Clutch device

Abstract

A centrifugal clutch mechanism (120) of a clutch device (10) is provided with: a holding member (124) that holds a weight member (122) so as to be movable between a radially inward position and a radially outward position; a spring (135) that urges the weight member (122) inward in the radial direction; a crimping member (126) that crimps the input-side rotating piece (20) and the output-side rotating piece (22) by moving the counterweight member (122) in the axial direction of the output shaft (15) from a radially inner position to a radially outer position; and a biasing member (140) that is positioned between the holding member (124) and the crimping member (126) in the axial direction of the output shaft (15), biases the weight member (122) held by the holding member (124) in the axial direction of the output shaft (15), and allows the weight member (122) to move in the radial direction.

Description

Technical Field

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

[0002] A straddle-type vehicle such as a motorized two-wheeler includes a clutch device capable of transmitting and cutting off the rotational driving force of a power source such as an engine to a driving wheel. For example, Patent Document 1 discloses a clutch device having an input member (hereinafter referred to as an input shaft) connected to the engine side, an output member (hereinafter referred to as an output shaft) connected to the driving wheel side, a clutch member (hereinafter referred to as a clutch center portion) connected to the output shaft, and a pressure member capable of approaching or separating from the clutch center portion.

[0003] In addition, the clutch device of Patent Document 1 includes a centrifugal clutch mechanism having a weight member that moves in the radial direction. The weight member moves from a position on the inner side in the radial direction to a position on the outer side in the radial direction by the centrifugal force accompanying the rotation of the clutch housing, and presses the driving-side clutch plate (hereinafter referred to as the input-side rotating plate) against the driven-side clutch plate (hereinafter referred to as the output-side rotating plate), thereby enabling the driving force of the engine to be transmitted to the wheel.

[0004] [Prior Art Documents]

[0005] [Patent Documents]

[0006] [Patent Document 1] Japanese Patent Application Laid-Open No. 2022-30211 Summary of the Invention

[0007] [Problems to be Solved by the Invention]

[0008] In addition, the centrifugal clutch mechanism includes a holding member and a pressing member arranged in the axial direction of the output shaft. The holding member holds the weight member so as to be movable in the radial direction. The pressing member is configured to press the input-side rotating plate against the output-side rotating plate as the weight member moves in the radial direction. In addition, the weight member is biased radially inward by a spring of the holding member. Here, in the axial direction of the output shaft, gaps are provided between the weight member and the holding member and the pressing member, respectively. Therefore, due to vibrations of the engine or the like, the weight member may vibrate in the axial direction of the output shaft. When the clutch housing rotates in a state where the weight member vibrates in the axial direction of the output shaft, the axial thrust of the output shaft generated on the weight member due to the centrifugal force accompanying the rotation of the clutch housing may not be effectively transmitted to the pressing member.

[0009] The present invention has been made in view of the above problems, and an object thereof is to provide a clutch device capable of effectively transmitting the axial thrust of the output shaft generated on the weight member due to centrifugal force to the pressing member.

[0010] [Means for Solving the Problem]

[0011] The clutch device of the present invention is a clutch device that transmits or cuts off the rotational driving force of the input shaft with respect to the output shaft, and is characterized by including: a clutch central portion that is housed in a clutch housing that holds a plurality of input-side rotating pieces that are rotationally driven by the rotational driving of the input shaft, and rotates together with the output shaft; a pressure member that is arranged to be able to approach or separate from the clutch central portion and can press the input-side rotating pieces and a plurality of output-side rotating pieces that are alternately arranged with the input-side rotating pieces; and a plurality of weight members that are configured to be able to move from a position on the inner side in the radial direction to a position on the outer side by centrifugal force accompanying the rotation of the clutch housing, and when the weight members are located at the position on the outer side in the radial direction, can cause the input-side rotating pieces and the output-side rotating pieces to be in pressure contact to become a state where the rotational driving force of the input shaft can be transmitted to the output shaft, and when the weight members are located at the position on the inner side in the radial direction, can release the pressure contact force between the input-side rotating pieces and the output-side rotating pieces to cut off the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism includes: a holding member that holds the weight members so as to be able to move between the position on the inner side in the radial direction and the position on the outer side; an elastic member that applies a force to the weight members in the radial direction toward the inner side; a pressure contact member that moves in the axial direction of the output shaft as the weight members move from the position on the inner side in the radial direction to the position on the outer side, and causes the input-side rotating pieces and the output-side rotating pieces to be in pressure contact; and a biasing member that is located between the holding member and the pressure contact member in the axial direction of the output shaft, applies a force to the weight members held by the holding member in the axial direction of the output shaft, and allows the weight members to move in the radial direction.

[0012] In the clutch device according to the present invention, the biasing member of the centrifugal clutch mechanism is located between the holding member and the pressure contact member in the axial direction of the output shaft, applies a force to the weight members held by the holding member in the axial direction of the output shaft, and allows the weight members to move in the radial direction. According to this method, the weight members are applied a force in the axial direction of the output shaft by the biasing member, so even if there is vibration from an engine or the like, vibration in the axial direction of the output shaft can be suppressed. As a result, the weight members can move smoothly in the radial direction, so the axial thrust of the output shaft generated in the weight members due to the centrifugal force accompanying the rotation of the clutch housing can be effectively transmitted to the pressure contact member.

[0013] [Advantages of the Invention]

[0014] According to the present invention, it is possible to provide a clutch device that can effectively transmit the thrust in the axial direction of the output shaft generated in the counterweight member due to centrifugal force to the crimping member. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 is a cross-sectional view of the clutch device of the first embodiment.

[0016] Figure 2 is a perspective view of the first clutch center portion of the first embodiment.

[0017] Figure 3 is a perspective view of the first clutch center portion of the first embodiment.

[0018] Figure 4 is a perspective view of the second clutch center portion of the first embodiment.

[0019] Figure 5 is a top view of the second clutch center portion of the first embodiment.

[0020] Figure 6 is a perspective view of the pressure member according to the first embodiment;

[0021] Figure 7 is a perspective view of the first pressure member according to the first embodiment;

[0022] Figure 8 is a perspective view of the first pressure member according to the first embodiment;

[0023] Figure 9 is a perspective view of the second pressure member according to the first embodiment;

[0024] Figure 10 is a perspective view of the second pressure member according to the first embodiment;

[0025] Figure 11A is a schematic diagram for explaining the action of the central side auxiliary cam surface and the pressure side auxiliary cam surface.

[0026] Figure 11B is a schematic diagram for explaining the action of the center side sliding cam surface and the pressure side sliding cam surface.

[0027] Figure 12 is a perspective view of the centrifugal clutch mechanism of the first embodiment.

[0028] Figure 13 is a cross-sectional view of the centrifugal clutch mechanism of the first embodiment.

[0029] Figure 14 is a perspective view showing the state where the crimping member is removed from the centrifugal clutch mechanism of the first embodiment.

[0030] Figure 15 It is a perspective view showing a state in which the crimping member and the guide member are removed from the centrifugal clutch mechanism of the first embodiment.

[0031] Figure 16 It is a top view showing a state in which the crimping member and the guide member are removed from the centrifugal clutch mechanism of the first embodiment.

[0032] Figure 17 It is a perspective view showing the biasing member of the centrifugal clutch mechanism of the first embodiment.

[0033] Figure 18 It is a top view showing a part of the centrifugal clutch mechanism of the second embodiment, and is a top view showing a state in which the weight member is located radially inward.

[0034] Figure 19 It is a perspective view showing the weight member according to the second embodiment.

[0035] Figure 20 It is a top view showing the weight member of the second embodiment.

[0036] Figure 21 It is a perspective view showing the weight member according to the second embodiment.

[0037] Figure 22 It is a bottom view showing the weight member according to the second embodiment.

[0038] Figure 23 It is a side view showing the weight member according to the second embodiment.

[0039] Figure 24 It is a top view showing a part of the centrifugal clutch mechanism according to the third embodiment, and is a top view showing a state in which the weight member is located radially inward.

[0040] Figure 25 It is a perspective view showing the weight member according to the third embodiment.

[0041] Figure 26 It is a bottom view showing the weight member according to the third embodiment.

[0042] Figure 27 It is a side view showing the weight member according to the third embodiment.

[0043] Figure 28A It is a perspective view showing the structure of the biasing member and its periphery of the fourth embodiment.

[0044] Figure 28BIt is a cross-sectional view showing the structure of the biasing member and its surroundings according to the fourth embodiment.

[0045] Figure 29A It is a perspective view showing the structure of the biasing member and its surroundings according to the fifth embodiment.

[0046] Figure 29B It is a cross-sectional view showing the structure of the biasing member and its surroundings according to the fifth embodiment. Specific Embodiments

[0047] Hereinafter, embodiments of the clutch device of the present invention will be described with reference to the drawings. In addition, the embodiments described herein are of course not intended to particularly limit the present invention. In addition, the same reference numerals are given to components and parts that perform the same functions, and redundant descriptions are appropriately omitted or simplified.

[0048] <First Embodiment>

[0049] Figure 1 It is a cross-sectional view of the clutch device 10 of the present embodiment. The clutch device 10 is provided, for example, in a straddle-type vehicle such as a motorcycle. The clutch device 10 is a device that transmits or cuts off the rotational driving force of the input shaft (crankshaft) of an engine, which is a power source of a motorcycle, to the output shaft 15. The clutch device 10 is a device for transmitting or cutting off the rotational driving force of the input shaft to the drive wheel (rear wheel) via the output shaft 15. The clutch device 10 is arranged between the engine and the transmission.

[0050] In the following description, the direction in which the pressure member 70 of the clutch device 10 approaches and separates from the clutch center portion 40 is set as the direction D, the direction in which the pressure member 70 approaches the clutch center portion 40 is set as the first direction D1, and the direction in which the pressure member 70 separates from the clutch center portion 40 is set as the second direction D2. In addition, the circumferential direction (i.e., the rotational direction) of the clutch center portion 40 and the pressure member 70 is set as the circumferential direction S, and the direction from one central side cam portion 60 toward the other central side cam portion 60 (the direction from one pressure side cam portion 90 toward the other pressure side cam portion 90) in the circumferential direction S is set as the first circumferential direction S1 (refer to Figure 2 ), and the direction from the other central side cam portion 60 toward one central side cam portion 60 (the direction from the other pressure side cam portion 90 toward one pressure side cam portion 90) is set as the second circumferential direction S2 (refer to Figure 2 ). In addition, the radial direction of the output shaft 15 is set as the radial direction M, the direction away from the output shaft 15 is set as the outer side M1 (refer to Figure 20 ), and the direction toward the output shaft 15 is set as the inner side M2 (refer to Figure 20). In the present embodiment, the axial direction of the output shaft 15 is the same as the direction D. Further, the pressure member 70 and the clutch center portion 40 rotate along the first circumferential direction S1 (i.e., the direction from the central side auxiliary cam surface 60A of one central side cam portion 60 toward the central side sliding cam surface 60S). However, the said direction is merely a direction determined for convenience of explanation, and does not limit the installation mode of the clutch device 10 nor the present invention.

