Clutch device

Abstract

To provide a clutch device in which damage to the engaging claws is suppressed. [Solution] The clutch device 10 includes a centrifugal clutch mechanism 120 having a weight member 130, the centrifugal clutch mechanism 120 includes a holding member 140 for holding the weight member 130, a spring 160 for biasing the weight member 130, and a pressure contact member 150 for pressing the input side rotating plate 20 and the output side rotating plate 22 into contact, the holding member 140 includes an engaging claw 143 that protrudes radially outward M1 from the outer peripheral edge 141E of the main body 141 and engages with the clutch housing 30, and a housing recess 145 for accommodating the weight member 130, the main body 141 includes a wall portion 141A located between the engaging claw 143 and the housing recess 145 with respect to the radial direction M, and a thickened portion 141T that protrudes radially inward M2 from the wall portion 141A and partitions a part of the housing recess 145.

Description

TECHNICAL FIELD

[0001] The present invention relates to a clutch device. BACKGROUND ART

[0002] Saddle-type vehicles such as motorcycles are provided with a clutch device capable of transmitting and interrupting the rotational driving force of a drive source such as an engine to drive wheels. For example, Patent Document 1 discloses a clutch device having an input member (hereinafter referred to as an input shaft) connected to the engine side, an output member (hereinafter referred to as an output shaft) connected to the drive wheel side, a clutch member (hereinafter referred to as a clutch center) connected to the output shaft, and a pressure member that can move toward or away from the clutch center.

[0003] Further, the clutch device of Patent Document 1 includes a centrifugal clutch mechanism provided with a weight member that moves in the radial direction and a holding member that accommodates the weight member. The holding member has engagement claws that engage with the clutch housing, and is configured to rotate together with the clutch housing. The engagement claws are located on the radially outer side of the weight member. The weight member moves from a radially inner position to a radially outer position by centrifugal force accompanying the rotation of the clutch housing, and is configured to transmit the driving force of the engine to the wheels by pressing a driving-side clutch plate (hereinafter referred to as an input-side rotating plate) and a driven-side clutch plate (hereinafter referred to as an output-side rotating plate) into pressure contact with each other. PRIOR ART DOCUMENTS PATENT DOCUMENTS

[0004] PATENT DOCUMENT 1 Japanese Unexamined Patent Publication No. 2022-30211 SUMMARY OF THE INVENTION PROBLEMS TO BE SOLVED BY THE INVENTION

[0005] Incidentally, since the rotational driving force of the clutch housing is transmitted to the retaining member via the engaging claws, the engaging claws are subjected to a relatively large load. If the engaging claws are damaged, a problem may arise in which the rotational driving force of the clutch housing cannot be sufficiently transmitted to the weight member. For this reason, there is a need for a clutch device that suppresses damage to the engaging claws.

[0006] The present invention has been made in view of the above, and its object is to provide a clutch device in which damage to the engaging claws is suppressed. [Means for solving the problem]

[0007] The inventors of this invention aimed to increase the torsional strength of the engaging claw by increasing its thickness. Furthermore, they discovered that a relatively large load is applied to the engaging claw by the load from the weight member, which is located radially inside the engaging claw, when it moves from its radially inside position to its radially outside position due to centrifugal force. Therefore, they aimed to improve the overall strength of the engaging claw by changing the shape of the area around the engaging claw.

[0008] The clutch device according to the present invention is a clutch device for transmitting or interrupting the rotational driving force of an input shaft to an output shaft, and comprises a clutch center housed 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 which rotates together with the output shaft; a pressure member provided so as to be able to approach or move away from the clutch center, which holds at least a portion of a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates, and which can press the input-side rotating plates and the output-side rotating plates; and a plurality of weight members configured to be movable from an inner position to an outer position in the radial direction by the centrifugal force accompanying the rotation of the clutch housing, wherein when the weight members are in the outer position in the radial direction, the input-side rotating plates and the output-side rotating plates are pressed together so as to be able to transmit the rotational driving force of the input shaft to the output shaft, and when the weight members are in the inner position in the radial direction, the pressing force between the input-side rotating plates and the output-side rotating plates is released so as to transmit 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 so as to be movable between an inner position in the radial direction and an outer position in the radial direction, a biasing member provided on the holding member that biases the weight member inward in the radial direction, and a contact member that moves in the axial direction of the output shaft as the weight member moves from the inner position in the radial direction to the outer position in the radial direction, thereby bringing the input side rotating plate and the output side rotating plate into contact, The retaining member comprises a ring-shaped body, an engaging claw protruding radially outward from the outer peripheral edge of the body and engaging with the clutch housing, and a housing recess formed in the body so as to be recessed in the axial direction of the output shaft and for accommodating the weight member so as to be movable in the radial direction. The body comprises a wall portion located between the engaging claw and the housing recess in the radial direction, and a thickened portion including a projection protruding radially inward from the wall portion and defining a part of the housing recess.

[0009] According to the clutch device of the present invention, the body of the retaining member has a thickened portion that includes a wall portion located radially between the engaging claw and the receiving recess, and a projection portion that protrudes radially inward from the wall portion and partitions a part of the receiving recess. In the above embodiment, since a thickened portion is provided between the engaging claw and the receiving recess, the radial thickness is increased by the amount of the thickened portion, and the rigidity of the engaging claw is increased. As a result, even if, for example, a weight member comes into contact with the projection portion, the rigidity of the engaging claw is improved, and damage to the engaging claw can be suppressed.

[0010] Another clutch device according to the present invention is a clutch device for transmitting or interrupting the rotational driving force of an input shaft to an output shaft, comprising: a clutch center housed in a clutch housing that holds a plurality of input-side rotating plates rotated by the rotational drive of the input shaft and rotates together with the output shaft; a pressure member provided so as to be able to approach or move away from the clutch center, holding at least a portion of a plurality of output-side rotating plates arranged alternately with the input-side rotating plates, and capable of pressing the input-side rotating plates and the output-side rotating plates; and a plurality of weight members configured to be movable from an inner radial position to an outer radial position by the centrifugal force accompanying the rotation of the clutch housing, wherein when the weight members are in the outer radial position, the input-side rotating plates and the output-side rotating plates are pressed together, enabling the transmission of the rotational driving force of the input shaft to the output shaft, and when the weight members are in the inner radial position, the pressure between the input-side rotating plates and the output-side rotating plates is released, enabling the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism comprises a holding member that holds the weight member so as to be movable between an inner position in the radial direction and an outer position in the radial direction, a biasing member provided on the holding member that biases the weight member inward in the radial direction, and a contact member that moves in the axial direction of the output shaft as the weight member moves from the inner position in the radial direction to the outer position in the radial direction, thereby pressing the input side rotating plate and the output side rotating plate into contact, wherein the holding member is The device comprises a ring-shaped body, an engaging claw protruding radially outward from the outer peripheral edge of the body and engaging with the clutch housing, and a housing recess formed in the body so as to be recessed in the axial direction of the output shaft and accommodating the weight member so as to be movable in the radial direction, wherein the body includes a wall portion located between the engaging claw and the housing recess in the radial direction, and the radial length of the wall portion is longer than the radial length from the outer peripheral edge of the body to the radially outer end of the engaging claw.

[0011] According to another clutch device of the present invention, the body of the retaining member has a wall portion located radially between the engaging claw and the receiving recess, and the radial length of the wall portion is longer than the radial length from the outer peripheral edge of the body to the radially outer end of the engaging claw. According to the above embodiment, the rigidity of the engaging claw is increased because the wall portion is relatively thick. As a result, even if, for example, a weight member comes into contact with the wall portion, the rigidity of the engaging claw is improved, and damage to the engaging claw can be suppressed. [Effects of the Invention]

[0012] According to the present invention, it is possible to provide a clutch device in which damage to the engaging claws is suppressed. [Brief explanation of the drawing]

[0013] [Figure 1] Figure 1 is a cross-sectional view of a clutch device according to the first embodiment. [Figure 2] Figure 2 is a perspective view of the first clutch center according to the first embodiment. [Figure 3] Figure 3 is a perspective view of the first clutch center according to the first embodiment. [Figure 4] Figure 4 is a perspective view of the second clutch center according to the first embodiment. [Figure 5] Figure 5 is a plan view of the second clutch center according to the first embodiment. [Figure 6] Figure 6 is a perspective view of the pressure member according to the first embodiment. [Figure 7] Figure 7 is a perspective view of the pressure member according to the first embodiment. [Figure 8A] Figure 8A is a schematic diagram illustrating the operation of the center-side assist cam surface and the pressure-side assist cam surface. [Figure 8B] Figure 8B is a schematic diagram illustrating the operation of the center slipper cam surface and the pressure slipper cam surface. [Figure 9A]FIG. 9A is a perspective view showing a part of the centrifugal clutch mechanism according to the first embodiment, and is a plan view showing a state where the weight member is positioned radially inward. [Figure 9B] FIG. 9B is a plan view showing a part of the centrifugal clutch mechanism according to the first embodiment, and is a plan view showing a state where the weight member is positioned radially inward. [Figure 10] FIG. 10 is a plan view showing the holding member according to the first embodiment. [Figure 11] FIG. 11 is a perspective view showing the holding member according to the first embodiment. [Figure 12A] FIG. 12A is an enlarged plan view showing a part of the holding member according to the first embodiment. [Figure 12B] FIG. 12B is an enlarged plan view showing a part of the holding member according to the first embodiment. [Figure 13] FIG. 13 is a perspective view showing the weight member according to the first embodiment. [Figure 14] FIG. 14 is a plan view showing the weight member according to the first embodiment. [Figure 15] FIG. 15 is a perspective view showing the weight member according to the first embodiment. [Figure 16] FIG. 16 is a bottom view showing the weight member according to the first embodiment. [Figure 17] FIG. 17 is a side view showing the weight member according to the first embodiment. [Figure 18] FIG. 18 is a plan view showing a part of the centrifugal clutch mechanism according to the first embodiment, and is a plan view showing a state where the weight member is positioned radially outward. [Figure 19] FIG. 19 is an enlarged plan view showing a state where the weight member is positioned radially outward. [Figure 20] FIG. 20 is a cross-sectional view showing a part of the clutch device according to the first embodiment, and is a cross-sectional view showing a state where the weight member is positioned radially inward. [Figure 21] FIG. 21 is a cross-sectional view showing a part of the clutch device according to the first embodiment, and is a cross-sectional view showing a state where the weight member is positioned radially outward. [Figure 22] Figure 22 is a cross-sectional view of the clutch device according to the second embodiment. [Figure 23] Figure 23 is a perspective view showing a retaining member according to the second embodiment. [Figure 24] Figure 24 is a perspective view showing a weight member according to the second embodiment. [Figure 25] Figure 25 is a bottom view showing the weight member according to the second embodiment. [Figure 26] Figure 26 is a side view showing a weight member according to the second embodiment. [Figure 27] Figure 27 is a cross-sectional view showing a part of the clutch device according to the second embodiment, and is a cross-sectional view showing the state in which the weight member is located radially inward. [Figure 28] Figure 28 is a cross-sectional view showing a part of the clutch device according to the second embodiment, and is a cross-sectional view showing the state in which the weight member is located radially outward. [Figure 29] Figure 29 is a plan view showing a part of the centrifugal clutch mechanism according to the second embodiment, and is a plan view showing the state in which the weight member is located radially inward. [Figure 30] Figure 30 is a plan view showing a part of the centrifugal clutch mechanism according to the second embodiment, and is a plan view showing the state in which the weight member is located radially outward. [Figure 31] Figure 31 is an enlarged plan view showing the state in which the weight member of the clutch device according to the third embodiment is located radially inward. [Figure 32] Figure 32 is a plan view showing a part of the centrifugal clutch mechanism according to the fourth embodiment, and is a plan view showing the state in which the weight member is located radially inward. [Figure 33A] Figure 33A is a graph showing the relationship between engine speed and the positions of the first and second weight members. [Figure 33B] Figure 33B is a graph showing the relationship between engine speed and the position of the pressure-welded member. [Figure 34]Figure 34 is a plan view showing a part of the centrifugal clutch mechanism according to the fifth embodiment, and is a plan view showing the state in which the weight member is located radially inward. [Figure 35] Figure 35 is a plan view showing a part of the centrifugal clutch mechanism according to the sixth embodiment, and is a plan view showing the state in which the weight member is located radially inward. [Figure 36] Figure 36 is a plan view showing a part of the centrifugal clutch mechanism according to the seventh embodiment, and is a plan view showing the state in which the weight member is located radially inward. [Figure 37] Figure 37 is a cross-sectional view showing the centrifugal clutch mechanism and its surroundings according to the eighth embodiment. [Figure 38] Figure 38 is a plan view showing a part of the centrifugal clutch mechanism according to the eighth embodiment, and is a plan view showing the state in which the weight member is located radially inward. [Figure 39] Figure 39 is a perspective view showing the weight member and spring according to the eighth embodiment. [Figure 40] Figure 40 is a perspective view showing a pressure-welded member according to the eighth embodiment. [Figure 41] Figure 41 is a schematic diagram showing a part of the centrifugal clutch mechanism according to the first modified example. [Figure 42] Figure 42 is a schematic diagram showing a part of the centrifugal clutch mechanism according to the second modified example. [Modes for carrying out the invention]

