Clutch device

Abstract

A clutch device (10) is provided with a clutch center section (40) and a pressure member (70). The pressure member (70) is provided with: a first pressure member (71); a second pressure member (81) externally fitted to the first pressure member (71); and a void portion (95) formed in the radial direction between an outer peripheral surface (75) of an opening end portion (71T) adjacent to the clutch center portion (40) of the first pressure member (71) and an inner peripheral surface (85) of the second pressure member (81) externally fitted to the outer peripheral surface (75), and a first notch (71H) capable of guiding clutch oil in the first pressure member (71) to the void portion (95) is formed in the opening end portion (71T) of the first pressure member (71).

Description

Technical Field

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

[0002] Straddle-type vehicles, such as motorcycles, are equipped with a clutch device capable of transmitting and disconnecting the rotational driving force of a power source, such as an engine, to the drive wheels. For example, Patent Document 1 discloses a clutch device comprising an input member (hereinafter referred to as an input shaft) coupled to the engine, an output member (hereinafter referred to as an output shaft) coupled to the drive wheels, a clutch member (hereinafter referred to as a clutch core) coupled to the output shaft, and a pressure member capable of moving toward and away from the clutch core.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: Japanese Patent Application Laid-Open No. 2022-173521 Summary of the Invention

[0006] Problems to be solved by the invention

[0007] However, the pressure member disclosed in Patent Document 1 is divided into a bearing retaining member located radially inward (hereinafter referred to as the first pressure member) and a pressure member located radially outward (hereinafter referred to as the second pressure member). To position the second pressure member relative to the first pressure member, the outer circumferential surface of the first pressure member contacts the inner circumferential surface of the second pressure member. Furthermore, the first pressure member is configured to slide relative to the second pressure member. However, since there is no gap between the outer circumferential surface of the first pressure member and the inner circumferential surface of the second pressure member, there is a problem that clutch oil cannot flow between the first and second pressure members, resulting in wear of the sliding portions of the first and second pressure members.

[0008] The present invention has been made in view of the above-mentioned points, and an object thereof is to provide a clutch device capable of supplying clutch oil to a sliding portion between a first pressure member and a second pressure member.

[0009] Means for solving problems

[0010] A clutch device according to the present invention transmits or disconnects the rotational driving force of an input shaft from an output shaft, and includes: a clutch core portion housed in a clutch housing that holds a plurality of input-side rotating plates that are rotationally driven by the rotational drive of the input shaft, and that holds a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates and is rotationally driven together with the output shaft; and a pressure member that is arranged to be able to approach or separate from the clutch core portion and to be relatively rotatable, and that is capable of pressing the input-side rotating plates and the output-side rotating plates. The pressure member includes: a first pressure member; a second pressure member externally fitted to the first pressure member; and a gap portion formed in a radial direction of the output shaft between an outer circumferential surface of an open end portion of the first pressure member adjacent to the clutch core portion and an inner circumferential surface of the second pressure member externally fitted to the outer circumferential surface. A first oil passage is formed in the open end portion of the first pressure member or in a portion of the clutch core portion adjacent to the open end portion of the first pressure member, and the first oil passage is capable of guiding clutch oil in the first pressure member to the gap portion.

[0011] According to the clutch device of the present invention, a first oil passage is formed at the open end of the first pressure member or at a portion of the clutch center adjacent to the open end of the first pressure member, capable of directing clutch oil within the first pressure member to the gap. This configuration allows clutch oil within the first pressure member to be supplied to the gap via the first oil passage. This prevents wear caused by sliding between the outer circumferential surface of the first pressure member and the inner circumferential surface of the second pressure member.

[0012] The clutch assembly of the present invention is a clutch assembly for transmitting or cutting off the rotational driving force of the input shaft relative to the output shaft, wherein the clutch assembly comprises: a clutch center portion accommodated in a clutch housing for holding a plurality of input-side rotating plates that are rotationally driven by the rotation of the input shaft, and a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates and are rotationally driven together with the output shaft; and a pressure member that is arranged to be close to or separate from the clutch center portion and to be relatively rotatable, and can press the input-side rotating plates and the output-side rotating plates, the pressure member comprising: a first pressure member; and a second pressure member that is externally fitted to the first pressure member, the first pressure member The force member and the second pressure member are configured to be rotatable relative to each other in the circumferential direction, and a first oil passage is formed at an open end portion of the first pressure member adjacent to the clutch center portion, the first oil passage being capable of guiding the clutch oil in the first pressure member to the outside of the first pressure member, and a second oil passage is formed at a portion of the second pressure member located radially outside the output shaft of the open end portion of the first pressure member, the second oil passage being capable of guiding the clutch oil to the outside of the second pressure member, and when the first pressure member and the second pressure member rotate relative to each other in the circumferential direction, the first oil passage and the second oil passage overlap when viewed in the radial direction of the output shaft.

[0013] According to another clutch device of the present invention, when the first and second pressure members rotate relative to each other, the first oil passage and the second oil passage communicate. This arrangement allows clutch oil within the first pressure member to be supplied to the exterior of the second pressure member via the first and second oil passages. Furthermore, clutch oil flowing in the first oil passage is supplied to the exterior of the first pressure member, for example, between the outer circumferential surface of the first pressure member and the inner circumferential surface of the second pressure member.

[0014] Effects of the Invention

[0015] According to the present invention, it is possible to provide a clutch device capable of supplying clutch oil to a sliding portion between a first pressure member and a second pressure member. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 This is a cross-sectional view of a clutch device according to one embodiment.

[0017] Figure 2 This is an enlarged cross-sectional view of a portion of a clutch device according to one embodiment.

[0018] Figure 3 This is a perspective view of the center portion of the first clutch according to one embodiment.

[0019] Figure 4 This is a perspective view of the center portion of the first clutch according to one embodiment.

[0020] Figure 5 This is a perspective view of the second clutch center portion according to one embodiment.

[0021] Figure 6 It is a top view of the second clutch center portion according to one embodiment.

[0022] Figure 7 This is a perspective view of a pressure member according to one embodiment.

[0023] Figure 8 This is a perspective view of a first pressure member according to one embodiment.

[0024] Figure 9 This is a perspective view of a first pressure member according to one embodiment.

[0025] Figure 10 This is a perspective view of a second pressure member according to one embodiment.

[0026] Figure 11 This is a perspective view of a second pressure member according to one embodiment.

[0027] Figure 12A This is a schematic diagram for explaining the functions of the center-side auxiliary cam surface and the pressure-side auxiliary cam surface.

[0028] Figure 12B This is a schematic diagram explaining the functions of the center-side sliding cam surface and the pressure-side sliding cam surface.

[0029] Figure 13 This is a cross-sectional view of a centrifugal clutch mechanism according to one embodiment.

[0030] Figure 14 This is a partially cutaway perspective view of a centrifugal clutch mechanism according to one embodiment.

[0031] Figure 15 It is a top view of a clutch device according to one embodiment.

[0032] Figure 16 This is a perspective view of a clutch device according to an embodiment. DETAILED DESCRIPTION

[0033] The following describes embodiments of the clutch device of the present invention with reference to the accompanying drawings. It should be noted that the embodiments described herein are not intended to limit the present invention. Components and locations that perform the same function are denoted by the same reference numerals, and any duplicate descriptions are omitted or simplified as appropriate.

[0034] Figure 1This is a cross-sectional view of a clutch device 10 according to this embodiment. The clutch device 10 is provided on a saddle-type vehicle, such as a motorcycle. The clutch device 10 is a device that transmits or disconnects the rotational driving force of the input shaft (crankshaft) of the engine, which serves as the power source for the motorcycle, to the output shaft 15. The clutch device 10 transmits or disconnects the rotational driving force of the input shaft to the drive wheels (rear wheels) via the output shaft 15. The clutch device 10 is disposed between the engine and the transmission.

[0035] In the following description, the direction in which the pressure member 70 of the clutch device 10 approaches and separates from the clutch center 40 is referred to as direction D, the direction in which the pressure member 70 approaches the clutch center 40 is referred to as first direction D1, and the direction in which the pressure member 70 separates from the clutch center 40 is referred to as second direction D2. Furthermore, the circumferential direction (i.e., the rotational direction) of the clutch center 40 and the pressure member 70 is referred to as circumferential direction S, and the direction from one center-side cam portion 60 toward the other center-side cam portion 60 (the direction from one pressure-side cam portion 90 toward the other pressure-side cam portion 90) in the circumferential direction S is referred to as first circumferential direction S1 (see FIG. 1 ). Figure 3 ), the direction from the other center-side cam portion 60 toward the one center-side cam portion 60 (the direction from the other pressure-side cam portion 90 toward the one pressure-side cam portion 90) is defined as the second circumferential direction S2 (refer to Figure 3 In this embodiment, the axial direction of the output shaft 15 is the same as direction D. Furthermore, the pressure member 70 and the clutch center 40 rotate in the first circumferential direction S1 (i.e., from the center-side auxiliary cam surface 60A of one center-side cam portion 60 toward the center-side sliding cam surface 60S). However, the above directions are merely defined for ease of explanation and do not limit the configuration of the clutch device 10 or the present invention in any way.

