Clutch device

Abstract

The clutch device (10) is provided with a centrifugal clutch mechanism (120) having a weight member (130), the centrifugal clutch mechanism (120) is provided with a holding member (140) holding the weight member (130), a spring (160) applying force to the weight member (130) to the inner side (M2) of the radial direction (M), a press contact member (150) having a press contact side inclined surface (150F) arranged to be able to contact the weight member (130) and pressing the input side rotating plate (20) and the output side rotating plate (22), the weight member (130) is provided with a first plane capable of sliding relative to the holding member (140) and a weight side inclined surface (130F) capable of sliding relative to the press contact side inclined surface (150F).

Description

Technical Field

[0001] This invention relates to clutch devices. Background Technology

[0002] Motorized two-wheeled vehicles and other straddle-type vehicles are equipped with clutch devices capable of transmitting and disconnecting the rotational driving force of a drive source such as an engine to the drive wheels. For example, Patent Document 1 discloses a clutch device having an input member (hereinafter referred to as an input shaft) connected to the engine side, an output member (hereinafter referred to as an output shaft) connected to the drive wheel side, a clutch member (hereinafter referred to as a clutch center sleeve) connected to the output shaft, and a pressure member capable of approaching or disengaging from the clutch center sleeve.

[0003] Furthermore, the clutch device in Patent Document 1 includes a centrifugal clutch mechanism, which has a counterweight member that moves radially and a retaining member that houses the counterweight member. The counterweight member is configured to move from a radially inner position to a radially outer position by centrifugal force associated with the rotation of the clutch housing, causing the drive-side clutch plate (hereinafter referred to as the input-side rotating plate) to press against the driven-side clutch plate (hereinafter referred to as the output-side rotating plate), thereby transmitting the engine's driving force to the wheels.

[0004] Existing technical documents

[0005] Patent documents

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

[0007] The technical problem that the invention aims to solve

[0008] Furthermore, in the centrifugal clutch mechanism described in Patent Document 1, when the counterweight member housed in the retaining member moves radially, the second spherical member mounted on the counterweight member rolls relative to the retaining member. The second spherical member is held with a portion protruding from the opening of a through hole formed in the counterweight member, which is another member. The counterweight member moves together with the second spherical member, thus generating significant vibration in the centrifugal clutch mechanism during start-up, potentially reducing ride comfort. Additionally, the presence of multiple spherical members increases the number of parts, leading to increased assembly time and cost.

[0009] The present invention was made in view of the above-mentioned problems, and its object is to provide a clutch device that can suppress the decrease in ride comfort during start-up.

[0010] Means for solving technical problems

[0011] The clutch device of the present invention transmits or cuts off the rotational driving force of the input shaft to the output shaft. The clutch device includes: a clutch center sleeve housing a clutch housing that holds a plurality of input-side rotating plates that are rotated by the rotational drive of the input shaft, and rotates together with the output shaft; a pressure member configured to approach or move away from the clutch center sleeve, and to hold at least a portion of a plurality of output-side rotating plates alternately arranged with the input-side rotating plates, and to press the input-side rotating plates and the output-side rotating plates; and a centrifugal clutch mechanism having a plurality of counterweight members configured to move from a radially inner position to a radially outer position by a centrifugal force accompanying the rotation of the clutch housing. When the counterweight members are in the radially outer position, the input-side rotating plates are pressed against the output-side rotating plates to a state capable of transmitting the rotational driving force of the input shaft to the output shaft. Furthermore, when the counterweight members are in the radially inner position, the input-side rotating plates are pressed against the output-side rotating plates. The centrifugal clutch mechanism is capable of cutting off the transmission of the rotational driving force of the input shaft to the output shaft by releasing the pressing force. It includes: a holding member that holds the counterweight member so that it can move between a radially inner position and a radially outer position; a force-applying member disposed on the holding member that applies a force to the counterweight member radially inner; and a pressing member having a pressing-side sliding portion configured to contact the counterweight member, and moving axially along the output shaft by moving the counterweight member from the radially inner position to the radially outer position, thereby pressing the input-side rotating plate against the output-side rotating plate. The counterweight member includes: a first plane extending in a direction intersecting the axial direction of the output shaft, capable of sliding relative to the holding member; and a counterweight-side sliding portion extending in a direction intersecting the axial direction of the output shaft, capable of sliding relative to the pressing-side sliding portion, wherein at least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface inclined relative to the axial direction of the output shaft.

[0012] According to the clutch device of the present invention, the counterweight member has a first plane extending in a direction intersecting the axial direction of the output shaft and capable of sliding relative to the retaining member. Thus, the counterweight member itself slides relative to the retaining member via the first plane, thereby suppressing vibration of the centrifugal clutch mechanism during start-up. That is, it can suppress the reduction in ride comfort during start-up. Furthermore, in addition to the first plane capable of sliding relative to the retaining member, the counterweight member also has a counterweight-side sliding portion capable of sliding relative to the pressing-side sliding portion of the pressing member. Thus, the counterweight member itself can slide relative to both the retaining member and the pressing member, resulting in a smaller number of parts and enabling the clutch device to be easily manufactured at low cost.

[0013] Another clutch device of the present invention transmits or cuts off the rotational driving force of the input shaft to the output shaft, wherein the clutch device comprises: a clutch center sleeve, which houses a clutch housing that holds a plurality of input-side rotating plates that are rotated by the rotational drive of the input shaft, and rotates together with the output shaft; a pressure member, configured to be able to approach or move away from the clutch center sleeve and hold at least a portion of a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates, and is capable of pressing the input-side rotating plates and the output-side rotating plates; and a centrifugal clutch mechanism having a plurality of counterweight members configured to be movable from a radially inner position to a radially outer position by centrifugal force accompanying the rotation of the clutch housing, wherein when the counterweight members are in the radially outer position, the input-side rotating plates are pressed against the output-side rotating plates to a state in which the rotational driving force of the input shaft is transmitted to the output shaft, and when the counterweight members are in the radially inner position, the input-side rotating plates are pressed against the output-side rotating plates to a state in which the rotational driving force of the input shaft is transmitted to the output shaft, and when the counterweight members are in the radially inner position, the input-side rotating plates are pressed against the output-side rotating plates to a state in which the rotational driving force of the input shaft is transmitted to the output shaft, and the input-side rotating plates are pressed against the output shaft by a centrifugal force accompanying the rotation of the clutch housing. The centrifugal clutch mechanism, by releasing the pressing force between the input side rotating plate and the output side rotating plate, can cut off the transmission of the rotational driving force of the input shaft to the output shaft. The centrifugal clutch mechanism includes: a retaining member that holds the counterweight member so that it can move between a radially inner position and a radially outer position; a pressing member that moves axially along the output shaft by moving the counterweight member from the radially inner position to the radially outer position, thereby pressing the input side rotating plate against the output side rotating plate; and a cylindrical member disposed axially between the counterweight member and the retaining member on the output shaft, extending in a direction intersecting the radial direction, and rolling relative to the counterweight member and the retaining member. The counterweight member has a guide portion formed on a surface facing the retaining member, and the guide portion holds the cylindrical member such that a portion of the cylindrical member protrudes from the surface of the counterweight member facing the retaining member toward the retaining member, and guides the radial movement of the cylindrical member.

[0014] According to another clutch device of the present invention, the counterweight member has a guide portion formed on the surface facing the retaining member. The guide portion holds the cylindrical member such that a portion of the cylindrical member protrudes from the surface of the counterweight member facing the retaining member toward the retaining member, and guides the radial movement of the cylindrical member. Here, the cylindrical member can roll relative to both the counterweight member and the retaining member, and only the cylindrical member is guided by the guide portion to move radially independently, thus suppressing vibrations in the centrifugal clutch mechanism during start-up. That is, it can suppress the reduction in ride comfort during start-up.

[0015] Another clutch device of the present invention transmits or cuts off the rotational driving force of the input shaft to the output shaft, wherein the clutch device comprises: a clutch center sleeve, which houses a plurality of input-side rotating plates that are rotated by the rotational drive of the input shaft and rotates together with the output shaft; a pressure member configured to approach or move away from the clutch center sleeve and to hold at least a portion of a plurality of output-side rotating plates alternately arranged with the input-side rotating plates, and to press the input-side rotating plates and the output-side rotating plates; and a centrifugal clutch mechanism having a plurality of counterweight members configured to move from a radially inner position to a radially outer position by centrifugal force associated with the rotation of the clutch housing, wherein when the counterweight members are in the radially outer position, the input-side rotating plates are pressed against the output-side rotating plates to a state in which the rotational driving force of the input shaft is transmitted to the output shaft, and when the counterweight members are in the radially inner position, the input-side rotating plates are pressed against the output-side rotating plates to a state in which the rotational driving force of the input shaft is transmitted to the output shaft, and when the counterweight members are in the radially inner position, the input-side rotating plates are pressed against the output-side rotating plates. The centrifugal clutch mechanism, which can cut off the transmission of the rotational driving force of the input shaft to the output shaft by releasing the pressing force of the rotating plate, includes: a retaining member that holds the counterweight member so that it can move between a radially inner position and a radially outer position; a force-applying member disposed on the retaining member that applies a force to the counterweight member radially inner; and a pressing member having a pressing-side sliding portion configured to contact the counterweight member, and moving axially along the output shaft by moving the counterweight member from the radially inner position to the radially outer position, thereby pressing the input-side rotating plate against the output-side rotating plate. The counterweight member includes: a plane extending in a direction intersecting the axial direction of the output shaft and capable of sliding relative to the retaining member; and a counterweight-side sliding portion located on the side opposite to the plane in the axial direction of the output shaft and capable of sliding relative to the pressing-side sliding portion, wherein at least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface inclined relative to the axial direction of the output shaft.

[0016] According to another clutch device of the present invention, the counterweight member has a plane extending in a direction intersecting the axial direction of the output shaft and capable of sliding relative to the retaining member. Thus, the counterweight member itself slides relative to the retaining member via the plane, thereby suppressing vibrations generated by the centrifugal clutch mechanism during start-up. That is, it can suppress the reduction in ride comfort during start-up. Furthermore, in addition to the plane capable of sliding relative to the retaining member, the counterweight member also has a counterweight-side sliding portion capable of sliding relative to the pressing-side sliding portion of the pressing member. Thus, the counterweight member itself can slide relative to both the retaining member and the pressing member, resulting in a smaller number of parts and enabling the clutch device to be easily manufactured at low cost.

[0017] Invention Effects

[0018] According to the present invention, a clutch device can be provided to suppress the reduction of ride comfort during start-up. Attached Figure Description

[0019] Figure 1 This is a cross-sectional view of the clutch device according to the first embodiment.

[0020] Figure 2 This is a perspective view of the center sleeve of the first clutch according to the first embodiment.

[0021] Figure 3 This is a perspective view of the center sleeve of the first clutch according to the first embodiment.

[0022] Figure 4 This is a perspective view of the center sleeve of the second clutch according to the first embodiment.

[0023] Figure 5 This is a top view of the center sleeve of the second clutch in the first embodiment.

[0024] Figure 6 This is a perspective view of the pressure member in the first embodiment.

[0025] Figure 7 This is a perspective view of the pressure member in the first embodiment.

[0026] Figure 8A This is a schematic diagram illustrating the function of the center-side assist cam surface and the pressure-side assist cam surface.

