Clutch device and motorcycle

Abstract

The present invention provides a clutch device and a motorcycle. The clutch device comprises: a clutch hub that holds output-side rotating plates arranged alternately with input-side rotating plates; and a pressure plate that is disposed so as to be able to move toward and away from the clutch hub. The pressure plate includes a plurality of pressure-plate-side engaging teeth that hold the output-side rotating plates. The clutch hub includes a plurality of hub-side engaging teeth that hold the output-side rotating plates. In a partially clutched state, portions of the hub-side engaging teeth overlap portions of the pressure-plate-side engaging teeth when viewed radially from the output shaft.

Description

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority based on Japanese Patent Application No. 2022-109218 filed on July 6, 2022 and Japanese Patent Application No. 2022-172870 filed on October 28, 2022, the entire contents of which are incorporated herein by reference. Technical Field

[0003] The present invention relates to a clutch device and a motorcycle. More specifically, it relates to a clutch device that arbitrarily transmits or cuts off the rotational driving force of an input shaft driven by a prime mover such as an engine to an output shaft, and a motorcycle equipped with the clutch device. Background Art

[0004] Traditionally, vehicles such as motorcycles have been equipped with clutch devices. These devices are positioned between the engine and the drive wheels, transferring or disconnecting the engine's rotational drive force from the drive wheels. These clutch devices typically consist of multiple input-side rotating plates, which rotate in response to the engine's rotational drive force, and multiple output-side rotating plates, which are connected to an output shaft that transmits the rotational drive force to the drive wheels. The input-side and output-side rotating plates are alternately stacked, and the rotational drive force is transferred or disconnected by pressing the input-side and output-side rotating plates into and out of contact.

[0005] For example, Japanese Patent No. 6903020 discloses a clutch device comprising: a clutch hub (clutch member) that holds an output-side rotating plate (driven-side clutch plate); and a pressure plate (pressure member) that is disposed so as to be able to move toward and away from the clutch hub. The pressure plate is configured to press against both the input-side rotating plate and the output-side rotating plate. Thus, in the clutch device, the clutch hub and pressure plate are assembled for use.

[0006] Furthermore, in the clutch device disclosed in Japanese Patent No. 6903020, the clutch hub has hub-side engaging teeth (an outer peripheral wall with splines formed thereon) as a portion for retaining the output-side rotating plate, and the pressure plate has pressure plate-side engaging teeth. When the clutch hub and pressure plate are assembled, the hub-side engaging teeth and the pressure plate-side engaging teeth are configured to overlap in the radial direction.

[0007] However, when the pressure plate separates from the clutch hub, a gap may form between the pressure plate-side meshing teeth and the hub-side meshing teeth in the direction of the pressure plate's movement (i.e., the axial direction of the output shaft). In this case, for example, clutch oil flowing inside the clutch hub flows outward through this gap, making it difficult for the clutch oil to flow to the output-side rotating plate held by the pressure plate.

[0008] The present invention has been made in view of the above-mentioned problems, and an object thereof is to provide a clutch device capable of supplying more clutch oil to an output-side rotating plate of pressure plate-side engaging teeth held on a pressure plate, and a motorcycle equipped with the clutch device. Summary of the Invention

[0009] The clutch device according to the present invention transmits or cuts off the rotational driving force of an input shaft to an output shaft, and comprises: a clutch sleeve 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 that are rotationally driven together with the output shaft; and a pressure plate that is arranged to be able to approach or separate from the clutch sleeve and to be relatively rotatable, and that is capable of pressing the input-side rotating plates and the output-side rotating plates, the pressure plate having a plurality of pressure plate-side engaging teeth arranged in a circumferential direction that hold at least one output-side rotating plate, the clutch sleeve comprising: an output shaft holding portion coupled to the output shaft; an outer peripheral wall located radially outward of the output shaft holding portion; and a plurality of sleeve-side engaging teeth that hold the output-side rotating plates, and are formed to protrude radially outward from an outer peripheral surface of the outer peripheral wall and are arranged in a circumferential direction, wherein in a partially clutched state, a portion of the sleeve-side engaging teeth overlaps a portion of the pressure plate-side engaging teeth when viewed in the radial direction of the output shaft.

[0010] According to the clutch device of the present invention, in the partially clutched state, a portion of the center sleeve-side meshing teeth overlaps a portion of the pressure plate-side meshing teeth when viewed radially from the output shaft. Specifically, in the partially clutched state, no gap exists between the pressure plate-side meshing teeth and the center sleeve-side meshing teeth in the direction of movement of the pressure plate. Therefore, for example, clutch oil flowing within the clutch center sleeve does not flow directly to the outside, but instead flows toward the pressure plate. This allows a larger amount of clutch oil to be supplied to the output-side rotating plate held by the pressure plate.

[0011] Another clutch device according to the present invention transmits or cuts off the rotational driving force of an input shaft to an output shaft, and comprises: a clutch sleeve 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 that are rotationally driven together with the output shaft; and a pressure plate that is arranged to be able to approach or separate from the clutch sleeve and to be relatively rotatable, and that is capable of pressing the input-side rotating plates and the output-side rotating plates, the pressure plate having a plurality of pressure plate-side engaging teeth arranged in a circumferential direction that hold at least one output-side rotating plate. The clutch sleeve comprises: an output shaft holding portion coupled to the output shaft; an outer peripheral wall located radially outward of the output shaft holding portion; and a plurality of sleeve-side engaging teeth that hold the output-side rotating plates and are formed to protrude radially outward from an outer peripheral surface of the outer peripheral wall and are arranged in a circumferential direction. When the clutch is cut off, portions of the sleeve-side engaging teeth overlap portions of the pressure plate-side engaging teeth when viewed in the radial direction of the output shaft.

[0012] According to another clutch device according to the present invention, when the clutch is disengaged, a portion of the center sleeve-side engaging teeth overlaps a portion of the pressure plate-side engaging teeth when viewed radially in the output shaft. Specifically, when the clutch is disengaged, no gap exists between the pressure plate-side engaging teeth and the center sleeve-side engaging teeth in the direction of movement of the pressure plate. Therefore, for example, clutch oil flowing within the clutch center sleeve does not flow directly to the outside, but instead flows toward the pressure plate. This allows a larger amount of clutch oil to be supplied to the output-side rotating plate held by the pressure plate.

[0013] Another clutch device involved in the present invention transmits or cuts off the rotational driving force of the input shaft to the output shaft, and comprises: a clutch center sleeve, which is accommodated 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 holds 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; a pressure plate that is arranged to be able to approach or leave the clutch center sleeve and to be able to rotate relatively, and to be able to press the input-side rotating plates and the output-side rotating plates; and a stop plate that is arranged to be able to contact the pressure plate and to inhibit the pressure plate from moving away from the clutch center sleeve. The clutch center sleeve is more than a specified distance away, and the pressure plate has a plurality of pressure plate side engaging teeth arranged in the circumferential direction for holding at least one output side rotating plate, and the clutch center sleeve has: an output shaft holding portion for connecting the output shaft; an outer peripheral wall located radially outward of the output shaft holding portion; and a plurality of center sleeve side engaging teeth for holding the output side rotating plate, and formed to protrude radially outward from the outer peripheral surface of the outer peripheral wall and arranged in the circumferential direction, and when the pressure plate is in contact with the stop plate, a portion of the center sleeve side engaging teeth overlaps with a portion of the pressure plate side engaging teeth when viewed from the radial direction of the output shaft.

[0014] According to another clutch device according to the present invention, when the pressure plate and the stopper plate are in contact, a portion of the center sleeve-side engaging teeth overlaps a portion of the pressure plate-side engaging teeth when viewed radially in the output shaft. Specifically, when the pressure plate and the stopper plate are in contact, no gap exists between the pressure plate-side engaging teeth and the center sleeve-side engaging teeth in the direction of movement of the pressure plate. Therefore, for example, clutch oil flowing within the clutch center sleeve does not flow directly to the outside, but instead flows toward the pressure plate. This allows a larger amount of clutch oil to be supplied to the output-side rotating plate held by the pressure plate.

[0015] According to the present invention, it is possible to provide a clutch device capable of supplying a larger amount of clutch oil to the output-side rotating plate held by the pressure plate-side engaging teeth of the pressure plate.

[0016] The above and other elements, features, steps, characteristics and advantages of the present invention will become more apparent from the following detailed description of preferred embodiments with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a cross-sectional view of the clutch device according to the first embodiment.

[0018] Figure 2 It is a perspective view of the clutch center sleeve according to the first embodiment.

[0019] Figure 3 It is a plan view of the clutch center sleeve according to the first embodiment.

[0020] Figure 4 It is a perspective view of the pressing plate according to the first embodiment.

[0021] Figure 5A It is a plan view of the press plate according to the first embodiment.

[0022] Figure 5B It is along Figure 5A Cross-sectional view of the VB-VB line in FIG.

[0023] Figure 6 It is a perspective view of the pressing plate according to the first embodiment.

[0024] Figure 7 It is a plan view of the press plate according to the first embodiment.

[0025] Figure 8 It is a side view in which a part of the pressure plate side cam part concerning 1st Embodiment is enlarged.

[0026] Figure 9 This is a partially enlarged perspective view of the press plate according to the first embodiment.

[0027] Figure 10 It is a plan view showing a state in which the clutch center sleeve and the pressure plate according to the first embodiment are assembled.

