Power transmission device

Abstract

A power transmission device (K) is provided with a centrifugal clutch unit (9) having: a weight member (10) that is movable from an inner diameter side position to an outer diameter side position by centrifugal force associated with rotation of a clutch housing (2); the press-contact member moves in a direction in which the drive-side clutch plate (6) and the driven-side clutch plate (7) are press-contacted by the weight member moving from the inner-diameter-side position to the outer-diameter-side position, and the weight member is configured so that the drive-side clutch plate (6) and the driven-side clutch plate (7) are pressed by the press-contact member when the weight member moves from the inner-diameter-side position to the outer-diameter-side position. The centrifugal clutch unit (9) has first inclined surfaces (10a, 12a) and second inclined surfaces (10b, 12b), which have a larger inclination angle with respect to the axial direction of the output shaft (3) than the first inclined surfaces (10a, 12a), at the portions where the counterweight member and the crimping member are in contact with each other.

Description

Technical Field

[0001] The present invention relates to a power transmission device capable of arbitrarily transmitting or cutting off the rotational force of an input member to an output member. Background Art

[0002] As a conventional power transmission device, for example, as disclosed in Patent Document 1, a centrifugal clutch unit having a weight member is proposed, and the weight member is moved from an inner diameter side position to an outer diameter side position by centrifugal force accompanying the rotation of the clutch housing, thereby enabling the driving side clutch plate and the driven side clutch plate to be pressed together via a pressing member. According to this conventional power transmission device, as the clutch housing rotates with the drive of a driving source such as an engine, centrifugal force can be applied to the weight member, and the driving side clutch plate and the driven side clutch plate can be pressed together via the pressing member to transmit the driving force of the engine to the wheels.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: International Publication No. 2013 / 183588 Summary of the invention

[0006] Problems to be solved by the invention

[0007] However, in the case where the above-mentioned conventional power transmission device is applied to a small vehicle with a small engine displacement and a low clutch housing rotation speed (i.e., the primary transmission is relatively large), it is relatively difficult to set the centrifugal force on the counterweight component to be relatively large. Therefore, for example, it is necessary to increase the inclination angle of the cam surface that converts the thrust of the counterweight component into the pressing force of the driving side clutch plate and the passive side clutch plate. However, if the inclination angle of the cam surface is set to be relatively large, the amount of movement of the pressing component in the axial direction of the output component will become smaller. That is, the amount of movement in the pressing direction (i.e., the axial direction of the output component) of the driving side clutch plate and the passive side clutch plate will become smaller. Therefore, it may be difficult to press the driving side clutch plate and the passive side clutch plate to fully transmit the driving force.

[0008] The present invention is completed in view of the above points, and its purpose is to provide a power transmission device of a centrifugal clutch unit having the ability to ensure the axial movement of the pressure-contacting member and the thrust of the weight member required to press-contact the driving side clutch plate and the driven side clutch plate to fully transmit the driving force.

[0009] Means for solving problems

[0010] The power transmission device of the present invention comprises: a clutch member, which is accommodated in a clutch housing that rotates together with an input member that rotates through a driving force of a driving source and holds a plurality of driving side clutch plates, and is connected to an output member that can rotate a wheel; a pressure member that is arranged in a manner that can approach or move away from the clutch member, and can press a plurality of driven side clutch plates and a plurality of driving side clutch plates that are alternately arranged with the driving side clutch plates; and a centrifugal clutch unit that has a weight member and a pressure contact member, wherein the weight member can be moved from an inner diameter side position to an outer diameter side position by a centrifugal force associated with the rotation of the clutch housing, the pressure contact member is arranged in a manner that can contact the weight member, and moves in a direction in which the driving side clutch plates and the driven side clutch plates are pressed into contact by the weight member moving from the inner diameter side position to the outer diameter side position, and the The centrifugal clutch unit can press the driving side clutch plate and the passive side clutch plate together when the counterweight member is in the outer diameter side position to form a state in which the driving force of the driving source can be transmitted to the wheel, and can release the pressing force between the driving side clutch plate and the passive side clutch plate when the counterweight member is in the inner diameter side position to cut off the transmission of the driving force of the driving source to the wheel. The counterweight member is configured to press the driving side clutch plate and the passive side clutch plate together via the pressing member during the movement of the counterweight member from the inner diameter side position to the outer diameter side position. The centrifugal clutch unit has a first inclined surface and a second inclined surface having an inclination angle larger than the first inclined surface with respect to the axial direction of the output member at a portion where the counterweight member and the pressing member contact each other.

[0011] According to the power transmission device of the present invention, the centrifugal clutch unit has a first inclined surface and a second inclined surface with a larger inclination angle than the first inclined surface relative to the axial direction of the output member at least one of the counterweight member and the pressing member, where the counterweight member and the pressing member contact each other. According to the above scheme, the amount of movement of the pressing member in the axial direction of the output member and the thrust of the counterweight member required by the pressing member can be ensured according to the operating state.

[0012] Another power transmission device of the present invention comprises: a clutch member, which is accommodated in a clutch housing that rotates together with an input member that rotates by a driving force of a driving source and holds a plurality of driving side clutch plates, and is connected to an output member that can rotate a wheel; a pressure member that is arranged in a manner that can approach or move away from the clutch member, and can press a plurality of driven side clutch plates and a plurality of driving side clutch plates that are alternately arranged with the driving side clutch plates; and a centrifugal clutch unit having a weight member and a pressing member, the weight member being movable from an inner diameter side position to an outer diameter side position by a centrifugal force accompanying the rotation of the clutch housing, the pressing member being arranged in a manner that can contact the weight member, and being movable in a direction in which the driving side clutch plates and the driven side clutch plates are pressed against each other by the weight member moving from the inner diameter side position to the outer diameter side position, and, The centrifugal clutch unit can press the driving side clutch plate and the passive side clutch plate together when the counterweight member is in the outer diameter side position to form a state in which the driving force of the driving source can be transmitted to the wheel, and can release the pressing force between the driving side clutch plate and the passive side clutch plate when the counterweight member is in the inner diameter side position to cut off the transmission of the driving force of the driving source to the wheel. The counterweight member is configured to press the driving side clutch plate and the passive side clutch plate together via the pressing member during the movement of the counterweight member from the inner diameter side position to the outer diameter side position. The centrifugal clutch unit has a first area and a second area in which the axial movement of the pressing member in the output member is smaller than that of the first area in at least one of the counterweight member and the pressing member.

[0013] According to another power transmission device of the present invention, the centrifugal clutch unit has a first area and a second area where the amount of axial movement of the pressure-contacting member in the output member is smaller than that in the first area at a portion where the weight member and the pressure-contacting member contact each other, at least one of the weight member and the pressure-contacting member. According to the above scheme, the amount of axial movement of the output member and the thrust of the weight member required by the pressure-contacting member can be ensured according to the operating state.

[0014] Another power transmission device of the present invention comprises: a clutch member, which is accommodated in a clutch housing that rotates together with an input member that rotates by a driving force of a driving source and holds a plurality of driving side clutch plates, and is connected to an output member that can rotate a wheel; a pressure member that is arranged in a manner that can approach or move away from the clutch member, and can press a plurality of driven side clutch plates and a plurality of driving side clutch plates that are alternately arranged with the driving side clutch plates; and a centrifugal clutch unit that has a weight member and a pressure contact member, the weight member being movable from an inner diameter side position to an outer diameter side position by a centrifugal force accompanying the rotation of the clutch housing, the pressure contact member being arranged in a manner that can contact the weight member, and being moved from the inner diameter side position to the outer diameter side position by the weight member in a direction in which the driving side clutch plates and the driven side clutch plates are pressure contacted. The wheel is then moved to a position adjacent to the driving wheel and the driven wheel is moved to a position adjacent to the driving wheel and the driven wheel is moved to a position adjacent to the driving wheel and the driven wheel is moved to a position adjacent to the driving wheel.

