Clutch device and motorcycle

Abstract

The invention provides a clutch device and a motorcycle. The clutch device is provided with: a clutch center sleeve provided with a plurality of center sleeve-side fitting teeth positioned further to the outside in the radial direction than the center sleeve-side fitting teeth so as to be separated from the center sleeve-side fitting teeth in the radial direction of the output shaft; and a pressure plate provided with a plurality of pressure plate-side fitting teeth positioned further to the outside in the radial direction than the center sleeve-side fitting teeth. When the center sleeve side auxiliary cam surface is in contact with the platen side auxiliary cam surface, an end portion of the platen side fitting tooth in the first direction is positioned closer to the first direction side than an end portion of the center sleeve side fitting tooth in the second direction, and at least a portion of a portion of the platen side fitting tooth overlaps the center sleeve side fitting tooth when viewed from the radial direction of the output shaft. At least a portion of the other portion of the platen-side fitting teeth does not overlap the center sleeve-side fitting teeth when viewed from the radial direction of the output shaft, and a straight line that passes through the center of the oil discharge hole and is parallel to the output shaft passes through the platen-side fitting teeth when viewed from the radial direction of the output shaft.

Description

[0001] This application is a divisional application of the application with application date of June 27, 2023, application number 202310764609.5, and invention name “Clutch device and motorcycle”. CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority based on Japanese Patent Application No. 2022-109217 filed on July 6, 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, and more particularly to a clutch device for arbitrarily transmitting or cutting off the rotational driving force of an input shaft rotationally driven by a prime mover such as an engine to an output shaft, and a motorcycle equipped with the clutch device. Background Art

[0004] In the past, vehicles such as motorcycles were equipped with clutch devices. The clutch device is arranged between the engine and the drive wheel to transmit or cut off the rotational driving force of the engine to the drive wheel. The clutch device usually includes: a plurality of input-side rotating plates that rotate by the rotational driving force of the engine; and a plurality of output-side rotating plates that are connected to the output shaft that transmits the rotational driving force to the drive wheel. The input-side rotating plates and the output-side rotating plates are alternately arranged in the stacking direction, and the rotational driving force is transmitted or cut off by pressing and separating the input-side rotating plates and the output-side rotating plates.

[0005] For example, Japanese Patent Gazette No. 6903020 discloses a clutch device, which includes: a clutch center sleeve (clutch member) that holds an output side rotating plate (driven side clutch plate); and a pressure plate (pressure member) that is arranged to be able to approach and leave the clutch center sleeve. The pressure plate is configured to be able to press the input side rotating plate and the output side rotating plate. In this way, in the clutch device, the clutch center sleeve and the pressure plate are used in an assembled manner.

[0006] In the clutch device of Japanese Patent No. 6903020, as a portion for holding the output side rotating plate, the clutch center sleeve has center sleeve side engaging teeth (an outer peripheral wall formed with splines), and the pressure plate has pressure plate side engaging teeth. When the clutch center sleeve and the pressure plate are assembled, the center sleeve side engaging teeth and the pressure plate side engaging teeth are configured to overlap in the radial direction.

[0007] However, in the radially overlapping portion of the center sleeve side engaging teeth and the pressure plate side engaging teeth, there is a tendency for the oil flowing out from the inside of the clutch center sleeve to the outside to be easily accumulated. Preferably, the clutch oil is supplied to the entire output side rotating plate held by the clutch center sleeve and the pressure plate and the input side rotating plate located between the output side rotating plate in a well-balanced manner.

[0008] The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to provide a clutch device capable of more effectively supplying clutch oil to an output-side rotating plate and an input-side rotating plate, and a motorcycle including the clutch device. Summary of the invention

[0009] The clutch device of the present invention transmits or cuts off the rotational driving force of the input shaft to the output shaft, and comprises: a clutch housing, which holds a plurality of input-side rotating plates that are rotationally driven by the rotational drive of the input shaft; a clutch center sleeve, which is accommodated in the clutch housing, holds a plurality of output-side rotating plates that are alternately arranged with the input-side rotating plates, and is rotationally driven together with the output shaft; and a pressure plate, which is arranged to be able to approach or leave the clutch center sleeve and to be relatively rotatable, and to press the input-side rotating plates and the output-side rotating plates. The clutch center sleeve comprises: an output shaft holding portion that is connected to the output shaft; an outer peripheral wall that is located radially outward of the output shaft holding portion; a plurality of center sleeve side engaging teeth that hold the output-side rotating plates and are formed to protrude radially outward from the outer peripheral surface of the outer peripheral wall and are arranged in the circumferential direction; and a plurality of spline grooves that are formed between adjacent center sleeve side engaging teeth. The pressure plate comprises a plurality of pressure plate side engaging teeth that hold the output-side rotating plates and are arranged in the circumferential direction. The pressure plate side engaging teeth are located radially outward of the center sleeve side engaging teeth. When the direction in which the pressure plate approaches the clutch center sleeve is set as a first direction and the direction in which the pressure plate leaves the clutch center sleeve is set as a second direction, the end of the pressure plate side engaging teeth in the first direction is located closer to the first direction than the end of the center sleeve side engaging teeth in the second direction. Some of the pressure plate side engaging teeth among the plurality of pressure plate side engaging teeth overlap with the center sleeve side engaging teeth in the radial direction at least in part, and other pressure plate side engaging teeth do not overlap with the center sleeve side engaging teeth in the radial direction at least in part.

[0010] According to the clutch device involved in the present invention, the clutch oil flowing out from the output shaft or the like is discharged to the outside of the clutch center sleeve through the drain hole or the like. Here, since the input side rotating plate and the output side rotating plate are held outside the clutch center sleeve, a part of the clutch oil is supplied to the input side rotating plate and the output side rotating plate when the pressure plate and the clutch center sleeve rotate. Moreover, the pressure plate side engaging teeth are located radially outwardly of the center sleeve side engaging teeth. Moreover, the end of the pressure plate side engaging teeth in the first direction is located on the first direction side of the end of the center sleeve side engaging teeth in the second direction. Here, a part of the pressure plate side engaging teeth among the plurality of pressure plate side engaging teeth overlap with the center sleeve side engaging teeth at least in a radial direction. Therefore, in this part, even when the pressure plate and the clutch center sleeve rotate, a part of the clutch oil does not fly to the outside and the clutch oil can be retained. Thus, the clutch oil can be supplied little by little to the output side rotating plate and the input side rotating plate near the pressure plate. On the other hand, another part of the pressure plate side engaging teeth among the plurality of pressure plate side engaging teeth do not overlap with the center sleeve side engaging teeth at least in a radial direction. Therefore, in this portion, when the pressure plate and the clutch center sleeve rotate, the clutch oil splashes to the outside, so that the clutch oil can be immediately supplied to the output-side rotating plate and the input-side rotating plate.

[0011] According to the present invention, it is possible to provide a clutch device capable of more efficiently supplying clutch oil to an output-side rotation plate and an input-side rotation plate.

[0012] 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

[0013] Figure 1 It is a cross-sectional view of a clutch device according to one embodiment.

[0014] Figure 2 The present invention is a perspective view of a clutch center sleeve according to an embodiment.

[0015] Figure 3 The figure is a top view of a clutch center sleeve according to one embodiment.

[0016] Figure 4 It is a perspective view of a pressing plate involved in one embodiment.

[0017] Figure 5 The figure is a top view of a pressing plate according to one embodiment.

[0018] Figure 6 It is a perspective view of a pressing plate involved in one embodiment.

[0019] Figure 7 The figure is a top view of a pressing plate according to one embodiment.

[0020] Figure 8 This is a side view in which a part of the pressure plate side cam part involved in one embodiment is enlarged.