[0036] 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 40, a pressure member 70, a stopper plate 100, a centrifugal clutch mechanism 120, an auxiliary clutch plate 150 and a disc spring 180.

[0037] like Figure 1 As shown, the output shaft 15 is a hollow shaft. One end of the output shaft 15 rotatably supports an input gear 35 (described later) and the clutch housing 30 via a needle bearing 28A. The output shaft 15 securely supports the clutch center 40 via a nut 28B. In other words, the output shaft 15 rotates integrally with the clutch center 40. The other end of the output shaft 15 is connected to, for example, a transmission (not shown) of a motorcycle.

[0038] like Figure 1 As shown, the output shaft 15 includes a main body 15A extending in a direction D. The main body 15A has an oil flow path 15H therein for the flow of clutch oil. The oil flow path 15H is formed between a sleeve 16C and the main body 15A. The sleeve 16C is externally fitted to a push rod 16A (described later). The clutch oil flows within the output shaft 15, that is, within the oil flow path 15H of the main body 15A.

[0039] like Figure 1 As shown, the oil flow path 15H of the output shaft 15 is provided with a push rod 16A and a pressing member 16B disposed adjacent to the push rod 16A. The push rod 16A and the pressing member 16B are slidable within a sleeve 16C. One end of the push rod 16A (the left end in the figure) is connected to the clutch operating lever (not shown) of the motorcycle. When the clutch operating lever is operated, the push rod 16A slides within the sleeve 16C, 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, in the second direction D2) and is connected to the release bearing 18 disposed on the pressure member 70. The sleeve 16C and the pressing member 16B are formed to be thinner than the inner diameter of the main body 15A, ensuring the flow of clutch oil within the oil flow path 15H.

[0040] The clutch housing 30 is formed of aluminum alloy. The clutch housing 30 is formed into a bottomed cylindrical shape. Figure 1 As shown, the clutch housing 30 includes a bottom wall 31 formed in a substantially circular shape and a side wall 33 extending in the second direction D2 from an edge of the bottom wall 31. The clutch housing 30 holds a plurality of input-side rotating plates 20.

[0041] 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 secured to the bottom wall 31 via a torque buffer 35A and rivets 35B. The input gear 35 meshes with a drive gear (not shown) that is rotated by the rotation of the engine's input shaft. The input gear 35 is driven to rotate integrally with the clutch housing 30, independent of the output shaft 15.

[0042] The input side rotating piece 20 is driven to rotate by the rotation of the input shaft. Figure 1 As shown, the input-side rotating plate 20 is retained on the inner circumferential surface of the side wall 33 of the clutch housing 30. The input-side rotating plate 20 is retained by the clutch housing 30 through a spline fit. The input-side rotating plate 20 is configured to be displaceable along the axial direction of the clutch housing 30 (i.e., direction D). The input-side rotating plate 20 is configured to rotate integrally with the clutch housing 30.

[0043] The input-side rotating plate 20 is a component that is pressed against the output-side rotating plate 22. It is annular and formed by aluminum die-casting. Friction materials (not shown) made of multiple paper sheets are attached to the front and back surfaces of the input-side rotating plate 20. Grooves several hundred microns deep are formed between the friction materials to retain clutch oil.

[0044] like Figure 1 As shown, the clutch center 40 is housed in the clutch housing 30. The clutch center 40 is concentrically arranged with the clutch housing 30. The clutch center 40 holds a plurality of output-side rotating plates 22 arranged alternately with the input-side rotating plates 20 in direction D. The clutch center 40 is driven to rotate together with the output shaft 15. The clutch center 40 includes a first clutch center 41 and a second clutch center 51. The first clutch center 41 and the second clutch center 51 are assembled together. The second clutch center 51 is located radially outward of the first clutch center 41. The second clutch center 51 is externally fitted to the first clutch center 41.

[0045] like Figure 3 As shown, the first clutch center portion 41 includes an output shaft holding portion 42 , an annular base wall 43 located radially outside the output shaft holding portion 42 , and a plurality of center-side cam portions 60 .

[0046] like Figure 1 As shown in FIG. 1 , the output shaft 15 is connected to the output shaft holding portion 42. The first pressure member 71 described later is externally fitted to the output shaft holding portion 42. Figure 3 As shown, the output shaft retaining portion 42 is formed in a cylindrical shape. An insertion hole 45 is formed in the output shaft retaining portion 42, into which the output shaft 15 is inserted and spline-engaged. The insertion hole 45 is formed through the output shaft retaining portion 42. A plurality of engaging teeth 47 extending along the axis of the output shaft 15 (i.e., direction D) are formed on an inner wall 45A of the output shaft retaining portion 42 that defines the insertion hole 45. The engaging teeth 47 engage with the output shaft 15.

[0047] The center-side cam portion 60 is formed into a table shape having a cam surface. The cam surface is composed of an inclined surface that constitutes an assist & slide (registered trademark) mechanism. The assist slide mechanism generates an assist torque that increases the pressing force (pressing force) between the input-side rotating piece 20 and the output-side rotating piece 22, or a slide torque that reduces the pressing force (pressing force) between the input-side rotating piece 20 and the output-side rotating piece 22 and shifts to a semi-clutch state. Figure 3As shown, the center-side cam portion 60 is formed to protrude in the second direction D2 from the surface 43D on the side of the base wall 43 in the second direction D2. The center-side cam portions 60 are arranged at equal intervals in the circumferential direction S of the first clutch center portion 41. In this embodiment, the first clutch center portion 41 has three center-side cam portions 60, but the number of center-side cam portions 60 is not limited to three.

[0048] like Figure 3 As shown, the center side cam portion 60 is located radially outside the output shaft holding portion 42. The center side cam portion 60 has a center side auxiliary cam surface 60A (also refer to Figure 4 ) and a center-side sliding cam surface 60S. The center-side auxiliary cam surface 60A is configured to generate a force in a direction that causes the pressure member 70 to approach the clutch center 40 in order to increase the pressing force (pressing force) between the input-side rotating plate 20 and the output-side rotating plate 22 when the center-side auxiliary cam surface 60A rotates relative to the pressure member 70. In this embodiment, the position of the pressure member 70 relative to the clutch center 40 does not change when this force is generated, and the pressure member 70 does not need to be physically close to the clutch center 40. It should be noted that the pressure member 70 may also be physically displaced relative to the clutch center 40. The center-side sliding cam surface 60S is configured to reduce the pressing force (pressing force) between the input-side rotating plate 20 and the output-side rotating plate 22 when the center-side auxiliary cam surface 60A rotates relative to the pressure member 70, thereby causing the pressure member 70 to separate from the clutch center 40. In the center-side cam portions 60 adjacent to each other in the circumferential direction S, the center-side auxiliary cam surface 60A of one center-side cam portion 60L and the center-side sliding cam surface 60S of the other center-side cam portion 60M are arranged to face each other in the circumferential direction S.

[0049] like Figure 3 As shown, the first clutch center portion 41 has a plurality of (three in this embodiment) boss portions 62. The boss portion 62 is a component that supports the pressure component 70. The plurality of boss portions 62 are arranged at equal intervals in the circumferential direction S. The boss portion 62 is formed in a cylindrical shape. The boss portion 62 is located radially outward of the output shaft retaining portion 42. The boss portion 62 extends toward the pressure component 70 (i.e., toward the second direction D2). The boss portion 62 is provided on the center side cam portion 60. The boss portion 62 is provided between the center side auxiliary cam surface 60A and the center side sliding cam surface 60S in the circumferential direction S. A space for the bolt 28 (refer to Figure 1 The threaded hole 62H extends along the axial direction of the clutch center 40 (ie, direction D).

[0050] like Figure 3 and Figure 4As shown, the first clutch center 41 has a center-side cam hole 43H extending through a portion of the base wall 43. The center-side cam hole 43H extends through the base wall 43 in the direction D. The center-side cam hole 43H is located between adjacent center-side cam portions 60 in the circumferential direction S. When viewed in the axial direction of the clutch center 40, the center-side auxiliary cam surface 60A overlaps a portion of the center-side cam hole 43H.

[0051] like Figure 3 As shown, the first clutch center portion 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 in the radial direction.

