Power transmission device

Abstract

Provided is a power transmission device capable of preventing an unintended sudden power transmission at a non-intended timing due to an inadvertent operation of a crimping assist cam at the start of a vehicle, in a vehicle equipped with a centrifugal clutch unit. In a process in which a counterweight member (10) of the centrifugal clutch unit (9) moves from an inner diameter side position to an outer diameter side position, and the transmission torque from an input gear (1) to an output shaft (3) increases, there are a first torque region (α1) that restricts the operation of the crimping assist cam, and a second torque region (α2) that permits the operation of the crimping assist cam.

Description

[0001] This application is a divisional application of the application with application number 202080099670.7, filed on October 11, 2022, and with the title “Power transmission device”. TECHNICAL FIELD

[0002] The present application relates to a power transmission device capable of arbitrarily transmitting or cutting off the transmission of a rotational force of an input member to an output member. BACKGROUND

[0003] Generally, a power transmission device provided in a two-wheeled motor vehicle is used to arbitrarily transmit or cut off the transmission of a driving force of an engine to a transmission and drive wheels, and has an input member linked to the engine side, an output member linked to the transmission and drive wheels side, a clutch member linked to the output member, and a pressure member capable of approaching or departing from the clutch member, and is configured to transmit the power by causing the pressure member to approach the clutch member to press the driving-side clutch plate and the driven-side clutch plate, and cut off the transmission of the power by causing the pressure member to depart from the clutch member to release the pressing force of the driving-side clutch plate and the driven-side clutch plate.

[0004] As a conventional power transmission device, for example, as disclosed in Patent Literature 1, a centrifugal clutch unit provided with a counterweight member that is moved from an inner diameter side position to an outer diameter side position of a groove portion by centrifugal force accompanying rotation of a clutch housing, thereby being capable of pressing the driving-side clutch plate and the driven-side clutch plate, is proposed. According to this conventional power transmission device, the centrifugal force is applied to the counterweight member by the rotation of the clutch housing accompanying the driving of the engine, and the driving-side clutch plate and the driven-side clutch plate are pressed to transmit the driving force of the engine to the wheels.

[0005] In addition, according to the above-described conventional power transmission device, since the pressing auxiliary cam for increasing the pressing force of the driving-side clutch plate and the driven-side clutch plate when becoming a state in which the rotational force input to the input member can be transmitted to the output member is provided, when the driver performs clutch operation to press the driving-side clutch plate and the driven-side clutch plate, the operation force can be reduced to smoothly transmit the power.

[0006] PRIOR ART DOCUMENTS

[0007] PATENT LITERATURE

[0008] Patent Literature 1: International Publication No. 2013 / 183588 SUMMARY

[0009] PROBLEMS TO BE SOLVED BY THE INVENTION

[0010] However, the above-described conventional power transmission device, in a process in which the weight member of the centrifugal clutch unit moves from the inner diameter side position to the outer diameter side position and the transmission torque from the input member to the output member increases, for example, in the half clutch region, the crimping assistance cam can be inadvertently operated, and power transmission can be suddenly performed at an unintended timing at the start of the vehicle, making smooth travel difficult.

[0011] The present application was completed in view of such circumstances, and provides a power transmission device capable of preventing an inadvertently operated crimping assistance cam from suddenly performing power transmission at an unintended timing at the start of a vehicle in a vehicle equipped with a centrifugal clutch unit.

[0012] Means for solving the problem

[0013] The invention described in Solution 1 is a power transmission device that includes: a clutch housing that rotates together with an input member that rotates by a driving force of an engine of a vehicle, and that is provided with a plurality of driving side clutch plates; a clutch member that is provided with a plurality of passive side clutch plates that are alternately formed with the driving side clutch plates of the clutch housing, and that is linked to an output member that can rotate a wheel of the vehicle; a pressure member that can move between an operating position and a non-operating position, the operating position being a position in which the driving side clutch plates and the passive side clutch plates are crimped to be in a state in which the driving force of the engine can be transmitted to the wheel, and the non-operating position being a position in which the crimping force of the driving side clutch plates and the passive side clutch plates is released to be able to cut off the transmission of the driving force of the engine to the wheel; a centrifugal clutch unit that includes a weight member that can move from an inner diameter side position to an outer diameter side position by centrifugal force accompanying rotation of the clutch housing, that causes the driving side clutch plates and the passive side clutch plates to be crimped to be in a state in which the driving force of the engine can be transmitted to the wheel when the weight member is in the outer diameter side position, and that releases the crimping force of the driving side clutch plates and the passive side clutch plates to be able to cut off the transmission of the driving force of the engine to the wheel when the weight member is in the inner diameter side position; and a crimping assistance cam for increasing the crimping force of the driving side clutch plates and the passive side clutch plates when the rotation force input to the input member becomes a state in which it can be transmitted to the output member, the power transmission device being characterized in that, in a process in which the weight member of the centrifugal clutch unit moves from the inner diameter side position to the outer diameter side position and the transmission torque from the input member to the output member increases, there are a first torque region that restricts operation of the crimping assistance cam and a second torque region that allows operation of the crimping assistance cam.

[0014] The invention described in Aspect 2 is the power transmission device described in Aspect 1, characterized in that the clutch member has a first clutch member linked to the output member and a second clutch member to which the passive-side clutch plate is attached, and the crimping-assistance cam is constituted by a slope surface formed in the first clutch member and a slope surface formed in the pressure member being opposed to each other.