[0014] Hereinafter, embodiments of the clutch device according to the present invention will be described with reference to the drawings. Naturally, the embodiments described herein are not intended to particularly limit the present invention. Furthermore, the same reference numerals are used for members and parts that perform the same function, and redundant explanations are omitted or simplified as appropriate.

[0015] <First Embodiment> Figure 1 is a cross-sectional view of the clutch device 10 according to this embodiment. The clutch device 10 is installed in a saddle-type vehicle such as a motorcycle. The clutch device 10 is a device that transmits or interrupts the rotational driving force of the input shaft (crankshaft) of an engine, which is an example of a drive source for a motorcycle, to the output shaft 15. The clutch device 10 is a device for transmitting or interrupting the rotational driving force of the input shaft to the drive wheel (rear wheel) via the output shaft 15. The clutch device 10 is positioned between the engine and the transmission.

[0016] 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 denoted as direction D, the direction in which the pressure member 70 approaches the clutch center 40 is denoted as the first direction D1, and the direction in which the pressure member 70 moves away from the clutch center 40 is denoted as the second direction D2. Furthermore, the circumferential direction (i.e., rotational direction) of the clutch center 40 and the pressure member 70 is denoted as the circumferential direction S, the direction from one center-side cam portion 60 toward the other center-side cam portion 60 (the direction from one pressure-side cam portion 90 toward the other pressure-side cam portion 90) toward the first circumferential direction S1 (see Figure 2), and the direction from the other center-side cam portion 60 toward the one center-side cam portion 60 (the direction from the other pressure-side cam portion 90 toward the one pressure-side cam portion 90) toward the second circumferential direction S2 (see Figure 2). Furthermore, 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 outward direction M1 (see Figure 20), and the direction toward the output shaft 15 is defined as the inward direction M2 (see Figure 20). In this embodiment, the axial direction of the output shaft 15 is the same as direction D. Also, the pressure member 70 and the clutch center 40 rotate in the 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 configuration of the clutch device 10 in any way, nor do they limit the present invention in any way.

[0017] As shown in Figure 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 180.

[0018] As shown in Figure 1, the output shaft 15 is a hollow shaft. One end of the output shaft 15 rotatably supports the input gear 35 and clutch housing 30, which will be described later, via a needle bearing 28A. The output shaft 15 fixedly supports the 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 motorcycle transmission (not shown).

[0019] As shown in Figure 1, the output shaft 15 has a main body portion 15A extending in direction D. The main body portion 15A has an oil passage 15H through which clutch oil flows. The oil passage 15H is formed between the sleeve 16C, which is fitted onto the push rod 16A (described later), and the main body portion 15A. The clutch oil flows inside the output shaft 15, that is, within the oil passage 15H of the main body portion 15A.

[0020] As shown in Figure 1, the oil passage 15H of the output shaft 15 is provided with a push rod 16A and a push member 16B adjacent to the push rod 16A. The push rod 16A and the push member 16B are slidably mounted within the sleeve 16C. One end of the push rod 16A (the left end in the figure) is connected to the clutch operating lever (not shown) of a motorcycle, and operation of the clutch operating lever causes it to slide within the sleeve 16C and press the push member 16B in a 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 passage 15H.

[0021] The clutch housing 30 is formed from die-cast aluminum. The clutch housing 30 is formed in a bottomed cylindrical shape. As shown in Figure 1, the clutch housing 30 has a substantially circular bottom wall 31 and a side wall 33 extending from the edge of the bottom wall 31 in a second direction D2. The clutch housing 30 holds a plurality of input-side rotating plates 20.

[0022] As shown in Figure 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 rivets 35B via a torque damper 35A. The input gear 35 meshes with a drive gear (not shown) that rotates due to the rotational drive of the engine's input shaft. The input gear 35 rotates independently of the output shaft 15 and integrally with the clutch housing 30.

[0023] The input-side rotating plate 20 is rotationally driven by the rotational drive of the input shaft. As shown in Figure 1, the input-side rotating plate 20 is held on the inner circumferential 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 (i.e., direction D) of the clutch housing 30. The input-side rotating plate 20 is provided so as to be rotatable integrally with the clutch housing 30.

[0024] The input-side rotating plate 20 is a component 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 made of die-cast aluminum. A friction material (not shown) consisting of multiple pieces of paper is attached to the front and back surfaces of the input-side rotating plate 20. Grooves several hundred micrometers deep are formed between the friction material to hold clutch oil.

[0025] As shown in Figure 1, the clutch center 40 is housed in the clutch housing 30. The clutch center 40 is positioned 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 are arranged alternately with the input-side rotating plates 20 in direction D. The clutch center 40 is rotationally driven together with the output shaft 15. The clutch center 40 comprises a first clutch center 41 and a second clutch center 51. The first clutch center 41 and the second clutch center 51 are assembled with each other. The second clutch center 51 is located radially outward M1 of the first clutch center 41. The second clutch center 51 is fitted onto the first clutch center 41.

[0026] As shown in Figure 2, the first clutch center 41 includes an output shaft holding portion 42, an annular base wall 43 located radially outward M1 of the output shaft holding portion 42, and a plurality of center-side cam portions 60.

[0027] As shown in Figure 1, the output shaft 15 is connected to the output shaft holder 42. As shown in Figure 2, the output shaft holder 42 is formed in a cylindrical shape. The output shaft holder 42 has 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 holder 42. The inner wall 45A of the output shaft holder 42 that partitions the insertion hole 45 has a plurality of fitting teeth 47 that extend in the axial direction (i.e., direction D) of the output shaft 15. The fitting teeth 47 engage with the output shaft 15.

[0028] The center-side cam portion 60 is formed in a trapezoidal shape and has a cam surface consisting of an inclined surface that constitutes an assist & slipper (registered trademark) mechanism that generates 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 slipper torque, which is a force that decreases the pressing force (contact force) between the input-side rotating plate 20 and the output-side rotating plate 22, causing the system to transition to a half-clutch state. The half-clutch state is a state between the state in which the clutch is fully engaged (i.e., the state in which the input-side rotating plate 20 and the output-side rotating plate 22 are pressed against each other) and the state in which the clutch is fully disengaged (i.e., the state in which the input-side rotating plate 20 and the output-side rotating plate 22 are separated from each other). As shown in Figure 2, the center-side cam portion 60 is formed to protrude in the second direction D2 from the surface 43D2 of the base wall 43 on the second direction D2 side. 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.

[0029] As shown in Figure 2, the center-side cam portion 60 is located radially outward M1 of the output shaft holding portion 42. The center-side cam portion 60 has a center-side assist cam surface 60A (see also Figure 3) and a center-side slipper cam surface 60S. The center-side assist cam surface 60A is configured to generate a force (here, a first direction D1) toward the clutch center 40 in order to increase the pressing force (compression force) between the input-side rotating plate 20 and the output-side rotating plate 22 when it rotates relative to the pressure member 70, such as when accelerating. In this embodiment, when the above force is generated, the position of the pressure member 70 relative to the clutch center 40 does not change, and it is not necessary for the pressure member 70 to physically approach the clutch center 40. However, the pressure member 70 may be physically displaced relative to the clutch center 40. The center slipper cam surface 60S is configured to separate the pressure member 70 from the clutch center 40 in order to reduce the pressing force (contact force) between the input rotating plate 20 and the output rotating plate 22 when it rotates relative to the pressure member 70, such as when decelerating. In adjacent center cam portions 60 with respect to the circumferential direction S, the center assist cam surface 60A of one center cam portion 60L and the center slipper cam surface 60S of the other center cam portion 60M are arranged facing each other in the circumferential direction S.

[0030] As shown in Figure 2, the first clutch center 41 is provided with a plurality (three in this embodiment) of boss portions 62. 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 radially outward M1 from the output shaft holding portion 42. 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. With respect to the circumferential direction S, the boss portions 62 are provided between the center-side assist cam surface 60A and the center-side slipper cam surface 60S. The boss portions 62 have screw holes 62H into which a bolt 28 (see Figure 1) is inserted. The screw holes 62H extend in the axial direction (i.e., direction D) of the clutch center 40.

[0031] As shown in Figures 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 extends radially M from the side of the output shaft holding portion 42. The center-side cam hole 43H is located between adjacent center-side cam portions 60 with respect to the circumferential direction S. 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.

[0032] As shown in Figure 2, the first clutch center 41 has a plurality of engagement grooves 49. The engagement grooves 49 are formed on the outer circumferential surface of the base wall 43. The engagement grooves 49 are recessed radially inward M2 from the outer circumferential surface of the base wall 43.

[0033] As shown in Figure 4, the second clutch center 51 comprises an annular outer peripheral wall 52, a flange 68 extending radially outward M1 from the outer peripheral wall 52, and a center-side fitting portion 54. The second clutch center 51 holds an input-side rotating plate 20 and a plurality of output-side rotating plates 22 arranged alternately in direction D. The flange 68 is configured to press against the input-side rotating plate 20 and the output-side rotating plates 22.

