Clutch device

Abstract

In a clutch device 10: a pressure member 70 has a pressing surface 98P capable of pressing an input side rotating plate 20 and an output side rotating plate 22; a centrifugal clutch mechanism 120 includes a pressure contact member 150 that moves in an axial direction of an output shaft 15 as a result of a weight member 130 moving from a radially inner position PI to a radially outer position PO, thereby bringing the input side rotating plate 20 and the output side rotating plate 22 into pressure contact with each other; at least a portion of a buffer member 190 is located between the pressure contact member 150 and the pressing surface 98P with respect to the axial direction of the output shaft 15; and in the process of the weight member 130 moving from the radially inner position PI to the radially outer position PO, the buffer member 190 overlaps at least a portion of the weight member 130 when viewed in the axial direction of the output shaft 15.

Description

Clutch device

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

[0002] A saddle-type vehicle such as a motorcycle is provided with a clutch device capable of transmitting or 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 connected to the engine side (hereinafter referred to as an input shaft), an output member connected to the drive wheel side (hereinafter referred to as an output shaft), a clutch member connected to the output shaft (hereinafter referred to as a clutch center), and a pressure member capable of moving toward and away from the clutch center.

[0003] Further, the clutch device of Patent Document 1 includes a centrifugal clutch mechanism provided with a plurality of weight members that move in the radial direction, and a pressure contact member pressed by the weight members. The pressure contact member is pressed when the weight members move from a first position (for example, a radially inner position) to a second position (for example, a radially outer position) due to centrifugal force accompanying rotation of the clutch housing, moves in the axial direction of the output shaft, and is configured to press a drive-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. Thereby, the driving force of the engine is transmitted to the drive wheels.

[0004] Japanese Patent No. 7480281

[0005] Meanwhile, in the process in which the plurality of weight members move from the first position to the second position, variation may occur in the movement of the weight members. In this case, the pressure contact member may not move smoothly in the axial direction of the output shaft, and there is a risk that judder may occur between the pressure contact member and the pressure member.

[0006] The present invention has been made in view of the above points, and an object thereof is to provide a clutch device capable of suppressing the occurrence of judder in the process in which the weight members move from the first position to the second position.

[0007] 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 and move away from the clutch center, and which is capable of pressing the input-side rotating plates and a plurality of output-side rotating plates arranged alternately with the input-side rotating plates; and a plurality of weight members configured to be movable from a first position to a second position by the centrifugal force accompanying the rotation of the clutch housing, and when the weight members are in the first position, the pressure force between the input-side rotating plates and the output-side rotating plates is released, thereby interrupting the transmission of the rotational driving force of the input shaft to the output shaft, and The device comprises a centrifugal clutch mechanism, the rotational driving force transmitted from the input shaft to the output shaft increases as the weight member moves from the first position to the second position, and a cushioning member, wherein the pressure member has a pressing surface capable of pressing the input side rotating plate and the output side rotating plate, and the centrifugal clutch mechanism includes a pressure contact member that moves in the axial direction of the output shaft as the weight member moves from the first position to the second position to bring the input side rotating plate and the output side rotating plate into contact, wherein at least a portion of the cushioning member is located between the pressure contact member and the pressing surface with respect to the axial direction of the output shaft, and in the process of the weight member moving from the first position to the second position, the cushioning member overlaps with at least a portion of the weight member when viewed in the axial direction of the output shaft.

[0008] According to the clutch device of the present invention, at least a portion of the cushioning member is positioned between the contact member and the pressing surface with respect to the axial direction of the output shaft, and in the process of the weight member moving from a first position to a second position, the cushioning member overlaps with at least a portion of the weight member when viewed in the axial direction of the output shaft. According to the above embodiment, even if there is variation in the movement of the weight member and the contact member does not move smoothly in the axial direction of the output shaft, the input side rotating plate and the output side rotating plate are pressed by the cushioning member, and the axial distance between the input side rotating plate and the output side rotating plate of the output shaft is appropriately maintained, thereby suppressing the occurrence of judder between the weight member and the pressure member.

[0009] 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 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 and move away from the clutch center, and which is capable of pressing the input-side rotating plates and a plurality of output-side rotating plates arranged alternately with the input-side rotating plates; and a plurality of weight members configured to be movable from a first position to a second position by the centrifugal force accompanying the rotation of the clutch housing, wherein when the weight members are in the first position, the pressure force between the input-side rotating plates and the output-side rotating plates is released, thereby interrupting the input The device comprises a centrifugal clutch mechanism that blocks the transmission of the rotational driving force of the force shaft to the output shaft, and increases the rotational driving force transmitted from the input shaft to the output shaft as the weight member moves from the first position to the second position, and a spacing member, wherein the pressure member has a pressing surface capable of pressing the input side rotating plate and the output side rotating plate, the centrifugal clutch mechanism includes a pressing member that moves in the axial direction of the output shaft as the weight member moves from the first position to the second position to press the input side rotating plate and the output side rotating plate into contact, and the spacing member is configured to make the axial spacing between the input side rotating plate and the output side rotating plate of the output shaft uniform over the entire circumferential direction.

[0010] In another clutch device according to the present invention, the spacing member is configured to make the axial spacing of the output shafts between the input-side rotating plate and the output-side rotating plate uniform over the entire circumferential direction. According to the above embodiment, even if there is variation in the movement of the weight member and the pressure member does not move smoothly in the axial direction of the output shaft, the spacing member appropriately maintains the axial spacing of the output shafts between the input-side rotating plate and the output-side rotating plate, thereby suppressing the occurrence of judder between the weight member and the pressure member.

[0011] According to the present invention, it is possible to provide a clutch device that can suppress the occurrence of judder during the process in which a weight member moves from a first position to a second position.

[0012] Figure 1 is a cross-sectional view of a clutch device according to one embodiment. Figure 2 is a perspective view of a first clutch center and a second clutch center according to one embodiment. Figure 3 is a plan view of the first clutch center and the second clutch center according to one embodiment. Figure 4 is a perspective view of the first clutch center according to one embodiment. Figure 5 is a plan view of the first clutch center according to one embodiment. Figure 6 is a perspective view of the second clutch center according to one embodiment. Figure 7 is a plan view of the second clutch center according to one embodiment. Figure 8 is a perspective view of a pressure member according to one embodiment. Figure 9 is a plan view of a pressure member according to one embodiment. Figure 10 is a perspective view of a pressure member according to one embodiment. Figure 11A is a schematic diagram illustrating the operation of the center-side assist cam surface and the pressure-side assist cam surface. Figure 11B is a schematic diagram illustrating the operation of the center-side slipper cam surface and the pressure-side slipper cam surface. Figure 12A is a plan view of a cushioning member according to one embodiment. Figure 12B is a side view of a cushioning member according to one embodiment. Figure 13 is a perspective view showing a centrifugal clutch mechanism according to one embodiment, with the weight member positioned radially inward. Figure 14 is a plan view showing the positional relationship between the buffer member and the weight member located radially inward. Figure 15 is a plan view showing the positional relationship between the buffer member and the weight member located radially outward. Figure 16 is an enlarged cross-sectional view of the clutch device according to one embodiment with the weight member located radially inward. Figure 17 is an enlarged cross-sectional view of the clutch device according to one embodiment with the weight member located radially outward. Figure 18 is a diagram showing the relationship between the radial position of the weight member and the engine speed according to one embodiment. Figure 19 is a cross-sectional view of a modified clutch device.

[0013] 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.

[0014] 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 the engine, which is the drive source of the 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.

[0015] In the following description, the directions in which the pressure member 70 of the clutch device 10 approaches and moves away from the clutch center 40 are denoted as the left-right direction LR, the direction in which the pressure member 70 approaches the clutch center 40 is denoted as left L, and the direction in which the pressure member 70 moves away from the clutch center 40 is denoted as right R. The symbols L and R in the drawings represent left and right, respectively. Furthermore, the circumferential direction (i.e., rotational direction) of the clutch center 40 and the pressure member 70 is defined as the circumferential direction S. With respect to 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) is defined as 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) is defined as the second circumferential direction S2 (see Figure 2). In this embodiment, the axial direction of the output shaft 15 is the same as the left-right direction LR. 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). In this embodiment, the radial directions of the output shaft 15, clutch housing 30, clutch center 40, and pressure member 70 are the same. In the following description, unless otherwise specified, "radial direction" refers to the radial direction of the output shaft 15. However, the above direction is merely defined for the convenience of explanation and does not limit the installation configuration of the clutch device 10 in any way, nor does it limit the present invention in any way.

[0016] 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, an auxiliary clutch plate 180, and a cushioning member 190.

[0017] 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).

[0018] As shown in Figure 1, the output shaft 15 has a main body portion 15A that extends in the left-right direction L and R. 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, inside the oil passage 15H of the main body portion 15A.

