft generated in a weight member by centrifugal force to a pressure-welding member.SOLUTION: A centrifugal clutch mechanism 120 of a clutch device 10 comprises: a holding member 124 that holds a weight member 122 movably between a radially inside position and a radially outside position; a spring 135 that biases the weight member 122 radially inward; a pressure-welding member 126 that moves in an axial direction of an output shaft 15 as the weight member 122 moves from the radially inside position to the radially outside position, thereby pressure-welding an input side rotating plate 20 and an output side rotating plate 22; and a biasing member 140 that is positioned between the holding member 124 and the pressure-welding member 126 in the axial direction of the output shaft 15, biases the weight member 122 held by the holding member 124 in the axial direction of the output shaft 15, and allows the weight member 122 to move radially.SELECTED DRAWING: Figure 15

Description

[Technical Field]

[0001] The present invention relates to a clutch device. [Background technology]

[0002] Straddle-type vehicles such as motorcycles are equipped with a clutch device that can transmit and cut off the rotational driving force of a power source such as an engine to a driving wheel. For example, Patent Document 1 discloses a clutch device that has 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 that can move toward or away from the clutch center.

[0003] The clutch device in Patent Document 1 also includes a centrifugal clutch mechanism with a weight member that moves radially. The weight member moves from a radially inner position to a radially outer position due to centrifugal force generated by rotation of the clutch housing, and presses a driving clutch plate (hereinafter referred to as an input side rotating plate) and a driven clutch plate (hereinafter referred to as an output side rotating plate) together, thereby transmitting the driving force of the engine to the wheels. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2022-30211 Summary of the Invention [Problem to be solved by the invention]

[0005] The centrifugal clutch mechanism includes a retaining member and a pressing member aligned in the axial direction of the output shaft. The retaining member holds a weight member so that it can move radially. The pressing member is configured to press the input rotating plate and the output rotating plate together as the weight member moves radially. The weight member is biased radially inward by a spring attached to the retaining member. Gaps are provided between the weight member and the retaining member and between the weight member and the pressing member in the axial direction of the output shaft. Therefore, the weight member can vibrate in the axial direction of the output shaft due to vibrations of the engine, etc. If the clutch housing rotates while the weight member is vibrating in the axial direction of the output shaft, the thrust in the axial direction of the output shaft generated in the weight member by centrifugal force due to rotation of the clutch housing may not be effectively transmitted to the pressing member.

[0006] The present invention has been made in consideration of the above points, and its object is to provide a clutch device that can effectively transmit the axial thrust of the output shaft that is generated in the weight member by centrifugal force to the pressure contact member. [Means for solving the problem]

[0007] The clutch device according to the present invention is a clutch device that transmits or cuts off the rotational drive 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 and that is rotationally driven together with the output shaft, a pressure member that is provided so as to be able to approach or move away from the clutch center and that is able to press the input side rotating plate and a plurality of output side rotating plates that are arranged alternately with the input side rotating plate, and a plurality of weight members that are configured to be movable from a radially inner position to an outer position by centrifugal force that accompanies rotation of the clutch housing, and when the weight members are at the radially outer position, they press the input side rotating plate and the output side rotating plate together, making it possible to transmit the rotational drive force of the input shaft to the output shaft, and and a centrifugal clutch mechanism that, when the weight member is in a radially inner position, releases the pressing force between the input side rotating plate and the output side rotating plate, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism includes: a holding member that holds the weight member movably between the radially inner position and the radially outer position; an elastic member that urges the weight member radially inward; a pressing member that moves in the axial direction of the output shaft as the weight member moves from the radially inner position to the radially outer position, thereby pressing the input side rotating plate and the output side rotating plate together; and a biasing member that is located between the holding member and the pressing member in the axial direction of the output shaft, and that urges the weight member held by the holding member in the axial direction of the output shaft and allows the weight member to move in the radial direction.

[0008] In the clutch device according to the present invention, the biasing member of the centrifugal clutch mechanism is located between the retaining member and the pressing member in the axial direction of the output shaft, and biases the weight member held by the retaining member in the axial direction of the output shaft while allowing the weight member to move radially. According to the above aspect, since the weight member is biased in the axial direction of the output shaft by the biasing member, axial vibration of the output shaft is suppressed even when there is vibration from the engine, etc. This allows the weight member to move smoothly in the radial direction, and therefore the thrust in the axial direction of the output shaft generated in the weight member by the centrifugal force accompanying rotation of the clutch housing can be effectively transmitted to the pressing member. [Effects of the Invention]

[0009] According to the present invention, it is possible to provide a clutch device that can effectively transmit the thrust force in the axial direction of the output shaft that is generated in the weight member by centrifugal force to the pressure contact member. [Brief explanation of the drawings]

[0010] [Figure 1] FIG. 1 is a cross-sectional view of a clutch device according to a first embodiment. [Figure 2] FIG. 2 is a perspective view of the first clutch center according to the first embodiment. [Figure 3] FIG. 3 is a perspective view of the first clutch center according to the first embodiment. [Figure 4] FIG. 4 is a perspective view of the second clutch center according to the first embodiment. [Figure 5] FIG. 5 is a plan view of the second clutch center according to the first embodiment. [Figure 6] FIG. 6 is a perspective view of a pressure member according to the first embodiment. [Figure 7] FIG. 7 is a perspective view of the first pressure member according to the first embodiment. [Figure 8] FIG. 8 is a perspective view of the first pressure member according to the first embodiment. [Figure 9] FIG. 9 is a perspective view of the second pressure member according to the first embodiment. [Figure 10] FIG. 10 is a perspective view of the second pressure member according to the first embodiment. [Figure 11A] FIG. 11A is a schematic diagram illustrating the action of the center-side assist cam surface and the pressure-side assist cam surface. [Figure 11B] FIG. 11B is a schematic diagram illustrating the action of the center-side slipper cam surface and the pressure-side slipper cam surface. [Figure 12] FIG. 12 is a perspective view of the centrifugal clutch mechanism according to the first embodiment. [Figure 13] FIG. 13 is a cross-sectional view of the centrifugal clutch mechanism according to the first embodiment. [Figure 14] FIG. 14 is a perspective view showing a state in which the pressing member is removed from the centrifugal clutch mechanism according to the first embodiment. [Figure 15] FIG. 15 is a perspective view showing a state in which the pressing member and the guide member are removed from the centrifugal clutch mechanism according to the first embodiment. [Figure 16] FIG. 16 is a plan view showing a state in which the pressing member and the guide member are removed from the centrifugal clutch mechanism according to the first embodiment. [Figure 17] FIG. 17 is a perspective view showing the biasing member of the centrifugal clutch mechanism according to the first embodiment. [Figure 18] FIG. 18 is a plan view showing a part of the centrifugal clutch mechanism according to the second embodiment, in which the weight members are positioned radially inward. [Figure 19] FIG. 19 is a perspective view showing a weight member according to the second embodiment. [Figure 20] FIG. 20 is a plan view showing a weight member according to the second embodiment. [Figure 21] FIG. 21 is a perspective view showing a weight member according to the second embodiment. [Figure 22] FIG. 22 is a bottom view showing the weight member according to the second embodiment. [Figure 23] FIG. 23 is a side view showing the weight member according to the second embodiment. [Figure 24] FIG. 24 is a plan view showing a part of the centrifugal clutch mechanism according to the third embodiment, in which the weight members are positioned radially inward. [Figure 25] FIG. 25 is a perspective view showing a weight member according to the third embodiment. [Figure 26] FIG. 26 is a bottom view showing the weight member according to the third embodiment. [Figure 27] FIG. 27 is a side view showing a weight member according to the third embodiment. [Figure 28A] FIG. 28A is a perspective view showing a biasing member and its surrounding structure according to a fourth embodiment. [Figure 28B] FIG. 28B is a cross-sectional view showing the biasing member and its surrounding structure according to the fourth embodiment. [Figure 29A] FIG. 29A is a perspective view showing a biasing member and its surrounding structure according to a fifth embodiment. [Figure 29B] FIG. 29B is a cross-sectional view showing the biasing member and its surrounding structure according to the fifth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0011] Hereinafter, an embodiment of a clutch device according to the present invention will be described with reference to the drawings. It should be noted that the embodiment described here is not intended to limit the present invention in any particular way. Furthermore, the same reference numerals are used to designate members and parts that perform the same functions, and redundant descriptions will be omitted or simplified as appropriate.