[0051] As Figure 1 shown, 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 portion 40, a pressure member 70, a stopper plate 100, a centrifugal clutch mechanism 120, and an auxiliary clutch plate 150.

[0052] As Figure 1 shown, the output shaft 15 is a hollow shaft body. One end portion of the output shaft 15 rotatably supports an input gear 35 and a clutch housing 30 described later via a needle bearing 28A. The output shaft 15 fixedly supports the clutch center portion 40 via a nut 28B. That is, the output shaft 15 rotates integrally with the clutch center portion 40. The other end portion of the output shaft 15 is connected to, for example, a transmission (not shown) of a motorcycle.

[0053] As Figure 1 shown, the output shaft 15 includes a main body portion 15A extending in the direction D. The main body portion 15A has an oil flow path 15H inside thereof for the clutch oil to flow. The oil flow path 15H is formed between a sleeve 16C externally fitted to a 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 flow path 15H of the main body portion 15A.

[0054] As Figure 1 shown, a push rod 16A and a pressing member 16B adjacent to the push rod 16A are provided in the oil flow path 15H of the output shaft 15. The push rod 16A and the pressing member 16B are provided so as to be slidable within the sleeve 16C. One end portion (the left end portion in the drawing) of the push rod 16A is connected to a clutch operating lever (not shown) of a motorcycle, and slides within the sleeve 16C by the operation of the clutch operating lever, pressing the pressing member 16B in the second direction D2. A part of the pressing member 16B protrudes outward of the output shaft 15 (here, in the second direction D2) and is connected to a release bearing 18 provided on the pressure member 70. The sleeve 16C and the pressing member 16B are formed to be thinner than the inner diameter of the main body portion 15A to ensure the fluidity of the clutch oil within the oil flow path 15H.

[0055] The clutch housing 30 is formed of an aluminum die casting. The clutch housing 30 is formed in a bottomed cylindrical shape. As Figure 1As shown, the clutch housing 30 has a bottom wall 31 formed in a substantially circular shape and a side wall 33 extending from the edge of the bottom wall 31 in the second direction D2. The clutch housing 30 holds a plurality of input-side rotating plates 20.

[0056] As Figure 1 shown, 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 via a torque damper 35A by a rivet 35B. The input gear 35 meshes with a drive gear (not shown) that rotates by the rotational drive of the input shaft of the engine. The input gear 35 rotates and drives integrally with the clutch housing 30 independently of the output shaft 15.

[0057] The input-side rotating plate 20 rotates and drives by the rotational drive of the input shaft. As Figure 1 shown, the input-side rotating plate 20 is held on the inner peripheral surface of the side wall 33 of the clutch housing 30. The input-side rotating plate 20 is held by spline fitting to the clutch housing 30. The input-side rotating plate 20 is arranged to be displaceable along the axial direction (i.e., direction D) of the clutch housing 30. The input-side rotating plate 20 is arranged to be able to rotate integrally with the clutch housing 30.

[0058] The input-side rotating plate 20 is a member that presses against the output-side rotating plate 22. The input-side rotating plate 20 is formed in a ring shape. The input-side rotating plate 20 is formed by die casting of aluminum. A friction material (not shown) composed of multiple sheets of paper is pasted on the front and back surfaces of the input-side rotating plate 20. Grooves for holding the clutch oil with a depth of several hundred μm are formed between the friction members.

[0059] As Figure 1 shown, the clutch center portion 40 is housed in the clutch housing 30. The clutch center portion 40 is arranged concentrically with the clutch housing 30. The clutch center portion 40 holds a plurality of output-side rotating plates 22. The output-side rotating plates 22 and the input-side rotating plates 20 are alternately arranged in the direction D. The clutch center portion 40 rotates and drives together with the output shaft 15. The clutch center portion 40 includes a first clutch center portion 41 and a second clutch center portion 51. The first clutch center portion 41 and the second clutch center portion 51 are assembled with each other. The second clutch center portion 51 is located on the outer side M1 in the radial direction M of the first clutch center portion 41. The second clutch center portion 51 is externally fitted to the first clutch center portion 41.

[0060] As Figure 2 shown, the first clutch center portion 41 includes an output shaft holding portion 42, an annular base wall 43 located on the outer side M1 in the radial direction M of the output shaft holding portion 42, and a plurality of center-side cam portions 60.

[0061] As Figure 1As shown, the output shaft 15 is connected to the output shaft holding portion 42. A first pressure member 71, which will be described later, is externally fitted to the output shaft holding portion 42. As Figure 2 shown, the output shaft holding portion 42 is formed in a cylindrical shape. An insertion hole 45 for inserting and spline-fitting the output shaft 15 is formed in the output shaft holding portion 42. The insertion hole 45 penetrates the output shaft holding portion 42. A plurality of fitting teeth 47 extending in the axial direction (i.e., direction D) of the output shaft 15 are formed on the inner wall 45A of the output shaft holding portion 42 that divides the insertion hole 45. The fitting teeth 47 are fitted with the output shaft 15.

[0062] The center-side cam portion 60 is formed in a table shape having a cam surface, which is composed of an inclined surface of an auxiliary & sliding (registered trademark) mechanism that generates an auxiliary torque, which is a force that increases the pressing force (contact force) between the input-side rotating piece 20 and the output-side rotating piece 22, or a sliding torque, which is a force that reduces the pressing force (contact force) between the input-side rotating piece 20 and the output-side rotating piece 22 and causes a transition to a semi-clutch state. As Figure 2 shown, the center-side cam portion 60 is formed to protrude from the surface 43D2 on the second direction D2 side of the base wall 43 in the second direction D2. The center-side cam portions 60 are arranged at equal intervals in the circumferential direction S of the first clutch center portion 41. In the present embodiment, the first clutch center portion 41 has three center-side cam portions 60, but the number of center-side cam portions 60 is not limited to three.

[0063] As Figure 2 shown, the center-side cam portion 60 is located on the outer side M1 in the radial direction M of the output shaft holding portion 42. The center-side cam portion 60 has a center-side auxiliary cam surface 60A (also refer to Figure 3 ) and a center-side sliding cam surface 60S. The center-side auxiliary cam surface 60A is configured to generate a force in the direction of approaching the clutch center portion 40 of the pressure member 70 in order to increase the pressing force (contact force) between the input-side rotating piece 20 and the output-side rotating piece 22 when relatively rotating with respect to the pressure member 70. In the present embodiment, when generating the said force, the position of the pressure member 70 with respect to the clutch center portion 40 does not change, and the pressure member 70 does not need to physically approach the clutch center portion 40. In addition, the pressure member 70 may also be physically displaced with respect to the clutch center portion 40. The center-side sliding cam surface 60S is configured to separate the pressure member 70 from the clutch center portion 40 in order to reduce the pressing force (contact force) between the input-side rotating piece 20 and the output-side rotating piece 22 when relatively rotating with respect to the pressure member 70. Among the center-side cam portions 60 adjacent in the circumferential direction S, the center-side auxiliary cam surface 60A of one center-side cam portion 60L and the center-side sliding cam surface 60S of the other center-side cam portion 60M are arranged to face each other in the circumferential direction S.

[0064] As Figure 2As shown, the first clutch center portion 41 has a plurality (three in this embodiment) of boss portions 62. The boss portions 62 are components 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 at a position radially M outside M1 of the output shaft holding portion 42. The boss portions 62 extend toward the pressure member 70 (i.e., toward the second direction D2). The boss portions 62 are provided on the central side cam portion 60. The boss portions 62 are provided between the central side auxiliary cam surface 60A and the central side sliding cam surface 60S in the circumferential direction S. A threaded hole 62H into which a bolt 28 (refer to Figure 1 ) is inserted is formed in the boss portion 62. The threaded hole 62H extends along the axial direction (i.e., direction D) of the clutch center portion 40.

[0065] As Figure 2 and Figure 3 shown, the first clutch center portion 41 has a central side cam hole 43H that penetrates a part of the base wall 43. The central side cam hole 43H penetrates the base wall 43 along the direction D. The central side cam hole 43H is located between adjacent central side cam portions 60 in the circumferential direction S. When viewed from the axial direction of the clutch center portion 40, a part of the central side auxiliary cam surface 60A overlaps with the central side cam hole 43H.

[0066] As Figure 2 shown, the first clutch center portion 41 has a plurality of engaging grooves 49. The engaging grooves 49 are formed on the outer peripheral surface of the base wall 43. The engaging grooves 49 are recessed from the outer peripheral surface of the base wall 43 toward the inside M2 in the radial direction M.

[0067] As Figure 4 shown, the second clutch center portion 51 includes an annular outer peripheral wall 52, a flange 68 that extends radially M outside M1 from the outer peripheral wall 52, and a central side fitting portion 54. The second clutch center portion 51 holds a plurality of output side rotating pieces 22 that are alternately arranged with the input side rotating piece 20 in the direction D.

[0068] As Figure 4As shown, a spline fitting portion 56 is provided on the outer peripheral surface of the outer peripheral wall 52. The spline fitting portion 56 has a plurality of center-side fitting teeth 57 that extend along the outer peripheral surface of the outer peripheral wall 52 in the axial direction (i.e., direction D) of the second clutch center portion 51, a plurality of spline grooves 58 that are formed between adjacent center-side fitting teeth 57 and extend in the axial direction (i.e., direction D) of the second clutch center portion 51, and an oil discharge hole 59. The center-side fitting teeth 57 hold the output-side rotating plate 22. The plurality of central-side fitting teeth 57 are arranged in the circumferential direction S. The plurality of central-side fitting teeth 57 are formed at equal intervals in the circumferential direction S. The plurality of center-side fitting teeth 57 are formed in the same shape. The center-side fitting teeth 57 project from the outer peripheral surface of the outer peripheral wall 52 toward the outer side M1 in the radial direction M. The oil discharge hole 59 is formed to penetrate the outer peripheral wall 52 in the radial direction M. The oil discharge hole 59 is formed between adjacent center-side fitting teeth 57. That is, the oil discharge hole 59 is formed in the spline groove 58. The oil discharge hole 59 is formed in the center-side fitting portion 54. The oil discharge hole 59 communicates the inside and the outside of the second clutch center portion 51. The oil discharge hole 59 is a hole that discharges clutch oil and the like that has flowed out from the output shaft 15 into the clutch center portion 40 to the outside of the clutch center portion 40. The clutch oil discharged from the oil discharge hole 59 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22 located on the outer side M1 in the radial direction M of the oil discharge hole 59.