[0015] The invention described in Aspect 3 is the power transmission device described in Aspect 2, characterized in that, in the first torque region, the first clutch member and the pressure member are in abutment and the operation of the crimping-assistance cam is restricted, and in the second torque region, the first clutch member and the pressure member are apart and the operation of the crimping-assistance cam is allowed.

[0016] The invention described in Aspect 4 is the power transmission device described in Aspect 3, characterized in that, in the first torque region, the centrifugal clutch unit moves the second clutch member while maintaining the abutment state of the first clutch member and the pressure member, and in the second torque region, the centrifugal clutch unit moves the second clutch member and the pressure member to separate the first clutch member and the pressure member.

[0017] The invention described in Aspect 5 is the power transmission device described in Aspect 4, characterized in that, during the operation of the centrifugal clutch unit, the transition from the first torque region to the second torque region is performed.

[0018] Effects of the Invention

[0019] According to the invention of Aspect 1, since there are the first torque region in which the operation of the crimping-assistance cam is restricted and the second torque region in which the operation of the crimping-assistance cam is allowed during the increase of the transmission torque from the input member to the output member as the weight member of the centrifugal clutch unit moves from the inner diameter side position to the outer diameter side position, it is possible to prevent the crimping-assistance cam from being operated by mistake and suddenly perform the power transmission at an unintended timing at the start of the vehicle in which the centrifugal clutch unit is provided.

[0020] According to the invention of Aspect 2, since the clutch member has the first clutch member linked to the output member and the second clutch member to which the passive-side clutch plate is attached, and the crimping-assistance cam is constituted by the slope surface formed in the first clutch member and the slope surface formed in the pressure member being opposed to each other, it is possible to operate the crimping-assistance cam by the first clutch member and the pressure member.

[0021] According to the invention of the aspect 3, since the working of the crimping assist cam is restricted in the first torque region where the first clutch member and the pressure member are in abutment, and the working of the crimping assist cam is allowed in the second torque region where the first clutch member and the pressure member are apart, the restriction of the working of the crimping assist cam in the first torque region and the allowance of the working of the crimping assist cam in the second torque region can be performed correctly and smoothly.

[0022] According to the invention of the aspect 4, since the centrifugal clutch unit moves the second clutch member to maintain the abutment state of the first clutch member and the pressure member in the first torque region, and moves the second clutch member and the pressure member to make the first clutch member and the pressure member apart in the second torque region, the restriction of the working of the crimping assist cam in the first torque region and the allowance of the working of the crimping assist cam in the second torque region can be performed by the working of the centrifugal clutch unit.

[0023] According to the invention of the aspect 5, since the transition from the first torque region to the second torque region is performed during the working of the centrifugal clutch unit, the restriction of the working of the crimping assist cam in the first torque region and the allowance of the working of the crimping assist cam in the second torque region can be performed continuously and smoothly. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 is an appearance view of a power transmission apparatus according to an embodiment of the present application.

[0025] Figure 2 is a cross-sectional view taken along line II-II in Figure 1

[0026] Figure 3 is a cross-sectional view taken along line III-III in Figure 1

[0027] Figure 4 is a perspective view of a clutch housing in a power transmission apparatus according to an embodiment of the present application.

[0028] Figure 5 is a three-view drawing of a first clutch member in a power transmission apparatus according to an embodiment of the present application.

[0029] Figure 6 is a perspective view of a first clutch member in a power transmission apparatus according to an embodiment of the present application.

[0030] Figure 7 is a three-view drawing of a second clutch member in a power transmission apparatus according to an embodiment of the present application.

[0031] Figure 8 ​​is a perspective view showing a second clutch member in a power transmission apparatus according to an embodiment of the present application.

[0032] Figure 9 is a three-view drawing showing a pressure member in a power transmission apparatus according to an embodiment of the present application.

[0033] Figure 10 is a perspective view showing a pressure member in a power transmission apparatus according to an embodiment of the present application.

[0034] Figure 11 is a longitudinal sectional view showing a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application.

[0035] Figure 12 is a perspective view showing a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application.

[0036] Figure 13 is a three-view drawing showing a retaining member of a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application.

[0037] Figure 14 is a three-view drawing showing a support member of a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application.

[0038] Figure 15 is a three-view drawing showing a pressure contact member of a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application.

[0039] Figure 16 is a four-view drawing showing a counterweight member of a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application.

[0040] Figure 17 is Figure 16 is a sectional view taken along lines XVII-XVII in FIG. 17.

[0041] Figure 18 is a plan view showing a state in which the counterweight member in a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application is in an inner diameter side position.

[0042] Figure 19 is a plan view showing a state in which the counterweight member in a centrifugal clutch unit in a power transmission apparatus according to an embodiment of the present application is in an outer diameter side position.

[0043] Figure 20 is a schematic view for explaining (a) an action of a pressure contact assisting cam and (b) an action of a reverse torque limiter cam in a power transmission apparatus according to an embodiment of the present application.

[0044] Figure 21 This is a schematic diagram of a vehicle to illustrate a power transmission device according to an embodiment of the present invention.

[0045] Figure 22 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in the position of the inner diameter side.

[0046] Figure 23 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in an intermediate position between the inner diameter side position and the outer diameter side position.