[0019] 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 to the right R. A part of the push member 16B protrudes outward from the output shaft 15 (to the right R in this case) 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. The push rod 16A may be configured to slide electrically by a servo motor or the like.

[0020] The clutch housing 30 is formed from aluminum die-cast. 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 to the right R from the edge of the bottom wall 31. The clutch housing 30 holds a plurality of input-side rotating plates 20.

[0021] 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.

[0022] 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 by engaging with a notch 30C formed in the clutch housing 30. The input-side rotating plate 20 is provided so as to be displaceable along the axial direction (i.e., left-right direction LR) of the clutch housing 30. The input-side rotating plate 20 is provided so as to be rotatable integrally with the clutch housing 30.

[0023] 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 molded from aluminum die-cast. 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.

[0024] 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 the left-right direction (L and R). The clutch center 40 is rotationally driven together with the output shaft 15. As shown in Figures 2 and 3, 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 from the first clutch center 41. The second clutch center 51 is fitted onto the first clutch center 41.

[0025] The first clutch center 41 is connected to the output shaft 15. The first clutch center 41 rotates together with the output shaft 15. As shown in Figure 4, the first clutch center 41 includes an annular base wall 43, an output shaft holding portion 44 provided in the center of the base wall 43, a first outer peripheral wall 45 located radially outside the base wall 43 and extending to the right R, and a plurality of center-side cam portions 60 connected to the base wall 43 and the first outer peripheral wall 45.

[0026] The output shaft holder 44 is formed in a cylindrical shape. The output shaft holder 44 has an insertion hole 44H into which the output shaft 15 is inserted and spline fitted. The insertion hole 44H is formed through the base wall 43. Multiple spline grooves are formed along the axial direction (i.e., left-right direction LR) on the inner circumferential surface 44A of the output shaft holder 44 that forms the insertion hole 44H. The output shaft 15 is connected to the output shaft holder 44.

[0027] As shown in Figure 4, the first outer peripheral wall 45 is formed in an annular shape. The first outer peripheral wall 45 is located radially outward from the output shaft holding portion 44. The first outer peripheral wall 45 extends to the right R from the base wall 43.

[0028] As shown in Figure 4, the outer circumferential surface 45A of the first outer circumferential wall 45 is provided with a plurality of engagement grooves 48. The engagement grooves 48 are recessed radially inward from the outer circumferential surface 45A. The engagement grooves 48 accommodate the engagement projections 53 (see Figure 6), which will be described later, of the second clutch center 51. The engagement grooves 48 include a first engagement groove 48A and a second engagement groove 48B. The two second engagement grooves 48B are located between the two first engagement grooves 48A with respect to the circumferential direction S. The first engagement groove 48A is demarcated by the first center-side stopper surface 49T, the first center-side cam surface 49C, and the first section screen 49D, which will be described later. The second engagement groove 48B is demarcated by the first center-side stopper surface 49T, the first center side surface 49F, and the first section screen 49D, which will be described later.

[0029] As shown in Figure 4, the first outer peripheral wall 45 is provided with a first center-side stopper surface 49T, a first center-side cam surface 49C, a first center side surface 49F, and a first section surface 49D. The first center-side stopper surface 49T extends in the axial direction (i.e., left-right direction LR) of the output shaft 15 and also extends radially. The first center-side stopper surface 49T suppresses the relative rotation of the second clutch center 51 with respect to the first clutch center 41 in the first circumferential direction S1.

[0030] As shown in Figure 4, the first center-side cam surface 49C extends in the axial direction (i.e., left-right direction L / R) of the output shaft 15 and also extends radially. The first center-side cam surface 49C moves the second clutch center 51 in the axial direction (i.e., left-right direction L / R) when the first clutch center 41 rotates relative to the second clutch center 51. The first center-side cam surface 49C is configured to allow the second clutch center 51 to move to the right R. The first center-side cam surface 49C is inclined with respect to the axial direction (i.e., left-right direction L / R) of the output shaft 15.

[0031] As shown in Figure 4, the first center side surface 49F extends in the axial direction (i.e., left-right direction L / R) of the output shaft 15 and also extends radially. The first center side surface 49F prevents the second clutch center 51 from moving beyond a predetermined distance R to the right. The first section screen 49D extends in the axial direction (i.e., left-right direction L / R) of the output shaft 15 and also extends in the circumferential direction S. The first section screen 49D is located radially inward from the outer circumferential surface 45A.

[0032] 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 clutch being engaged (i.e., all input-side rotating plates 20 and the output-side rotating plate 22 are pressed against each other) and the clutch being disengaged (i.e., the input-side rotating plate 20 and the output-side rotating plate 22 are separated from each other, and there is a gap between the input-side rotating plate 20 and the output-side rotating plate 22). As shown in Figure 4, the center-side cam portion 60 is formed to protrude to the right R from the base wall 43. The center-side cam portions 60 are arranged at equal intervals in the circumferential direction S of the first clutch center 41. In this embodiment, the first clutch center 41 has three center-side cam portions 60, but the number of center-side cam portions 60 is not limited to three.

[0033] As shown in Figure 4, the center-side cam portion 60 is located radially outside the output shaft holding portion 44. The center-side cam portion 60 has a center-side assist cam surface 60A and a center-side slipper cam surface 60S. The center-side assist cam surface 60A is configured to generate a force (in this case, leftward L) 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 the pressure member 70 rotates relative to the first clutch center 41, such as during acceleration. 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-side 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-side rotating plate 20 and the output-side rotating plate 22 when the first clutch center 41 rotates relative to the pressure member 70, such as when decelerating. In adjacent center-side cam portions 60 with respect to the circumferential direction S, the center-side assist cam surface 60A of one center-side cam portion 60L and the center-side slipper cam surface 60S of the other center-side cam portion 60M are arranged facing each other in the circumferential direction S.

[0034] As shown in Figure 4, the first clutch center 41 is provided with a plurality of (three in this embodiment) 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 from the output shaft holding portion 44. The boss portions 62 extend toward the pressure member 70 (i.e., toward the right R). 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., left-right direction LR) of the clutch center 40.

[0035] As shown in Figures 4 and 5, 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 the left-right direction LR. The center-side cam hole 43H extends from the side of the output shaft holding portion 44 along the first outer peripheral wall 45. The center-side cam hole 43H is located between adjacent center-side cam portions 60 with respect to the circumferential direction S. When viewed from the axial direction of the output shaft 15 (i.e., the left-right direction LR), the center-side assist cam surface 60A and a portion of the center-side cam hole 43H overlap.

[0036] As shown in Figures 2 and 3, the second clutch center 51 is assembled to the first clutch center 41. The second clutch center 51 is provided so as to be movable relative to the first clutch center 41 in the axial direction of the output shaft 15 (i.e., in the left-right direction L and R). The second clutch center 51 holds at least a portion of the plurality of output-side rotating plates 22. The output-side rotating plates 22 are arranged alternately with the input-side rotating plates 20 in the left-right direction L and R. As shown in Figure 6, the second clutch center 51 includes an annular second outer peripheral wall 55, a center-side flange 68 extending radially outward from the second outer peripheral wall 55, and a center-side fitting portion 52.

[0037] As shown in Figure 6, a spline fitting portion 56 is provided on the outer circumferential surface 55A of the second outer circumferential wall 55. The spline fitting portion 56 has a plurality of center-side fitting teeth 57 extending in the axial direction (i.e., left-right direction LR) of the second clutch center 51 along the outer circumferential surface 55A of the second outer circumferential wall 55, a plurality of spline grooves 58 formed between adjacent center-side fitting teeth 57 and extending in the axial direction (i.e., left-right direction LR) of the second clutch center 51, and an oil discharge hole 59. The center-side fitting teeth 57 hold at least a portion of the plurality of output-side rotating plates 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 from the outer circumferential surface 55A of the second outer circumferential wall 55. Multiple spline grooves 58 are arranged in the circumferential direction S. Multiple spline grooves 58 are formed at equal intervals in the circumferential direction S. Multiple spline grooves 58 are formed to have the same shape. The oil discharge hole 59 is formed to penetrate the second outer peripheral wall 55 in the radial direction. 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 communicates the inside and outside of the second clutch center 51.

[0038] The output-side rotating plate 22 is held by the spline fitting portion 56 and the pressure member 70 of the second clutch center 51. A portion of the output-side rotating plate 22 is held by the second clutch center 51. More specifically, 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 member 70. More specifically, another portion of the output-side rotating plate 22 is held by the pressure-side fitting teeth 77 (see Figure 8), 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., left-right direction LR) of the second clutch center 51. The output-side rotating plate 22 is provided so as to be rotatable integrally with the second clutch center 51.

[0039] 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 a flat plate formed in an annular shape. The output-side rotating plate 22 is formed by punching out an annular shape from a thin 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.