[0021] Fig. 9 This is a perspective view showing an enlarged portion of a pressing plate according to one embodiment.

[0022] Fig.10 It is a plan view showing a state where a clutch center sleeve and a pressure plate according to an embodiment are assembled.

[0023] Fig.11A It is a schematic diagram for explaining the functions of the auxiliary cam surface on the center sleeve side and the auxiliary cam surface on the pressure plate side.

[0024] Fig. 11B It is a schematic diagram for explaining the functions of the sliding cam surface on the center sleeve side and the sliding cam surface on the pressure plate side.

[0025] Fig.12 The present invention is a cross-sectional view of a clutch center sleeve and a pressure plate according to an embodiment.

[0026] Fig.13 1 is a side view of a clutch center sleeve and a pressure plate according to an embodiment.

[0027] Fig.14 It is a side view of the clutch center sleeve and pressure plate when the sliding cam surface on the pressure plate side contacts the sliding cam surface on the center sleeve side.

[0028] Fig.15 It is a side view of the clutch center sleeve and pressure plate when the sliding cam surface on the pressure plate side is not in contact with the sliding cam surface on the center sleeve side and the auxiliary cam surface on the pressure plate side is not in contact with the auxiliary cam surface on the center sleeve side.

[0029] Fig.16 It is a side view of the clutch center sleeve and pressure plate when the auxiliary cam surface on the pressure plate side contacts the auxiliary cam surface on the center sleeve side. DETAILED DESCRIPTION

[0030] Hereinafter, the embodiment of the clutch device involved in the present invention will be described with reference to the accompanying drawings. In addition, the embodiment described here is certainly not intended to specifically limit the present invention. In addition, the same reference numerals are marked on the components and parts that play the same role, and repeated descriptions are appropriately omitted or simplified.

[0031] Figure 11 is a cross-sectional view of the clutch device 10 involved in the present embodiment. The clutch device 10 is provided in a vehicle such as a motorcycle, for example. The clutch device 10 is a device for transmitting or cutting off the rotational driving force of the input shaft (crankshaft) of the engine of the motorcycle to the output shaft 15, for example. The clutch device 10 is a device for transmitting or cutting off the rotational driving force of the input shaft to the drive wheel (rear wheel) via the output shaft 15. The clutch device 10 is arranged between the engine and the transmission.

[0032] In the following description, the direction in which the pressure plate 70 of the clutch device 10 and the clutch center sleeve 40 are arranged is referred to as direction D, the direction in which the pressure plate 70 approaches the clutch center sleeve 40 is referred to as first direction D1, and the direction in which the pressure plate 70 leaves the clutch center sleeve 40 is referred to as second direction D2. In addition, the circumferential direction of the clutch center sleeve 40 and the pressure plate 70 is referred to as 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 first circumferential direction S1 (refer to Figure 5 ), 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 5 ). In the present embodiment, the axial direction of the output shaft 15, the axial direction of the clutch housing 30, the axial direction of the clutch center sleeve 40, and the axial direction of the pressure plate 70 are the same direction as the direction D. In addition, the pressure plate 70 and the clutch center sleeve 40 rotate in the first circumferential direction S1. However, the above directions are only directions determined for the convenience of explanation, and do not limit the setting method of the clutch device 10 at all, nor do they limit the present invention at all.

[0033] 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 .

[0034] like Figure 1 As shown in FIG. 1 , the output shaft 15 is a shaft body formed in a hollow shape. 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 fixedly supports the clutch center sleeve 40 via a nut 15B. That is, the output shaft 15 rotates integrally with the clutch center sleeve 40. The other end of the output shaft 15 is connected to, for example, a transmission (not shown) of a motorcycle.

[0035] like Figure 1As shown, the output shaft 15 has a push rod 16A and a push member 16B disposed adjacent to the push rod 16A in the hollow portion 15H thereof. The hollow portion 15H has a function as a flow path for clutch oil. The clutch oil flows in the output shaft 15, that is, in the hollow portion 15H. The push rod 16A and the push member 16B are disposed so as to be able to slide in the hollow portion 15H of the output shaft 15. One end portion (the end portion on the left side in the figure) of the push rod 16A is connected to a clutch operating lever (not shown) of the motorcycle, and the push member 16B is pressed in the second direction D2 by sliding in the hollow portion 15H through the operation of the clutch operating lever. A portion of the push member 16B protrudes outwardly of the output shaft 15 (in this case, the second direction D2) and is connected to a release bearing 18 disposed 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, and the flowability of the clutch oil is ensured in the hollow portion 15H.

[0036] The clutch housing 30 is formed of an 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.

[0037] 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 drive of the input shaft of the engine. The input gear 35 is independently driven to rotate integrally with the clutch housing 30 from the output shaft 15.

[0038] 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 held on the inner peripheral surface of the side wall 33 of the clutch housing 30. The input side rotating plate 20 is held in the clutch housing 30 by spline fitting. The input side rotating plate 20 is provided to be displaceable along the axial direction of the clutch housing 30. The input side rotating plate 20 is provided to be rotatable integrally with the clutch housing 30.

[0039] The input side rotating plate 20 is a member pressed against the output side rotating plate 22. The input side rotating plate 20 is a flat plate formed in a ring shape. The input side rotating plate 20 is formed by punching a thin plate made of SPCC (cold rolled steel plate) material into a ring shape. Friction members (not shown) made of a plurality of paper sheets are attached to the surface and back of the input side rotating plate 20. Grooves with a depth of several μm to several tens of μm for retaining clutch oil are formed between the friction members.

[0040] like Figure 1As shown, the clutch center sleeve 40 is accommodated in the clutch housing 30. The clutch center sleeve 40 is arranged concentrically with the clutch housing 30. The clutch center sleeve 40 has a cylindrical main body 42 and a flange 68 extending radially outward from the outer peripheral edge of the main body 42. The clutch center sleeve 40 holds a plurality of output side rotating plates 22 alternately arranged with the input side rotating plates 20 in the direction D. The clutch center sleeve 40 is a member that is driven to rotate together with the output shaft 15.

[0041] 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.

[0042] The output shaft holding portion 50 is formed in a cylindrical shape. An insertion hole 51 is formed in the output shaft holding portion 50 for the output shaft 15 to be inserted and splined. The insertion hole 51 is formed to penetrate the base wall 43. An inner peripheral surface 50A of the output shaft holding portion 50 where the insertion hole 51 is formed is formed with a plurality of spline grooves along the axial direction. The output shaft holding portion 50 is connected to the output shaft 15.