[0028] Figure 11A This is a schematic diagram illustrating the functions of the auxiliary cam surface on the center sleeve side and the auxiliary cam surface on the pressure plate side.

[0029] Figure 11B This is a schematic diagram illustrating the functions of the center sleeve side sliding cam surface and the pressure plate side sliding cam surface.

[0030] Figure 12 It is a cross-sectional view of the clutch center sleeve and the pressure plate according to the first embodiment.

[0031] Figure 13 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in normal operation.

[0032] Figure 14A It is a cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in normal operation.

[0033] Figure 14B It is a cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate when the pressure plate is farthest from the clutch center sleeve.

[0034] Figure 15 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in normal operation according to the second and third embodiments.

[0035] Figure 16 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in the half-clutch state according to the second embodiment.

[0036] Figure 17 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in a state where the clutch according to the second embodiment is disengaged.

[0037] Figure 18 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in a state where the pressure plate is in contact with the stopper plate according to the second embodiment.

[0038] Figure 19 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in the half-clutch state according to the third embodiment.

[0039] Figure 20 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in a state where the clutch according to the third embodiment is disengaged.

[0040] Figure 21 It is a partially enlarged cross-sectional view showing the positional relationship between the clutch center sleeve and the pressure plate in a state where the pressure plate and the stopper plate are in contact with each other according to the third embodiment.

[0041] Figure 22 It is an exploded perspective view of a clutch center sleeve and a pressure plate according to a fourth embodiment.

[0042] Figure 23 It is a perspective view of a pressing plate according to a fourth embodiment. DETAILED DESCRIPTION

[0043] The following describes embodiments of the clutch device according to the present invention with reference to the accompanying drawings. The embodiments described herein are not intended to limit the present invention in any particular manner. Components and parts that perform the same function are designated by the same reference numerals, and any duplicate descriptions are omitted or simplified as appropriate.

[0044] <First embodiment>

[0045] Figure 1 This is a cross-sectional view of a clutch device 10 according to this embodiment. The clutch device 10 is provided on a vehicle such as a motorcycle. The clutch device 10, for example, transmits or disconnects the rotational driving force of the input shaft (crankshaft) of the motorcycle's engine to the output shaft 15. The clutch device 10 transmits or disconnects 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.

[0046] In the following description, the direction in which the pressure plate 70 of the clutch device 10 approaches and moves away from the clutch sleeve 40 is referred to as direction D (an example of a moving direction), the direction in which the pressure plate 70 approaches the clutch sleeve 40 is referred to as a first direction D1, and the direction in which the pressure plate 70 moves away from the clutch sleeve 40 is referred to as a second direction D2. In addition, the circumferential direction of the clutch sleeve 40 and the pressure plate 70 is referred to as a circumferential direction S, and the direction from one pressure plate side cam portion 90 toward the other pressure plate side cam portion 90 in the circumferential direction S is referred to as a first circumferential direction S1 (see Figure 5A ), the direction from the other platen side cam portion 90 toward the one platen side cam portion 90 is defined as the second circumferential direction S2 (refer to Figure 5A In this embodiment, the axial directions of the output shaft 15, the clutch housing 30, the clutch sleeve 40, and the pressure plate 70 are the same as direction D. Furthermore, the pressure plate 70 and the clutch sleeve 40 rotate in the first circumferential direction S1. However, these directions are merely defined for ease of explanation and do not in any way limit the configuration of the clutch device 10 or the present invention.

[0047] like Figure 1 As shown, the clutch device 10 includes an output shaft 15 , an input-side rotating plate 20 , an output-side rotating plate 22 , a clutch housing 30 , a clutch center sleeve 40 , a pressure plate 70 , and a stopper plate 100 .

[0048] like Figure 1 As shown, the output shaft 15 is a hollow shaft. One end of the output shaft 15 rotatably supports the input gear 35 and the clutch housing 30 (described later) via a needle bearing 15A. The output shaft 15 also securely supports the clutch hub 40 via a nut 15B. In other words, the output shaft 15 rotates integrally with the clutch hub 40. The other end of the output shaft 15 is connected to, for example, a motorcycle transmission (not shown).

[0049] like Figure 1As shown, the output shaft 15 includes a push rod 16A and a push member 16B located adjacent to the push rod 16A within its hollow portion 15H. The hollow portion 15H functions as a circulation path for clutch oil. Clutch oil flows within the output shaft 15, i.e., within the hollow portion 15H. The push rod 16A and the push member 16B are slidable within the hollow portion 15H of the output shaft 15. One end of the push rod 16A (the left end in the figure) is connected to the motorcycle's clutch lever (not shown). When the clutch lever is operated, the push rod 16A slides within the hollow portion 15H, pressing the push member 16B in the second direction D2. A portion of the push member 16B protrudes outward from the output shaft 15 (in this case, in the second direction D2) and is connected to the release bearing 18 provided on the pressure plate 70. The push rod 16A and the push member 16B are formed to be thinner than the inner diameter of the hollow portion 15H, ensuring the smooth flow of clutch oil within the hollow portion 15H.

[0050] 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 rotation plates 20.

[0051] 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 by rivets 35B via a torque damper 35A. 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.

[0052] The input side rotating plate 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 spline engagement. The input-side rotating plate 20 is provided so as to be displaceable along the axial direction of the clutch housing 30. The input-side rotating plate 20 is provided so as to be rotatable integrally with the clutch housing 30.

[0053] The input-side rotating plate 20 is a member that presses against the output-side rotating plate 22. The input-side rotating plate 20 is a flat, annular plate. It is formed by punching a thin sheet of SPCC (cold-rolled steel) into an annular shape. Friction materials (not shown) made of multiple paper sheets are affixed to the front and back surfaces of the input-side rotating plate 20. Grooves with a depth of several to several tens of microns are formed between the friction materials to retain clutch oil.

[0054] like Figure 1As shown, the clutch sleeve 40 is housed in the clutch housing 30. The clutch sleeve 40 is concentrically arranged with the clutch housing 30. The clutch sleeve 40 has a cylindrical main body 42 and a flange 68 extending radially outward from the outer periphery of the main body 42. The clutch sleeve 40 holds a plurality of output-side rotating plates 22 that are alternately arranged with the input-side rotating plates 20 in direction D. The clutch sleeve 40 is driven to rotate together with the output shaft 15.

[0055] like Figure 2 As shown, the main body 42 includes: an annular base wall 43, an outer peripheral wall 45 located radially outside the base wall 43 and extending toward the second direction D2, an output shaft retaining portion 50 arranged in the center of the base wall 43, a plurality of center sleeve side cam portions 60 connected to the base wall 43 and the outer peripheral wall 45, and a center sleeve side interlocking portion 58.

[0056] The output shaft retaining portion 50 is cylindrical. An insertion hole 51 is formed in the output shaft retaining portion 50, into which the output shaft 15 is inserted and spline-engaged. The insertion hole 51 extends through the base wall 43. Multiple spline grooves are formed along the axial direction on the inner circumferential surface 50A of the output shaft retaining portion 50, where the insertion hole 51 is formed. The output shaft 15 is coupled to the output shaft retaining portion 50.

[0057] like Figure 2As shown, the outer peripheral wall 45 of the clutch hub 40 is positioned radially outward from the output shaft retaining portion 50. The outer peripheral wall 45 is integrally formed with the output shaft retaining portion 50. A splined engagement portion 46 is provided on the outer peripheral surface of the outer peripheral wall 45. The splined engagement portion 46 includes a plurality of hub-side engagement teeth 47 extending along the outer peripheral surface of the outer peripheral wall 45 in the axial direction of the clutch hub 40; a plurality of spline grooves 48 formed between adjacent hub-side engagement teeth 47 and extending in the axial direction of the clutch hub 40; and an oil drain hole 49. The hub-side engagement teeth 47 retain the output-side rotating plate 22. The plurality of hub-side engagement teeth 47 are arranged in the circumferential direction S. The plurality of hub-side engagement teeth 47 are formed at equal intervals in the circumferential direction S. The plurality of hub-side engagement teeth 47 have the same shape and protrude radially outward from the outer peripheral surface of the outer peripheral wall 45. The outer circumferential surface of the center sleeve-side engaging teeth 47 is formed substantially parallel to the axis of the output shaft 15. An oil drain hole 49 is formed radially through the outer circumferential wall 45. The oil drain hole 49 is formed between adjacent center sleeve-side engaging teeth 47. Specifically, the oil drain hole 49 is formed in the spline groove 48. The oil drain hole 49 is formed lateral to the center sleeve-side cam portion 60. The oil drain hole 49 is formed lateral to the center sleeve-side sliding cam surface 60S of the center sleeve-side cam portion 60. The oil drain hole 49 is formed on the side of the center sleeve-side sliding cam surface 60S in the first circumferential direction S1. The oil drain hole 49 is formed on the side of the boss portion 54 (described later) in the second circumferential direction S2. The oil drain hole 49 connects the interior and exterior of the clutch sleeve 40. The oil drain hole 49 is a hole for discharging clutch oil that has flowed from the output shaft 15 into the clutch sleeve 40 to the exterior of the clutch sleeve 40.