[0034] As shown in Figure 4, a spline fitting portion 56 is provided on the outer circumferential surface of the outer circumferential wall 52. The spline fitting portion 56 has a plurality of center-side fitting teeth 57 extending in the axial direction (i.e., direction D) of the second clutch center 51 along the outer circumferential surface of the outer circumferential wall 52, a plurality of spline grooves 58 formed between adjacent center-side fitting teeth 57 and extending in the axial direction (i.e., direction D) of the second clutch center 51, and an oil discharge hole 59. The center-side fitting teeth 57 hold the output-side rotating plate 22. The plurality of center-side fitting teeth 57 are arranged in the circumferential direction S. The plurality of center-side fitting teeth 57 are formed at equal intervals in the circumferential direction S. The plurality of center-side fitting teeth 57 are formed to have the same shape. The center-side fitting teeth 57 protrude radially outward M1 from the outer circumferential surface of the outer circumferential wall 52. The oil discharge hole 59 is formed by penetrating the outer circumferential wall 52 radially M. The oil discharge hole 59 is formed between adjacent center-side fitting teeth 57. That is, the oil discharge hole 59 is formed in the spline groove 58. The oil discharge hole 59 is formed in the center-side fitting portion 54. The oil discharge hole 59 connects the inside and outside of the second clutch center 51. The oil discharge hole 59 is a hole that discharges clutch oil, etc., that has flowed out from the output shaft 15 into the clutch center 40 to the outside of the clutch center 40. The clutch oil discharged from the oil discharge hole 59 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22 located radially outward M1 of the oil discharge hole 59.

[0035] 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 spline fitting to the center-side fitting teeth 57 and spline groove 58 of the second clutch center 51. Another portion of the output-side rotating plate 22 is held by the pressure-side fitting teeth 87 (see Figure 6), which will be described later, of the pressure member 70. The output-side rotating plate 22 is provided so as to be displaceable along the axial direction (i.e., direction D) of the clutch center 40. The output-side rotating plate 22 is provided so as to be rotatable integrally with the clutch center 40. The output-side rotating plate 22 is provided so as to be displaceable along the axial direction (i.e., direction D) of the pressure member 70. The output-side rotating plate 22 is provided so as to be rotatable integrally with the pressure member 70.

[0036] The output-side rotating plate 22 is a component that is pressed against the input-side rotating plate 20. The output-side rotating plate 22 is formed in an annular shape. The output-side rotating plate 22 is formed by punching out an annular shape from a thin sheet 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 it may be provided on both the input-side rotating plate 20 and the output-side rotating plate 22.

[0037] As shown in Figure 4, the center-side fitting portion 54 is formed on the inner 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 portion 15T of the output shaft 15 (see Figure 1) to the pressure-side fitting portion 88. That is, a gap is formed between the center-side fitting portion 54 and the pressure-side fitting portion 88.

[0038] As shown in Figures 4 and 5, the second clutch center 51 has a plurality of engaging projections 55. The engaging projections 55 engage with the engaging grooves 49 (see Figure 2) of the first clutch center 41. The engaging projections 55 are formed on the inner surface of the outer peripheral wall 52. The engaging projections 55 protrude radially inward M2 from the inner surface of the outer peripheral wall 52.

[0039] As shown in Figure 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 relative to the clutch center 40. The pressure member 70 is configured to be able to press the input side rotating plate 20 and the output side rotating plate 22. The pressure member 70 is positioned concentrically with the clutch center 40 and the clutch housing 30. The pressure member 70 is fitted inside the second clutch center 51. This positions the pressure member 70 radially in the direction M. The pressure member 70 is provided so as to be able to slide relative to the first clutch center 41 and the second clutch center 51 in the direction D. The pressure member 70 and the first clutch center 41 and the second clutch center 51 are configured to rotate relative to each other in the circumferential direction S. As shown in Figure 6, the pressure member 70 has a main body 72 and a flange 98 that is connected to the outer peripheral edge of the main body 72 on the second direction D2 side and extends radially outward M1. The main body 72 protrudes further in the first direction D1 than the flange 98. The flange 98 is located at the outer diameter end of the pressure member 70. The flange 98 is located radially outward M1 than the cylindrical portion 80 (see also Figure 7), which will be described later. The pressure member 70 holds at least a portion of the multiple output-side rotating plates 22 that are arranged alternately with the input-side rotating plate 20. The flange 98 is configured to press against the input-side rotating plate 20 and the output-side rotating plates 22.

[0040] As shown in Figure 6, the main body 72 comprises a cylindrical portion 80, a plurality of pressure-side cam portions 90, a pressure-side fitting portion 88, and a spring housing portion 84 (see Figure 7).

[0041] The cylindrical portion 80 is formed in a cylindrical shape. The cylindrical portion 80 is formed integrally with the pressure-side cam portion 90. The cylindrical portion 80 houses the tip portion 15T (see Figure 1) of the output shaft 15. The release bearing 18 (see Figure 1) is housed in the cylindrical portion 80. The cylindrical portion 80 is the part that receives the pressing force from the push member 16B. The cylindrical portion 80 is the part that receives the clutch oil that flows out from the tip portion 15T of the output shaft 15.

[0042] As shown in Figure 6, the pressure-side cam portion 90 is formed in a trapezoidal shape and has a cam surface consisting of an inclined surface that slides against the center-side cam portion 60 to generate assist torque or slipper torque, forming an assist & slipper (registered trademark) mechanism. The pressure-side cam portion 90 is formed to protrude from the flange 98 in the first direction D1. The pressure-side cam portions 90 are arranged at equal intervals in the circumferential direction S of the pressure member 70. In this embodiment, the pressure member 70 has three pressure-side cam portions 90, but the number of pressure-side cam portions 90 is not limited to three.

[0043] As shown in Figure 6, the pressure-side cam portion 90 is located radially M1 outward from the cylindrical portion 80. The pressure-side cam portion 90 has a pressure-side assist cam surface 90A (see also Figure 7) and a pressure-side slipper cam surface 90S. The pressure-side assist cam surface 90A is configured to be in contact with the center-side assist cam surface 60A. The pressure-side assist cam surface 90A is configured to generate a force in the direction toward the clutch center 40 (here, the first direction D1) from the pressure member 70 to increase the pressing force (compression force) between the input-side rotating plate 20 and the output-side rotating plate 22 when it rotates relative to the clutch center 40, such as when accelerating. The pressure-side slipper cam surface 90S is configured to be in contact with the center-side slipper cam surface 60S. The pressure-side slipper cam surface 90S is configured to separate the pressure member 70 from the clutch center 40 in order to reduce the pressing force (contact force) between the input-side rotating plate 20 and the output-side rotating plate 22 when it rotates relative to the clutch center 40, such as when decelerating. In adjacent pressure-side cam portions 90 with respect to 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 facing each other in the circumferential direction S.

[0044] Here, the operation of the center-side cam portion 60 and the pressure-side cam portion 90 will be explained. When the engine speed increases and the rotational driving force input to the input gear 35 and 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 Figure 8A. As a result, the operation of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A generates a force in the first direction D1 on the pressure member 70, increasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22.

[0045] 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, resulting in back torque, a first rotational force in the circumferential direction S1 is applied to the clutch center 40, as shown in Figure 8B. As a result, the action of the center-side slipper cam surface 60S and the pressure-side slipper cam surface 90S moves the pressure member 70 in the second direction D2, releasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22. This prevents malfunctions in the engine and transmission caused by back torque.

[0046] As shown in Figure 6, the pressure-side fitting portion 88 is located radially outward M1 from the pressure-side cam portion 90. The pressure-side fitting portion 88 is located in a second direction D2 towards 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 Figure 4).

[0047] As shown in Figures 6 and 7, the pressure member 70 has a pressure-side cam hole 83H that penetrates the main body 72 and a portion of the flange 98. The pressure-side cam hole 83H is located radially M1 outward from the cylindrical portion 80. The pressure-side cam hole 83H extends radially M from the side of the cylindrical portion 80 to radially M1 outward from the pressure-side fitting portion 88. 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. Viewed from the axial direction of the pressure member 70, the pressure-side assist cam surface 90A and a portion of the pressure-side cam hole 83H overlap. The boss portion 62 of the first clutch center 41 (see Figure 2) is inserted into the pressure-side cam hole 83H. The boss portion 62 penetrates the pressure-side cam hole 83H.

[0048] As shown in Figure 6, the pressure member 70 is provided with a plurality of pressure-side mating teeth 87 located on the flange 98. The pressure-side mating teeth 87 hold at least a portion of the output-side rotating plate 22. The pressure-side mating teeth 87 protrude from the flange 98 in a first direction D1. The pressure-side mating teeth 87 are located radially M1 outward from the cylindrical portion 80. The pressure-side mating teeth 87 are located radially M1 outward from the pressure-side cam portion 90. The pressure-side mating teeth 87 are located radially M1 outward from the pressure-side mating portion 88. The plurality of pressure-side mating teeth 87 are aligned in the circumferential direction S. The plurality of pressure-side mating 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 that area is wider, but the other adjacent pressure-side fitting teeth 87 are arranged at equal intervals. As shown in Figure 1, the pressure-side fitting teeth 87 hold the end plate 21. The end plate 21 is a plate used to adjust the distance in direction D between the input-side rotating plate 20 and the output-side rotating plate 22 (i.e., the axial distance of the output shaft 15) when the weight member 130 of the centrifugal clutch mechanism 120, which will be described later, is at position PI in the inner M2 direction radially M.

[0049] As shown in Figure 7, the spring housing portion 84 is formed in the pressure-side cam portion 90. The spring housing portion 84 is located radially outward M1 from the cylindrical portion 80. The spring housing portion 84 is formed to be recessed from the second direction D2 to the first direction D1. The spring housing portion 84 is formed in a circular shape. The spring housing portion 84 houses the clutch spring 25.

[0050] As shown in Figure 1, the clutch spring 25 is housed in the spring housing 84. The end 25D1 of the clutch spring 25 in the first direction D1 is in contact with the pressure member 70. The end 25D2 of the clutch spring 25 in the second direction D2 is in contact with the stopper plate 100. The clutch spring 25 biases the pressure member 70 toward the clutch center 40 (i.e., toward the first direction D1). The clutch spring 25 is, for example, a coil spring made by winding spring steel in a spiral shape. The clutch spring 25 extends in direction D.

[0051] As shown in Figure 1, the centrifugal clutch mechanism 120 is provided within the clutch housing 30. The centrifugal clutch mechanism 120 is located 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 Figure 9A, the centrifugal clutch mechanism 120 has a plurality of weight members 130, a holding member 140, a pressure contact member 150 (see Figure 1), a spring 160 (see also Figure 9B), and a contact member 170 (see also Figure 1). When the weight members 130 are at position PO on the outer side M1 in the radial direction M (see Figures 1 and 21), the centrifugal clutch mechanism 120 presses the input side rotating plate 20 and the output side rotating plate 22 into contact, enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15. The centrifugal clutch mechanism 120 is configured to release the contact force between the input-side rotating plate 20 and the output-side rotating plate 22 when the weight member 130 is at position PI, which is M2 on the inside of the radial direction M (see Figure 20), thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15. The centrifugal clutch mechanism 120 is configured to be able to press the auxiliary clutch plate 180 (see Figure 1).

[0052] As shown in Figure 9B, the retaining member 140 holds the weight member 130 so that it can move between a position PI on the inside M2 ​​in the radial direction M and a position PO on the outside M1 in the radial direction M (see Figure 18). The retaining member 140 is formed in an annular shape. The retaining member 140 is made of die-cast aluminum. The retaining member 140 comprises a main body 141, a plurality of engaging claws 143, a plurality of receiving recesses 145, and a pressing portion 149 (see Figure 1).