[0027] Figure 8B This is a schematic diagram illustrating the function of the center-side sliding cam surface and the pressure-side sliding cam surface.

[0028] Figure 9A This is a perspective view showing a portion of the centrifugal clutch mechanism of the first embodiment, and a top view showing the counterweight member located radially inside.

[0029] Figure 9B This is a top view showing a portion of the centrifugal clutch mechanism of the first embodiment, and a top view showing the state in which the counterweight member is located radially inside.

[0030] Figure 10 This is a top view showing the retaining member of the first embodiment.

[0031] Figure 11 This is a perspective view showing the retaining member of the first embodiment.

[0032] Figure 12 This is an enlarged top view showing a portion of the retaining member in the first embodiment.

[0033] Figure 13 This is a perspective view showing the counterweight component of the first embodiment.

[0034] Figure 14 This is a top view showing the counterweight component of the first embodiment.

[0035] Figure 15 This is a perspective view showing the counterweight component of the first embodiment.

[0036] Figure 16 This is a bottom view showing the counterweight component of the first embodiment.

[0037] Figure 17 This is a side view showing the counterweight component of the first embodiment.

[0038] Figure 18 This is a top view showing a portion of the centrifugal clutch mechanism of the first embodiment, and a top view showing the counterweight member located radially outward.

[0039] Figure 19 This is an enlarged top view showing the counterweight component located on the radially outer side.

[0040] Figure 20 This is a cross-sectional view showing a portion of the clutch device according to the first embodiment, and a cross-sectional view showing the state in which the counterweight member is located radially inside.

[0041] Figure 21 This is a cross-sectional view showing a portion of the clutch device according to the first embodiment, and a cross-sectional view showing the counterweight member located on the radially outer side.

[0042] Figure 22 This is a cross-sectional view of the clutch device according to the second embodiment.

[0043] Figure 23 This is a perspective view showing the retaining member of the second embodiment.

[0044] Figure 24 This is a perspective view showing the counterweight component of the second embodiment.

[0045] Figure 25 This is a bottom view showing the counterweight component of the second embodiment.

[0046] Figure 26 This is a side view showing the counterweight component of the second embodiment.

[0047] Figure 27 This is a cross-sectional view showing a portion of the clutch device according to the second embodiment, and a cross-sectional view showing the state in which the counterweight member is located radially inside.

[0048] Figure 28This is a cross-sectional view showing a portion of the clutch device according to the second embodiment, and a cross-sectional view showing the counterweight member located on the radially outer side.

[0049] Figure 29 This is a top view showing a portion of the centrifugal clutch mechanism of the second embodiment, and a top view showing the state in which the counterweight member is located radially inside.

[0050] Figure 30 This is a top view showing a portion of the centrifugal clutch mechanism of the second embodiment, and a top view showing the counterweight member located radially outward.

[0051] Figure 31 This is an enlarged top view showing the state in which the counterweight member of the clutch device in the third embodiment is located radially inside. Detailed Implementation

[0052] Hereinafter, embodiments of the clutch device of the present invention will be described with reference to the accompanying drawings. It should be noted that the embodiments described herein are not intended to limit the present invention in any particular way. Furthermore, components and parts that perform the same function will be labeled with the same reference numerals, and repeated descriptions will be omitted or simplified where appropriate.

[0053] <First Implementation Method>

[0054] Figure 1 This is a cross-sectional view of the clutch device 10 according to this embodiment. The clutch device 10 is provided, for example, in a motorized two-wheeled vehicle or other straddle-type vehicle. The clutch device 10 is, for example, a device that transmits or disconnects the rotational driving force of the input shaft (crankshaft) of an engine, which is an example of the drive source of a motorized two-wheeled vehicle, to the output shaft 15. The clutch device 10 is a device for transmitting or disconnecting the rotational driving force of the input shaft to the drive wheel (rear wheel) via the output shaft 15. The clutch device 10 is disposed between the engine and the transmission.

[0055] In the following description, the direction in which the pressure member 70 of the clutch device 10 approaches and moves away from the clutch center sleeve 40 is defined as direction D; the direction in which the pressure member 70 approaches the clutch center sleeve 40 is defined as the first direction D1; and the direction in which the pressure member 70 moves away from the clutch center sleeve 40 is defined as the second direction D2. Furthermore, the circumferential direction (i.e., the rotational direction) of the clutch center sleeve 40 and the pressure member 70 is defined as circumferential direction S; and the direction in circumferential direction S from one center-side cam portion 60 toward the other center-side cam portion 60 (from one pressure-side cam portion 90 toward the other pressure-side cam portion 90) is defined as the first circumferential direction S1 (refer to...). Figure 2The direction from the center side cam 60 of the other side toward the center side cam 60 of one side (from the pressure side cam 90 of the other side toward the pressure side cam 90 of one side) is set as the second circumferential S2 (refer to...). Figure 2 Additionally, the radial direction of the output shaft 15 is set to radial M, and the direction away from the output shaft 15 is set to outward M1 (refer to...). Figure 20 ), set the direction toward output shaft 15 as the inner side M2 ​​(refer to Figure 20 In this embodiment, the axial direction of the output shaft 15 is the same as that of direction D. Furthermore, the pressure member 70 and the clutch center sleeve 40 rotate along the first circumferential direction S1 (i.e., from the center-side assist cam surface 60A of a center-side cam portion 60 towards the center-side sliding cam surface 60S). However, the above-described direction is merely for ease of explanation and does not limit the arrangement of the clutch device 10, nor does it limit the present invention.

[0056] like Figure 1 As shown, the clutch device 10 includes an output shaft 15, multiple input-side rotating plates 20, multiple output-side rotating plates 22, a clutch housing 30, a clutch center sleeve 40, a pressure member 70, a stop plate 100, a centrifugal clutch mechanism 120, and a power assist clutch plate 180.

[0057] like Figure 1 As shown, the output shaft 15 is a hollow shaft. One end of the output shaft 15 supports the input gear 35 (described later) and the clutch housing 30 via a needle roller bearing 28A, allowing them to rotate freely. The output shaft 15 securely supports the clutch center sleeve 40 via a nut 28B. That is, the output shaft 15 and the clutch center sleeve 40 rotate integrally. The other end of the output shaft 15 is connected, for example, to the transmission (not shown) of a motorized two-wheeled vehicle.

[0058] like Figure 1 As shown, the output shaft 15 includes a main body 15A extending in the direction D. The main body 15A has an oil flow path 15H inside for clutch fluid to circulate. The oil flow path 15H is formed between a sleeve 16C, which is externally fitted into the push rod 16A (described later), and the main body 15A. Clutch fluid circulates within the output shaft 15, specifically within the oil flow path 15H of the main body 15A.

[0059] like Figure 1As 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 configured to slide within the sleeve 16C. One end of the push rod 16A (the end on the left side of the figure) is connected to the clutch operating lever (not shown) of a motorized two-wheeled vehicle, and slides within the sleeve 16C by operating the clutch operating lever, pressing the pressing member 16B in the second direction D2. A portion of the pressing member 16B protrudes outward from the output shaft 15 (in this case, the second direction D2) and is connected to the release bearing 18 provided in the pressure member 70. The sleeve 16C and the pressing member 16B are formed to be smaller than the inner diameter of the main body 15A to ensure the flow of clutch oil within the oil flow path 15H.

[0060] The clutch housing 30 is formed from a die-cast aluminum part. The clutch housing 30 is formed into a bottomed cylindrical shape. For example... Figure 1 As shown, the clutch housing 30 has a bottom wall 31 formed in a generally circular shape and a side wall 33 extending from the edge of the bottom wall 31 in a second direction D2. The clutch housing 30 holds a plurality of input-side rotating plates 20.

[0061] like Figure 1 As 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 and a rivet 35B. The input gear 35 meshes with a drive gear (not shown) that rotates due to the rotational drive of the engine's input shaft. The input gear 35 is rotated integrally with the clutch housing 30, independent of the output shaft 15.

[0062] The input-side rotary plate 20 is driven to rotate by the rotation of the input shaft. For example... Figure 1 As shown, the input-side rotating plate 20 is held on the inner circumferential surface of the side wall 33 of the clutch housing 30. The input-side rotating plate 20 is held in the clutch housing 30 by spline engagement. The input-side rotating plate 20 is configured to be displaceable along the axial direction (i.e., direction D) of the clutch housing 30. The input-side rotating plate 20 is configured to rotate integrally with the clutch housing 30.

[0063] The input-side rotating plate 20 is a component 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 from an aluminum die-casting. Friction elements (not shown) composed of multiple sheets of paper are attached to the surface and back of the input-side rotating plate 20. Grooves for maintaining clutch oil at a depth of several hundred μm are formed between the friction elements.

[0064] like Figure 1As shown, the clutch center sleeve 40 is housed within the clutch housing 30. The clutch center sleeve 40 is concentrically arranged with the clutch housing 30. The clutch center sleeve 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 direction D. The clutch center sleeve 40 is driven to rotate together with the output shaft 15. The clutch center sleeve 40 includes a first clutch center sleeve 41 and a second clutch center sleeve 51. The first clutch center sleeve 41 and the second clutch center sleeve 51 are assembled together. The second clutch center sleeve 51 is located radially M outward M1 of the first clutch center sleeve 41. The second clutch center sleeve 51 is externally fitted into the first clutch center sleeve 41.

[0065] like Figure 2 As shown, the first clutch center sleeve 41 includes an output shaft holding portion 42, an annular base wall 43 located on the outer side M1 of the output shaft holding portion 42 in the radial direction M, and a plurality of center side cam portions 60.

[0066] like Figure 1 As shown, an output shaft 15 is connected to the output shaft holding part 42. Figure 2 As shown, the output shaft holding portion 42 is formed in a cylindrical shape. An insertion hole 45 is formed in the output shaft holding portion 42 for the output shaft 15 to be inserted and splined into. The insertion hole 45 is formed through the output shaft holding portion 42. Multiple engaging teeth 47 extending along the axial direction (i.e., direction D) of the output shaft 15 are formed on the inner wall 45A of the dividing insertion hole 45 in the output shaft holding portion 42. The engaging teeth 47 engage with the output shaft 15.

[0067] The central cam portion 60 is formed as a platform with a cam surface. This cam surface is formed by an inclined surface constituting an assist-slipper (registered trademark) mechanism that generates assist torque or slip torque. Assist torque is the force that increases the pressing force (coupling force) between the input-side rotating plate 20 and the output-side rotating plate 22. Slip torque is the force that decreases the pressing force (coupling force) between the input-side rotating plate 20 and the output-side rotating plate 22, shifting towards a semi-clutch state. The semi-clutch state refers to the state between the fully engaged clutch state (i.e., the state where the input-side rotating plate 20 and the output-side rotating plate 22 are pressed against each other) and the fully disengaged clutch state (i.e., the state where the input-side rotating plate 20 and the output-side rotating plate 22 are separated from each other). Figure 2 As 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 direction. The center-side cam portions 60 are arranged at equal intervals on the circumferential direction S of the first clutch center sleeve 41. In this embodiment, the first clutch center sleeve 41 has three center-side cam portions 60, but the number of center-side cam portions 60 is not limited to three.