[0058] The output side rotating plate 22 is held by the spline fitting portion 46 of the clutch center sleeve 40 and the pressure plate 70. A portion of the output side rotating plate 22 is held by the center sleeve side fitting teeth 47 and the spline grooves 48 of the clutch center sleeve 40 through spline fitting. The other portion of the output side rotating plate 22 is held by the pressure plate side fitting teeth 77 (see FIG. 1 ) of the pressure plate 70, which will be described later. Figure 4 The output side rotating plate 22 is provided so as to be displaceable along the axial direction of the clutch center sleeve 40. The output side rotating plate 22 is provided so as to be rotatable integrally with the clutch center sleeve 40.

[0059] The output-side rotating plate 22 is a component that is pressed against the input-side rotating plate 20. The output-side rotating plate 22 is a flat plate formed in an annular shape. The output-side rotating plate 22 is formed by punching a thin plate made of SPCC material into an annular shape. Grooves with a depth of several μm to several tens of μm for retaining clutch oil are formed on the surface and back of the output-side rotating plate 22. In order to improve wear resistance, the surface and back of the output-side rotating plate 22 are respectively subjected to surface hardening treatment. In addition, the friction member provided on the input-side rotating plate 20 can be provided on the output-side rotating plate 22 instead of on the input-side rotating plate 20, or can be provided on the input-side rotating plate 20 and the output-side rotating plate 22 separately.

[0060] The center sleeve side cam portion 60 is formed into a table shape having a cam surface composed of an inclined surface that constitutes an Assist & Slipper (registered trademark) mechanism. This Assist & Slipper mechanism generates an assist torque that increases the pressing force (pressing force) between the input side rotating plate 20 and the output side rotating plate 22, or a slip torque that causes the input side rotating plate 20 and the output side rotating plate 22 to separate quickly and shift to a semi-clutch state. The center sleeve side cam portion 60 is formed to protrude from the base wall 43 in the second direction D2. Figure 3 As shown, the hub cam portions 60 are arranged at equal intervals in the circumferential direction S of the clutch hub 40. In this embodiment, the clutch hub 40 has three hub cam portions 60, but the number of hub cam portions 60 is not limited to three.

[0061] like Figure 3 As shown, the hub-side cam portion 60 is located radially outward of the output shaft retaining portion 50. The hub-side cam portion 60 includes a hub-side auxiliary cam surface 60A and a hub-side sliding cam surface 60S. The hub-side auxiliary cam surface 60A is configured to generate a force that moves the pressure plate 70 toward the clutch hub 40 during relative rotation relative to the pressure plate 70, thereby increasing the pressing force (pressing force) between the input-side rotating plate 20 and the output-side rotating plate 22. In this embodiment, the pressure plate 70 does not change its position relative to the clutch hub 40 when this force is generated, and the pressure plate 70 does not need to physically approach the clutch hub 40. Alternatively, the pressure plate 70 may be physically displaced relative to the clutch hub 40. The hub-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 during relative rotation relative to the pressure plate 70, thereby moving the pressure plate 70 away from the clutch hub 40. In the center sleeve side cam portions 60 adjacent to each other in the circumferential direction S, the center sleeve side auxiliary cam surface 60A of one center sleeve side cam portion 60L and the center sleeve side sliding cam surface 60S of the other center sleeve side cam portion 60M are arranged to face each other in the circumferential direction S.

[0062] like Figure 2As shown, the clutch center sleeve 40 has a plurality of (three in this embodiment) bosses 54. The bosses 54 are components that support the pressure plate 70. The plurality of bosses 54 are arranged at equal intervals in the circumferential direction S. The bosses 54 are formed in a cylindrical shape. The bosses 54 are located radially outward of the output shaft retaining portion 50. The bosses 54 extend toward the pressure plate 70 (i.e., toward the second direction D2). The bosses 54 are provided on the base wall 43. A space for the bolts 28 (see FIG. 2 ) is formed on the bosses 54. Figure 1 The threaded hole 54H extends in the axial direction of the clutch center sleeve 40.

[0063] like Figure 2 As shown, the center sleeve side fitting portion 58 is located radially outward from the output shaft holding portion 50. The center sleeve side fitting portion 58 is located radially outward from the center sleeve side cam portion 60. The center sleeve side fitting portion 58 is located on the second direction D2 side from the center sleeve side cam portion 60. The center sleeve side fitting portion 58 is formed on the inner peripheral surface of the outer peripheral wall 45. The center sleeve side fitting portion 58 is configured to be slidably fitted onto the pressure plate side fitting portion 88 (see FIG. 1 ) described later. Figure 4 ). The inner diameter of the center sleeve side fitting portion 58 is formed to have a fitting tolerance relative to the pressure plate side fitting portion 88 that allows the circulation of the clutch oil flowing out from the front end portion 15T of the output shaft 15. That is, a gap is formed between the center sleeve side fitting portion 58 and the pressure plate side fitting portion 88 described later. In the present embodiment, for example, the center sleeve side fitting portion 58 is formed to have an inner diameter that is 0.1 mm larger than the outer diameter of the pressure plate side fitting portion 88. The dimensional tolerance between the inner diameter of the center sleeve side fitting portion 58 and the outer diameter of the pressure plate side fitting portion 88 is appropriately set according to the amount of clutch oil to be circulated, for example, to be greater than 0.1 mm and less than 0.5 mm.

[0064] like Figure 2 and Figure 3 As shown, the clutch hub 40 has a hub-side cam hole 43H extending through a portion of the base wall 43. The hub-side cam hole 43H extends from the side of the output shaft retaining portion 50 to the outer peripheral wall 45. The hub-side cam hole 43H is formed between the hub-side auxiliary cam surface 60A of the hub-side cam portion 60 and the boss portion 54. When viewed in the axial direction of the clutch hub 40, the hub-side auxiliary cam surface 60A overlaps with a portion of the hub-side cam hole 43H.

[0065] like Figure 1As shown, the pressure plate 70 is provided so as to be able to approach or leave the clutch center sleeve 40 and to rotate relatively. The pressure plate 70 is configured to be able to press the input side rotating plate 20 and the output side rotating plate 22. The pressure plate 70 is arranged concentrically with the clutch center sleeve 40 and the clutch housing 30. The pressure plate 70 has a main body 72 and a flange 98 connected to the outer peripheral edge of the main body 72 on the second direction D2 side and extending radially outward. The main body 72 protrudes in the first direction D1 more than the flange 98. The flange 98 is located at the outer diameter end of the pressure plate 70. The flange 98 is located at a position larger than the cylindrical portion 80 (refer to Figure 4 The pressure plate 70 holds the plurality of output-side rotating plates 22 arranged alternately with the input-side rotating plates 20. The flange 98 is configured to press the input-side rotating plates 20 and the output-side rotating plates 22.

[0066] like Figure 4 As shown, the main body 72 includes a cylindrical portion 80, a plurality of pressure plate side cam portions 90, a pressure plate side fitting portion 88 and a spring receiving portion 84 (see also Figure 6 ).

[0067] The cylindrical portion 80 is formed in a cylindrical shape. The cylindrical portion 80 is formed integrally with the pressure plate side cam portion 90. The cylindrical portion 80 accommodates the front end portion 15T of the output shaft 15 (see Figure 1 The release bearing 18 is housed in the cylindrical portion 80 (see Figure 1 The cylindrical portion 80 is a portion that receives the pressing force from the thrust member 16B. The cylindrical portion 80 is a portion that receives the clutch oil flowing out from the front end portion 15T of the output shaft 15.

[0068] The pressure plate side cam portion 90 is formed into a table shape having a cam surface composed of an inclined surface constituting an assist and slide (registered trademark) mechanism. The assist and slide mechanism slides on the center sleeve side cam portion 60 to generate an assist torque or a slide torque. The pressure plate side cam portion 90 is formed to protrude in the first direction D1 from the flange 98. Figure 5A As shown, the pressure plate side cam portions 90 are arranged at equal intervals in the circumferential direction S of the pressure plate 70. In the present embodiment, the pressure plate 70 has three pressure plate side cam portions 90, but the number of pressure plate side cam portions 90 is not limited to three.

[0069] like Figure 5A As shown, the pressure plate side cam portion 90 is located radially outside the cylindrical portion 80. The pressure plate side cam portion 90 has a pressure plate side auxiliary cam surface 90A (also refer to Figure 7 and Figure 9) and the pressure plate-side sliding cam surface 90S. The pressure plate-side auxiliary cam surface 90A is configured to be in contact with the center sleeve-side auxiliary cam surface 60A. The pressure plate-side auxiliary cam surface 90A is configured to generate a force in a direction that causes the pressure plate 70 to approach the clutch center sleeve 40 in order to increase 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 sleeve 40. The pressure plate-side sliding cam surface 90S is configured to be in contact with the center sleeve-side sliding cam surface 60S. The pressure plate-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 sleeve 40, thereby causing the pressure plate 70 to separate from the clutch center sleeve 40. Of the platen-side cam portions 90 adjacent to each other in the circumferential direction S, the platen-side auxiliary cam surface 90A of one platen-side cam portion 90L and the platen-side sliding cam surface 90S of the other platen-side cam portion 90M are arranged to face each other in the circumferential direction S.

[0070] like Figure 8 As shown, a chamfered portion 90AP is formed at the end of the pressure plate-side auxiliary cam surface 90A of the pressure plate-side cam portion 90 in the circumferential direction S. The angle of the chamfered portion 90AP (the angle in the first direction D1 and in the first circumferential direction S1) is a right angle. More specifically, the chamfered portion 90AP is formed at the end 90AB of the pressure plate-side auxiliary cam surface 90A in the first circumferential direction S1.