[0040] As shown in Figure 6, the inner circumferential surface 55B of the second outer circumferential wall 55 is provided with a plurality of engaging projections 53. The engaging projections 53 protrude radially inward from the inner circumferential surface 55B. The engaging projections 53 are housed in the engaging grooves 48 (see Figure 4) of the first clutch center 41. The engaging projections 53 include a first engaging projection 53A and a second engaging projection 53B. The two second engaging projections 53B are located between the two first engaging projections 53A with respect to the circumferential direction S.

[0041] As shown in Figure 6, the first engaging projection 53A is provided with a second center-side stopper surface 54T, a second center-side cam surface 54C, and a second section surface 54D. The second engaging projection 53B is provided with a second center-side stopper surface 54T, a second center side surface 54F, and a second section surface 54D. The second center-side stopper surface 54T extends in the axial direction (i.e., left-right direction LR) of the output shaft 15 and also extends radially. The second center-side stopper surface 54T is provided so as to be in contact with the first center-side stopper surface 49T. The second center-side stopper surface 54T suppresses the second clutch center 51 from rotating relative to the first clutch center 41 in the first circumferential direction S1.

[0042] As shown in Figure 6, the second center-side cam surface 54C extends in the axial direction (i.e., left-right direction L / R) of the output shaft 15 and also extends radially. The second center-side cam surface 54C is provided so as to be in contact with the first center-side cam surface 49C. When the first clutch center 41 rotates relative to the second clutch center 51, the second center-side cam surface 54C moves the second clutch center 51 in the axial direction (i.e., left-right direction L / R). The second center-side cam surface 54C is configured to move the second clutch center 51 to the right R. The second center-side cam surface 54C is inclined with respect to the axial direction (i.e., left-right direction L / R) of the output shaft 15. When the second center-side cam surface 54C and the first center-side cam surface 49C come into contact, the second clutch center 51 moves to the right R, causing the input-side rotating plate 20 and the output-side rotating plate 22 to be pressed against each other by the center-side flange 68 and the pressure-side flange 98. This increases the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22.

[0043] As shown in Figure 6, the second center side surface 54F extends in the axial direction (i.e., left-right direction L / R) of the output shaft 15 and also extends radially. The second center side surface 54F is provided so as to be in contact with the first center side surface 49F. The second center side surface 54F prevents the second clutch center 51 from moving beyond a predetermined distance to the right R. The second section surface 54D extends in the axial direction (i.e., left-right direction L / R) of the output shaft 15 and also extends in the circumferential direction S. The second section surface 54D is located radially inward from the inner circumferential surface 55B.

[0044] Here, the operation of the engagement groove 48 of the first clutch center 41 and the engagement protrusion 53 of the second clutch center 51 will be described. When the engine speed increases and a weight member 130, which will be described later, of the centrifugal clutch mechanism 120 moves to a radially outer position, the input-side rotating plate 20 and the output-side rotating plate 22 are pressed against each other, and the rotational driving force of the input shaft is transmitted to the second clutch center 51. When the second clutch center 51 rotates in the first circumferential direction S1, the second center-side stopper surface 54T abuts on the first center-side stopper surface 49T. Here, the first center-side stopper surface 49T restrains the second clutch center 51 from rotating relative to the first clutch center 41 in the first circumferential direction S1. That is, the first clutch center 41 rotates integrally with the second clutch center 51 in the first circumferential direction S1.

[0045] On the other hand, when the rotational speed of the output shaft 15 exceeds the rotational speeds of the input gear 35 and the clutch housing 30, and back torque is applied from the output shaft 15 to the first clutch center 41, the first clutch center 41 rotates relative to the second clutch center 51, and the second clutch center 51 moves rightward R by the action of the first center-side cam surface 49C and the second center-side cam surface 54C. As a result, the input-side rotating plate 20 and the output-side rotating plate 22 are pressed into contact by the center-side flange 68 and the pressure-side flange 98, so that engine braking is applied. In addition, the first center side surface 49F abuts on the second center side surface 54F, so that the second clutch center 51 is restrained from moving rightward R by a predetermined distance or more.

[0046] As shown in FIG. 6, the center-side fitting portion 52 is located on the right side R relative to the engagement protrusion 53. The center-side fitting portion 52 is formed on the inner peripheral surface 55B of the second outer peripheral wall 55. The center-side fitting portion 52 is configured to be slidably fitted externally to a pressure-side fitting portion 88 (see FIG. 8) which will be described later. The inner diameter of the center-side fitting portion 52 is formed with a fitting tolerance that allows clutch oil flowing out from the tip end portion 15T (see FIG. 1) of the output shaft 15 to flow to the pressure-side fitting portion 88. That is, a gap is formed between the center-side fitting portion 52 and the pressure-side fitting portion 88 to be described later.

[0047] As shown in FIG. 6 and FIG. 7, the center-side flange 68 extends radially outward from the left end portion of the second outer peripheral wall 55. The center-side flange 68, together with a pressure-side flange 98 (see FIG. 8) of the pressure member 70 which will be described later, clamps the input-side rotary plate 20 and the output-side rotary plate 22. The center-side flange 68 is provided so as to be capable of pressing the input-side rotary plate 20 and the output-side rotary plate 22. The center-side flange 68 is a member that applies a pressing force to the input-side rotary plate 20 and the output-side rotary plate 22. The center-side flange 68 has a pressing surface 68P capable of pressing the input-side rotary plate 20 and the output-side rotary plate 22.

[0048] As shown in FIG. 1, the pressure member 70 is provided so as to be capable of moving toward and away from the clutch center 40. The pressure member 70 is provided so as to be rotatable relative to the clutch center 40. The pressure member 70 is configured to be capable of pressing the input-side rotary plate 20 and the output-side rotary plate 22. The pressure member 70 is disposed concentrically with the clutch center 40 and the clutch housing 30. The pressure member 70 is fitted inside the second clutch center 51. Thereby, the radial positioning of the pressure member 70 is achieved. The pressure member 70 is provided so as to be slidable in the left-right direction LR with respect to the second clutch center 51. The pressure member 70, the first clutch center 41, and the second clutch center 51 are configured to be capable of relative rotation with each other in the circumferential direction S. As shown in FIG. 8, the pressure member 70 has a main body 72, and a pressure-side flange 98 connected to the outer peripheral edge on the right R side of the main body 72 and extending radially outward. The main body 72 protrudes further to the left L than the pressure-side flange 98. The pressure-side flange 98 is configured to be capable of pressing the input-side rotary plate 20 and the output-side rotary plate 22. The pressure member 70 holds at least a part of the plurality of output-side rotary plates 22 arranged alternately with the input-side rotary plates 20.

[0049] As shown in FIG. 8, the main body 72 includes a cylindrical portion 80, a plurality of pressure-side cam portions 90, a pressure-side fitting portion 88, and a spring accommodating portion 84 (see FIG. 9).

[0050] 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.

[0051] As shown in Figure 8, 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 to the left L from the pressure-side flange 98. 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.

[0052] As shown in Figure 9, the pressure-side cam portion 90 is located radially outward from the cylindrical portion 80. The pressure-side cam portion 90 has a pressure-side assist cam surface 90A (see also Figure 10) 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 from the pressure member 70 toward the clutch center 40 (in this case, to the left L) in order to increase the pressing force (contact force) between the input-side rotating plate 20 and the output-side rotating plate 22 when the pressure member 70 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 the clutch center 40 rotates relative to the pressure member 70, 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.

[0053] 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 first rotational force in the circumferential direction S1 is applied to the pressure member 70, as shown in Figure 11A. As a result, due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, a force to the left L is generated on the pressure member 70, increasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22.

[0054] 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 circumferential rotational force S1 is applied to the clutch center 40, as shown in Figure 11B. 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 to the right R, 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.

[0055] As shown in Figure 8, the pressure-side fitting portion 88 is located radially outward from the pressure-side cam portion 90. The pressure-side fitting portion 88 is located to the right (R) of the pressure-side cam portion 90. The pressure-side fitting portion 88 is configured to be slidably fitted into the center-side fitting portion 52 (see Figure 6).

[0056] As shown in Figures 8 and 10, the pressure member 70 has a pressure-side cam hole 83H that penetrates the main body 72 and a portion of the pressure-side flange 98. The pressure-side cam hole 83H is located radially outward from the cylindrical portion 80. The pressure-side cam hole 83H extends radially from the side of the cylindrical portion 80 to radially 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. When 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 4) is inserted into the pressure-side cam hole 83H. The boss portion 62 penetrates the pressure-side cam hole 83H.

[0057] As shown in Figure 10, the spring housing portion 84 is formed in the pressure-side cam portion 90. The spring housing portion 84 is located radially outward from the cylindrical portion 80. The spring housing portion 84 is formed to be recessed from the right (R) to the left (L). The spring housing portion 84 is formed in a circular shape. The spring housing portion 84 houses the clutch spring 25.