[0047] Figure 24 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in the position of the outer diameter side.

[0048] Figure 25 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in the outer diameter side position and the pressure member in the non-working position.

[0049] Figure 26 This is a graph showing the relationship between engine speed and torque / auxiliary cam position in the power transmission device of this embodiment.

[0050] Figure 27 It is a graph showing the relationship between engine speed and torque / auxiliary cam position in conventional power transmission devices. Detailed Implementation

[0051] The following is a reference to the appendix. Figure 1 The embodiments of the present invention will be described in detail below.

[0052] The power transmission device K in this embodiment is as follows: Figure 21 As shown, it is configured in the vehicle to arbitrarily transmit or disconnect the driving force of the engine E via the transmission M to the drive wheel T side, such as... Figures 1 to 17 As shown, the system comprises a clutch housing 2 having an input gear 1 (input member) that rotates under the driving force of the engine E of the vehicle, an output shaft 3 (output member) connected to the transmission M, clutch members (first clutch member 4a and second clutch member 4b), a pressure member 5, multiple drive-side clutch plates 6 and multiple passive-side clutch plates 7, a centrifugal clutch unit 9 having a counterweight member 10, and an auxiliary clutch plate 17.

[0053] If the input gear 1 is fed with driving force (rotational force) transmitted from the engine E, it can rotate around the output shaft 3 and is connected to the clutch housing 2 via rivets, etc. The clutch housing 2 is composed of... Figure 2 , 3The cylindrical member with an opening at the right end is configured to be connected to the input gear 1 and can rotate together with the rotation of the input gear 1 by the driving force of the engine E.

[0054] In addition, such as Figure 4 As shown, the clutch housing 2 has multiple circumferential cuts 2a, into which multiple drive-side clutch plates 6 are mounted. Each drive-side clutch plate 6 is formed as a generally annular plate and rotates together with the clutch housing 2, and is configured to be axially ( Figure 2 , 3 Slide up in the left or right direction.

[0055] The clutch components (first clutch component 4a and second clutch component 4b) are equipped with a plurality of passive clutch plates 7 that alternately form with the drive-side clutch plates 6 of the clutch housing 2, and are connected to the output shaft 3 (output component) that can rotate the drive wheel T via the vehicle's transmission M. The clutch components are constructed by assembling the first clutch component 4a and the second clutch component 4b.

[0056] The first clutch component 4a is configured such that a through hole is formed in its center (see reference). Figure 5 , 6 The output shaft 3 is inserted through and the gears formed by them mesh to connect in the direction of rotation. For example... Figure 5 , 6 As shown, the first clutch member 4a has a slope surface 4aa that forms a cam for pressing assistance and a slope surface 4ab that forms a cam for counter-torque limiter. It should be noted that the reference numeral 4ac in the figure indicates a protrusion, which has a through hole for bolt B for connecting the first clutch member 4a and the fixing member 8.

[0057] like Figure 7 , 8 As shown, the second clutch member 4b is composed of an annular member having a flange portion 4bb, configured such that the driven side clutch plate 7 is mounted by spline engagement at the spline engagement portion 4ba formed on the outer peripheral surface. Furthermore, as... Figure 2 , 3 As shown, a pressure member 5 is assembled in the clutch components (first clutch component 4a and second clutch component 4b), and multiple drive-side clutch plates 6 and driven-side clutch plates 7 are alternately stacked between the flange portion 5c of the pressure member 5 and the flange portion 4bb of the second clutch component 4b.

[0058] like Figure 9 , 10As shown, the pressure member 5 is composed of a circular plate-shaped member formed with a flange portion 5c over the entire peripheral portion, and is movable between an operating position and a non-operating position. The operating position is a position in which the driving-side clutch plate 6 and the driven-side clutch plate 7 are pressed to be in a state in which the driving force of the engine E can be transmitted to the wheels, and the non-operating position is a position in which the pressing force of the driving-side clutch plate 6 and the driven-side clutch plate 7 is released to be able to cut off the transmission of the driving force of the engine E to the wheels.

[0059] More specifically, as shown in Figure 7 , 8 shown, the spline-fitting portion 4ba formed in the second clutch member 4b is composed of a concave-convex shape integrally formed over substantially the entire circumference of the outer peripheral surface of the second clutch member 4b, and is configured to be fitted into the groove that constitutes the spline-fitting portion 4ba by the driven-side clutch plate 7, to allow movement of the driven-side clutch plate 7 in the axial direction of the second clutch member 4b while restricting movement in the rotational direction, and to be rotatable together with the second clutch member 4b.

[0060] The driven-side clutch plate 7 is alternately stacked with the driving-side clutch plate 6, and each adjacent clutch plate 6, 7 can achieve pressing or release of the pressing force. That is, the two clutch plates 6, 7 are allowed to slide in the axial direction of the second clutch member 4b, and the clutch is opened by pressing each clutch plate (6a, 6b, 7a, 7b), so that 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, and the clutch is closed by releasing the pressing force of each clutch plate (6a, 6b, 7a, 7b), so that the first clutch member 4a and the second clutch member 4b no longer follow the rotation of the clutch housing 2, and the transmission of the rotational force to the output shaft 3 no longer occurs.