[0068] like Figure 2As shown, the center-side cam portion 60 is located radially outward of the output shaft retaining portion 42, at a distance M1. The center-side cam portion 60 has a center-side assist cam surface 60A (see also...). Figure 3 The center-side sliding cam surface 60S is configured such that, during acceleration and other periods of relative rotation relative to the pressure member 70, a force (here, the first direction D1) is generated that causes the pressure member 70 to move towards the clutch center sleeve 40 in order to increase the pressing force (clamping force) between the input-side rotating plate 20 and the output-side rotating plate 22. In this embodiment, when the above force is generated, the position of the pressure member 70 relative to the clutch center sleeve 40 does not change, and the pressure member 70 does not need to physically approach the clutch center sleeve 40. Furthermore, the pressure member 70 may also physically displace relative to the clutch center sleeve 40. The center-side sliding cam surface 60S is configured such that, during deceleration and other periods of relative rotation relative to the pressure member 70, the pressure member 70 moves away from the clutch center sleeve 40 in order to reduce the pressing force (clamping force) between the input-side rotating plate 20 and the output-side rotating plate 22. In the adjacent center-side cam portions 60 on the circumferential S, the center-side assist 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 facing each other on the circumferential S.

[0069] like Figure 2 As shown, the first clutch center sleeve 41 has a plurality of (three in this embodiment) bosses 62. The bosses 62 are members that indirectly hold the pressure member 70. The plurality of bosses 62 are arranged at equal intervals in the circumferential direction S. The bosses 62 are formed in a cylindrical shape. The bosses 62 are located at a position M1 further outward radially M than the output shaft holding portion 42. The bosses 62 extend toward the pressure member 70 (i.e., toward the second direction D2). The bosses 62 are provided on the center-side cam portion 60. The bosses 62 are provided in the circumferential direction S between the center-side assist cam surface 60A and the center-side sliding cam surface 60S. A bolt 28 (see reference) is formed in the bosses 62. Figure 1 The threaded hole 62H is inserted. The threaded hole 62H extends along the axial direction (i.e., direction D) of the clutch center sleeve 40.

[0070] like Figure 2 and Figure 3 As shown, the first clutch center sleeve 41 has a center-side cam hole 43H that penetrates a portion of the base wall 43. The center-side cam hole 43H penetrates the base wall 43 in direction D. The center-side cam hole 43H extends radially M from the side of the output shaft retaining portion 42. The center-side cam hole 43H is located between adjacent center-side cam portions 60 in the circumferential direction S. When viewed axially from the clutch center sleeve 40, the center-side assist cam surface 60A overlaps with a portion of the center-side cam hole 43H.

[0071] like Figure 2As shown, the first clutch center sleeve 41 has a plurality of engagement grooves 49. The engagement grooves 49 are formed on the outer peripheral surface of the base wall 43. The engagement grooves 49 are recessed from the outer peripheral surface of the base wall 43 toward the inner side M2 ​​in the radial direction M.

[0072] like Figure 4 As shown, the second clutch center sleeve 51 has an annular outer peripheral wall 52, a flange 68 extending radially outward M1 from the outer peripheral wall 52, and a center-side engagement portion 54. The second clutch center sleeve 51 is held in place by a plurality of output-side rotating plates 22 that are alternately arranged with the input-side rotating plate 20 in the direction D. The flange 68 is configured to press against the input-side rotating plate 20 and the output-side rotating plate 22.

[0073] like Figure 4 As shown, a splined engagement portion 56 is provided on the outer peripheral surface of the outer peripheral wall 52. The splined engagement portion 56 has a plurality of center-side engagement teeth 57 extending along the outer peripheral surface of the outer peripheral wall 52 in the axial direction (i.e., direction D) of the second clutch center sleeve 51, a plurality of spline grooves 58 formed between adjacent center-side engagement teeth 57 and extending in the axial direction (i.e., direction D) of the second clutch center sleeve 51, and an oil discharge hole 59. The center-side engagement teeth 57 hold the output-side rotating plate 22. The plurality of center-side engagement teeth 57 are arranged circumferentially in the S direction. The plurality of center-side engagement teeth 57 are formed at equal intervals in the circumferential direction S. The plurality of center-side engagement teeth 57 are formed with the same shape. The center-side engagement teeth 57 protrude from the outer peripheral surface of the outer peripheral wall 52 outwards in the radial direction M by M1. The oil discharge hole 59 is formed by penetrating the outer peripheral wall 52 in the radial direction M. The oil discharge hole 59 is formed between adjacent center-side engagement 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 interior and exterior of the second clutch center sleeve 51. The oil discharge hole 59 is a hole for discharging clutch oil and other fluids that flow from the output shaft 15 into the clutch center sleeve 40 to the exterior of the clutch center sleeve 40. The clutch oil discharged from the oil discharge hole 59 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22 located radially M outward M1 of the oil discharge hole 59.

[0074] The output-side rotating plate 22 is held in the spline engagement portion 56 of the second clutch center sleeve 51 and the pressure member 70. A portion of the output-side rotating plate 22 is held in the center-side engagement tooth 57 and spline groove 58 of the second clutch center sleeve 51 by spline engagement. Another portion of the output-side rotating plate 22 is held in the pressure-side engagement tooth 87 of the pressure member 70 (described later). Figure 6The output-side rotating plate 22 is configured to be displaceable along the axial direction (i.e., direction D) of the clutch center sleeve 40. The output-side rotating plate 22 is configured to rotate integrally with the clutch center sleeve 40. The output-side rotating plate 22 is configured to be displaced along the axial direction (i.e., direction D) of the pressure member 70. The output-side rotating plate 22 is configured to rotate integrally with the pressure member 70.

[0075] The output-side rotating plate 22 is a component that presses against the input-side rotating plate 20. The output-side rotating plate 22 is formed in a ring shape. The output-side rotating plate 22 is formed by punching a thin sheet of SPCC material into a ring shape. In addition, the friction element provided on the input-side rotating plate 20 may be provided on the output-side rotating plate 22 instead of the input-side rotating plate 20, or it may be provided on both the input-side rotating plate 20 and the output-side rotating plate 22 separately.

[0076] like Figure 4 As 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 slidably fitted into the pressure-side fitting portion 88 (see reference 88) described later. Figure 6 The inner diameter of the center-side fitting portion 54 is formed such that it allows the output shaft 15 to pass through the front end portion 15T (see reference 88) relative to the pressure-side fitting portion 88. Figure 1 The clutch oil flowing out has a fitting tolerance. That is, a gap is formed between the center-side fitting part 54 and the pressure-side fitting part 88.

[0077] like Figure 4 and Figure 5 As shown, the second clutch center sleeve 51 has multiple engaging protrusions 55. The engaging protrusions 55 engage with the engaging grooves 49 of the first clutch center sleeve 41 (see reference). Figure 2 Engagement. Engagement protrusion 55 is formed on the inner circumferential surface of the outer peripheral wall 52. Engagement protrusion 55 protrudes from the inner circumferential surface of the outer peripheral wall 52 toward the inner side M2 ​​of the radial M.

[0078] like Figure 1 As shown, the pressure member 70 is configured to approach or move away from the clutch center sleeve 40. The pressure member 70 is configured to rotate relative to the clutch center sleeve 40. The pressure member 70 is configured to press the input-side rotating plate 20 and the output-side rotating plate 22. The pressure member 70 is concentrically arranged with the clutch center sleeve 40 and the clutch housing 30. The pressure member 70 is embedded in the second clutch center sleeve 51. This allows for radial M-positioning of the pressure member 70. The pressure member 70 is configured to slide relative to the first clutch center sleeve 41 and the second clutch center sleeve 51 in the direction D. The pressure member 70, the first clutch center sleeve 41, and the second clutch center sleeve 51 are configured to rotate relative to each other in the circumferential direction S. Figure 6As shown, the pressure member 70 has a body 72 and a flange 98, which is connected to the outer periphery of the body 72 on the second direction D2 side and extends radially outward M1. The body 72 protrudes further in the first direction D1 than the flange 98. The flange 98 is located at the outer diameter end of the pressure member 70. The flange 98 is located at the cylindrical portion 80 described later (also refer to...). Figure 7 The pressure member 70 holds at least a portion of the plurality of output-side rotating plates 22 that are alternately arranged with the input-side rotating plate 20. The flange 98 is configured to press the input-side rotating plate 20 and the output-side rotating plate 22.

[0079] like Figure 6 As shown, the main body 72 includes a cylindrical portion 80, multiple pressure-side cam portions 90, a pressure-side fitting portion 88, and a spring receiving portion 84 (see reference). Figure 7 ).

[0080] The cylindrical portion 80 is formed in a cylindrical shape. The cylindrical portion 80 is integrally formed with the pressure-side cam portion 90. The cylindrical portion 80 houses the front end portion 15T of the output shaft 15 (see reference). Figure 1 The cylindrical section 80 houses the release bearing 18 (see reference). Figure 1 The cylindrical portion 80 is the part that receives the pressing force from the pushing member 16B. The cylindrical portion 80 is the part that receives the clutch oil flowing out from the front end 15T of the output shaft 15.

[0081] like Figure 6 As shown, the pressure-side cam portion 90 slides relative to the center-side cam portion 60 and is formed into a platform shape with a cam surface. This cam surface is formed by an inclined surface constituting an assist-slipper (registered trademark) mechanism that generates assist torque or slip torque. The pressure-side cam portion 90 is formed to protrude from the flange 98 in a first direction D1. The pressure-side cam portions 90 are equally spaced along the circumferential direction S of the pressure member 70. In this embodiment, the pressure member 70 has three pressure-side cam portions 90, but the number of pressure-side cam portions 90 is not limited to three.

[0082] like Figure 6 As shown, the pressure-side cam portion 90 is located radially outward by M1 compared to the cylindrical portion 80. The pressure-side cam portion 90 has a pressure-side assist cam surface 90A (see also...). Figure 7The pressure-side sliding cam surface 90A is configured to contact the center-side sliding cam surface 60A. The pressure-side sliding cam surface 90A is configured to generate a force from the pressure member 70 toward the clutch center sleeve 40 (here, the first direction D1) to increase the pressing force (clamping force) between the input-side rotating plate 20 and the output-side rotating plate 22 during acceleration and other relative rotation relative to the clutch center sleeve 40. The pressure-side sliding cam surface 90S is configured to contact the center-side sliding cam surface 60S. The pressure-side sliding cam surface 90S is configured to reduce the pressing force (clamping force) between the input-side rotating plate 20 and the output-side rotating plate 22 during deceleration and other relative rotation relative to the clutch center sleeve 40, causing the pressure member 70 to disengage from the clutch center sleeve 40. In the adjacent pressure-side cam portions 90 in the circumferential direction S, the pressure-side assist 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 facing each other in the circumferential direction S.

[0083] Here, the functions of the center-side cam portion 60 and the pressure-side cam portion 90 are explained. When the engine speed increases 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 sleeve 40, as... Figure 8A As shown, a first circumferential rotational force S1 is applied to the pressure member 70. Therefore, through the action of the center-side assist cam surface 60A and the pressure-side assist cam surface 90A, a force in the first direction D1 is generated in the pressure member 70, increasing the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22.

[0084] On the other hand, when the rotational speed of the output shaft 15 exceeds the rotational speed of the input gear 35 and the clutch housing 30, resulting in reverse torque, such as Figure 8B As shown, a first circumferential rotational force S1 is applied to the clutch center sleeve 40. Therefore, through the action of the center-side sliding cam surface 60S and the pressure-side sliding cam surface 90S, the pressure member 70 moves in the second direction D2, releasing the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22. This avoids adverse effects on the engine and transmission caused by reverse torque.