[0043] like Figure 2 As shown in FIG. 1 , the outer peripheral wall 45 of the clutch center sleeve 40 is arranged radially outward from the output shaft holding portion 50. A spline fitting portion 46 is provided on the outer peripheral surface of the outer peripheral wall 45. The spline fitting portion 46 includes: a plurality of center sleeve side fitting teeth 47 extending in the axial direction of the clutch center sleeve 40 along the outer peripheral surface of the outer peripheral wall 45, a plurality of spline grooves 48 formed between adjacent center sleeve side fitting teeth 47 and extending in the axial direction of the clutch center sleeve 40, and an oil discharge hole 49. The center sleeve side fitting teeth 47 hold the output side rotating plate 22. The plurality of center sleeve side fitting teeth 47 are arranged in the circumferential direction S. The plurality of center sleeve side fitting teeth 47 are formed at equal intervals in the circumferential direction S. The plurality of center sleeve side fitting teeth 47 are formed in the same shape. The center sleeve side fitting teeth 47 protrude radially outward from the outer peripheral surface of the outer peripheral wall 45. It is preferable that the number of the center sleeve side fitting teeth 47 is a multiple of the number of the center sleeve side cam portion 60. In this embodiment, as described later, the number of the center sleeve side cam portions 60 is 3, and the number of the center sleeve side engaging teeth 47 is 30. In addition, the number of the center sleeve side engaging teeth 47 may not be a multiple of the number of the center sleeve side cam portions 60. Figure 3As shown, the center sleeve side engaging teeth 47 include: a pair of side surfaces 47P extending in the radial direction and a top surface 47Q connecting the radially outer ends of the pair of side surfaces 47P. The side surface 47P is an example of a first side surface. The top surface 47Q is an example of a first top surface. The top surface 47Q extends in the circumferential direction S. The oil drain hole 49 is formed by penetrating the outer peripheral wall 45 in the radial direction. The oil drain hole 49 is formed between adjacent center sleeve side engaging teeth 47. That is, the oil drain hole 49 is formed in the spline groove 48. The oil drain hole 49 is formed on the side 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 of the center sleeve side cam portion 60. The oil drain hole 49 is formed on the second circumferential direction S1 side of the center sleeve side sliding cam surface 60S. The oil drain hole 49 is formed on the first circumferential direction S2 side of the boss portion 54 described later. In the present embodiment, three drain holes 49 are formed at three locations of the outer peripheral wall 45 in the circumferential direction S. The drain holes 49 are arranged at equal intervals in the circumferential direction S. The drain holes 49 connect the inside and the outside of the clutch center sleeve 40. The drain holes 49 are holes for discharging the clutch oil that has flowed out of the output shaft 15 into the clutch center sleeve 40 to the outside of the clutch center sleeve 40.

[0044] 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. Another 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.

[0045] The output side rotating plate 22 is a component pressed against the input side rotating plate 20. The output side rotating plate 22 is a flat plate formed in a ring shape. The output side rotating plate 22 is formed by punching a thin plate made of SPCC material into a ring shape. 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, surface hardening treatment is applied to the surface and back of the output side rotating plate 22, respectively. 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 being provided 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, respectively.

[0046] The center sleeve side cam portion 60 is formed into a table shape having a cam surface composed of an inclined surface constituting an assist & slipper (registered trademark) mechanism, which generates a force that increases the pressing force (pressing force) between the input side rotating plate 20 and the output side rotating plate 22, namely an assist torque, or a force that causes the input side rotating plate 20 and the output side rotating plate 22 to separate as soon as possible and transfer to a semi-clutch state, namely a slip torque. 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 center sleeve side cam portions 60 are arranged at equal intervals in the circumferential direction S of the clutch center sleeve 40. In the present embodiment, the clutch center sleeve 40 has three center sleeve side cam portions 60, but the number of the center sleeve side cam portions 60 is not limited to three.

[0047] like Figure 3 As shown in FIG. 1 , the center sleeve side cam portion 60 is located radially outside the output shaft holding portion 50. The center sleeve side cam portion 60 includes a center sleeve side auxiliary cam surface 60A and a center sleeve side sliding cam surface 60S. The center sleeve side auxiliary cam surface 60A 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 when the center sleeve side auxiliary cam surface 60A rotates relative to the pressure plate 70. In the present embodiment, when the above-mentioned force is generated, the position of the pressure plate 70 relative to the clutch center sleeve 40 does not change, and the pressure plate 70 does not need to physically approach the clutch center sleeve 40. Alternatively, the pressure plate 70 may be physically displaced relative to the clutch center sleeve 40. The center sleeve side sliding cam surface 60S is configured to reduce the pressing force (pressing force) between the input side rotating plate 20 and the output side rotating plate 22 when the center sleeve side sliding cam surface 60S rotates relative to the pressure plate 70 so that the pressure plate 70 moves away from the clutch center sleeve 40. Of 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.

[0048] like Figure 2 As 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.

[0049] like Figure 2As 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 on 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 flow of 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, not less than 0.1 mm and not more than 0.5 mm.

[0050] like Figure 2 and Figure 3 As shown, the clutch center sleeve 40 has a center sleeve side cam hole 43H that penetrates a portion of the base wall 43. The center sleeve side cam hole 43H extends from the side of the output shaft holding portion 50 to the outer peripheral wall 45. The center sleeve side cam hole 43H is formed between the center sleeve side auxiliary cam surface 60A of the center sleeve side cam portion 60 and the boss portion 54. When viewed from the axial direction of the clutch center sleeve 40, the center sleeve side auxiliary cam surface 60A overlaps a portion of the center sleeve side cam hole 43H.

[0051] like Figure 1 As shown, the pressure plate 70 is provided to be able to approach or leave the clutch center sleeve 40 and to be relatively rotatable. 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 than the flange 98. The pressure plate 70 holds a plurality of output side rotating plates 22 alternately arranged with the input side rotating plates 20.

[0052] 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 ).

[0053] 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 1The 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.

[0054] The platen-side cam portion 90 is formed in a table shape having a cam surface composed of an inclined surface constituting an assist and slide (registered trademark) mechanism that slides on the center sleeve-side cam portion 60 to generate an assist torque or a slide torque. The platen-side cam portion 90 is formed to protrude in the first direction D1 from the flange 98. Figure 5 As shown, the press plate side cam portions 90 are arranged at equal intervals in the circumferential direction S of the press plate 70. In the present embodiment, the press plate 70 has three press plate side cam portions 90, but the number of the press plate side cam portions 90 is not limited to three.

[0055] like Figure 5 As shown, the platen side cam portion 90 is located radially outside the cylindrical portion 80. The platen side cam portion 90 has a platen side auxiliary cam surface 90A (see also Figure 7 and Fig. 9 ) and the pressure plate side sliding cam surface 90S. The pressure plate side auxiliary cam surface 90A is configured to be able to 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 when the clutch center sleeve 40 is relatively rotated. The pressure plate side sliding cam surface 90S is configured to be able to 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 when the clutch center sleeve 40 is relatively rotated. In 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.

[0056] like Figure 8 As shown, a chamfered portion 90AP chamfered into a straight line is formed at the end of the pressure plate side auxiliary cam surface 90A in the circumferential direction S of the pressure plate side cam portion 90. The angle of the chamfered portion 90AP (the angle in the first direction D1 and the first circumferential direction S1 side) 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.

[0057] Here, the functions of the center sleeve side cam portion 60 and the pressure plate side cam portion 90 are 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. Fig.11A As shown, the pressing plate 70 is subjected to a rotational force in the first circumferential direction S1. Therefore, the center sleeve side auxiliary cam surface 60A and the pressing plate side auxiliary cam surface 90A generate a force in the first direction D1 on the pressing plate 70. As a result, the pressing force between the input side rotating plate 20 and the output side rotating plate 22 is increased.

[0058] 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. Fig. 11B As shown, the clutch center sleeve 40 is applied with a rotational force in the first circumferential direction S1. Therefore, 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 to release the pressing force between the input side rotating plate 20 and the output side rotating plate 22. Thus, adverse conditions on the engine or transmission caused by reverse torque can be avoided.

[0059] like Figure 4 As 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 Figure 2 ).

[0060] like Figure 4 and Figure 5 As shown, the pressure plate 70 has a pressure plate side cam hole 73H that penetrates 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 5 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 a portion of the pressure plate side cam hole 73H.

[0061] like Figure 4As shown, the pressure plate 70 includes a plurality of pressure plate side engaging teeth 77 arranged on the flange 98 and a plurality of through portions 78 formed between adjacent pressure plate side engaging teeth 77. The pressure plate side engaging teeth 77 hold the output side rotating plate 22. The pressure plate side engaging teeth 77 protrude from 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. The plurality of pressure plate side engaging teeth 77 are arranged in the circumferential direction S. The plurality of pressure plate side engaging teeth 77 are arranged at equal intervals in the circumferential direction S. As shown Figure 5 As shown, the pressure plate side engaging teeth 77 include: a pair of side surfaces 77P extending in the radial direction and a top surface 77Q connecting the radially outer ends of the pair of side surfaces 77P. The side surface 77P is an example of a second side surface. The top surface 77Q is an example of a second top surface. The top surface 77Q extends in the circumferential direction S. In addition, in the present embodiment, since a portion of the pressure plate side engaging teeth 77 is removed, the interval of the portion is enlarged, but other adjacent pressure plate side engaging teeth 77 are arranged at equal intervals. A through portion 78 is formed between adjacent pressure plate side engaging teeth 77. The through portion 78 penetrates in the radial direction. The through portion 78 is open in the radial direction and in the first direction D1.