[0053] As shown in Figure 10, the main body 141 is formed in a ring shape. As shown in Figure 12A, the main body 141 has a wall portion 141A and a thickened portion 141T including a protruding portion 141B. The wall portion 141A is located between the engaging claw 143 and the receiving recess 145 with respect to the radial direction M. The protruding portion 141B protrudes from the wall portion 141A inward M2 in the radial direction M. The protruding portion 141B partitions a part of the receiving recess 145. The inner end 141BX of the protruding portion 141B in the radial direction M2 is located inward M2 in the radial direction M than the outer end 145X of the receiving recess 145 in the radial direction M1. As shown in Figure 9B, the protruding portion 141B is located between the first spring 161 and the second spring 162, which will be described later, with respect to the circumferential direction S. The dashed line 141EL in Figure 12B indicates the outer edge 141E. The dashed line 145XL in Figure 12B represents a straight line that passes through the outer end M1 of the receiving recess 145 in the radial direction M and is perpendicular to the radial direction M when viewed from the axial direction of the output shaft 15. The dashed line 141BXL in Figure 12B represents a straight line that passes through the inner end M2 of the protrusion 141B in the radial direction M and is perpendicular to the radial direction M when viewed from the axial direction of the output shaft 15.

[0054] As shown in Figure 10, the engaging claw 143 protrudes radially outward M1 from the outer peripheral edge 141E of the main body 141. The engaging claw 143 is integrally formed with the main body 141. The engaging claw 143 engages with the clutch housing 30 (see Figure 1). Multiple engaging claws 143 are arranged in the circumferential direction S. As shown in Figure 12A, the engaging claw 143 has a head portion 143A and a root portion 143B located radially inward from the head portion 143A. The circumferential length LA of the head portion 143A is longer than the circumferential length LB of the root portion 143B.

[0055] As shown in Figure 1, the housing recess 145 is formed in the main body 141 so as to be recessed in the axial direction (i.e., direction D) of the output shaft 15. The housing recess 145 is recessed in the first direction D1. The housing recess 145 houses the weight member 130 so as to be movable in the radial direction M. Multiple housing recesses 145 are arranged in the circumferential direction S. As shown in Figures 10 and 11, the housing recess 145 is provided with a sliding surface 145M on which the weight member 130 slides when the weight member 130 moves in the radial direction M. The housing recess 145 has a housing groove 146 formed therein for housing a part of the spring 160. The housing groove 146 extends in the radial direction M. The housing groove 146 includes a first housing groove 146A for housing the first spring 161, which will be described later, and a second housing groove 146B for housing the second spring 162. The first housing groove 146A is located on the first circumferential direction S1 side of the protrusion 141B. The second housing groove 146B is located on the second circumferential direction S2 side of the protrusion 141B. One end of the first spring 161 and the second spring 162 abut against the outer end 145X of the housing recess 145 on the radial direction M1. As shown in Figure 19, the housing recess 145 is provided with a pressing surface 145H that is pressed by the weight member 130 when the weight member 130 is at position PO on the radial direction M1. A stress is applied to the pressing surface 145H from the weight member 130 on the radial direction M1. The engaging claw 143 and the pressing surface 145H are offset with respect to the circumferential direction S. Here, the engaging claw 143 is positioned between a pair of pressing surfaces 145H with respect to the circumferential direction S. Furthermore, the receiving recess 145 may have a through hole formed therein that penetrates the main body 141 in the axial direction (i.e., direction D) of the output shaft 15. In this case, the clutch oil flowing outside the retaining member 140 flows into the receiving recess 145 through the through hole.

[0056] As shown in Figure 12A, the circumferential length S1 of the projection 141B is greater than or equal to the circumferential length S2 of the engaging claw 143. The radial length M3 from the outer peripheral edge 141E of the main body 141 to the inner end M2 of the projection 141BX in the radial direction M is longer than the radial length M4 from the outer peripheral edge 141E of the main body 141 to the outer end M1 of the engaging claw 143X in the radial direction M. The first circumferential end S1 141BL of the projection 141B is located on the first circumferential direction S1 side than the first circumferential end S1 143AL of the engaging claw 143. Here, the first circumferential end S1 143AL of the engaging claw 143 is the first circumferential end S1 of the head 143A. The end portion 141BR of the projection 141B in the second circumferential direction S2 is located on the second circumferential direction S2 side of the engaging claw 143 than the end portion 143AR of the engaging claw 143 in the second circumferential direction S2. Here, the end portion 143AR of the engaging claw 143 in the second circumferential direction S2 is the end portion of the head portion 143A in the second circumferential direction S2. Also, the end portion 141BL of the projection 141B in the first circumferential direction S1 is located on the first circumferential direction S1 side of the root portion 143B than the end portion 143BL of the root portion 143B in the first circumferential direction S1. The end portion 141BR of the projection 141B in the second circumferential direction S2 is located on the second circumferential direction S2 side of the root portion 143B than the end portion 143BR of the root portion 143B. The surfaces of the wall portion 141A, the projection 141B, and the engaging claw 143 on the side facing the pressure contact member 150 are formed flush. Note that the dashed line 143XL in Figure 12B represents a straight line that passes through the outer end 143X of the engaging claw 143 in the radial direction M1 and is perpendicular to the radial direction M when viewed from the axial direction of the output shaft 15. The dashed line 141BLL in Figure 12B represents a straight line that passes through the end 141BL of the protruding portion 141B in the first circumferential direction S1 and is parallel to the radial direction M when viewed from the axial direction of the output shaft 15. The dashed line 143ALL in Figure 12B represents a straight line that passes through the end 143AL of the engaging claw 143 in the first circumferential direction S1 and is parallel to the radial direction M when viewed from the axial direction of the output shaft 15. The dashed line 143BLL in Figure 12B represents a straight line that passes through the end 143BL of the root portion 143B in the first circumferential direction S1 and is parallel to the radial direction M when viewed from the axial direction of the output shaft 15. The dashed line 141BRL in Figure 12B represents a straight line that passes through the second circumferential end 141BR of the projection 141B in the circumferential direction S2 and is parallel to the radial direction M when viewed from the axial direction of the output shaft 15.The dashed line 143ARL in Figure 12B represents a straight line that passes through the second circumferential end 143AR of the engaging claw 143 in the circumferential direction S2 and is parallel to the radial direction M when viewed from the axial direction of the output shaft 15. The dashed line 143BRL in Figure 12B represents a straight line that passes through the second circumferential end 143BR of the root portion 143B in the circumferential direction S2 and is parallel to the radial direction M when viewed from the axial direction of the output shaft 15.

[0057] As shown in Figure 9B, the multiple weight members 130 are arranged in the circumferential direction S. The weight members 130 are configured to move from an inner position M2 PI in the radial direction M to an outer position due to the centrifugal force accompanying the rotation of the clutch housing 30. The weight members 130 are configured to press the contact member 150 toward a second direction D2. As shown in Figure 20, when no centrifugal force is applied, the weight member 130 is held at an inner position M2 PI in the radial direction M by the spring 160 (see Figure 9B). As shown in Figure 21, when centrifugal force is applied, the weight member 130 moves toward an outer position M1 in the radial direction M against the biasing force of the spring 160, and moves to an outer position M1 PO in the radial direction M. At this time, as shown in Figure 19, the weight member 130 presses the pressing surface 145H of the receiving recess 145, but the weight member 130 does not come into contact with the protrusion 141B of the holding member 140. The weight member 130 is housed in the receiving recess 145 of the holding member 140. As shown in Figure 15, the weight member 130 includes a biasing member holding portion 131, a first plane 133 provided on one side of the biasing member holding portion 131 in the circumferential direction S, a second plane 135 provided on the other side of the biasing member holding portion 131 in the circumferential direction S, and a weight-side inclined surface 130F (see Figure 13) located on the opposite side of the first plane 133 and the second plane 135 with respect to the axial direction (i.e., direction D) of the output shaft 15. The weight-side inclined surface 130F is an example of a weight-side sliding portion.

[0058] The biasing member holder 131 holds the spring 160. As shown in Figure 15, the biasing member holder 131 is a recessed groove that extends from a first direction D1 to a second direction D2 and from the outer M1 to the inner M2 in the radial direction M. The biasing member holder 131 includes a retaining wall 132 that holds the inner M2 end of the spring 160 in the radial direction M. In this embodiment, the biasing member holder 131 includes a first biasing member holder 131A that holds a first spring 161, which will be described later, and a second biasing member holder 131B that holds a second spring 162, which will be described later.

[0059] As shown in Figures 15 and 16, the first plane 133 is located on the first circumferential direction S1 side of the biasing member holding portion 131. More specifically, the first plane 133 is located on the first circumferential direction S1 side of the first biasing member holding portion 131A. The first plane 133 is located circumferentially parallel to the first biasing member holding portion 131A. The second plane 135 is located on the second circumferential direction S2 side of the biasing member holding portion 131. More specifically, the second plane 135 is located on the second circumferential direction S2 side of the second biasing member holding portion 131B. The second plane 135 is located circumferentially parallel to the second biasing member holding portion 131B. As shown in Figure 17, the first plane 133 and the second plane 135 are perpendicular to the axial direction (i.e., direction D) of the output shaft 15. The first plane 133 and the second plane 135 are formed flush with each other. The first plane 133 and the second plane 135 are slidably mounted relative to the retaining member 140. More specifically, the first plane 133 and the second plane 135 are slidably mounted relative to the sliding surface 145M of the receiving recess 145. As shown in Figure 16, the inner M2 end 133A of the first plane 133 and the inner M2 end 135A of the second plane 135 are located inward M2 in the radial direction M from the retaining wall 132.

[0060] As shown in Figure 15, the weight member 130 has a third plane 137. The third plane 137 is located between the first plane 133 and the second plane 135 with respect to the circumferential direction S. The third plane 137 is located between the first biasing member holding portion 131A and the second biasing member holding portion 131B with respect to the circumferential direction S. The third plane 137 may be slidably provided with respect to the holding member 140. The third plane 137 may be formed flush with the first plane 133 and the second plane 135.

[0061] The weight-side inclined surface 130F is provided so as to be able to contact the pressure contact member 150. As shown in Figure 17, the weight-side inclined surface 130F is inclined with respect to the axial direction (i.e., direction D) of the output shaft 15. The weight-side inclined surface 130F is inclined toward the first direction D1, from the inner side M2 ​​in the radial direction M toward the outer side M1 in the radial direction M. The weight-side inclined surface 130F is configured to be slidable with respect to the pressure contact side inclined surface 150F of the pressure contact member 150 (see Figure 20), which will be described later.

[0062] As shown in Figure 17, the outer M1 end 133B of the first plane 133 and the outer M1 end 135B of the second plane 135 are located further outward in the radial direction M1 than the inner M2 end 130FA of the weight-side inclined surface 130F. The inner M2 end 133A of the first plane 133 and the inner M2 end 135A of the second plane 135 are located further inward in the radial direction M2 than the inner M2 end 130FA of the weight-side inclined surface 130F. The radial length L5 of the first plane 133 and the second plane 135 is longer than the radial length L6 of the weight-side inclined surface 130F. The combined area of ​​the first plane 133 and the second plane 135 is greater than the area of ​​the weight-side inclined surface 130F. The length L7 (see Figure 16) of the circumferential direction S from the end 133S1 of the first circumferential direction S1 of the first plane 133 to the end 135S2 of the second circumferential direction S2 of the second plane 135 is longer than the length L8 (see Figure 14) of the circumferential direction S of the weight-side inclined surface 130F.