[0052] like Figure 3 As shown, the first clutch center portion 41 has a recess 50 that is recessed toward the first direction D1 from the surface on the second direction D2 side of the first clutch center portion 41 (here, the surface 43D on the second direction D2 side of the base wall 43). The recess 50 is formed into a circular shape when viewed from above, but its shape is not particularly limited. In this embodiment, the first clutch center portion 41 has three recesses 50. The recesses 50 are arranged at equal intervals in the circumferential direction S. The recess 50 is radially arranged between the output shaft retaining portion 42 and the center side cam portion 60. The recess 50 is arranged radially inward of the center side sliding cam surface 60S. As shown Figure 2 As shown, the recess 50 is provided adjacent to the open end 71T of the first pressure member 71, described later. The recess 50 is located on the first direction D1 side of the open end 71T. The recess 50 serves as an oil passage that guides the clutch oil within the first pressure member 71 to the gap 95, described later. The recess 50 is an example of a first oil passage.

[0053] like Figure 5 As shown, the second clutch center 51 includes an annular outer peripheral wall 52, a flange 68 extending radially outward from the outer peripheral wall 52, and a center-side fitting portion 54. The second clutch center 51 holds a plurality of output-side rotating plates 22 arranged alternately with the input-side rotating plates 20 in the direction D.

[0054] like Figure 5As shown, a splined engagement portion 56 is provided on the outer circumferential surface of the outer circumferential wall 52. The splined engagement portion 56 includes: a plurality of center-side engagement teeth 57 extending along the outer circumferential surface of the outer circumferential wall 52 in the axial direction (i.e., direction D) of the second clutch center portion 51; a plurality of spline grooves 58 formed between adjacent center-side engagement teeth 57 and extending along the axial direction (i.e., direction D) of the second clutch center portion 51; and an oil discharge hole 59. The center-side engagement teeth 57 retain the output-side rotating plate 22. The plurality of center-side engagement teeth 57 are arranged along the circumferential direction S. 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 have the same shape. The center-side engagement teeth 57 protrude radially outward from the outer circumferential surface of the outer circumferential wall 52. The oil discharge hole 59 is formed radially through the outer circumferential wall 52. The oil discharge hole 59 is formed between adjacent center-side engagement teeth 57. Specifically, the oil drain hole 59 is formed in the spline groove 58. The oil drain hole 59 is formed in the center-side fitting portion 54. The oil drain hole 59 connects the interior of the second clutch center 51 with the exterior. The oil drain hole 59 drains the clutch oil and other components that have flowed from the output shaft 15 into the clutch center 40 to the exterior of the clutch center 40. The clutch oil drained from the oil drain hole 59 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22 located radially outside the oil drain hole 59.

[0055] The output side rotating plate 22 is held by the spline fitting portion 56 of the second clutch center portion 51 and the pressure member 70. A portion of the output side rotating plate 22 is held by the center side fitting teeth 57 and the spline grooves 58 of the second clutch center portion 51 through spline fitting. The other portion of the output side rotating plate 22 is held by the pressure side fitting teeth 87 (see FIG. 1 ) described later on the pressure member 70. Figure 7 The output-side rotating plate 22 is provided so as to be displaceable along the axial direction of the clutch core 40 (ie, direction D). The output-side rotating plate 22 is provided so as to be rotatable integrally with the clutch core 40 .

[0056] The output-side rotating piece 22 is a component that is pressed against the input-side rotating piece 20. The output-side rotating piece 22 is a flat, annular plate. It is formed by punching a thin sheet of SPCC material into an annular shape. It should be noted that the friction member provided on the input-side rotating piece 20 may be provided on the output-side rotating piece 22 instead of the input-side rotating piece 20, or may be provided separately on both the input-side rotating piece 20 and the output-side rotating piece 22.

[0057] like Figure 5 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 onto the pressure side fitting portion 88 (see FIG. Figure 7The inner diameter of the center-side fitting portion 54 is formed to allow the top end portion 15T of the output shaft 15 to be inserted into the pressure-side fitting portion 88 (see FIG. Figure 1 That is, a gap is formed between the center-side fitting portion 54 and the pressure-side fitting portion 88.

[0058] like Figure 5 and Figure 6 As shown, the second clutch center portion 51 has a plurality of engagement protrusions 55. The engagement protrusions 55 engage the engagement grooves 49 (see FIG. Figure 3 ) engages. The engaging protrusion 55 is formed on the inner circumferential surface of the outer circumferential wall 52. The engaging protrusion 55 protrudes radially inward from the inner circumferential surface of the outer circumferential wall 52. The engaging protrusion 55 is located closer to the first direction D1 than the oil discharge hole 59.

[0059] like Figure 1 As shown, the pressure member 70 is provided to be able to approach or separate from the clutch center 40 and to rotate relatively. 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 arranged concentrically with the clutch center 40 and the clutch housing 30. Figure 7 As shown, the pressure member 70 includes a first pressure member 71 and a second pressure member 81. The first pressure member 71 and the second pressure member 81 are assembled with each other. The second pressure member 81 is located radially outside the first pressure member 71. The second pressure member 81 is externally embedded in the first pressure member 71. The first pressure member 71 and the second pressure member 81 are configured to be able to move relative to each other in the direction D. The first pressure member 71 and the second pressure member 81 are configured to be able to rotate relative to each other in the circumferential direction S within a predetermined angle range. Here, the predetermined angle range refers to the angle from Figure 12A The state (the state in which the pressure side auxiliary cam surface 90A and the center side auxiliary cam surface 60A are in contact with each other) is rotated to Figure 12B The first pressure member 71 is provided so as to be movable relative to the second pressure member 81 in the direction D. Thus, the pressure member 70 includes the first pressure member 71 and the second pressure member 81, so that the first pressure member 71 and the second pressure member 81 can move (rotate) independently of each other.

[0060] like Figure 8 and Figure 9 As shown, the first pressure member 71 is formed into a cylindrical shape. The first pressure member 71 is externally fitted to the output shaft holding portion 42 (see Figure 1The first pressure member 71 accommodates the top end portion 15T of the output shaft 15 (see Figure 1 The first pressure member 71 houses the release bearing 18 (see Figure 1 The first pressure member 71 is subjected to pressure from the pressing member 16B (refer to Figure 1 ) is a portion of the output shaft 15 that receives the pressing force. The first pressure member 71 is configured to be movable in the second direction D2 by clutch operation (for example, operation based on a clutch lever, operation based on a button). The first pressure member 71 is a portion that receives the clutch oil flowing out from the top end portion 15T of the output shaft 15. The first pressure member 71 includes a cylindrical first portion 71A that is externally embedded in the output shaft retaining portion 42, a cylindrical second portion 71B that is continuous with the first portion 71A and has a smaller diameter than the first portion 71A, and a cylindrical third portion 71C that is continuous with the second portion 71B and has a smaller diameter than the second portion 71B. As Figure 2 As shown, the first portion 71A is open in the first direction D1. The open end portion 71T of the first pressure member 71 is included in the first portion 71A. The open end portion 71T contacts the surface 43D2 on the second direction D2 side of the base wall 43. The open end portion 71T is located on the second direction D2 side of the recess 50. By fitting the first portion 71A onto the output shaft retaining portion 42, the pressure member 70 is positioned relative to the clutch center portion 40. The release bearing 18 is arranged on the inner side of the second portion 71B. The second portion 71B retains the release bearing 18. The third portion 71C is open in the second direction D2. It should be noted that the third portion 71C can also be closed without being open in the second direction D. The disc spring 180 is locked to the third portion 71C.

[0061] like Figure 8 and Figure 9 As shown, the first pressure member 71 has a first notch 71H that can guide the clutch oil in the first pressure member 71 to the outside of the first pressure member 71. The first notch 71H is an example of a first oil passage. The first notch 71H can guide the clutch oil in the first pressure member 71 to the gap portion 95 described later and the second notch 81H (see Figure 10 ). The first cutout 71H is formed at the opening end 71T of the first pressure member 71. The first cutout 71H is recessed from the opening end 71T toward the second direction D2. A plurality of first cutouts 71H are provided in the circumferential direction of the opening end 71T (six in this embodiment). The plurality of first cutouts 71H are arranged at equal intervals in the circumferential direction S. Figure 1 As shown, the end portion of the first notch 71H on the second direction D2 side is located closer to the second direction D2 side than the end portion of the output shaft holding portion 42 on the second direction D2 side.