[0062] like Fig.12 As shown, the pressure plate side interlocking teeth 77 are located radially outward of the center sleeve side interlocking teeth 47 in a manner away from the center sleeve side interlocking teeth 47 in the radial direction of the output shaft 15. A gap is formed between the pressure plate side interlocking teeth 77 and the center sleeve side interlocking teeth 47 in the radial direction. Fig.13 As shown, when the center sleeve side auxiliary cam surface 60A contacts the pressure plate side auxiliary cam surface 90A, the end 77T of the pressure plate side engaging tooth 77 in the first direction D1 is located closer to the first direction D1 side than the end 47T of the center sleeve side engaging tooth 47 in the second direction D2.

[0063] like Fig.12As shown, in the clutch device 10, in the normal state (i.e., in the state where the pressure plate side auxiliary cam surface 90A is in contact with the center sleeve side auxiliary cam surface 60A), a part of the pressure plate side engaging teeth 77 among the plurality of pressure plate side engaging teeth 77 at least partially overlap with the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15. Here, the pressure plate side engaging teeth 77 overlap with the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15, for example, means that the top surface 77Q of the pressure plate side engaging teeth 77 overlaps with the top surface 47Q of the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15. In addition, the pressure plate side engaging teeth 77 at least partially overlap with the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15 means that 50% to 100%, preferably 60% to 100% of the area of ​​the top surface 77Q of the pressure plate side engaging teeth 77 overlaps with the top surface 47Q of the center sleeve side engaging teeth 47. In addition, when a portion of the plurality of pressure plate side engaging teeth 77 is viewed from the radial direction of the output shaft 15, more than half of the length of the pressure plate side engaging teeth 77 in the circumferential direction S overlaps with the center sleeve side engaging teeth 47. In the present embodiment, the length of the top surface 47Q in the circumferential direction S is longer than the length of the top surface 77Q in the circumferential direction S. For example, when the pressure plate side engaging teeth 77A, which is one of the pressure plate side engaging teeth 77, is viewed from the radial direction of the output shaft 15, the entire length of the pressure plate side engaging teeth 77A in the circumferential direction S overlaps with the center sleeve side engaging teeth 47A. In addition, when the clutch device 10 is normally in operation, at least a portion of at least one through portion 78A of the plurality of through portions 78 overlaps with the center sleeve side engaging teeth 47 when viewed from the radial direction of the output shaft 15. Furthermore, in normal operation of the clutch device 10 , the top surfaces 77Q of some of the plurality of pressure plate side engaging teeth 77 at least partially overlap with the top surfaces 47Q of the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15 .

[0064] like Fig.12As shown, in the normal state of the clutch device 10, another part of the pressure plate side engaging teeth 77 among the plurality of pressure plate side engaging teeth 77 does not overlap with the center sleeve side engaging teeth 47 in at least a portion when viewed in the radial direction of the output shaft 15. Here, the pressure plate side engaging teeth 77 do not overlap with the center sleeve side engaging teeth 47 in the radial direction of the output shaft 15, for example, means that the top surface 77Q of the pressure plate side engaging teeth 77 does not overlap with the top surface 47Q of the center sleeve side engaging teeth 47 in the radial direction of the output shaft 15. In addition, the pressure plate side engaging teeth 77 do not overlap with the center sleeve side engaging teeth 47 in at least a portion when viewed in the radial direction of the output shaft 15, which means that 50% to 100%, preferably 60% to 100% of the area of ​​the top surface 77Q of the pressure plate side engaging teeth 77 does not overlap with the top surface 47Q of the center sleeve side engaging teeth 47. In addition, when the pressure plate side engaging teeth 77 are viewed from the radial direction of the output shaft 15, more than half of the length of the pressure plate side engaging teeth 77 in the circumferential direction S does not overlap with the center sleeve side engaging teeth 47. For example, when the pressure plate side engaging teeth 77B, which is one of the pressure plate side engaging teeth 77, are viewed from the radial direction of the output shaft 15, more than half of the length of the pressure plate side engaging teeth 77B in the circumferential direction S does not overlap with the center sleeve side engaging teeth 47B and the center sleeve side engaging teeth 47C. In addition, when the clutch device 10 is normally in operation, the top surfaces 77Q of the pressure plate side engaging teeth 77 of the other part of the plurality of pressure plate side engaging teeth 77 do not overlap with the top surfaces 47Q of the center sleeve side engaging teeth 47 at least partially when viewed from the radial direction of the output shaft 15.

[0065] like Fig.14As shown, in the state where the pressure plate side sliding cam surface 90S is in contact with the center sleeve side sliding cam surface 60S, a part of the pressure plate side engaging teeth 77 (for example, the top surface 77Q of the pressure plate side engaging teeth 77) in the plurality of pressure plate side engaging teeth 77 at least partially overlaps with the center sleeve side engaging teeth 47 (for example, the top surface 47Q of the center sleeve side engaging teeth 47) when viewed from the radial direction of the output shaft 15, and another part of the pressure plate side engaging teeth 77 (for example, the top surface 77Q of the pressure plate side engaging teeth 77) in the plurality of pressure plate side engaging teeth 77 at least partially does not overlap with the center sleeve side engaging teeth 47 (for example, the top surface 47Q of the center sleeve side engaging teeth 47) when viewed from the radial direction of the output shaft 15. In addition, in the state where the pressure plate side sliding cam surface 90S is in contact with the center sleeve side sliding cam surface 60S, at least one through portion 78A in the plurality of through portions 78 at least partially overlaps with the center sleeve side engaging teeth 47 when viewed from the radial direction of the output shaft 15. In addition, when the sliding cam surface 90S on the pressure plate side is in contact with the sliding cam surface 60S on the center sleeve side, among the multiple pressure plate side engaging teeth 77, the top surfaces 77Q of some of the pressure plate side engaging teeth 77 at least partially overlap with the top surfaces 47Q of the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15, and the top surfaces 77Q of other part of the pressure plate side engaging teeth 77 at least partially do not overlap with the top surfaces 47Q of the center sleeve side engaging teeth 47 when viewed in the radial direction of the output shaft 15.