[0085] like Figure 6 As shown, the pressure-side fitting portion 88 is located radially M outward M1 from the pressure-side cam portion 90. The pressure-side fitting portion 88 is located further in the second direction D2 than the pressure-side cam portion 90. The pressure-side fitting portion 88 is configured to be slidably fitted into the center-side fitting portion 54 (see reference). Figure 4 ).

[0086] like Figure 6 and Figure 7As shown, the pressure member 70 has a pressure-side cam hole 83H that passes through a portion of the main body 72 and the flange 98. The pressure-side cam hole 83H is located at a position M1 radially outward from the cylindrical portion 80. The pressure-side cam hole 83H extends radially from the side of the cylindrical portion 80 to a position M1 radially outward from the pressure-side mating portion 88. The pressure-side cam hole 83H is formed between the pressure-side assist cam surface 90A and the pressure-side sliding cam surface 90S of the adjacent pressure-side cam portion 90. Viewed axially from the pressure member 70, the pressure-side assist cam surface 90A overlaps with a portion of the pressure-side cam hole 83H. A boss portion 62 of the first clutch center sleeve 41 is inserted into the pressure-side cam hole 83H (see reference). Figure 2 The boss portion 62 passes through the pressure side cam hole 83H.

[0087] like Figure 6 As shown, the pressure member 70 includes a plurality of pressure-side engaging teeth 87 disposed on the flange 98. The pressure-side engaging teeth 87 retain at least a portion of the output-side rotating plate 22. The pressure-side engaging teeth 87 protrude from the flange 98 in a first direction D1. The pressure-side engaging teeth 87 are located radially M outward M1 from the cylindrical portion 80. The pressure-side engaging teeth 87 are located radially M outward M1 from the pressure-side cam portion 90. The pressure-side engaging teeth 87 are located radially M outward M1 from the pressure-side engaging portion 88. The plurality of pressure-side engaging teeth 87 are arranged circumferentially S. The plurality of pressure-side engaging teeth 87 are arranged at equal intervals along the circumferential direction S. Furthermore, in this embodiment, since a portion of the pressure-side engaging teeth 87 is removed, the spacing of that portion is wider, but other adjacent pressure-side engaging teeth 87 are arranged at equal intervals. Figure 1 As shown, the pressure-side engagement tooth 87 holds the end plate 21. The end plate 21 is a plate used to adjust the distance in the direction D (i.e., the axial distance of the output shaft 15) between the input-side rotating plate 20 and the output-side rotating plate 22 when the counterweight member 130 described later in the centrifugal clutch mechanism 120 is located in the position M2 inside the radial direction M.

[0088] like Figure 7 As shown, a spring receiving portion 84 is formed on the pressure-side cam portion 90. The spring receiving portion 84 is located radially M outward M1 from the cylindrical portion 80. The spring receiving portion 84 is formed to be recessed from the second direction D2 towards the first direction D1. The spring receiving portion 84 is formed in a circular shape. The spring receiving portion 84 houses the clutch spring 25.

[0089] like Figure 1As shown, the clutch spring 25 is housed in the spring housing portion 84. The end 25D1 of the clutch spring 25 in the first direction D1 abuts against the pressure member 70. The end 25D2 of the clutch spring 25 in the second direction D2 abuts against the stop plate 100. The clutch spring 25 exerts force on the pressure member 70 toward the clutch center sleeve 40 (i.e., toward the first direction D1). The clutch spring 25 is, for example, a helical spring made of spring steel wound into a spiral shape. The clutch spring 25 extends along direction D.

[0090] like Figure 1 As shown, a centrifugal clutch mechanism 120 is disposed within the clutch housing 30. The centrifugal clutch mechanism 120 is positioned closer to the clutch center sleeve 40 in the first direction D1. The centrifugal clutch mechanism 120 is held within the clutch housing 30. The centrifugal clutch mechanism 120 is configured to rotate integrally with the clutch housing 30. Figure 9A As shown, the centrifugal clutch mechanism 120 has multiple counterweight components 130, retaining components 140, and pressing components 150 (see reference). Figure 1 ), Spring 160 (also refer to) Figure 9B Contact component 170 (also refer to) Figure 1 When the centrifugal clutch mechanism 120 is at position PO, outside the radial direction M1, at which point the counterweight member 130 is located (refer to...) Figure 1 and Figure 21 The input-side rotating plate 20 and the output-side rotating plate 22 are pressed together to form a state in which the rotational driving force of the input shaft can be transmitted to the output shaft 15. When the centrifugal clutch mechanism 120 is at position PI, inside the radial direction M on the inner side M2 ​​(refer to...) Figure 20 The centrifugal clutch mechanism 120 releases the pressure between the input-side rotating plate 20 and the output-side rotating plate 22, thus cutting off the transmission of the rotational driving force from the input shaft to the output shaft 15. The centrifugal clutch mechanism 120 is configured to press the power-assisted clutch plate 180 (see reference 120). Figure 1 ).

[0091] like Figure 9B As shown, retaining member 140 holds counterweight member 130 at a position PI on the inner side M2 ​​of the radial M and a position PO on the outer side M1 of the radial M (refer to...). Figure 18 The retaining member 140 is formed in an annular shape. The retaining member 140 is formed from an aluminum die-casting. The retaining member 140 includes a main body 141, multiple engaging claws 143, multiple receiving recesses 145, and a pressing portion 149 (see reference). Figure 1 ).

[0092] like Figure 10 As shown, the main body 141 is formed in a ring shape. Figure 12As shown, the main body 141 includes a thick-walled portion 141T comprising a wall portion 141A and a protrusion 141B. The wall portion 141A is located radially M between the engaging claw 143 and the receiving recess 145. The protrusion 141B protrudes from the wall portion 141A toward the inner side M2 ​​in the radial direction M. The protrusion 141B divides a portion of the receiving recess 145. The end 141BX of the protrusion 141B at the inner side M2 ​​in the radial direction M is located at a position closer to the inner side M2 ​​in the radial direction M than the end 145X of the outer side M1 in the radial direction M of the receiving recess 145. Figure 9B As shown, the protrusion 141B is located in the circumferential direction S between the first spring 161 and the second spring 162, which will be described later.

[0093] like Figure 10 As shown, the engaging pawl 143 protrudes from the outer periphery 141E of the body 141 toward the outer side M1 in the radial direction M. The engaging pawl 143 is integrally formed with the body 141. The engaging pawl 143 and the clutch housing 30 (see reference) Figure 1 (Interlocking.) Multiple interlocking claws 143 are arranged circumferentially in an S-shape. For example... Figure 12 As shown, the engaging claw 143 has a head 143A and a root 143B located radially inward of the head 143A. The circumferential length LA of the head 143A is longer than the circumferential length LB of the root 143B.

[0094] like Figure 1 As shown, the receiving recess 145 is formed in the body 141 in a manner that it is recessed in the axial direction (i.e., direction D) of the output shaft 15. The receiving recess 145 is recessed in the first direction D1. The receiving recess 145 accommodates the counterweight member 130 so that it can move radially M. A plurality of receiving recesses 145 are arranged circumferentially S. Figure 10 and Figure 11 As shown, a sliding surface 145M is provided in the receiving recess 145 for the counterweight member 130 to slide when it moves radially M. A receiving groove 146 is formed in the receiving recess 145 to receive a portion of the spring 160. The receiving groove 146 extends radially M. The receiving groove 146 includes a first receiving groove 146A for receiving the first spring 161 (described later) and a second receiving groove 146B for receiving the second spring 162. The first receiving groove 146A is located on the first circumferential S1 side relative to the protrusion 141B. The second receiving groove 146B is located on the second circumferential S2 side relative to the protrusion 141B. One end of each of the first spring 161 and the second spring 162 abuts against the end 145X of the outer radial M1 of the receiving recess 145. Figure 19As shown, a pressing surface 145H is provided in the receiving recess 145, which is pressed by the counterweight member 130 when the counterweight member 130 is located at position PO, which is the outermost point M1 of the radial direction M. A stress of the outermost point M1 of the radial direction M is applied from the counterweight member 130 to the pressing surface 145H. The engaging pawl 143 is offset from the pressing surface 145H in the circumferential direction S. Here, the engaging pawl 143 is positioned between a pair of pressing surfaces 145H in the circumferential direction S. Alternatively, a through hole may be formed in the receiving recess 145, penetrating the main body 141 along the axial direction (i.e., direction D) of the output shaft 15. In this case, clutch oil flowing outside the retaining member 140 flows into the receiving recess 145 through the through hole.

[0095] like Figure 12 As shown, the circumferential length L1 of the protrusion 141B is greater than the circumferential length L2 of the engaging claw 143. The radial length L3 from the outer periphery 141E of the body 141 to the end 141BX of the inner side M2 ​​of the radial direction M of the protrusion 141B is longer than the radial length L4 from the outer periphery 141E of the body 141 to the end 143X of the outer side M1 of the radial direction M of the engaging claw 143. The end 141BL of the first circumferential S1 of the protrusion 141B is located closer to the first circumferential S1 side than the end 143AL of the first circumferential S1 of the engaging claw 143. Here, the end 143AL of the first circumferential S1 of the engaging claw 143 is the end of the first circumferential S1 of the head 143A. The end 141BR of the second circumferential S2 of the protrusion 141B is located closer to the second circumferential S2 side than the end 143AR of the second circumferential S2 of the engaging claw 143. Here, the end 143AR of the second circumferential S2 of the engaging claw 143 is the end of the second circumferential S2 of the head 143A. Furthermore, the end 141BL of the first circumferential S1 of the protrusion 141B is located closer to the first circumferential S1 side than the end 143BL of the first circumferential S1 of the root 143B. The end 141BR of the second circumferential S2 of the protrusion 141B is located closer to the second circumferential S2 side than the end 143BR of the second circumferential S2 of the root 143B. The surfaces of the wall portion 141A, the protrusion 141B, and the engaging claw 143 on the pressing member 150 side are formed to be coplanar.

[0096] like Figure 9B As shown, multiple counterweight members 130 are arranged circumferentially along the S direction. The counterweight members 130 are configured to move from a position PI, inner side M2 ​​in the radial direction M, to a position outer side by the centrifugal force associated with the rotation of the clutch housing 30. The counterweight members 130 are configured to press the pressing member 150 towards the second direction D2. Figure 20 As shown, the counterweight component 130 is subjected to spring 160 (refer to) when no centrifugal force is applied. Figure 9B ) Maintain the position PI inside M2 ​​in the radial direction. For example Figure 21As shown, the counterweight component 130 is moved outward M1 radially M by being subjected to centrifugal force, overcoming the force of the spring 160, and moves to position PO radially outward M1. At this time, as... Figure 19 As shown, the counterweight member 130 presses against the pressing surface 145H of the receiving recess 145, but the counterweight member 130 does not contact the protrusion 141B of the retaining member 140. The counterweight member 130 is received in the receiving recess 145 of the retaining member 140. Figure 15 As shown, the counterweight member 130 includes: a force-applying member holding portion 131; a first plane 133 disposed on the side of the force-applying member holding portion 131 closer to the circumferential direction S; a second plane 135 disposed on the other side of the force-applying member holding portion 131 closer to the circumferential direction S; and a counterweight-side inclined surface 130F (see reference). Figure 13 The counterweight-side inclined surface 130F is located on the side opposite to the first plane 133 and the second plane 135 in the axial direction (i.e., direction D) of the output shaft 15. It is an example of a counterweight-side sliding part.