[0012] First Embodiment 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-ride 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.

[0013] In the following description, the direction in which the pressure member 70 of the clutch device 10 approaches and moves away from the clutch center 40 is referred to as direction D, the direction in which the pressure member 70 approaches the clutch center 40 is referred to as a first direction D1, and the direction in which the pressure member 70 moves away from the clutch center 40 is referred to as a second direction D2. The circumferential direction (i.e., the rotational direction) of the clutch center 40 and the pressure member 70 is referred to as a circumferential direction S, the direction from one center-side cam portion 60 to the other center-side cam portion 60 with respect to the circumferential direction S (the direction from one pressure-side cam portion 90 to the other pressure-side cam portion 90) is referred to as a first circumferential direction S1 (see FIG. 2), and the direction from the other center-side cam portion 60 to one center-side cam portion 60 (the direction from the other pressure-side cam portion 90 to one pressure-side cam portion 90) is referred to as a second circumferential direction S2 (see FIG. 2). The radial direction of the output shaft 15 is defined as the radial direction M, the direction away from the output shaft 15 is defined as the outer side M1 (see FIG. 20), and the direction toward the output shaft 15 is defined as the inner side M2 ​​(see FIG. 20). In this embodiment, the axial direction of the output shaft 15 is the same as the direction D. The pressure member 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). However, the above directions are merely defined for the convenience of explanation and do not limit the installation mode of the clutch device 10 or the present invention in any way.

[0014] As shown in FIG. 1, 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 member 70, a stopper plate 100, a centrifugal clutch mechanism 120, and an auxiliary clutch plate 150.

[0015] As shown in Fig. 1, 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. That is, 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.

[0016] As shown in Fig. 1, the output shaft 15 has a main body 15A extending in direction D. The main body 15A has an oil flow path 15H therein through which clutch oil flows. The oil flow path 15H is formed between the main body 15A and a sleeve 16C that fits onto the outside of a push rod 16A (described later). The clutch oil flows inside the output shaft 15, i.e., inside the oil flow path 15H of the main body 15A.

[0017] As shown in FIG. 1, the oil flow path 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 slidably provided 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. When the clutch operating lever is operated, the push rod 16A slides within the sleeve 16C and presses the push member 16B in the second direction D2. A portion of the push member 16B protrudes outward from the output shaft 15 (in this case, in the second direction D2) and is connected to a release bearing 18 provided on the pressure member 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 path 15H.

[0018] The clutch housing 30 is formed by aluminum die-casting. 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 in the second direction D2 from an edge of the bottom wall 31. The clutch housing 30 holds a plurality of input side rotating plates 20.

[0019] As shown in Fig. 1, 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 a rivet 35B via a torque damper 35A. The input gear 35 meshes with a drive gear (not shown) that rotates as the input shaft of the engine rotates. The input gear 35 rotates integrally with the clutch housing 30, independently of the output shaft 15.

[0020] The input side rotating plate 20 is rotationally driven 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 as to be displaceable along the axial direction of the clutch housing 30 (i.e., direction D). The input side rotating plate 20 is provided so as to be rotatable integrally with the clutch housing 30.

[0021] 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 formed in an annular shape. The input side rotating plate 20 is formed by aluminum die-casting. 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 hundred microns deep are formed between the friction materials to hold clutch oil.

[0022] As shown in FIG. 1, 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 a plurality of output side rotating plates 22. The output side rotating plates 22 and the input side rotating plates 20 are arranged alternately in 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 outside M1 of the first clutch center 41 in the radial direction M. The second clutch center 51 is fitted onto the first clutch center 41.

[0023] As shown in Figure 2, the first clutch center 41 includes an output shaft holding portion 42, an annular base wall 43 located on the outer side M1 of the output shaft holding portion 42 in the radial direction M, and a plurality of center side cam portions 60.

[0024] As shown in FIG. 1, the output shaft 15 is connected to the output shaft holding portion 42. A first pressure member 71, which will be described later, is fitted onto the output shaft holding portion 42. As shown in FIG. 2, the output shaft holding portion 42 is formed in a cylindrical shape. The output shaft holding portion 42 is formed with an insertion hole 45 into which the output shaft 15 is inserted and spline-fitted. The insertion hole 45 is formed to penetrate the output shaft holding portion 42. An inner wall 45A of the output shaft holding portion 42 that defines the insertion hole 45 is formed with a plurality of fitting teeth 47 that extend in the axial direction of the output shaft 15 (i.e., direction D). The fitting teeth 47 fit with the output shaft 15.

[0025] The center-side cam portion 60 is formed in a trapezoidal shape with a cam surface made of an inclined surface that constitutes an Assist & Slipper (registered trademark) mechanism that generates an assist torque, which is a force that increases the pressing force (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 (contact force) between the input-side rotating plate 20 and the output-side rotating plate 22, thereby transitioning to a half-clutch state. As shown in FIG. 2 , the center-side cam portion 60 is formed so as to protrude in the second direction D2 from a surface 43D2 on the second direction D2 side of the base wall 43. The center-side cam portions 60 are arranged at equal intervals in the circumferential direction S of the first clutch center 41. In this embodiment, the first clutch center 41 has three center-side cam portions 60, but the number of center-side cam portions 60 is not limited to three.

[0026] As shown in FIG. 2, the center-side cam portion 60 is located on the outer side M1 of the output shaft holding portion 42 in the radial direction M. The center-side cam portion 60 has a center-side assist cam surface 60A (see also FIG. 3) 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 member 70 closer to the clutch center 40 when it rotates relative to the pressure member 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. In this embodiment, when the force is generated, the position of the pressure member 70 relative to the clutch center 40 does not change, and the pressure member 70 does not need to physically move closer to the clutch center 40. Note that the pressure member 70 may be physically displaced relative to the clutch center 40. The center-side slipper cam surface 60S is configured to move the pressure member 70 away from the clutch center 40 when rotating relative to the pressure member 70, in order to reduce the pressing force (pressure contact force) between the input-side rotating plate 20 and the output-side rotating plate 22. In the center-side cam portions 60 adjacent to each other in the circumferential direction S, 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.

[0027] As shown in FIG. 2, the first clutch center 41 has a plurality of boss portions 62 (three in this embodiment). The boss portions 62 are members that indirectly hold the pressure member 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 on the outer side M1 of the output shaft holding portion 42 in the radial direction M. The boss portions 62 extend toward the pressure member 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. A threaded hole 62H is formed in the boss portion 62, into which the bolt 28 (see FIG. 1) is inserted. The threaded hole 62H extends in the axial direction of the clutch center 40 (i.e., in the direction D).

[0028] 2 and 3, 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. 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.

[0029] 2, the first clutch center 41 has a plurality of engagement grooves 49. The engagement grooves 49 are formed in the outer peripheral surface of the base wall 43. The engagement grooves 49 are recessed from the outer peripheral surface of the base wall 43 toward an inner side M2 ​​in the radial direction M.

[0030] 4, the second clutch center 51 includes an annular outer peripheral wall 52, a flange 68 extending from the outer peripheral wall 52 toward the outside M1 in the radial direction M, 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 the direction D.

[0031] As shown in FIG. 4 , a spline fitting portion 56 is provided on the outer peripheral surface of the outer peripheral wall 52. The spline fitting portion 56 has a plurality of center-side fitting teeth 57 extending along the outer peripheral surface of the outer peripheral wall 52 in the axial direction of the second clutch center 51 (i.e., direction D), a plurality of spline grooves 58 formed between adjacent center-side fitting 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 fitting teeth 57 hold the output-side rotating plate 22. The center-side fitting teeth 57 are aligned in the circumferential direction S. The center-side fitting teeth 57 are formed at equal intervals in the circumferential direction S. The center-side fitting teeth 57 are formed to have the same shape. The center-side fitting teeth 57 protrude from the outer peripheral surface of the outer peripheral wall 52 to the outside M1 in the radial direction M. The oil discharge hole 59 is formed to penetrate the outer peripheral wall 52 in the radial direction M. The oil discharge holes 59 are formed between adjacent center-side fitting teeth 57. That is, the oil discharge holes 59 are formed in the spline grooves 58. The oil discharge holes 59 are formed in the center-side fitting portion 54. The oil discharge holes 59 communicate between the inside and outside of the second clutch center 51. The oil discharge holes 59 are holes that discharge clutch oil and the like that has flowed into the clutch center 40 from the output shaft 15 to the outside of the clutch center 40. The clutch oil discharged from the oil discharge holes 59 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22 that are located on the outside M1 of the oil discharge holes 59 in the radial direction M.