[0069] The output-side rotating plate 22 is held by the spline fitting portion 56 of the second clutch center portion 51 and the pressure member 70. A part of the output-side rotating plate 22 is held by the center-side fitting teeth 57 and the spline grooves 58 of the second clutch center portion 51 through spline fitting. Another part of the output-side rotating plate 22 is held by the pressure-side fitting teeth 87 (refer to Figure 6 ) of the pressure member 70 to be described later. The output-side rotating plate 22 is arranged to be displaceable along the axial direction (i.e., direction D) of the clutch center portion 40. The output-side rotating plate 22 is arranged to be rotatable integrally with the clutch center portion 40. All the output-side rotating plates 22 can be held by the pressure member 70 (for example, the pressure-side engaging teeth 87).

[0070] The output-side rotating plate 22 is a member that presses against the input-side rotating plate 20. The output-side rotating plate 22 is a flat plate formed in a ring shape. The output-side rotating plate 22 is formed by punching a thin plate made of SPCC material into a ring shape. In addition, the friction member provided on the input-side rotating plate 20 can be provided on the output-side rotating plate 22 instead of the input-side rotating plate 20, or can be provided on the input-side rotating plate 20 and the output-side rotating plate 22 respectively.

[0071] As Figure 4 shown, the center-side fitting portion 54 is formed on the inner peripheral surface of the outer peripheral wall 52. The center-side fitting portion 54 is configured to be externally fitted to the pressure-side fitting portion 88 (refer to Figure 6). The inner diameter of the central side fitting portion 54 is formed to have a fitting tolerance that allows the clutch oil flowing out from the front end portion 15T of the output shaft 15 (refer to Figure 1 ) to flow through to the pressure side fitting portion 88. That is, a gap is formed between the central side fitting portion 54 and the pressure side fitting portion 88.

[0072] As Figure 4 and Figure 5 shown, the second clutch center portion 51 has a plurality of engaging protrusions 55. The engaging protrusions 55 engage with the engaging grooves 49 of the first clutch center portion 41 (refer to Figure 2 ). The engaging protrusions 55 are formed on the inner peripheral surface of the outer peripheral wall 52. The engaging protrusions 55 protrude from the inner peripheral surface of the outer peripheral wall 52 toward the inner side M2 in the radial direction M. The engaging protrusions 55 are located at a position closer to the first direction D1 than the outer peripheral wall 52.

[0073] As Figure 1 shown, the pressure member 70 is arranged to be able to approach or separate from the clutch center portion 40. The pressure member 70 is arranged to be able to rotate relative to the clutch center portion 40. The pressure member 70 is configured to be able to press the input side rotating plate 20 and the output side rotating plate 22. The pressure member 70 is arranged concentrically with the clutch center portion 40 and the clutch housing 30. As Figure 6 shown, the pressure member 70 includes a first pressure member 71 and a second pressure member 81. The first pressure member 71 and the second pressure member 81 are assembled with each other. The second pressure member 81 is located on the outer side M1 in the radial direction M of the first pressure member 71. The second pressure member 81 is externally fitted to the first pressure member 71. The first pressure member 71 and the second pressure member 81 are configured to be able to move relative to each other in the direction D. The first pressure member 71 and the second pressure member 81 are configured to be able to rotate relative to each other within a range of a specified angle in the circumferential direction S. Here, the range of the specified angle refers to the range of the angle from Figure 11A the state (the state where the pressure side auxiliary cam surface 90A contacts the central side auxiliary cam surface 60A, which will be described later) to Figure 11B the state (more specifically, the state where the pressure side sliding cam surface 90S contacts the central side sliding cam surface 60S and the second pressure member 81 abuts against the limit plate 100, which will be described later). Thus, since the pressure member 70 includes the first pressure member 71 and the second pressure member 81, the first pressure member 71 and the second pressure member 81 can be moved (rotated) independently of each other.

[0074] As Figure 7 and Figure 8 shown, the first pressure member 71 is formed in a cylindrical shape. The first pressure member 71 is configured to be externally fitted to the output shaft holding portion 42 (refer to Figure 1 ). The first pressure member 71 houses the front end portion 15T of the output shaft 15 (refer toFigure 1 ). The first pressing member 71 is a part that receives the pressing force from the pressing member 16B (refer to Figure 1 ). The first pressure member 71 is configured to be movable in the second direction D2 through clutch operation (e.g., operation of a clutch lever or a button). The first pressure member 71 is a part that receives the clutch oil flowing out from the front end portion 15T of the output shaft 15. The first pressure member 71 is externally fitted to the output shaft holding portion 42, thereby positioning the pressure member 70 relative to the clutch center portion 40. A release bearing 18 is disposed inside the first pressure member 71. The first pressure member 71 holds the release bearing 18.

[0075] As Figure 1 shown, the second pressure member 81 is configured to be pressed by the first pressure member 71 and movable in the second direction D2. The second pressure member 81 is internally fitted to the second clutch center portion 51. Thereby, the positioning in the radial direction M of the second pressure member 81 is performed. The second pressure member 81 is provided to be slidable relative to the second clutch center portion 51 in the direction D. The second pressure member 81 and the second clutch center portion 51 are configured to be rotatable relative to each other in the circumferential direction S. As Figure 9 shown, the second pressure member 81 has a main body 82 and a flange 98 that is connected to the outer peripheral edge on the second direction D2 side of the main body 82 and extends toward the outer side M1 in the radial direction M. The main body 82 protrudes more toward the first direction D1 than the flange 98. The flange 98 is located at a position on the outer side M1 in the radial direction M with respect to a cylindrical portion 80 described later. The second pressure member 81 holds a plurality of output-side rotating plates 22 that are alternately arranged with the input-side rotating plate 20. The flange 98 is configured to be able to press the input-side rotating plate 20 and the output-side rotating plate 22.

[0076] As Figure 9 shown, the main body 82 includes a cylindrical portion 80, a plurality of pressure-side cam portions 90, a pressure-side fitting portion 88, and a spring housing portion 84 (refer to Figure 10 ).

[0077] As Figure 9 shown, the cylindrical portion 80 has a partition wall 80A formed in a cylindrical shape. The cylindrical portion 80 is integrally formed with the pressure-side cam portion 90. The pressure-side cam portion 90 is located on the outer side M1 in the radial direction M of the partition wall 80A. As Figure 6 shown, the first pressure member 71 is housed in the cylindrical portion 80. The inner peripheral surface 85 of the partition wall 80A is configured to be slidable relative to the outer peripheral surface 75 of the first pressure member 71 in the direction D.

[0078] The pressure-side cam portion 90 is formed in a table shape having a cam surface, and the cam surface is formed by the center-side cam portion 60 (refer to Figure 2It is composed of an inclined surface of an auxiliary & sliding (registered trademark) mechanism that generates an auxiliary torque or a sliding torque when sliding on (etc.). As Figure 9 shown, the pressure-side cam portion 90 is formed to protrude in the first direction D1 more than the flange 98. The pressure-side cam portions 90 are arranged at equal intervals in the circumferential direction S of the second pressure member 81. In the present embodiment, the second pressure member 81 has three pressure-side cam portions 90, but the number of pressure-side cam portions 90 is not limited to three.

[0079] As Figure 9 shown, the pressure-side cam portion 90 is located outside M1 in the radial direction M of the cylindrical portion 80. The pressure-side cam portion 90 has a pressure-side auxiliary cam surface 90A (also refer to Figure 10 ), and a pressure-side sliding cam surface 90S. The pressure-side auxiliary cam surface 90A is configured to be able to contact the central-side auxiliary cam surface 60A. The pressure-side auxiliary cam surface 90A is configured such that when relatively rotating with respect to the clutch center portion 40, in order to increase the pressing force (contact pressure) between the input-side rotating piece 20 and the output-side rotating piece 22, a force in the direction of approaching the clutch center portion 40 of the pressure member 70 is generated. The pressure-side sliding cam surface 90S is configured to be able to contact the center-side sliding cam surface 60S. The pressure-side sliding cam surface 90S is configured such that when relatively rotating with respect to the clutch center portion 40, in order to reduce the pressing force (contact pressure) between the input-side rotating piece 20 and the output-side rotating piece 22, the pressure member 70 is separated from the clutch center portion 40. Among the pressure-side cam portions 90 adjacent in the circumferential direction S, the pressure-side auxiliary cam surface 90A of one pressure-side cam portion 90L and the pressure-side sliding cam surface 90S of the other pressure-side cam portion 90M are arranged to face each other in the circumferential direction S.

[0080] Here, the functions of the central-side cam portion 60 and the pressure-side cam portion 90 will be described. When the engine speed rises to a state where the rotational driving force input to the input gear 35 and the clutch housing 30 can be transmitted to the output shaft 15 via the clutch center portion 40, as Figure 11A shown, a rotational force in the first circumferential direction S1 is applied to the pressure member 70. Therefore, by the action of the central-side auxiliary cam surface 60A and the pressure-side auxiliary cam surface 90A, a force in the first direction D1 is generated in the pressure member 70. Thereby, the contact pressure between the input-side rotating piece 20 and the output-side rotating piece 22 is increased.

[0081] 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 a reverse torque is generated, as Figure 11BAs shown, a rotational force in the first circumferential direction S1 is imparted to the clutch center portion 40. Therefore, by the action of the center-side sliding cam surface 60S and the pressure-side sliding cam surface 90S, the pressure member 70 is moved in the second direction D2 to release the pressing force between the input-side rotating piece 20 and the output-side rotating piece 22. Thereby, it is possible to avoid adverse conditions to the engine and transmission caused by reverse torque. In addition, by applying a rotational force in the first circumferential direction S1 to the clutch center portion 40, the first pressure member 71 and the second pressure member 81 rotate relative to each other in the circumferential direction S.