[0097] The force-applying component retaining part 131 retains the spring 160. For example... Figure 15 As shown, the force-applying member retaining portion 131 has a groove recessed from the outer side M1 in the first direction D1 toward the second direction D2 and from the outer side M1 in the radial direction M2 toward the inner side M2 ​​of the spring 160. The force-applying member retaining portion 131 includes a retaining wall 132 that retains the inner end of the spring 160 in the radial direction M2. In this embodiment, the force-applying member retaining portion 131 includes a first force-applying member retaining portion 131A that retains the first spring 161 (described later) and a second force-applying member retaining portion 131B that retains the second spring 162 (described later).

[0098] like Figure 15 and Figure 16 As shown, the first plane 133 is positioned closer to the first circumferential S1 side than the force-applying member holding portion 131A. More specifically, the first plane 133 is positioned closer to the first circumferential S1 side than the first force-applying member holding portion 131A. The first plane 133 and the first force-applying member holding portion 131A are arranged circumferentially. The second plane 135 is positioned closer to the second circumferential S2 side than the force-applying member holding portion 131B. More specifically, the second plane 135 is positioned closer to the second circumferential S2 side than the second force-applying member holding portion 131B. The second plane 135 and the second force-applying member holding portion 131B are arranged circumferentially. Figure 17As shown, the first plane 133 and the second plane 135 are planes extending along a direction intersecting the axial direction (i.e., direction D) of the output shaft 15 (e.g., a direction inclined at an angle of 80° or more and 90° or less relative to the axial direction of the output shaft 15; for example, a direction orthogonal to the axial direction of the output shaft 15). The first plane 133 and the second plane 135 are formed to be coplanar. The first plane 133 and the second plane 135 are configured to slide relative to the retaining member 140. More specifically, the first plane 133 and the second plane 135 are configured to slide relative to the sliding surface 145M of the receiving recess 145. Figure 16 As shown, the end 133A of the inner side M2 ​​of the first plane 133 and the end 135A of the inner side M2 ​​of the second plane 135 are located at a position closer to the inner side M2 ​​of the radial M than the retaining wall 132.

[0099] like Figure 15 As shown, the counterweight member 130 includes a third plane 137. The third plane 137 is located between the first plane 133 and the second plane 135 in the circumferential direction S. The third plane 137 is located between the first force-applying member holding portion 131A and the second force-applying member holding portion 131B in the circumferential direction S. The third plane 137 is a plane extending in a direction intersecting the axial direction (i.e., direction D) of the output shaft 15 (for example, a direction inclined at an angle of 80° or more and 90° or less relative to the axial direction of the output shaft 15. For example, a direction orthogonal to the axial direction of the output shaft 15). The third plane 137 may also be configured to slide relative to the holding member 140. The third plane 137 may also be formed to be coplanar with the first plane 133 and the second plane 135.

[0100] The counterweight-side inclined surface 130F is configured to contact the pressing member 150. For example... Figure 17 As shown, the counterweight-side inclined surface 130F is inclined relative to the axial direction (i.e., direction D) of the output shaft 15. The counterweight-side inclined surface 130F is inclined in a first direction D1 from the inner side M2 ​​of the radial M towards the outer side M1 of the radial M. The counterweight-side inclined surface 130F is configured to be able to be inclined relative to the crimping-side inclined surface 150F (described later) of the crimping member 150 (see reference). Figure 20 )slide.

[0101] like Figure 17As shown, the end 133B of the outer radial M1 of the first plane 133 and the end 135B of the outer radial M1 of the second plane 135 are located closer to the outer radial M1 than the end 130FA of the inner radial M2 of the counterweight-side inclined surface 130F. The end 133A of the inner radial M2 of the first plane 133 and the end 135A of the inner radial M2 of the second plane 135 are located closer to the inner radial M2 than the end 130FA of the inner radial M2 of the counterweight-side inclined surface 130F. The length L5 of the radial M of the first plane 133 and the second plane 135 is longer than the length L6 of the radial M of the counterweight-side inclined surface 130F. The combined area of ​​the first plane 133 and the second plane 135 is larger than the area of ​​the counterweight-side inclined surface 130F. The length L7 of the circumferential S from the end 133S1 of the first circumferential S1 of the first plane 133 to the end 135S2 of the second circumferential S2 of the second plane 135 (refer to...) Figure 16 The length L8 of the circumferential S of the counterweight side inclined surface 130F (refer to) Figure 14 )long.

[0102] like Figure 9B As shown, spring 160 is disposed on the outer side M1 of the counterweight member 130 in the radial direction M. Spring 160 is an example of a force-applying member. Spring 160 is disposed on retaining member 140. Spring 160 is received in receiving recess 145 of retaining member 140. More specifically, a portion of spring 160 is received in receiving groove 146 (see reference). Figure 10 A portion of spring 160 is located inside the counterweight member 130. That is, a portion of spring 160 is located within the force-applying member retaining portion 131. Spring 160 applies force to the counterweight member 130 toward the inner side M2 ​​in the radial direction M. Spring 160 is, for example, a helical spring. Spring 160 includes a first spring 161 and a second spring 162 arranged circumferentially S. The first spring 161 is an example of a first force-applying member. The second spring 162 is an example of a second force-applying member. The first spring 161 and the second spring 162 have the same shape. The first spring 161 and the second spring 162 are received in a receiving recess 145. The first spring 161 and the second spring 162 apply force to the counterweight member 130 toward the inner side M2 ​​in the radial direction M. The first spring 161 and the second spring 162 are disposed circumferentially between a first plane 133 and a second plane 135.

[0103] like Figure 1 As shown, the contact member 170 is disposed between the retaining member 140 and the crimping member 150. The contact member 170 is disposed on the opposite side of the retaining member 140, separated from the counterweight member 130, along the axial direction (direction D) of the output shaft 15. Figure 9AAs shown, the contact member 170 is formed in the shape of a circular plate. The contact member 170 is fixed to the retaining member 140. More specifically, the contact member 170 is secured by bolts 172 to bolt holes 140H formed in the retaining member 140 (see reference). Figure 9B The contact member 170 is fixed to the retaining member 140. Furthermore, the means of fixing the contact member 170 to the retaining member 140 are not limited to bolts 172. Instead of bolts 172, other fixing means such as rivets can also be used to fix the contact member 170 to the retaining member 140. The contact member 170 contacts the counterweight member 130. The contact member 170 is a member that inhibits the counterweight member 130 from moving in the second direction D2. A plurality of openings 170H arranged circumferentially S are formed in the contact member 170. The counterweight-side inclined surface 130F of the counterweight member 130 protrudes outward from the openings 170H. A portion of the counterweight member 130 (e.g., the counterweight-side inclined surface 130F) protrudes in the axial direction (here, direction D) of the output shaft 15 toward the opposite side of the retaining member 140 (here, the second direction D2 side) compared to the contact member 170 fixed to the opening of the retaining member 140.

[0104] The crimping member 150 is configured to move along the axial direction (in this case, the second direction D2) of the output shaft 15 by moving from position PI (inner side M2) to position PO (outer side M1) via the counterweight member 130, thereby enabling it to crimp the input-side rotating plate 20 and the output-side rotating plate 22. The crimping member 150 is formed in an annular shape. Figure 1 As shown, the crimping member 150 has a crimping-side inclined surface 150F and a pressing surface 150P. The crimping-side inclined surface 150F is an example of a crimping-side sliding portion. The crimping-side inclined surface 150F is configured to contact the counterweight member 130. The crimping-side inclined surface 150F is inclined relative to the axial direction (i.e., direction D) of the output shaft 15. The crimping-side inclined surface 150F is inclined in a first direction D1 from the inner side M2 ​​of the radial M towards the outer side M1 of the radial M. The crimping-side inclined surface 150F is configured to slide relative to the counterweight-side inclined surface 130F of the counterweight member 130. Figure 21As shown, in a cross-sectional view of a plane including the axial (i.e., direction D) and radial M of the output shaft 15, a straight line CL1 passing through the center 150FC of the radial M of the pressing-side inclined surface 150F and parallel to the axial (i.e., direction D) of the output shaft 15, passes through the first plane 133 and the second plane 135 when the counterweight member 130 is located outside the radial M M1. Multiple pressing-side inclined surfaces 150F are provided on each counterweight member 130 throughout the circumferential S. When the clutch housing 30 rotates and a centrifugal force is applied to the counterweight member 130, the counterweight member 130 moves along the pressing-side inclined surface 150F, thereby moving the pressing member 150 in a direction away from the retaining member 140 (i.e., the second direction D2). As a result, the pressing surface 150P of the pressing member 150 presses against the flange 68 of the second clutch center sleeve 51 towards the second direction D2. The pressing member 150 has multiple engaging protrusions 153 formed throughout the circumferential S. The engaging protrusion 153 overlaps with the engaging claw 143 of the retaining member 140. The engaging protrusion 153 engages with the clutch housing 30. The retaining member 140 and the pressing member 150 are held in the clutch housing 30 by spline engagement. The retaining member 140 and the pressing member 150 are configured to be displaceable along the axial direction (i.e., direction D) of the clutch housing 30. The retaining member 140 and the pressing member 150 are configured to be rotatable integrally with the clutch housing 30.

[0105] In such a centrifugal clutch mechanism 120, such as Figure 9A and Figure 20 As shown, when no centrifugal force is applied to the counterweight 130, the counterweight 130 is held at position PI, inside the radial direction M2, resulting in the release of the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22. On the other hand, as... Figure 18 and Figure 21 As shown, when centrifugal force is applied to the counterweight member 130, the counterweight member 130 moves from the inner side M2 ​​position PI to the outer side M1 position PO in the radial direction M. When the counterweight member 130 moves radially M, the counterweight-side inclined surface 130F of the counterweight member 130 slides against the pressing-side inclined surface 150F of the pressing member 150, and the first plane 133 and the second plane 135 of the counterweight member 130 slide against the sliding surface 145M of the holding member 140. At this time, the pressing surface 150P of the pressing member 150 presses against the input-side rotating plate 20 and the output-side rotating plate 22 via the flange 68 of the second clutch center sleeve 51, thus achieving a pressing state, allowing the rotational driving force of the input shaft to be transmitted to the output shaft 15. Simultaneously, the holding member 140 moves in the first direction D1, and the pressing portion 149 of the holding member 140 (refer to...) Figure 1 Press the power assist clutch plate 180 degrees.

[0106] like Figure 1As shown, a power-assisted clutch plate 180 is disposed within the clutch housing 30. The power-assisted clutch plate 180 is fixed to the output shaft 15. An insertion hole 152H is formed in the power-assisted clutch plate 180 for the output shaft 15 to be inserted and splined. The power-assisted clutch plate 180 is positioned relative to a portion of the centrifugal clutch mechanism 120 on the first direction D1 side. The power-assisted clutch plate 180 is adjacent to the first clutch center sleeve 41.

[0107] The power-assisted clutch plate 180 is configured such that, when the input-side rotating plate 20 and the output-side rotating plate 22 are pressed together (i.e., when the counterweight member 130 of the centrifugal clutch mechanism 120 is located at position PO, M1, on the outer side of radial M), it is pressed by the centrifugal clutch mechanism 120 (here, the pressing portion 149 of the retaining member 140) to a state capable of transmitting the rotational driving force of the input shaft to the output shaft 15. The power-assisted clutch plate 180 is configured such that, when the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22 is released (i.e., when the counterweight member 130 is located at position PI, M2, on the inner side of radial M), the pressing of the centrifugal clutch mechanism 120 (here, the pressing portion 149 of the retaining member 140) is released, cutting off the transmission of the rotational driving force of the input shaft to the output shaft 15.