[0063] As shown in Figure 9B, the spring 160 is positioned radially outward M1 of the weight member 130. The spring 160 is an example of a biasing member. The spring 160 is provided on the retaining member 140. The spring 160 is housed in a housing recess 145 of the retaining member 140. More specifically, a portion of the spring 160 is housed in a housing groove 146 (see Figure 10). A portion of the spring 160 is located inside the weight member 130. That is, a portion of the spring 160 is located within the biasing member retaining portion 131. The spring 160 biases the weight member 130 radially inward M2. The spring 160 is, for example, a coil spring. The spring 160 includes a first spring 161 and a second spring 162 arranged in the circumferential direction S. The first spring 161 is an example of a first biasing member. The second spring 162 is an example of a second biasing member. The first spring 161 and the second spring 162 have the same shape. The first spring 161 and the second spring 162 are housed in the housing recess 145. The first spring 161 and the second spring 162 bias the weight member 130 inward M2 in the radial direction M. The first spring 161 and the second spring 162 are provided between the first plane 133 and the second plane 135 with respect to the circumferential direction S.

[0064] As shown in Figure 1, the contact member 170 is positioned between the holding member 140 and the pressure contact member 150. The contact member 170 is positioned on the opposite side of the holding member 140 with respect to the axial direction (direction D in this case) of the output shaft 15, with the weight member 130 in between. As shown in Figure 9A, the contact member 170 is formed in a disc shape. The contact member 170 is fixed to the holding member 140. More specifically, the contact member 170 is fixed to the holding member 140 by fastening a bolt 172 into a bolt hole 140H (see Figure 9B) formed in the holding member 140. Note that the means for fixing the contact member 170 to the holding member 140 are not limited to the bolt 172. Instead of the bolt 172, the contact member 170 may be fixed to the holding member 140 by other fixing means such as a rivet. The contact member 170 is in contact with the weight member 130. The contact member 170 is a member that suppresses the movement of the weight member 130 in the second direction D2. The contact member 170 has a plurality of openings 170H arranged in the circumferential direction S. The weight-side inclined surface 130F of the weight member 130 is exposed to the outside through the openings 170H.

[0065] The pressure contact member 150 is configured to press against the input side rotating plate 20 and the output side rotating plate 22 by moving the weight member 130 from the inner position M2 PI to the outer position M1 PO of the radial direction M, thereby moving in the axial direction of the output shaft 15 (here, in the second direction D2). The pressure contact member 150 is formed in an annular shape. As shown in Figure 1, the pressure contact member 150 has a pressure contact side inclined surface 150F and a pressing surface 150P. The pressure contact side inclined surface 150F is an example of a pressure contact side sliding part. The pressure contact side inclined surface 150F is provided so as to be in contact with the weight member 130. The pressure contact side inclined surface 150F is inclined with respect to the axial direction (i.e., direction D) of the output shaft 15. The pressure contact side inclined surface 150F is inclined from the inner M2 of the radial direction M toward the outer M1 of the radial direction M toward the first direction D1. The pressure-contacting inclined surface 150F is configured to slide relative to the weight-side inclined surface 130F of the weight member 130. As shown in Figure 21, in a cross-sectional view in a plane including the axial direction (i.e., direction D) and radial direction M of the output shaft 15, a straight line CL1 passing through the center 150FC of the radial direction M of the pressure-contacting inclined surface 150F and parallel to the axial direction (i.e., direction D) of the output shaft 15 passes through the first plane 133 and the second plane 135 when the weight member 130 is located outside M1 in the radial direction M. Multiple pressure-contacting inclined surfaces 150F are provided for each weight member 130 over the circumferential direction S. When the clutch housing 30 rotates and centrifugal force is applied to the weight member 130, the weight member 130 moves along the pressure-contacting inclined surface 150F, causing the pressure-contacting member 150 to move in a direction away from the holding member 140 (i.e., the second direction D2). As a result, the pressing surface 150P of the contact member 150 presses the flange 68 of the second clutch center 51 in the second direction D2. The contact member 150 has a plurality of engaging projections 153 formed along the circumferential direction S. The engaging projections 153 overlap with the engaging claws 143 of the retaining member 140. The engaging projections 153 engage with the clutch housing 30. The retaining member 140 and the contact member 150 are held in the clutch housing 30 by spline fitting. The retaining member 140 and the contact member 150 are provided so as to be displaceable along the axial direction (i.e., direction D) of the clutch housing 30.The retaining member 140 and the pressure contact member 150 are provided to be rotatable integrally with the clutch housing 30.

[0066] In this centrifugal clutch mechanism 120, as shown in Figures 9A and 20, when no centrifugal force is applied to the weight member 130, the weight member 130 is held at position PI, which is inward M2 in the radial direction M, and the contact force between the input-side rotating plate 20 and the output-side rotating plate 22 is released. On the other hand, as shown in Figures 18 and 21, when centrifugal force is applied to the weight member 130, the weight member 130 moves from position PI, which is inward M2 in the radial direction M, to position PO, which is outward M1. When the weight member 130 moves in the radial direction M, the weight-side inclined surface 130F of the weight member 130 and the contact-side inclined surface 150F of the contact-contact member 150 slide against each other, and the first plane 133 and the second plane 135 of the weight member 130 slide against the sliding surface 145M of the holding member 140. At this time, the pressing surface 150P of the contact member 150 presses the input side rotating plate 20 and the output side rotating plate 22 via the flange 68 of the second clutch center 51, creating a contact state, and enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15. Simultaneously, the holding member 140 moves in the first direction D1, and the pressing portion 149 (see Figure 1) of the holding member 140 presses the auxiliary clutch plate 180.

[0067] As shown in Figure 1, the auxiliary clutch plate 180 is provided within the clutch housing 30. The auxiliary clutch plate 180 is fixed to the output shaft 15. The auxiliary clutch plate 180 has an insertion hole 152H into which the output shaft 15 is inserted and spline-fitted. The auxiliary clutch plate 180 is positioned on the first direction D1 side of a part of the centrifugal clutch mechanism 120. The auxiliary clutch plate 180 is adjacent to the first clutch center 41.

[0068] The auxiliary clutch plate 180 is configured to be pressed by the centrifugal clutch mechanism 120 (in this case, by the pressing portion 149 of the holding member 140) when the input side rotating plate 20 and the output side rotating plate 22 are in contact (i.e., when the weight member 130 of the centrifugal clutch mechanism 120 is located at position PO, which is M1 on the outside in the radial direction M), thereby enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15. The auxiliary clutch plate 180 is configured to be released from the pressure of the centrifugal clutch mechanism 120 (in this case, by the pressing portion 149 of the holding member 140) when the contact force between the input side rotating plate 20 and the output side rotating plate 22 is released (i.e., when the weight member 130 is located at position PI, which is M2 on the inside in the radial direction M), thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15.

[0069] As shown in Figure 1, the stopper plate 100 is provided so as to be in 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 in the second direction D2 by a predetermined distance or more. The stopper plate 100 is fixed to the boss portion 62 of the first clutch center 41 by bolts 28. The pressure member 70 is fixed to the clutch center 40 by bolts 28 being tightened to the boss portion 62 via the stopper plate 100, with the clutch spring 25 positioned in the spring housing portion 84. The stopper plate 100 is formed in a ring shape in plan view.

[0070] As described above, according to the clutch device 10 of this embodiment, the main body 141 of the retaining member 140 includes a thickened portion 141T which includes a wall portion 141A located between the engaging claw 143 and the housing recess 145 with respect to the radial direction M, and a protruding portion 141B that protrudes inward M2 in the radial direction M from the wall portion 141A and partitions a part of the housing recess 145. According to the above embodiment, since the thickened portion 141T is provided between the engaging claw 143 and the housing recess 145, the thickness in the radial direction M is increased by the amount of the thickened portion 141T, and the rigidity of the engaging claw 143 is increased. As a result, even if, for example, the weight member 130 comes into contact with the protruding portion 141B, the rigidity of the engaging claw 143 is improved, and damage to the engaging claw 143 can be suppressed.

[0071] In the clutch device 10 of this embodiment, the length L1 of the circumferential S of the protruding portion 141B is greater than or equal to the length L2 of the circumferential S of the engaging claw 143. According to the above embodiment, the rigidity of the engaging claw 143 can be increased.

[0072] In the clutch device 10 of this embodiment, the radial length L3 from the outer peripheral edge 141E of the main body 141 to the inner end 141BX of the projection 141B in the radial direction M is longer than the radial length L4 from the outer peripheral edge 141E of the main body 141 to the outer end 143X of the engaging claw 143 in the radial direction M. According to the above embodiment, the rigidity of the engaging claw 143 can be increased.

[0073] In the clutch device 10 of this embodiment, the protruding portion 141B is located between the first spring 161 and the second spring 162 with respect to the circumferential direction S. According to the above embodiment, the load from the weight member 130 applied to the engaging claw 143 can be reduced.

[0074] <Second Embodiment> As shown in Figure 22, the centrifugal clutch mechanism 220 according to the second embodiment includes a plurality of weight members 230, a holding member 240, a pressure contact member 150, a spring 160 (see Figure 25), and a cylindrical member 270. The centrifugal clutch mechanism 220 has the same configuration as the centrifugal clutch mechanism 120 according to the first embodiment, except that it has weight members 230 instead of weight member 130, a holding member 240 instead of holding member 140, and further includes a cylindrical member 270.

[0075] As shown in Figures 22 and 23, the retaining member 240 includes a retaining member-side guide portion 245 that accommodates a portion of the cylindrical member 270. The retaining member-side guide portion 245 is formed on the surface 245M of the accommodating recess 145 that faces the weight member 230. The retaining member-side guide portion 245 holds the cylindrical member 270 such that a portion of the cylindrical member 270 protrudes from the surface 245M of the retaining member 240 that faces the weight member 230 toward the weight member 230 (i.e., toward the second direction D2). The retaining member-side guide portion 245 guides the radial movement M of the cylindrical member 270. The retaining member-side guide portion 245 is located between the first accommodating groove 146A and the second accommodating groove 146B with respect to the circumferential direction S. The retaining member-side guide portion 245 is formed in a rectangular shape in plan view. The retaining member side guide portion 245 is configured to restrict the movement of the cylindrical member 270 in the circumferential direction S, and to restrict the movement of the cylindrical member 270 in the radial direction M by a predetermined distance or more.

[0076] As shown in Figure 24, the weight member 230 is provided with a guide portion 238 that accommodates a part of the cylindrical member 270. The guide portion 238 is formed on the surface facing the holding member 240 (here, the third plane 137). The guide portion 238 holds the cylindrical member 270 such that a part of the cylindrical member 270 protrudes toward the holding member 240 (i.e., toward the first direction D1) from the surface of the weight member 230 facing the holding member 240 (here, the third plane 137) (see Figure 26). The guide portion 238 guides the radial movement M of the cylindrical member 270. The guide portion 238 is located between the first biasing member holding portion 131A and the second biasing member holding portion 131B with respect to the circumferential direction S. As shown in Figure 25, the guide portion 238 is formed in a rectangular shape in plan view. The guide section 238 includes a first restricting section 238S that restricts the movement of the cylindrical member 270 in the circumferential direction S, and a second restricting section 238M that restricts the movement of the cylindrical member 270 beyond a predetermined distance in the radial direction M. The first restricting section 238S is provided on the first circumferential direction S1 side and the second circumferential direction S2 side with respect to the circumferential direction S. The second restricting section 238M is provided on the outer M1 and inner M2 sides with respect to the radial direction M. The guide section 238 has a recessed accommodating groove 238P that is recessed in the direction from the holding member 240 toward the weight member 230 (i.e., the second direction D2) with respect to the axial direction (i.e., direction D) of the output shaft 15 and accommodates a part of the cylindrical member 270. The accommodating groove 238P is demarcated by the first restricting section 238S and the second restricting section 238M.