[0015] According to another power transmission device of the present invention, the centrifugal clutch unit has a first region and a second region where the thrust of the weight member is greater than the first region in a portion where the weight member and the pressing member contact each other, at least one of the weight member and the pressing member. According to the above scheme, the amount of axial movement of the pressing member required by the output member and the thrust of the weight member can be ensured according to the operating state.

[0016] Effects of the Invention

[0017] According to the present invention, a power transmission device including a centrifugal clutch unit can be provided which can ensure the axial movement amount of the pressure contact member in the output member and the thrust force of the weight member required to press the driving side clutch plate and the driven side clutch plate to fully transmit the driving force. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is an external view showing the power transmission device according to the first embodiment.

[0019] Figure 2 It is along Figure 1 Cross-sectional view along line II-II.

[0020] Figure 3 It is along Figure 1 Cross-sectional view along line III-III.

[0021] Figure 4 It is an exploded perspective view of the power transmission device according to the first embodiment.

[0022] Figure 5 It is an exploded perspective view of the power transmission device according to the first embodiment.

[0023] Figure 6 It is an exploded perspective view of the centrifugal clutch unit according to the first embodiment.

[0024] Figure 7 It is a perspective view showing the weight member according to the first embodiment.

[0025] Figure 8 1 and 2 are a plan view and a rear view showing the weight member according to the first embodiment.

[0026] Fig. 9 It is along Figure 8 A cross-sectional view taken along line IX-IX.

[0027] Fig.10 It is a perspective view showing the crimping member according to the first embodiment.

[0028] Fig.11 It is a plan view and a side view which show the crimping member of the first embodiment.

[0029] Fig.12 It is along Fig.11 A cross-sectional view taken along line XII-XII.

[0030] Fig.13 It is a perspective view showing the holding member according to the first embodiment.

[0031] Fig.14 This is a cross-sectional view showing the operation of the centrifugal clutch unit according to the first embodiment (the weight member is located at the inner diameter side).

[0032] Fig.15 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the first embodiment (the weight member is located between the inner diameter side position and the outer diameter side position).

[0033] Fig.16 This is a cross-sectional view showing the operation of the centrifugal clutch unit according to the first embodiment (the weight member is located at the outer diameter side).

[0034] Fig.17 It is a schematic diagram showing a vehicle to which the power transmission device according to the first embodiment is applied.

[0035] Fig.18 It is a perspective view showing a weight member according to a second embodiment.

[0036] Fig.19 1 and 2 are a plan view and a rear view showing a weight member according to a second embodiment.

[0037] Fig. 20 It is along Fig.19 Cross-sectional view of line XX-XX.

[0038] Fig.21 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the second embodiment (the weight member is located at the inner diameter side).

[0039] Fig. 22 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the second embodiment (the weight member is located between the inner diameter side position and the outer diameter side position).

[0040] Fig.23 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the second embodiment (the weight member is located at the outer diameter side).

[0041] Fig.24 It is a perspective view showing a weight member according to a third embodiment.

[0042] Fig.25 1 and 2 are a plan view and a rear view showing a weight member according to a third embodiment.

[0043] Fig.26 It is along Fig.25 A cross-sectional view taken along line XXVI-XXVI.

[0044] Fig. 27 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the third embodiment (the weight member is located at the inner diameter side).

[0045] Fig.28 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the third embodiment (the weight member is located between the inner diameter side position and the outer diameter side position).

[0046] Fig.29 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the third embodiment (the weight member is located at the outer diameter side).

[0047] Fig.30 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the fourth embodiment (the weight member is located at the inner diameter side).

[0048] Fig.31 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the fourth embodiment (the weight member is located between the inner diameter side position and the outer diameter side position).

[0049] Fig.32 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the fourth embodiment (the weight member is located at the outer diameter side).

[0050] Fig.33 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the fifth embodiment (the weight member is located at the inner diameter side).

[0051] Fig.34 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the fifth embodiment (the weight member is located between the inner diameter side position and the outer diameter side position).

[0052] Fig.35 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the fifth embodiment (the weight member is located at the outer diameter side).

[0053] Fig.36 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the sixth embodiment (the weight member is located at the inner diameter side).

[0054] Fig.37 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the sixth embodiment (the weight member is located between the inner diameter side position and the outer diameter side position).

[0055] Fig.38 It is a cross-sectional view showing the operation of the centrifugal clutch unit according to the sixth embodiment (the weight member is located at the outer diameter side).

[0056] Fig.39 It is a graph showing the relationship between the rotation speed of the engine and the movement amount of the pressing member.

[0057] Fig.40 It is a graph showing the relationship between the rotation speed of the engine and the thrust of the weight member. DETAILED DESCRIPTION

[0058] <First Embodiment>

[0059] Below, while referring to the attached Figure 1 The embodiments of the present invention are described in detail. Fig.17 As shown, the power transmission device K is provided in the vehicle and is used to arbitrarily transmit or cut off the driving force of the engine E to the driving wheel T side via the transmission M. The engine E is an example of a driving source. The driving wheel T is an example of a wheel. Figures 1 to 16As shown, the power transmission device K has a clutch housing 2 formed with an input gear 1 that rotates by the driving force of the engine E of the vehicle, an output shaft 3 connected to the transmission M, a clutch member 4, a pressure member 5, a plurality of driving side clutch plates 6 and a plurality of driven side clutch plates 7, and a centrifugal clutch unit 9 having a weight member 10. It should be noted that in the figure, reference numeral 8 represents a fixing member, reference numeral S represents a clutch spring, reference numeral f represents a return spring, and reference numeral B represents a bolt. The input gear 1 is an example of an input member. The output shaft 3 is an example of an output member.

[0060] The input gear 1 is configured to rotate around the output shaft 3 when receiving the driving force (rotational force) transmitted from the engine E. The input gear 1 is connected to the clutch housing 2 by rivets or the like. Figure 4 , 5 As shown in FIG. 1 , the clutch housing 2 is formed in a cylindrical shape with one end opened. The clutch housing 2 rotates together with the input gear 1 by the driving force of the engine E.

[0061] like Figure 4 , 5 As shown, a plurality of cutouts 2a are formed in the entire circumference of the clutch housing 2. A plurality of drive-side clutch plates 6 are fitted in the cutouts 2a. That is, the clutch housing 2 holds a plurality of drive-side clutch plates 6. The drive-side clutch plates 6 are formed of a substantially annular plate. The drive-side clutch plates 6 are configured to be movable along the axial direction of the clutch housing 2 (i.e., the axial direction of the output shaft 3) and to be rotatable integrally with the clutch housing 2.

[0062] like Figure 2 As shown, the clutch member 4 is accommodated in the clutch housing 2. The clutch member 4 holds a plurality of driven side clutch plates 7 arranged alternately with the driving side clutch plates 6. The clutch member 4 is connected to the output shaft 3 that can rotate the driving wheel T via the transmission M of the vehicle. Figure 4 and Figure 5 As shown, the clutch member 4 includes a first clutch member 4a and a second clutch member 4b. The first clutch member 4a is engaged with the second clutch member 4b.