[0066] On the pressure plate 70 from Fig.14 When the clutch center sleeve 40 is approached by a predetermined distance, the pressure plate side sliding cam surface 90S does not contact the center sleeve side sliding cam surface 60S, and the pressure plate side auxiliary cam surface 90A does not contact the center sleeve side auxiliary cam surface 60A (refer to Fig.15 ).like Fig.15As shown, when the pressure plate side sliding cam surface 90S is not in contact with the center sleeve side sliding cam surface 60S and the pressure plate side auxiliary cam surface 90A is not in contact with the center sleeve side auxiliary cam surface 60A, a portion of the multiple pressure plate side engaging teeth 77 (for example, the top surface 77Q of the pressure plate side engaging teeth 77) overlaps with the center sleeve side engaging teeth 47 (for example, the top surface 47Q of the center sleeve side engaging teeth 47) when viewed from the radial direction of the output shaft 15, and another portion of the multiple pressure plate side engaging teeth 77 (for example, the top surface 77Q of the pressure plate side engaging teeth 77) does not overlap with the center sleeve side engaging teeth 47 (for example, the top surface 47Q of the center sleeve side engaging teeth 47) when viewed from the radial direction of the output shaft 15. In addition, in a state where the pressure plate side sliding cam surface 90S does not contact the center sleeve side sliding cam surface 60S and the pressure plate side auxiliary cam surface 90A does not contact the center sleeve side auxiliary cam surface 60A, at least one through portion 78A among the plurality of through portions 78 at least partially overlaps with the center sleeve side engaging tooth 47 when viewed in the radial direction of the output shaft 15. In addition, in a state where the pressure plate side sliding cam surface 90S does not contact the center sleeve side sliding cam surface 60S and the pressure plate side auxiliary cam surface 90A does not contact the center sleeve side auxiliary cam surface 60A, among the plurality of pressure plate side engaging teeth 77, at least partially overlaps with the top surface 47Q of the center sleeve side engaging tooth 47 when viewed in the radial direction of the output shaft 15, and at least partially does not overlap with the top surface 47Q of the center sleeve side engaging tooth 47 when viewed in the radial direction of the output shaft 15.

[0067] On the pressure plate 70 from Fig.15 When the clutch center sleeve 40 is further approached by a predetermined distance in the state shown in FIG. 1 , the pressure plate side auxiliary cam surface 90A contacts the center sleeve side auxiliary cam surface 60A (see FIG. 1 ). Fig.16 ).like Fig.16 As shown, when the auxiliary cam surface 90A on the pressure plate side is in contact with the auxiliary cam surface 60A on the center sleeve side (i.e., normally), a portion of the multiple pressure plate side engaging teeth 77 (e.g., the top surface 77Q of the pressure plate side engaging teeth 77) at least partially overlaps with the center sleeve side engaging teeth 47 (e.g., the top surface 47Q of the center sleeve side engaging teeth 47) when viewed in the radial direction of the output shaft 15, and another portion of the multiple pressure plate side engaging teeth 77 (e.g., the top surface 77Q of the pressure plate side engaging teeth 77) at least partially does not overlap with the center sleeve side engaging teeth 47 (e.g., the top surface 47Q of the center sleeve side engaging teeth 47) when viewed in the radial direction of the output shaft 15.

[0068] like Fig.12As shown, in the clutch device 10, when the clutch device 10 is normally in operation, at least a portion of the spline groove 48 in which the oil drain hole 49 is formed does not overlap with the pressure plate side engaging tooth 77 when viewed in the radial direction of the output shaft 15. Here, the spline groove 48 in which the oil drain hole 49 is formed does not overlap with the pressure plate side engaging tooth 77 when viewed in the radial direction of the output shaft 15, for example, means that a portion of the top surface 77Q of the pressure plate side engaging tooth 77 does not overlap with a portion of the outer peripheral surface 45S of the outer peripheral wall 45 in which the oil drain hole 49 is formed when viewed in the radial direction of the output shaft 15. In addition, the spline groove 48 does not overlap with the pressure plate side engaging tooth 77 in at least a portion when viewed in the radial direction of the output shaft 15, which means that 50% to 100%, preferably 60% to 100%, of the area of ​​the top surface 77Q of the pressure plate side engaging tooth 77 does not overlap with the outer peripheral surface 45S of the outer peripheral wall 45. As shown in FIG. Fig.12 and Fig.14 As shown, for example, when the spline groove 48A is viewed in the radial direction of the output shaft 15, 60% of the spline groove 48A does not overlap with the pressure plate side engaging teeth 77C and the pressure plate side engaging teeth 77D.

[0069] 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 provided 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.

[0070] like Figure 1 As shown, the pressure spring 25 is accommodated in the spring accommodation portion 84. The pressure spring 25 is held by the boss portion 54 inserted into the insertion hole 84H of the spring accommodation portion 84. The pressure spring 25 applies force to the pressure plate 70 toward the clutch center sleeve 40 (i.e., toward the first direction D1). The pressure spring 25 is, for example, a coil spring formed by winding spring steel into a spiral shape.

[0071] Fig.10 2 is a top view showing a state in which the clutch center sleeve 40 and the pressure plate 70 are combined. Fig.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 regarded as the normal state of the clutch device 10. Fig.10As shown, the distance L5 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) in the circumferential direction S is normally shorter than the distance L6 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) in the circumferential direction S.

[0072] like Figure 1 As shown in FIG. 1 , the stopper plate 100 is provided so as to be contactable with the pressure plate 70. The stopper plate 100 is a member for preventing the pressure plate 70 from being separated from the clutch center sleeve 40 in the second direction D2 by a predetermined distance or more. The stopper plate 100 is fixed to the boss portion 54 of the clutch center sleeve 40 by the bolt 28. The pressure plate 70 is fixed to the boss portion 54 via the stopper plate 100 by tightening the bolt 28 in a state where the boss portion 54 of the clutch center sleeve 40 and the pressure spring 25 are arranged in the spring receiving portion 84. The stopper plate 100 is formed in a substantially triangular shape in a plan view.

[0073] Here, when the pressing plate 70 contacts the stopper plate 100, the pressing plate side sliding cam surface 90S and the center sleeve side sliding cam surface 60S contact each other by 50% to 90% of the area of ​​the pressing plate side sliding cam surface 90S and 50% to 90% of the area of ​​the center sleeve side sliding cam surface 60S, respectively. In addition, when the pressing plate 70 contacts the stopper plate 100, the pressure spring 25 leaves the side wall of the spring receiving portion 84. That is, the pressure spring 25 is not sandwiched between the boss portion 54 and the spring receiving portion 84, and excessive stress on the boss portion 54 is suppressed.

[0074] 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 located on the first circumferential direction S1 side of one pressure plate side cam portion 90L in the adjacent pressure plate side cam portions 90 to the end 90SA in the first direction D1 of the 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 Figure 5 ) is greater than the circumferential length L2 (refer to Figure 3 )long.

[0075] In addition, when viewed from the axial direction of the output shaft 15, an angle θ1 is formed by the center of the pressure plate 70 (here, the center 80C of the cylindrical portion 80), an end 90AB in the first circumferential direction S1 of a pressure plate side auxiliary cam surface 90A of one pressure plate side cam portion 90L located on the first circumferential direction S1 side of the pressure plate side cam portion 90 adjacent to each other in the circumferential direction S, and an end 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 Figure 5 ) 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 the 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 ) is large. Angle θ1 is the angle formed by a straight line passing through the center 80C and the end 90AB of the cylindrical portion 80 and a straight line passing through the center 80C and the end 90SB. Angle θ2 is the angle formed by a straight line passing through the center 50C and the end 60AB of the output shaft holding portion 50 and a straight line passing through the center 50C and the end 60SB.

[0076] 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 of the pressure plate side auxiliary cam surface 90A in the first direction D1 to the insertion hole 84H (see Figure 5 )long.

[0077] When viewed from the axial direction of the output shaft 15, the center 50C of the output shaft holding portion 50, the end 60AB of the center sleeve side auxiliary cam surface 60A of the center sleeve side cam portion 60 in the second circumferential direction S2, and the center 54C of the boss portion 54 form an angle θ3 (see Figure 3 ) is an angle θ4 (see FIG. 1 ) formed by the center of the pressure plate 70 (here, 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. Figure 5 ) is large. Angle θ3 is the angle formed by a straight line passing through the center 50C and the end 60AB of the output shaft holding portion 50 and a straight line passing through the center 50C and the center 54C of the boss portion 54. Angle θ4 is the angle formed by a straight line passing through the center 80C and the end 90AB of the cylindrical portion 80 and a straight line passing through the center 80C and the center 84HC of the insertion hole 84H.