[0077] As shown in Figure 22, the cylindrical member 270 is provided between the weight member 230 and the retaining member 240 with respect to the axial direction (i.e., direction D) of the output shaft 15. The cylindrical member 270 is positioned to extend in a direction intersecting the radial direction M (here, a direction perpendicular to both the radial direction M and direction D). The cylindrical member 270 rolls relative to the weight member 230 and the retaining member 240. Part of the cylindrical member 270 is housed in the retaining member-side guide portion 245 of the retaining member 240, and the other part of the cylindrical member 270 is housed in the guide portion 238 of the weight member 230. The cylindrical member 270 rolls relative to the retaining member-side guide portion 245 and the guide portion 238. As shown in Figure 25, the cylindrical member 270 is located between the first spring 161 and the second spring 162 with respect to the circumferential direction S. The length L9 of the circumferential direction S of the cylindrical member 270 is at least one-quarter of the length L8 of the circumferential direction S of the weight-side inclined surface 130F (see Figure 14).

[0078] As shown in Figure 27, in a cross-sectional view in a plane including the axial direction (i.e., direction D) and radial direction M of the output shaft 15, when the weight member 230 is located inward M2 in the radial direction M, at least a portion of the cylindrical member 270 overlaps with the spring 160. Here, the entire cylindrical member 270 overlaps with the spring 160. In a cross-sectional view in a plane including the axial direction (i.e., direction D) and radial direction M of the output shaft 15, when the weight member 230 is located inward M2 in the radial direction M, at least a portion of the guide portion 238 overlaps with the spring 160. Here, the entire guide portion 238 overlaps with the spring 160.

[0079] As shown in Figure 28, in a cross-sectional view in a plane including the axial direction (i.e., direction D) and radial direction M of the output shaft 15, the straight line CL2 passing through the center 150FC of the radial direction M of the pressure-contact side inclined surface 150F and parallel to the axial direction (i.e., direction D) of the output shaft 15 passes through the guide portion 238 when the weight member 230 is located on the outside M1 of the radial direction M. As shown in Figure 29, when the weight member 230 is located on the inside M2 ​​of the radial direction M and viewed from the axial direction (i.e., direction D) of the output shaft 15, at least a part of the weight-side inclined surface 130F and the retaining member-side guide portion 245 overlap. As shown in Figure 30, when the weight member 230 is located on the outside M1 of the radial direction M and viewed from the axial direction (i.e., direction D) of the output shaft 15, at least a part of the pressure-contact side inclined surface 150F and the guide portion 238 overlap.

[0080] In this centrifugal clutch mechanism 220, as shown in Figures 27 and 29, when no centrifugal force is applied to the weight member 230, the weight member 230 is held at position PI, which is inward M2 in the radial direction M, and the contact force between the input-side rotating plate 20 and the output-side rotating plate 22 is released. On the other hand, as shown in Figures 28 and 30, when centrifugal force is applied to the weight member 230, the weight member 230 moves from position PI, which is inward M2 in the radial direction M, to position PO, which is outward M1. When the weight member 230 moves in the radial direction M, the cylindrical member 270 rolls relative to the weight member 230 and the holding member 240, guided by the guide portion 238 and the holding member-side guide portion 245. At this time, the first plane 133 and the second plane 135 of the weight member 230 do not slide against the sliding surface 145M of the holding member 240.

[0081] <Third Embodiment> As shown in Figure 31, the retaining member 340 according to the third embodiment comprises a main body 341, a plurality of engaging claws 143, a plurality of receiving recesses 345, and a pressing portion 149 (see Figure 1).

[0082] The main body 341 is formed in a ring shape. As shown in Figure 31, the main body 341 has a wall portion 341A. The wall portion 341A is located between the engaging claw 143 and the receiving recess 345 with respect to the radial direction M. The wall portion 341A partitions a portion of the receiving recess 345.

[0083] As shown in Figure 31, the housing recess 345 is formed in the main body 341 so as to be recessed in the axial direction of the output shaft 15. The housing recess 345 is recessed in the first direction D1. The housing recess 345 accommodates the weight member 130 so as to be movable in the radial direction M. One end of the first spring 161 and the second spring 162 abut against the outer end 345X of the housing recess 345 in the radial direction M1.

[0084] As shown in Figure 31, the radial length M L10 of the wall portion 341A is longer than the radial length M L4 from the outer peripheral edge 141E of the main body 341 to the outer end M1 of the engaging claw 143 in the radial direction M 143X. Here, the radial length M L10 of the wall portion 341A is the radial length M from the outer peripheral edge 141E of the main body 341 to the outer end M1 of the receiving recess 345 in the radial direction M 145X. The circumferential length S L11 of the wall portion 341A is greater than or equal to the circumferential length S L2 of the engaging claw 143.

[0085] According to the clutch device 10 of this embodiment, the main body 341 of the retaining member 340 has a wall portion 341A located between the engaging claw 143 and the receiving recess 345 with respect to the radial direction M, and the length L10 of the wall portion 341A in the radial direction M is longer than the length L4 of the radial direction M from the outer peripheral edge 141E of the main body 341 to the outer end 143X of the engaging claw 143 in the radial direction M. According to the above embodiment, since the wall portion 341A is relatively thick, the rigidity of the engaging claw 143 is increased. As a result, even if, for example, the weight member 130 comes into contact with the wall portion 341A, the rigidity of the engaging claw 143 is improved, and damage to the engaging claw 143 can be suppressed.

[0086] In the clutch device 10 of this embodiment, the circumferential length S L11 of the wall portion 341A is greater than or equal to the circumferential length S L2 of the engaging claw 143. According to the above embodiment, the rigidity of the engaging claw 143 can be increased. <Fourth Embodiment> Figure 32 is a plan view showing a part of the centrifugal clutch mechanism 420 according to the fourth embodiment. The centrifugal clutch mechanism 420 includes a plurality of weight members 130, a holding member 140, a pressure contact member 150 (see Figure 1), a spring 160, and a contact member 170 (see Figure 1). The plurality of weight members 130 include a first weight member 130A and a second weight member 130B. The first weight member 130A and the second weight member 130B have the same configuration except that the first weight member 130A is lighter than the second weight member 130B. The first weight member 130A and the second weight member 130B are formed from different materials, for example. In the example shown in Figure 1, the first weight member 130A and the second weight member 130B are configured to move the pressure contact member 150 in the second direction D2.

[0087] As shown in Figure 32, the first weight members 130A and the second weight members 130B are arranged alternately with respect to the circumferential direction S. That is, one first weight member 130A is located between two second weight members 130B that are aligned with respect to the circumferential direction S. The number of first weight members 130A is the same as the number of second weight members 130B. In this embodiment, there are three first weight members 130A and three second weight members 130B, but the number of each is not limited to three. When viewed in the axial direction of the output shaft 15, some of the multiple first weight members 130A are arranged symmetrically with respect to the straight line LC passing through the center 15C of the output shaft 15, and some of the multiple second weight members 130B are arranged symmetrically with respect to the straight line LC.

[0088] As shown in Figures 33A and 33B, the second weight member 130B begins to move from position PI, on the inside M2 ​​in the radial direction M, toward position PO, on the outside M1 in the radial direction M, when the engine speed is at a first rotational speed E1. The first rotational speed E1 is the engine speed when the vehicle starts. The second weight member 130B begins to press against the contact member 150 when the engine speed is at the first rotational speed E1, causing the contact member 150 to move axially (i.e., in direction D). The contact member 150 begins to move from its initial position, position PD1, which is closest to the first direction D1, toward position PD2, which is closest to the second direction D2. While the engine speed is moving from the first rotational speed E1 to the second rotational speed E2, the second weight member 130B continues to move radially M, and the contact member 150 continues to move in the second direction D2. The first weight member 130A begins to move from position PI, the inner M2 in the radial direction M, to position PO, the outer M1 in the radial direction M, when the clutch is partially engaged. The engine speed when the clutch is partially engaged is higher than the engine speed when the vehicle starts (here, the first rotational speed E1). For example, when the engine speed is the second rotational speed E2, the first weight member 130A begins to move from position PI, the inner M2 in the radial direction M, to position PO, the outer M1 in the radial direction M. While the engine speed is moving from the second rotational speed E2 to the third rotational speed E3, the second weight member 130B does not move in the radial direction M, the pressure contact member 150 does not move in direction D, and only the first weight member 130A continues to move in the radial direction M. The first weight member 130A begins to press against the contact member 150 when the engine speed is the third rotational speed E3, causing the contact member 150 to move axially (i.e., in direction D). When the engine speed is the third rotational speed E3, the first weight member 130A and the second weight member 130B begin to press against the contact member 150 simultaneously, causing the contact member 150 to start moving again in direction D. Subsequently, when the engine speed is the sixth rotational speed E6, the first weight member 130A and the second weight member 130B reach position PO on the outer side M1 in the radial direction M. At this time, the contact member 150 also reaches position PD2.Thus, since the entirety of the first weight member 130A and the second weight member 130B are not used to press the contact member 150 from the beginning, the input-side rotating plate 20 and the output-side rotating plate 22 are not pressed together suddenly but gradually. In other words, sudden clutch engagement can be suppressed, and thus a decrease in ride comfort is suppressed. In this embodiment, the first radial displacement MD1 of the second weight member 130B from the first rotational speed E1 to the second rotational speed E2 is different from the second radial displacement MD2 of the second weight member 130B from the second rotational speed E2 to the sixth rotational speed E6. Here, the second displacement MD2 is greater than the first displacement MD1. Furthermore, the third radial displacement MD3 of the second weight member 130B from the second rotational speed E2 to the fifth rotational speed E5 is greater than the first displacement MD1. In Figures 33A and 33B, E0 is the engine speed at idle, E4 is the engine speed at which a force is generated from the pressure member 70 toward the clutch center 40 (in this case, the first direction D1) due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, and E5 is the engine speed at which the input-side rotating plate 20 and the output-side rotating plate 22 are in complete contact. The center-side assist cam surface 60A and the pressure-side assist cam surface 90A are configured to start generating a force from the pressure member 70 toward the clutch center 40 when the engine speed is the fourth rotational speed E4. Furthermore, in Figure 33A, the solid line shows the trajectory of the movement of the second weight member 130B, the dashed line shows the trajectory of the movement of the first weight member 130A, and the dotted line shows the trajectories of the movement of both the first weight member 130A and the second weight member 130B.

[0089] In the examples of Figures 33A and 33B, the contact member 150 does not move in direction D (here, the second direction D2) while the engine speed is increasing from the second rotational speed E2 to the third rotational speed E3, but it may move continuously in direction D as the engine speed increases. For example, while the engine speed is increasing from the second rotational speed E2 to the third rotational speed E3, the first weight member 130A and the second weight member 130B may move radially in direction M, and the contact member 150 may move in direction D. In this case, for example, when the engine speed reaches the second rotational speed E2, the first weight member 130A and the second weight member 130B may start pressing the contact member 150 simultaneously. Furthermore, in the example shown in Figure 33A, the first weight member 130A and the second weight member 130B begin to press the contact member 150 simultaneously at a third rotational speed E3, which is lower than the fourth rotational speed E4. However, the first weight member 130A and the second weight member 130B may also begin to press the contact member 150 simultaneously at a rotational speed higher than the fourth rotational speed E4. That is, at rotational speeds lower than the fourth rotational speed E4, when a force begins to be generated in the direction from the pressure member 70 toward the clutch center 40 (here, the first direction D1) due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, only the second weight member 130B, which is part of the weight member 130, presses against the contact member 150, and the first weight member 130A, which is another part of the weight member 130, does not press against the contact member 150. In other words, the third rotational speed E3, which is the upper limit of the first region RE1 described later, may be set to a rotational speed higher than the fourth rotational speed E4. As a result, when a force is generated from the pressure member 70 toward the clutch center 40 due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, the input-side rotating plate 20 and the output-side rotating plate 22 are gradually pressed together only by the second weight member 130B, thereby suppressing sudden clutch engagement and preventing a decrease in ride comfort.