[0082] As Figure 9 shown, the pressure-side fitting portion 88 is located at a position M1 outside the pressure-side cam portion 90 in the radial direction M. The pressure-side fitting portion 88 is located on the second direction D2 side 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 54 (see Figure 4 ).

[0083] As Figure 9 and Figure 10 shown, the second pressure member 81 has a pressure-side cam hole 83H that penetrates a part of the through-body 82 and the flange 98. The pressure-side cam hole 83H is located at a position M1 outside the cylindrical portion 80 in the radial direction M. The pressure-side cam hole 83H extends from the side of the cylindrical portion 80 to a position M1 outside the pressure-side fitting portion 88 in the radial direction M. The pressure-side cam hole 83H is formed between the pressure-side auxiliary cam surface 90A and the pressure-side sliding cam surface 90S of the adjacent pressure-side cam portion 90. When viewed axially from the second pressure member 81, a part of the pressure-side auxiliary cam surface 90A overlaps with the pressure-side cam hole 83H. A boss portion 62 of the first clutch center portion 41 is inserted into the pressure-side cam hole 83H (see Figure 2 ). The boss portion 62 penetrates the pressure-side cam hole 83H.

[0084] As Figure 9 shown, the second pressure member 81 includes a plurality of pressure-side fitting teeth 87 disposed on the flange 98. The pressure-side fitting teeth 87 hold the output-side rotating piece 22. The pressure-side fitting teeth 87 project from the flange 98 toward the first direction D1. The pressure-side fitting teeth 87 are located at a position M1 outside the cylindrical portion 80 in the radial direction M. The pressure-side fitting teeth 87 are located at a position M1 outside the pressure-side cam portion 90 in the radial direction M. The pressure-side fitting teeth 87 are located at a position M1 outside the pressure-side fitting portion 88 in the radial direction M. 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 addition, in the present embodiment, since a part of the pressure-side fitting teeth 87 is removed, the interval of this part is wider, but the other adjacent pressure-side fitting teeth 87 are arranged at equal intervals.

[0085] AsFigure 1 As shown, a spring storage portion 84 is formed in the pressure-side cam portion 90 (also refer to Figure 10 ). The spring storage portion 84 is located at a position on the outer side M1 in the radial direction M with respect to the partition wall 80A of the cylindrical portion 80. The spring storage portion 84 is formed so as to be recessed from the second direction D2 toward the first direction D1 (also refer to Figure 12 A). The spring storage portion 84 is formed in a circular shape. The spring storage portion 84 stores the clutch spring 25.

[0086] As Figure 1 shown, the clutch spring 25 is stored in the spring storage portion 84. One end of the clutch spring 25 in the first direction D1 abuts against the second pressure member 81. The other end of the clutch spring 25 in the second direction D2 abuts against the limit plate 100. The clutch spring 25 applies a force to the pressure member 70 (more specifically, the second pressure member 81) toward the clutch center portion 40 (i.e., toward the first direction D1). The clutch spring 25 is, for example, a helical spring formed by winding spring steel into a spiral shape. The clutch spring 25 extends along the direction D.

[0087] As Figure 1 shown, a centrifugal clutch mechanism 120 is provided inside the clutch housing 30. The centrifugal clutch mechanism 120 is provided on the first direction D1 side with respect to the clutch center portion 40. The centrifugal clutch mechanism 120 is held by the clutch housing 30. The centrifugal clutch mechanism 120 is provided so as to be rotatable integrally with the clutch housing 30. As Figure 12 and Figure 13 shown, the centrifugal clutch mechanism 120 includes a plurality of weight members 122, a holding member 124, a crimping member 126, a guiding member 128 (also refer to Figure 14 ), a first spherical member 131, a second spherical member 132, a spring 135 (also refer to Figure 1 ), and a biasing member 140 (refer to Figure 15 ). The centrifugal clutch mechanism 120 causes the input-side rotating piece 20 and the output-side rotating piece 22 to be crimped together when the weight members 122 are located at positions on the outer side M1 in the radial direction M, thereby enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15. The centrifugal clutch mechanism 120 releases the crimping force between the input-side rotating piece 20 and the output-side rotating piece 22 when the weight members 122 are located at positions on the inner side M2 in the radial direction M, thereby enabling the transmission of the rotational driving force of the input shaft to the output shaft 15 to be cut off. The centrifugal clutch mechanism 120 is configured to be able to press the auxiliary clutch plate 150 (refer to Figure 1 ).

[0088] As Figure 16As shown, a plurality of counterweight members 122 are arranged circumferentially along S. The counterweight members 122 are configured to be movable from a position on the inner side M2 in the radial direction M to a position on the outer side M1 by centrifugal force accompanying the rotation of the clutch housing 30. As Figure 13 shown, the counterweight members 122 are housed in a housing portion 124A of a holding member 124 described later. As Figure 15 shown, the counterweight member 122 includes a main body portion 122A formed in a substantially rectangular parallelepiped shape and flat portions 122B located at both ends in the circumferential direction S of the main body portion 122A. The counterweight member 122 has a through-hole 122H (refer to Figure 13 ) that penetrates the main body portion 122A in the axial direction (i.e., direction D) of the output shaft 15. Two through-holes 122H are formed in one counterweight member 122. The flat portion 122B is located on the side closer to the first direction D1 than the main body portion 122A. The flat portion 122B has a plane orthogonal to the axial direction of the output shaft 15. The flat portion 122B is a portion that is urged by an urging portion 142 of an urging member 140 described later. The counterweight member 122 is held at a position on the inner side M2 in the radial direction M by a spring 135 in a state where no centrifugal force is applied. The counterweight member 122 moves toward the outer side M1 in the radial direction M by overcoming the acting force of the spring 135 when centrifugal force is applied, and moves to the position on the outer side M1 in the radial direction M.

[0089] As Figure 13 shown, a first spherical member 131 is attached to the counterweight member 122. The first spherical member 131 is, for example, a steel ball. A part of the first spherical member 131 protrudes from an opening on one side (here, the second direction D2) of the through-hole 122H formed in the counterweight member 122 and contacts a rolling surface of a crimping member 126. A second spherical member 132 is attached to the counterweight member 122. The second spherical member 132 is, for example, a steel ball. A part of the second spherical member 132 protrudes from an opening on the other side (here, the first direction D1) of the through-hole 122H formed in the counterweight member 122 and contacts a rolling surface of the holding member 124. The first spherical member 131 and the second spherical member 132 are configured to be able to roll.

[0090] As Figure 1 shown, the spring 135 is disposed on the outer side M1 in the radial direction M of the counterweight member 122. The spring 135 is provided in the holding member 124. The spring 135 is housed in the housing portion 124A of the holding member 124 (refer to Figure 13 ). A part of the spring 135 is located inside the counterweight member 122. The spring 135 urges the counterweight member 122 toward the inner side M2 in the radial direction M. The spring 135 is, for example, a helical spring. As Figure 16As shown, the spring 135 includes a first spring 135A and a second spring 135B arranged circumferentially along S. The first spring 135A and the second spring 135B have the same shape. The first spring 135A and the second spring 135B are arranged between a pair of first spherical members 131 in the circumferential direction S. In addition, the pair of first spherical members 131 may also be arranged between the first spring 135A and the second spring 135B in the circumferential direction S. The spring 135 is an example of an elastic member. The elastic member may also be rubber. The first spring 135A is an example of a first elastic member, and the second spring 135B is an example of a second elastic member.

[0091] As Figure 13 shown, the holding member 124 holds the weight member 122 so that it can move between a position on the inner side M2 of the radial direction M and a position on the outer side M1 of the radial direction M. The holding member 124 is formed in an annular shape. The holding member 124 is formed by an aluminum die casting. The holding member 124 has a plurality of storage portions 124A, pressing portions 124C, and engaging protrusions 125 formed throughout the circumferential direction S (see Figure 14 ). The storage portion 124A stores the weight member 122. The storage portion 124A is formed in a concave shape that conforms to the shape and movement range of the weight member 122. One end of the spring 135 is configured to be able to abut against the outer peripheral wall surface 124AA of the storage portion 124A. An abutment surface 124B against which the weight member 130 abuts when the weight member 122 moves in the radial direction M is provided in the storage portion 124A. The abutment surface 124B faces the weight member 122 in the axial direction (i.e., direction D) of the output shaft 15. Here, the second spherical member 132 of the weight member 130 abuts against the abutment surface 124B. As Figure 16 shown, the engaging protrusion 125 is located at a position on the outer side M1 of the radial direction M relative to the spring 135. The engaging protrusion 125 protrudes toward the outer side M1 of the radial direction M. The engaging protrusion 125 engages with the clutch housing 30. A plurality of engaging protrusions 125 are formed throughout the circumferential direction S. The holding member 124 includes a pressing surface 124AP, which is a part of the outer peripheral wall surface 124AA of the storage portion 124A and is a pressing surface 124AP that is pressed by the weight member 122 when the weight member 122 is located at the outer side M1 of the radial direction M. A stress in the outer side M1 of the radial direction M is applied from the weight member 122 to the pressing surface 124AP. The engaging protrusion 125 and the pressing surface 124AP are arranged offset from each other in the circumferential direction S. Here, the engaging protrusion 125 is arranged between a pair of pressing surfaces 124AP in the circumferential direction S. The holding member 124 is an example of an abutting member.

[0092] As Figure 13As shown, the crimping member 126 is configured to move from the position on the inner side M2 of the radial direction M to the position on the outer side M1 by the weight member 122 and move in the second direction D2, so that the input-side rotating piece 20 and the output-side rotating piece 22 can be crimped. The crimping member 126 is formed in an annular shape. The crimping member 126 has a plurality of ramp portions 126A formed over the circumferential direction S, grooves 126B respectively formed at the positions where the ramp portions 126A are formed, and a pressing surface 126C. The ramp portions 126A are respectively formed at positions corresponding to the weight member 122. The ramp portions 126A are inclined so as to face the first direction D1 from the inner side M2 of the radial direction M toward the outer side M1 of the radial direction M. In a state where the clutch housing 30 is stopped, the weight member 122 is held at the inner side M2 of the radial direction M by the acting force of the spring 135. In a state where the clutch housing 30 rotates and centrifugal force is applied to the weight member 122, the weight member 122 moves along the ramp portion 126A, whereby the crimping member 126 moves in the direction of separating from the holding member 124 (i.e., the second direction D2). Thereby, the pressing surface 126C of the crimping member 126 presses the flange 68 of the second clutch center portion 51 (refer to Figure 1 ). As Figure 12 shown, the crimping member 126 has a plurality of protrusions 127 formed over the circumferential direction S. The protrusions 127 overlap with the engaging protrusions 125 of the holding member 124. The protrusions 127 are engaged with the clutch housing 30. The holding member 124 and the crimping member 126 are held on the inner circumferential surface of the side wall 33 of the clutch housing 30 via the engaging protrusions 125 and the protrusions 127 in the same manner as the input-side rotating piece 20. The holding member 124 and the crimping member 126 are held on the clutch housing 30 by spline fitting. The holding member 124 and the crimping member 126 are provided so as to be displaceable along the axial direction (i.e., the direction D) of the clutch housing 30. The holding member 124 and the crimping member 126 are provided so as to be rotatable integrally with the clutch housing 30.