[0058] As shown in Figure 1, the clutch device 10 is equipped with a clutch spring 25. The clutch spring 25 is housed in a spring housing 84. The clutch spring 25 extends in the left-right direction L and R. The left end 25L of the clutch spring 25 is in contact with the pressure member 70. The right end 25R of the clutch spring 25 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 left L). The clutch spring 25 is, for example, a coil spring made by winding spring steel in a spiral shape.

[0059] As shown in Figure 8, the pressure member 70 is provided with a plurality of pressure-side fitting teeth 87 arranged on the pressure-side flange 98. The pressure-side fitting teeth 87 hold at least a portion of the output-side rotating plate 22. The pressure-side fitting teeth 87 protrude to the left L from the pressure-side flange 98. The pressure-side fitting teeth 87 are located radially outward from the cylindrical portion 80. The pressure-side fitting teeth 87 are located radially outward from the pressure-side cam portion 90. The pressure-side fitting teeth 87 are located radially outward from the pressure-side fitting portion 88. The plurality of pressure-side fitting teeth 87 are arranged in the circumferential direction S. The plurality of pressure-side fitting teeth 87 are arranged at equal intervals in the circumferential direction S. In this embodiment, some of the pressure-side fitting teeth 87 have been removed, so the spacing in 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 left-right LR spacing (i.e., the axial spacing of the output shaft 15) between the input-side rotating plate 20 and the output-side rotating plate 22 when the weight member 130 of the centrifugal clutch mechanism 120, which will be described later, is in a radially inward position. The end plate 21 is an example of an adjustment plate.

[0060] As shown in Figures 8 and 10, the pressure-side flange 98 extends radially outward from the outer peripheral edge 72 of the main body. The pressure-side flange 98 is located radially outward from the cylindrical portion 80 (see also Figure 9). The pressure-side flange 98 is located radially outward from the pressure-side cam portion 90. The pressure-side flange 98, together with the center-side flange 68 of the clutch center 40, clamps the input-side rotating plate 20 and the output-side rotating plate 22. The pressure-side flange 98 is provided so as to be able to press the input-side rotating plate 20 and the output-side rotating plate 22. The pressure-side flange 98 is a member that applies pressing force to the input-side rotating plate 20 and the output-side rotating plate 22. The pressure-side flange 98 has a pressing surface 98P capable of pressing the input-side rotating plate 20 and the output-side rotating plate 22. In this embodiment, the pressing surface 98P indirectly presses the input-side rotating plate 20 and the output-side rotating plate 22 via the end plate 21. However, if the end plate 21 is not provided, the input-side rotating plate 20 and the output-side rotating plate 22 may be pressed directly. If the end plate 21 is not provided, the cushioning member 190 housed in the cushioning member housing 82 may be in direct contact with the input-side rotating plate 20 or the output-side rotating plate 22.

[0061] As shown in Figures 8 and 9, the pressure member 70 includes a cushioning member housing portion 82. The cushioning member housing portion 82 houses the cushioning member 190 (see Figure 1). The cushioning member housing portion 82 houses the cushioning member 190 such that a portion of the cushioning member 190 protrudes to the left L beyond the pressing surface 98P. The cushioning member housing portion 82 is formed on the pressure-side flange 98. The cushioning member housing portion 82 is formed to recess from the left L to the right R. The cushioning member housing portion 82 is formed over the entire circumferential direction S of the pressure-side flange 98. The cushioning member housing portion 82 is located radially outward from the pressure-side fitting teeth 87. The cushioning member housing portion 82 is located radially inward from the pressing surface 98P. The cushioning member housing portion 82 may also be formed on a portion of the pressing surface 98P.

[0062] The cushioning member 190 is, for example, a disc spring, a wave spring, a coil spring, etc., but is not limited to these. The cushioning member 190 is formed in an annular shape when viewed in the axial direction (i.e., left-right direction LR) of the output shaft 15. However, the cushioning member 190 is not limited to an annular shape. In this embodiment, as shown in Figures 12A and 12B, the cushioning member 190 is, for example, an annular wave spring. The wave spring may have a portion cut out in the circumferential direction S. In this embodiment, the pressure member 70 is provided with one cushioning member 190, but for example, a plurality of cushioning members 190 may be provided, spaced apart from each other in the circumferential direction S. As shown in Figure 1, at least a portion of the cushioning member 190 is located between the pressure contact member 150 of the centrifugal clutch mechanism 120 (described later) and the pressing surface 98P of the pressure side flange 98 with respect to the axial direction (i.e., left-right direction LR) of the output shaft 15. At least a portion of the cushioning member 190 is positioned between the end plate 21 and the pressing surface 98P with respect to the axial direction (i.e., left-right direction L / R) of the output shaft 15. The cushioning member 190 is held by the pressure member 70. The cushioning member 190 is held by the pressure member 70 so as to be able to expand and contract relative to it in the left-right direction L / R. The cushioning member 190 is housed in the cushioning member housing portion 82 of the pressure member 70. As shown in Figure 16, when the weight member 130 is in the radially inward position PI, a portion of the cushioning member 190 protrudes to the left L beyond the pressing surface 98P of the pressure side flange 98. When the weight member 130 is in the radially inward position PI, the length of the cushioning member 190 in the axial direction (i.e., left-right direction LR) of the output shaft 15 is longer than the length of the gap (i.e., left-right direction LR) between the input-side rotating plate 20 and the output-side rotating plate 22 when the weight member is in the radially inward position PI (the total length if there are multiple gaps). In this embodiment, the cushioning member 190 presses the end plate 21 to the left L. As a result, the cushioning member 190 indirectly presses the input-side rotating plate 20 and the output-side rotating plate 22. As shown in Figure 17, when the weight member 130 is in the radially outward position PO, the entire cushioning member 190 is housed in the cushioning member housing 82. At this time, the pressing surface 98P is in contact with the end plate 21.When viewed in the axial direction of the output shaft 15 (i.e., left-right direction L / R), at least a portion of the cushioning member 190 overlaps with the input side rotating plate 20. When viewed in the axial direction of the output shaft 15 (i.e., left-right direction L / R), at least a portion of the cushioning member 190 overlaps with the output side rotating plate 22. When viewed in the axial direction of the output shaft 15 (i.e., left-right direction L / R), at least a portion of the cushioning member 190 overlaps with the sliding surface between the input side rotating plate 20 and the output side rotating plate 22. When viewed in the axial direction of the output shaft 15 (i.e., left-right direction L / R), at least a portion of the cushioning member 190 overlaps with the retaining member 140 (see Figure 14), which will be described later, of the centrifugal clutch mechanism 120. When viewed in the axial direction of the output shaft 15 (i.e., left-right direction L / R), at least a portion of the cushioning member 190 overlaps with the housing portion 145 (see Figure 14), which will be described later, of the retaining member 140. The buffer member 190 is configured to make the axial distance (i.e., left-right direction LR) of the output shaft 15 between the input-side rotating plate 20 and the output-side rotating plate 22 uniform over the entire circumferential direction S as the weight member 130 moves from the radially inner position PI to the radially outer position PO. For example, when the weight member 130 moves from the radially inner position PI to the radially outer position PO, the axial distance (i.e., left-right direction LR) of the output shaft 15 between the input-side rotating plate 20 and the output-side rotating plate 22 gradually narrows, but the buffer member 190 ensures that this distance remains uniform over the entire circumferential direction S as it gradually narrows. "Making the spacing uniform over the entire circumferential direction S during the process in which the weight member 130 moves from the radially inner position PI to the radially outer position PO" includes both the case where "making the spacing uniform over the entire circumferential direction S throughout the entire process" and the case where "making the spacing uniform over the entire circumferential direction S at a predetermined timing in the process (when the weight member 130 is in a specific position)."If the buffer member 190 makes the distance between the input-side rotating plate 20 and the output-side rotating plate 22 uniform over the entire circumferential direction S throughout the entire process in which the weight member 130 moves from the radially inner position PI to the radially outer position PO, then even if there is variation in the movement of the weight member 130 and the pressure contact member 150 does not move smoothly in the axial direction (i.e., left-right direction LR) of the output shaft 15, the buffer member 190 maintains an appropriate distance between the input-side rotating plate 20 and the output-side rotating plate 22 in the axial direction of the output shaft 15 throughout the entire process, thereby suppressing the occurrence of judder between the weight member 130 and the pressure member 70 throughout the entire process. "To make the spacing uniform throughout the entire circumferential direction S" includes cases where the spacing is the same throughout the entire circumferential direction S, and cases where there is variation in the spacing throughout the entire circumferential direction S, but the variation in the spacing is within ±5% (for example, within ±3%, preferably within ±1%). The buffer member 190 is an example of a spacing-holding member.