[0062] like Figure 1As shown, the second pressure member 81 is configured to press against the first pressure member 71 and be movable in the second direction D2. The second pressure member 81 is embedded in the second clutch center portion 51. Thus, the radial positioning of the second pressure member 81 is performed. The second pressure member 81 is configured to be able to slide relative to the second clutch center portion 51 in the direction D. The second pressure member 81 and the second clutch center portion 51 are configured to be able to rotate relative to each other in the circumferential direction S. Figure 10 As shown, the second pressure member 81 includes a main body 82 and a flange 98 connected to the outer peripheral edge of the main body 82 on the second direction D2 side and extending radially outward. The main body 82 protrudes in the first direction D1 beyond the flange 98. The flange 98 is located radially outward of the cylindrical portion 80, which will be described later. The second pressure member 81 holds a plurality of output-side rotating pieces 22 arranged alternately with the input-side rotating pieces 20. The flange 98 is configured to press the input-side rotating pieces 20 and the output-side rotating pieces 22.

[0063] like Figure 10 As shown, the main body 82 includes a cylindrical portion 80, a plurality of pressure-side cam portions 90, a pressure-side fitting portion 88, and a spring receiving portion 84 (see Figure 11 ).

[0064] like Figure 10 As shown, the cylindrical portion 80 has a cylindrical partition wall 80A. The cylindrical portion 80 is formed integrally with the pressure side cam portion 90. The pressure side cam portion 90 is located radially outside the partition wall 80A. Figure 7 As shown, the first pressure member 71 is housed in the cylindrical portion 80 . The inner peripheral surface 85 of the partition wall 80A is configured to be slidable in the direction D relative to the outer peripheral surface 75 of the first portion 71A of the first pressure member 71 .

[0065] like Figure 2 As shown, the pressure member 70 includes a gap 95 formed between the outer circumferential surface 75 of the open end 71T of the first pressure member 71, adjacent to the clutch center 40 (more specifically, the first clutch center 41), and the inner circumferential surface 85 of the partition wall 80A of the second pressure member 81, which fits over the outer circumferential surface 75. In other words, a gap is defined between the outer circumferential surface 75 and the inner circumferential surface 85, allowing clutch oil to flow. The clutch oil within the first pressure member 71 is guided into the gap 95 via the recess 50 of the first clutch center 41 and the first notch 71H of the first pressure member 71. The clutch oil is retained in the gap 95. The gap 95 is open in both the first direction D1 and the second direction D2. The open end 71T is located on the first direction D1 side of the gap 95. The disc spring 180 is located on the second direction D2 side of the gap 95. The clutch oil held in the gap portion 95 flows, for example, toward the second direction D2 side and flows from the opening end portion 95H (see FIG. Figure 1) flows out and is supplied to the disc spring 180 via the oil supply path 96 described later.

[0066] like Figure 2 As shown, the pressure member 70 has an oil supply path 96 formed between the first pressure member 71 and the second pressure member 81. The oil supply path 96 is formed between the first wall surface 71M of the first pressure member 71 and the second wall surface 81M of the second pressure member 81. The outer surface of the second part 71B of the first pressure member 71 and the outer surface of the third part 71C constitute a part of the oil supply path 96. The first wall surface 71M and the second wall surface 81M extend in the radial direction of the output shaft 15. The second wall surface 81M is opposite to the first wall surface 71M. The first wall surface 71M is configured to be able to contact the second wall surface 81M. In the state where the first wall surface 71M and the second wall surface 81M are in contact, the first wall surface 71M and the second wall surface 81M sometimes slide in the circumferential direction S. The oil supply path 96 is connected to the opening end 95H of the second direction D2 of the gap portion 95 (refer to Figure 1 ). The oil supply passage 96 extends radially along the output shaft 15. The oil supply passage 96 guides the clutch oil flowing out of the gap 95 along the outer surfaces of the second portion 71B and the third portion 71C of the first pressure member 71 to the disc spring 180 (for example, the sliding portion between the disc spring 180 and the third portion 71C of the first pressure member 71).

[0067] Here, when the driver of the motorcycle operates the clutch lever in the clutch-engaged state, the pressing member 16B pressed by the push rod 16A overcomes the biasing force of the disc spring 180 and presses the first pressure member 71 in the second direction D2. At this time, the first wall surface 71M of the first pressure member 71 contacts the second wall surface 81M of the second pressure member 81, and the first pressure member 71 presses the second pressure member 81 in the second direction D2. As a result, the second pressure member 81 overcomes the biasing force of the clutch spring 25 and displaces in the direction (second direction D2) away from the clutch center 40 (more specifically, the second clutch center 51). As a result, the clutch center 40 enters a clutch-disengaged state (i.e., a clutch-disconnected state) in which the frictional connection between the input-side rotating plate 20 and the output-side rotating plate 22 is eliminated, thereby entering a state in which the rotational drive is attenuated or stopped. In other words, the rotational drive force of the engine is cut off relative to the clutch center 40. Thus, in the clutch-disengaged state, the oil supply path 96 is closed. On the other hand, In the clutch-engaged state, the oil supply passage 96 is open. When the oil supply passage 96 is open, clutch oil is supplied to the contact surface between the first wall surface 71M and the second wall surface 81M. When switching from the clutch-engaged state to the clutch-disengaged state, or vice versa, the first wall surface 71M and the second wall surface 81M slide. Since clutch oil is supplied to the contact area (contact surface) between the first wall surface 71M and the second wall surface 81M via the oil supply passage 96, wear of the first wall surface 71M and the second wall surface 81M is suppressed even during sliding.

[0068] like Figure 10 As shown, the second pressure member 81 has a second notch 81H capable of directing clutch oil to the exterior of the second pressure member 81. For example, the second notch 81H can direct clutch oil directed to the gap 95 to the exterior of the second pressure member 81. The second notch 81H is an example of a second oil passage. The second notch 81H can direct clutch oil within the gap 95 and the first pressure member 71 to the pressure-side assist cam surface 90A and pressure-side sliding cam surface 90S, the center-side assist cam surface 60A and center-side sliding cam surface 60S, and the like, which will be described later. The second notch 81H is formed in the partition wall 80A of the cylindrical portion 80. The second notch 81H is recessed in the second direction D2 from the end 80AT of the partition wall 80A on the first direction D1 side. A plurality of second notches 81H (three in this embodiment) are provided in the circumferential direction S of the second pressure member 81 (more specifically, in the circumferential direction S of the partition wall 80A). The plurality of second notches 81H are evenly spaced in the circumferential direction S. The second cutout 81H is located between the pressure-side cam portions 90 adjacent to each other in the circumferential direction. Figure 7As shown, the second cutout 81H is formed in a portion of the second pressure member 81 located radially outside the output shaft 15 of the open end portion 71T of the first pressure member 71. Figure 1 As shown, the end portion of the second notch 81H on the second direction D2 side is located closer to the second direction D2 side than the end portion of the output shaft holding portion 42 on the second direction D2 side.

[0069] like Figure 1 and Figure 7 As shown, when viewed in the radial direction of the output shaft 15, at least a portion of the first notch 71H overlaps with the second notch 81H. Furthermore, when the first pressure member 71 and the second pressure member 81 rotate relative to each other in the circumferential direction S, the first notch 71H and the second notch 81H overlap when viewed in the radial direction of the output shaft 15. The length of the first notch 71H in the circumferential direction S is longer than the circumferential length of the second notch 81H.

[0070] The pressure side cam portion 90 is formed in a table shape having a cam surface, and the cam surface is formed by the center side cam portion 60 (refer to Figure 3 The inclined surface of the assist & slide (registered trademark) mechanism that generates assist torque or sliding torque by sliding on the surface of the vehicle. Figure 10 As shown, the pressure-side cam portion 90 is formed to protrude in the first direction D1 beyond the flange 98. The pressure-side cam portions 90 are arranged at equal intervals in the circumferential direction S of the second pressure member 81. In this embodiment, the second pressure member 81 has three pressure-side cam portions 90, but the number of pressure-side cam portions 90 is not limited to three.

[0071] like Figure 10 As shown, the pressure side cam portion 90 is located radially outside the cylindrical portion 80. The pressure side cam portion 90 has a pressure side auxiliary cam surface 90A (also see Figure 11 ) and a pressure-side sliding cam surface 90S. The pressure-side auxiliary cam surface 90A is configured to contact the center-side auxiliary cam surface 60A. The pressure-side auxiliary cam surface 90A is configured to generate a force that moves the pressure member 70 toward the clutch center 40, increasing the pressing force (pressing force) between the input-side rotating plate 20 and the output-side rotating plate 22 during relative rotation with respect to the clutch center 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 (pressing force) between the input-side rotating plate 20 and the output-side rotating plate 22 during relative rotation with respect to the clutch center 40, thereby separating the pressure member 70 from the clutch center 40. In adjacent pressure-side cam portions 90 in the circumferential direction S, the pressure-side auxiliary cam surface 90A of one pressure-side cam portion 90L and the pressure-side sliding cam surface 90S of the other pressure-side cam portion 90M are arranged facing each other in the circumferential direction S.