[0093] As Figure 12 and Figure 13 shown, the guide member 128 is located between the holding member 124 and the crimping member 126 in the axial direction (i.e., the direction D) of the output shaft 15. The guide member 128 is mounted on the holding member 124. The guide member 128 is fixed to the holding member 124. More specifically, the guide member 128 is fixed to the surface of the holding member 124 where the accommodating portion 124A is formed. The guide member 128 holds the weight member 122 so as to be movable in the radial direction M. The guide member 128 guides the movement of the weight member 122 in the radial direction M. As Figure 14As shown, the guide member 128 is formed in an annular shape. The guide member 128 has a guide portion 129A for guiding the movement of the weight member 122 and a fixing portion 129B for fixing the biasing member 140. The guide portion 129A extends in the radial direction M. The guide portion 129A is fitted into a groove 122AH (see Figure 15 ) formed substantially at the center of the main body portion 122A of the weight member 122. The fixing portion 129B is formed in a substantially triangular shape. The fixing portion 129B fixes a fixing portion 141 (see Figure 17 ) of the biasing member 140 described later. An insertion hole 129C for inserting a rivet 136 described later is formed in the fixing portion 129B (see Figure 14 , Figure 29A ).

[0094] The biasing member 140 is located between the holding member 124 and the crimping member 126 in the axial direction (i.e., direction D) of the output shaft 15. As Figure 14 shown, the biasing member 140 is located between the holding member 124 and the guide member 128 in the axial direction (i.e., direction D) of the output shaft 15. The biasing member 140 is provided between the guide member 128 and the weight member 122. The biasing member 140 is provided on the guide member 128. The biasing member 140 is fixed to the holding member 124. The biasing member 140 is provided on the guide member 128 between adjacent weight members 122. The biasing member 140 is fixed to the holding member 124 between adjacent weight members 122. The biasing member 140 and the guide member 128 are fixed to the holding member 124 together by a rivet 136. In addition, the biasing member 140 may be fixed to the holding member 124 by a fastening member such as a bolt instead of the rivet 136. In the present embodiment, the biasing member 140 and the guide member 128 are formed separately, but may be formed integrally with the guide member 128. The biasing member 140 biases the weight member 122 held by the holding member 124 in the axial direction of the output shaft 15. The biasing member 140 biases the weight member 122 toward the axial direction of the output shaft 15 and against the contact surface 124B (see Figure 1 ). The biasing member 140 presses the end portion of the weight member 122 in the circumferential direction S. The biasing member 140 always biases the weight member 122 in the axial direction of the output shaft 15. That is, throughout the entire range from when the weight member 122 is located on the inner side M2 in the radial direction M to when it is located on the outer side M1 in the radial direction M, the biasing member 140 biases the weight member 122 in the axial direction of the output shaft 15. In the present embodiment, the biasing member 140 biases the weight member 122 in the first direction D1. The biasing member 140 biases the weight member 122 toward the axial direction of the output shaft 15 and against the holding member 124. The second spherical member 132 of the centrifugal clutch mechanism 120 is pressed against the holding member 124 (here, the contact surface 124B) by the biasing member 140. The biasing member 140 allows the weight member 122 to move in the radial direction M.

[0095] As shown Figure 17 in FIG. [ID], the biasing member 140 is composed of a plate member. The biasing member 140 is formed of, for example, SPCC (cold-rolled steel sheet). The biasing member 140 is a so-called leaf spring. The biasing member 140 includes a fixing portion 141 formed in a substantially triangular shape and biasing portions 142 respectively provided on the outer side M1 in the radial direction M and at both ends in the circumferential direction S of the fixing portion 141. The fixing portion 141 is a portion that contacts the holding member 124 and the guide member 128. The biasing portion 142 is located on the side of the first direction D1 with respect to the fixing portion 141. The biasing portion 142 is a portion that contacts the weight member 122. More specifically, the biasing portion 142 is a portion that contacts the flat portion 122B of the weight member 122 (refer to Figure 15 ). The biasing portion 142 biases the weight member 122 in the axial direction of the output shaft 15 (i.e., the direction D). The biasing portion 142 biases the weight member 122 in the first direction D1. The biasing portion 142 is configured to be elastically deformable. As shown Figure 16 in FIG. [ID], the biasing portion 142 includes a first biasing portion 142A provided at the end on the first circumferential direction S1 side of the fixing portion 141 and a second biasing portion 142B provided at the end on the second circumferential direction S2 side of the fixing portion 141. The first biasing portion 142A biases the flat portion 122B of the weight member 122 located on the first circumferential direction S1 side with respect to the biasing member 140. The second biasing portion 142B biases the flat portion 122B of the weight member 122 located on the second circumferential direction S2 side with respect to the biasing member 140. In this way, one biasing member 140 biases a plurality of weight members 122 (here, two weight members 122) in the axial direction of the output shaft 15.

[0096] In such a centrifugal clutch mechanism 120, when no centrifugal force is applied to the weight member 122, the weight member 122 is held at the position on the inner side M2 in the radial direction M, and the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22 is released. On the other hand, when centrifugal force is applied to the weight member 122, the weight member 122 moves from the position on the inner side M2 in the radial direction M to the position on the outer side M1. At this time, since the weight member 122 is biased by the biasing member 140 in the first direction D1, the weight member 122 does not vibrate in the axial direction of the output shaft 15 (i.e., the direction D), but smoothly moves from the position on the inner side M2 in the radial direction M to the outer side M1 in the radial direction M. As a result, the pressing surface 126C formed on the pressing member 126 presses the input-side rotating plate 20 and the output-side rotating plate 22 via the flange 68 of the second clutch center portion 51 to be in a pressed state, and the rotational driving force of the input shaft can be transmitted to the output shaft 15. At this time, the holding member 124 moves in the first direction D1, and the pressing portion 124C formed on the holding member 124 presses the auxiliary clutch plate 150.

[0097] As Figure 1 shown, the auxiliary clutch disc 150 is disposed within the clutch housing 30. The auxiliary clutch disc 150 is fixed to the output shaft 15. An insertion hole 152H into which the output shaft 15 is inserted and spline-fitted is formed in the auxiliary clutch disc 150. The auxiliary clutch disc 150 is disposed on the side of the first direction D1 rather than a part of the centrifugal clutch mechanism 120. The auxiliary clutch disc 150 is adjacent to the first clutch center portion 41.

[0098] The auxiliary clutch disc 150 is configured such that when the input-side rotating disc 20 and the output-side rotating disc 22 are pressed against each other (i.e., when the weight member 122 of the centrifugal clutch mechanism 120 is located at the outer side M1 in the radial direction M), the auxiliary clutch disc 150 is pressed by the centrifugal clutch mechanism 120 (here, the pressing portion 124C of the holding member 124) and becomes a state in which the rotational driving force of the input shaft can be transmitted to the output shaft 15. The auxiliary clutch disc 150 is configured such that when the pressing force between the input-side rotating disc 20 and the output-side rotating disc 22 is released (i.e., when the weight member 122 is located at the inner side M2 in the radial direction M), the pressing by the centrifugal clutch mechanism 120 (here, the pressing portion 124C of the holding member 124) is released and the transmission of the rotational driving force of the input shaft to the output shaft 15 is cut off.

[0099] As Figure 1 shown, the stopper plate 100 is disposed so as to be able to contact the pressure member 70. The stopper plate 100 is a member that suppresses the pressure member 70 from moving away from the clutch center portion 40 in the second direction D2 by more than a specified distance. The stopper plate 100 is fixed to the boss portion 62 of the first clutch center portion 41 by bolts 28. The pressure member 70 is fixed to the clutch center portion 40 by fastening the bolts 28 to the boss portion 62 via the stopper plate 100 in a state where the clutch spring 25 is disposed in the spring housing portion 84. The stopper plate 100 is formed in an annular shape in a plan view.

[0100] As described above, in the clutch device 10 according to the present embodiment, the biasing member 140 of the centrifugal clutch mechanism 120 is located between the holding member 124 and the pressing member 126 in the axial direction of the output shaft 15, biases the weight member 122 held by the holding member 124 in the axial direction of the output shaft 15, and allows the weight member 122 to move in the radial direction M. According to this configuration, the weight member 122 is biased in the axial direction of the output shaft 15 by the biasing member 140, so that even if there is vibration of an engine or the like, vibration in the axial direction of the output shaft 15 can be suppressed. Thus, the weight member 122 can move smoothly in the radial direction M, and therefore the axial thrust of the output shaft 15 generated in the weight member 122 due to the centrifugal force accompanying the rotation of the clutch housing 30 can be effectively transmitted to the pressing member 126.

[0101] In the clutch device 10 of the present embodiment, the biasing member 140 is constituted by a plate member. According to this configuration, the biasing member 140 with a simple structure can bias the weight member 122 in the axial direction of the output shaft 15.

[0102] In the clutch device 10 of the present embodiment, a guide member 128 is provided between the holding member 124 and the crimping member 126 in the axial direction of the output shaft 15 and guides the movement of the weight member 122 in the radial direction M. The biasing member 140 is provided on the guide member 128. According to this configuration, the biasing member 140 can more reliably bias a specified portion of the weight member 122 in the axial direction of the output shaft 15.

[0103] In the clutch device 10 of the present embodiment, the biasing member 140 is fixed to the holding member 124. According to this configuration, since the biasing member 140 is fixed to the holding member 124, the biasing member 140 can more reliably bias a specified portion of the weight member 122 in the axial direction of the output shaft 15.