[0078] like Fig.12As shown, when observed from the axial direction of the output shaft 15 (i.e., direction D), the smallest angle θ5 among the angles formed by a straight line passing through the center 80C of the cylindrical portion 80 (i.e., the center 15C of the output shaft 15) and the end 77SA on the first circumferential direction S1 side of one of the pressure plate side engaging teeth 77 adjacent in the circumferential direction S and a straight line passing through the center 80C of the cylindrical portion 80 and the end 77SB on the second circumferential direction S2 side of another pressure plate side engaging tooth 77F adjacent in the circumferential direction S is larger than the angle θ6 formed by a straight line passing through the center 50C of the output shaft retaining portion 50 and the end 47SA on the first circumferential direction S1 side of one of the center sleeve side engaging teeth 47 adjacent in the circumferential direction S and the end 47SB on the second circumferential direction S2 side of another center sleeve side engaging tooth 47E adjacent in the circumferential direction S. In addition, the angle θ5 may be smaller than the angle θ6. In addition, in the present embodiment, since a portion of the pressure plate side interlocking teeth 77 is removed, for example, the angle θ7 formed by a straight line passing through the center 80C of the cylindrical portion 80 and the end 77SA on the first circumferential direction S1 side of one of the pressure plate side interlocking teeth 77G adjacent in the circumferential direction S and a straight line passing through the center 80C of the cylindrical portion 80 and the end 77SB on the second circumferential direction S2 side of another of the pressure plate side interlocking teeth 77H adjacent in the circumferential direction S is larger than θ5 and θ6.

[0079] A predetermined amount of clutch oil is filled in the clutch device 10. The clutch oil flows into the clutch center sleeve 40 and the pressure plate 70 through the hollow portion 15H of the output shaft 15, and is then supplied to the input side rotating plate 20 and the output side rotating plate 22 through the gap between the center sleeve side fitting portion 58 and the pressure plate side fitting portion 88 and the oil drain hole 49. The clutch oil suppresses the absorption of heat and the wear of the friction member. The clutch device 10 of this embodiment is a so-called wet multi-plate friction clutch device.

[0080] 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 engine and the transmission of the motorcycle, and transmits or cuts off the rotational driving force of the engine to the transmission when the driver operates the clutch lever.

[0081] In the clutch device 10, when the driver of the motorcycle does not operate the clutch lever, the clutch release mechanism (not shown) does not press the push rod 16A, so the pressure plate 70 presses the input side rotating plate 20 by the urging force (elastic force) of the pressure spring 25. As a result, the clutch center sleeve 40 is in a clutch connection state in which the input side rotating plate 20 and the output side rotating plate 22 are frictionally connected to each other, thereby being rotationally driven. That is, the rotational driving force of the engine is transmitted to the clutch center sleeve 40, and the output shaft 15 is rotationally driven.

[0082] 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 The clutch oil adhering to the cylindrical portion 80 is introduced into the clutch sleeve 40. As a result, the clutch oil flows out to the outside of the clutch sleeve 40 through the drain hole 49. In addition, the clutch oil flows out to the outside of the clutch sleeve 40 through the gap between the sleeve-side fitting portion 58 and the pressure plate-side fitting portion 88. The clutch oil flowing out to the outside of the clutch sleeve 40 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22.

[0083] On the other hand, in the clutch device 10, when the driver of the motorcycle operates the clutch lever in the clutch connected state, the clutch release mechanism (not shown) presses the push rod 16A, so that the pressure plate 70 overcomes the urging force of the pressure spring 25 and displaces in the direction (second direction D2) away from the clutch hub 40. As a result, the clutch hub 40 is in a clutch disconnected state in which the friction connection between the input side rotating plate 20 and the output side rotating plate 22 is released, and thus the rotation drive is attenuated or stopped. That is, the rotation drive force of the engine is disconnected from the clutch hub 40.

[0084] In the clutch disconnected 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 is introduced into the clutch hub 40 in the same manner as in the clutch connected state. At this time, the pressure plate 70 is separated from the clutch hub 40, so the amount of engagement between the hub side engagement portion 58 and the pressure plate side engagement portion 88 is reduced. As a result, the clutch oil in the cylindrical portion 80 flows out more actively to the outside of the clutch hub 40 and flows to various places inside the clutch device 10. In particular, the clutch oil can be actively introduced between the input side rotating plate 20 and the output side rotating plate 22 that are separated from each other.

[0085] When the driver releases the clutch lever in the clutch-off 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.

[0086] As described above, according to the clutch device 10 of the present embodiment, the clutch oil flowing out from the output shaft 15 and the like is discharged to the outside of the clutch sleeve 40 through the drain hole 49 and the like. Here, since the input-side rotating plate 20 and the output-side rotating plate 22 are held outside the clutch sleeve 40, a part of the clutch oil is supplied to the input-side rotating plate 20 and the output-side rotating plate 22 when the pressure plate 70 and the clutch sleeve 40 rotate. Moreover, the pressure plate-side engaging teeth 77 are located radially outward of the sleeve-side engaging teeth 47. Moreover, the end 77T of the pressure plate-side engaging teeth 77 in the first direction D1 is located on the first direction D1 side of the end 47T of the sleeve-side engaging teeth 47 in the second direction D2. Here, a part of the pressure plate-side engaging teeth 77 among the plurality of pressure plate-side engaging teeth 77 overlaps at least a part of the sleeve-side engaging teeth 47 in the radial direction. Therefore, in this part, even when the pressure plate 70 and the clutch sleeve 40 rotate, a part of the clutch oil does not scatter to the outside and the clutch oil can be retained. Thus, the clutch oil can be supplied little by little to the output side rotating plate 22 and the input side rotating plate 20 near the pressure plate 70. On the other hand, at least a part of the other part of the plurality of pressure plate side engaging teeth 77 does not overlap with the center sleeve side engaging teeth 47 in the radial direction. Therefore, in this part, when the pressure plate 70 and the clutch center sleeve 40 rotate, the clutch oil is scattered to the outside, so that the clutch oil can be immediately supplied to the output side rotating plate 22 and the input side rotating plate 20.

[0087] In the clutch device 10 of the present embodiment, a portion of the plurality of pressure plate side engaging teeth 77 overlaps with the center sleeve side engaging teeth 47 at a portion of more than half of the length of the pressure plate side engaging teeth 77 in the circumferential direction S in the radial direction, and a portion of the other pressure plate side engaging teeth 77 does not overlap with the center sleeve side engaging teeth 47 at a portion of more than half of the length of the pressure plate side engaging teeth 77 in the circumferential direction S in the radial direction. According to the above-described method, in the pressure plate side engaging teeth 77, the retention of clutch oil and the scattering to the outside can be achieved in a well-balanced manner.

[0088] In the clutch device 10 of the present embodiment, the clutch sleeve 40 has a plurality of sleeve-side cam portions 60, which are located radially outward of the output shaft holding portion 50 and have sleeve-side auxiliary cam surfaces 60A that generate a force in a direction that causes the pressure plate 70 to approach the clutch sleeve 40 in order to increase the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22 when relatively rotating with respect to the pressure plate 70, and sleeve-side sliding cam surfaces 60S that cause the pressure plate 70 to move away from the clutch sleeve 40 in order to reduce the pressing force between the input-side rotating plate 20 and the output-side rotating plate 22, and the oil discharge holes 49 are formed on the sides of the plurality of sleeve-side cam portions 60, respectively, and the number of sleeve-side engaging teeth 47 is a multiple of the number of sleeve-side cam portions 60. According to the above-described embodiment, the positional relationship between the sleeve-side cam portions 60 and the oil discharge holes 49 can be made the same. Therefore, the variation in the amount of clutch oil discharged to the outside from the oil discharge holes 49 is reduced.