[0072] Here, the functions of the center-side cam portion 60 and the pressure-side cam portion 90 will be described. When the engine speed increases and the rotational driving force input to the input gear 35 and the clutch housing 30 can be transmitted to the output shaft 15 via the clutch center portion 40, as shown in FIG. Figure 12A As shown, a rotational force in the first circumferential direction S1 is applied to the pressure member 70. Consequently, the center-side auxiliary cam surface 60A and the pressure-side auxiliary cam surface 90A generate a force in the first direction D1 on the pressure member 70. This increases the contact force between the input-side rotating piece 20 and the output-side rotating piece 22.

[0073] On the other hand, when the rotation speed of the output shaft 15 exceeds the rotation speed of the input gear 35 and the clutch housing 30 and a reverse torque is generated, as shown in FIG. Figure 12B As shown, a rotational force in the first circumferential direction S1 is applied to the clutch center 40. Consequently, the center-side sliding cam surface 60S and the pressure-side sliding cam surface 90S cause the pressure member 70 to move in the second direction D2, releasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22. This prevents adverse effects on the engine and transmission caused by reverse torque. It should be noted that the application of the rotational force in the first circumferential direction S1 to the clutch center 40 causes the first pressure member 71 and the second pressure member 81 to rotate relative to each other in the circumferential direction S.

[0074] like Figure 10 As shown, the pressure side fitting portion 88 is located radially outward from the pressure side cam portion 90. The pressure side fitting portion 88 is located on the second direction D2 side from the pressure side cam portion 90. The pressure side fitting portion 88 is slidably fitted into the center side fitting portion 54 (see FIG. Figure 5 ).

[0075] like Figure 10 and Figure 11 As shown, the second pressure component 81 has a pressure side cam hole 83H that passes through the main body 82 and a portion of the flange 98. The pressure side cam hole 83H is located radially outward of the cylindrical portion 80. The pressure side cam hole 83H extends from the side of the cylindrical portion 80 to a radially outward position of the pressure side fitting portion 88. The pressure side cam hole 83H is formed between the pressure side auxiliary cam surface 90A and the pressure side sliding cam surface 90S of the adjacent pressure side cam portion 90. When viewed from the axial direction of the second pressure component 81, the pressure side auxiliary cam surface 90A overlaps with a portion of the pressure side cam hole 83H. The boss portion 62 of the first clutch center portion 41 (see Figure 3 The boss portion 62 passes through the pressure-side cam hole 83H. The pressure-side cam hole 83H is an example of a through hole.

[0076] like Figure 10 As shown, the second pressure component 81 has a plurality of pressure side interlocking teeth 87 arranged on the flange 98. The pressure side interlocking teeth 87 hold the output side rotating piece 22. The pressure side interlocking teeth 87 protrude from the flange 98 toward the first direction D1. The pressure side interlocking teeth 87 are located radially outside of the cylindrical portion 80. The pressure side interlocking teeth 87 are located radially outside of the pressure side cam portion 90. The pressure side interlocking teeth 87 are located radially outside of the pressure side interlocking portion 88. The plurality of pressure side interlocking teeth 87 are arranged along the circumferential direction S. The plurality of pressure side interlocking teeth 87 are arranged at equal intervals in the circumferential direction S. It should be noted that in this embodiment, since a portion of the pressure side interlocking teeth 87 is removed, the interval between the portions is enlarged, but the other adjacent pressure side interlocking teeth 87 are arranged at equal intervals.

[0077] like Figure 1 As shown, the spring receiving portion 84 is formed on the pressure side cam portion 90 (see also Figure 11 The spring receiving portion 84 is located radially outward from the partition wall 80A of the cylindrical portion 80. The spring receiving portion 84 is formed to be recessed from the second direction D2 toward the first direction D1 (see also Figure 12A ). The spring housing portion 84 is formed in a circular shape. The spring housing portion 84 houses the clutch spring 25. The spring housing portion is an example of a housing portion.

[0078] like Figure 1 As shown, the clutch spring 25 is housed in the spring housing 84. The end of the clutch spring 25 in the first direction D1 abuts the second pressure member 81. The end of the clutch spring 25 in the second direction D2 abuts the stopper plate 100. The clutch spring 25 urges the pressure member 70 (more specifically, the second pressure member 81) toward the clutch center 40 (i.e., in the first direction D1). The clutch spring 25 is, for example, a coil spring made of spring steel wound into a helical shape. The clutch spring 25 extends in the direction D.

[0079] like Figure 11 As shown, the second pressure member 81 has a plurality of stoppers 99 extending in the second direction D2 (see also FIG. Figure 2 ). The stopper 99 is configured to be in contact with the stopper plate 100. Figure 15As shown, the stopper 99 has a generally triangular shape when viewed from above. It is formed into a generally triangular prism. The stopper 99 includes a first stopper 99A, which is positioned on one side of the clutch spring 25 in the circumferential direction S (here, on the side of the clutch spring 25 in the first circumferential direction S1), and a second stopper 99B, which is positioned on the other side of the clutch spring 25 in the circumferential direction S (here, on the side of the clutch spring 25 in the second circumferential direction S2). In the circumferential direction S, the spring receiving portion 84 is located between the first stopper 99A and the second stopper 99B. The first stopper 99A is positioned on the pressure-side auxiliary cam surface 90A side. The second stopper 99B is positioned on the pressure-side sliding cam surface 90S side. When viewed radially from the output shaft 15, at least a portion of the first stopper 99A overlaps with the clutch spring 25. When viewed radially from the output shaft 15, at least a portion of the second stopper 99B overlaps with the clutch spring 25.

[0080] like Figure 10 As shown, the second pressure member 81 has a through-hole 86 that guides clutch oil directed to the gap 95 to the spring housing 84. The through-hole 86 is an example of a second oil passage. The through-hole 86 connects the gap 95 with the spring housing 84. The through-hole 86 guides clutch oil within the gap 95 and the first pressure member 71 to the clutch spring 25 and other components. The through-hole 86 is formed in the partition wall 80A of the cylindrical portion 80. The through-hole 86 extends from the partition wall 80A of the cylindrical portion 80 to the pressure-side cam portion 90. The through-hole 86 penetrates the partition wall 80A and a portion of the pressure-side cam portion 90. Multiple through-holes 86 (three in this embodiment) are provided circumferentially around the partition wall 80A. These multiple through-holes 86 are evenly spaced in the circumferential direction S. One through-hole 86 is formed in each pressure-side cam portion 90. The through hole 86 is located between the second slits 81H adjacent to each other in the circumferential direction S.

[0081] A predetermined amount of clutch oil is supplied to the clutch device 10. The clutch oil suppresses heat absorption and wear of the friction members. The clutch device 10 of this embodiment is a so-called wet multi-plate friction clutch device. The clutch oil flows into the first pressure member 71 via the oil flow path 15H of the output shaft 15. Figure 2 As shown by the arrow F1, the clutch oil in the first pressure member 71 flows to the gap portion 95 through the first notch 71H. And, a part of the clutch oil retained in the gap portion 95 is supplied to, for example, the disc spring 180 through the oil supply path 96. Figure 1 As shown by the arrow F2, the clutch oil in the first pressure member 71 flows to the outside of the second pressure member 81 through the first notch 71H and the second notch 81H. The clutch oil flowing to the outside of the second pressure member 81 is supplied to, for example, the center side cam portion 60, the pressure side cam portion 90, the input side rotary plate 20, and the output side rotary plate 22. Figure 2 As indicated by arrow F3, the clutch oil in the first pressure member 71 flows into the spring accommodating portion 84 via the first notch 71H, the gap 95, and the through-hole 86. The clutch oil flowing into the spring accommodating portion 84 is supplied to the clutch spring 25 and the disc spring 180. Furthermore, the clutch oil in the first pressure member 71 is guided to the gap 95 and other portions via the recess 50.

[0082] like Figure 1 As shown, the centrifugal clutch mechanism 120 is provided in the clutch housing 30. The centrifugal clutch mechanism 120 is provided at a position closer to the first direction D1 side than the clutch center 40. The centrifugal clutch mechanism 120 is held in the clutch housing 30. The centrifugal clutch mechanism 120 is provided so as to be rotatable integrally with the clutch housing 30. Figure 13 and Figure 14 As shown, the centrifugal clutch mechanism 120 includes a weight member 122, a holding member 124, a pressing member 126, a support member 128, a first spherical member 131, a second spherical member 132, and a biasing member 135 (see FIG. Figure 1 ). When the weight component 122 is located at the radially outer position, the centrifugal clutch mechanism 120 presses the input side rotating plate 20 and the output side rotating plate 22 to form a state in which the rotational driving force of the input shaft can be transmitted to the output shaft 15. When the weight component 122 is located at the radially inner position, the centrifugal clutch mechanism 120 releases the pressing force between the input side rotating plate 20 and the output side rotating plate 22 to form a state in which the rotational driving force of the input shaft can be cut off from being transmitted to the output shaft 15. The centrifugal clutch mechanism 120 is configured to press the auxiliary clutch plate 150 (refer to Figure 1 ).