[0108] like Figure 1 As shown, the stop plate 100 is configured to contact the pressure member 70. The stop plate 100 is a member that prevents the pressure member 70 from moving away from the clutch center sleeve 40 in the second direction D2 by a predetermined distance. The stop plate 100 is fixed to the boss portion 62 of the first clutch center sleeve 41 by bolts 28. With the clutch spring 25 disposed in the spring receiving portion 84, the pressure member 70 is fixed to the clutch center sleeve 40 by fastening the bolts 28 to the boss portion 62 via the stop plate 100. The stop plate 100 is formed into a ring shape when viewed from above.

[0109] As described above, in the clutch device 10 according to this embodiment, the counterweight member 130 has a first plane 133 and a second plane 135. The first plane 133 and the second plane 135 are planes extending in a direction intersecting the axial direction (i.e., direction D) of the output shaft 15 and are slidable relative to the retaining member 140. Thus, the counterweight member 130 itself slides relative to the retaining member 140 via the two planes (i.e., the first plane 133 and the second plane 135), thereby suppressing vibrations in the centrifugal clutch mechanism 120 during start-up. That is, it can suppress the reduction in ride comfort during start-up. Furthermore, in addition to having the first plane 133 and the second plane 135 that are slidable relative to the retaining member 140, the counterweight member 130 also has a counterweight-side inclined surface 130F that is slidable relative to the pressing-side inclined surface 150F of the pressing member 150. Therefore, since the counterweight member 130 itself can slide relative to the retaining member 140 and the pressing member 150, the number of parts is small, and the clutch device 10 can be easily manufactured at low cost.

[0110] In the clutch device 10 of this embodiment, the end 133A of the inner side M2 ​​of the first plane 133 and the end 135A of the inner side M2 ​​of the second plane 135 are located at a position closer to the inner side M2 ​​of the retaining wall 132. According to the above method, since the first plane 133 and the second plane 135 are relatively large, the contact area with the retaining member 140 can be increased.

[0111] In the clutch device 10 of this embodiment, the ends 133B and 135B of the outer radial M of the first plane 133 and the second plane 135 are located closer to the outer radial M of the first plane 133 and the second plane 135 than the end 130FA of the inner radial M of the counterweight inclined surface 130F. The ends 133A and 135A of the inner radial M of the first plane 133 and the second plane 135 are located closer to the inner radial M of the second plane 130FA than the end 130FA of the inner radial M of the counterweight inclined surface 130F. According to this arrangement, since the first plane 133 and the second plane 135 are relatively large, the contact area with the retaining member 140 can be increased.

[0112] In the clutch device 10 of this embodiment, the radial length L5 of the first plane 133 and the second plane 135 is longer than the radial length L6 of the counterweight side inclined surface 130F. According to the above method, since the first plane 133 and the second plane 135 are relatively large, the contact area with the retaining member 140 can be increased.

[0113] In the clutch device 10 of this embodiment, the combined area of ​​the first plane 133 and the second plane 135 is larger than the area of ​​the counterweight-side inclined surface 130F. According to the above method, since the first plane 133 and the second plane 135 are relatively large, the contact area with the retaining member 140 can be increased.

[0114] In the clutch device 10 of this embodiment, the length L7 of the circumferential S from the end 133S2 of the second circumferential S2 of the first plane 133 to the end 135S1 of the first circumferential S1 of the second plane 135 is longer than the length L8 of the circumferential S of the counterweight side inclined surface 130F. According to this method, since the first plane 133 and the second plane 135 are relatively large, the contact area with the retaining member 140 can be increased.

[0115] In the clutch device 10 of this embodiment, a plurality of springs 160 are provided between the first plane 133 and the second plane 135 in the circumferential direction S. According to the above method, the counterweight member 130 itself can slide better relative to the retaining member 140 via the first plane 133 and the second plane 135.

[0116] In the clutch device 10 of this embodiment, in cross-sectional view at a plane including the axial (i.e., direction D) and radial M of the output shaft 15, a straight line CL1, parallel to the axial direction of the output shaft 15 and centered on the radial M of the pressing side inclined surface 150F, passes through the first plane 133 and the second plane 135 when the counterweight member 130 is located outside the radial M M1. According to the above method, since the first plane 133 and the second plane 135 are relatively large, the contact area with the retaining member 140 can be increased.

[0117] <Second Implementation Method>

[0118] like Figure 22 As shown, the centrifugal clutch mechanism 220 of the second embodiment includes a plurality of counterweight members 230, a retaining member 240, a pressing member 150, and a spring 160 (see reference). Figure 25 The centrifugal clutch mechanism 220 has the same structure as the centrifugal clutch mechanism 120 of the first embodiment, except that it has a counterweight member 230 instead of a counterweight member 130, a retaining member 240 instead of a retaining member 140, and a cylindrical member 270.

[0119] like Figure 22 and Figure 23As shown, the retaining member 240 includes a retaining member-side guide 245 that accommodates a portion of the cylindrical member 270. The retaining member-side guide 245 is formed in the receiving recess 145 on a surface 245M facing the counterweight member 230. The retaining member-side guide 245 holds the cylindrical member 270 in such a way that a portion of the cylindrical member 270 protrudes from the surface 245M of the retaining member 240 facing the counterweight member 230 toward the counterweight member 230 (i.e., toward the second direction D2). The retaining member-side guide 245 guides the radial M movement of the cylindrical member 270. The retaining member-side guide 245 is located in the circumferential direction S between the first receiving groove 146A and the second receiving groove 146B. The retaining member-side guide 245 is rectangular in shape when viewed from above. The retaining member-side guide 245 is configured to restrict the movement of the cylindrical member 270 in the circumferential direction S and to restrict the movement of the cylindrical member 270 in the radial direction M by a predetermined distance.

[0120] like Figure 24 As shown, the counterweight member 230 includes a guide portion 238 for receiving a portion of the cylindrical member 270. The guide portion 238 is formed on a surface facing the retaining member 240 (here, the third plane 137). The guide portion 238 holds the cylindrical member 270 in such a manner that a portion of the cylindrical member 270 protrudes from the surface of the counterweight member 230 facing the retaining member 240 (here, the third plane 137) toward the retaining member 240 (i.e., toward the first direction D1). Figure 26 The guide portion 238 guides the radial M movement of the cylindrical member 270. The guide portion 238 is located circumferentially S between the first force-applying member holding portion 131A and the second force-applying member holding portion 131B. Figure 25 As shown, the guide portion 238 is rectangular in shape when viewed from above. The guide portion 238 includes a first limiting portion 238S that restricts the cylindrical member 270 from moving circumferentially in the S direction, and a second limiting portion 238M that restricts the cylindrical member 270 from moving radially in the M direction by a predetermined distance. The first limiting portion 238S is respectively provided on the first circumferential S1 side and the second circumferential S2 side in the circumferential S direction. The second limiting portion 238M is respectively provided on the outer side M1 and the inner side M2 ​​in the radial direction M. The guide portion 238 has a receiving groove 238P that is recessed in the axial direction (i.e., direction D) of the output shaft 15 in the direction from the holding member 240 toward the counterweight member 230 (i.e., the second direction D2) and accommodates a portion of the cylindrical member 270. The receiving groove 238P is divided by the first limiting portion 238S and the second limiting portion 238M.

[0121] like Figure 22As shown, a cylindrical member 270 is disposed between the counterweight member 230 and the retaining member 240 in the axial direction (i.e., direction D) of the output shaft 15. The cylindrical member 270 is configured to extend in a direction intersecting the radial direction M (here, a direction orthogonal to both the radial direction M and direction D). The cylindrical member 270 rolls relative to the counterweight member 230 and the retaining member 240. A portion of the cylindrical member 270 is received in the retaining member-side guide 245 of the retaining member 240, and another portion of the cylindrical member 270 is received in the guide 238 of the counterweight member 230. The cylindrical member 270 rolls relative to the retaining member-side guide 245 and guide 238. Figure 25 As shown, the cylindrical member 270 is located between the first spring 161 and the second spring 162 in the circumferential direction S. The length L9 of the cylindrical member 270 in the circumferential direction S is the same as the length L8 of the counterweight-side inclined surface 130F in the circumferential direction S (refer to...). Figure 14 More than a quarter of that.

[0122] like Figure 27 As shown, in a cross-sectional view along a plane including the output shaft 15 in the axial direction (i.e., direction D) and radial direction M, when the counterweight member 230 is located inside the radial direction M2, at least a portion of the cylindrical member 270 overlaps with the spring 160. Here, the cylindrical member 270 completely overlaps with the spring 160. In a cross-sectional view along a plane including the output shaft 15 in the axial direction (i.e., direction D) and radial direction M, when the counterweight member 230 is located inside the radial direction M2, at least a portion of the guide portion 238 overlaps with the spring 160. Here, the guide portion 238 completely overlaps with the spring 160.

[0123] like Figure 28 As shown, in a cross-sectional view of a plane including the axial (i.e., direction D) and radial M of the output shaft 15, a straight line CL2, parallel to the axial (i.e., direction D) of the output shaft 15 and passing through the center 150FC of the radial M of the inclined surface 150F on the pressing side, passes through the guide portion 238 when the counterweight member 230 is located outside the radial M M1. Figure 29 As shown, when the counterweight member 230 is located inside the radial direction M2 and viewed from the axial direction (i.e., direction D) of the output shaft 15, at least a portion of the counterweight-side inclined surface 130F overlaps with the retaining member-side guide portion 245. Figure 30 As shown, when the counterweight member 230 is located outside the radial direction M1 and viewed from the axial direction (i.e., direction D) of the output shaft 15, the inclined surface 150F of the pressing side overlaps with at least a portion of the guide portion 238.

[0124] In such a centrifugal clutch mechanism 220, such as Figure 27 and Figure 29As shown, when no centrifugal force is applied to the counterweight member 230, the counterweight member 230 is held at position PI, inside the radial direction M2, resulting in a state where the pressing force on the input-side rotating plate 20 and the output-side rotating plate 22 is released. On the other hand, as... Figure 28 and Figure 30 As shown, when centrifugal force is applied to the counterweight member 230, the counterweight member 230 moves from position PI, inner side M2, to position PO, outer side M1, in the radial direction M. As the counterweight member 230 moves radially M, it is guided by the guide portion 238 and the retaining member-side guide portion 245, and the cylindrical member 270 rolls relative to the counterweight member 230 and the retaining member 240. At this time, the first plane 133 and the second plane 135 of the counterweight member 230 do not slide relative to the sliding surface 145M of the retaining member 240.

[0125] According to the clutch device 10 of this embodiment, the counterweight member 230 includes a guide portion 238 formed on a third plane 137 facing the retaining member 240. The guide portion 238 holds the cylindrical member 270 such that a portion of the cylindrical member 270 protrudes from the third plane 137 of the counterweight member 230 toward the retaining member 240, and guides the radial M-direction of the cylindrical member 270. Here, the cylindrical member 270 can roll relative to the counterweight member 230 and the retaining member 240, and only the cylindrical member 270 can be guided by the guide portion 238 to move independently along the radial M. Therefore, vibration generated in the centrifugal clutch mechanism 120 during start-up can be suppressed. That is, the reduction in ride comfort during start-up can be suppressed.