[0089] In the clutch device 10 of the present embodiment, the number of the center sleeve side cam portions 60 is 3, and the number of the center sleeve side engaging teeth 47 is a multiple of 3. According to the above, when the clutch center sleeve 40 rotates relative to the pressure plate 70, the increase and decrease of the pressing force of the input side rotating plate 20 and the output side rotating plate 22 can be achieved in a well-balanced manner.

[0090] In the clutch device 10 of the present embodiment, the spline groove 48 in which the oil drain hole 49 is formed does not overlap at least a portion in the radial direction with the pressure plate side engaging teeth 77. According to the above-mentioned embodiment, the clutch oil flowing out of the oil drain hole 49 to the outside of the clutch center sleeve 40 can be effectively supplied to the input side rotating plate 20 and the output side rotating plate 22.

[0091] In the clutch device 10 of the present embodiment, the spline groove 48 in which the oil drain hole 49 is formed does not overlap the pressure plate side engaging teeth 77 in the radial direction. According to the above-mentioned embodiment, the clutch oil flowing out of the oil drain hole 49 to the outside of the clutch center sleeve 40 can be more effectively supplied to the input side rotating plate 20 and the output side rotating plate 22.

[0092] In the clutch device 10 of the present embodiment, when viewed from the axial direction of the output shaft 15 (i.e., direction D), the smallest angle θ5 among the angles formed by a straight line passing through the center 15C of the output shaft 15 and the end 77SA on the first circumferential direction S1 side of one of the pressure plate side engaging teeth 77 adjacent in the circumferential direction S and a straight line passing through the center 15C of the output shaft 15 and the end 77SB on the second circumferential direction S2 side of another of the pressure plate side engaging teeth 77 adjacent in the circumferential direction S is smaller than the angle θ6 formed by a straight line passing through the center 50C of the output shaft retaining portion 50 and the end 47SA on the first circumferential direction S1 side of one of the center sleeve side engaging teeth 47 adjacent in the circumferential direction S and a straight line passing through the center 50C of the output shaft retaining portion 50 and the end 47SB on the second circumferential direction S2 side of another of the center sleeve side engaging teeth 47 adjacent in the circumferential direction S. According to the above aspect, in the pressure plate side fitting teeth 77, retention of the clutch oil and dispersion to the outside can be achieved in a well-balanced manner.

[0093] In the clutch device 10 of the present embodiment, the clutch sleeve 40 includes an oil drain hole 49 formed in the spline groove 48 so as to penetrate the outer peripheral wall 45 and discharge the clutch oil flowing out from the output shaft 15 to the outside of the clutch sleeve 40, and the pressure plate 70 includes a cylindrical portion 80 for accommodating the front end portion 15T of the output shaft 15, and the pressure plate side engaging teeth 77 are located radially outward of the cylindrical portion 80. According to the above embodiment, the clutch oil flowing out from the front end portion 15T of the output shaft 15 to the cylindrical portion 80 through the oil drain hole 49 can be more efficiently discharged to the outside of the clutch sleeve 40.

[0094] The preferred embodiments of the present invention have been described above, but the above embodiments are merely examples, and the present invention can be implemented in various other forms.

[0095] The preferred embodiments of the present invention are 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 only by the appended claims.

Claims

1. A clutch device for transmitting or cutting off the rotational driving force of an input shaft to an output shaft, the clutch device comprising: A clutch center sleeve 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 is a member that is rotationally driven together with the output shaft; and The pressure plate is arranged 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 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 holding portion; A plurality of center sleeve side engaging teeth, which 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; A plurality of spline grooves are formed between adjacent center sleeve side engaging teeth; an oil drain hole formed in the spline groove in a manner penetrating the outer peripheral wall, and discharging the clutch oil flowing out of the output shaft to the outside of the clutch center sleeve; and A plurality of center sleeve side cam portions are located radially outside the output shaft holding portion and have center sleeve side auxiliary cam surfaces. When the center sleeve side auxiliary cam surfaces rotate relative to the pressure plate, they generate a force in a direction that causes the pressure plate to approach the clutch center sleeve in order to increase the pressing force between the input side rotating plate and the output side rotating plate. The pressing plate has: A plurality of pressure plate side engaging teeth are arranged in a circumferential direction to hold the output side rotating plate; A plurality of pressure plate side cam portions, each having a pressure plate side auxiliary cam surface, which generates a force in a direction causing the pressure plate to approach the clutch center sleeve in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the pressure plate side cam portions rotate relative to the clutch center sleeve; and A plurality of through-portions are formed between adjacent pressing plate side engaging teeth and penetrate in the radial direction, The pressure plate side engaging teeth are located radially outward of the center sleeve side engaging teeth in a manner away from the center sleeve side engaging teeth in the radial direction of the output shaft. The direction in which the pressure plate approaches the clutch center sleeve is set as a first direction, and the direction in which the pressure plate leaves the clutch center sleeve is set as a second direction. When the auxiliary cam surface on the center sleeve side contacts the auxiliary cam surface on the pressure plate side, the end of the engaging teeth on the pressure plate side in the first direction is located closer to the first direction side than the end of the engaging teeth on the center sleeve side in the second direction. When the auxiliary cam surface on the center sleeve side contacts the auxiliary cam surface on the pressure plate side, for a part of the plurality of pressure plate side engaging teeth, when each pressure plate side engaging teeth is observed from the radial direction of the output shaft, at least a part of the pressure plate side engaging teeth overlaps with the center sleeve side engaging teeth, and for another part of the pressure plate side engaging teeth, when each pressure plate side engaging teeth is observed from the radial direction of the output shaft, at least a part of the pressure plate side engaging teeth does not overlap with the center sleeve side engaging teeth, and when observed from the radial direction of the output shaft, a straight line passing through the center of the oil drain hole and parallel to the output shaft passes through the pressure plate side engaging teeth, At least one of the plurality of penetration portions has at least a portion overlapping the center sleeve-side fitting teeth when viewed in the radial direction of the output shaft.

2. The clutch device according to claim 1, wherein: A portion of the multiple pressure plate side interlocking teeth overlaps with the center sleeve side interlocking teeth at more than half of the circumferential length of the pressure plate side interlocking teeth when viewed from the radial direction of the output shaft, and a portion of the other pressure plate side interlocking teeth does not overlap with the center sleeve side interlocking teeth at more than half of the circumferential length of the pressure plate side interlocking teeth when viewed from the radial direction of the output shaft.

3. The clutch device according to claim 1 or 2, wherein: The spline groove is formed with a plurality of the oil drain holes arranged in the axial direction of the output shaft. When the auxiliary cam surface on the center sleeve side contacts the auxiliary cam surface on the pressure plate side, when observed from the radial direction of the output shaft, in each of the multiple oil drain holes, a straight line passing through the center of the oil drain hole and parallel to the output shaft passes through the pressure plate side engaging tooth.

4. The clutch device according to claim 1 or 2, wherein: When the center sleeve side auxiliary cam surface contacts the pressure plate side auxiliary cam surface, the pressure plate side engaging teeth include the pressure plate side engaging teeth overlapping the entirety of the oil discharge hole when the pressure plate side engaging teeth are viewed in the radial direction of the output shaft.

5. The clutch device according to claim 1 or 2, wherein: The center sleeve side cam portion has a center sleeve side sliding cam surface, and the center sleeve side sliding cam surface is used to reduce the pressing force between the input side rotating plate and the output side rotating plate when the center sleeve side cam portion rotates relative to the pressure plate so as to separate the pressure plate from the clutch center sleeve. The oil drain holes are respectively formed on the sides of the plurality of center sleeve side cam portions. The number of the center sleeve side engaging teeth is a multiple of the number of the center sleeve side cam portions.