[0032] The output side rotating plate 22 is held by the spline fitting portion 56 of the second clutch center 51 and the pressure member 70. A portion of the output side rotating plate 22 is held by the center side fitting teeth 57 and the spline grooves 58 of the second clutch center 51 through spline fitting. Another portion of the output side rotating plate 22 is held by pressure side fitting teeth 87 (see FIG. 6 ) of the pressure member 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. Note that all of the output side rotating plate 22 may be held by the pressure member 70 (for example, the pressure side fitting teeth 87).

[0033] 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 punching out an annular shape from a thin plate material made of SPCC material. 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.

[0034] As shown in Figure 4, 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 Figure 6), 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 Figure 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.

[0035] As shown in Figures 4 and 5, the second clutch center 51 has a plurality of engagement protrusions 55. The engagement protrusions 55 engage with the engagement grooves 49 (see Figure 2) of the first clutch center 41. The engagement protrusions 55 are formed on the inner peripheral surface of the outer peripheral wall 52. The engagement protrusions 55 protrude from the inner peripheral surface of the outer peripheral wall 52 toward the inside M2 ​​in the radial direction M. The engagement protrusions 55 are located closer to the first direction D1 than the outer peripheral wall 52.

[0036] As shown in FIG. 1, the pressure member 70 is provided so as to be able to move toward or away from the clutch center 40. The pressure member 70 is provided so as to be able to rotate relatively to the clutch center 40. The pressure member 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 member 70 is arranged concentrically with the clutch center 40 and the clutch housing 30. As shown in FIG. 6, the pressure member 70 includes a first pressure member 71 and a second pressure member 81. The first pressure member 71 and the second pressure member 81 are assembled to each other. The second pressure member 81 is located on the outer side M1 of the first pressure member 71 in the radial direction M. The second pressure member 81 fits onto the first pressure member 71. The first pressure member 71 and the second pressure member 81 are configured so as to be able to move relative to each other in the direction D. The first pressure member 71 and the second pressure member 81 are configured to be rotatable relative to each other within a predetermined angular range in the circumferential direction S. Here, the predetermined angular range refers to the angular range required for rotation from the state of FIG. 11A (a state in which a pressure-side assist cam surface 90A and a center-side assist cam surface 60A, which will be described later, are in contact) to the state of FIG. 11B (more specifically, a state in which a pressure-side slipper cam surface 90S and a center-side slipper cam surface 60S, which will be described later, are in contact and the second pressure member 81 is in contact with the stopper plate 100). In this way, since the pressure member 70 includes the first pressure member 71 and the second pressure member 81, the first pressure member 71 and the second pressure member 81 can be moved (rotated) independently of each other.

[0037] As shown in FIGS. 7 and 8, the first pressure member 71 is formed in a cylindrical shape. The first pressure member 71 is configured to fit onto the output shaft holding portion 42 (see FIG. 1). The first pressure member 71 houses the tip end 15T (see FIG. 1) of the output shaft 15. The first pressure member 71 is a portion that receives a pressing force from the push member 16B (see FIG. 1). The first pressure member 71 is configured to be movable in the second direction D2 by clutch operation (for example, operation using a clutch lever or a button). The first pressure member 71 is a portion that receives clutch oil that flows out from the tip end 15T of the output shaft 15. The first pressure member 71 is fitted onto the output shaft holding portion 42, thereby positioning the pressure member 70 with respect to the clutch center 40. A release bearing 18 is disposed inside the first pressure member 71. The first pressure member 71 holds the release bearing 18 .

[0038] As shown in FIG. 1, the second pressure member 81 is configured to be pressed by the first pressure member 71 and move in the second direction D2. The second pressure member 81 is fitted into the second clutch center 51, thereby positioning the second pressure member 81 in the radial direction M. The second pressure member 81 is provided so as to be slidable in the direction D relative to the second clutch center 51. The second pressure member 81 and the second clutch center 51 are configured to be rotatable relative to each other in the circumferential direction S. As shown in FIG. 9, the second pressure member 81 has a main body 82 and a flange 98 that is connected to the outer circumferential edge of the main body 82 on the second direction D2 side and extends outward M1 in the radial direction M. The main body 82 protrudes in the first direction D1 beyond the flange 98. The flange 98 is located outward M1 in the radial direction M beyond a tubular portion 80, which will be described later. The second pressure member 81 holds the input side rotary plates 20 and the multiple output side rotary plates 22 arranged alternately. The flange 98 is configured to be able to press the input side rotary plates 20 and the output side rotary plates 22.

[0039] As shown in FIG. 9, the main body 82 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. 10).

[0040] As shown in Fig. 9, the cylindrical portion 80 has a cylindrically formed partition wall 80A. The cylindrical portion 80 is formed integrally with a pressure-side cam portion 90. The pressure-side cam portion 90 is located on the outer side M1 of the partition wall 80A in the radial direction M. As shown in Fig. 6, the cylindrical portion 80 accommodates the first pressure member 71. An inner peripheral surface 85 of the partition wall 80A is configured to be slidable in the direction D relative to an outer peripheral surface 75 of the first pressure member 71.

[0041] The pressure-side cam portion 90 is formed in a platform shape having a cam surface made up of an inclined surface that constitutes an Assist & Slipper (registered trademark) mechanism that slides on the center-side cam portion 60 (see FIG. 2, etc.) to generate assist torque or 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. The pressure-side cam portions 90 are arranged at equal intervals in the circumferential direction S of the second pressure member 81. In this embodiment, the second pressure member 81 has three pressure-side cam portions 90, but the number of pressure-side cam portions 90 is not limited to three.

[0042] As shown in FIG. 9, the pressure-side cam portion 90 is located on the outer side M1 of the cylindrical portion 80 in the radial direction M. The pressure-side cam portion 90 has a pressure-side assist cam surface 90A (see also FIG. 10) 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 moves the pressure member 70 closer to the clutch center 40 when rotating relative 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. 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 member 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. In the pressure-side cam portions 90 adjacent to each other in the circumferential direction S, 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.

[0043] Here, the action of the center-side cam portion 60 and the pressure-side cam portion 90 will be described. When the engine speed increases and the rotational driving force input to the input gear 35 and the clutch housing 30 can be transmitted to the output shaft 15 via the clutch center 40, a rotational force in the first circumferential direction S1 is applied to the pressure member 70, as shown in FIG. 11A. Therefore, due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, a force in the first direction D1 is generated in the pressure member 70. This increases the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22.

[0044] On the other hand, when the rotational speed of the output shaft 15 exceeds the rotational speed of the input gear 35 and the clutch housing 30 and back torque is generated, a rotational force in the first circumferential direction S1 is applied to the clutch center 40, as shown in FIG. 11B. As a result, the center-side slipper cam surface 60S and the pressure-side slipper cam surface 90S act to move the pressure member 70 in the second direction D2, thereby releasing the pressure contact force between the input-side rotating plate 20 and the output-side rotating plate 22. This makes it possible to avoid malfunctions in the engine and transmission due to back torque. Note that the application of the rotational force in the first circumferential direction S1 to the clutch center 40 causes the first pressure member 71 and the second pressure member 81 to rotate relative to each other in the circumferential direction S.

[0045] 9, the pressure-side fitting portion 88 is located on the outer side M1 in the radial direction M than the pressure-side cam portion 90. The pressure-side fitting portion 88 is located on the second direction D2 side than 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. 4).

[0046] As shown in FIGS. 9 and 10, the second pressure member 81 has a pressure-side cam hole 83H that penetrates the main body 82 and a portion of the flange 98. The pressure-side cam hole 83H is located on the outer side M1 of the cylindrical portion 80 in the radial direction M. The pressure-side cam hole 83H extends from the side of the cylindrical portion 80 to the outer side M1 of the pressure-side fitting portion 88 in the radial direction M. The pressure-side cam hole 83H 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. When viewed from the axial direction of the second pressure member 81, the pressure-side assist cam surface 90A and a portion of the pressure-side cam hole 83H overlap. The boss portion 62 (see FIG. 2) of the first clutch center 41 is inserted into the pressure-side cam hole 83H. The boss portion 62 passes through the pressure-side cam hole 83H.