[0063] like Figure 4 and Figure 5As shown, the first clutch member 4a has an insertion hole 4ac formed in the center. The output shaft 3 is inserted into the insertion hole 4ac, and the splines formed on the insertion hole 4ac and the output shaft 3 are meshed with each other and connected in the rotation direction. That is, the first clutch member 4a is connected to the output shaft 3. The second clutch member 4b has an outer peripheral wall 4bc formed in an annular shape and a flange portion 4bb extending radially outward from the outer peripheral wall 4bc. A spline fitting portion 4ba is formed on the outer peripheral wall 4bc. The spline fitting portion 4ba has a concave and convex shape formed integrally on the outer peripheral wall 4bc and substantially the entire circumference. The groove of the spline fitting portion 4ba is installed with a passive side clutch plate 7 by spline fitting. That is, the second clutch member 4b holds the passive side clutch plate 7. The passive side clutch plate 7 is configured to be movable along the axial direction (i.e., the axial direction of the output shaft 3) of the clutch member 4 (e.g., the second clutch member 4b) and to be able to rotate integrally with the clutch member 4 (e.g., the first clutch member 4a and the second clutch member 4b). The second clutch member 4 b is configured to be movable in the axial direction of the output shaft 3 .

[0064] like Figure 4 As shown, the pressure member 5 is composed of a disc-shaped member having a flange portion 5a formed on the peripheral portion. The pressure member 5 is assembled to the clutch member 4. The pressure member 5 is arranged in a manner that allows it to approach or move away from the clutch member 4. The pressure member 5 is configured to enable the driving side clutch plate 6 and the passive side clutch plate 7 to be pressed into contact. The pressure member 5 is configured to enable the driving side clutch plate 6 and the passive side clutch plate 7 to be pressed into contact together with the clutch member 4. By pressing the driving side clutch plate 6 and the passive side clutch plate 7 into contact by the pressure member 5, the driving force of the engine E can be transmitted to the driving wheel W. That is, the driving side clutch plate 6 and the passive side clutch plate 7 are arranged in a stacked state between the flange portion 5a of the pressure member 5 and the flange portion 4bb of the second clutch member 4b. If the second clutch member 4b is moved in a direction approaching the pressure member 5 ( Figure 2 DR2 direction), the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other, and the rotational force of the clutch housing 2 is transmitted to the output shaft 3 via the second clutch member 4b and the first clutch member 4a. On the other hand, if the second clutch member 4b moves away from the pressure member 5 ( Figure 2 When the driven side clutch plate 6 and the driven side clutch plate 7 move in the direction of the arrow DR1), the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7 is released, and the first clutch member 4a and the second clutch member 4b no longer follow the rotation of the clutch housing 2, and no longer transmit the rotational force of the clutch housing 2 to the output shaft 3. The driving side clutch plate 6 and the driven side clutch plate 7 are arranged to be movable in the axial direction of the output shaft 3 relative to the second clutch member 4b.

[0065] In this way, when the driving side clutch plate 6 and the driven side clutch plate 7 are in pressure contact, the rotational force input to the clutch housing 2 (i.e., the driving force of the engine E) is transmitted to the driving wheel T side (i.e., the transmission M) via the output shaft 3. In addition, when the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is released, the rotational force input to the clutch housing 2 is not transmitted to the output shaft 3.

[0066] like Figure 2 As shown, the centrifugal clutch unit 9 has a structure that can be moved from the inner diameter side position (see Fig.14 ) to the outer diameter side (refer to Fig.16 ) The centrifugal clutch unit 9 is arranged on the opening side of the clutch housing 2 ( Figure 2 The centrifugal clutch unit 9 is arranged on the opposite side of the pressure member 5 across the driving side clutch plate 6 and the driven side clutch plate 7. Here, the centrifugal clutch unit 9 is arranged closer to the pressure member 5 than to the driving side clutch plate 6 and the driven side clutch plate 7. Figure 2 The centrifugal clutch unit 9 is located at the arrow DR1 direction side. When the weight member 10 is at the outer diameter side position, the driving side clutch plate 6 and the driven side clutch plate 7 are pressed into contact with each other to form a state in which the driving force of the engine E can be transmitted to the driving wheel T. The centrifugal clutch unit 9 is configured to apply a pressing force to the driving side clutch plate 6 and the driven side clutch plate 7 during the process of the weight member 10 moving from the inner diameter side position to the outer diameter side position. The centrifugal clutch unit 9 is configured to release the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7 when the weight member 10 is at the inner diameter side position, thereby cutting off the transmission of the driving force of the engine E to the driving wheel T. That is, the centrifugal clutch unit 9 is configured to release the pressing force applied to the driving side clutch plate 6 and the driven side clutch plate 7 when the weight member 10 is at the inner diameter side position, thereby cutting off the transmission of the driving force of the engine E to the driving wheel T.

[0067] like Figure 6 As shown, the centrifugal clutch unit 9 includes a plurality of weight members 10 , a holding member 11 that holds the weight members 10 so as to be movable between an inner diameter side position and an outer diameter side position, a pressing member 12 , and a plurality of biasing springs 13 .

[0068] like Figure 7~Figure 9 As shown, the weight member 10 includes a main body 10h, a weight member side cam surface K1 formed on the main body 10h, and a biasing spring 13 (see Figure 6 ) and a groove portion 10c formed in the main body portion 10h and capable of sliding relative to the slidable surface 11b of the holding member 11 (see Fig.13The weight member 10 is accommodated in the holding member 11. The weight member 10 is held at the inner diameter side position (see Fig.14 The weight member 10 is moved radially outward by the centrifugal force applied thereto, overcoming the biasing force of the biasing spring 13, and reaches the outer diameter side position (see Fig.16 ). When the weight member 10 moves from the inner diameter side position to the outer diameter side position, the clutch member 4 (here, the second clutch member 4b) moves toward the direction approaching the pressure member 5 ( Figure 2 The weight member 10 is configured so that the driving side clutch plate 6 and the driven side clutch plate 7 are pressed together via the pressing member 12 during the movement of the weight member 10 from the inner diameter side position to the outer diameter side position. It should be noted that the weight member 10 does not need to press together the driving side clutch plate 6 and the driven side clutch plate 7 via the pressing member 12 while starting to move from the inner diameter side position to the outer diameter side position. The driving side clutch plate 6 and the driven side clutch plate 7 may be pressed together via the pressing member 12 after the weight member 10 moves a predetermined distance from the inner diameter side position to the outer diameter side position.

[0069] like Fig.14 As shown in FIG. 1 , the weight member side cam surface K1 is provided in a manner that can contact with the later described pressing member side cam surface K2. The weight member side cam surface K1 is a portion that contacts the pressing member 12. Fig. 9 As shown, the weight member 10 has a first inclined surface 10a and a second inclined surface 10b whose inclination angle relative to the axial direction of the output shaft 3 is larger than that of the first inclined surface 10a on the weight member side cam surface K1. The first inclined surface 10a is located radially outward of the second inclined surface 10b. The first inclined surface 10a is a plane. The second inclined surface 10b is a plane. The inclination angle α of the first inclined surface 10a relative to the axial direction of the output shaft 3 is smaller than the inclination angle β of the second inclined surface 10b relative to the axial direction of the output shaft 3. In the present embodiment, the first inclined surface 10a and the second inclined surface 10b are continuous, but they can also be connected via a curved surface. In this way, the centrifugal clutch unit 9 has the first inclined surface 10a and the second inclined surface 10b at the portion of the weight member 10 where the weight member 10 and the pressing member 12 contact (here, the weight member side cam surface K1). When the engine speed increases by a predetermined speed and the weight member 10 moves a predetermined distance in the radial direction, the amount of movement of the pressing member 12 on the second inclined surface 10b in the axial direction of the output shaft 3 is smaller than the amount of movement of the pressing member 12 on the first inclined surface 10a in the axial direction of the output shaft 3. The thrust of the weight member 10 generated on the second inclined surface 10b is greater than the thrust of the weight member 10 generated on the first inclined surface 10a. The first inclined surface 10a is an example of the first region. The second inclined surface 10b is an example of the second region.