[0061] Thus, in a state in which the driving-side clutch plate 6 and the driven-side clutch plate 7 are pressed, the rotational force (driving force of the engine E) input to the clutch housing 2 is transmitted to the drive wheel side (transmission M) via the output shaft 3 (output member), and in a state in which the pressing of the driving-side clutch plate 6 and the driven-side clutch plate 7 is released, the transmission of the rotational force (driving force of the engine E) input to the clutch housing 2 to the output shaft 3 (output member) can be cut off.

[0062] In addition, as shown in Figure 9 , 10 the pressure member 5 is formed with a plurality of (three in this embodiment) insertion holes 5d over the entire circumferential direction, and the clutch spring S is inserted into each insertion hole 5d. As shown in Figure 2As shown, the clutch spring S is housed in the insertion hole 5d and one end abuts against the fixed member 8, and is forced in a direction to press the driving-side clutch plate 6 and the driven-side clutch plate 7. Also, by operating a clutch operation unit not shown, pressing or release of the driving-side clutch plate 6 and the driven-side clutch plate 7 can be performed.

[0063] Also, in the present embodiment, as shown in Figure 5 , 6 , 9, 10, a slope surface 4aa and a slope surface 4ab are formed in the first clutch member 4a, and a slope surface 5a and a slope surface 5b opposed to these slope surfaces 4aa and 4ab are formed in the pressure member 5. That is, the slope surface 4aa and the slope surface 5a abut to constitute a pressing assisting cam, and the slope surface 4ab and the slope surface 5b abut to constitute a reverse torque limiter cam.

[0064] Also, when the rotational speed of the engine E rises to a state where the rotational force input to the input gear 1 and the clutch housing 2 can be transmitted to the output shaft 3 via the first clutch member 4a and the second clutch member 4b (the weight member 10 is at the outer diameter side position), as shown in Figure 20 (a), a rotational force in the a direction is applied to the pressure member 5, and thus, by the action of the pressing assisting cam, a force in the c direction in the figure is generated in the pressure member 5. Thereby, the pressure member 5 moves in a direction in which the flange portion 5c thereof further approaches the flange portion 4bb of the second clutch member 4b (the left side in the figure), and the pressing force of the driving-side clutch plate 6 and the driven-side clutch plate 7 is increased. Figure 2 , 3

[0065] On the other hand, when the rotation of the output shaft 3 exceeds the rotational speed of the input gear 1 and the clutch housing 2 and a reverse torque is generated, as shown in Figure 20 (b), a rotational force in the b direction is applied to the clutch member 4, and thus, by the action of the reverse torque limiter cam, the pressure member 5 moves in the d direction in the figure to release the pressing force of the driving-side clutch plate 6 and the driven-side clutch plate 7. Thereby, it is possible to avoid a bad condition with respect to the power transmission device K, the power source (the engine E side) caused by the reverse torque.

[0066] As shown in Figures 11 to 19 , the centrifugal clutch unit 9 is provided with a weight member 10 that can move from an inner diameter side position (refer to Figure 18 ) to an outer diameter side position (refer to Figure 19 ​) the movable weight member 10 is configured to press the drive side clutch plate 6 and the passive side clutch plate 7 to be in a state where the driving force of the engine E is transmitted to the wheels (drive wheels T) when the weight member 10 is in the outer diameter side position, and to release the pressing force of the drive side clutch plate 6 and the passive side clutch plate 7 to be able to cut off the transmission of the driving force of the engine E to the wheels (drive wheels T) when the weight member 10 is in the inner diameter side position.

[0067] Specifically, the centrifugal clutch unit 9 is configured to have the weight member 10 composed of a shogi piece-shaped (block-shaped) member, the holding member 11 on which the support member 13 is mounted, the pressing member 12, the first ball-shaped member 14, the second ball-shaped member 15, and the biasing member 16 composed of a coil spring. Note that the holding member 11 and the pressing member 12 are formed with a plurality of protruding portions over the entire circumferential direction, and are fitted and mounted to the cutout 2a of the clutch housing 2, like the drive side clutch plate 6. Thus, the holding member 11 and the pressing member 12 are able to move in the axial direction of the clutch housing 2, respectively, and are able to be engaged in the rotational direction to rotate together with the clutch housing 2.

[0068] As shown in Figure 16 , the weight member 10 is composed of a shogi piece-shaped member having one face X and another face Y, as shown in the drawing and Figure 17 , the weight member 10 is configured to have a through-hole 10a formed through from the one face X to the other face Y, an insertion portion 10b formed on the other face Y, and a groove 10c formed on the one face X. As shown in Figure 18 , 19 , the weight member 10 is housed in the housing portion 11a of the holding member 11, and is held at the inner diameter side position (see Figure 18 ) in a state where no centrifugal force is applied, and is moved to the outer diameter side position (see Figure 19 ) by being applied with a centrifugal force against the force of the biasing member 16.

[0069] The holding member 11 holds the weight member 10 to be movable between the inner diameter side position and the outer diameter side position, and is composed of a circular ring-shaped member, as shown in Figure 13 , and is configured to have a plurality of housing portions 11a formed over the entire circumferential direction and housing the weight member 10, a groove shape 11b formed inside the housing portion 11a, and a pressing face 11c. Each of the housing portions 11a is composed of a concave shape matching the shape and the range of movement of the weight member 10, and is configured such that one end of the biasing member 16 is able to abut against the inner peripheral wall face 11aa thereof.