[0047] As shown in FIG. 9, the second pressure member 81 has a plurality of pressure side fitting teeth 87 arranged on a flange 98. The pressure side fitting teeth 87 hold the output side rotating plate 22. The pressure side fitting teeth 87 protrude from the flange 98 in a first direction D1. The pressure side fitting teeth 87 are located on the outer side M1 in the radial direction M than the cylindrical portion 80. The pressure side fitting teeth 87 are located on the outer side M1 in the radial direction M than the pressure side cam portion 90. The pressure side fitting teeth 87 are located on the outer side M1 in the radial direction M than the pressure side fitting portion 88. The plurality of pressure side fitting teeth 87 are aligned in the circumferential direction S. The plurality of pressure side fitting teeth 87 are arranged at equal intervals in the circumferential direction S. In this embodiment, some of the pressure-side fitting teeth 87 have been removed, so the spacing in those areas is wider, but the other adjacent pressure-side fitting teeth 87 are arranged at equal intervals.

[0048] As shown in FIG. 1, the spring accommodating portion 84 is formed in the pressure-side cam portion 90 (see also FIG. 10). The spring accommodating portion 84 is located on the outer side M1 in the radial direction M of the partition wall 80A of the cylindrical portion 80. 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. 12A). The spring accommodating portion 84 is formed in a circular shape. The spring accommodating portion 84 accommodates the clutch spring 25.

[0049] As shown in FIG. 1, the clutch spring 25 is accommodated in the spring accommodating portion 84. An end of the clutch spring 25 in the first direction D1 abuts against the second pressure member 81. An end of the clutch spring 25 in the second direction D2 abuts against the stopper plate 100. The clutch spring 25 biases the pressure member 70 (more specifically, the second pressure member 81) toward the clutch center 40 (i.e., toward the first direction D1). The clutch spring 25 is, for example, a coil spring made of spring steel wound in a spiral shape. The clutch spring 25 extends in the direction D.

[0050] As shown in FIG. 1, 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 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 FIGS. 12 and 13, the centrifugal clutch mechanism 120 has a plurality of weight members 122, a holding member 124, a pressing member 126, a guide member 128 (see also FIG. 14), a first spherical member 131, a second spherical member 132, a spring 135 (see also FIG. 1), and a biasing member 140 (see FIG. 15). When the weight member 122 is located at a position M1 on the outer side in the radial direction M, the centrifugal clutch mechanism 120 presses the input side rotating plate 20 and the output side rotating plate 22 together, enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15. When the weight member 122 is located at a position M2 on the inner side in the radial direction M, the centrifugal clutch mechanism 120 releases the pressing force between the input side rotating plate 20 and the output side rotating plate 22, enabling 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 an auxiliary clutch plate 150 (see FIG. 1).

[0051] As shown in FIG. 16, the multiple weight members 122 are arranged in the circumferential direction S. The weight members 122 are configured to be movable from an inner position M2 to an outer position M1 in the radial direction M by centrifugal force generated by rotation of the clutch housing 30. As shown in FIG. 13, the weight members 122 are accommodated in an accommodating portion 124A (described later) of the holding member 124. As shown in FIG. 15, the weight member 122 includes a main body portion 122A formed in a substantially rectangular parallelepiped shape and flat portions 122B located at both ends of the main body portion 122A in the circumferential direction S. The weight member 122 includes through holes 122H (see FIG. 13) that penetrate the main body portion 122A in the axial direction of the output shaft 15 (i.e., direction D). Two through holes 122H are formed in one weight member 122. The flat portion 122B is located closer to the first direction D1 than the main body portion 122A. The flat surface portion 122B has a plane perpendicular to the axial direction of the output shaft 15. The flat surface portion 122B is a portion that is biased by a biasing portion 142 (described later) of the biasing member 140. When no centrifugal force is applied, the weight member 122 is held at a position on the inner side M2 ​​in the radial direction M by the spring 135. When centrifugal force is applied, the weight member 122 moves toward the outer side M1 in the radial direction M against the biasing force of the spring 135, and moves to the position on the outer side M1 in the radial direction M.

[0052] As shown in FIG. 13 , 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 (here, in the second direction D2) of a through hole 122H formed in the weight member 122 and contacts the rolling surface of the pressing 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 (here, in the first direction D1) of the through hole 122H formed in the weight member 122 and contacts the rolling surface of the holding member 124. The first spherical member 131 and the second spherical member 132 are configured to be rollable.

[0053] As shown in FIG. 1, the spring 135 is disposed on the outer side M1 of the weight member 122 in the radial direction M. The spring 135 is provided in the holding member 124. The spring 135 is housed in a housing portion 124A (see FIG. 13) of the holding member 124. A portion of the spring 135 is located inside the weight member 122. The spring 135 biases the weight member 122 toward the inner side M2 ​​in the radial direction M. The spring 135 is, for example, a coil spring. As shown in FIG. 16, the spring 135 includes a first spring 135A and a second spring 135B arranged in the circumferential direction S. The first spring 135A and the second spring 135B have the same shape. The first spring 135A and the second spring 135B are disposed between the pair of first spherical members 131 in the circumferential direction S. The pair of first spherical members 131 may be disposed between the first spring 135A and the second spring 135B in the circumferential direction S. The spring 135 is an example of an elastic member. The elastic member may be rubber. The first spring 135A is an example of a first elastic member, and the second spring 135B is an example of a second elastic member.

[0054] As shown in FIG. 13, the holding member 124 holds the weight member 122 movably between a position on the inner side M2 ​​in the radial direction M and a position on the outer side M1 in the radial direction M. The holding member 124 is formed in an annular shape. The holding member 124 is molded by aluminum die-casting. The holding member 124 has a plurality of accommodating portions 124A formed in the circumferential direction S, pressing portions 124C, and engaging protrusions 125 (see FIG. 14). The accommodating portion 124A accommodates the weight member 122. The accommodating portion 124A is formed in a concave shape that matches the shape and movement range of the weight member 122. One end of the spring 135 is configured to be able to abut against an outer peripheral wall surface 124AA of the accommodating portion 124A. The accommodating portion 124A is provided with an abutting surface 124B against which the weight member 130 abuts when the weight member 122 moves in the radial direction M. The abutment surface 124B faces the weight member 122 in the axial direction of the output shaft 15 (i.e., direction D). Here, the second spherical member 132 of the weight member 130 abuts against the abutment surface 124B. As shown in FIG. 16 , the engagement protrusion 125 is located outwardly M1 in the radial direction M from the spring 135. The engagement protrusion 125 protrudes toward the outwardly M1 in the radial direction M. The engagement protrusion 125 engages with the clutch housing 30. A plurality of engagement protrusions 125 are formed along the circumferential direction S. The holding member 124 is provided with a pressing surface 124AP that is part of the outer circumferential wall surface 124AA of the accommodating portion 124A and is pressed by the weight member 122 when the weight member 122 is located at the outer side M1 in the radial direction M. Stress from the weight member 122 toward the outer side M1 in the radial direction M is applied to the pressing surface 124AP. The engagement protrusion 125 and the pressing surface 124AP are arranged so as to be offset from each other in the circumferential direction S. Here, the engagement protrusion 125 is arranged between the pair of pressing surfaces 124AP in the circumferential direction S. The holding member 124 is an example of an abutting member.

[0055] As shown in FIG. 13 , the pressing member 126 is configured to move in a second direction D2 as the weight member 122 moves from a position on the inside M2 ​​in the radial direction M to a position on the outside M1, thereby pressing the input side rotating plate 20 and the output side rotating plate 22 together. The pressing member 126 is formed in an annular shape. The pressing member 126 has a plurality of sloped portions 126A formed along the circumferential direction S, grooves 126B formed at the positions where the sloped portions 126A are formed, and a pressing surface 126C. The sloped portions 126A are formed at positions corresponding to the weight members 122. The sloped portions 126A are inclined in the first direction D1 from the inside M2 ​​in the radial direction M to the outside M1 in the radial direction M. When the clutch housing 30 is stationary, the weight member 122 is held at the inside M2 ​​in the radial direction M by the biasing force of the spring 135. When the clutch housing 30 rotates and centrifugal force is applied to the weight member 122, the weight member 122 moves along the sloped portion 126A, causing the pressing member 126 to move in a direction away from the holding member 124 (i.e., in the second direction D2). As a result, 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. As shown in FIG. 12, the pressing member 126 has multiple protrusions 127 formed along the circumferential direction S. The protrusions 127 overlap with the engaging protrusions 125 of the holding member 124. The protrusions 127 engage with the clutch housing 30. Similar to the input-side rotating plate 20, the holding member 124 and the pressing member 126 are held by the inner circumferential surface of the side wall 33 of the clutch housing 30 via the engaging protrusions 125 and the protrusions 127. The holding member 124 and the pressure contact member 126 are held in the clutch housing 30 by spline fitting. 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.