[0070] like Figure 2 As shown, the holding member 11 holds the weight member 10 in such a manner that the weight member 10 can move between an inner diameter side position and an outer diameter side position. Fig.13 As shown, the holding member 11 has an annular main body 11c, a wall 11a extending from the outer periphery of the main body 11c, and a sliding surface 11b on which the weight member 10 slides. One end of the biasing spring 13 contacts the wall 11a.

[0071] The pressing member 12 is provided in a manner capable of contacting the weight member 10. The pressing member 12 is configured to pass through the weight member 10 from the inner diameter side position (refer to Fig.14 ) to the outer diameter side (refer to Fig.16 ) and in the direction of pressing the driving side clutch plate 6 and the driven side clutch plate 7 into contact ( Fig.14 The pressing member 12 is configured to press the driving side clutch plate 6 and the driven side clutch plate 7. Figure 10~Figure 12 As shown, the crimping member 12 has an annular main body 12d, a plurality of crimping member side cam surfaces K2 formed on the entire circumference of the main body 12d, a pressing surface 12c formed on the surface opposite to the surface on which the crimping member side cam surface K2 is formed in the main body 12d, and a plurality of protrusions 12e formed on the entire circumference of the main body 12d. The crimping member 12 is fitted into the notch 2a of the clutch housing 2 (see Figure 4 ) and is mounted on the clutch housing 2. The pressing member 12 is provided so as to be movable in the axial direction of the clutch housing 2 (i.e., the axial direction of the output shaft 3). The pressing member 12 is provided so as to be engaged with the clutch housing 2 in the rotational direction and rotate together with the clutch housing 2.

[0072] like Fig.14 As shown in FIG. 1 , the cam surface K2 on the pressing member side is provided in a manner that can contact the cam surface K1 on the weight member side. The cam surface K2 on the pressing member side is a portion that contacts the weight member 10. Fig.12As shown, the crimping member 12 has a first inclined surface 12a and a second inclined surface 12b whose inclination angle relative to the axial direction of the output shaft 3 is larger than that of the first inclined surface 12a on the crimping member side cam surface K2. The first inclined surface 12a is located radially inward of the second inclined surface 12b. The first inclined surface 12a is a plane. The second inclined surface 12b is a plane. The inclination angle α of the first inclined surface 12a relative to the axial direction of the output shaft 3 is smaller than the inclination angle β of the second inclined surface 12b relative to the axial direction of the output shaft 3. The first inclined surface 12a is arranged in a manner that can contact the first inclined surface 10a of the cam surface K1 on the weight member side. The second inclined surface 12b is arranged in a manner that can contact the second inclined surface 10b of the cam surface K1 on the weight member side. In the present embodiment, the first inclined surface 12a and the second inclined surface 12b are continuous, but may also be connected via a curved surface. In this way, the centrifugal clutch unit 9 has a first inclined surface 12a and a second inclined surface 12b at a portion of the pressing member 12 where the weight member 10 contacts the pressing member 12 (here, the pressing member side cam surface K2). When the engine speed increases by a predetermined speed and the weight member 10 moves a predetermined distance in the radial direction, the amount of movement of the pressing member 12 on the second inclined surface 12b in the axial direction of the output shaft 3 is smaller than the amount of movement of the pressing member 12 on the first inclined surface 12a in the axial direction of the output shaft 3. The thrust of the weight member 10 generated on the second inclined surface 12b is greater than the thrust of the weight member 10 generated on the first inclined surface 12a. The first inclined surface 12a is an example of the first region. The second inclined surface 12b is an example of the second region.

[0073] When the weight member 10 is positioned from the inner diameter side (refer to Fig.14 ) to the outer diameter side (refer to Fig.16 ) is transmitted to the pressing member 12 via the cam surface K1 on the weight member side and the cam surface K2 on the pressing member side. As a result, the pressing member 12 moves in the direction of pressing the driving side clutch plate 6 and the driven side clutch plate 7 ( Fig.14 Move in the direction of arrow DR2. Figure 14~Figure 16 As shown, the weight member side cam surface K1 and the pressure contact member side cam surface K2 are configured so that the weight member 10 is located from the inner diameter side position (refer to Fig.14 ) to the outer diameter side (refer to Fig.16) in the process of movement, the inclined surface that functions as a cam surface is changed from the first inclined surface 10a and the first inclined surface 12a to the second inclined surface 10b and the second inclined surface 12b. In the process of the weight member 10 moving from the inner diameter side position to the outer diameter side position, until the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 starts, the first inclined surface 10a and the first inclined surface 12a function as cam surfaces, and after the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 starts, the second inclined surface 10b and the second inclined surface 12b function as cam surfaces.

[0074] like Fig.14 As shown, in the process of the weight member 10 moving from the inner diameter side position to the outer diameter side position, until the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 begins, the first inclined surface 10a and the first inclined surface 12a contact each other and slide in the weight member side cam surface K1 and the pressure contact member side cam surface K2. As a result, the thrust generated when the weight member 10 moves from the inner diameter side position to the outer diameter side position is transmitted to the pressure contact member 12 via the first inclined surface 10a and the first inclined surface 12a. In addition, the pressure contact member 12 moves in the direction of causing the driving side clutch plate 6 and the driven side clutch plate 7 to be pressed ( Fig.14 At this time, the thrust of the weight member 10 transmitted to the pressing member 12 is relatively small, but the movement amount of the pressing member 12 in the axial direction of the output shaft 3 is relatively large.

[0075] And, if Fig.15 As shown, if the counterweight member 10 moves further from the inner diameter side position to the outer diameter side position and the pressing contact between the driving side clutch plate 6 and the driven side clutch plate 7 begins, the boundary between the first inclined surface 10a and the second inclined surface 10b of the counterweight member side cam surface K1 and the boundary between the first inclined surface 12a and the second inclined surface 12b of the pressing member side cam surface K2 are in contact with each other.

[0076] And, if Fig.16 As shown, if the weight member 10 moves further from the inner diameter side position to the outer diameter side position, then in the weight member side cam surface K1 and the pressure contact member side cam surface K2, after the pressure contact between the driving side clutch plate 6 and the passive side clutch plate 7 begins, the second inclined surface 10b and the second inclined surface 12b contact each other and slide. As a result, the thrust generated when the weight member 10 moves from the inner diameter side position to the outer diameter side position is transmitted to the pressure contact member 12 via the second inclined surface 10b and the second inclined surface 12b. In addition, the pressure contact member 12 moves in the direction of causing the driving side clutch plate 6 and the passive side clutch plate 7 to be pressed ( Fig.16 At this time, the amount of movement of the pressing member 12 in the axial direction of the output shaft 3 is relatively small, but the thrust of the weight member 10 transmitted to the pressing member 12 is relatively large.

[0077] It should be noted that the structure may also be such that, during the process of the engine E's speed increasing, the weight member 10 and the pressing member 12, after the first inclined surface 10a and the first inclined surface 12a contact each other (i.e., contact each other in the first area), contact each other with the second inclined surface 10b and the second inclined surface 12b (i.e., contact each other in the second area). In addition, the structure may also be such that, when the engine E's speed is lower than the speed at which the driving side clutch plate 6 and the driven side clutch plate 7 start to be pressed, the weight member 10 and the pressing member 12, after the first inclined surface 10a and the first inclined surface 12a contact each other (i.e., contact each other in the first area), contact each other with the second inclined surface 10b and the second inclined surface 12b (i.e., contact each other in the second area). It can also be configured such that when the rotation speed of the engine E is lower than the rotation speed when the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is completed, the weight member 10 and the pressure contact member 12 are in contact with each other at the first inclined surface 10a and the first inclined surface 12a (i.e., in contact with each other at the first area), and then in contact with each other at the second inclined surface 10b and the second inclined surface 12b (i.e., in contact with each other at the second area). It should be noted that in the area where the rotation speed of the engine E is higher than the rotation speed of the engine E when the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is completed, the driving side clutch plate 6 and the driven side clutch plate 7 remain in pressure contact.