[0070] In addition, the support member 13 is fixed to the face of the holding member 11 on which the housing portion 11a is formed. As shown in Figure 14As shown, the support member 13 has a radially formed retaining portion 13a, which matches the groove 10c of the counterweight member 10, thereby holding the counterweight member 10 to the retaining member 11. That is, the counterweight member 10 has a groove 10c formed at the center of one of its surfaces X in the direction from the inner diameter side to the outer diameter side. By matching the retaining portion 13a with the groove 10c, the counterweight member 10 is held so that it can move radially (in the direction from the inner diameter side to the outer diameter side).

[0071] The pressing member 12 moves from the inner diameter side to the outer diameter side via the counterweight member 10 in the stacking direction of the driving side clutch plate 6 and the driven side clutch plate 7. Figure 2 , 3 The right side moves to press the drive-side clutch plate 6 and the driven-side clutch plate 7 into contact. Specifically, as... Figure 15 As shown, the pressing member 12 is composed of an annular member and is configured to have multiple circumferentially formed slope grooves 12a, groove shapes 12b formed at the positions where the slope grooves 12a are formed, and pressing surfaces 12c.

[0072] The slope grooves 12a are formed at positions corresponding to the counterweight member 10, and are configured to slope upwards from the inside to the outside. Thus, when the clutch housing 2 is stopped, the counterweight member 10 is held in the inner diameter position by the force of the force-applying member 16, and if the clutch housing 2 rotates, centrifugal force is applied to the counterweight member 10 and it moves along the slope grooves 12a, thereby causing the pressing member 12 to move away from the holding member 11 (i.e., the direction in which the driving side clutch plate 6 and the driven side clutch plate 7 are pressed).

[0073] Therefore, if the counterweight component 10 is positioned in the middle while the retaining component 11 and the pressing component 12 are assembled, then as follows: Figure 11 , 12 As shown, the slope groove 12a is located at the position corresponding to each counterweight component 10. The counterweight component 10 moves from the inner diameter side to the outer diameter side via centrifugal force along the slope groove 12a. The pressing component 12... Figure 11 The component moves in the direction of the middle arrow (right side in the figure), and the pressing surface 12c formed on the pressing member 12 presses the driving side clutch plate 6 and the driven side clutch plate 7 to set them into a pressing state, and the holding member 11 is held in a pressing state by its reaction force. Figure 11 Moving in the opposite direction of the middle arrow (left side in the figure), the pressing surface 11c formed on the retaining member 11 presses the auxiliary clutch plate 17 into place.

[0074] like Figure 18 , 19As shown, in this embodiment, the counterweight member 10 is housed in a plurality of receiving portions 11a formed circumferentially around the retaining member 11 and is movable in a radial direction. The force-applying member 16 is located on the inner peripheral wall surface 11aa of the receiving portion 11a (see reference). Figure 13 Multiple (two in this embodiment) are arranged circumferentially between the receiving part 11a and the counterweight 10 to apply force to the counterweight 10 from the outer diameter side to the inner diameter side. Here, the inner circumferential wall surface 11aa of the receiving part 11a is set as a flat surface that abuts against one end of the force-applying member 16, so that the force-applying member 16 can be installed in a stable state.

[0075] Furthermore, the counterweight member 10 in this embodiment has a surface that faces the retaining member 11. Figure 17 The other side (Y) of the tube has an opening, through which the force-applying member 16 can be inserted for installation. Furthermore, by housing the counterweight member 10, with the force-applying member 16 inserted into the insertion portion 10b, in the receiving portion 11a of the retaining member 11, the force-applying member 16 is installed between the inner peripheral wall surface 11aa of the receiving portion 11a and the counterweight member 10. It should be noted that the force-applying member 16 is arranged such that one end abuts against the inner peripheral wall surface 11aa and the other end abuts against the end wall surface 10ba of the insertion portion 10b, enabling force to be applied to the counterweight member 10 from the outer diameter side position toward the inner diameter side position.

[0076] The first spherical component 14 is composed of steel balls installed on the counterweight component 10, such as Figure 16 , 17 As shown, a portion protrudes from one opening 10aa (an opening with a small diameter on the X side) formed in the through hole 10a of the counterweight member 10, allowing it to contact and roll with the rolling surface of the pressing member 12. Furthermore, the second spherical member 15 is composed of a steel ball mounted on the counterweight member 10, as shown... Figure 16 , 17 As shown, a portion protrudes from the opening 10ab (the large-diameter opening on the Y side of the other side of the through hole 10a formed in the counterweight member 10) and is able to roll in contact with the rolling surface of the retaining member 11.

[0077] like Figure 17As shown, the through-hole 10a of the present embodiment is formed in a tapered shape in which the diameter continuously increases from the one opening 10aa (the small-diameter opening on the one face X side) to the other opening 10ab (the large-diameter opening on the other face Y side), and the first spherical member 14 is prevented from coming off from the outer peripheral edge portion of the small-diameter opening (in the present embodiment, the one opening 10aa on the one face X side) of the one opening 10aa and the other opening 10ab. That is, the first spherical member 14 and the second spherical member 15 of the present embodiment are composed of spherical members (the second spherical member 15 is a member having a larger diameter than the first spherical member 14) having mutually different diameters in accordance with the inner diameter of the through-hole 10a, and the small-diameter first spherical member 14 is able to roll in a state in which it is prevented from coming off from the opening edge portion of the small-diameter side of the through-hole 10a and is in contact with the inner peripheral surface of the through-hole 10a, respectively.