[0126] In the clutch device 10 of this embodiment, the guide portion 238 includes: a first limiting portion 238S that limits the cylindrical member 270 to move in the circumferential direction S; and a second limiting portion 238M that limits the cylindrical member 270 to move in the radial direction M by a predetermined distance or more. According to the above method, the cylindrical member 270 can move smoothly in the guide portion 238 in the radial direction M.

[0127] In the clutch device 10 of this embodiment, the guide portion 238 has a receiving groove 238P that is recessed in the axial direction (i.e., direction D) of the output shaft 15 toward the counterweight member 230 and accommodates a portion of the cylindrical member 270. According to the above method, the cylindrical member 270 can move smoothly in the guide portion 238 in the radial direction M.

[0128] In the clutch device 10 of this embodiment, the first limiting part 238S and the second limiting part 238M divide the receiving groove 238P. According to the above method, the restriction of the movement of the cylindrical member 270 in a predetermined direction and the reception of the cylindrical member 270 can be easily realized.

[0129] In the clutch device 10 of this embodiment, in cross-sectional view along a plane including the output shaft 15 in the axial direction (i.e., direction D) and radial direction M, when the counterweight member 230 is located inside the radial direction M2, at least a portion of the cylindrical member 270 overlaps with the spring 160. According to the above method, the cylindrical member 270 can be compactly arranged in the axial direction of the output shaft 15.

[0130] In the clutch device 10 of this embodiment, the cylindrical member 270 is located between the first spring 161 and the second spring 162 in the circumferential direction S. According to the above method, the cylindrical member 270 can be compactly arranged in the circumferential direction S.

[0131] In the clutch device 10 of this embodiment, in cross-sectional view along a plane including the output shaft 15 in the axial direction (i.e., direction D) and radial direction M, when the counterweight member 230 is located inside the radial direction M2, at least a portion of the guide portion 238 overlaps with the spring 160. According to the above method, the cylindrical member 270 can be compactly arranged in the axial direction of the output shaft 15.

[0132] In the clutch device 10 of this embodiment, in cross-sectional view at a plane including the axial (i.e., direction D) and radial M of the output shaft 15, the counterweight member 230 passes through the guide portion 238 when the counterweight member 230 is located outside the radial M, along the straight line LC2 of the radial M center 150FC of the pressing side inclined surface 150F and parallel to the axial direction of the output shaft 15. According to the above method, since the guide portion 238 is relatively large, the radial M movement range of the cylindrical member 270 can be further expanded.

[0133] In the clutch device 10 of this embodiment, when viewed axially from the output shaft 15 with the counterweight member 230 located on the outer side M1 of the radial direction M, the pressing side inclined surface 150F overlaps with at least a portion of the guide portion 238. According to the above method, the guide portion 238 can be compactly arranged in the radial direction M, thus preventing the counterweight member 230 from becoming too large in the radial direction M.

[0134] In the clutch device 10 of this embodiment, the circumferential length L9 of the cylindrical member 270 is more than one-quarter of the circumferential length L8 of the counterweight-side inclined surface 130F. According to the above method, the cylindrical member 270 can roll well relative to the counterweight member 230 and the retaining member 240.

[0135] In the clutch device 10 of this embodiment, the retaining member 240 includes a retaining member-side guide portion 245, which is formed on a surface 245M facing the counterweight member 230. The retaining member 270 is held in such a way that a portion of the cylindrical member 270 protrudes from the surface 245M of the retaining member 240 facing the counterweight member 230 toward the counterweight member 230, and the radial M-movement of the cylindrical member 270 is guided. According to this method, the radial M-movement of the cylindrical member 270 can be guided more reliably.

[0136] In the clutch device 10 of this embodiment, when viewed axially from the output shaft 15 with the counterweight member 230 located inside the radial direction M on the inner side M2, at least a portion of the counterweight-side inclined surface 130F overlaps with the retaining member-side guide portion 245. According to this method, the radial movement of the cylindrical member 270 can be smoothly guided.

[0137] <Third Implementation Method>

[0138] like Figure 31 As shown, the retaining member 340 of the third embodiment includes a main body 341, a plurality of engaging claws 143, a plurality of receiving recesses 345, and a pressing portion 149 (see reference). Figure 1 ).

[0139] The main body 341 is formed in a ring shape. For example... Figure 31 As shown, the main body 341 includes a wall portion 341A. The wall portion 341A is located radially M between the engaging claw 143 and the receiving recess 345. The wall portion 341A divides a portion of the receiving recess 345.

[0140] like Figure 31 As shown, the receiving recess 345 is formed in the body 341 in such a way that it is recessed axially toward the output shaft 15. The receiving recess 345 is recessed in the first direction D1. The receiving recess 345 houses the counterweight member 130 so that it can move radially M. One end of each of the first spring 161 and the second spring 162 abuts against the end 345X of the outer side M1 of the receiving recess 345 in the radial direction M.

[0141] like Figure 31 As shown, the radial length L10 of the wall portion 341A is longer than the radial length L4 from the outer periphery 141E of the main body 341 to the end 143X of the outer side M1 of the engaging claw 143. Here, the radial length L10 of the wall portion 341A is the radial length from the outer periphery 141E of the main body 341 to the end 345X of the outer side M1 of the receiving recess 345. The circumferential length L11 of the wall portion 341A is greater than or equal to the circumferential length L2 of the engaging claw 143.

[0142] The preferred embodiments of the present invention have been described above. However, the above embodiments are merely illustrative, and the present invention can be implemented in various other ways.

[0143] In the above embodiments, spring 160 is cited as an example of a force-applying member, but the embodiment is not limited to this. The force-applying member may also be an elastomer such as rubber.

[0144] In the above embodiments, an example of a crimp-side sliding portion is a crimp-side inclined surface 150F, and an example of a counterweight-side sliding portion is a counterweight-side inclined surface 130F. Both are inclined surfaces that are inclined relative to the axial direction (i.e., direction D) of the output shaft 15, but are not limited to this. As long as at least one of the crimp-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft 15, the other one may not be an inclined surface but a protrusion or the like.

[0145] In the above embodiments, the counterweight members 130 and 230 are provided with a force-applying member retaining portion 131, but they may not be provided with a force-applying member retaining portion 131. In this case, for example, the spring 160 is configured to abut against the end (e.g., end face) of the outer side M1 of the radial direction M of the counterweight members 130 and 230.

[0146] In the above embodiments, two springs 160 are provided in one counterweight member 130, but this is not a limitation. One spring 160 may be provided in one counterweight member 130, or more than three springs 160 may be provided. For example, when one spring 160 is provided in one counterweight member 130, the counterweight member 130 may also have a force-applying member holding part 131, and two planes (i.e., a first plane 133 and a second plane 135) that can slide relative to the holding member 140 are respectively provided on both sides of the force-applying member holding part 131 in the circumferential direction S.

[0147] In the first embodiment described above, the counterweight member 130 has a first plane 133 and a second plane 135 configured to slide relative to the retaining member 140, but it may also have only one of them. The first plane 133 and the second plane 135 are examples of planes. In this case, the counterweight member 130 itself can slide better relative to the retaining member 140 via the first plane 133 or the second plane 135.

[0148] In the first embodiment described above, the counterweight member 130 includes a first plane 133 and a second plane 135 that are slidable relative to the retaining member 140. However, it can also be configured such that the first plane 133 and the second plane 135 do not slide relative to the retaining member 140, and only the third plane 137 can slide relative to the retaining member 140. Furthermore, one, two, or all of the first plane 133, the second plane 135, and the third plane 137 can be configured to slide relative to the retaining member 140.

[0149] In the first embodiment described above, the first plane 133, the second plane 135 and the third plane 137 are located on the side opposite to the counterweight side inclined surface 130F in the axial direction (i.e., direction D) of the output shaft 15, but they may also be located on the same side as the counterweight side inclined surface 130F.

[0150] In the embodiments described above, the crimping member 150 is configured to indirectly crimp the input-side rotating plate 20 and the output-side rotating plate 22 via the flange 68 of the second clutch center sleeve 51, but is not limited to this. The crimping member 150 may also be configured to crimp the input-side rotating plate 20 and the output-side rotating plate 22 by directly pressing either the input-side rotating plate 20 or the output-side rotating plate 22.

[0151] In the above embodiments, the pressure member 70 (more specifically, the pressure-side engagement tooth 87) holds one output-side rotating plate 22, but multiple output-side rotating plates 22 may also be held.

[0152] In the above embodiments, the pressure member 70 holds a portion of the plurality of output-side rotating plates 22, and the clutch center sleeve 40 (more specifically, the second clutch center sleeve 51) holds another portion of the plurality of output-side rotating plates 22, but is not limited thereto. For example, it is also possible that the pressure member 70 holds all of the plurality of output-side rotating plates 22, and the clutch center sleeve 40 does not hold the output-side rotating plates 22.

[0153] In the above embodiments, the clutch center sleeve 40 includes a first clutch center sleeve 41 and a second clutch center sleeve 51, but the first clutch center sleeve 41 and the second clutch center sleeve 51 may also be integrally formed.

[0154] In the above embodiments, the counterweight member 130 is configured to directly press and connect to the member 150, but it can also be configured to press indirectly.

[0155] In the above embodiments, an engine is used as the driving source, but the driving source is not limited to an engine; for example, it can also be an electric motor.

[0156] The technology disclosed herein can be applied to various types of clutch devices. In the embodiments described above, a so-called internal wedge clutch device has been used as an example, where the axial pressure member 70 of the output shaft 15 is located on the side opposite to the clutch housing 30, separated from the clutch center sleeve 40, but this is not a limitation. For example, it can also be applied to a so-called external wedge clutch device where the axial pressure member 70 of the output shaft 15 is located between the clutch center sleeve 40 and the clutch housing 30.