[0063] As shown in Figures 14 and 15, during the process of the weight member 130 moving from the radially inner position PI to the radially outer position PO, the buffer member 190 overlaps with at least a portion of the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR). As shown in Figure 14, when the weight member 130 is at the radially inner position PI, the buffer member 190 does not overlap with the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR). As shown in Figure 15, when the weight member 130 is at the radially outer position PO, the buffer member 190 overlaps with at least a portion of the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR). Furthermore, when the weight member 130 is at the radially inner position PI and when the weight member 130 is at the radially outer position PO, the buffer member 190 may be positioned so as to overlap with the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR). As shown in Figure 14, when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR), the buffer member 190 is located on the center line LC that passes through the center 15C of the output shaft 15 and the center 130C of the circumferential direction S of the weight member 130. When viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR), on the center line LC, the buffer member 190 is located on the side of the outer peripheral edge of the housing portion 145 that intersects the center line LC, rather than the portion 145A of the inner peripheral edge of the housing portion 145 that intersects the center line LC. In the radial direction, the distance between the buffer member 190 and the portion 145A of the inner periphery of the housing 145 that intersects the center line LC is longer than the distance between the buffer member 190 and the portion 145B of the outer periphery of the housing 145 that intersects the center line LC. The buffer member 190 is located radially outward from the radial center 145C of the housing 145. In Figures 14 and 15, the buffer member 190 is shown by a dashed line.

[0064] As shown in Figure 1, the centrifugal clutch mechanism 120 is provided within the clutch housing 30. The centrifugal clutch mechanism 120 is located to the left L of the clutch center 40. The centrifugal clutch mechanism 120 is held by the clutch housing 30. The centrifugal clutch mechanism 120 is rotatably mounted integrally with the clutch housing 30. As shown in Figure 13, the centrifugal clutch mechanism 120 includes a plurality of weight members 130, a holding member 140, a pressure contact member 150, a spring (not shown) that biases the weight members 130 radially inward, and a contact member 170 (see also Figure 1). The centrifugal clutch mechanism 120 releases the pressure contact force between the input side rotating plate 20 and the output side rotating plate 22 when the weight members 130 are in the radially inward position PI (see Figure 16), thereby transmitting the rotational driving force of the input shaft to the output shaft 15 (i.e., the clutch is disengaged). In the centrifugal clutch mechanism 120, as the weight member 130 moves from the radially inner position PI to the radially outer position PO (see Figures 1 and 17) (during the process of the weight member 130 moving from the radially inner position PI to the radially outer position PO), the rotational driving force transmitted from the input shaft to the output shaft 15 increases (at this time, a semi-clutch state may occur). In the centrifugal clutch mechanism 120, when the weight member 130 is at the radially outer position PO, the input side rotating plate 20 and the output side rotating plate 22 are pressed against each other (i.e., the clutch is engaged), and the rotational driving force of the input shaft is transmitted to the output shaft 15 without slippage between the input side rotating plate 20 and the output side rotating plate 22. The centrifugal clutch mechanism 120 is configured to be able to press an auxiliary clutch plate 180 (see Figure 1). Note that the auxiliary clutch plate 180 is not required. The radially inner position PI is an example of a first position. The radially outer position PO is an example of a second position.

[0065] As shown in Figure 13, the retaining member 140 holds the weight member 130 so that it can move between a radially inner position PI and a radially outer position PO. 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 housing portions 145 (see Figure 1), and a pressing portion 149 (see Figure 1) capable of pressing the auxiliary clutch plate 180 (see Figure 1) toward the left L.

[0066] As shown in Figure 13, the main body 141 is formed in an annular shape. An insertion hole 141H into which the output shaft 15 (see Figure 1) is inserted is formed in the center of the main body 141.

[0067] As shown in Figure 13, the engaging claws 143 protrude radially outward from the outer peripheral edge 141E of the main body 141. The engaging claws 143 are integrally formed with the main body 141. The engaging claws 143 engage with the clutch housing 30 (see Figure 1). Multiple engaging claws 143 are arranged in the circumferential direction S.

[0068] As shown in Figure 1, the housing section 145 is formed in the main body 141 so as to be recessed in the axial direction of the output shaft 15 (i.e., in the left-right direction L). The housing section 145 is recessed from the right R to the left L. The housing section 145 houses the weight member 130 so as to be movable in the radial direction. Multiple housing sections 145 are arranged in the circumferential direction S.

[0069] As shown in Figure 13, the multiple weight members 130 are arranged in the circumferential direction S. The weight members 130 are configured to be movable from an inner radial position PI to an outer radial position PO 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 the right R. When no centrifugal force is applied, the weight members 130 are held at the inner radial position PI by a spring (not shown). As shown in Figure 1, when centrifugal force is applied, the weight members 130 move radially outward against the biasing force of the spring (not shown) and move to an outer radial position PO. The weight members 130 are held by the holding member 140 so as to be movable between the inner radial position PI and the outer radial position PO. The weight members 130 are housed in the housing portion 145 of the holding member 140.

[0070] As shown in Figure 1, the weight member 130 has a weight-side contact surface 130F. The weight-side contact surface 130F is provided so as to be in contact with the pressure-contacting member 150. The weight-side contact surface 130F is inclined with respect to the axial direction (i.e., left-right direction L and R) of the output shaft 15. The weight-side contact surface 130F is inclined to the left L as it moves from the radially inner side to the radially outer side. The weight-side contact surface 130F is configured to be slidable with respect to the pressure-contacting side contact surface 150F of the pressure-contacting member 150, which will be described later.

[0071] 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 (i.e., the right R side) with respect to the axial direction of the output shaft 15 (here, the left-right direction L and R), with the weight member 130 in between. The contact member 170 is a member that suppresses the movement of the weight member 130 to the right R.

[0072] The pressure contact member 150 is configured to press against the input side rotating plate 20 and the output side rotating plate 22 as the weight member 130 moves from a radially inner position PI to a radially outer position PO, thereby moving in the axial direction (here, to the right R) of the output shaft 15. 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 surface 150F and a pressing surface 150P. The pressure contact side surface 150F is provided so as to be in contact with the weight member 130. The pressure contact side surface 150F is inclined with respect to the axial direction (i.e., left-right direction LR) of the output shaft 15. The pressure contact side surface 150F is inclined to the left L as it moves from the radially inner side to the radially outer side. The pressure contact side surface 150F is configured to be slidable with respect to the weight side contact surface 130F of the weight member 130. Multiple pressure-contact surfaces 150F are provided for each weight member 130 along 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-contact surfaces 150F, causing the pressure member 150 to move away from the holding member 140 (i.e., to the right R). As a result, the pressing surface 150P of the pressure member 150 presses the center-side flange 68 of the second clutch center 51 toward the right R. As shown in Figure 13, the pressure member 150 has multiple engagement projections 153 formed along the circumferential direction S. The engagement projections 153 overlap with the engagement claws 143 of the holding member 140. The engagement projections 153 engage with the clutch housing 30. The retaining member 140 and the contacting member 150 are held by engaging with a notch 30C (see Figure 1) formed in the clutch housing 30. The retaining member 140 and the contacting member 150 are provided so as to be displaceable along the axial direction (i.e., left-right direction L / R) of the clutch housing 30. The retaining member 140 and the contacting member 150 are provided so as to be rotatable integrally with the clutch housing 30.

[0073] Figure 18 is a diagram showing the relationship between the radial position of the weight member 130 of the centrifugal clutch mechanism 120 according to this embodiment and the engine speed. In Figure 18, the vertical axis shows the radial position of the weight member 130, and the horizontal axis shows the engine speed. PI is the radially inner position, PO is the radially outer position, and PW1 is the first position. When the engine speed E0 (for example, idling speed), the weight member 130 is located at the radially inner position PI. In Figure 18, the solid line shows the position of the weight member 130 as the engine speed increases.

[0074] As shown in Figure 18, the weight member 130 is configured to start power transmission from the input-side rotating plate 20 to the output-side rotating plate 22 when it reaches the first position PW1 in the radial direction by moving from the radially inner position PI to the radially outer position PO (i.e., the saddle-type vehicle is configured to start). In other words, it is in a semi-clutch state. For example, the weight member 130 starts moving radially outward at engine speed E1, reaches the first position PW1 at engine speed E2, and starts power transmission from the input-side rotating plate 20 to the output-side rotating plate 22. As the weight member 130 starts moving radially outward, the weight member 130 presses the pressure contact member 150 to the right R. Alternatively, power transmission from the input-side rotating plate 20 to the output-side rotating plate 22 may be started at an engine speed lower than the engine speed at which the weight member 130 reaches the first position PW1, for example, at engine speed EA2.