[0104] In the clutch device 10 of the present embodiment, the biasing member 140 includes a biasing portion 142 that biases the weight member 122 in the axial direction of the output shaft 15, and the biasing portion 142 is formed to be elastically deformable. According to this configuration, excessive biasing of the weight member 122 by the biasing portion 142 is suppressed.

[0105] In the clutch device 10 of the present embodiment, in one biasing member 140, biasing portions 142 are provided at the end on one side (first circumferential direction S1 side) in the circumferential direction S of the biasing member 140 and at the end on the other side (second circumferential direction S2 side) of the biasing member 140, respectively. According to this configuration, the weight member 122 can be biased in the axial direction of the output shaft 15 by each biasing portion 142.

[0106] In the clutch device 10 of the present embodiment, the weight member 122 includes a flat surface portion 122B that is biased by the biasing portion 142. According to this configuration, the acting force from the biasing portion 142 can be effectively transmitted through the weight member 122.

[0107] In the clutch device 10 of the present embodiment, one biasing member 140 biases a plurality of weight members 122 in the axial direction of the output shaft 15. According to this configuration, the centrifugal clutch mechanism 120 can be simplified.

[0108] In the clutch device 10 of the present embodiment, a plurality of weight members 122 are arranged in the circumferential direction S, and the biasing member 140 is provided on the guide member 128 between adjacent weight members 122. According to this configuration, the biasing member 140 can be arranged compactly.

[0109] In the clutch device 10 of the present embodiment, the biasing member 140 is fixed to the holding member 124 between adjacent weight members 122. According to this configuration, the biasing member 140 can be arranged compactly.

[0110] In the clutch device 10 of the present embodiment, the holding member 124 includes: an engaging projection 125 located at a position radially outside M1 of the spring 135 in the radial direction M and engaging with the clutch housing 30; and a pressing surface 124AP that is pressed by the weight member 122 when the weight member 122 is located at a position radially outside M1 in the radial direction M. The engaging projection 125 and the pressing surface 124AP are arranged offset from each other in the circumferential direction S. According to this configuration, an excessive load is not applied to the engaging projection 125, and thus breakage of the engaging projection 125 can be suppressed.

[0111] In the clutch device 10 of the present embodiment, the weight member 122 may include a plurality of through holes 122H penetrating in the axial direction of the output shaft 15, the spring 135 may include a first spring 135A and a second spring 135B arranged in the circumferential direction S, and the centrifugal clutch mechanism 120 may include a first spherical member 131 that partially protrudes from the opening of the through hole 122H and is configured to be able to roll. The first spherical member 131 is arranged between the first spring 135A and the second spring 135B in the circumferential direction S. According to this configuration, the weight member 122 can be biased well in the radially inner direction M2 in the radial direction M by the first spring 135A and the second spring 135B.

[0112] In the clutch device 10 of the present embodiment, the biasing member 140 biases the weight member 122 in the axial direction of the output shaft 15 and against the holding member 124. According to this configuration, the weight member 122 is always in contact with the holding member 124 by the biasing member 140, and thus even if there is vibration from an engine or the like, the weight member 122 can more reliably suppress vibration in the axial direction of the output shaft 15.

[0113] <Second Embodiment>

[0114] Figure 18 is a plan view showing a part of the centrifugal clutch mechanism 120 according to the second embodiment, and is a plan view showing a state in which the weight member 530 is located on the radially inner side M2. As Figure 18As shown, a plurality of counterweight members 530 are arranged along the circumferential direction S. The counterweight members 530 are configured to be movable from a position on the inner side M2 in the radial direction M to a position on the outer side M1 by the centrifugal force accompanying the rotation of the clutch housing 30. The counterweight members 530 are configured to press the crimping member 126 toward the second direction D2. The counterweight members 530 are held at the position on the inner side M2 in the radial direction M by the spring 135 in a state where no centrifugal force is applied. The counterweight members 530 move toward the outer side M1 in the radial direction M against the action of the spring 135 by being applied with centrifugal force and move to the position on the outer side M1 in the radial direction M. The counterweight members 530 are housed in the housing portion 124A of the holding member 124. As Figure 21 shown, the counterweight member 530 includes: a biasing member holding portion 531; a first plane 533 provided on the circumferential direction S side closer to the circumferential direction S than the biasing member holding portion 531; a second plane 535 provided on the other side of the circumferential direction S closer to the circumferential direction S than the biasing member holding portion 531; and a counterweight side inclined surface 530F (see Figure 19 and Figure 20 ), which is located on the side opposite to the first plane 533 and the second plane 535 in the axial direction (i.e., the direction D) of the output shaft 15.

[0115] The biasing member holding portion 531 holds the spring 135. As Figure 21 shown, the biasing member holding portion 531 is a groove recessed from the second direction D2 and the outer side M1 in the radial direction M toward the inner side M2. The biasing member holding portion 531 includes a holding wall 532 that holds the end portion on the inner side M2 in the radial direction M of the spring 135. In the present embodiment, the biasing member holding portion 531 includes a first biasing member holding portion 531A that holds the first spring 135A (see Figure 18 ), and a second biasing member holding portion 531B that holds the second spring 135B (see Figure 18 ).

[0116] As Figure 21 and Figure 22 shown, the first plane 533 is provided on the first circumferential direction S1 side closer to the circumferential direction S than the biasing member holding portion 531. More specifically, the first plane 533 is provided at a position on the first circumferential direction S1 side closer to the first biasing member holding portion 531A. The first plane 533 and the first biasing member holding portion 531A are arranged in the circumferential direction S. The second plane 535 is provided on the second circumferential direction S2 side closer to the circumferential direction S than the biasing member holding portion 531. More specifically, the second plane 535 is provided at a position on the second circumferential direction S2 side closer to the second biasing member holding portion 531B. The second plane 535 and the second biasing member holding portion 531B are arranged in the circumferential direction S. As Figure 23As shown, the first plane 533 and the second plane 535 are orthogonal to the axial direction (i.e., direction D) of the output shaft 15. The first plane 533 and the second plane 535 are formed flush. The first plane 533 and the second plane 535 are arranged to be able to abut against the abutting surface 124B of the holding member 124. The first plane 533 and the second plane 535 are arranged to be able to slide relative to the holding member 124. More specifically, the first plane 533 and the second plane 535 are arranged to be able to slide relative to the abutting surface 124B.

[0117] As Figure 21 shown, the weight member 530 includes a third plane 537. The third plane 537 is located between the first plane 533 and the second plane 535 in the circumferential direction S. The third plane 537 is located between the first biasing member holding portion 531A and the second biasing member holding portion 531B in the circumferential direction S. The third plane 537 may also be arranged to be able to slide relative to the holding member 124. The third plane 537 may also be formed coplanar with the first plane 533 and the second plane 535.

[0118] The weight side inclined surface 530F is arranged to be able to contact the crimping member 126. As Figure 23 shown, the weight side inclined surface 530F is inclined with respect to the axial direction (i.e., direction D) of the output shaft 15. The weight side inclined surface 530F is inclined so as to face the first direction D1 from the inner side M2 of the radial direction M toward the outer side M1 of the radial direction M. The weight side inclined surface 530F is configured to be able to slide relative to the ramp portion 126A of the crimping member 126 (see Figure 13 ).

[0119] As Figure 18As shown, the force - applying member 140 applies a force to the counterweight member 530 axially (i.e., in the direction D) toward the output shaft 15 and against the contact surface 124B. The force - applying portion 142 of the force - applying member 140 abuts against the counterweight member 530. When the counterweight member 530 is at least in the inner side M2 in the radial direction M, when viewed axially from the output shaft 15, the fixing portion 141 of the force - applying member 140A is on the circumferential - direction S side (the first circumferential - direction S1 side) with respect to the first plane 533, and the force - applying portion 142 of the force - applying member 140A overlaps at least a part of the first plane 533. When the counterweight member 530 is at least in the inner side M2 in the radial direction M, when viewed axially from the output shaft 15, the fixing portion 141 of the force - applying member 140B is on the circumferential - direction S side (the second circumferential - direction S2 side) with respect to the second plane 535, and the force - applying portion 142 of the force - applying member 140B overlaps at least a part of the second plane 535. Further, it is also possible that in at least a part of the process of the counterweight member 530 moving from the inner side M2 to the outer side M1 in the radial direction M and in the state where the counterweight member 530 is on the outer side M1 in the radial direction M, when viewed axially from the output shaft 15, the force - applying portion 142 of the force - applying member 140A overlaps at least a part of the first plane 533, and the force - applying portion 142 of the force - applying member 140B overlaps at least a part of the second plane 535.

[0120] In such a centrifugal clutch mechanism 120, as Figure 18 shown, when no centrifugal force is applied to the counterweight member 530, the counterweight member 530 is held at the position on the inner side M2 in the radial direction M, and the pressing force between the input - side rotating plate 20 and the output - side rotating plate 22 is released. On the other hand, when centrifugal force is applied to the counterweight member 530, the counterweight member 530 moves from the position on the inner side M2 in the radial direction M to the position on the outer side M1. When the counterweight member 530 moves in the radial direction M, the counterweight - side inclined surface 530F of the counterweight member 530 slides on the ramp portion 126A of the pressing member 126, and the first plane 533 and the second plane 535 of the counterweight member 530 slide on the contact surface 124B of the holding member 124. At this time, the pressing surface 126C of the pressing member 126 (refer to Figure 13 ) presses the input - side rotating plate 20 and the output - side rotating plate 22 via the flange 68 of the second clutch center portion 51 to be in a pressed state, and the rotational driving force of the input shaft can be transmitted to the output shaft 15. At the same time, the holding member 124 moves in the first direction D1, and the pressing portion 124C of the holding member 124 (refer to Figure 13 ) presses the auxiliary clutch plate 150.