6. The clutch device according to claim 5, wherein: The number of the center sleeve side cam portions is 3, and the number of the center sleeve side engaging teeth is a multiple of 3.

7. The clutch device according to claim 1 or 2, wherein: When the center sleeve-side auxiliary cam surface contacts the pressure plate-side auxiliary cam surface, at least a portion of the spline groove in which the oil discharge hole is formed does not overlap with the pressure plate-side engaging teeth when viewed in the radial direction of the output shaft.

8. The clutch device according to claim 7, wherein: When the center sleeve-side auxiliary cam surface contacts the pressure plate-side auxiliary cam surface, the spline groove in which the oil discharge hole is formed does not overlap with the pressure plate-side engaging teeth when viewed in the radial direction of the output shaft.

9. The clutch device according to claim 1 or 2, wherein: The pressure plate side cam portion has a pressure plate side sliding cam surface, and the pressure plate side sliding cam surface is used to reduce the pressing force between the input side rotating plate and the output side rotating plate when the pressure plate rotates relative to the clutch center sleeve so as to separate the pressure plate from the clutch center sleeve. When the direction from one of the pressure plate side cam portions toward the other pressure plate side cam portion in the circumferential direction is set as a first circumferential direction, and the direction from the other pressure plate side cam portion toward one of the pressure plate side cam portions is set as a second circumferential direction, When observed from the axial direction of the output shaft, the minimum angle formed by a straight line passing through the center of the output shaft and the end of the first circumferential side of one of the circumferentially adjacent pressure plate side chimeric teeth and a straight line passing through the center of the output shaft and the end of the second circumferential side of another of the circumferentially adjacent pressure plate side chimeric teeth is smaller than the angle formed by a straight line passing through the center of the output shaft retaining portion and the end of the first circumferential side of one of the circumferentially adjacent center sleeve side chimeric teeth and a straight line passing through the center of the output shaft retaining portion and the end of the second circumferential side of another of the circumferentially adjacent center sleeve side chimeric teeth.

10. The clutch device according to claim 1 or 2, wherein: The pressure plate includes a cylindrical portion for accommodating the front end portion of the output shaft. The pressure plate-side engaging teeth are located radially outward of the cylindrical portion.

11. A motorcycle comprising the clutch device according to claim 1 or 2.

12. A clutch device for transmitting or cutting off the rotational driving force of an input shaft to an output shaft, the clutch device comprising: A clutch center sleeve 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 is a member that is rotationally driven together with the output shaft; and The pressure plate is arranged 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 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 holding portion; A plurality of center sleeve side engaging teeth, which 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; A plurality of spline grooves are formed between adjacent center sleeve side engaging teeth; an oil drain hole formed in the spline groove in a manner penetrating the outer peripheral wall, and discharging the clutch oil flowing out of the output shaft to the outside of the clutch center sleeve; and A plurality of center sleeve side cam portions are located radially outside the output shaft holding portion and have center sleeve side auxiliary cam surfaces. When the center sleeve side auxiliary cam surfaces rotate relative to the pressure plate, they generate a force in a direction that causes the pressure plate to approach the clutch center sleeve in order to increase the pressing force between the input side rotating plate and the output side rotating plate. The pressing plate has: A plurality of pressure plate side engaging teeth, which hold the output side rotating plate and are arranged in a circumferential direction; and A plurality of pressure plate side cam portions have pressure plate side auxiliary cam surfaces, which generate a force in a direction causing the pressure plate to approach the clutch center sleeve in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the pressure plate side auxiliary cam surfaces rotate relative to the clutch center sleeve. The pressure plate side engaging teeth are located radially outward of the center sleeve side engaging teeth in a manner away from the center sleeve side engaging teeth in the radial direction of the output shaft. The center sleeve side engaging teeth have a pair of first side surfaces extending in the radial direction and a first top surface connecting radially outer ends of the pair of first side surfaces. The pressure plate side engaging teeth have a pair of second side surfaces extending in the radial direction and a second top surface connecting radially outer ends of the pair of second side surfaces. The direction in which the pressure plate approaches the clutch center sleeve is set as a first direction, and the direction in which the pressure plate leaves the clutch center sleeve is set as a second direction. When the auxiliary cam surface on the center sleeve side contacts the auxiliary cam surface on the pressure plate side, the end of the engaging teeth on the pressure plate side in the first direction is located closer to the first direction side than the end of the engaging teeth on the center sleeve side in the second direction. When the auxiliary cam surface on the center sleeve side contacts the auxiliary cam surface on the pressure plate side, the second top surfaces of a part of the multiple pressure plate side engaging teeth at least partially overlap with the first top surfaces of the center sleeve side engaging teeth when each pressure plate side engaging teeth is observed from the radial direction of the output shaft, and the second top surfaces of another part of the pressure plate side engaging teeth at least partially do not overlap with the first top surfaces of the center sleeve side engaging teeth when each pressure plate side engaging teeth is observed from the radial direction of the output shaft, and a straight line passing through the center of the oil drain hole and parallel to the output shaft passes through the pressure plate side engaging teeth when observed from the radial direction of the output shaft.

13. A clutch device for transmitting or cutting off the rotational driving force of an input shaft to an output shaft, the clutch device comprising: A clutch center sleeve 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 is a member that is rotationally driven together with the output shaft; and The pressure plate is arranged 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 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 holding portion; A plurality of center sleeve side engaging teeth, which 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; A plurality of spline grooves are formed between adjacent center sleeve side engaging teeth; an oil drain hole formed in the spline groove in a manner penetrating the outer peripheral wall, and discharging the clutch oil flowing out of the output shaft to the outside of the clutch center sleeve; and A plurality of center sleeve side cam portions are located radially outside the output shaft retaining portion and have a center sleeve side auxiliary cam surface and a center sleeve side sliding cam surface. The center sleeve side auxiliary cam surface generates a force in a direction that causes the pressure plate to approach the clutch center sleeve in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the center sleeve side auxiliary cam surface rotates relative to the pressure plate. The center sleeve side sliding cam surface reduces the pressing force between the input side rotating plate and the output side rotating plate when the center sleeve side sliding cam surface rotates relative to the pressure plate so as to cause the pressure plate to leave the clutch center sleeve. The pressing plate has: A plurality of pressure plate side engaging teeth are arranged in a circumferential direction to hold the output side rotating plate; A plurality of pressure plate side cam portions, each having a pressure plate side auxiliary cam surface and a pressure plate side sliding cam surface, wherein the pressure plate side auxiliary cam surface generates a force in a direction causing the pressure plate to approach the clutch center sleeve in order to increase the pressing force between the input side rotating plate and the output side rotating plate when the pressure plate rotates relative to the clutch center sleeve, and the pressure plate side sliding cam surface causes the pressure plate to leave the clutch center sleeve in order to reduce the pressing force between the input side rotating plate and the output side rotating plate when the pressure plate rotates relative to the clutch center sleeve; and A plurality of inter-tooth portions are formed between adjacent pressure plate side engaging teeth and hold the output side rotating plate together with the pressure plate side engaging teeth. Between the state in which the auxiliary cam surface on the center sleeve side contacts the auxiliary cam surface on the pressure plate side and the state in which the sliding cam surface on the center sleeve side contacts the sliding cam surface on the pressure plate side, when observed from the radial direction of the output shaft, there is a state in which a straight line passing through the center of the oil drain hole and parallel to the output shaft passes through the engaging teeth on the pressure plate side and a state in which the straight line passes through the inter-tooth portion.

14. The clutch device according to claim 13, wherein: When the direction in which the pressure plate approaches the clutch center sleeve is set as a first direction and the direction in which the pressure plate leaves the clutch center sleeve is set as a second direction, the clutch center sleeve has the oil drain hole located closer to the first direction side than the edge of the pressure plate side engaging tooth on the first direction side.

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