[0075] As shown in Figure 18, at engine speed ES, all input-side rotating plates 20 and all output-side rotating plates 22 are pressed against each other (i.e., the clutch is engaged). From engine speed E2 to engine speed E3, the biasing force of the clutch spring 25 is greater than the pressing force of the weight member 130, so the weight member 130 remains in the first position PW1 even as the engine speed increases. At engine speed E3, the pressing force of the weight member 130 exceeds the biasing force of the clutch spring 25, so the weight member 130 begins to move radially outward again. When the weight member 130 is located radially outside the first position PW1 (for example, at engine speed E3 or higher), it presses the contact member 150 to the right R, moving the contact member 150 to the right R. The pressure member 70 is pressed to the right R by the contact member 150 and moves to the right R, separating from the clutch center 40 (for example, the first clutch center 41). This makes the pressure member 70 and the clutch center 40 rotatable relative to each other. The weight member 130 reaches the radially outer position PO when the engine speed is E4. At the engine speed E3, all input-side rotating plates 20 and all output-side rotating plates 22 may be pressed against each other (i.e., the clutch may be engaged). That is, at the same time the clutch is engaged, the pressure member 70 may separate from the clutch center 40.

[0076] As shown in Figure 18, after the weight member 130 reaches the first position PW1, the center-side assist cam surface 60A and the pressure-side assist cam surface 90A come into contact. For example, at engine speed EA1, the center-side assist cam surface 60A and the pressure-side assist cam surface 90A come into contact. Here, engine speed EA1 is higher than engine speed E2 and lower than engine speed E3. From engine speed EA1 to engine speed E3, the center-side assist cam surface 60A and the pressure-side assist cam surface 90A are in contact, but no assist force is generated. When the engine speed exceeds E3, the pressure member 70 separates from the clutch center 40, allowing the pressure member 70 and the clutch center 40 to rotate relative to each other. Due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, an assist force is generated in the pressure member 70, increasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22. The center-side assist cam surface 60A and the pressure-side assist cam surface 90A may come into contact before the weight member 130 reaches the first position PW1. For example, the center-side assist cam surface 60A and the pressure-side assist cam surface 90A may come into contact when the engine speed is EA2. Here, the engine speed EA2 is higher than the engine speed E1 and lower than the engine speed E2. Furthermore, the center-side assist cam surface 60A and the pressure-side assist cam surface 90A may come into contact after the weight member 130 begins moving radially outward from the first position PW1. For example, the center-side assist cam surface 60A and the pressure-side assist cam surface 90A may come into contact when the engine speed EA3. Here, the engine speed EA3 is higher than the engine speed E3 and lower than the engine speed E4. In this case, as soon as the center-side assist cam surface 60A and the pressure-side assist cam surface 90A come into contact, an assist force is generated in the pressure member 70 due to the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, and the pressure contact force between the input-side rotating plate 20 and the output-side rotating plate 22 increases.

[0077] As shown in Figure 1, the auxiliary clutch plate 180 is provided inside 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 180H into which the output shaft 15 is inserted and spline-fitted. The auxiliary clutch plate 180 is positioned to the left L of a part of the centrifugal clutch mechanism 120. The auxiliary clutch plate 180 is adjacent to the first clutch center 41.

[0078] The auxiliary clutch plate 180 is configured to be pressed by the centrifugal clutch mechanism 120 (in this case, 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 in the radially outer position PO), 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, 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 in the radially inner position PI), thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15.

[0079] 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 to the right R by a predetermined distance or more. The stopper plate 100 is fixed to the first clutch center 41. The stopper plate 100 is fixed to the boss portion 62 of the first clutch center 41 by bolts 28. The stopper plate 100 is fixed to the boss portion 62 with the clutch spring 25 arranged in the spring housing portion 84.

[0080] The centrifugal clutch mechanism 120 of this embodiment is configured in a so-called normally open state. When the throttle of a saddle-type vehicle (for example, a motorcycle) is not operated, that is, when the engine is idling, the weight member 130 is in the radially inward position PI. When the weight member 130 is in the radially inward position PI, the centrifugal clutch mechanism 120 releases the contact force between the input-side rotating plate 20 and the output-side rotating plate 22, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15. When the weight member 130 is in the radially inward position PI, the input-side rotating plate 20 and the output-side rotating plate 22 are separated from each other, and there is a gap between the input-side rotating plate 20 and the output-side rotating plate 22. In other words, the clutch is disengaged.

[0081] When the throttle is operated to increase the engine speed from idling speed (when the throttle is not operated; engine speed E0), at engine speed E1, the weight member 130 begins to move from the radially inner position PI to the radially outer position PO due to centrifugal force. As the weight member 130 begins to move toward the radially outer position PO, the weight member 130 begins to press the contact member 150 to the right R. That is, the contact member 150 begins to move to the right R. When the weight member 130 reaches the first radial position PW1 at engine speed E2, the contact member 150 presses the input side rotating plate 20 and the output side rotating plate 22 against each other, causing the input side rotating plate 20 and the output side rotating plate 22 to come into contact with each other, resulting in a semi-clutch state. In other words, the input-side rotating plate 20 and the output-side rotating plate 22 are pressed together by the pressure contact member 150, resulting in a semi-clutch state, which is between a state where the clutch is disengaged and a state where the clutch is engaged (i.e., all input-side rotating plates 20 and all output-side rotating plates 22 are pressed against each other). As the input-side rotating plate 20 and the output-side rotating plate 22 come into contact with each other, the transmission of rotational driving force from the input shaft to the output shaft 15 begins. In other words, the saddle-type vehicle starts moving. In the semi-clutch state, the pressure contact force between the input-side rotating plate 20 and the output-side rotating plate 22 is intermediate, so the rotational driving force from the engine is transmitted to the transmission and drive wheels (rear wheels), etc., with some slippage. Note that the semi-clutch state may also occur at the same time that the weight member 130 begins to move from the radially inner position PI to the radially outer position PO. Alternatively, the saddle-type vehicle may be set to start when it enters a semi-clutch state (a state in which the input-side rotating plate 20 and the output-side rotating plate 22 are in contact with each other) and the rotational driving force transmitted from the input shaft to the output shaft 15 increases further.

[0082] When the throttle is further operated from a half-clutch state to further increase the engine speed, the centrifugal force acting on the weight member 130 increases. Here, the pressure member 70 is biased to the left L by the biasing force of the clutch spring 25, and the left L side surface of the pressure member 70 is in contact with the right R side surface of the clutch center 40 (for example, the first clutch center 41). Therefore, when the centrifugal force acting on the weight member 130 increases, the weight member 130 remains in the first radial position PW1 until the pressing force that the weight member 130 exerts on the pressure contact member 150 to the right R exceeds the biasing force of the clutch spring 25, and presses the input side rotating plate 20 and the output side rotating plate 22 via the pressure contact member 150. In other words, the pressing surface 150P of the contact member 150 presses the center-side flange 68 of the second clutch center 51 toward the right (R), thereby pressing the input-side rotating plate 20 and the output-side rotating plate 22. The left-side surface L of the pressure member 70 contacts the right-side surface R of the clutch center 40 (for example, the first clutch center 41), and the pressure member 70 and the clutch center 40 do not rotate relative to each other until the pressing force of the weight member 130 pressing the contact member 150 toward the right (R) exceeds the biasing force of the clutch spring 25. As the engine speed increases further, at engine speed ES, all input-side rotating plates 20 and all output-side rotating plates 22 are pressed against each other (in close contact), and the clutch is engaged. Furthermore, after the weight member 130 moves radially outward from the first position PW1 (for example, when the engine speed is EA3), all input-side rotating plates 20 and all output-side rotating plates 22 may be pressed against each other (closely in contact), that is, in a state where the clutch is engaged.

[0083] When the throttle is further operated from a clutch-engaged state to increase the engine speed, at engine speed E3, the pressing force of the weight member 130 against the contact member 150 to the right R exceeds the biasing force of the clutch spring 25, and the pressure member 70 is pressed to the right R by the contact member 150 and moves to the right R, separating from the clutch center 40 (for example, the first clutch center 41). In other words, contact between the left L side surface of the pressure member 70 and the right R side surface of the clutch center 40 (for example, the first clutch center 41) is released. As a result, the weight member 130 begins to move radially outward from the first position PW1. As the engine speed increases, the weight member 130 moves to the radially outward position PO at engine speed E4. Here, when the engine speed exceeds E3, the pressure member 70 separates from the clutch center 40 (for example, the first clutch center 41), allowing the pressure member 70 and the clutch center 40 to rotate relative to each other. Furthermore, as the pressure member 70 separates from the clutch center 40 (for example, the first clutch center 41), the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A generates a force (so-called assist force) on the pressure member 70 in the direction toward the clutch center 40 (for example, the first clutch center 41) (in this case, to the left L), increasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22. Note that at engine speeds lower than the engine speed at which the saddle-type vehicle starts, the pressure-side assist cam surface 90A and the center-side assist cam surface 60A may be in contact. Furthermore, the pressure-side assist cam surface 90A and the center-side assist cam surface 60A may be in contact at the engine speed at which the saddle-type vehicle starts moving. Alternatively, the pressure-side assist cam surface 90A and the center-side assist cam surface 60A may be in contact at an engine speed higher than the engine speed at which the saddle-type vehicle starts moving. In this case, the pressure-side assist cam surface 90A and the center-side assist cam surface 60A may be in contact after the pressure member 70 has separated from the clutch center 40 (for example, the first clutch center 41).