[0071] Here, the functions of the center sleeve side cam portion 60 and the pressure plate 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 sleeve 40, as shown in FIG. Figure 11A As shown, a rotational force in the first circumferential direction S1 is applied to the pressure plate 70. Consequently, the center sleeve-side auxiliary cam surface 60A and the pressure plate-side auxiliary cam surface 90A generate a force in the first direction D1 on the pressure plate 70. This causes the pressure plate 70 to move closer to the clutch center sleeve 40 (in the first direction D1), increasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22.

[0072] 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 11B As shown, a rotational force in the first circumferential direction S1 is applied to the clutch center sleeve 40. Consequently, the center sleeve-side sliding cam surface 60S and the pressure plate-side sliding cam surface 90S act to move the pressure plate 70 in the second direction D2, releasing the contact force between the input-side rotating plate 20 and the output-side rotating plate 22. This prevents adverse effects on the engine or transmission caused by reverse torque.

[0073] like Figure 4As shown, the pressure plate side fitting portion 88 is located radially outward from the pressure plate side cam portion 90. The pressure plate side fitting portion 88 is located on the second direction D2 side from the pressure plate side cam portion 90. The pressure plate side fitting portion 88 is configured to be slidably fitted into the center sleeve side fitting portion 58 (see FIG. Figure 2 ).

[0074] like Figure 4 and Figure 5A As shown, the pressure plate 70 has a pressure plate side cam hole 73H that passes through the main body 72 and a portion of the flange 98. The pressure plate side cam hole 73H is located radially outward of the cylindrical portion 80. The pressure plate side cam hole 73H extends from the side of the cylindrical portion 80 to the radially outward of the pressure plate side fitting portion 88. The pressure plate side cam hole 73H is formed between the pressure plate side auxiliary cam surface 90A and the pressure plate side sliding cam surface 90S of the adjacent pressure plate side cam portion 90. Figure 5A and Figure 7 As shown, when viewed from the axial direction of the pressure plate 70 , the pressure plate side auxiliary cam surface 90A overlaps with a portion of the pressure plate side cam hole 73H.

[0075] like Figure 4 As shown, the pressure plate 70 includes a plurality of pressure plate side engaging teeth 77 disposed on the first direction surface 98A of the flange 98. The pressure plate side engaging teeth 77 hold at least one output side rotating plate 22. The input side rotating plate 20 and the output side rotating plate 22 are provided so as to be able to move along the outer peripheral surface 77A of the pressure plate side engaging teeth 77 (see also FIG. Figure 13 ) moves in the direction D. The pressure plate side engaging teeth 77 protrude from the first direction surface 98A of the flange 98 toward the first direction D1. The pressure plate side engaging teeth 77 are located radially outward of the cylindrical portion 80. The pressure plate side engaging teeth 77 are located radially outward of the pressure plate side cam portion 90. The pressure plate side engaging teeth 77 are located radially outward of the pressure plate side engaging portion 88. A plurality of pressure plate side engaging teeth 77 are arranged in the circumferential direction S. A plurality of pressure plate side engaging teeth 77 are arranged at equal intervals in the circumferential direction S. As Figure 13As shown, a radially inwardly recessed recess 77H is formed at the end portion of the outer circumferential surface 77A of the pressure plate-side interlocking tooth 77 in the second direction D2. The recess 77H is formed along the entire circumference of the end portion of the outer circumferential surface 77A of the pressure plate-side interlocking tooth 77 in the second direction D2. The length RA of the recess 77H in the direction D is shorter than the length RB of one input-side rotating plate 20 in the direction D. In addition, the inner circumferential surface 77B of the pressure plate-side interlocking tooth 77 is inclined radially outward as it advances in the first direction D1. The inner circumferential surface 77B of the pressure plate-side interlocking tooth 77 is inclined relative to the output shaft 15, for example, by approximately 2°, so that it is positioned radially outward as it advances in the first direction D1. The inclination angle of the inner circumferential surface 77B is greater than the inclination angle of other portions, such as the outer circumferential surface 77A of the pressure plate-side interlocking tooth 77. The outer circumferential surface 77A of the pressure plate-side interlocking tooth 77 is inclined radially outward as it advances in the second direction D2. The outer peripheral surface 77A of the pressure plate side engaging tooth 77 is inclined, for example, by about 1° with respect to the output shaft 15 so as to be located radially outward as it advances in the second direction D2. Figure 5B As shown, when viewed from the radial direction of the output shaft 15, the pair of side surfaces 77F of the pressure plate-side engaging teeth 77 in the circumferential direction S are inclined so as to approach each other as the pressure plate-side engaging teeth 77 travel in the first direction D1. The angle α formed between the side surfaces 77F and the straight line 15L parallel to the axis of the output shaft 15 is, for example, greater than 0° and less than 5° (e.g., greater than 0° and less than 1°). Furthermore, in this embodiment, since some of the pressure plate-side engaging teeth 77 are removed, the spacing between these portions is increased, but the remaining adjacent pressure plate-side engaging teeth 77 are arranged at equal intervals.

[0076] like Figure 14A As shown, the length P1 of the direction D of the pressure plate side engaging tooth 77 is longer than the total distance (P2+P3) of the maximum moving distance P2 of the pressure plate 70 in the direction D and the rotating plate distance P3, and the rotating plate distance P3 is the normal distance from the end 22AT of the second direction D2 of the output side rotating plate 22 located closest to the first direction D1 side in the output side rotating plate 22 held by the pressure plate side engaging tooth 77, that is, the outermost output side rotating plate 22A on the pressure plate side, to the end 77Q of the second direction D2 of the pressure plate side engaging tooth 77 (the boundary portion with the flange 98). That is, P1>(P2+P3) holds. In addition, the so-called normal time means when the pressure plate 70 is closest to the clutch center sleeve 40. Here, the so-called normal time means the state in which the clutch is connected (hereinafter also referred to as the clutch connection state). Therefore, as Figure 14BAs shown, when the pressure plate 70 moves the maximum moving distance P2 from the normal state to the second direction D2, the outermost output side rotating plate 22A on the pressure plate side overlaps with a part of the pressure plate side interlocking teeth 77, and the outermost output side rotating plate 22A on the pressure plate side is retained on the pressure plate side interlocking teeth 77. That is, the pressure plate side interlocking teeth 77 always retain the outermost output side rotating plate 22A on the pressure plate side, and have a length P1 that the outermost output side rotating plate 22A on the pressure plate side will not fall off. In addition, the rotating plate distance P3 can also be the normal distance from the end 22DT of the outermost output side rotating plate 22A on the pressure plate side in the first direction D1 to the end 77Q (the boundary portion with the flange 98) of the pressure plate side interlocking teeth 77 in the second direction D2. In addition, when the pressure plate 70 moves the maximum moving distance P2 from the normal state to the second direction D2, the pressure plate 70 and the stop plate 100 (refer to Figure 1 ) contact. In addition, if Figure 14BAs shown, when the pressure plate 70 is furthest from the clutch hub 40, the input-side rotating plate 20, located closer to the first direction D1 than the outermost pressure plate-side output-side rotating plate 22A, as viewed radially from the output shaft 15, does not overlap with the end 77T of the pressure plate-side engaging teeth 77 in the first direction D1. That is, when the pressure plate 70 is furthest from the clutch hub 40, the outermost pressure plate-side output-side rotating plate 22A is located closest to the pressure plate-side engaging teeth 77 in the first direction D1. Therefore, when the pressure plate 70 is assembled to the clutch hub 40 while the output-side rotating plate 22 is held by the pressure plate-side engaging teeth 77, the output-side rotating plate 22 is held by the end of the pressure plate-side engaging teeth 77 (i.e., the end 77T in the first direction D1), preventing it from falling from the pressure plate-side engaging teeth 77. This facilitates assembly of the pressure plate 70 to the clutch hub 40. Furthermore, when the pressure plate 70 is furthest from the clutch hub 40 (e.g., when the pressure plate 70 contacts the stopper plate 100, hereinafter referred to as "overtravel"), the input-side rotating plate 20, which is located farther in the first direction D1 than the pressure plate-side outermost output-side rotating plate 22A as viewed radially from the output shaft 15, does not overlap with the pressure plate-side engaging teeth 77 (i.e., the pressure plate-side engaging teeth 77 are shortened to prevent overlap). Consequently, when the clutch is engaged, the end portions 77T of the pressure plate-side engaging teeth 77 in the first direction D1 are prevented from colliding with the input-side rotating plate 20 held by the clutch hub 40. Furthermore, since the pressure plate-side engaging teeth 77 can be made compact (i.e., shortened), and the pressure plate-side outermost output-side rotating plate 22A is always held by the pressure plate-side engaging teeth 77 regardless of the position of the pressure plate 70, the pressure plate-side outermost output-side rotating plate 22A can be prevented from falling off the pressure plate-side engaging teeth 77. On the other hand, if it is formed so that when overtravel occurs, as viewed radially from the output shaft 15, the input side rotating plate 20 located closer to the first direction D1 side than the outermost output side rotating plate 22A on the pressure plate side overlaps with the pressure plate side engaging teeth 77 (that is, the pressure plate side engaging teeth 77 are lengthened for the purpose of overlapping), then when the clutch is connected, the end 77T of the pressure plate side engaging teeth 77 in the first direction D1 may collide with the input side rotating plate 20 held on the clutch center sleeve 40.