[0078] On the other hand, as shown in Figure 11 , 12 , the second spherical member 15 is prevented from coming off from the rolling surface of the holding member 11. Thereby, the small-diameter first spherical member 14 is prevented from coming off from the opening edge portion of the small-diameter side of the through-hole 10a, and the large-diameter second spherical member 15 is prevented from coming off from the rolling surface of the holding member 11 in a state in which a part thereof protrudes from the opening of the large-diameter side of the through-hole 10a. Note that in the present embodiment, the large-diameter second spherical member 15 is assembled in a manner in which it opposes the rolling surface of the holding member 11, but the second spherical member 15 can also be assembled in a manner in which it opposes the rolling surface of the press-fitting member 12. In this case, the small-diameter first spherical member 14 is prevented from coming off from the opening edge portion of the small-diameter side of the through-hole 10a, and the large-diameter second spherical member 15 is prevented from coming off from the rolling surface of the press-fitting member 12 in a state in which a part thereof protrudes from the opening of the large-diameter side of the through-hole 10a.

[0079] As shown in Figure 13 , the rolling surface of the holding member 11 (in the present embodiment, the rolling surface of the second spherical member 15) is composed of a groove shape 11b along the moving direction of the weight member 10 (the direction connecting the inner-diameter side position and the outer-diameter side position), and as shown in Figure 15 , the rolling surface of the press-fitting member 12 (in the present embodiment, the rolling surface of the first spherical member 14) is composed of a groove shape 12b along the moving direction of the weight member 10 (the direction connecting the inner-diameter side position and the outer-diameter side position).

[0080] Furthermore, as shown in Figure 16 , 18As shown in Figs. 19, the first and second ball members 14 and 15 according to the present embodiment are each formed with a plurality of (in the present embodiment, two) members that extend in the circumferential direction (width direction of the weight member 10) of the holding member 11, and are each capable of moving along the groove shapes 11b and 12b while rolling within the through-hole 10a, in conjunction with movement of the weight member 10.

[0081] The auxiliary clutch plate 17 is formed of a circular ring member having a diameter different from (in the present embodiment, smaller than) the drive-side and driven-side clutch plates 6 and 7, as shown in Figs. 18 and 19, and is fitted to the output shaft 3 (output member) so as to be in a fitted state with the central opening 17a, and is configured to have a pressed surface 17b that opposes the pressing surface 11c of the holding member 11. Figure 2 、 3 As shown in Figs. 18 and 19, the auxiliary clutch plate 17 is fitted to the output shaft 3 (output member) so as to be in a fitted state with the central opening 17a, and is configured to have a pressed surface 17b that opposes the pressing surface 11c of the holding member 11.

[0082] The auxiliary clutch plate 17 is pressed by the pressing surface 11c of the holding member 11 when the weight member 10 is in the outer diameter side position (i.e., when the drive-side and driven-side clutch plates 6 and 7 are in the pressed state), and is pressed by the pressing force of the pressing surface 11c of the holding member 11 when the weight member 10 is in the inner diameter side position (i.e., when the pressing force of the drive-side and driven-side clutch plates 6 and 7 is released), and thus is capable of transmitting the driving force of the engine E to the output shaft 3 when the weight member 10 is in the outer diameter side position, and is capable of cutting off the transmission of the driving force of the engine E to the output shaft 3 when the weight member 10 is in the inner diameter side position.

[0083] That is, when the weight member 10 moves to the outer diameter side position, the slope groove 12a functions as a cam, and the holding member 11 and the pressing member 12 move in a direction away from each other. Thus, the pressing surface 12c of the pressing member 12 presses the drive-side and driven-side clutch plates 6 and 7, and the pressing surface 11c of the holding member 11 presses the pressed surface 17b of the auxiliary clutch plate 17, and thus the driving force of the engine E is transmitted to the drive wheels T.

[0084] According to the power transmission device K of the present embodiment, the through-hole 10a of the weight member 10 in the centrifugal clutch unit 9 is formed in a tapered shape from the one opening 10aa to the other opening 10ab, and the first ball member 14 is prevented from coming off by the outer peripheral edge portion of the smaller diameter opening of the one opening 10aa and the other opening 10ab, and thus the first ball member 14 can be easily and accurately installed to the weight member 10, and the manufacturing cost can be reduced.

[0085] Further, the first and second ball members 14 and 15 are constituted by ball members having diameters different from each other corresponding to the inner diameter of the through hole 10a, and are able to roll in a state of contacting the inner peripheral surface of the through hole 10a respectively, so that the first and second ball members 14 and 15 are able to roll stably at the time of movement of the weight member 10, and smooth movement can be achieved. Also, the second ball member 15 of the present embodiment is prevented from coming off by the rolling surface of the holding member 11 or the press contact member 12, so that the prevention of the second ball member 15 from coming off can be easily performed.

[0086] Further, the rolling surface of the holding member 11 or the press contact member 12 is constituted by a groove shape (11b, 12b) along the moving direction of the weight member 10, so that the prevention of the second ball member 15 from coming off on the opening side of the large diameter and the prevention of the first ball member 14 from coming off on the opening side of the small diameter can be reliably performed respectively, and smoother movement of the weight member 10 can be achieved.