[0078] Fig.39 Graph 1 is a graph showing the relationship between the rotation speed of the engine E and the amount of movement of the pressing member 12 in the axial direction of the output shaft 3. Fig.39 In FIG. 1 , the horizontal axis represents the rotation speed of the engine E, and the vertical axis represents the movement amount of the pressing member 12 in the axial direction of the output shaft 3 . Fig.40 : is a graph showing the relationship between the rotation speed of the engine E and the thrust of the weight member 10. Fig.40 In FIG. 1 , the horizontal axis represents the rotation speed of the engine E, and the vertical axis represents the thrust of the weight member 10. Fig.39 and Fig.40 In the figure, the speed EID indicates the speed of the engine E in the idle state, the speed EC indicates the speed of the engine E when the pressure contact between the driving side clutch plate 6 and the passive side clutch plate 7 starts (here, when the inclined surface acting as the cam surface changes from the first inclined surface 10a and the first inclined surface 12a to the second inclined surface 10b and the second inclined surface 12b), the speed EIN indicates the speed of the engine E when the driving force of the engine E starts to be transmitted to the driving wheel T, the speed EST indicates the speed of the engine E when the driving side clutch plate 6 and the passive side clutch plate 7 are completely pressure contacted (when the pressure contact between the driving side clutch plate 6 and the passive side clutch plate 7 is completed), and the speed EE indicates the speed of the engine E when the counterweight member 10 reaches the outer diameter side position. Fig.39 and Fig.40As shown, when the rotation speed of the engine E is the rotation speed EID~the rotation speed EC, the displacement LM1 of the pressing member 12 in the axial direction of the output shaft 3 is relatively large, and the thrust FM1 of the weight member 10 is relatively small. On the other hand, when the rotation speed of the engine E is the rotation speed EC~the rotation speed EE, the displacement LM2 of the pressing member 12 in the axial direction of the output shaft 3 is relatively small (displacement LM2<displacement LM1), and the thrust FM2 of the weight member 10 is relatively large (thrust FM2>thrust FM1).

[0079] As described above, according to the power transmission device K of this embodiment, the centrifugal clutch unit 9 has the first inclined surfaces 10a, 12a and the second inclined surfaces 10b, 12b having an inclination angle larger than the first inclined surfaces 10a, 12a with respect to the axial direction of the output shaft 3 on the weight member side cam surface K1. According to the above scheme, the amount of movement of the pressure contact member 12 in the axial direction of the output shaft 3 and the thrust of the weight member 10 required can be ensured according to the operating state.

[0080] In the power transmission device K of the present embodiment, the weight member 10 and the pressing member 12 may contact each other at the second inclined surfaces 10b and 12b after the first inclined surfaces 10a and 12a contact each other during the increase in the rotation speed of the engine E. According to the above scheme, the axial movement of the pressing member 12 can be increased first, and then the thrust of the weight member 10 can be increased.

[0081] In the power transmission device K of the present embodiment, the first inclined surface 10a and the second inclined surface 10b may be connected via a curved surface, and the first inclined surface 12a and the second inclined surface 12b may be connected via a curved surface. According to the above scheme, since the first inclined surface 10a and the second inclined surface 10b are connected via a curved surface, and the first inclined surface 12a and the second inclined surface 12b are connected via a curved surface, the contact portion between the weight member 10 and the pressing member 12 can be smoothly changed from the first inclined surfaces 10a and 12a to the second inclined surfaces 10b and 12b.

[0082] In the power transmission device K of the present embodiment, when the rotation speed of the engine E is lower than the rotation speed when the driving side clutch plate 6 and the driven side clutch plate 7 start to be pressed, the weight member 10 and the pressing member 12 may contact each other at the second inclined surfaces 10b and 12b after contacting each other at the first inclined surfaces 10a and 12a. According to the above scheme, since the contact portion between the weight member 10 and the pressing member 12 is changed from the first inclined surfaces 10a and 12a to the second inclined surfaces 10b and 12b at a rotation speed lower than the rotation speed when the driving side clutch plate 6 and the driven side clutch plate 7 start to be pressed, it is possible to ensure the axial movement amount of the pressing member 12 in the output shaft 3 before the driving side clutch plate 6 and the driven side clutch plate 7 start to be pressed, and it is possible to ensure the thrust required by the weight member 10 after the driving side clutch plate 6 and the driven side clutch plate 7 start to be pressed.

[0083] In the power transmission device K of the present embodiment, when the rotation speed of the engine E is lower than the rotation speed when the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is completed, the weight member 10 and the pressure contact member 12 may contact each other at the second inclined surfaces 10b and 12b after contacting each other at the first inclined surfaces 10a and 12a. According to the above scheme, since the contact portion between the weight member 10 and the pressure contact member 12 is changed from the first inclined surfaces 10a and 12a to the second inclined surfaces 10b and 12b at a rotation speed lower than the rotation speed when the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is completed, the required amount of movement of the pressure contact member 12 in the axial direction of the output shaft 3 can be ensured before the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is completed, and the required thrust of the weight member 10 can be ensured after the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is completed.

[0084] In the power transmission device K of the present embodiment, the weight member 10 may have a sliding surface 10d that can slide relative to the retaining member 11, the weight member 10 may have a first inclined surface 10a and a second inclined surface 10b at a portion where the weight member 10 and the pressing member 12 contact (e.g., the weight member side cam surface K1), and the pressing member 12 may have a first inclined surface 12a and a second inclined surface 12b at a portion where the weight member 10 and the pressing member 12 contact (e.g., the pressing member side cam surface K2). According to the above scheme, the weight member 10 having the sliding surface 10d that can slide relative to the retaining member 11 can be well applied.

[0085] In addition, according to the power transmission device K of the present embodiment, the centrifugal clutch unit 9 has the first inclined surfaces 10a, 12a as the first region and the second inclined surfaces 10b, 12b as the second region where the amount of movement of the pressing member 12 in the axial direction of the output shaft 3 is smaller than that in the first region. According to the above scheme, the amount of movement of the pressing member 12 in the axial direction of the output shaft 3 and the thrust of the weight member 10 required can be ensured according to the operating state. It should be noted that the thrust of the weight member 10 in the second region is greater than the thrust of the weight member 10 in the first region.

[0086] In the power transmission device K of the present embodiment, the weight member 10 and the pressing member 12 may contact each other at the second inclined surfaces 10b and 12b as the second area after the first inclined surfaces 10a and 12a as the first area contact each other during the increase in the rotation speed of the engine E. According to the above scheme, the axial movement amount of the pressing member 12 can be increased first, and then the thrust of the weight member 10 can be increased.

[0087] In the power transmission device K of the present embodiment, the first region may be a first inclined surface 10a, 12a formed of a plane, the second region may be a second inclined surface 10b, 12b formed of a plane, and the weight member 10 and the pressing member 12 may be configured to be in contact with each other at the first inclined surface 10a, 12a and the second inclined surface 10b, 12b. According to the above scheme, the movement amount of the pressing member 12 and the thrust of the weight member 10 can be smoothly changed in the first region and the second region.