[0090] As shown in Figures 33A and 33B, the system is configured such that when the engine speed is in the first region RE1, a portion of the multiple weight members 130 (in this case, the second weight member 130B) presses against the contact member 150, and when the engine speed is in the second region RE2, all of the multiple weight members 130 (in this case, the first weight member 130A and the second weight member 130B) press against the contact member 150. Here, pressing the contact member 150 includes cases where the contact member 150 is pressed and moves in the second direction D2, and cases where the contact member 150 is pressed but does not move in the second direction D2. The first region RE1 ranges from the engine speed when the vehicle starts (e.g., the first rotational speed E1) to a predetermined first rotational speed of the engine in a half-clutch state (e.g., the third rotational speed E3). The upper limit of the first region RE1 is lower than the fourth rotational speed E4. The second region RE2 is a predetermined first rotational speed (e.g., the third rotational speed E3) of the engine in a half-clutch state, and a predetermined second rotational speed (e.g., the sixth rotational speed E6) that is higher than the predetermined first rotational speed. The region RH in a half-clutch state is a range from the first rotational speed E1 to the fifth rotational speed E5.

[0091] Next, the relationship between the engine speed and the contact between the input-side rotating plate 20 and the output-side rotating plate 22 will be explained. As shown in Figures 33A and 33B, while the engine speed is moving from the first rotational speed E1 to the second rotational speed E2, the contact member 150 presses the flange 68 of the second clutch center 51 in the second direction D2. As a result, the second clutch center 51 moves in the second direction D2 relative to the first clutch center 41, and the input-side rotating plate 20 and the output-side rotating plate 22 come into contact, resulting in a semi-clutch state. In this semi-clutch state, the rotational driving force of the input shaft begins to be transmitted to the output shaft 15. When the engine speed reaches the second rotational speed E2, the second weight member 130B attempts to move the pressure member 150 further in the second direction D2. Because the input-side rotating plate 20 and the output-side rotating plate 22 are in contact, the pressure member 150 attempts to move the pressure member 70 in the second direction D2 via the input-side rotating plate 20 and the output-side rotating plate 22. At this point, the wall surface 84D1 (see Figure 20) of the spring housing portion 84 of the pressure member 70 on the first direction D1 side is in contact with the wall surface 41D2 (see Figure 20) of the first clutch center 41 on the second direction D2 side, and the pressure member 70 is biased toward the first direction D1 by the clutch spring 25. Therefore, until the engine speed increases further from the second rotational speed E2 and the force acting on the pressure contact member 150 from the weight member 130 (here, the first weight member 130A and the second weight member 130B) in the second direction D2 exceeds the spring force of the clutch spring 25, the pressure contact member 150 remains in position PDS at the second rotational speed E2 (see Figure 33B). That is, the pressure member 70 is held in contact with the wall surface 41D2 on the second direction D2 side of the first clutch center 41 by the spring force of the clutch spring 25. Then, when the engine speed reaches the third rotational speed E3 and the first weight member 130A begins to press against the contact member 150, both the first weight member 130A and the second weight member 130B press against the contact member 150, so the force acting from the weight member 130 to the contact member 150 in the second direction D2 exceeds the spring force of the clutch spring 25.As a result, the contact member 150 moves further in the second direction D2, moving the second clutch center 51 and the pressure member 70 in the second direction D2. Consequently, the input side rotating plate 20 and the output side rotating plate 22 are further pressed together, and when the engine speed reaches the fifth rotational speed E5, the input side rotating plate 20 and the output side rotating plate 22 are completely pressed together.

[0092] <Fifth Embodiment> Figure 34 is a plan view showing a part of the centrifugal clutch mechanism 520 according to the fifth embodiment. The centrifugal clutch mechanism 520 includes a plurality of weight members 130, a holding member 140, a pressure contact member 150 (see Figure 1), a spring 160, and a contact member 170 (see Figure 1). The plurality of weight members 130 include a first weight member 130A and a second weight member 130B. The first weight member 130A and the second weight member 130B have the same configuration except that they differ in the number of springs 160 that bias them inward M2 in the radial direction M. The first weight member 130A is biased inward M2 in the radial direction M by one spring 160. The second weight member 130B is biased inward M2 in the radial direction M by two springs 160. The timing of the start of movement and the arrangement of the first weight member 130A and the second weight member 130B in the fifth embodiment are the same as those of the first weight member 130A and the second weight member 130B in the fourth embodiment.

[0093] <Sixth Embodiment> Figure 35 is a plan view showing a part of the centrifugal clutch mechanism 620 according to the sixth embodiment. The centrifugal clutch mechanism 620 includes a plurality of weight members 130, a holding member 140, a pressure contact member 150 (see Figure 1), a spring 160, a contact member 170 (see Figure 1), and a suppression member 190. The plurality of weight members 130 include a first weight member 130A and a second weight member 130B. The first weight member 130A and the second weight member 130B have the same configuration except that the second weight member 130B is provided with a second suppression member 190B, which will be described later. The timing of the start of movement and the arrangement of the first weight member 130A and the second weight member 130B according to the sixth embodiment are the same as those of the first weight member 130A and the second weight member 130B according to the fourth embodiment.

[0094] As shown in Figure 35, the restraining member 190 includes a first restraining member 190A provided on the holding member 140 and a second restraining member 190B provided on the second weight member 130B. The first restraining member 190A and the second restraining member 190B are, for example, magnets. When the second weight member 130B is at position PI on the inside M2 ​​in the radial direction M, the first restraining member 190A and the second restraining member 190B are attracted to each other by magnetic force. The restraining member 190 suppresses the start of movement of the second weight member 130B from position PI on the inside M2 ​​in the radial direction M to position PO on the outside M1 in the radial direction M until the centrifugal force reaches a predetermined magnitude (for example, until the second rotational speed E2 is reached). That is, when the suction force between the first restraining member 190A and the second restraining member 190B is greater than the centrifugal force, the second weight member 130B does not move in the radial direction M. The restraining member 190 prevents the second weight member 130B from pressing against the contact member 150 until the centrifugal force reaches a predetermined magnitude. When the centrifugal force exceeds a predetermined magnitude (for example, when it reaches a second rotational speed E2), the restraining member 190 allows the second weight member 130B to begin moving from its position PI at the inside M2 ​​in the radial direction M to its position PO at the outside M1 in the radial direction M. That is, when the centrifugal force becomes greater than the suction force between the first restraining member 190A and the second restraining member 190B, the second weight member 130B moves in the radial direction M. The suppression member 190 allows the second weight member 130B to press against the contact member 150 when the centrifugal force exceeds a predetermined magnitude.

[0095] <Seventh Embodiment> Figure 36 is a plan view showing a part of the centrifugal clutch mechanism 720 according to the seventh embodiment. The centrifugal clutch mechanism 720 has the same configuration as the centrifugal clutch mechanism 420, except that the number of first weight members 130A and the number of second weight members 130B are different. The number of first weight members 130A is greater than the number of second weight members 130B. The number of second weight members 130B may also be greater than the number of first weight members 130A. In addition, in the centrifugal clutch mechanism 520 and centrifugal clutch mechanism 620 described above, the number of first weight members 130A and the number of second weight members 130B may also be different, similar to the centrifugal clutch mechanism 720. The timing of the start of movement and the arrangement of the first weight member 130A and the second weight member 130B in the seventh embodiment are the same as those of the first weight member 130A and the second weight member 130B in the fourth embodiment.

[0096] <Eighth Embodiment> Figure 37 is a cross-sectional view showing a centrifugal clutch mechanism 820 and its surroundings according to the eighth embodiment. The centrifugal clutch mechanism 820 includes a plurality of weight members 830, a holding member 840, a pressure contact member 850, a spring 160, and a contact member 170. As shown in Figure 38, the plurality of weight members 830 include a first weight member 830A and a second weight member 830B.

[0097] As shown in Figures 37 and 38, the retaining member 840 holds the weight member 830 so that it can move between a position PI on the inside M2 ​​in the radial direction M and a position PO on the outside M1 in the radial direction M. The retaining member 840 is formed in an annular shape. The retaining member 840 is made of die-cast aluminum. The retaining member 840 comprises a main body 141, a plurality of engaging claws 143, a plurality of receiving recesses 145, and a pressing portion 149 (see Figure 1).

[0098] As shown in Figure 39, the weight member 830 comprises a weight body 830X, a through hole 833, a cylindrical member 834, and a spherical member 835. The through hole 833 is formed in the weight body 830X. The through hole 833 is a hole that penetrates the weight body 830X in the axial direction (i.e., direction D) of the output shaft 15. The through hole 833 is provided with a cylindrical member 834 that holds the spherical member 835 so that it can roll. The cylindrical member 834 is fitted inside the through hole 833 and extends in the axial direction (i.e., direction D) of the output shaft 15. A portion of the spherical member 835 protrudes from the opening of the through hole 833. The spherical member 835 is, for example, a steel ball. The spherical member 835 includes a first spherical member 835A that can contact (abut) the pressure contact member 850, and a second spherical member 835B that can contact (abut) the holding member 840. The first spherical member 835A is provided so as to be rotatable with respect to the inclined surface 856 of the pressure contact member 850, which will be described later. The second spherical member 835B is provided so as to be rotatable with respect to the housing recess 145 of the holding member 840. The first spherical member 835A is an example of a contact portion on the weight member side.

[0099] The contact member 850 is configured to press against the input side rotating plate 20 and the output side rotating plate 22 by moving the weight member 830 from a position PI on the inside M2 ​​in the radial direction M to a position PO on the outside M1 in the radial direction M, thereby moving in the axial direction of the output shaft 15 (here, in the second direction D2). As shown in Figure 40, the contact member 850 is formed in an annular shape. The contact member 850 comprises an annular main body portion 851, a plurality of protrusions 855, and a plurality of engaging claws 843. The engaging claws 843 protrude from the outer peripheral edge 851E of the main body portion 851 toward the outside M1 in the radial direction M. The engaging claws 843 are integrally formed with the main body portion 851. The engaging claws 843 engage with the clutch housing 30 (see Figure 1). The plurality of engaging claws 843 are arranged in the circumferential direction S.

[0100] As shown in Figure 40, the protrusion 855 projects from the main body 851 in the axial direction of the output shaft 15 (here, the first direction D1). The protrusion 855 extends in the radial direction M. Multiple protrusions 855 are arranged in the circumferential direction S. The protrusion 855 has an inclined surface 856 that contacts the weight member 830. More specifically, the inclined surface 856 contacts (abuts against) the first spherical member 835A of the weight member 830. The inclined surface 856 is inclined with respect to the axial direction of the output shaft 15 (i.e., direction D). The inclined surface 856 is inclined toward the first direction D1 as it moves outward M1 in the radial direction M. A guide groove 857 is formed in the inclined surface 856 that guides the radial movement of the first spherical member 835A in the radial direction M. The guide groove 857 extends in the radial direction M. The inclined surface 856 is an example of a contact portion on the pressure-welding member side. As the weight member 830 moves from position PI on the inside M2 ​​in the radial direction M to position PO on the outside M1 in the radial direction M, the first spherical member 835A and the inclined surface 856 come into contact, and the pressure-welding member 850 moves in the axial direction of the output shaft 15 (in this case, the second direction D2).