[0087] In addition to this, the weight member 10 of the present embodiment is housed in the accommodation portions 11a formed in plurality over the circumferential direction of the holding member 11 and is able to move in the radial direction, and the urging members 16 are provided in plurality in the circumferential direction between the inner peripheral wall surface 11aa of the accommodation portion 11a and the weight member 10 and urge the weight member 10 from the position of the outer diameter side toward the position of the inner diameter side, so that the weight member 10 can be urged with high precision from the position of the outer diameter side toward the position of the inner diameter side, and the weight member 10 can be moved stably according to the centrifugal force.

[0088] Further, the weight member 10 of the present embodiment is formed with the insertion portion 10b which opens the surface opposed to the holding member 11 and in which the urging member 16 is able to be inserted and installed, so that the assembly of the urging member 16 with respect to the weight member 10 can be easily performed. Also, the weight member 10 of the present embodiment is formed with the groove 10c in the direction from the position of the inner diameter side toward the position of the outer diameter side, and the holding member 11 (specifically, the support member 13 fixed to the holding member 11 and integrated therewith) is formed with the holding portion 13a which matches with the groove 10c and holds the weight member 10, so that the movement of the weight member 10 can be stably performed.

[0089] Further, the centrifugal clutch unit 9 of the present embodiment is constituted by the first ball member 14 which protrudes a part from the opening 10aa of one side of the through hole 10a formed in the weight member 10 and is able to roll in contact with the rolling surface (groove shape 12b) of the press contact member 12, and the second ball member 15 which protrudes a part from the opening 10ab of the other side of the through hole 10a formed in the weight member 10 and is able to roll in contact with the rolling surface (groove shape 11b) of the holding member 11, so that the movement of the weight member 10 can be more stably performed.

[0090] In particular, the holding member 11 or the press-contact member 12 has a groove shape (11b, 12b) along the moving direction of the weight member 10, which is set as a rolling surface of the first ball-shaped member 14 or the second ball-shaped member 15, so that the movement of the weight member 10 can be performed more smoothly. Also, the first ball-shaped member 14 and the second ball-shaped member 15 of the present embodiment are each formed with a plurality of members across the circumferential direction (the width direction of the weight member 10) of the holding member 11, so that further stable movement of the weight member 10 can be sought.

[0091] Here, the power transmission device K of the present embodiment is configured such that, in a process in which the weight member 10 of the centrifugal clutch unit 9 moves from the inner diameter side position to the outer diameter side position and the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member) increases, as shown in Figure 26 , there is a first torque region al in which the operation of the press-contact assisting cam (cam composed of the slope surface 4aa and the slope surface 5a) is restricted and a second torque region a2 in which the operation of the press-contact assisting cam is allowed.

[0092] Specifically, as shown in Figure 5 , 6 , the first clutch member 4a of the present embodiment is formed with an abutting surface 4ad at a portion of the surface opposite to the pressure member 5, and as shown in Figure 9 , 10 , the pressure member 5 is formed with an abutting surface 5e at a portion of the surface opposite to the first clutch member 4a, and in a state in which the first clutch member 4a, the second clutch member 4b, and the pressure member 5 are assembled (a state in which the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member) is not transmitted), as shown in Figure 2 , 3 , the abutting surface 4ad and the abutting surface 5e are set to be in an abutting state.

[0093] In the first torque region al in which the abutting surface 4ad and the abutting surface 5e are thus in an abutting state (t1 to t2 in Figure 26 ), in a process in which the weight member 10 of the centrifugal clutch unit 9 moves from the inner diameter side position (refer to Figure 22 ) to the intermediate position (refer to Figure 23 ) and the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member) increases, the relative movement between the first clutch member 4a and the pressure member 5 is not allowed, so the operation of the press-contact assisting cam is restricted.

[0094] After that, if the weight member 10 of the centrifugal clutch unit 9 moves from the intermediate position (refer to Figure 23 ) toward the outer diameter side position (refer to Figure 24Further movement causes the driven clutch plate 6 and the driven clutch plate 7 to be pressed together by the flange portion 4bb of the second clutch member 4b, and the pressing force of the flange portion 4bb becomes greater than the force of the clutch spring S. Then, relative to the first clutch member 4a, the second clutch member 4b and the pressure member 5 are axially ( Figure 2 , 3 The mechanism moves (in the right direction) to separate the contact surface 4ad of the first clutch component 4a from the contact surface 5e of the pressure component 5. It should be noted that... Figure 25 The diagram shows the counterweight member 10 in the outer diameter position and the pressure member 5 in the non-working position (clutch closed).

[0095] In the state where the contact surfaces 4ad and 5e are separated ( Figure 26 During the second torque region α2 after t2 in the centrifugal clutch unit 9, as the counterweight member 10 moves from the inner diameter side position to the outer diameter side position and the torque transmitted from the input gear 1 (input member) to the output shaft 3 (output member) increases, the relative movement between the first clutch member 4a and the pressure member 5 is permitted, and therefore the operation of the pressing auxiliary cam is permitted.

[0096] That is, in this embodiment, in the first torque region α1, the contact surface 4ad of the first clutch member 4a and the contact surface 5e of the pressure member 5 abut together, and the operation of the pressing auxiliary cam is restricted; while in the second torque region α2, the contact surface 4ad of the first clutch member 4a and the contact surface 5e of the pressure member 5 separate, and the operation of the pressing auxiliary cam is permitted.