[0088] <Second Embodiment>

[0089] like Figures 21 to 23 As shown, a power transmission device 200K of the second embodiment includes a centrifugal clutch unit 209 having a weight member 14. It is to be noted that the same components as those of the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

[0090] like Fig.21 As shown, the centrifugal clutch unit 209 includes a plurality of weight members 14 , a holding member 11 that holds the weight members 14 so as to be movable between an inner diameter side position and an outer diameter side position, a pressing member 15 , and a plurality of biasing springs 13 .

[0091] like Figure 18~Figure 20 As shown, the weight member 14 is configured to be able to move from the inner diameter side position (see Fig.21 ) to the outer diameter side (refer to Fig.23The weight member 14 includes a main body 14h, a spherical member 14a that can move relative to the holding member 11 while making point contact or rolling, a holding hole 14f formed in the main body 14h and holding the spherical member 14a, and a groove 14b formed in the main body 14h and holding the biasing spring 13. The spherical member 14a is an example of a contact portion.

[0092] The pressing member 15 is provided so as to be in contact with the weight member 14. The pressing member 15 is configured to be pressed from the inner diameter side position (see Fig.21 ) to the outer diameter side (refer to Fig.23 ) moves in a direction in which the driving side clutch plate 6 and the driven side clutch plate 7 are pressed into contact ( Fig.21 The pressing member 15 is configured to press the driving side clutch plate 6 and the driven side clutch plate 7. Fig.21 As shown, the crimping member 15 has a crimping member side cam surface 200K2 formed over the entire circumference of the main body portion 12d.

[0093] like Fig.21 As shown, the crimping member side cam surface 200K2 is arranged in a manner that can contact the spherical member 14a. The crimping member side cam surface 200K2 is the portion that contacts the counterweight member 14. The crimping member 15 has a first inclined surface 15a and a second inclined surface 15b whose inclination angle relative to the axial direction of the output shaft 3 is larger than that of the first inclined surface 15a on the crimping member side cam surface 200K2. The first inclined surface 15a is located radially inward of the second inclined surface 15b. The first inclined surface 15a is a plane. The second inclined surface 15b is a curved surface. The first inclined surface 15a and the second inclined surface 15b are arranged in a manner that can contact the spherical member 14a. In the present embodiment, the first inclined surface 15a and the second inclined surface 15b are continuous, but may also be connected via a curved surface. When the engine speed increases by a predetermined speed and the weight member 10 moves a predetermined distance in the radial direction, the amount of movement of the pressing member 15 on the second inclined surface 15b in the axial direction of the output shaft 3 is smaller than the amount of movement of the pressing member 15 on the first inclined surface 15a in the axial direction of the output shaft 3. In addition, when the engine speed increases by a predetermined speed and the weight member 10 moves a predetermined distance in the radial direction, the thrust of the weight member 14 generated on the second inclined surface 15b is greater than the thrust of the weight member 14 generated on the first inclined surface 15a. The first inclined surface 15a is an example of the first region. The second inclined surface 12b is an example of the second region.

[0094] The weight member 14 is positioned from the inner diameter side (refer to Fig.21 ) to the outer diameter side (refer to Fig.23) is transmitted to the pressing member 15 via the spherical member 14a and the pressing member side cam surface 200K2. As a result, the pressing member 15 moves in the direction of pressing the driving side clutch plate 6 and the driven side clutch plate 7 ( Fig.21 Move in the direction of arrow DR2. Figure 21~Figure 23 As shown, the spherical member 14a and the pressing member side cam surface 20K2 are configured so that the weight member 14 is positioned from the inner diameter side (see Fig.21 ) to the outer diameter side (refer to Fig.23 ), the inclined surface that functions as a cam surface relative to the spherical member 14a is changed from the first inclined surface 15a to the second inclined surface 15b during the movement of the weight member 14 from the inner diameter side position to the outer diameter side position, until the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 starts, the first inclined surface 15a functions as a cam surface, and after the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 starts, the second inclined surface 15b functions as a cam surface.

[0095] like Fig.21 As shown, during the movement of the weight member 14 from the inner diameter side position to the outer diameter side position, until the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 begins, the spherical member 14a and the first inclined surface 15a contact each other and slide in the spherical member 14a and the pressure contact member side cam surface K2. As a result, the thrust generated when the weight member 14 moves from the inner diameter side position to the outer diameter side position is transmitted to the pressure contact member 15 via the spherical member 14a and the first inclined surface 15a. In addition, the pressure contact member 15 moves in the direction of causing the driving side clutch plate 6 and the driven side clutch plate 7 to be pressure contacted ( Fig.21 At this time, the thrust of the weight member 14 transmitted to the crimping member 15 is relatively small, but the amount of movement of the crimping member 15 in the axial direction of the output shaft 3 is relatively large.

[0096] And, if Fig. 22 As shown, if the counterweight member 14 moves further from the inner diameter side position to the outer diameter side position and the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 begins, the boundary between the first inclined surface 15a and the second inclined surface 15b of the spherical member 14a and the pressure contact member side cam surface 200K2 is in contact with each other.

[0097] And, if Fig.23As shown, if the weight member 14 moves further from the inner diameter side position to the outer diameter side position, then in the spherical member 14a and the pressing member side cam surface 200K2, after the pressing contact between the driving side clutch plate 6 and the passive side clutch plate 7 begins, the spherical member 14a and the second inclined surface 15b contact each other and slide. As a result, the thrust generated when the weight member 14 moves from the inner diameter side position to the outer diameter side position is transmitted to the pressing member 15 via the spherical member 14a and the second inclined surface 15b. In addition, the pressing member 15 moves in the direction of pressing the driving side clutch plate 6 and the passive side clutch plate 7 ( Fig.23 At this time, the amount of movement of the pressing member 15 in the axial direction of the output shaft 3 is relatively small, but the thrust of the weight member 14 transmitted to the pressing member 15 is relatively large.

[0098] In the power transmission device 200K of the present embodiment, the weight member 14 has a spherical member 14a that can move while making point contact with respect to the retaining member 11, and the pressing member 15 has a first inclined surface 15a and a second inclined surface 15b on the pressing member side cam surface 200K2. According to the above scheme, the weight member 14 having the spherical member 14a that can move while making point contact with respect to the retaining member 11 can be well used.

[0099] <Third Embodiment>

[0100] like Figures 27 to 29 As shown, a power transmission device 300K of the third embodiment includes a centrifugal clutch unit 309 having a weight member 16. Note that the same components as those of the first and second embodiments are denoted by the same reference numerals, and detailed description thereof will be omitted.

[0101] like Figure 24~Figure 26 As shown, the weight member 16 is configured to be able to move from the inner diameter side position (see Fig. 27 ) to the outer diameter side (refer to Fig.29 ) moves. The weight member 16 has a main body 16h, a pair of rolling members 16a, 16b that can move relative to the retaining member 11 while making point contact or rolling, a retaining hole 16f formed in the main body 16h and retaining the rolling members 16a, 16b, and a groove 16c formed in the main body 16h and retaining the biasing spring 13. The rolling member 16a is arranged in a manner that can contact the crimping member side cam surface 200K2. The rolling member 16b is arranged in a manner that can contact the retaining member 11. The rolling members 16a, 16b are retained in the retaining hole 16f in a manner that contacts each other. The rolling members 16a, 16b are an example of a contact portion.