[0056] As shown in FIGS. 12 and 13 , the guide member 128 is located between the holding member 124 and the pressing member 126 in the axial direction of the output shaft 15 (i.e., direction D). The guide member 128 is attached to the holding member 124. The guide member 128 is fixed to the holding member 124. More specifically, the guide member 128 is fixed to the surface of the holding member 124 on which the accommodation portion 124A is formed. The guide member 128 holds the weight member 122 so that the weight member 122 is movable in the radial direction M. The guide member 128 guides the movement of the weight member 122 in the radial direction M. As shown in FIG. 14 , the guide member 128 is formed in an annular shape. The guide member 128 has a guide portion 129A that guides the movement of the weight member 122 and a fixing portion 129B to which the biasing member 140 is fixed. The guide portion 129A extends in the radial direction M. Guide portion 129A fits into groove 122AH (see FIG. 15) formed approximately in the center of main body portion 122A of weight member 122. Fixing portion 129B is formed in a substantially triangular shape. Fixing portion 129B fixes fixing portion 141 (see FIG. 17) of biasing member 140, which will be described later. Fixing portion 129B is formed with insertion hole 129C (see FIGS. 14 and 29A), into which rivet 136, which will be described later, is inserted.

[0057] The urging member 140 is located between the holding member 124 and the pressing member 126 in the axial direction of the output shaft 15 (i.e., direction D). As shown in FIG. 14 , the urging member 140 is located between the holding member 124 and the guide member 128 in the axial direction of the output shaft 15 (i.e., direction D). The urging member 140 is provided between the guide member 128 and the weight member 122. The urging member 140 is provided on the guide member 128. The urging member 140 is fixed to the holding member 124. The urging member 140 is provided on the guide member 128 between adjacent weight members 122. The urging member 140 is fixed to the holding member 124 between adjacent weight members 122. The urging member 140, together with the guide member 128, is fixed to the holding member 124 by a rivet 136. The biasing member 140 may be fixed to the holding member 124 by a fastening member such as a bolt instead of the rivet 136. In this embodiment, the biasing member 140 is formed separately from the guide member 128, but it may be formed integrally with the guide member 128. The biasing member 140 biases the weight member 122 held by the holding member 124 in the axial direction of the output shaft 15. The biasing member 140 biases the weight member 122 in the axial direction of the output shaft 15 and toward the abutment surface 124B (see FIG. 1). The biasing member 140 presses the end of the weight member 122 in the circumferential direction S. The biasing member 140 constantly biases the weight member 122 in the axial direction of the output shaft 15. That is, the biasing member 140 biases the weight member 122 in the axial direction of the output shaft 15 throughout the entire range from when the weight member 122 is positioned on the inner side M2 ​​in the radial direction M to when it is positioned on the outer side M1 in the radial direction M. In this embodiment, the biasing member 140 biases the weight member 122 in the first direction D1. The biasing member 140 biases the weight member 122 in the axial direction of the output shaft 15 and toward the holding member 124. The biasing member 140 presses the second spherical member 132 of the centrifugal clutch mechanism 120 against the holding member 124 (here, the abutment surface 124B). The biasing member 140 allows the weight member 122 to move in the radial direction M.

[0058] As shown in FIG. 17 , the biasing member 140 is made of a plate member. The biasing member 140 is made of, for example, SPCC (cold-rolled steel plate). The biasing member 140 is a so-called leaf spring. The biasing member 140 includes a fixed portion 141 formed in a substantially triangular shape and biasing portions 142 provided on the outer side M1 in the radial direction M of the fixed portion 141 and at both ends in the circumferential direction S. The fixed portion 141 is a portion that contacts the holding member 124 and the guide member 128. The biasing portion 142 is located closer to the first direction D1 than the fixed portion 141. The biasing portion 142 is a portion that contacts the weight member 122. More specifically, the biasing portion 142 is a portion that contacts the flat portion 122B (see FIG. 15 ) of the weight member 122. The biasing portion 142 biases the weight member 122 in the axial direction of the output shaft 15 (i.e., direction D). The biasing portion 142 biases the weight member 122 in a first direction D1. The biasing portion 142 is configured to be elastically deformable. As shown in FIG. 16 , the biasing portion 142 includes a first biasing portion 142A provided at an end of the fixed portion 141 on the first circumferential direction S1 side and a second biasing portion 142B provided at an end of the fixed portion 141 on the second circumferential direction S2 side. The first biasing portion 142A biases the flat portion 122B of the weight member 122 located closer to the first circumferential direction S1 than the biasing member 140. The second biasing portion 142B biases the flat portion 122B of the weight member 122 located closer to the second circumferential direction S2 than the biasing member 140. In this way, one biasing member 140 biases a plurality of weight members 122 (two weight members 122 in this example) in the axial direction of the output shaft 15.

[0059] In this centrifugal clutch mechanism 120, when no centrifugal force is applied to the weight member 122, the weight member 122 is held at a position on the inner side M2 ​​in the radial direction M, and the pressure contact force between the input side rotary plate 20 and the output side rotary plate 22 is released. On the other hand, when centrifugal force is applied to the weight member 122, the weight member 122 moves from the position on the inner side M2 ​​in the radial direction M to a position on the outer side M1. At this time, because the weight member 122 is biased in the first direction D1 by the biasing member 140, the weight member 122 moves smoothly from the position on the inner side M2 ​​in the radial direction M to the position on the outer side M1 in the radial direction M without vibrating in the axial direction of the output shaft 15 (i.e., direction D). As a result, the pressing surface 126C formed on the pressing member 126 presses the input side rotating plate 20 and the output side rotating plate 22 via the flange 68 of the second clutch center 51, bringing them into a pressed state, and the rotational driving force of the input shaft becomes transmittable to the output shaft 15. At this time, the holding member 124 moves in the first direction D1, and the pressing portion 124C formed on the holding member 124 presses the auxiliary clutch plate 150.

[0060] As shown in FIG. 1, the auxiliary clutch plate 150 is provided in the clutch housing 30. The auxiliary clutch plate 150 is fixed to the output shaft 15. An insertion hole 152H is formed in the auxiliary clutch plate 150, into which the output shaft 15 is inserted and spline-fitted. The auxiliary clutch plate 150 is disposed closer to the first direction D1 than a portion of the centrifugal clutch mechanism 120. The auxiliary clutch plate 150 is adjacent to the first clutch center 41.

[0061] The auxiliary clutch plate 150 is configured to be pressed by the centrifugal clutch mechanism 120 (here, the pressing portion 124C of the holding member 124) when the input side rotating plate 20 and the output side rotating plate 22 are in pressure contact with each other (i.e., when the weight member 122 of the centrifugal clutch mechanism 120 is located at a position M1 on the outside in the radial direction M), thereby enabling transmission of the rotational driving force of the input shaft 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 portion 124C of the holding member 124) when the pressure contact 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 a position M2 on the inside in the radial direction M), thereby blocking transmission of the rotational driving force of the input shaft to the output shaft 15.

[0062] As shown in FIG. 1 , the stopper plate 100 is provided so as to be able to come into contact with the pressure member 70. The stopper plate 100 is a member that prevents the pressure member 70 from moving away from the clutch center 40 by more than a predetermined distance in the second direction D2. The stopper plate 100 is fixed to the boss portion 62 of the first clutch center 41 by a bolt 28. With the clutch spring 25 disposed in the spring accommodating portion 84, the pressure member 70 is fixed to the clutch center 40 by tightening the bolt 28 to the boss portion 62 via the stopper plate 100. The stopper plate 100 is formed in a ring shape in a plan view.