[0157] Explanation of reference numerals in the attached figures

[0158] 10 Clutch Device

[0159] 15 output shafts

[0160] 20 Input Side Rotary Plate

[0161] 22 Output Side Rotary Plate

[0162] 30 Clutch Housing

[0163] 40 clutch center sleeve

[0164] 70 pressure components

[0165] 120 centrifugal clutch mechanism

[0166] 130 counterweight components

[0167] 130F counterweight side inclined surface (counterweight side sliding part)

[0168] 131 Force-applying component retention part

[0169] 131A First Force-Applying Component Holding Part

[0170] 131B Second Force-Applying Component Holding Part

[0171] 132 retain wall

[0172] 133 First Plane

[0173] 133A radial inner end

[0174] 135 Second Plane

[0175] 135A radial inner end

[0176] 137 Third Plane

[0177] 140 retaining member

[0178] 145 Containment recess

[0179] 145M sliding surface

[0180] 150 Crimped Components

[0181] 150F Crimping Side Inclined Surface (Crimping Side Sliding Part)

[0182] 160 spring (force-applying component)

[0183] 161 First Spring

[0184] 162 Second Spring

[0185] 220 Centrifugal Clutch Mechanism

[0186] 230 counterweight components

[0187] 238 Guidance Department

[0188] 238S First Restriction Section

[0189] 238M Second Restriction Section

[0190] 238P Reception Slot

[0191] 240 retaining member

[0192] 245 Retaining component side guide

[0193] 270 cylindrical components

Claims

1. A clutch device for transmitting or disengaging the rotational driving force of an input shaft to an output shaft, wherein, The clutch device includes: A clutch center sleeve is housed in a clutch housing that holds multiple input-side rotating plates that are rotated by the rotational drive of the input shaft, and is rotated together with the output shaft. A pressure member is configured to approach or disengage relative to the clutch center sleeve, and to retain at least a portion of a plurality of output-side rotating plates alternately arranged with the input-side rotating plate, and to press against the input-side rotating plate and the output-side rotating plate; and A centrifugal clutch mechanism includes multiple counterweight members configured to move from a radially inner position to a radially outer position via centrifugal force accompanying the rotation of the clutch housing. When the counterweight members are in the radially outer position, the input-side rotating plate is pressed against the output-side rotating plate to transmit the rotational driving force of the input shaft to the output shaft. When the counterweight members are in the radially inner position, the pressing force between the input-side rotating plate and the output-side rotating plate is released to cut off the transmission of the rotational driving force from the input shaft to the output shaft. The centrifugal clutch mechanism includes: A retaining member holds the counterweight member so that it can move between a position on the inner side of the radial direction and a position on the outer side of the radial direction; A force-applying component, disposed on the retaining component, applies a force to the counterweight component in the radial direction inward; and The pressing member has a pressing-side sliding portion configured to contact the counterweight member, and moves axially along the output shaft by moving the counterweight member from a radially inner position to a radially outer position, thereby pressing the input-side rotating plate against the output-side rotating plate. The counterweight component includes: The first plane is a plane extending in a direction intersecting the axial direction of the output shaft, and is capable of sliding relative to the retaining member; and The counterweight-side sliding portion is a plane extending in a direction intersecting the axial direction of the output shaft, and is capable of sliding relative to the pressing-side sliding portion. At least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft.

2. The clutch device according to claim 1, wherein, The counterweight component includes a force-applying component retaining part for holding the force-applying component. The first plane is positioned on the circumferential side of the force-applying member holding portion. The counterweight-side sliding part is located on the side opposite to the first plane in the axial direction of the output shaft.

3. The clutch device according to claim 2, wherein, The counterweight member has a second plane, which is located on the other side of the circumference than the holding part of the force-applying member, and is a plane extending in a direction intersecting the axial direction of the output shaft, and is capable of sliding relative to the holding member.

4. The clutch device according to claim 3, wherein, The force-applying member retaining portion includes a retaining wall that retains the radially inner end of the force-applying member. The radially inner end of the first plane and the radially inner end of the second plane are located at a position that is radially inner than the retaining wall.

5. The clutch device according to claim 3, wherein, The radially outer ends of the first plane and the second plane are located further radially outer than the radially inner end of the counterweight-side sliding portion. The radially inner ends of the first plane and the second plane are located closer to the radially inner end than the radially inner end of the counterweight sliding portion.

6. The clutch device according to claim 5, wherein, The radial lengths of the first plane and the second plane are longer than the radial lengths of the counterweight-side sliding portion.

7. The clutch device according to claim 3, wherein, The combined area of ​​the first plane and the second plane is larger than the area of ​​the counterweight-side sliding part.

8. The clutch device according to claim 3, wherein, The circumferential length from one end of the first plane to the other end of the second plane is longer than the circumferential length of the counterweight-side sliding portion.

9. The clutch device according to claim 3, wherein, In the circumferential direction, a plurality of force-applying members are provided between the first plane and the second plane.

10. The clutch device according to claim 3, wherein, In a cross-sectional view at a plane including the axial and radial directions of the output shaft, a straight line passing through the radial center of the pressing-side sliding portion and parallel to the axial direction of the output shaft passes through the first plane and the second plane when the counterweight member is located outside the radial direction.

11. The clutch device according to claim 3, wherein, The pressing-side sliding portion is a pressing-side inclined surface that is inclined relative to the axial direction of the output shaft. The counterweight-side sliding part is a counterweight-side inclined surface that is axially inclined relative to the output shaft and slides relative to the pressing-side inclined surface.

12. A clutch device that transmits or disconnects the rotational driving force of an input shaft to an output shaft, wherein, The clutch device includes: A clutch center sleeve is housed in a clutch housing that holds multiple input-side rotating plates that are rotated by the rotational drive of the input shaft, and is rotated together with the output shaft. A pressure member is configured to approach or disengage relative to the clutch center sleeve, and to retain at least a portion of a plurality of output-side rotating plates alternately arranged with the input-side rotating plate, and to press against the input-side rotating plate and the output-side rotating plate; and A centrifugal clutch mechanism includes multiple counterweight members configured to move from a radially inner position to a radially outer position via centrifugal force accompanying the rotation of the clutch housing. When the counterweight members are in the radially outer position, the input-side rotating plate is pressed against the output-side rotating plate to transmit the rotational driving force of the input shaft to the output shaft. When the counterweight members are in the radially inner position, the pressing force between the input-side rotating plate and the output-side rotating plate is released to cut off the transmission of the rotational driving force from the input shaft to the output shaft. The centrifugal clutch mechanism includes: A retaining member holds the counterweight member so that it can move between a position on the inner side of the radial direction and a position on the outer side of the radial direction; The pressing member moves axially along the output shaft by moving from the inner radial position to the outer radial position via the counterweight member, thereby pressing the input side rotating plate against the output side rotating plate. and A cylindrical member is disposed axially between the counterweight member and the retaining member on the output shaft, extends in a direction intersecting the radial direction, and rolls relative to the counterweight member and the retaining member. The counterweight member has a guide portion formed on a surface facing the retaining member, and holds the cylindrical member such that a portion of the cylindrical member protrudes from the surface of the counterweight member facing the retaining member toward the retaining member, and guides the radial movement of the cylindrical member.

13. The clutch device according to claim 12, wherein, The guide portion includes: a first limiting portion for limiting the cylindrical member to move in the circumferential direction; and a second limiting portion for limiting the cylindrical member to move a predetermined distance or more in the radial direction.

14. The clutch device according to claim 13, wherein, The guide portion has a receiving groove that is recessed in the axial direction of the output shaft from the retaining member toward the counterweight member, and receives a portion of the cylindrical member.

15. The clutch device according to claim 14, wherein, The first limiting part and the second limiting part divide the receiving groove.

16. The clutch device according to claim 12, wherein, The centrifugal clutch mechanism includes a force-applying member disposed on the retaining member and applying a force to the counterweight member radially inward. In a cross-sectional view along a plane including the axial and radial directions of the output shaft, at least a portion of the cylindrical member overlaps with the force-applying member when the counterweight member is located inside the radial direction.

17. The clutch device according to claim 16, wherein, The force-applying components include a first force-applying component and a second force-applying component arranged circumferentially. The cylindrical component is located between the first force-applying component and the second force-applying component in the circumferential direction.

18. The clutch device according to claim 12, wherein, The centrifugal clutch mechanism includes a force-applying member disposed on the retaining member and applying a force to the counterweight member radially inward. In a cross-sectional view along a plane including the axial and radial directions of the output shaft, when the counterweight member is located inside the radial direction, at least a portion of the guide portion overlaps with the force-applying member.

19. The clutch device according to claim 12, wherein, The pressing member has a pressing-side sliding portion configured to contact the counterweight member. The counterweight component has a counterweight-side sliding portion that can slide relative to the pressing-side sliding portion. At least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft. In a cross-sectional view in a plane including the axial and radial directions of the output shaft, a straight line passing through the radial center of the pressing-side sliding portion and parallel to the axial direction of the output shaft passes through the guide portion when the counterweight member is located outside the radial direction.

20. The clutch device according to claim 12, wherein, The pressing member has a pressing-side sliding portion configured to contact the counterweight member. The counterweight component has a counterweight-side sliding portion that can slide relative to the pressing-side sliding portion. At least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft. When viewed axially from the output shaft with the counterweight member located on the outer side of the radial direction, the pressing-side sliding portion overlaps with at least a portion of the guide portion.

21. The clutch device according to claim 12, wherein, The pressing member has a pressing-side sliding portion configured to contact the counterweight member. The counterweight component has a counterweight-side sliding portion that can slide relative to the pressing-side sliding portion. At least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft. The circumferential length of the cylindrical component is more than one-quarter of the circumferential length of the counterweight-side sliding part.

22. The clutch device according to claim 12, wherein, The retaining member has a retaining member side guide portion formed on the surface facing the counterweight member, and retains the cylindrical member in such a way that a portion of the cylindrical member protrudes from the surface of the retaining member facing the counterweight member toward the counterweight member, and guides the radial movement of the cylindrical member.

23. The clutch device according to claim 22, wherein, The pressing member has a pressing-side sliding portion configured to contact the counterweight member. The counterweight component has a counterweight-side sliding portion that can slide relative to the pressing-side sliding portion. At least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft. When viewed axially from the output shaft with the counterweight member located inside the radial direction, at least a portion of the counterweight-side sliding portion overlaps with the retaining member-side guide portion.

24. A clutch device that transmits or disconnects the rotational driving force of an input shaft to an output shaft, wherein, The clutch device includes: A clutch center sleeve is housed in a clutch housing that holds multiple input-side rotating plates that are rotated by the rotational drive of the input shaft, and is rotated together with the output shaft. A pressure member is configured to approach or disengage relative to the clutch center sleeve, and to retain at least a portion of a plurality of output-side rotating plates alternately arranged with the input-side rotating plate, and to press against the input-side rotating plate and the output-side rotating plate; and A centrifugal clutch mechanism includes multiple counterweight members configured to move from a radially inner position to a radially outer position via centrifugal force accompanying the rotation of the clutch housing. When the counterweight members are in the radially outer position, the input-side rotating plate is pressed against the output-side rotating plate to transmit the rotational driving force of the input shaft to the output shaft. When the counterweight members are in the radially inner position, the pressing force between the input-side rotating plate and the output-side rotating plate is released to cut off the transmission of the rotational driving force from the input shaft to the output shaft. The centrifugal clutch mechanism includes: A retaining member holds the counterweight member so that it can move between a position on the inner side of the radial direction and a position on the outer side of the radial direction; A force-applying component, disposed on the retaining component, applies a force to the counterweight component in the radial direction inward; and The pressing member has a pressing-side sliding portion configured to contact the counterweight member, and moves axially along the output shaft by moving the counterweight member from a radially inner position to a radially outer position, thereby pressing the input-side rotating plate against the output-side rotating plate. The counterweight component includes: A plane extending in a direction intersecting the axial direction of the output shaft and capable of sliding relative to the retaining member; and The counterweight-side sliding portion is located on the side opposite to the plane in the axial direction of the output shaft, and is capable of sliding relative to the pressing-side sliding portion. At least one of the pressing-side sliding portion and the counterweight-side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft.

25. The clutch device according to claim 24, wherein, The counterweight component includes a force-applying component retaining part for holding the force-applying component. The plane and the force-applying member retaining part are arranged in a circumferential direction.

26. The clutch device according to claim 24, wherein, The counterweight component includes a force-applying component retaining part for holding the force-applying component. The plane includes: A first plane is disposed on a circumferential side of the force-applying member retaining portion, and extends in a direction intersecting the axial direction of the output shaft, and is slidable relative to the retaining member; and The second plane is located on the other side of the circumference of the force-applying member holding part, and is a plane extending in a direction intersecting the axial direction of the output shaft, and is slidable relative to the holding member.

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