[0121] <Third Embodiment>

[0122] Figure 24It is a top view showing a part of the centrifugal clutch mechanism 120 according to the third embodiment, and is a top view showing the state where the weight member 630 is located inside M2 in the radial direction M. As Figure 24 shown, a plurality of weight members 630 are arranged in the circumferential direction S. As Figure 25 shown, the weight member 630 includes a guide portion 638 that houses a part of the cylindrical member 670. The guide portion 638 is formed on the surface facing the holding member 124 (here, the third plane 537). The guide portion 638 holds the cylindrical member 670 in such a manner that a part of the cylindrical member 670 protrudes from the surface of the weight member 630 facing the holding member 124 (here, the third plane 537) toward the holding member 124 (i.e., in the first direction D1) (refer to Figure 27 ). The guide portion 638 guides the movement of the cylindrical member 670 in the radial direction M. The guide portion 638 is located between the first biasing member holding portion 531A and the second biasing member holding portion 531B in the circumferential direction S. As Figure 26 shown, the guide portion 638 is formed in a rectangular shape in a top view. The guide portion 638 includes a first restricting portion 638S that restricts the movement of the cylindrical member 670 in the circumferential direction S and a second restricting portion 638M that restricts the movement of the cylindrical member 670 in the radial direction M by more than a specified distance. The first restricting portion 638S is provided on the first circumferential side S1 and the second circumferential side S2 in the circumferential direction S, respectively. The second restricting portion 638M is provided on the outer side M1 and the inner side M2 in the radial direction M, respectively. The guide portion 638 has a receiving groove 638P that is recessed in the axial direction of the output shaft 15 (i.e., the direction D) from the holding member 124 toward the weight member 630 (i.e., the second direction D2) and houses a part of the cylindrical member 670. The receiving groove 638P is demarcated by the first restricting portion 638S and the second restricting portion 638M.

[0123] As Figure 24 shown, the cylindrical member 670 is provided between the weight member 630 and the holding member 124 in the axial direction of the output shaft 15 (i.e., the direction D). The cylindrical member 670 is arranged to extend in a direction intersecting the radial direction M (here, a direction orthogonal to the radial direction M and the direction D). The cylindrical member 670 rolls relative to the weight member 630 and the holding member 124. A part of the cylindrical member 670 is received in the receiving portion 124A of the holding member 124, and another part of the cylindrical member 670 is received in the guide portion 638 of the weight member 630. The cylindrical member 670 rolls relative to the abutting surface 124B of the receiving portion 124A and the guide portion 638. As Figure 26 shown, the cylindrical member 670 is located between the first spring 135A and the second spring 135B in the circumferential direction S.

[0124] As Figure 24As shown, the force - applying member 140 applies a force to the weight member 630 axially (i.e., in direction D) toward the output shaft 15 and against the abutting surface 124B. The force - applying portion 142 of the force - applying member 140 abuts against the weight member 630. In a state where the weight member 630 is at least inside the inner side M2 of the radial direction M, when viewed axially from the output shaft 15, the force - applying portion 142 of the force - applying member 140A is located laterally (on the first circumferential S1 side) in the circumferential direction S with respect to the guiding portion 638, and the force - applying portion 142 of the force - applying member 140B is located laterally (on the second circumferential S2 side) in the circumferential direction S with respect to the guiding portion 638. Further, it is also possible that in at least a part of the process of the weight member 630 moving from the inner side M2 to the outer side M1 of the radial direction M and in a state where the weight member 630 is on the outer side M1 of the radial direction M, when viewed axially from the output shaft 15, the force - applying portion 142 of the force - applying member 140A is located laterally (on the first circumferential S1 side) in the circumferential direction S with respect to the guiding portion 638, and the force - applying portion 142 of the force - applying member 140B is located laterally (on the second circumferential S2 side) in the circumferential direction S with respect to the guiding portion 638.

[0125] In such a centrifugal clutch mechanism 120, as Figure 24 shown, when no centrifugal force is applied to the weight member 630, the weight member 630 is held at the position on the inner side M2 of the radial direction M, and the pressing force between the input - side rotating piece 20 and the output - side rotating piece 22 is released. On the other hand, when centrifugal force is applied to the weight member 630, the weight member 630 moves from the position on the inner side M2 of the radial direction M to the position on the outer side M1. When the weight member 630 moves along the radial direction M, it is guided by the guiding portion 638 and the accommodating portion 124A, and the cylindrical member 670 rolls relative to the weight member 630 and the holding member 124. At this time, the first plane 533 and the second plane 535 of the weight member 630 do not slide on the abutting surface 124B of the holding member 124.

[0126] <Fourth Embodiment>

[0127] As Figure 28A and Figure 28B shown, the force - applying member 240 according to the fourth embodiment is provided on the weight member 122. The force - applying member 240 is provided between the guiding member 128 and the weight member 122. The force - applying member 240 is provided on the guiding portion 129A of the guiding member 128 (refer to Figure 14Between the groove 122AH of the counterweight member 122. The biasing member 240 is disposed on the second direction D2 side of the counterweight member 122. The biasing member 240 is disposed at the central portion of the circumferential direction S of the counterweight member 122. The biasing member 240 is mounted in the groove 122AH of the main body portion 122A of the counterweight member 122. The biasing member 240 is disposed between the pair of through holes 122H in the circumferential direction S. At least a part of the biasing member 240 is located at a position closer to the inner side M2 in the radial direction M than the first spherical member 131 and the second spherical member 132 (i.e., the through hole 122H). The biasing member 240 is made of an elastic body. The biasing member 240 is, for example, rubber or a leaf spring. The biasing member 240 extends in the radial direction M. The biasing member 240 has a rectangular parallelepiped shape. The length of the biasing member 240 in the radial direction M is longer than the length in the circumferential direction S. The biasing member 240 contacts the guide portion 129A of the guide member 128 (refer to Figure 14 ). By the contact between the biasing member 240 and the guide member 128, the biasing member 240 biases the counterweight member 122 in the first direction D1. The biasing member 240 biases the counterweight member 122 toward the axial direction of the output shaft 15 and the holding member 124. Further, in a state before the guide member 128 is mounted on the holding member 124, the surface 240D2 on the second direction D2 side of the biasing member 240 protrudes more toward the D2 side than the surface 122D2 on the second direction D2 side of the counterweight member 122. Moreover, in a state where the guide member 128 is mounted on the holding member 124, the biasing member 240 is compressed in the first direction D1. At this time, the surface 240D2 on the second direction D2 side of the biasing member 240 may be coplanar with the surface 122D2 on the second direction D2 side of the counterweight member 122, or may protrude more toward the second direction D2 side than the surface 122D2 on the second direction D2 side of the counterweight member 122 (in any case, the biasing member 240 can bias the counterweight member 122 toward the axial direction of the output shaft 15 and the holding member 124).

[0128] In the clutch device 10 of the present embodiment, the biasing member 240 is made of an elastic body. According to this configuration, excessive biasing of the counterweight member 122 by the biasing member 240 is suppressed.

[0129] In the clutch device 10 of the present embodiment, the biasing member 240 is disposed on the counterweight member 122. According to this configuration, a predetermined portion of the counterweight member 122 can be more reliably biased in the axial direction of the output shaft 15 by the biasing member 240.

[0130] In the clutch device 10 of the present embodiment, the biasing member 240 is disposed at the central portion of the circumferential direction S of the counterweight member 122. According to this configuration, the counterweight member 122 can be biased in a well-balanced manner in the axial direction of the output shaft 15 by the biasing member 240.

[0131] In the clutch device 10 of the present embodiment, the biasing member 240 extends in the radial direction M. According to this configuration, the biasing member 240 can bias the weight member 122 more evenly in the axial direction of the output shaft 15.

[0132] In the clutch device 10 of the present embodiment, at least a part of the biasing member 240 is located at a position radially inward M2 of the first spherical member 131 and the second spherical member 132. According to this configuration, the biasing member 240 can bias the weight member 122 more evenly in the axial direction of the output shaft 15.

[0133] In the present embodiment, the biasing member 240 is provided on the surface of the weight member 122 on the second direction D2 side, but is not limited thereto. For example, the biasing member 240 may be provided on the surface of the weight member 122 on the first direction D1 side to bias the weight member 122 in the axial direction of the output shaft 15 and the guide member 128. Thus, the weight member 122 is always in contact with the guide member 128 through the biasing member 240, so that even if there is vibration from an engine or the like, the weight member 122 can more reliably suppress the vibration in the axial direction of the output shaft 15.

[0134] <Fifth Embodiment>

[0135] As Figure 29A and Figure 29B shown, the biasing member 440 of the fourth embodiment is provided on the guide member 128. The biasing member 440 is provided on the first direction D1 side of the guide member 128. The biasing members 440 are respectively provided on the guide portions 129A of the guide member 128. The biasing member 440 is located circumferentially S between a pair of first spherical members 131. The biasing member 440 is made of an elastic body. The biasing member 440 is, for example, rubber. The biasing member 440 extends in the radial direction M. The biasing member 440 has a flat plate shape. The biasing member 440 contacts the weight member 122. The biasing member 440 is fitted into the groove 122AH of the main body portion 122A of the weight member 122 and contacts the main body portion 122A. By contacting the weight member 122, the biasing member 440 biases the weight member 122 in the first direction D1. The biasing member 440 biases the weight member 122 in the axial direction of the output shaft 15 and the holding member 124.

[0136] In the clutch device 10 of the present embodiment, the centrifugal clutch mechanism 120 includes a guide member 128 that is located axially of the output shaft 15 between the holding member 124 and the crimping member 126 and guides the radial M movement of the weight member 122, and the biasing member 440 is provided on the guide member 128. According to this configuration, the biasing member 440 can more reliably bias a specified portion of the weight member 122 in the axial direction of the output shaft 15.

[0137] In the clutch device 10 of the present embodiment, the weight member 122 has a plurality of through holes 122H penetrating in the axial direction of the output shaft 15, the centrifugal clutch mechanism 120 has a pair of first spherical members 131 partially protruding from the openings of the through holes 122H and configured to be able to roll, and the biasing member 440 is located between the pair of first spherical members 131 in the circumferential direction S and extends in the radial direction M. According to the above manner, the weight member 122 can be biased more balancedly in the axial direction of the output shaft 15 by the biasing member 440.

[0138] As described above, the preferred embodiments of the present invention have been described. However, the above-described embodiments are merely illustrative, and the present invention can be implemented in various other ways.

[0139] In each of the above embodiments, the weight member 122 has flat portions 122B located at both ends in the circumferential direction S of the main body portion 122A, but it is not limited thereto. The weight member 122 may have curved surface portions instead of the flat portions 122B.

[0140] In each of the above embodiments, the biasing portion 142 of the biasing member 140 biases the flat portion 122B of the weight member 122, but it may bias the main body portion 122A instead of the flat portion 122B.

[0141] In the above embodiment, the crimping member 126 is formed separately from the clutch center portion 40, but for example, it may be formed integrally with the second clutch center portion 51. For example, it may be formed integrally with the flange 68 of the second clutch center portion 51.