[0083] The weight member 122 is configured to be movable from a radially inner position to an outer position by the centrifugal force accompanying the rotation of the clutch housing 30. Figure 13 As shown, the weight member 122 is housed in a housing portion 124A (described later) of the holding member 124. The weight member 122 is held at a radially inner position when no centrifugal force is applied. The weight member 122 overcomes the force applying member 135 (see FIG. 1 ) by the centrifugal force applied thereto. Figure 1 ) and moves radially outward due to the force of the radially outer side.

[0084] like Figure 13As shown, the holding member 124 holds the counterweight member 122 so that it can move between a radially inner position and a radially outer position. The holding member 124 is formed in an annular shape. The holding member 124 has a plurality of receiving portions 124A formed throughout the circumference, a groove 124B formed in the receiving portion 124 A, and a pressing surface 124C. The receiving portion 124 A receives the counterweight member 122. The receiving portion 124A is formed in a concave shape that is consistent with the shape and movement range of the counterweight member 122. The outer peripheral wall surface 124 AA of the receiving portion 124 A is configured to accommodate the force applying member 135 (see Figure 1 ) is abutted against one end.

[0085] like Figure 13 and Figure 14 As shown, the crimping component 126 is configured to be able to move in the second direction D2 by the counterweight component 122 from the radially inner position to the radially outer position, thereby crimping the input side rotating piece 20 and the output side rotating piece 22. The crimping component 126 is formed in an annular shape. The crimping component 126 has a plurality of inclined grooves 126A formed throughout the circumference, grooves 126B respectively formed at positions where the inclined grooves 126 A are formed, and a pressing surface 126C. The inclined grooves 126 A are respectively formed at positions corresponding to the counterweight component 122. The inclined grooves 126 A are inclined in a manner that goes from the radially inner side to the radially outer side and goes to the first direction D1. When the clutch housing 30 is stopped, the counterweight component 122 is pressed by the force applying component 135 (refer to Figure 1 ) is maintained radially inward. When the clutch housing 30 rotates and imparts centrifugal force to the weight member 122, the weight member 122 moves along the inclined groove 126A, thereby moving the pressing member 126 in a direction away from the retaining member 124 (i.e., the second direction D2). As a result, the pressing surface 126C of the pressing member 126 presses the flange 68 of the second clutch center portion 51 in the second direction D2 (see Figure 1 ). It should be noted that the retaining member 124 and the pressing member 126 have a plurality of protrusions 127 formed throughout the circumference. Like the input-side rotating plate 20, the retaining member 124 and the pressing member 126 are retained on the inner circumferential surface of the side wall 33 of the clutch housing 30 via the protrusions 127. The retaining member 124 and the pressing member 126 are retained in the clutch housing 30 by spline engagement. The retaining member 124 and the pressing member 126 are configured to be displaceable along the axial direction (i.e., direction D) of the clutch housing 30. The retaining member 124 and the pressing member 126 are configured to rotate integrally with the clutch housing 30.

[0086] like Figure 13 and Figure 14As shown, the support member 128 is attached to the holding member 124. The support member 128 is fixed to the surface of the holding member 124 where the receiving portion 124A is formed. The support member 128 holds the weight member 122 so as to be movable in the radial direction.

[0087] like Figure 13 and Figure 14 As shown, a first spherical component 131 is attached to the weight component 122. The first spherical component 131 is, for example, a steel ball. A portion of the first spherical component 131 protrudes from one opening of the through-hole formed in the weight component 122 and contacts the rolling surface of the pressing component 126. A second spherical component 132 is attached to the weight component 122. The second spherical component 132 is, for example, a steel ball. A portion of the second spherical component 132 protrudes from the other opening of the through-hole formed in the weight component 122 and contacts the rolling surface of the retaining component 124.

[0088] like Figure 1 As shown, the urging member 135 is arranged radially outside the weight member 122. The urging member 135 urges the weight member 122 radially inward. The urging member 135 is, for example, a coil spring.

[0089] In this centrifugal clutch mechanism 120, when no centrifugal force is applied to the weight member 122, it is held radially inward, releasing the pressure between the input-side rotating plate 20 and the output-side rotating plate 22. On the other hand, when centrifugal force is applied to the weight member 122, it moves from its radially inward position to its radially outward position. Consequently, the pressing surface 126C formed on the pressing member 126 presses the input-side rotating plate 20 and the output-side rotating plate 22 via the flange 68 of the second clutch center 51, creating a pressure-contact state. This allows the rotational drive force of the input shaft to be transmitted to the output shaft 15. At this time, the retaining member 124 moves in the first direction D1, and the pressing surface 124C formed on the retaining member 124 presses the auxiliary clutch plate 150.

[0090] like Figure 1 As shown, the auxiliary clutch plate 150 is disposed within the clutch housing 30. The auxiliary clutch plate 150 is fixed to the output shaft 15. The auxiliary clutch plate 150 has an insertion hole 152H formed therein, into which the output shaft 15 is inserted and spline-engaged. The auxiliary clutch plate 150 is positioned closer to the first direction D1 than a portion of the centrifugal clutch mechanism 120. The auxiliary clutch plate 150 is adjacent to the first clutch center portion 41.

[0091] The auxiliary clutch plate 150 is configured so that when the input-side rotating plate 20 and the output-side rotating plate 22 are in pressure contact (i.e., when the weight member 122 of the centrifugal clutch mechanism 120 is located radially outward), the auxiliary clutch plate 150 is pressed by the centrifugal clutch mechanism 120 (here, the pressing surface 124C of the retaining member 124), thereby enabling transmission of the rotational driving force of the input shaft to the output shaft 15. When the pressure between the input-side rotating plate 20 and the output-side rotating plate 22 is released (i.e., when the weight member 122 is located radially inward), the auxiliary clutch plate 150 is released from the pressure of the centrifugal clutch mechanism 120 (here, the pressing surface 124C of the retaining member 124), thereby blocking transmission of the rotational driving force of the input shaft to the output shaft 15.

[0092] like Figure 1 As shown, the disc spring 180 is arranged concentrically with the pressure member 70. The disc spring 180 is arranged between the pressure member 70 and the stop plate 100. The disc spring 180 is locked to the first pressure member 71 of the pressure member 70. More specifically, the disc spring 180 is locked to the third portion 71C of the first pressure member 71. The inner peripheral end portion 180H of the disc spring 180 is locked to the third portion 71C of the first pressure member 71. By locking the disc spring 180 to the first pressure member 71, the disc spring 180 is positioned relative to the first pressure member 71. Figure 15 As shown, the radial outer edge 180S of the disc spring 180 on the output shaft 15 is located radially outward of the clutch spring 25. More specifically, when viewed axially from the output shaft 15, the radial outer edge 180S of the disc spring 180 on the output shaft 15 is located radially outward of the clutch spring 25 on a line LX passing through the axis 15C of the output shaft 15 and the axis 25C of the clutch spring 25. It should be noted that, when viewed axially from the output shaft 15, it is sufficient that the radial outer edge 180S of the disc spring 180 on the output shaft 15 is located radially outward of the clutch spring 25 on at least the line LX. Throughout the entire circumference of the disc spring 180, the radial outer edge 180S of the output shaft 15 is located radially outward of an imaginary circle LY centered on the axis 15C of the output shaft 15 and inscribed within the radial outer edge of the clutch spring 25. It should be noted that the radial outer edge 180S of the output shaft 15 of the disc spring 180 does not necessarily need to be located radially outward of the imaginary circle LY over the entire circumference of the disc spring 180. In other words, a portion of the outer edge 180S may be located radially inward of the imaginary edge LY. For example, the portion of the outer edge 180S of the disc spring 180 that is sandwiched between the adjacent clutch springs 25 in the circumferential direction S (e.g., see FIG. 1 ) may be located radially inward of the imaginary edge LY. Figure 15At least a portion of the disk (denoted by reference symbol Q) is located radially inward of the imaginary circle LY. The disk spring 180 urges the pressure member 70 (more specifically, the first pressure member 71) in the first direction D1. The disk spring 180 is, for example, a diaphragm spring.

[0093] like Figure 15 and Figure 16 As shown, the disc spring 180 includes a main body portion 181 , a plurality of extension portions 182 , a plurality of first openings 187 , and a plurality of second openings 189 .