[0101] In the eighth embodiment, the first weight member 830A is lighter than the second weight member 830B. The timing of the start of movement and the arrangement of the first weight member 830A and the second weight member 830B in the eighth embodiment are the same as those of the first weight member 130A and the second weight member 130B in the fourth embodiment. Also, as in the fifth embodiment, the number of springs 160 biasing toward the inside M2 ​​in the radial direction M may differ between the first weight member 830A and the second weight member 830B. Also, as in the sixth embodiment, the centrifugal clutch mechanism 820 may include a restraining member 190. Also, as in the seventh embodiment, the number of first weight members 830A and the number of second weight members 830B may differ.

[0102] In the eighth embodiment described above, the first weight member 830A was lighter than the second weight member 830B, but the embodiment is not limited to this. For example, when the first weight member 830A and the second weight member 830B have the same configuration, as shown in Figure 41, the position PIA of the first weight member 830A on the inside M2 ​​in the radial direction M and the position PIB of the second weight member 830B on the inside M2 ​​in the radial direction M may be different with respect to the radial direction M. In this case, the first spherical member 835A of the first weight member 830A presses the contact member 850 in the second direction D2 via the inclined surface 856 between position PIA and position PIB. At this time, the first spherical member 835A of the second weight member 830B does not press the contact member 850 in the second direction D2. Then, between position PIB and position PO, the first spherical member 835A of the first weight member 830A presses the contact member 850 in the second direction D2 via the inclined surface 856, and the first spherical member 835A of the second weight member 830B also presses the contact member 850 in the second direction D2 via the inclined surface 856. That is, the first weight member 830A presses the contact member 850 in the range of region PRA, and the second weight member 830B presses the contact member 850 in the range of region PRB. In this modified example, the shape of the first spherical member 835A of the first weight member 830A and the shape of the first spherical member 835A of the second weight member 830B may be different. In Figure 41, the first spherical member 835A located at position PI, M2 on the inside of the radial direction M, is shown by a solid line, and the first spherical member 835A located at position PO, M1 on the outside of the radial direction M, is shown by a dashed line.

[0103] In the eighth embodiment described above, the first weight member 830A was lighter than the second weight member 830B, and the inclined surface 856 on which the first spherical member 835A of the first weight member 830A rolled and the inclined surface 856 on which the first spherical member 835A of the second weight member 830B rolled had the same shape, but the embodiment is not limited to this. For example, when the first weight member 830A and the second weight member 830B have the same configuration, as shown in Figure 42, the inclined surface 856A on which the first spherical member 835A of the first weight member 830A rolled and the inclined surface 856B on which the first spherical member 835A of the second weight member 830B rolled may have different shapes in a cross-sectional view including the axis of the output shaft 15. That is, the radial length M of the inclined surface 856A may be longer than the radial length M of the inclined surface 856B. The inner end 856BM2 of the inclined surface 856B in the radial direction M is located radially outward M1 than the inner end 856AM2 of the inclined surface 856A in the radial direction M. In this case, the position PIA of the inner M2 of the first weight member 830A and the position PIB of the inner M2 of the second weight member 830B are different with respect to radial direction M. Between position PIA and position PIB, the first spherical member 835A of the first weight member 830A presses the contact member 850 in the second direction D2 via the inclined surface 856A. At this time, the first spherical member 835A of the second weight member 830B does not press the contact member 850 in the second direction D2. Then, between position PIB and position PO, the first spherical member 835A of the first weight member 830A presses the contact member 850 in the second direction D2 via the inclined surface 856A, and the first spherical member 835A of the second weight member 830B presses the contact member 850 in the second direction D2 via the inclined surface 856B. That is, the first weight member 830A presses the contact member 850 within the range of region PRA, and the second weight member 830B presses the contact member 850 within the range of region PRB. In this modified example, the position of the inner diameter M2 of the second weight member 830B may be the same as the position PIA of the inner diameter M2 of the first weight member 830A, and the second weight member 830B may be configured to contact (i.e., press against) the inclined surface 856B from the inner diameter M2 end 856BM2 of the inclined surface 856B.Furthermore, the radial positions M of the inclined surface 856A and the inclined surface 856B may be different. In Figure 42, the first spherical member 835A located at position PI, M2 on the inside of the radial direction M, is shown by a solid line, and the first spherical member 835A located at position PO, M1 on the outside of the radial direction M, is shown by a dashed line.

[0104] Preferred embodiments of the present invention have been described above. However, the embodiments described above are merely illustrative, and the present invention can be implemented in various other forms.

[0105] In the embodiments described above, a spring 160 was given as an example of a biasing member, but the invention is not limited to this. The biasing member may be an elastic body such as rubber.

[0106] In the embodiments described above, an example of the contact-side sliding portion is the contact-side inclined surface 150F, and an example of the weight-side sliding portion is the weight-side inclined surface 130F. Both were inclined surfaces that were inclined with respect to the axial direction (i.e., direction D) of the output shaft 15, but the invention is not limited to these. At least one of the contact-side sliding portion and the weight-side sliding portion is an inclined surface that is inclined with respect to the axial direction of the output shaft 15, and the other may be a projection or the like instead of an inclined surface.

[0107] In the embodiments described above, the weight members 130 and 230 were provided with a biasing member holding portion 131, but they do not necessarily have to be provided with a biasing member holding portion 131. In this case, for example, the spring 160 is positioned to abut against the outer end (e.g., end face) of the weight members 130 and 230 in the radial direction M.

[0108] In the first embodiment described above, the weight member 130 had a first plane 133 and a second plane 135 that were slidably provided with respect to the holding member 140, but it may have only one of them. The first plane 133 and the second plane 135 are examples of planes. In this case, the weight member 130 itself can slide better with respect to the holding member 140 via the first plane 133 or the second plane 135.

[0109] In the embodiments described above, the contact member 150 was configured to indirectly press the input-side rotating plate 20 and the output-side rotating plate 22 through the flange 68 of the second clutch center 51, but is not limited thereto. The contact member 150 may also be configured to press the input-side rotating plate 20 and the output-side rotating plate 22 by directly pressing either the input-side rotating plate 20 or the output-side rotating plate 22.

[0110] In each of the embodiments described above, the pressure member 70 holds one output-side rotating plate 22, but it may hold multiple output-side rotating plates 22.

[0111] In the embodiments described above, the pressure member 70 held a portion of the multiple output-side rotating plates 22, and the clutch center 40 (more specifically, the second clutch center 51) held the other portion of the multiple output-side rotating plates 22, but this is not limited to this configuration. For example, the pressure member 70 may hold all of the multiple output-side rotating plates 22.

[0112] In the embodiments described above, the clutch center 40 comprises a first clutch center 41 and a second clutch center 51, but the first clutch center 41 and the second clutch center 51 may be formed integrally.

[0113] In the embodiments described above, the weight member 130 was configured to directly press the contact member 150, but it may also be configured to press indirectly.

[0114] In the embodiments described above, an engine was used as the drive source, but the drive source is not limited to an engine and may be an electric motor or the like.

[0115] The shapes of the weight members 130, 230, and 830 are not limited to the shapes of the embodiments described above, and may be, for example, spherical.

[0116] The technology disclosed herein can be applied to various types of clutch devices. In the embodiments described above, a so-called internal-cut type clutch device is described as an example, in which the pressure member 70 is located on the opposite side of the clutch housing 30 from the clutch center 40 in the axial direction of the output shaft 15, but the technology is not limited thereto. For example, it can also be similarly applied to a so-called external-cut type clutch device in which the pressure member 70 is located between the clutch center 40 and the clutch housing 30 in the axial direction of the output shaft 15. [Explanation of Symbols]

[0117] 10. Clutch device 15 Output shaft 20 Input side rotating plate 22 Output side rotating plate 30 Clutch Housing 40 Clutch Center 70 Pressure components 120 Centrifugal clutch mechanism 130 Weight component 140 Retaining member 141 Main unit 141A Wall section 141B Projection 141E Outer edge 141T thick part 143 Engaging claw 143A Head 143B Base 145 Recessed 150 Pressure-welded member 160 Spring (Biasing Member) 161 First spring 162 Second spring

Claims

1. A clutch device for transmitting or interrupting the rotational driving force of an input shaft to an output shaft, A clutch center is housed in a clutch housing that holds a plurality of input-side rotating plates which are rotated by the rotational drive of the input shaft, and which rotates together with the output shaft, A pressure member is provided so as to be able to approach or move away from the clutch center, and holds at least a portion of the plurality of output-side rotating plates arranged alternately with the input-side rotating plate, and is capable of pressing the input-side rotating plate and the output-side rotating plate. The clutch housing has a plurality of weight members configured to move from an inner radial position to an outer radial position by the centrifugal force accompanying its rotation, and the centrifugal clutch mechanism is capable of pressing the input side rotating plate and the output side rotating plate together when the weight members are in the outer radial position, thereby enabling the transmission of the rotational driving force of the input shaft to the output shaft, and releasing the pressing force between the input side rotating plate and the output side rotating plate when the weight members are in the inner radial position, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism described above is: The weight member is provided with a biasing member that biases it inward in the radial direction, The aforementioned weight member is The biasing member comprises a first weight member that is biased inward in the radial direction by a first force, A clutch device comprising: a second weight member that biases the biasing member radially inward with a second force greater than the first force.

2. The clutch device according to claim 1, wherein one of the first weight members is located between two of the second weight members that are aligned in the circumferential direction.

3. The weight member includes a plurality of the first weight members and a plurality of the second weight members, The clutch device according to claim 1, wherein, when viewed in the axial direction of the output shaft, a portion of the first weight member is arranged symmetrically with respect to a straight line passing through the center of the output shaft, and a portion of the second weight member is arranged symmetrically with respect to the straight line.

4. A clutch device for transmitting or interrupting the rotational driving force of an input shaft to an output shaft, A clutch center is housed in a clutch housing that holds a plurality of input-side rotating plates which are rotated by the rotational drive of the input shaft, and which rotates together with the output shaft, A pressure member is provided so as to be able to approach or move away from the clutch center, and holds at least a portion of the plurality of output-side rotating plates arranged alternately with the input-side rotating plate, and is capable of pressing the input-side rotating plate and the output-side rotating plate. The clutch housing has a plurality of weight members configured to move from an inner radial position to an outer radial position by the centrifugal force accompanying its rotation, and the centrifugal clutch mechanism is capable of pressing the input side rotating plate and the output side rotating plate together when the weight members are in the outer radial position, thereby enabling the transmission of the rotational driving force of the input shaft to the output shaft, and releasing the pressing force between the input side rotating plate and the output side rotating plate when the weight members are in the inner radial position, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism described above is: The weight member is provided with a biasing member that biases it inward in the radial direction, The aforementioned weight member is A first weight member, the first force being the force required to move from the radially inner position to the radially outer position against the biasing force of the biasing member, A clutch device comprising: a second weight member, the second force being greater than the first force, is required to move from a radially inner position to a radially outer position against the biasing force of the biasing member.

5. The clutch device according to claim 4, wherein one of the first weight members is located between two of the second weight members that are aligned in the circumferential direction.

6. The weight member includes a plurality of the first weight members and a plurality of the second weight members, The clutch device according to claim 4, wherein, when viewed in the axial direction of the output shaft, a portion of the first weight member is arranged symmetrically with respect to a straight line passing through the center of the output shaft, and a portion of the second weight member is arranged symmetrically with respect to the straight line.

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