[0063] As described above, according to the clutch device 10 of this embodiment, the biasing member 140 of the centrifugal clutch mechanism 120 is located between the holding member 124 and the pressing member 126 in the axial direction of the output shaft 15, and biases the weight member 122 held by the holding member 124 in the axial direction of the output shaft 15 while allowing the weight member 122 to move in the radial direction M. According to the above aspect, the weight member 122 is biased in the axial direction of the output shaft 15 by the biasing member 140, so that axial vibration of the output shaft 15 is suppressed even if there is vibration of the engine, etc. As a result, the weight member 122 can move smoothly in the radial direction M, and therefore thrust in the axial direction of the output shaft 15 generated in the weight member 122 by centrifugal force accompanying rotation of the clutch housing 30 can be effectively transmitted to the pressing member 126.

[0064] In the clutch device 10 of this embodiment, the biasing member 140 is made up of a plate member. According to the above aspect, the weight member 122 can be biased in the axial direction of the output shaft 15 by the biasing member 140 having a simple configuration.

[0065] The clutch device 10 of this embodiment includes a guide member 128 that is located between the retaining member 124 and the pressing member 126 in the axial direction of the output shaft 15 and that guides movement of the weight member 122 in the radial direction M, and the biasing member 140 is provided on the guide member 128. According to the above aspect, the biasing member 140 can more reliably bias a predetermined portion of the weight member 122 in the axial direction of the output shaft 15.

[0066] In the clutch device 10 of this embodiment, the biasing member 140 is fixed to the holding member 124. According to the above aspect, since the biasing member 140 is fixed to the holding member 124, the biasing member 140 can more reliably bias a predetermined portion of the weight member 122 in the axial direction of the output shaft 15.

[0067] In the clutch device 10 of this embodiment, the biasing member 140 includes a biasing portion 142 that biases the weight member 122 in the axial direction of the output shaft 15, and the biasing portion 142 is formed to be elastically deformable. According to the above aspect, the biasing portion 142 is prevented from biasing the weight member 122 excessively.

[0068] In the clutch device 10 of this embodiment, one biasing member 140 is provided with a biasing portion 142 at an end portion on one side in the circumferential direction S (first circumferential direction S1 side) of the biasing member 140 and at an end portion on the other side (second circumferential direction S2 side) of the biasing member 140. According to the above aspect, the weight member 122 can be biased in the axial direction of the output shaft 15 by each of the biasing portions 142.

[0069] In the clutch device 10 of this embodiment, the weight member 122 has a flat portion 122B that is biased by the biasing portion 142. According to the above aspect, the biasing force from the biasing portion 142 can be transmitted to the weight member 122 more effectively.

[0070] In the clutch device 10 of this embodiment, one biasing member 140 biases the multiple weight members 122 in the axial direction of the output shaft 15. According to the above aspect, the centrifugal clutch mechanism 120 can be simplified.

[0071] In the clutch device 10 of this embodiment, the multiple weight members 122 are aligned in the circumferential direction S, and the biasing members 140 are provided on the guide member 128 between adjacent weight members 122. According to the above aspect, the biasing members 140 can be arranged compactly.

[0072] In the clutch device 10 of this embodiment, the biasing member 140 is fixed to the holding member 124 between adjacent weight members 122. According to the above-described aspect, the biasing member 140 can be arranged compactly.

[0073] In the clutch device 10 of this embodiment, the retaining member 124 is positioned on the outer side M1 of the spring 135 in the radial direction M, and includes an engaging protrusion 125 that engages with the clutch housing 30, and a pressing surface 124AP that is pressed by the weight member 122 when the weight member 122 is at the outer side M1 in the radial direction M, and the engaging protrusion 125 and the pressing surface 124AP are arranged to be offset from each other in the circumferential direction S. According to the above aspect, an excessive load is not applied to the engaging protrusion 125, and therefore damage to the engaging protrusion 125 can be suppressed.

[0074] In the clutch device 10 of this embodiment, the weight member 122 may have a plurality of through holes 122H that penetrate in the axial direction of the output shaft 15, the spring 135 may include a first spring 135A and a second spring 135B that are aligned in the circumferential direction S, and the centrifugal clutch mechanism 120 may have a first spherical member 131 that partially protrudes from the opening of the through hole 122H and is configured to be rollable, and the first spherical member 131 may be disposed between the first spring 135A and the second spring 135B in the circumferential direction S. According to the above aspect, the weight member 122 can be biased inward M2 in the radial direction M by the first spring 135A and the second spring 135B in a balanced manner.

[0075] In the clutch device 10 of this embodiment, the biasing member 140 biases the weight member 122 in the axial direction of the output shaft 15 and toward the holding member 124. According to the above aspect, the weight member 122 is always in contact with the holding member 124 by the biasing member 140, so that vibration of the weight member 122 in the axial direction of the output shaft 15 is more reliably suppressed even when there is vibration of the engine or the like.

[0076] Second Embodiment FIG. 18 is a plan view showing a portion of the centrifugal clutch mechanism 120 according to the second embodiment, illustrating a state in which a weight member 530 is positioned on the inner side M2 ​​in the radial direction M. As shown in FIG. 18, multiple weight members 530 are arranged in the circumferential direction S. The weight members 530 are configured to be movable from a position on the inner side M2 ​​in the radial direction M to a position on the outer side M1 in the radial direction M by centrifugal force generated by rotation of the clutch housing 30. The weight members 530 are configured to be able to press the pressing member 126 in the second direction D2. When no centrifugal force is applied, the weight members 530 are held at the position on the inner side M2 ​​in the radial direction M by the springs 135. When centrifugal force is applied, the weight members 530 move toward the outer side M1 in the radial direction M against the biasing force of the springs 135, and move to the position on the outer side M1 in the radial direction M. The weight members 530 are accommodated in the accommodation portions 124A of the holding member 124. As shown in Figure 21, the weight member 530 includes a biasing member holding portion 531, a first plane 533 provided on one side of the biasing member holding portion 531 in the circumferential direction S, a second plane 535 provided on the other side of the biasing member holding portion 531 in the circumferential direction S, and a weight-side inclined surface 530F (see Figures 19 and 20) located on the opposite side of the first plane 533 and the second plane 535 in the axial direction of the output shaft 15 (i.e., direction D).

[0077] The biasing member holding portion 531 holds the spring 135. As shown in FIG. 21 , the biasing member holding portion 531 is a recessed groove recessed from the outer side M1 to the inner side M2 ​​in the second direction D2 and the radial direction M. The biasing member holding portion 531 includes a holding wall 532 that holds an end portion of the spring 135 on the inner side M2 ​​in the radial direction M. In the present embodiment, the biasing member holding portion 531 includes a first biasing member holding portion 531A that holds the first spring 135A (see FIG. 18 ) and a second biasing member holding portion 531B that holds the second spring 135B (see FIG. 18 ).

[0078] As shown in FIGS. 21 and 22 , the first flat surface 533 is provided closer to the first circumferential direction S1 than the biasing member holding portion 531. More specifically, the first flat surface 533 is provided closer to the first circumferential direction S1 than the first biasing member holding portion 531A. The first flat surface 533 is provided alongside the first biasing member holding portion 531A in the circumferential direction S. The second flat surface 535 is provided closer to the second circumferential direction S2 than the biasing member holding portion 531. More specifically, the second flat surface 535 is provided closer to the second circumferential direction S2 than the second biasing member holding portion 531B. The second flat surface 535 is provided alongside the second biasing member holding portion 531B in the circumferential direction S. As shown in FIG. 23 , the first flat surface 533 and the second flat surface 535 are perpendicular to the axial direction of the output shaft 15 (i.e., direction D). The first flat surface 533 and the second flat surface 535 are formed flush with each other. The first flat surface 533 and the second flat surface 535 are provided so as to be able to come into contact with the contact surface 124B of the holding member 124. The first flat surface 533 and the second flat surface 535 are provided so as to be able to slide relative to the holding member 124. More specifically, the first flat surface 533 and the second flat surface 535 are provided so as to be able to slide relative to the contact surface 124B.

[0079] 21 , the weight member 530 has a third flat surface 537. The third flat surface 537 is located between the first flat surface 533 and the second flat surface 535 in the circumferential direction S. The third flat surface 537 is located between the first biasing member holding portion 531A and the second biasing member holding portion 531B in the circumferential direction S. The third flat surface 537 may be provided to be slidable with respect to the holding member 124. The third flat surface 537 may be formed flush with the first flat surface 533 and the second flat surface 535.