[0094] like Figure 15 As shown, the main body 181 is formed into a ring shape. Figure 2 As shown, the main body portion 181 is in contact with the stopper plate 100 .

[0095] like Figure 15 As shown, the extension portion 182 includes a first extension portion 183 and a second extension portion 185. The first extension portion 183 extends radially inward from the radial inner edge 180T of the main body portion 181. The first extension portion 183 is located on one side of the boss portion 62 in the circumferential direction S (here, closer to the first circumferential direction S1 than the boss portion 62). The first extension portion 183 is locked to the first pressure member 71. The second extension portion 185 extends radially inward from the radial inner edge 180T of the main body portion 181. The second extension portion 185 is located on the other side of the boss portion 62 in the circumferential direction S (here, closer to the second circumferential direction S2 than the boss portion 62). The second extension portion 185 is locked to the first pressure member 71. The first extension portion 183 and the second extension portion 185 are separated in the circumferential direction S. The distance L1 between the first extension portion 183 and the boss portion 62 in the circumferential direction S, and the distance L2 between the second extension portion 185 and the boss portion 62 in the circumferential direction S, are shorter than the distance L3 between the first extension portion 183 and the clutch spring 25 in the circumferential direction S, and the distance L4 between the second extension portion 185 and the clutch spring 25 in the circumferential direction S. While the distance L1 and the distance L2 are identical, they may be different. Furthermore, the distance L3 is longer than the distance L4.

[0096] like Figure 15 As shown, the first opening portion 187 is formed between the first extension portion 183 and the second extension portion 185 of one extension portion 182 in the circumferential direction S. Figure 16 As shown, the boss portion 62 passes through the first opening portion 187. That is, the boss portion 62 is located in the first opening portion 187. The opening area of the first opening portion 187 is smaller than the opening area of the second opening portion 189.

[0097] like Figure 15 As shown, the second opening 189 is formed between the first extension portion 183 of the extension portion 182 on one side and the second extension portion 185 of the extension portion 182 on the other side in the circumferential direction S. Figure 16As shown, the clutch spring 25 passes through the second opening 189. The stopper 99 passes through the second opening 189. That is, the clutch spring 25 and the stopper 99 are located in the second opening 189.

[0098] like Figure 15 As shown, the distance L6 between the second stopper 99B and the disc spring 180 in the circumferential direction S is longer than the distance L5 between the first stopper 99A and the disc spring 180 in the circumferential direction S. The distance L5 between the first stopper 99A and the disc spring 180 in the circumferential direction S is longer than the distance L1 between the first extension 183 and the boss portion 62 in the circumferential direction S, and the distance L2 between the second extension 185 and the boss portion 62 in the circumferential direction S.

[0099] like Figure 1 As shown, the stopper plate 100 is configured to be in contact with the pressure member 70. The stopper plate 100 is a member that prevents the pressure member 70 from separating from the clutch center 40 by more than a predetermined distance in the second direction D2. The stopper plate 100 is positioned closer to the disc spring 180 in the second direction D2. The stopper plate 100 is secured to the boss 62 of the first clutch center 41 by bolts 28. With the clutch spring 25 positioned in the spring accommodating portion 84 and the disc spring 180 engaged with the first pressure member 71, the bolts 28 are tightened to the boss 62 via the stopper plate 100, thereby securing the pressure member 70 to the clutch center 40. The stopper plate 100 is formed in an annular shape when viewed from above.

[0100] As described above, according to the clutch device 10 of this embodiment, the first notch 71H is formed at the open end portion 71T of the first pressure member 71, which is capable of guiding the clutch oil in the first pressure member 71 to the gap portion 95. Due to this configuration, the clutch oil in the first pressure member 71 can be supplied to the gap portion 95 via the first notch 71H. This can prevent the outer peripheral surface 75 of the first pressure member 71 and the inner peripheral surface 85 of the second pressure member 81 from sliding against each other and causing wear.

[0101] In the clutch device 10 of this embodiment, the first oil passage is formed by the first notch 71H formed in the open end portion 71T of the first pressure member 71. According to the above configuration, the oil in the first pressure member 71 can be easily supplied to the gap 95.

[0102] In the clutch device 10 of this embodiment, a plurality of first notches 71H are provided in the opening end 71T in the circumferential direction S. This allows the clutch oil in the first pressure member 71 to be supplied to a wider area of the gap 95 or to a wider area outside the second pressure member 81.

[0103] In the clutch device 10 of this embodiment, the second pressure member 81 has a second notch 81H that can guide the clutch oil guided to the gap 95 to the outside of the second pressure member 81. According to this embodiment, the clutch oil guided to the gap 95 can be supplied to other components arranged outside the second pressure member 81.

[0104] In the clutch device 10 of this embodiment, the second pressure member 81 includes a cylindrical partition wall 80A including an inner peripheral surface 85, and the second oil passage is formed by a second notch 81H formed in a portion of the partition wall 80A. This configuration facilitates the supply of clutch oil guided to the gap 95 to the exterior of the second pressure member 81.

[0105] In the clutch device 10 of this embodiment, a plurality of second notches 81H are provided in the second pressure member 81 (e.g., the partition wall 80A) in the circumferential direction S. This configuration allows the clutch oil in the first pressure member 71 to be supplied to a wider area outside the second pressure member 81 via the gap 95 .

[0106] In the clutch device 10 of this embodiment, the first oil passage is formed by a first notch 71H formed in the open end portion 71T of the first pressure member 71, and at least a portion of the first notch 71H overlaps with the second notch 81H when viewed in the radial direction of the output shaft 15. This configuration allows the clutch oil in the first pressure member 71 to be smoothly supplied to the outside of the second pressure member 81.

[0107] In the clutch device 10 of this embodiment, the first pressure member 71 and the second pressure member 81 are configured to be rotatable relative to each other in the circumferential direction S. When the first pressure member 71 and the second pressure member 81 rotate relative to each other, the first notch 71H and the second notch 81H overlap when viewed in the radial direction of the output shaft 15. This configuration allows the clutch oil in the first pressure member 71 to be smoothly supplied to the outside of the second pressure member 81.

[0108] In the clutch device 10 of this embodiment, the second oil passage is formed by a through hole 86 formed in a portion of the partition wall 80A, and connects the gap 95 with the spring accommodating portion 84. In this manner, the clutch oil in the first pressure member 71 can be supplied to the clutch spring 25 accommodated in the spring accommodating portion 84.

[0109] In the clutch device 10 of this embodiment, the first oil passage is formed by a recessed portion 50 that is recessed in the first direction D1 from the surface 43D2 on the second direction D2 side of the first clutch center portion 41. The recessed portion 50 is located on the first direction D1 side of the opening end portion 71T. This configuration allows clutch oil within the first pressure member 71 to be supplied to the gap 95 via the recessed portion 50.

[0110] In the clutch device 10 of this embodiment, the first clutch center portion 41 includes an output shaft retaining portion 42 that retains the output shaft 15, and the first pressure member 71 is configured to be externally fitted onto the output shaft retaining portion 42. This configuration facilitates positioning of the pressure member 70 relative to the clutch center portion 40, and allows clutch oil within the first pressure member 71 to be supplied to the outside of the gap 95 and the second pressure member 81.

[0111] In the clutch device 10 of this embodiment, the gap 95 is open in both the first direction D1 and the second direction D2, and the opening end 71T is located on the first direction D1 side of the gap 95. In this manner, the clutch oil introduced into the gap 95 from the opening end 71T side is supplied to the outside from the second direction D2 side of the gap 95.

[0112] In the clutch device 10 of this embodiment, the pressure member 70 includes an oil supply passage 96. This oil supply passage 96 is formed between the first pressure member 71 and the second pressure member 81 and communicates with the open end 95H of the gap 95 in the second direction D2. The oil supply passage 96 supplies the clutch oil flowing out of the gap 95 to the disc spring 180. This configuration allows the clutch oil to be supplied to the sliding portion between the disc spring 180 and the first pressure member 71, thereby suppressing wear of the inner peripheral end 180H of the disc spring 180.

[0113] In the clutch device 10 of this embodiment, the pressure member 70 includes an oil supply passage 96 formed between the first wall surface 71M and the second wall surface 81M and communicating with an open end portion 95H in the second direction D2 of the gap portion 95. Due to this configuration, the clutch oil in the gap portion 95 can be supplied to the first wall surface 71M and the second wall surface 81M, thereby suppressing wear caused by sliding between the first wall surface 71M and the second wall surface 81M.

[0114] While preferred embodiments of the present invention have been described above, the above embodiments are merely examples, and the present invention can be implemented in various other forms.

[0115] In the above embodiment, the first notch 71H serving as the first oil passage is formed in the open end portion 71T of the first pressure member 71 . However, a through hole may be formed in place of the notch, or both the notch and the through hole may be used in combination.