[0084] In this embodiment, as the weight member 130 moves from the radially inner position PI to the radially outer position PO, the rotational driving force transmitted from the input shaft to the output shaft 15 increases continuously. However, the transmitted rotational driving force does not necessarily have to increase continuously. For example, the rotational driving force transmitted from the input shaft to the output shaft 15 may be kept constant for a portion of the movement of the weight member 130 from the radially inner position PI to the radially outer position PO, thereby making the increase in rotational driving force discontinuous. Furthermore, the increase in rotational driving force transmitted from the input shaft to the output shaft 15 does not have to be constant. For example, the increase in rotational driving force transmitted from the input shaft to the output shaft 15 may change as the weight member 130 moves from the radially inner position PI to the radially outer position PO.

[0085] As described above, according to the clutch device 10 of this embodiment, at least a portion of the cushioning member 190 is positioned between the contact member 150 and the pressing surface 98P with respect to the axial direction of the output shaft 15 (i.e., the left-right direction LR), and in the process of the weight member 130 moving from the radially inner position PI to the radially outer position PO, the cushioning member 190 overlaps with at least a portion of the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR). According to the above embodiment, even if there is variation in the movement of the weight member 130 and the contact member 150 does not move smoothly in the axial direction of the output shaft 15 (i.e., the left-right direction LR), the input side rotating plate 20 and the output side rotating plate 22 etc. are pressed by the cushioning member 190, and the distance between the input side rotating plate 20 and the output side rotating plate 22 etc. in the axial direction of the output shaft 15 (i.e., the left-right direction LR) is appropriately maintained, so the occurrence of judder between the weight member 130 and the pressure member 70 can be suppressed. Furthermore, since the cushioning member 190 is formed in an annular shape when viewed in the axial direction of the output shaft 15, even if there is variation in the movement of the weight member 130, the axial distance between the input-side rotating plate 20 and the output-side rotating plate 22 on the output shaft 15 is appropriately maintained along the circumferential direction S. Therefore, the occurrence of judder between the weight member 130 and the pressure member 70 can be suppressed more reliably.

[0086] In the clutch device 10 of this embodiment, the cushioning member 190 is a wave spring. According to the above configuration, the input side rotating plate 20 and the output side rotating plate 22 are pressed by the wave spring, eliminating or reducing the gap between the input side rotating plate 20 and the output side rotating plate 22 in the axial direction (i.e., left-right direction L and R) of the output shaft 15, thereby suppressing the occurrence of judder. Furthermore, the wave spring is formed in an annular shape when viewed in the axial direction of the output shaft 15. Therefore, the gap between the input side rotating plate 20 and the output side rotating plate 22 is eliminated or reduced over the circumferential direction S, thereby more reliably suppressing the occurrence of judder.

[0087] In the clutch device 10 of this embodiment, the axial length of the output shaft 15 of the cushioning member 190 when the weight member 130 is in the radially inner position PI is longer than the axial gap of the output shaft 15 between the input side rotating plate 20 and the output side rotating plate 22 when the weight member 130 is in the radially inner position PI. According to the above embodiment, the occurrence of judder can be suppressed more reliably from the state in which the weight member 130 is in the radially inner position PI to the state in which it is in the radially outer position PO.

[0088] In the clutch device 10 of this embodiment, at least a portion of the cushioning member 190 is positioned between the end plate 21 and the pressing surface 98P with respect to the axial direction (i.e., left-right direction L / R) of the output shaft 15. According to the above configuration, the input-side rotating plate 20 and the output-side rotating plate 22 are pressed by the cushioning member 190, eliminating or reducing the axial gap (i.e., left-right direction L / R) between the input-side rotating plate 20 and the output-side rotating plate 22 and the output shaft 15, thereby suppressing the occurrence of judder. Furthermore, since at least a portion of the cushioning member 190 is adjacent to the end plate 21, the axial gap between the input-side rotating plate 20 and the output-side rotating plate 22 and the output shaft 15 can be easily adjusted.

[0089] In the clutch device 10 of this embodiment, when the weight member 130 is at the radially outer position PO, the cushioning member 190 overlaps with at least a portion of the weight member 130 when viewed in the axial direction (i.e., left-right direction LR) of the output shaft 15. According to the above embodiment, even if there is variation in the movement of the weight member 130 when the weight member 130 approaches the radially outer position PO, the pressing force by the weight member 130 is absorbed by the cushioning member 190, thus suppressing the occurrence of judder.

[0090] In the clutch device 10 of this embodiment, when the weight member 130 is at the radially inner position PI, the cushioning member 190 does not overlap with the weight member 130 when viewed in the axial direction (i.e., left-right direction LR) of the output shaft 15. According to the above embodiment, even if there is variation in the movement of the weight member 130 when the weight member 130 approaches the radially inner position PI, the pressing force by the weight member 130 is absorbed by the cushioning member 190, thus suppressing the occurrence of judder.

[0091] In the clutch device 10 of this embodiment, when viewed in the axial direction (i.e., left-right direction LR) of the output shaft 15, the cushioning member 190 is located on the center line LC that passes through the center 15C of the output shaft 15 and the center 130C of the circumferential direction S of the weight member 130. That is, the cushioning member 190 is located in the central part of the circumferential direction S, which is the part in which the weight member 130 presses the input-side rotating plate 20 and the output-side rotating plate 22 via the pressure contact member 150. As a result, the distance between the input-side rotating plate 20 and the output-side rotating plate 22 in the axial direction (i.e., left-right direction LR) of the output shaft 15 is appropriately maintained over the circumferential direction S, and the occurrence of judder between the weight member 130 and the pressure member 70 can be effectively suppressed.

[0092] In the clutch device 10 of this embodiment, when viewed in the axial direction (i.e., left-right direction LR) of the output shaft 15, the cushioning member 190 is located on the center line LC passing through the center 15C of the output shaft 15 and the center 130C of the circumferential direction S of the weight member 130, on the outer edge of the housing portion 145 that intersects the center line LC, rather than on the outer edge of the housing portion 145 that intersects the center line LC, rather than on the inner edge of the housing portion 145 that intersects the center line LC, the cushioning member 190 is located on the outer edge 145B side of the inner edge of the housing portion 145. According to the above embodiment, the cushioning member 190 is located further outward in the radial direction. Therefore, the distance between the input-side rotating plate 20 and the output-side rotating plate 22 in the axial direction (i.e., left-right direction LR) of the output shaft 15 is appropriately maintained over the circumferential direction S, and the occurrence of judder between the weight member 130 and the pressure member 70 can be effectively suppressed.

[0093] In the clutch device 10 of this embodiment, when viewed in the axial direction of the output shaft 15 (i.e., left-right direction L / R), at least a portion of the cushioning member 190 overlaps with the sliding surfaces of the input-side rotating plate 20 and the output-side rotating plate 22. According to the above embodiment, the distance between the sliding surfaces of the input-side rotating plate 20 and the output-side rotating plate 22 in the axial direction of the output shaft 15 (i.e., left-right direction L / R) is appropriately maintained, and the occurrence of judder between the weight member 130 and the pressure member 70 can be effectively suppressed.

[0094] In the clutch device 10 of this embodiment, at least a portion of the cushioning member 190 overlaps with the input side rotating plate 20 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction L and R). According to the above embodiment, the cushioning member 190 can effectively press against the input side rotating plate 20 and the output side rotating plate 22.

[0095] 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.

[0096] In the embodiment described above, the clutch device 10 was equipped with an end plate 21, but it is not required to be equipped with an end plate 21. If the clutch device 10 is not equipped with an end plate 21, at least a portion of the cushioning member 190 is positioned between the input side rotating plate 20 or the output side rotating plate 22, which is located on the side furthest to the pressing surface 98P (here, to the right R) with respect to the axial direction of the output shaft 15 (i.e., left-right direction LR), and the pressing surface 98P. In this case, the cushioning member 190 is provided so as to be able to contact the input side rotating plate 20 or the output side rotating plate 22, and presses the input side rotating plate 20 or the output side rotating plate 22 to the left L. According to the above embodiment, the input-side rotating plate 20 and the output-side rotating plate 22 are pressed by the cushioning member 190, eliminating or reducing the axial gap (i.e., left-right direction L / R) of the output shaft 15 between the input-side rotating plate 20 and the output-side rotating plate 22, thereby suppressing the occurrence of judder.