[0077] like Figure 12 As shown, the pressure plate side interlocking teeth 77 are located radially outward from the center sleeve side interlocking teeth 47. A gap is formed between the pressure plate side interlocking teeth 77 and the center sleeve side interlocking teeth 47 in the radial direction. Figure 13As shown, the end 77T of the pressure plate-side interlocking tooth 77 in the first direction D1 is located closer in the first direction D1 than the end 47T of the center sleeve-side interlocking tooth 47 in the second direction D2. The radial distance LX between the pressure plate-side interlocking tooth 77 and the center sleeve-side interlocking tooth 47 is longer than the radial distance LY between the pressure plate-side interlocking portion 88 and the center sleeve-side interlocking portion 58. As described above, since the inner circumferential surface 77B of the pressure plate-side interlocking tooth 77 tilts radially outward as it advances in the first direction D1, and the outer circumferential surface of the center sleeve-side interlocking tooth 47 is formed substantially parallel to the axis of the output shaft 15, the distance LX increases as it advances in the first direction D1. As a result, when the pressure plate 70 and the clutch hub 40 rotate, clutch oil retained in the space between the pressure plate-side engaging teeth 77 and the hub-side engaging teeth 47 is easily dispersed toward the output-side rotating plate 22 and the input-side rotating plate 20 through the wide opening formed between the end 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the hub-side engaging teeth 47, thereby improving the lubricity of the output-side rotating plate 22 and the input-side rotating plate 20. Furthermore, the distance LX is the shortest distance in the radial direction between the pressure plate-side engaging teeth 77 and the hub-side engaging teeth 47. Furthermore, under normal conditions, a gap CX is formed between the end 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the hub-side outermost output-side rotating plate 22B, which is the output-side rotating plate 22 located closest to the second direction D2 among the output-side rotating plates 22 retained by the clutch hub 40. That is, the pressure plate side engaging teeth 77 do not come into contact with the center sleeve side outermost output side rotating plate 22B.

[0078] like Figure 6 and Figure 7 As shown, the spring receiving portion 84 is formed on the pressure plate side cam portion 90. The spring receiving portion 84 is formed to be recessed from the second direction D2 to the first direction D1. The spring receiving portion 84 is formed in an elliptical shape. The spring receiving portion 84 receives the pressure spring 25 (see Figure 1 The spring receiving portion 84 is formed with a boss portion 54 (see Figure 2 ) is inserted into the insertion hole 84H. That is, the insertion hole 84H is formed through the pressure plate side cam portion 90. The insertion hole 84H is formed in an elliptical shape.

[0079] like Figure 1 As shown, the pressure spring 25 is housed in the spring housing 84. The pressure spring 25 is retained by the boss 54 inserted into the insertion hole 84H of the spring housing 84. The pressure spring 25 urges the pressure plate 70 toward the clutch center sleeve 40 (i.e., in the first direction D1). The pressure spring 25 is, for example, a coil spring made by winding spring steel into a helical shape.

[0080] Figure 10 1 is a top view showing a state in which the clutch center sleeve 40 and the pressure plate 70 are combined. Figure 10 In the state shown, the pressure plate side auxiliary cam surface 90A does not contact the center sleeve side auxiliary cam surface 60A, and the pressure plate side sliding cam surface 90S does not contact the center sleeve side sliding cam surface 60S. At this time, the pressure plate 70 is closest to the clutch center sleeve 40. This state is referred to as the normal state of the clutch device 10. Figure 10 As shown, the distance L5 in the circumferential direction S between the boss portion 54 and the end portion 84HA on the auxiliary cam surface 90A side of the pressure plate side of the insertion hole 84H (i.e., the first circumferential direction S1 side) is shorter than the distance L6 in the circumferential direction S between the boss portion 54 and the end portion 84HB on the sliding cam surface 90S side of the pressure plate side of the insertion hole 84H (i.e., the second circumferential direction S2 side).

[0081] like Figure 1 As shown, the stopper plate 100 is provided so as to be contactable with the pressure plate 70. The stopper plate 100 prevents the pressure plate 70 from moving beyond a predetermined distance in the second direction D2 from the clutch hub 40. The stopper plate 100 is secured to the boss portion 54 of the clutch hub 40 by bolts 28. With the boss portion 54 of the clutch hub 40 and the pressure spring 25 positioned in the spring receiving portion 84, the pressure plate 70 is secured to the boss portion 54 via the stopper plate 100 by tightening the bolts 28. The stopper plate 100 is formed into a generally triangular shape in plan view.

[0082] Here, when the pressure plate 70 contacts the stopper plate 100, the pressure plate-side sliding cam surface 90S and the center sleeve-side sliding cam surface 60S contact each other over an area ranging from 50% to 90% of the area of ​​the pressure plate-side sliding cam surface 90S and from 50% to 90% of the area of ​​the center sleeve-side sliding cam surface 60S, respectively. Furthermore, when the pressure plate 70 contacts the stopper plate 100, the pressure spring 25 clears the side wall of the spring receiving portion 84. This prevents the pressure spring 25 from being sandwiched between the boss portion 54 and the spring receiving portion 84, thus preventing excessive stress from being applied to the boss portion 54.

[0083] Here, the length L1 in the circumferential direction S from the end 90AA in the first direction D1 of the pressure plate side auxiliary cam surface 90A of one pressure plate side cam portion 90L located on the first circumferential direction S1 side to the end 90SA in the first direction D1 of the pressure plate side sliding cam surface 90S of the other pressure plate side cam portion 90M located on the second circumferential direction S2 side (refer to Figure 5A ) is greater than the circumferential length L2 of one center sleeve side cam portion 60 from the end 60AA of the center sleeve side auxiliary cam surface 60A in the second direction D2 to the end 60SA of the center sleeve side sliding cam surface 60S in the second direction D2 (see Figure 3 )long.

[0084] Furthermore, when viewed from the axial direction of the output shaft 15, an angle θ1 is formed by the center 80C of the cylindrical portion 80, an end portion 90AB in the first circumferential direction S1 of a pressure plate side auxiliary cam surface 90A located on the first circumferential direction S1 side of one pressure plate side cam portion 90L of the pressure plate side cam portions 90 adjacent to each other in the circumferential direction S, and an end portion 90SB in the first circumferential direction S1 of a pressure plate side sliding cam surface 90S located on the second circumferential direction S2 side of the other pressure plate side cam portion 90M (refer to FIG. Figure 5A ) is greater than the angle θ2 (refer to the angle θ2 of the center 50C of the output shaft holding portion 50, the end 60AB of the center sleeve side auxiliary cam surface 60A of one center sleeve side cam portion 60 in the second circumferential direction S2, and the end 60SB of the center sleeve side sliding cam surface 60S in the second circumferential direction S2) formed by Figure 3 )big.

[0085] In addition, the length L3 in the circumferential direction S from the end 60AA of the center sleeve side auxiliary cam surface 60A in the second direction D2 to the boss portion 54 (see Figure 3 ) is greater than the length L4 in the circumferential direction S from the end 90AA in the first direction D1 of the pressure plate side auxiliary cam surface 90A to the insertion hole 84H (see Figure 5A )long.

[0086] Furthermore, when viewed from the axial direction of the output shaft 15, an angle θ3 is formed by the center 50C of the output shaft holding portion 50, the end 60AB of the center sleeve side auxiliary cam surface 60A in the second circumferential direction S2 of the center sleeve side cam portion 60, and the center 54C of the boss portion 54 (see FIG. Figure 3 ) than the angle θ4 formed by the center 80C of the cylindrical portion 80, the end 90AB of the first circumferential direction S1 of the pressure plate side auxiliary cam surface 90A, and the center 84HC of the insertion hole 84H (refer to Figure 5A )big.

[0087] The clutch device 10 is filled with a predetermined amount of clutch oil. The clutch oil flows through the hollow portion 15H of the output shaft 15 into the clutch hub 40 and pressure plate 70. The oil is then supplied to the input-side rotating plate 20 and the output-side rotating plate 22 via the gap between the hub-side fitting 58 and the pressure plate-side fitting 88 and the oil drain hole 49. The clutch oil suppresses heat absorption and wear of the friction members. The clutch device 10 of this embodiment is a so-called wet-type multi-plate friction clutch device.

[0088] Next, the operation of the clutch device 10 of this embodiment will be described. As described above, the clutch device 10 is disposed between the motorcycle's engine and transmission, and transmits and disconnects the engine's rotational drive force to and from the transmission through clutch operation by the driver (e.g., by the driver operating a clutch lever or button).

[0089] In the clutch device 10, when the motorcycle driver does not operate the clutch (for example, when the driver does not operate the clutch lever), the clutch release mechanism (not shown) does not press the push rod 16A. Therefore, the pressure plate 70 presses the input-side rotating plate 20 due to the biasing force (elastic force) of the pressure spring 25. As a result, the clutch hub 40 enters a clutch-connected state (i.e., a clutch-engaged state) in which the input-side rotating plate 20 and the output-side rotating plate 22 abut against each other and are frictionally coupled, thereby causing rotational drive. Specifically, the engine's rotational drive force is transmitted to the clutch hub 40, causing the output shaft 15 to rotate.