[0116] In the above embodiment, the second notch 81H serving as the second oil passage is formed in the end 80AT of the partition wall 80A of the cylindrical portion 80 on the first direction D1 side. However, a through hole may be formed instead of the notch, or both the notch and the through hole may be used in combination.

[0117] In the above embodiment, the through hole 86 serving as the second oil passage is formed from the partition wall 80A of the tubular portion 80 to the pressure-side cam portion 90 . However, a cutout may be formed instead of the through hole, or both the cutout and the through hole may be used in combination.

[0118] In the above-described embodiment, the stopper 99 includes the first stopper 99A and the second stopper 99B, but it is sufficient to include at least one of them.

[0119] In the above embodiment, the stopper 99 is arranged to pass through the second opening 189 , but may be arranged to pass through the first opening 187 .

[0120] In the above embodiment, the clutch center 40 includes the first clutch center 41 and the second clutch center 51, and the first clutch center 41 and the second clutch center 51 are assembled for use. However, the first clutch center 41 and the second clutch center 51 may be integral.

[0121] In the above embodiment, the clutch core 40 includes the center-side auxiliary cam surface 60A and the center-side sliding cam surface 60S. However, the clutch core 40 does not need to include the center-side auxiliary cam surface 60A and the center-side sliding cam surface 60S. Furthermore, the pressure member 70 includes the pressure-side auxiliary cam surface 90A and the pressure-side sliding cam surface 90S. However, the pressure member 70 does not need to include the pressure-side auxiliary cam surface 90A and the pressure-side sliding cam surface 90S.

[0122] In the above-described embodiment, an engine is used as a power source, but the power source is not limited to an engine, and may be, for example, an electric motor or the like.

[0123] The straddle-type vehicle of this embodiment is a vehicle in which the driver rides astride. Straddle-type vehicles are not limited to two-wheeled motor vehicles such as scooters. Examples of straddle-type vehicles include motor tricycles, ATVs (all-terrain vehicles), and snowmobiles.

[0124] Description of Reference Numerals

[0125] 10 Clutch device

[0126] 15 output shaft

[0127] 25 clutch spring

[0128] 30 clutch housing

[0129] 40 clutch center

[0130] 41 First clutch center

[0131] 42 output shaft holding portion

[0132] 50 recess (first oil passage)

[0133] 62 boss part

[0134] 51 Second clutch center

[0135] 70 pressure parts

[0136] 71 first pressure member

[0137] 71H first incision (first oil passage)

[0138] 71T open end

[0139] 75 outer surface

[0140] 80 cylindrical part

[0141] 80A dividing wall

[0142] 81 second pressure member

[0143] 81H second incision (second oil passage)

[0144] 84 spring receiving portion (receiving portion)

[0145] 85 inner surface

[0146] 86 through hole (second oil passage)

[0147] 95 gap portion.

Claims

1. A clutch device that transmits or cuts off the rotational driving force of an input shaft relative to an output shaft, wherein: have: a clutch center portion housed in a clutch housing that holds a plurality of input-side rotating plates that are rotationally driven by the rotational drive of the input shaft, and that holds a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates and is rotationally driven together with the output shaft; and The pressure member is provided so as to be able to approach or separate from the clutch center portion and to be relatively rotatable, and is capable of pressing the input-side rotating plate and the output-side rotating plate. The pressure component comprises: a first pressure member; a second pressure member, externally embedded in the first pressure member; and A gap is formed in the radial direction of the output shaft between the outer peripheral surface of the opening end portion of the first pressure member adjacent to the clutch center portion and the inner peripheral surface of the second pressure member fitted onto the outer peripheral surface. A first oil passage is formed at the open end of the first pressure member or at a portion of the clutch center portion adjacent to the open end of the first pressure member. The first oil passage can guide clutch oil in the first pressure member to the gap.

2. The clutch device according to claim 1, wherein: The first oil passage is formed by a cutout or a through-hole formed in the open end portion of the first pressure member.

3. The clutch device according to claim 2, wherein: A plurality of first oil passages are provided in a circumferential direction of the opening end portion.

4. The clutch device according to claim 1, wherein: The second pressure member includes a second oil passage capable of guiding the clutch oil guided to the gap to the outside of the second pressure member.

5. The clutch device according to claim 4, wherein: The second pressure member has a partition wall formed into a cylindrical shape including the inner peripheral surface. The second oil passage is formed of a cutout or a through-hole formed in a portion of the partition wall.

6. The clutch device according to claim 5, wherein: A plurality of second oil passages are provided in the circumferential direction of the partition wall.

7. The clutch device according to claim 5 or 6, wherein: The first oil passage is formed by a cutout or a through-hole formed at the open end of the first pressure member. When viewed in the radial direction of the output shaft, at least a portion of the first oil passage overlaps with the second oil passage.

8. The clutch device according to claim 5 or 6, wherein: The first oil passage is formed by a cutout or a through-hole formed at the open end of the first pressure member. The first pressure member and the second pressure member are configured to be rotatable relative to each other in the circumferential direction. When the first pressure member and the second pressure member rotate relative to each other, the first oil passage and the second oil passage overlap with each other when viewed in the radial direction of the output shaft.

9. The clutch device according to claim 4, wherein: A clutch spring is provided, which urges the pressure member toward the clutch center. The second pressure member includes: a partition wall formed into a cylindrical shape including the inner peripheral surface; and The receiving portion is located on the outer side of the partition wall in the radial direction and receives the clutch spring. The second oil passage is formed of a cutout or a through-hole formed in a portion of the partition wall, and connects the gap portion and the housing portion.

10. The clutch device according to claim 1 or 2, wherein: When the direction in which the pressure member approaches the clutch center is defined as a first direction and the direction in which the pressure member moves away from the clutch center is defined as a second direction, the first oil passage is formed by a recessed portion that is recessed toward the first direction from a surface on the second direction side of the clutch center. The recessed portion is located on the first direction side of the opening end portion.

11. The clutch device according to claim 1 or 2, wherein: The clutch center portion includes an output shaft holding portion that holds the output shaft. The first pressure member is configured to be fitted onto the output shaft holding portion.

12. The clutch device according to claim 1 or 2, wherein: When the direction in which the pressure member approaches the clutch center is defined as a first direction and the direction in which the pressure member moves away from the clutch center is defined as a second direction, the gap opens in the first direction and the second direction. The opening end portion is located on the first direction side of the gap portion.

13. The clutch device according to claim 12, wherein: A disc spring is provided to bias the first pressure member in the first direction. The inner peripheral end portion of the disc spring is locked with the first pressure member. The pressure member includes an oil supply passage formed between the first pressure member and the second pressure member, communicating with an open end portion of the gap in the second direction, and supplying clutch oil flowing out of the gap to the disc spring.

14. The clutch device according to claim 12, wherein: The first pressure member has a first wall extending in the radial direction, The second pressure member has a second wall surface extending in the radial direction, facing the first wall surface, and arranged to be able to contact the first wall surface. The pressure member includes an oil supply passage formed between the first wall surface and the second wall surface and communicating with an opening end portion of the gap in the second direction.

15. A clutch device for transmitting or disconnecting the rotational driving force of an input shaft relative to an output shaft, wherein: have: a clutch center portion housed in a clutch housing that holds a plurality of input-side rotating plates that are rotationally driven by the rotational drive of the input shaft, and that holds a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates and is rotationally driven together with the output shaft; and The pressure member is provided so as to be able to approach or separate from the clutch center portion and to be relatively rotatable, and is capable of pressing the input-side rotating plate and the output-side rotating plate. The pressure component comprises: a first pressure member; and A second pressure component is embedded in the first pressure component. The first pressure member and the second pressure member are configured to be rotatable relative to each other in the circumferential direction. A first oil passage is formed at an open end portion of the first pressure member adjacent to the clutch center portion. The first oil passage is capable of guiding the clutch oil in the first pressure member to the outside of the first pressure member. A second oil passage is formed in a portion of the second pressure member located radially outward of the output shaft relative to the open end of the first pressure member. The second oil passage is capable of guiding clutch oil to the outside of the second pressure member. When the first pressure member and the second pressure member rotate relative to each other in the circumferential direction, the first oil passage and the second oil passage overlap with each other when viewed in the radial direction of the output shaft.

16. The clutch device according to claim 15, wherein: A plurality of first oil passages are provided in a circumferential direction of the opening end portion.

17. The clutch device according to claim 15 or 16, wherein: A plurality of second oil passages are provided in the circumferential direction of the second pressure member.

18. The clutch device according to claim 15 or 16, wherein: The clutch center portion includes an output shaft holding portion that holds the output shaft. The first pressure member is configured to be fitted onto the output shaft holding portion.

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