[0142] In the above embodiment, the biasing members 140, 240, 440 are provided between the guide member 128 and the weight member 122, but it is not limited thereto. For example, the biasing members 140, 240, 440 may be disposed between the holding member 124 and the weight member 122. In this case, the biasing members 140, 240, 440 bias the weight member 122 in the axial direction of the output shaft 15 and toward the crimping member 126. The first spherical member 131 of the centrifugal clutch mechanism 120 is pressed against the crimping member 126 by the biasing members 140, 240, 440. In this case, the crimping member 126 is an example of the abutting member.

[0143] [Description of Reference Numerals]

[0144] 10 Clutch device

[0145] 15 Output shaft

[0146] 20 Input side rotating plate

[0147] 22 Output side rotating plate

[0148] 30 Clutch housing

[0149] 40 Clutch center part

[0150] 70 Pressure member

[0151] 120 Centrifugal clutch mechanism

[0152] 122 Counterweight member

[0153] 122 B Plane part

[0154] 122 H Through hole

[0155] 124 Holding member

[0156] 125 Engaging projection

[0157] 126 Crimping member

[0158] 128 Guide member

[0159] 131 First spherical member

[0160] 132 Second spherical member

[0161] 135 Spring (elastic member)

[0162] 140 Biasing member

[0163] 141 Fixing part

[0164] 142 Biasing part.

Claims

1. A clutch device that transmits or cuts off the rotational driving force of an input shaft with respect to an output shaft, wherein, Comprising: A clutch center part, which is housed in a clutch housing that holds a plurality of input-side rotating pieces that are rotationally driven by the rotational drive of the input shaft, and is rotationally driven together with the output shaft; A pressure member, which is arranged to be able to approach or separate from the clutch center part, and is able to press the input-side rotating pieces and a plurality of output-side rotating pieces that are alternately arranged with the input-side rotating pieces; And A centrifugal clutch mechanism, which has a plurality of weight members. The weight members are configured to be able to move from a position on the inner side in the radial direction to a position on the outer side by the centrifugal force accompanying the rotation of the clutch housing. And when the weight members are in the position on the outer side in the radial direction, the centrifugal clutch mechanism can make the input-side rotating pieces and the output-side rotating pieces come into pressure contact to be in a state where the rotational driving force of the input shaft can be transmitted to the output shaft, and when the weight members are in the position on the inner side in the radial direction, the centrifugal clutch mechanism can release the pressure contact force between the input-side rotating pieces and the output-side rotating pieces to cut off the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism includes A holding member, which holds the weight members so that they can move between the position on the inner side in the radial direction and the position on the outer side in the radial direction; An elastic member, which applies a force to the weight members in the radial direction toward the inner side; A pressure contact member, which moves in the axial direction of the output shaft as the weight members move from the position on the inner side in the radial direction to the position on the outer side in the radial direction, so as to make the input-side rotating pieces and the output-side rotating pieces come into pressure contact; and A biasing member, which is located between the holding member and the pressure contact member in the axial direction of the output shaft, applies a force to the weight members held by the holding member in the axial direction of the output shaft, and allows the weight members to move in the radial direction.

2. The clutch device according to claim 1, wherein The biasing member is composed of a plate member.

3. The clutch device according to claim 2, wherein The centrifugal clutch mechanism includes a guiding member, which is located between the holding member and the pressure contact member in the axial direction of the output shaft, and guides the movement of the weight members in the radial direction. The biasing member is provided on the guiding member.

4. The clutch device according to claim 3, wherein The biasing member is fixed to the holding member.

5. The clutch device according to claim 2, wherein The biasing member has a biasing portion that applies a force to the weight members in the axial direction of the output shaft. The biasing portion is formed to be elastically deformable.

6. The clutch device according to claim 5, wherein In one biasing member, the biasing portions are respectively provided at one end in the circumferential direction of the biasing member and the other end of the biasing member.

7. The clutch device according to claim 5 or 6, wherein The weight members have a planar portion that is biased by the biasing portion.

8. The clutch device according to claim 3 or 5, wherein One biasing member applies a force to a plurality of weight members in the axial direction of the output shaft.

9. The clutch device according to claim 3, wherein, a plurality of the weight members are arranged circumferentially, the biasing member is disposed on the guiding member between adjacent ones of the weight members.

10. The clutch device according to claim 9, wherein, the biasing member is fixed to the holding member between adjacent ones of the weight members.

11. The clutch device according to claim 2, wherein, the centrifugal clutch mechanism includes a guiding member that is axially located between the holding member and the crimping member on the output shaft and guides the radial movement of the weight members, the biasing member is disposed between the guiding member and the weight members.

12. The clutch device according to claim 11, wherein, the guiding member is fixed to the holding member.

13. The clutch device according to claim 1 or 2, wherein, the biasing member is made of an elastic body.

14. The clutch device according to claim 13, wherein, the biasing member is disposed on the weight member.

15. The clutch device according to claim 14, wherein, the biasing member is disposed at a circumferential central portion of the weight member.

16. The clutch device according to claim 15, wherein, the biasing member extends in the radial direction.

17. The clutch device according to claim 14, wherein, the weight member has a through hole that penetrates axially through the output shaft, the centrifugal clutch mechanism includes a spherical member configured to project partly from an opening of the through hole and be able to roll, at least a part of the biasing member is located at a position radially inside the spherical member.

18. The clutch device according to claim 1, wherein, the centrifugal clutch mechanism includes a guiding member that is axially located between the holding member and the crimping member on the output shaft and guides the radial movement of the weight members, the biasing member is disposed on the guiding member.

19. The clutch device according to claim 18, wherein, the biasing member is fixed to the holding member.

20. The clutch device according to claim 18, wherein, the weight member has a plurality of through holes that penetrate axially through the output shaft, the centrifugal clutch mechanism includes a pair of spherical members configured to project partly from an opening of the through hole and be able to roll, the biasing member is circumferentially located between the pair of spherical members and extends in the radial direction.

21. The clutch device according to claim 1, wherein, the holding member includes: an engaging projection that is located radially outside the elastic member and engages with the clutch housing; and a pressing surface that is pressed by the weight member when the weight member is located at a radially outer position, the engaging projection and the pressing surface are circumferentially offset.

22. The clutch device according to claim 1, wherein, the weight member has a plurality of through holes that penetrate axially through the output shaft, The elastic member includes a first elastic member and a second elastic member arranged circumferentially. The centrifugal clutch mechanism includes a spherical member configured such that a part thereof protrudes from the opening of the through hole and is capable of rolling. The spherical member is circumferentially disposed between the first elastic member and the second elastic member.

23. The clutch device according to claim 1, wherein the biasing member biases the weight member axially toward the output shaft and toward the holding member.

24. The clutch device according to claim 1, wherein the holding member has an abutting surface that faces the weight member axially of the output shaft and against which the weight member abuts. the biasing member biases the weight member axially toward the output shaft and toward the abutting surface.

25. The clutch device according to claim 24, wherein the weight member has a flat surface capable of abutting against the abutting surface, when the weight member is at least on the inner side in the radial direction, at least a part of the biasing member is located laterally in the circumferential direction with respect to the flat surface when viewed axially of the output shaft.

26. The clutch device according to claim 25, wherein when the weight member is at least on the inner side in the radial direction, at least a part of the biasing member is located on both lateral sides in the circumferential direction with respect to the flat surface when viewed axially of the output shaft.

27. The clutch device according to claim 24, wherein the weight member has a flat surface capable of abutting against the abutting surface, the biasing member has a biasing portion that abuts against the weight member, when the weight member is at least on the inner side in the radial direction, at least a part of the biasing portion overlaps at least a part of the flat surface when viewed axially of the output shaft.

28. The clutch device according to claim 24, wherein the centrifugal clutch mechanism includes a cylindrical member that is axially disposed between the weight member and the holding member, extends in a direction intersecting the radial direction, and rolls relative to the weight member and the holding member. the weight member has a guiding portion formed on the surface facing the holding member, and holds the cylindrical member such that a part of the cylindrical member protrudes from the surface of the weight member facing the holding member toward the holding member and guides the movement of the cylindrical member in the radial direction. the biasing member has a biasing portion that abuts against the weight member, when the weight member is at least on the inner side in the radial direction, at least a part of the biasing portion is located laterally in the circumferential direction with respect to the guiding portion when viewed axially of the output shaft.

29. The clutch device according to claim 28, wherein when the weight member is at least on the inner side in the radial direction, at least a part of the biasing portion is located on both lateral sides in the circumferential direction with respect to the guiding portion when viewed axially of the output shaft.

30. The clutch device according to claim 1, wherein The elastic member is disposed on the holding member.

31. The clutch device according to claim 1, wherein the holding member has an abutting surface against which the weight member abuts, and the biasing member biases the weight member toward the abutting surface.

32. A clutch device that transmits or cuts off the rotational driving force of an input shaft with respect to an output shaft, wherein, Comprising: a clutch center portion housed in a clutch housing that holds a plurality of input-side rotating plates rotated by rotation driving of the input shaft, and rotated together with the output shaft; a pressure member arranged to be able to approach or separate from the clutch center portion and to be able to press the input-side rotating plates and a plurality of output-side rotating plates alternately arranged with the input-side rotating plates; and a centrifugal clutch mechanism having a plurality of weight members configured to be able to move from a position on the inner side in the radial direction to a position on the outer side by centrifugal force accompanying rotation of the clutch housing, and the centrifugal clutch mechanism being able to bring the input-side rotating plates into pressure contact with the output-side rotating plates when the weight members are located at positions on the outer side in the radial direction to be in a state capable of transmitting the rotational driving force of the input shaft to the output shaft, and being able to release the pressure contact force between the input-side rotating plates and the output-side rotating plates when the weight members are located at positions on the inner side in the radial direction to cut off the transmission of the rotational driving force of the input shaft to the output shaft, the centrifugal clutch mechanism comprising: an abutting member against which the weight member abuts between the position on the inner side in the radial direction and the position on the outer side in the radial direction; an elastic member that biases the weight member toward the inner side in the radial direction; a pressure contact member that moves in the axial direction of the output shaft as the weight member moves from the position on the inner side in the radial direction to the position on the outer side in the radial direction, to bring the input-side rotating plates into pressure contact with the output-side rotating plates; and a biasing member that biases the weight member toward the abutting member in the axial direction of the output shaft and allows the weight member to move in the radial direction.

Images