[0080] The weight-side inclined surface 530F is provided so as to be able to come into contact with the pressing member 126. As shown in Fig. 23, the weight-side inclined surface 530F is inclined with respect to the axial direction of the output shaft 15 (i.e., direction D). The weight-side inclined surface 530F is inclined so as to face in a first direction D1 from an inner side M2 ​​in the radial direction M to an outer side M1 in the radial direction M. The weight-side inclined surface 530F is configured so as to be able to slide on the sloped portion 126A of the pressing member 126 (see Fig. 13).

[0081] 18 , the biasing member 140 biases the weight member 530 in the axial direction of the output shaft 15 (i.e., direction D) and toward the abutment surface 124B. The biasing portion 142 of the biasing member 140 abuts against the weight member 530. When the weight member 530 is positioned at least on the inner side M2 ​​in the radial direction M, as viewed from the axial direction of the output shaft 15, the fixing portion 141 of the biasing member 140A is positioned to the side in the circumferential direction S (first circumferential direction S1 side) of the first flat surface 533, and the biasing portion 142 of the biasing member 140A overlaps with at least a portion of the first flat surface 533. When the weight member 530 is positioned at least on the inner side M2 ​​in the radial direction M, the fixed portion 141 of the urging member 140B is positioned to the side in the circumferential direction S (on the second circumferential direction S2 side) of the second plane 535, when viewed from the axial direction of the output shaft 15, and the urging portion 142 of the urging member 140B overlaps with at least a portion of the second plane 535. Note that when the weight member 530 is moving from the inner side M2 ​​to the outer side M1 in the radial direction M, and when the weight member 530 is positioned on the outer side M1 in the radial direction M, the urging portion 142 of the urging member 140A may overlap with at least a portion of the first plane 533, and the urging portion 142 of the urging member 140B may overlap with at least a portion of the second plane 535, when viewed from the axial direction of the output shaft 15.

[0082] 18 , when no centrifugal force is applied to the weight member 530, the weight member 530 is held at a position on the inner side M2 ​​in the radial direction M, and the pressing force between the input side rotating plate 20 and the output side rotating plate 22 is released. On the other hand, when centrifugal force is applied to the weight member 530, the weight member 530 moves from the position on the inner side M2 ​​to a position on the outer side M1 in the radial direction M. When the weight member 530 moves in the radial direction M, the weight-side inclined surface 530F of the weight member 530 slides against the sloped portion 126A of the pressing member 126, and the first flat surface 533 and the second flat surface 535 of the weight member 530 slide against the abutting surface 124B of the holding member 124. At this time, the pressing surface 126C (see FIG. 13) of the pressing member 126 presses the input side rotating plate 20 and the output side rotating plate 22 via the flange 68 of the second clutch center 51, bringing them into a pressed state, and the rotational driving force of the input shaft becomes capable of being transmitted to the output shaft 15. At the same time, the holding member 124 moves in the first direction D1, and the pressing portion 124C (see FIG. 13) of the holding member 124 presses the auxiliary clutch plate 150.

[0083] Third Embodiment FIG. 24 is a plan view showing a portion of the centrifugal clutch mechanism 120 according to the third embodiment, illustrating a state in which a weight member 630 is positioned on the inner side M2 ​​in the radial direction M. As shown in FIG. 24, multiple weight members 630 are aligned in the circumferential direction S. As shown in FIG. 25, the weight member 630 includes a guide portion 638 that accommodates a portion of the cylindrical member 670. The guide portion 638 is formed on a surface (here, the third flat surface 537) that faces the holding member 124. The guide portion 638 holds the cylindrical member 670 such that a portion of the cylindrical member 670 protrudes from the surface (here, the third flat surface 537) of the weight member 630 that faces the holding member 124 toward the holding member 124 (i.e., toward the first direction D1) (see FIG. 27). The guide portion 638 guides the movement of the cylindrical member 670 in the radial direction M. The guide portion 638 is located between the first biasing member holding portion 531A and the second biasing member holding portion 531B in the circumferential direction S. As shown in FIG. 26 , the guide portion 638 is formed in a rectangular shape in a plan view. The guide portion 638 includes a first restricting portion 638S that restricts the cylindrical member 670 from moving in the circumferential direction S, and a second restricting portion 638M that restricts the cylindrical member 670 from moving in the radial direction M by more than a predetermined distance. The first restricting portion 638S is provided on each of the first circumferential direction S1 side and the second circumferential direction S2 side in the circumferential direction S. The second restricting portion 638M is provided on each of the outer side M1 and the inner side M2 ​​in the radial direction M. The guide portion 638 has an accommodation groove 638P that is recessed in a direction from the retaining member 124 toward the weight member 630 (i.e., second direction D2) with respect to the axial direction of the output shaft 15 (i.e., direction D) and accommodates a part of the cylindrical member 670. The accommodation groove 638P is defined by a first restriction portion 638S and a second restriction portion 638M.

[0084] As shown in FIG. 24 , the cylindrical member 670 is provided between the weight member 630 and the holding member 124 in the axial direction of the output shaft 15 (i.e., direction D). The cylindrical member 670 is disposed so as to extend in a direction intersecting the radial direction M (here, a direction perpendicular to the radial direction M and direction D). The cylindrical member 670 rolls relative to the weight member 630 and the holding member 124. A portion of the cylindrical member 670 is housed in the housing portion 124A of the holding member 124, and another portion of the cylindrical member 670 is housed in the guide portion 638 of the weight member 630. The cylindrical member 670 rolls relative to the abutment surface 124B of the housing portion 124A and the guide portion 638. As shown in FIG. 26 , the cylindrical member 670 is located between the first spring 135A and the second spring 135B in the circumferential direction S.

[0085] 24, the biasing member 140 biases the weight member 630 in the axial direction of the output shaft 15 (i.e., direction D) and toward the abutment surface 124B. The biasing portion 142 of the biasing member 140 abuts against the weight member 630. When the weight member 630 is positioned at least on the inner side M2 ​​in the radial direction M, as viewed from the axial direction of the output shaft 15, the biasing portion 142 of the biasing member 140A is positioned on the side in the circumferential direction S (first circumferential direction S1 side) of the guide portion 638, and the biasing portion 142 of the biasing member 140B is positioned on the side in the circumferential direction S (second circumferential direction S2 side) of the guide portion 638. In addition, when viewed from the axial direction of the output shaft 15, in at least a part of the state in which the weight member 630 is moving from the inner side M2 ​​to the outer side M1 in the radial direction M, and in the state in which the weight member 630 is positioned on the outer side M1 in the radial direction M, the biasing portion 142 of the biasing member 140A may be positioned on the side in the circumferential direction S (first circumferential direction S1 side) of the guide portion 638, and the biasing portion 142 of the biasing member 140B may be positioned on the side in the circumferential direction S (second circumferential direction S2 side) of the guide portion 638.

[0086] 24 , when no centrifugal force is applied to the weight member 630, the weight member 630 is held at a position on the inner side M2 ​​in the radial direction M, and the pressure force between the input side rotating plate 20 and the output side rotating plate 22 is released. On the other hand, when centrifugal force is applied to the weight member 630, the weight member 630 moves from the position on the inner side M2 ​​to a position on the outer side M1 in the radial direction M. When the weight member 630 moves in the radial direction M, the cylindrical member 670 rolls relative to the weight member 630 and the holding member 124, guided by the guide portion 638 and the housing portion 124A. At this time, the first flat surface 533 and the second flat surface 535 of the weight member 630 do not slide on the abutting surface 124B of the holding member 124.

[0087] <Fourth embodiment> As shown in FIGS. 28A and 28B, a biasing member 240 according to the fourth embodiment is provided on the weight member 122. The biasing member 240 is provided between the guide member 128 and the weight member 122. The biasing member 240 is provided between the guide portion 129A (see FIG. 14) of the guide member 128 and the groove 122AH of the weight member 122. The biasing member 240 is provided on the second direction D2 side of the weight member 122. The biasing member 240 is provided at the center of the weight member 122 in the circumferential direction S. The biasing member 240 is attached to the groove 122AH of the main body portion 122A of the weight member 122. The biasing member 240 is disposed between the pair of through-holes 122H in the circumferential direction S. At least a portion of the biasing member 240 is located inward M2 in the radial direction M from the first spherical member 131 and the second spherical member 132 (i.e., the through-hole 122H). The biasing member 240 is made of an elastic material. The biasing member 240 is, for example, rubber or a leaf spring. The biasing member 240 extends in the radial direction M. The biasing member 240 has a rectangular parallelepiped shape. The length of the biasing member 240 in the radial direction M is longer than the length in the circumferential direction S. The biasing member 240 contacts the guide portion 129A of the guide member 128 (see FIG. 14). When the biasing member 240 contacts the guide member 128, the biasing member 240 biases the weight member 122 in the first direction D1. The biasing member 240 biases the weight member 122 in the axial direction of the output shaft 15 and toward the holding member 124. Note that, before the guide member 128 is attached to the holding member 124, a surface 240D2 on the second direction D2 side of the urging member 240 protrudes toward the D2 side further than a surface 122D2 on the second direction D2 side of the weight member 122. Then, when the guide member 128 is attached to the holding member 124, the urging member 240 is compressed in the first direction D1. At this time, the surface 240D2 on the second direction D2 side of the urging member 240 may be flush with the surface 122D2 on the second direction D2 side of the weight member 122, or may protrude toward the second direction D2 further than the surface 122D2 on the second direction D2 side of the weight member 122 (in either case, the urging member 240 can urge the weight member 122 in the axial direction of the output shaft 15 and toward the holding member 124).