[0102] The weight member 16 is positioned from the inner diameter side (refer to Fig. 27 ) to the outer diameter side (refer to Fig.29 ) is transmitted to the pressing member 15 via the rolling members 16a, 16b and the pressing member side cam surface 200K2. As a result, the pressing member 15 moves in the direction ( ) in which the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other. Fig. 27 Move in the direction of arrow DR2. Figure 27~Figure 29 As shown, the rolling member 16a and the pressing member side cam surface 20K2 are configured so that the weight member 16 is located from the inner diameter side position (refer to Fig. 27 ) to the outer diameter side (refer to Fig.29 ) during the movement of the weight member 16, the inclined surface that functions as a cam surface relative to the rolling member 16a is changed from the first inclined surface 15a to the second inclined surface 15b. During the movement of the weight member 16 from the inner diameter side position to the outer diameter side position, the first inclined surface 15a functions as a cam surface until the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 begins, and the second inclined surface 15b functions as a cam surface after the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 begins. It should be noted that the functions and effects of the third embodiment are the same as those of the second embodiment.

[0103] 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.

[0104] <Fourth Embodiment>

[0105] In the first embodiment described above, the centrifugal clutch unit 9 is arranged on the opening side of the clutch housing 2 ( Figure 2 For example, in the power transmission device 400K of the fourth embodiment, as shown in FIG. Figure 30~Figure 32 As shown, the centrifugal clutch unit 9 may also be arranged on the bottom side of the clutch housing 2 ( Fig.30 The centrifugal clutch unit 9 is arranged on the opposite side of the pressure member 5 across the driving side clutch plate 6 and the driven side clutch plate 7. Here, the centrifugal clutch unit 9 is arranged closer to the clutch member 4 (more specifically, the second clutch member 4b). Fig.30 On the side in the direction of arrow DR2.

[0106] <Fifth Embodiment>

[0107] In the second embodiment described above, the centrifugal clutch unit 209 is arranged on the opening side of the clutch housing 2 ( Fig.21 For example, in the power transmission device 500K of the fifth embodiment, as shown in FIG. Figure 33~Figure 35As shown, the centrifugal clutch unit 209 may also be arranged on the bottom side of the clutch housing 2 ( Fig.33 The centrifugal clutch unit 209 is arranged on the opposite side of the pressure member 5 across the driving side clutch plate 6 and the driven side clutch plate 7. Here, the centrifugal clutch unit 209 is arranged closer to the clutch member 4 (more specifically, the second clutch member 4b). Fig.33 On the side in the direction of arrow DR2.

[0108] <Sixth Implementation Method>

[0109] In the third embodiment described above, the centrifugal clutch unit 309 is arranged on the opening side ( Fig. 27 For example, in the power transmission device 600K of the sixth embodiment, as shown in FIG. Figure 36~Figure 38 As shown, the centrifugal clutch unit 309 may also be arranged on the bottom side of the clutch housing 2 ( Fig.36 The centrifugal clutch unit 309 is arranged on the opposite side of the pressure member 5 across the driving side clutch plate 6 and the driven side clutch plate 7. Here, the centrifugal clutch unit 309 is arranged closer to the clutch member 4 (more specifically, the second clutch member 4b). Fig.36 On the side in the direction of arrow DR2.

[0110] In the above-mentioned embodiment, the centrifugal clutch unit 9 has the first inclined surface 10a and the second inclined surface 10b on the weight member side cam surface K1, and has the first inclined surface 12a and the second inclined surface 12b on the pressing member side cam surface K2, but the present invention is not limited thereto. The centrifugal clutch unit 9 may also have the first inclined surface 10a and the second inclined surface 10b on the weight member side cam surface K1, and not have the first inclined surface 12a and the second inclined surface 12b on the pressing member side cam surface K2. In addition, the centrifugal clutch unit 9 may not have the first inclined surface 10a and the second inclined surface 10b on the weight member side cam surface K1, and may have the first inclined surface 12a and the second inclined surface 12b on the pressing member side cam surface K2.

[0111] In the above-mentioned embodiment, the first inclined surface 10a, the second inclined surface 10b, the first inclined surface 12a, and the second inclined surface 12b are respectively plane surfaces, but they may also be curved surfaces. In addition, when at least one of the first inclined surface 10a and the second inclined surface 10b is a curved surface, it is preferred that the first inclined surface 10a and the second inclined surface 10b be directed outward (for example, toward the Fig.14 In the case where at least one of the first inclined surface 12a and the second inclined surface 12b is a curved surface, it is preferred to face outward (for example, toward Fig.14 The shape of the convex surface is (in the direction of arrow DR1).

[0112] In the above-mentioned embodiment, the weight member 10 has a first inclined surface 10a and a second inclined surface 10b having an inclination angle larger than that of the first inclined surface 10a with respect to the axial direction of the output shaft 3 on the weight member side cam surface K1, but the present invention is not limited thereto. The weight member 10 may also have a third inclined surface having an inclination angle smaller than that of the first inclined surface 10a with respect to the axial direction of the output shaft 3 on the radially outer side than the first inclined surface 10a. In addition, the weight member 10 may also have a fourth inclined surface having an inclination angle larger than that of the second inclined surface 10b with respect to the axial direction of the output shaft 3 on the radially inner side than the second inclined surface 10b.

[0113] In the above-mentioned embodiment, the crimping member 12 has a first inclined surface 12a and a second inclined surface 12b with a larger inclination angle relative to the axial direction of the output shaft 3 than the first inclined surface 12a on the crimping member side cam surface K2, but is not limited thereto. The crimping member 12 may also have a third inclined surface with a smaller inclination angle relative to the axial direction of the output shaft 3 than the first inclined surface 12a at a radially inner side than the first inclined surface 12a. In addition, the crimping member 12 may also have a fourth inclined surface with a larger inclination angle relative to the axial direction of the output shaft 3 than the second inclined surface 12b at a radially outer side than the second inclined surface 12b.

[0114] In the above-mentioned embodiment, the crimping member 15 has a first inclined surface 15a and a second inclined surface 15b having an inclination angle with respect to the axial direction of the output shaft 3 greater than that of the first inclined surface 15a on the crimping member side cam surface 200K2, but is not limited thereto. The crimping member 15 may also have a third inclined surface with an inclination angle with respect to the axial direction of the output shaft 3 smaller than that of the first inclined surface 15a at a radially inner side than the first inclined surface 15a. In addition, the crimping member 15 may also have a fourth inclined surface with an inclination angle with respect to the axial direction of the output shaft 3 greater than that of the second inclined surface 15b at a radially outer side than the second inclined surface 15b.

[0115] In the above-mentioned embodiment, all the passive side clutch plates 7 are held by the clutch member 4 (e.g., the second clutch member 4b), but the present invention is not limited thereto. For example, a part of the passive side clutch plates 7 may be held by the clutch member 4 (e.g., the second clutch member 4b), and another part of the passive side clutch plates 7 may be held by the pressure member 5. In this case, the other part of the passive side clutch plates 7 is configured to be movable along the axial direction of the pressure member 5 (i.e., the axial direction of the output shaft 3) and to be rotatable integrally with the pressure member 5.

[0116] In each of the above-mentioned embodiments, the engine E is used as the driving source, but the driving source is not limited to the engine E, and may be, for example, an electric motor or the like.

[0117] The power transmission device of each embodiment described above can be applied to various multi-plate clutch type power transmission devices such as automobiles, three-wheel or four-wheel ATVs, or general-purpose machines in addition to motorcycles.

[0118] Description of Reference Numerals

[0119] 1 Input gear (input component)

[0120] 2 Clutch housing

[0121] 3 Output shaft (output component)

[0122] 4 Clutch components

[0123] 4a First clutch member

[0124] 4b Second clutch member

[0125] 5 Pressure components

[0126] 6 Drive side clutch plate

[0127] 7 Passive side clutch plate

[0128] 9 Centrifugal clutch unit

[0129] 10 Counterweight component

[0130] 10a First inclined surface

[0131] 10b Second inclined surface

[0132] 11. Retaining member

[0133] 12 Crimping components

[0134] 12a First inclined surface

[0135] 12b Second inclined surface

[0136] 14 Counterweight component

[0137] 14a Spherical member (contact portion)

[0138] 15 Crimping components

[0139] 15a First inclined surface

[0140] 15b Second inclined surface

[0141] 16 Counterweight component

[0142] 16a, 16b rolling element (contact portion)

[0143] K Power transmission device

[0144] K1 Cam surface on the side of the weight component

[0145] K2 Cam surface on the crimping member side.