[0090] In the clutch connection state, the clutch oil flowing in the hollow portion H of the output shaft 15 and flowing out from the front end portion 15T of the output shaft 15 falls or splashes and adheres to the inside of the cylindrical portion 80 (see Figure 1 (Indicated by arrow F). The clutch oil adhering to the cylindrical portion 80 is introduced into the clutch hub 40. As a result, the clutch oil flows out of the clutch hub 40 through the oil drain hole 49. Furthermore, the clutch oil flows out of the clutch hub 40 through the gap between the hub-side fitting 58 and the pressure plate-side fitting 88. The clutch oil flowing out of the clutch hub 40 is then supplied to the input-side rotating plate 20 and the output-side rotating plate 22.

[0091] On the other hand, in the clutch device 10, when the motorcycle driver operates the clutch in the clutch-engaged state (when the driver operates the clutch lever), the clutch release mechanism (not shown) presses the push rod 16A, causing the pressure plate 70 to displace in the direction away from the clutch hub 40 (the second direction D2) against the biasing force of the pressure spring 25. This disengages the clutch hub 40 from the clutch-engaged state (i.e., the clutch-disengaged state), releasing the frictional connection between the input-side rotating plate 20 and the output-side rotating plate 22. Consequently, the clutch hub 40 enters a clutch-disengaged state (i.e., the clutch-disengaged state), resulting in a state in which the rotational drive is attenuated or stopped. In other words, the engine's rotational drive force is disconnected from the clutch hub 40. The pressure plate 70 is configured to move in the second direction D2 when the driver's clutch operation causes it to transition from the clutch-engaged state (the clutch-engaged state) to the clutch-disengaged state (the clutch-disengaged state) via the partially engaged state.

[0092] In the clutch-disengaged state, the clutch oil flowing within the hollow portion H of the output shaft 15 and out of the front end portion 15T of the output shaft 15 is introduced into the clutch hub 40, similarly to the clutch-engaged state. At this time, the pressure plate 70 is spaced apart from the clutch hub 40, reducing the amount of engagement between the hub-side engagement portion 58 and the pressure plate-side engagement portion 88. As a result, the clutch oil within the cylindrical portion 80 flows more actively out of the clutch hub 40 and into various locations within the clutch device 10. In particular, the clutch oil can be actively introduced between the separated input-side rotating plate 20 and output-side rotating plate 22.

[0093] Furthermore, when the driver releases the clutch operating lever in the clutch-disengaged state, the clutch release mechanism (not shown) releases the pressure on the pressure plate 70 via the pushing member 16B, so that the pressure plate 70 is displaced in the direction (first direction D1) approaching the clutch center sleeve 40 by the force of the compression spring 25.

[0094] Figure 15 FIG is a partially enlarged cross-sectional view of the clutch device 110 according to the second embodiment and the clutch device 210 according to the third embodiment in a normal state (a state in which the clutch is connected). Figure 15 As shown, in clutch devices 110 and 210, when the clutch is connected, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 when viewed radially of the output shaft 15 (i.e., when viewed in a direction orthogonal to direction D). Here, in direction D, the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 overlap by a length G1. Furthermore, when the clutch is connected, a radial distance LX between the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 is shorter than a distance LZ between an end portion 47T of the center sleeve-side engaging teeth 47 on the second direction D2 side and the pressure plate 70 (here, the flange 98) in direction D. Alternatively, distance LX may be longer than distance LZ. Furthermore, when the clutch device 110 and the clutch device 210 undergo a temperature change in a usable temperature range (e.g., -10°C to 400°C) from a low-temperature side temperature range (e.g., -10°C to 40°C) to a high-temperature side temperature range (e.g., 80°C to 400°C), a portion of the center sleeve side interlocking teeth 47 overlaps a portion of the pressure plate side interlocking teeth 77 when viewed in the radial direction of the output shaft 15 in the entire usable temperature range (see FIG. 1 ). Figures 15 to 21 The low-temperature temperature range is, for example, the outside air temperature before the engine is started. The high-temperature temperature range is, for example, the temperature of the clutch devices 110 and 210 during operation after the engine is warmed up.

[0095] <Second embodiment>

[0096] like Figures 16 to 18As shown, in the clutch device 110 involved in the second embodiment, when the pressure plate 70 moves in the direction away from the clutch center sleeve 40 (i.e., the second direction D2), the input side rotating plate 20 and the output side rotating plate 22 as a whole remain on the side of the clutch center sleeve 40, and a gap (gap in direction D) is formed between the pressure plate 70 (more specifically, the flange 98) and the input side rotating plate 20A among the multiple input side rotating plates 20 and the multiple output side rotating plates 22, which is located closest to the second direction D2.

[0097] like Figure 16 As shown, in the clutch device 110, in the semi-clutch state, when viewed from the radial direction of the output shaft 15 (i.e., when viewed from the direction orthogonal to the direction D), a portion of the center sleeve side engaging teeth 47 overlaps with a portion of the pressure plate side engaging teeth 77. Here, in the direction D, the center sleeve side engaging teeth 47 overlap with the pressure plate side engaging teeth 77 by a length G2 (G1>G2). That is, no gap is generated in the direction D for the end portion 77T of the pressure plate side engaging teeth 77 in the first direction D1 and the end portion 47T of the center sleeve side engaging teeth 47 in the second direction D2. Therefore, even in the case where the clutch oil flowing from the inside of the clutch center sleeve 40 is scattered radially outward due to centrifugal force, most of the clutch oil will hit the pressure plate side engaging teeth 77, with the result that the clutch oil is supplied to the output side rotating plate 22, etc., which is held by the pressure plate side engaging teeth 77. In addition, the semi-clutch state is a state in which the clutch is connected (refer to Figure 15 ) and the clutch is disconnected (refer to Figure 17 ) between the states.

[0098] like Figure 17 As shown, in the clutch device 110, when the clutch is disengaged, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 when viewed radially of the output shaft 15 (i.e., viewed in a direction orthogonal to direction D). Here, in direction D, the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 overlap by a length G3 (G2>G3). In other words, no gap is formed in direction D between the end portions 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the end portions 47T of the center sleeve-side engaging teeth 47 in the second direction D2.

[0099] like Figure 18As shown, in the clutch device 110, when the pressure plate 70 is in contact with the stop plate 100, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 when viewed radially of the output shaft 15 (i.e., when viewed in a direction orthogonal to direction D). Here, in direction D, the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 overlap by a length G4 (G3>G4). In other words, no gap is generated in direction D between the end portions 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the end portions 47T of the center sleeve-side engaging teeth 47 in the second direction D2.

[0100] <Third embodiment>

[0101] like Figures 19 to 21 As shown, in the clutch device 210 according to the third embodiment, when the pressure plate 70 moves away from the clutch hub 40 (i.e., in the second direction D2), only the input-side rotating plate 20B, located closest to the first direction D1, of the input-side rotating plates 20 remains on the clutch hub 40 side, forming a gap (gap in direction D) between the input-side rotating plate 20B and the output-side rotating plate 22. Furthermore, the gap in direction D formed when the pressure plate 70 moves away from the clutch hub 40 is not limited to the gap between the input-side rotating plate 20B and the output-side rotating plate 22. For example, the gap may be formed between the clutch hub 40 and the input-side rotating plate 20B, between adjacent input-side rotating plates 20 and output-side rotating plates 22, or between the pressure plate 70 and the input-side rotating plate 20.

[0102] like Figure 19 As shown, in the clutch device 210, in the partially engaged state, when viewed radially of the output shaft 15 (i.e., viewed in a direction orthogonal to direction D), a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77. Here, in direction D, the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 overlap by a length G5 (G1>G5). In other words, no gap is generated in direction D between the end portions 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the end portions 47T of the center sleeve-side engaging teeth 47 in the second direction D2.

[0103] like Figure 20 As shown, in the clutch device 210, when the clutch is disengaged, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 when viewed radially of the output shaft 15 (i.e., viewed in a direction orthogonal to direction D). Here, in direction D, the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 overlap by a length G6 (G5>G6). In other words, no gap is formed in direction D between the end portions 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the end portions 47T of the center sleeve-side engaging teeth 47 in the second direction D2.

[0104] like Figure 21 As shown, in the clutch device 210, when the pressure plate 70 is in contact with the stop plate 100, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 when viewed radially of the output shaft 15 (i.e., when viewed in a direction orthogonal to direction D). Here, in direction D, the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 overlap by a length G7 (G6>G7). In other words, no gap is generated in direction D between the end portions 77T of the pressure plate-side engaging teeth 77 in the first direction D1 and the end portions 47T of the center sleeve-side engaging teeth 47 in the second direction D2.

[0105] As described above, according to the clutch device 110 of the second embodiment and the clutch device 210 of the third embodiment, in each of the partially engaged state, the clutch disengaged state, and the state in which the pressure plate 70 is in contact with the stopper plate 100, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 when viewed in the radial direction of the output shaft 15. In other words, in each of the partially engaged state, the clutch disengaged state, and the state in which the pressure plate 70 is in contact with the stopper plate 100, no gap is generated between the pressure plate-side engaging teeth 77 and the center sleeve-side engaging teeth 47 in direction D. Therefore, for example, clutch oil flowing within the clutch center sleeve 40 does not flow directly to the outside but instead flows toward the pressure plate 70. This allows a larger amount of clutch oil to be supplied to the output-side rotating plate 22 and the input-side rotating plate 20 held by the pressure plate 70.