[0088] In the clutch device 10 of this embodiment, the biasing member 240 is made of an elastic body. According to the above aspect, the biasing member 240 is prevented from biasing the weight member 122 excessively.

[0089] In the clutch device 10 of this embodiment, the biasing member 240 is provided on the weight member 122. According to the above aspect, the biasing member 240 can more reliably bias a predetermined portion of the weight member 122 in the axial direction of the output shaft 15.

[0090] In the clutch device 10 of this embodiment, the biasing member 240 is provided at the center of the weight member 122 in the circumferential direction S. According to the above aspect, the biasing member 240 can bias the weight member 122 in the axial direction of the output shaft 15 in a balanced manner.

[0091] In the clutch device 10 of this embodiment, the biasing member 240 extends in the radial direction M. According to the above aspect, the biasing member 240 can bias the weight member 122 in the axial direction of the output shaft 15 in a more balanced manner.

[0092] In the clutch device 10 of this embodiment, at least a portion of the biasing member 240 is located inward M2 in the radial direction M from the first spherical member 131 and the second spherical member 132. According to the above aspect, the biasing member 240 can bias the weight member 122 in the axial direction of the output shaft 15 in a more balanced manner.

[0093] In the present embodiment, the biasing member 240 is provided on the surface of the weight member 122 on the second direction D2 side, but the present invention is not limited to this. For example, the biasing member 240 may be provided on the surface of the weight member 122 on the first direction D1 side, and bias the weight member 122 in the axial direction of the output shaft 15 and toward the guide member 128. In this way, the weight member 122 is always in contact with the guide member 128 by the biasing member 240, so that vibration of the weight member 122 in the axial direction of the output shaft 15 is more reliably suppressed even when there is vibration of the engine or the like.

[0094] Fifth Embodiment As shown in FIGS. 29A and 29B , a biasing member 440 according to the fourth embodiment is provided on the guide member 128. The biasing member 440 is provided on the first direction D1 side of the guide member 128. The biasing members 440 are provided on the guide portions 129A of the guide member 128. The biasing members 440 are located between the pair of first spherical members 131 in the circumferential direction S. The biasing members 440 are made of an elastic body. The biasing members 440 are made of, for example, rubber. The biasing members 440 extend in the radial direction M. The biasing members 440 have a flat plate shape. The biasing members 440 come into contact with the weight member 122. The biasing members 440 fit into grooves 122AH in the main body portion 122A of the weight member 122 and come into contact with the main body portion 122A. When the biasing member 440 comes into contact with the weight member 122, the biasing member 440 biases the weight member 122 in the first direction D1. The biasing member 440 biases the weight member 122 in the axial direction of the output shaft 15 and toward the holding member 124.

[0095] In the clutch device 10 of this embodiment, the centrifugal clutch mechanism 120 is located between the holding member 124 and the pressing member 126 in the axial direction of the output shaft 15, and includes a guide member 128 that guides movement of the weight member 122 in the radial direction M, and the biasing member 440 is provided on the guide member 128. According to the above aspect, the biasing member 440 can more reliably bias a predetermined portion of the weight member 122 in the axial direction of the output shaft 15.

[0096] In the clutch device 10 of this embodiment, the weight member 122 has a plurality of through holes 122H that penetrate in the axial direction of the output shaft 15, the centrifugal clutch mechanism 120 has a pair of first spherical members 131 that partially protrude from the openings of the through holes 122H and are configured to be rollable, and the biasing member 440 is located between the pair of first spherical members 131 in the circumferential direction S and extends in the radial direction M. According to the above aspect, the biasing member 440 can bias the weight member 122 in the axial direction of the output shaft 15 in a well-balanced manner.

[0097] Although the preferred embodiments of the present invention have been described above, the above-described embodiments are merely examples, and the present invention can be embodied in various other forms.

[0098] In each of the above-described embodiments, the weight member 122 includes the flat portions 122B located at both ends of the main body portion 122A in the circumferential direction S, but is not limited to this. The weight member 122 may include curved portions instead of the flat portions 122B.

[0099] In the above-described embodiments, the biasing portion 142 of the biasing member 140 biases the flat portion 122B of the weight member 122, but it may also bias the main body portion 122A instead of the flat portion 122B.

[0100] In the above-described embodiment, the pressure contact member 126 is formed separately from the clutch center 40, but it may be formed integrally with the second clutch center 51, for example. For example, it may be formed integrally with the flange 68 of the second clutch center 51.

[0101] In the above-described embodiment, the biasing members 140, 240, 440 are provided between the guide member 128 and the weight member 122, but this is not limiting. For example, the biasing members 140, 240, 440 may be disposed between the holding member 124 and the weight member 122. In this case, the biasing members 140, 240, 440 bias the weight member 122 in the axial direction of the output shaft 15 and toward the pressing member 126. The biasing members 140, 240, 440 press the first spherical member 131 of the centrifugal clutch mechanism 120 against the pressing member 126. In this case, the pressing member 126 is an example of an abutting member. [Explanation of symbols]

[0102] 10. Clutch device 15 Output shaft 20 Input side rotating plate 22 Output side rotating plate 30 Clutch housing 40 Clutch center 70 Pressure member 120 Centrifugal clutch mechanism 122 Weight member 122B Flat part 122H through hole 124 Retaining member 125 Engagement protrusion 126 Pressure welding member 128 Guide member 131 First spherical member 132 Second spherical member 135 Springs (elastic members) 140 biasing member 141 Fixed part 142 energizing section

Claims

1. A clutch device that transmits or cuts off the rotational driving force of an input shaft to an output shaft, a clutch center that is accommodated in a clutch housing that holds a plurality of input side rotary plates that are rotationally driven by the rotational drive of the input shaft, and that is rotationally driven together with the output shaft; a pressure member that is provided so as to be able to approach or move away from the clutch center and that is able to press the input side rotary plate and a plurality of output side rotary plates that are arranged alternately with the input side rotary plate; a centrifugal clutch mechanism having a plurality of weight members configured to be movable from a radially inner position to an outer position by centrifugal force accompanying rotation of the clutch housing, and which presses the input side rotating plate and the output side rotating plate together when the weight members are at the radially outer positions, thereby enabling transmission of the rotational drive force of the input shaft to the output shaft, and which releases the pressing force between the input side rotating plate and the output side rotating plate when the weight members are at the radially inner positions, thereby blocking transmission of the rotational drive force of the input shaft to the output shaft, The centrifugal clutch mechanism includes: a holding member that holds the weight member movably between an inner position in the radial direction and an outer position in the radial direction; a plurality of elastic members that urge the weight members inward in the radial direction, The holding member is a plurality of engaging projections positioned radially outward of the elastic member and engaging with the clutch housing; When viewed in the axial direction of the output shaft, all of the straight lines passing through the center of the output shaft and the circumferential center of the weight member pass through the engaging projection.

2. 2. The clutch device according to claim 1, wherein all of the straight lines pass through the circumferential center of the engaging projection when viewed in the axial direction.

3. 3. The clutch device according to claim 2, wherein the elastic members include, for one of the weight members, a first elastic member located on one side of the straight line in the circumferential direction, and a second elastic member located on the other side of the straight line in the circumferential direction.

4. The holding member is 2. The clutch device according to claim 1, further comprising a plurality of other engagement projections that are positioned between adjacent engagement projections in the circumferential direction, engage with the clutch housing, and through which the straight line does not pass.

Images