Claims

1. A power transmission device comprising: A clutch member is housed in a clutch housing that rotates together with an input member that rotates by a driving force of a driving source and holds a plurality of driving-side clutch plates, and is connected to an output member that can rotate a wheel; a pressure member disposed in a manner capable of approaching or moving away from the clutch member and capable of pressing a plurality of driven-side clutch plates alternately arranged with the driving-side clutch plates and the plurality of driving-side clutch plates; as well as The centrifugal clutch unit comprises a weight member and a pressing member, wherein the weight member can be moved from an inner diameter side position to an outer diameter side position by the centrifugal force accompanying the rotation of the clutch housing, and the pressing member is arranged in a manner capable of contacting the weight member, and the weight member is moved from the inner diameter side position to the outer diameter side position to move in a direction in which the driving side clutch plate and the passive side clutch plate are pressed against each other, and the centrifugal clutch unit can press the driving side clutch plate and the passive side clutch plate against each other when the weight member is in the outer diameter side position to form a state in which the driving force of the driving source can be transmitted to the wheel, and when the weight member is in the inner diameter side position, the pressing force between the driving side clutch plate and the passive side clutch plate is released to cut off the transmission of the driving force of the driving source to the wheel. The weight member is configured to press the driving side clutch plate and the driven side clutch plate together via the pressing member during the movement of the weight member from the inner diameter side position to the outer diameter side position. The centrifugal clutch unit includes a first inclined surface and a second inclined surface having a larger inclination angle than the first inclined surface with respect to the axial direction of the output member at a portion where the weight member and the pressure contact member contact each other.

2. The power transmission device according to claim 1, In a process where the rotation speed of the driving source increases, the weight member and the pressing member come into contact with each other at the second inclined surface after coming into contact with each other at the first inclined surface.

3. The power transmission device according to claim 1 or 2, The first inclined surface and the second inclined surface are connected via a curved surface.

4. The power transmission device according to claim 1 or 2, When the rotation speed of the driving source is lower than the rotation speed when the driving side clutch plate and the driven side clutch plate start to come into pressure contact, the weight member and the pressure contact member come into contact with each other at the second inclined surface after coming into contact with each other at the first inclined surface.

5. The power transmission device according to claim 1 or 2, When the rotation speed of the driving source is lower than the rotation speed when the pressure contact between the driving side clutch plate and the driven side clutch plate is completed, the weight member and the pressure contact member contact each other at the second inclined surface after contacting each other at the first inclined surface.

6. The power transmission device according to claim 1 or 2, The centrifugal clutch unit includes a holding member that holds the weight member so that the weight member can move between the inner diameter side position and the outer diameter side position. The weight member has a sliding surface that can slide relative to the holding member, The weight member has the first inclined surface and the second inclined surface at a portion where the weight member and the pressing member contact each other. The pressing member has the first inclined surface and the second inclined surface at a portion where the weight member and the pressing member are in contact.

7. The power transmission device according to claim 1 or 2, The centrifugal clutch unit includes a holding member that holds the weight member so that the weight member can move between the inner diameter side position and the outer diameter side position. The weight member has a contact portion that can move relative to the holding member while making point contact or rolling. The pressing member has the first inclined surface and the second inclined surface at a portion where the weight member and the pressing member are in contact.

8. A power transmission device comprising: A clutch member is housed in a clutch housing that rotates together with an input member that rotates by a driving force of a driving source and holds a plurality of driving-side clutch plates, and is connected to an output member that can rotate a wheel; a pressure member disposed in a manner capable of approaching or moving away from the clutch member and capable of pressing a plurality of driven-side clutch plates alternately arranged with the driving-side clutch plates and the plurality of driving-side clutch plates; as well as The centrifugal clutch unit comprises a weight member and a pressing member, wherein the weight member can be moved from an inner diameter side position to an outer diameter side position by the centrifugal force accompanying the rotation of the clutch housing, and the pressing member is arranged in a manner capable of contacting the weight member, and the weight member is moved from the inner diameter side position to the outer diameter side position to move in a direction in which the driving side clutch plate and the passive side clutch plate are pressed against each other, and the centrifugal clutch unit can press the driving side clutch plate and the passive side clutch plate against each other when the weight member is in the outer diameter side position to form a state in which the driving force of the driving source can be transmitted to the wheel, and when the weight member is in the inner diameter side position, the pressing force between the driving side clutch plate and the passive side clutch plate is released to cut off the transmission of the driving force of the driving source to the wheel. The weight member is configured to press the driving side clutch plate and the driven side clutch plate together via the pressing member during the movement of the weight member from the inner diameter side position to the outer diameter side position. The centrifugal clutch unit includes a first region in a portion of at least one of the weight member and the pressing member where the weight member and the pressing member are in contact, and a second region where the amount of movement of the pressing member in the axial direction of the output member is smaller than that of the first region.

9. The power transmission device according to claim 8, During the process of increasing the rotation speed of the driving source, the weight member and the pressing member come into contact with each other at the second region after coming into contact with each other at the first region.

10. The power transmission device according to claim 8 or 9, The first region is a first inclined surface consisting of a plane, The second region is a second inclined surface consisting of a plane, The weight member and the pressing member are configured to be able to contact each other at the first inclined surface and the second inclined surface.

11. A power transmission device comprising: A clutch member is housed in a clutch housing that rotates together with an input member that rotates by a driving force of a driving source and holds a plurality of driving-side clutch plates, and is connected to an output member that can rotate a wheel; a pressure member disposed in a manner capable of approaching or moving away from the clutch member and capable of pressing a plurality of driven-side clutch plates alternately arranged with the driving-side clutch plates and the plurality of driving-side clutch plates; as well as The centrifugal clutch unit comprises a weight member and a pressing member, wherein the weight member can be moved from an inner diameter side position to an outer diameter side position by the centrifugal force accompanying the rotation of the clutch housing, and the pressing member is arranged in a manner capable of contacting the weight member, and the weight member is moved from the inner diameter side position to the outer diameter side position to move in a direction in which the driving side clutch plate and the passive side clutch plate are pressed against each other, and the centrifugal clutch unit can press the driving side clutch plate and the passive side clutch plate against each other when the weight member is in the outer diameter side position to form a state in which the driving force of the driving source can be transmitted to the wheel, and when the weight member is in the inner diameter side position, the pressing force between the driving side clutch plate and the passive side clutch plate is released to cut off the transmission of the driving force of the driving source to the wheel. The weight member is configured to press the driving side clutch plate and the driven side clutch plate together via the pressing member during the movement of the weight member from the inner diameter side position to the outer diameter side position. The centrifugal clutch unit includes a first region at a portion of at least one of the weight member and the pressure contact member where the weight member and the pressure contact member are in contact, and a second region where the thrust of the weight member is greater than the first region.

12. The power transmission device according to claim 11, During the process of increasing the rotation speed of the driving source, the weight member and the pressing member come into contact with each other at the second region after coming into contact with each other at the first region.

13. The power transmission device according to claim 11 or 12, The first region is a first inclined surface consisting of a plane, The second region is a second inclined surface consisting of a plane, The weight member and the pressing member are configured to be able to contact each other at the first inclined surface and the second inclined surface.

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