[0097] In the above-described embodiment, when the weight member 130 is at the radially inner position PI, the buffer member 190 does not overlap with the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR), however at least a part of the buffer member 190 may overlap with the weight member 130. Also, when the weight member 130 is at the radially outer position PO, the buffer member 190 overlaps with at least a part of the weight member 130 when viewed in the axial direction of the output shaft 15 (i.e., the left-right direction LR), however the buffer member 190 does not have to overlap with the weight member 130.

[0098] In the above-described embodiment, the cushioning member 190 was housed in the cushioning member housing portion 82 of the pressure member 70, but is not limited to this. For example, as shown in Figure 19, the cushioning member 190 may be located between the second clutch center 51 and the pressure member 70. In the example shown in Figure 19, the cushioning member 190 is located between the second clutch center 51 and the pressure member 70. More specifically, the cushioning member 190 is located between the center-side fitting teeth 57 of the second clutch center 51 and the pressure member 70 (for example, the portion radially inward from the pressure-side fitting teeth 87). According to the above embodiment, the cushioning member 190 appropriately maintains the axial distance (i.e., left-right direction LR) of the output shaft 15 between the second clutch center 51 and the pressure member 70, thereby suppressing the occurrence of judder in the pressure member 70. The cushioning member 190 may be positioned between the output-side rotating plate 22 and the input-side rotating plate 20, which are held by the pressure-side fitting teeth 87.

[0099] In the embodiment described above, the weight member 130 was configured to move as a whole between a first position (a radially inner position PI) and a second position (a radially outer position PO), but is not limited thereto. For example, a part of the weight member may be configured to swing (move) between the first position and the second position around a pivot axis that is perpendicular to the axis of the output shaft 15 and located radially outward from the axis of the output shaft 15. Furthermore, the ability of the weight member to move from the first position to the second position includes cases where the entire weight member is movable as described above, and cases where only a part of the weight member is movable (swings).

[0100] In the embodiment described above, the pressing surface 150P of the contact member 150 is configured to press the center-side flange 68 of the second clutch center 51 toward the right (R), but is not limited to this. The pressing surface 150P of the contact member 150 may also be configured to directly press the input-side rotating plate 20 or the output-side rotating plate 22 toward the right (R).

[0101] In the embodiment described above, as shown in Figure 1, the pressure member 70 holds one output-side rotating plate 22, but it may also hold multiple output-side rotating plates 22.

[0102] In the embodiment described above, the pressure member 70 held a portion of the output-side rotating plate 22 and the clutch center 40 held another portion of the output-side rotating plate 22, but the embodiment is not limited to this. For example, the pressure member 70 may hold the entire output-side rotating plate 22, and the clutch center 40 may not hold the output-side rotating plate 22 at all.

[0103] 10 Clutch device 15 Output shaft 20 Input side rotating plate 21 End plate 22 Output side rotating plate 30 Clutch housing 40 Clutch center 41 First clutch center 51 Second clutch center 57 Center side fitting teeth 70 Pressure member 82 Cushioning member housing 87 Pressure side fitting teeth 98 Pressure side flange 98P Pressing surface 120 Centrifugal clutch mechanism 130 Weight member 140 Holding member 145 Housing 150 Pressure contact member 190 Cushioning member

Claims

1. 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 and move away from the clutch center and capable of pressing the input-side rotating plates and a plurality of output-side rotating plates arranged alternately with the input-side rotating plates; a centrifugal clutch mechanism having a plurality of weight members configured to be movable from a first position to a second position by the centrifugal force accompanying the rotation of the clutch housing, and which, when the weight members are in the first position, releases the pressure force between the input-side rotating plates and the output-side rotating plates, thereby interrupting the transmission of the rotational driving force of the input shaft to the output shaft, and which increases the rotational driving force transmitted from the input shaft to the output shaft as the weight members move from the first position to the second position; and a buffer member, wherein the pressure member is A clutch device having a pressing surface capable of pressing the input side rotating plate and the output side rotating plate, wherein the centrifugal clutch mechanism includes a pressure contact member that moves in the axial direction of the output shaft as the weight member moves from a first position to a second position, causing the input side rotating plate and the output side rotating plate to come into contact, at least a portion of the cushioning member is located between the pressure contact member and the pressing surface with respect to the axial direction of the output shaft, and in the process of the weight member moving from the first position to the second position, the cushioning member overlaps with at least a portion of the weight member when viewed in the axial direction of the output shaft.

2. The clutch device according to claim 1, wherein the cushioning member is a wave spring.

3. The clutch device according to claim 2, wherein the axial length of the buffer member in relation to the output shaft when the weight member is in the first position is longer than the axial gap between the input side rotating plate and the output side rotating plate in relation to the output shaft when the weight member is in the first position.

4. The clutch device according to claim 1, wherein at least a portion of the cushioning member is located between the input side rotating plate and a specific rotating plate that is closest to the pressing surface with respect to the axial direction of the output shaft, and the pressing surface, with respect to the axial direction of the output shaft.

5. The clutch device according to claim 1, comprising an adjustment plate for adjusting the distance between the input-side rotating plate and the output-side rotating plate in the axial direction of the output shaft when the weight member is in the first position, wherein at least a portion of the cushioning member is located between the adjustment plate and the pressing surface with respect to the axial direction of the output shaft.

6. The clutch device according to claim 1, wherein when the weight member is in the second position, the buffer member overlaps with at least a portion of the weight member when viewed in the axial direction of the output shaft.

7. The clutch device according to claim 6, wherein when the weight member is in the first position, the buffer member does not overlap with the weight member when viewed in the axial direction of the output shaft.

8. The clutch device according to claim 1, wherein, when viewed in the axial direction of the output shaft, the cushioning member is located on a center line passing through the center of the output shaft and the circumferential center of the weight member.

9. The clutch device according to claim 1, wherein the centrifugal clutch mechanism comprises a retaining member having a housing portion for housing the weight member, and when viewed in the axial direction of the output shaft, the buffer member is located on the outer peripheral edge of the housing portion that intersects the center line, rather than on the outer peripheral edge of the housing portion that intersects the center line, than on the outer peripheral edge of the housing portion that intersects the center line, compared with the inner peripheral edge of the housing portion that intersects the center line.

10. The clutch device according to claim 1, wherein, when viewed in the axial direction of the output shaft, at least a portion of the cushioning member overlaps with the sliding surface between the input side rotating plate and the output side rotating plate.

11. The clutch device according to claim 1, wherein at least a portion of the cushioning member overlaps with the input side rotating plate when viewed in the axial direction of the output shaft.

12. The clutch device according to claim 1, wherein the clutch center includes a first clutch center connected to the output shaft, and a second clutch center assembled to the first clutch center and provided to be movable in the axial direction of the output shaft relative to the first clutch center and holding at least a portion of the output side rotating plate, and the cushioning member is located between the second clutch center and the pressure member.

13. 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 and move away from the clutch center and capable of pressing the input-side rotating plates and a plurality of output-side rotating plates arranged alternately with the input-side rotating plates; a centrifugal clutch mechanism having a plurality of weight members configured to be movable from a first position to a second position by the centrifugal force accompanying the rotation of the clutch housing, and which, when the weight members are in the first position, releases the pressure force between the input-side rotating plates and the output-side rotating plates, thereby interrupting the transmission of the rotational driving force of the input shaft to the output shaft, and which increases the rotational driving force transmitted from the input shaft to the output shaft as the weight members move from the first position to the second position; and a spacing member, wherein the pressure member is A clutch device having a pressing surface capable of pressing the input side rotating plate and the output side rotating plate, wherein the centrifugal clutch mechanism includes a pressing member that moves in the axial direction of the output shaft as the weight member moves from the first position to the second position, thereby pressing the input side rotating plate and the output side rotating plate into contact, and the spacing member is configured to make the axial spacing between the input side rotating plate and the output side rotating plate in the output shaft uniform over the entire circumferential direction during the process in which the weight member moves from the first position to the second position.

14. The clutch device according to claim 13, wherein the spacing member is a wave spring.

15. The clutch device according to claim 13, wherein at least a portion of the spacing member is located between the input side rotating plate and a specific rotating plate that is closest to the pressing surface with respect to the axial direction of the output shaft, and the pressing surface, with respect to the axial direction of the output shaft.

16. The clutch device according to claim 13, comprising an adjustment plate for adjusting the distance between the input-side rotating plate and the output-side rotating plate in the axial direction of the output shaft when the weight member is in the first position, wherein at least a portion of the distance-holding member is located between the adjustment plate and the pressing surface with respect to the axial direction of the output shaft.

Images