[0106] In the clutch device 110 of the second embodiment and the clutch device 210 of the third embodiment, the pair of side surfaces 77F of the pressure plate-side engaging teeth 77 in the circumferential direction S are inclined so as to approach each other as the pressure plate 70 travels in the first direction D1, when viewed radially from the output shaft 15. This makes it possible to easily move the pressure plate 70 toward and away from the clutch center sleeve 40.

[0107] In the clutch device 110 of the second embodiment and the clutch device 210 of the third embodiment, when the clutch is engaged, the distance LX in the radial direction S between the center sleeve-side engaging teeth 47 and the pressure plate-side engaging teeth 77 may be longer than the distance LZ in the direction D between the end portion 47T of the center sleeve-side engaging teeth 47 on the side in the second direction D2 and the pressure plate 70. This configuration facilitates clutch oil flow through the gap between the pressure plate-side engaging teeth 77 and the center sleeve-side engaging teeth 47.

[0108] In the clutch device 110 of the second embodiment and the clutch device 210 of the third embodiment, when the clutch devices 110 and 210 undergo a temperature change within their usable temperature range, from a low-temperature range to a high-temperature range, a portion of the center sleeve-side engaging teeth 47 overlaps a portion of the pressure plate-side engaging teeth 77 throughout the entire usable temperature range, as viewed in the radial direction of the output shaft 15. Due to this configuration, no gaps are created between the pressure plate-side engaging teeth 77 and the center sleeve-side engaging teeth 47 in direction D within the usable temperature range of the clutch devices 110 and 210. Therefore, for example, clutch oil flowing within the clutch center sleeve 40 does not flow directly to the outside, but instead flows toward the pressure plate 70. This allows a larger amount of clutch oil to be supplied to the output-side rotating plate 22 and the input-side rotating plate 20 held by the pressure plate 70.

[0109] <Fourth embodiment>

[0110] Figure 22 It is an exploded perspective view of a clutch center sleeve 340 and a pressure plate 370 of a clutch device 310 according to a fourth embodiment.

[0111] The clutch center sleeve 340 is accommodated in the clutch housing 30 (refer to Figure 1 ). The clutch center sleeve 340 is concentrically arranged with the clutch housing 30. Figure 22 As shown, the clutch sleeve 340 includes a main body 342 and a flange 368 connected to the outer peripheral edge of the main body 342 on the first direction D1 side and extending radially outward. The main body 342 protrudes in the second direction D2 beyond the flange 368. The clutch sleeve 340 does not hold the output side rotating plate 22. The clutch sleeve 340 is connected to the output shaft 15 (see FIG. Figure 1 ) are driven to rotate together.

[0112] like Figure 22 As shown, the main body 342 includes an output shaft retaining portion 350, a plurality of center sleeve cam portions 60, and a center sleeve engaging portion 358. The center sleeve cam portions 60 are formed to protrude in the second direction D2 beyond the flange 368. The center sleeve cam portions 60 are located radially outward of the output shaft retaining portion 350. The center sleeve cam portions 60 are integrally formed with the output shaft retaining portion 350.

[0113] The output shaft holding portion 350 is formed in a cylindrical shape. Figure 1 ) is inserted and spline-engaged into an insertion hole 351. Insertion hole 351 is formed through main body 342. Multiple spline grooves are formed along the axial direction on the inner circumferential surface 350A of output shaft retaining portion 350, where insertion hole 351 is formed. The output shaft 15 is connected to output shaft retaining portion 350.

[0114] like Figure 22 As shown, the clutch center sleeve 340 has a plurality (three in this embodiment) of bosses 54. The bosses 54 are located radially outward of the output shaft holding portion 350. The bosses 54 are provided on the main body 342.

[0115] like Figure 22 As shown, the clutch hub 340 has a hub-side cam hole 343H that penetrates the main body 342 and a portion of the flange 368. The hub-side cam hole 343H penetrates the main body 342 and the flange 368 in the direction D. The hub-side cam hole 343H extends from the side of the output shaft retaining portion 350 to the flange 368. The hub-side cam hole 343H is formed between the hub-side auxiliary cam surface 60A of the hub-side cam portion 60 and the boss portion 54. When viewed in the axial direction of the clutch hub 340, the hub-side auxiliary cam surface 60A overlaps with a portion of the hub-side cam hole 343H.

[0116] like Figure 22 As shown, the center sleeve side fitting portion 358 is provided on the main body 342. The center sleeve side fitting portion 358 is located radially outward from the center sleeve side cam portion 60. The center sleeve side fitting portion 358 is located on the first direction D1 side from the center sleeve side cam portion 60. The center sleeve side fitting portion 358 is configured to be slidably fitted into the pressure plate side fitting portion 388 (see Figure 23 ).

[0117] like Figure 22 As shown, the flange 368 extends radially outward from the outer peripheral edge of the main body 342. Here, the flange 368 extends radially outward from the outer peripheral edge of the center sleeve-side fitting portion 358. The flange 368 is configured to press against the input-side rotating plate 20 and the output-side rotating plate 22. The flange 368 is located closer to the input-side rotating plate 20 and the output-side rotating plate 22 in the first direction D1. The flange 368 sandwiches the input-side rotating plate 20 and the output-side rotating plate 22 between the flange 398 of the pressure plate 370 and the flange 398 of the pressure plate 370.

[0118] The pressure plate 370 is disposed so as to be able to move toward and away from the clutch hub 340 and to rotate relative thereto. The pressure plate 370 is configured to press the input-side rotating plate 20 and the output-side rotating plate 22. The pressure plate 370 is arranged concentrically with the clutch hub 340 and the clutch housing 30. The pressure plate 370 includes a cylindrical main body 372 and a flange 398 extending radially outward from the outer periphery of the main body 372. The pressure plate 370 holds a plurality of output-side rotating plates 22 that are alternately arranged with the input-side rotating plates 20 in direction D. In this embodiment, the output-side rotating plates 22 are held only by the pressure plate 370.

[0119] like Figure 23As shown, the main body 372 includes: an annular base wall 373, an outer peripheral wall 375 located radially outward of the base wall 373 and extending toward the first direction D1, a cylindrical portion 380 provided at the center of the base wall 373, a plurality of pressure plate side cam portions 90 connected to the base wall 373 and the outer peripheral wall 375, a pressure plate side fitting portion 388, and a spring receiving portion 84 (see Figure 22 The pressure plate side cam portion 90 is formed to protrude from the main body 372 in the first direction D1. The pressure plate side cam portion 90 is located radially outside the cylindrical portion 380. The pressure plate side cam portion 90 is located radially inside the outer peripheral wall 375.

[0120] The cylindrical portion 380 is formed in a cylindrical shape. The cylindrical portion 380 is formed integrally with the pressure plate side cam portion 90. The cylindrical portion 380 accommodates the front end portion 15T of the output shaft 15 (see Figure 1 The release bearing 18 is housed in the cylindrical portion 380 (see Figure 1 The cylindrical portion 380 is a portion that receives the pressing force from the thrust member 16B. The cylindrical portion 380 is a portion that receives the clutch oil flowing out from the front end portion 15T of the output shaft 15.

[0121] like Figure 23As shown, the outer peripheral wall 375 of the pressure plate 370 is arranged radially outward from the cylindrical portion 380. The outer peripheral wall 375 is formed integrally with the cylindrical portion 380. The outer peripheral wall 375 is formed into a circular ring shape extending in the direction D. A spline interlocking portion 376 is provided on the outer peripheral surface 375A of the outer peripheral wall 375. The spline interlocking portion 376 includes: a plurality of pressure plate side interlocking teeth 377 extending along the outer peripheral surface 375A of the outer peripheral wall 375 in the axial direction of the pressure plate 370; a plurality of spline grooves 378 formed between adjacent pressure plate side interlocking teeth 377 and extending in the axial direction of the pressure plate 370; and an oil drain hole 379. The pressure plate side interlocking teeth 377 hold the output side rotating plate 22. The plurality of pressure plate side interlocking teeth 377 are arranged in the circumferential direction S. The plurality of pressure plate side interlocking teeth 377 are formed at equal intervals in the circumferential direction S. The plurality of pressure plate-side interlocking teeth 377 are formed to have the same shape. The pressure plate-side interlocking teeth 377 protrude radially outward from the outer peripheral surface 375A of the outer peripheral wall 375. When viewed radially from the output shaft 15, a pair of side surfaces 377F of the pressure plate-side interlocking teeth 377 in the circumferential direction S are inclined so as to approach each other as the pressure plate 377 travels in the first direction D1. An oil drain hole 379 is formed radially through the outer peripheral wall 375. The oil drain hole 379 is formed between adjacent pressure plate-side interlocking teeth 377. In other words, the oil drain hole 379 is formed in the spline groove 378. The oil drain hole 379 is formed to the side of the pressure plate-side cam portion 90. The oil drain hole 379 is formed to the side of the pressure plate-side auxiliary cam surface 90A of the pressure plate-side cam portion 90. The oil drain hole 379 is formed closer to the first circumferential direction S1 than the pressure plate-side auxiliary cam surface 90A. The oil drain hole 379 is formed on the second circumferential direction S2 side of the pressure plate side sliding cam surface 90S. In the present embodiment, three oil drain holes 379 are formed at three locations on the outer peripheral wall 375 in the circumferential direction S. The oil drain holes 379 are arranged at equally spaced positions on the circumferential direction S. The oil drain holes 379 connect the inside of the pressure plate 370 with the outside. The oil drain hole 379 is a hole for discharging the clutch oil flowing from the output shaft 15 into the pressure plate 370 to the outside of the pressure plate 370. Here, the oil drain hole 379 discharges the clutch oil flowing on the inner peripheral surface 375B side of the outer peripheral wall 375 to the outside of the pressure plate 370. At least a portion of the oil drain hole 379 is provided on the mating portion 358 (refer to the center sleeve side) on the center sleeve side. Figure 22 ) facing each other.

[0122] The output-side rotating plate 22 is retained by the splined engagement portion 376 of the pressure plate 370. The output-side rotating plate 22 is retained by the pressure plate-side engaging teeth 377 and the splined grooves 378 through spline engagement. The output-side rotating plate 22 is provided so as to be displaceable along the axis of the pressure plate 370. The output-side rotating plate 22 is provided so as to be rotatable integrally with the pressure plate 370.

[0123] like Figure 22 and Figure 23As shown, the pressure plate 370 has a pressure plate-side cam hole 373H that penetrates a portion of the base wall 373. The pressure plate-side cam hole 373H penetrates the base wall 373 in direction D. The pressure plate-side cam hole 373H is located radially outward of the cylindrical portion 380. The pressure plate-side cam hole 373H extends from the side of the cylindrical portion 380 to the outer peripheral wall 375. The pressure plate-side cam hole 373H is formed between adjacent pressure plate-side cam portions 90. The pressure plate-side cam hole 373H is formed between adjacent pressure plate-side cam portions 90 and between the pressure plate-side auxiliary cam surface 90A and the pressure plate-side sliding cam surface 90S of the adjacent pressure plate-side cam portions 90. When viewed in the axial direction of the pressure plate 370, the pressure plate-side auxiliary cam surface 90A overlaps with a portion of the pressure plate-side cam hole 373H. Clutch oil flows from the outside of the pressure plate 373 into the pressure plate-side cam hole 373H.

[0124] like Figure 23 As shown, the pressure plate side fitting portion 388 is located radially outward from the cylindrical portion 380. The pressure plate side fitting portion 388 is located radially outward from the pressure plate side cam portion 90. The pressure plate side fitting portion 388 is located on the first direction D1 side from the pressure plate side cam portion 90. The pressure plate side fitting portion 388 is formed on the inner peripheral surface 375B of the outer peripheral wall 375. The pressure plate side fitting portion 388 is configured to be slidably fitted onto the center sleeve side fitting portion 358 (see Figure 22 A gap is formed between the pressure plate side fitting portion 388 and the center sleeve side fitting portion 358.

[0125] While preferred embodiments of the present invention have been described above, these embodiments are merely examples, and the present invention can be implemented in various other forms.

[0126] In the above-described embodiments, the clutch devices 10, 110, 210, and 310 are so-called manual clutches configured to transmit and disconnect the engine's rotational driving force to and from the transmission by a driver's clutch operation (e.g., the driver's operation of a clutch lever), but the present invention is not limited thereto. The clutch devices 10, 110, 210, and 310 may also be so-called automatic clutches configured to automatically transmit and disconnect the engine's rotational driving force to and from the transmission using a clutch actuator.

[0127] In the above-described embodiments, the output shaft retaining portion 50 and the outer peripheral wall 45 of the clutch hub 40 are integrally formed, but the present invention is not limited thereto. For example, the clutch hub 40 may include a first member having the output shaft retaining portion 50 and a second member having the outer peripheral wall 45 and formed separately from the first member, with the first and second members being engaged with each other.

[0128] In the fourth embodiment, the clutch hub 340 is configured not to hold the output-side rotating plate 22, but the present invention is not limited thereto. The clutch hub 340 may also include hub-side engaging teeth having a structure similar to the pressure plate-side engaging teeth 77 of the first embodiment that can hold the output-side rotating plate 22.

[0129] The overlapping state of the center sleeve-side meshing teeth and the pressure plate-side meshing teeth in the semi-clutch state specified in the technical solution may be visually confirmed or not when the input-side rotating plate and the output-side rotating plate are mounted on the clutch center sleeve and the pressure plate. In other words, when the input-side rotating plate and the output-side rotating plate are mounted on the clutch center sleeve and the pressure plate, as long as the overlapping state of the pressure plate-side meshing teeth and the center sleeve-side meshing teeth is as specified in the technical solution, even if this cannot be visually confirmed, it is included within the scope of the present claims.

[0130] The preferred embodiments of the present invention have been described above, but it should be understood that various changes and modifications will be apparent to those skilled in the art without departing from the scope and spirit of the present invention. Therefore, the scope of the present invention is determined solely by the appended claims.

Claims

1. A clutch device for transmitting or disconnecting a rotational driving force of an input shaft to an output shaft, the clutch device comprising: a clutch center sleeve 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; The pressure plate is configured to be able to approach or leave the clutch center sleeve and to rotate relatively, and to press the input side rotating plate and the output side rotating plate. The pressure plate includes a plurality of pressure plate side engaging teeth arranged in a circumferential direction for holding at least one output side rotating plate. The clutch center sleeve has: an output shaft holding portion connected to the output shaft; an outer peripheral wall located radially outward of the output shaft retaining portion; A plurality of center sleeve side engaging teeth hold the output side rotating plate and are formed to protrude radially outward from the outer peripheral surface of the outer peripheral wall and are arranged in the circumferential direction. In the half-clutch state, a portion of the center sleeve side engaging teeth overlaps a portion of the pressure plate side engaging teeth when viewed from the radial direction of the output shaft. When the direction in which the pressure plate approaches the clutch center sleeve is set as the first direction and the direction in which the pressure plate leaves the clutch center sleeve is set as the second direction, The inner circumferential surface of the pressure plate side engaging tooth is inclined radially outward as it moves toward the first direction, and the outer circumferential surface of the pressure plate side engaging tooth is inclined radially outward as it moves toward the second direction. When observed from the radial direction of the output shaft, a pair of circumferential side surfaces of the pressure plate side engaging tooth are inclined from the end in the second direction in a manner that approaches each other as it moves along the first direction, and an angle α formed by each side surface and a straight line parallel to the axis of the output shaft is greater than 0° and less than 5°.

2. A clutch device for transmitting or disconnecting the rotational driving force of an input shaft to an output shaft, the clutch device comprising: a clutch center sleeve 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; The pressure plate is configured to be able to approach or leave the clutch center sleeve and to rotate relatively, and to press the input side rotating plate and the output side rotating plate. The pressure plate includes a plurality of pressure plate side engaging teeth arranged in a circumferential direction for holding at least one output side rotating plate. The clutch center sleeve has: an output shaft holding portion connected to the output shaft; an outer peripheral wall located radially outward of the output shaft retaining portion; A plurality of center sleeve side engaging teeth hold the output side rotating plate and are formed to protrude radially outward from the outer peripheral surface of the outer peripheral wall and are arranged in the circumferential direction. When the clutch is disconnected, a portion of the center sleeve side engaging teeth overlaps a portion of the pressure plate side engaging teeth when viewed in the radial direction of the output shaft. When the direction in which the pressure plate approaches the clutch center sleeve is set as the first direction and the direction in which the pressure plate leaves the clutch center sleeve is set as the second direction, The inner circumferential surface of the pressure plate side engaging tooth is inclined radially outward as it moves toward the first direction, and the outer circumferential surface of the pressure plate side engaging tooth is inclined radially outward as it moves toward the second direction. When observed from the radial direction of the output shaft, a pair of circumferential side surfaces of the pressure plate side engaging tooth are inclined from the end in the second direction in a manner that approaches each other as it moves along the first direction, and an angle α formed by each side surface and a straight line parallel to the axis of the output shaft is greater than 0° and less than 5°.

3. A clutch device for transmitting or disconnecting the rotational driving force of an input shaft to an output shaft, the clutch device comprising: a clutch center sleeve 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; a pressure plate, configured to be able to approach or leave the clutch center sleeve and relatively rotate, and to press the input-side rotating plate and the output-side rotating plate; and The stopper plate is provided so as to be in contact with the pressure plate and to prevent the pressure plate from being separated from the clutch center sleeve by more than a predetermined distance. The pressure plate includes a plurality of pressure plate side engaging teeth arranged in a circumferential direction for holding at least one output side rotating plate. The clutch center sleeve has: an output shaft holding portion connected to the output shaft; an outer peripheral wall located radially outward of the output shaft retaining portion; A plurality of center sleeve side engaging teeth hold the output side rotating plate and are formed to protrude radially outward from the outer peripheral surface of the outer peripheral wall and are arranged in the circumferential direction. When the pressure plate is in contact with the stop plate, a portion of the center sleeve side engaging teeth overlaps a portion of the pressure plate side engaging teeth when viewed in the radial direction of the output shaft. When the direction in which the pressure plate approaches the clutch center sleeve is set as the first direction and the direction in which the pressure plate leaves the clutch center sleeve is set as the second direction, The inner circumferential surface of the pressure plate side engaging tooth is inclined radially outward as it moves toward the first direction, and the outer circumferential surface of the pressure plate side engaging tooth is inclined radially outward as it moves toward the second direction. When observed from the radial direction of the output shaft, a pair of circumferential side surfaces of the pressure plate side engaging tooth are inclined from the end in the second direction in a manner that approaches each other as it moves along the first direction, and an angle α formed by each side surface and a straight line parallel to the axis of the output shaft is greater than 0° and less than 5°.

Images