[0097] Furthermore, in this embodiment, the centrifugal clutch unit 9 maintains the contact state between the first clutch member 4a and the pressure member 5 by moving the second clutch member 4b while not moving the first clutch member 4a in the first torque region α1. In the second torque region α2, the centrifugal clutch unit 9 moves both the second clutch member 4b and the pressure member 5, causing the contact surface 4ad of the first clutch member 4a and the contact surface 5e of the pressure member 5 to separate. Specifically, in this embodiment, the centrifugal clutch unit 9 transitions from the first torque region α1 to the second torque region α2 during operation.

[0098] On the other hand, for example, in the case of a conventional power transmission device that does not abut against the first clutch member 4a and the pressure member 5 and does not have a first torque region α1 (only has a torque region β), such as Figure 27As shown, the crimping assist cam operates while the weight member 10 of the centrifugal clutch unit 9 moves from the inner diameter side position to the outer diameter side position to generate the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member), and power transmission is unexpectedly and suddenly performed at the start of the vehicle, which makes smooth running difficult.

[0099] According to the present embodiment, in the process in which the weight member 10 of the centrifugal clutch unit 9 moves from the inner diameter side position to the outer diameter side position to increase the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member), there are the first torque region al in which the operation of the crimping assist cam is restricted and the second torque region a2 in which the operation of the crimping assist cam is permitted, and thus in the vehicle provided with the centrifugal clutch unit 9, it is possible to prevent the crimping assist cam from inadvertently operating and suddenly performing power transmission at an unintended timing at the start of the vehicle.

[0100] In addition, the clutch member of the present embodiment has the first clutch member 4a linked to the output shaft 3 (output member) and the second clutch member 4b on which the passive side clutch plate 7 is mounted, and the crimping assist cam is constituted by the slope surface 4aa formed in the first clutch member 4a and the slope surface 5a formed in the pressure member 5 being opposed to each other, and thus it is possible to operate the crimping assist cam by the first clutch member 4a and the pressure member 5.

[0101] Further, since the first clutch member 4a and the pressure member 5 are in abutment in the first torque region al and the operation of the crimping assist cam is restricted, and the first clutch member 4a and the pressure member 5 are apart in the second torque region a2 and the operation of the crimping assist cam is permitted, it is possible to correctly and smoothly perform the restriction of the operation of the crimping assist cam in the first torque region al and the permission of the operation of the crimping assist cam in the second torque region a2.

[0102] Further, since the centrifugal clutch unit 9 does not move the first clutch member 4a and moves the second clutch member 4b to maintain the abutment state of the first clutch member 4a and the pressure member 5 in the first torque region al, and the centrifugal clutch unit 9 moves the second clutch member 4a and the pressure member 5 to separate the first clutch member 4a and the pressure member 5 in the second torque region a2, it is possible to perform the restriction of the operation of the crimping assist cam in the first torque region al and the permission of the operation of the crimping assist cam in the second torque region a2 by the operation of the centrifugal clutch unit 9.

[0103] In particular, in the present embodiment, since the shift from the first torque region al to the second torque region a2 occurs in the operation of the centrifugal clutch unit 9 (the movement of the weight member 10 from the inner diameter side position to the outer diameter side position), the restriction of the operation of the crimping assist cam in the first torque region al and the allowance of the operation of the crimping assist cam in the second torque region a2 can be performed continuously and smoothly.

[0104] The present embodiment has been described above, but the present application is not limited thereto, and for example, can be a structure without the reverse torque limiter cam (the slope surface 4ab and the slope surface 5b), a structure without the assist clutch plate 17, or a structure in which the centrifugal clutch unit 9 is in another form (a structure in which the weight member is composed of a steel ball, or the like). Note that the power transmission device of the present application can be applied to various multi-plate clutch type power transmission devices other than two-wheeled motor vehicles, such as automobiles, three- or four-wheeled off-road vehicles, or general-purpose machines.

[0105] Industrial applicability

[0106] As long as the power transmission device has a first torque region in which the operation of the crimping assist cam is restricted and a second torque region in which the operation of the crimping assist cam is allowed in a process in which the weight member of the centrifugal clutch unit moves from the inner diameter side position to the outer diameter side position and the transmission torque from the input member to the output member increases, the power transmission device can be applied to power transmission devices having different external shapes or power transmission devices to which other functions are added.

[0107] Explanation of reference numerals

[0108] 1 input gear (input member)

[0109] 2 clutch housing

[0110] 2a cutout

[0111] 3 output shaft (output member)

[0112] 4a first clutch member

[0113] 4aa slope surface (crimping assist cam)

[0114] 4ab slope surface (reverse torque limiter cam)

[0115] 4ac protrusion

[0116] 4ad abutment surface

[0117] 4b second clutch member

[0118] 4ba spline fitting portion

[0119] 4bb flange portion

[0120] 5 pressure member

[0121] 5a slope surface (cam for crimping assistance)

[0122] 5b slope surface (cam for reverse torque limiter)

[0123] 5c flange portion

[0124] 5d insertion hole

[0125] 5e abutment surface

[0126] 6 drive-side clutch plate

[0127] 7 driven-side clutch plate

[0128] 8 fixing member

[0129] 9 centrifugal clutch unit

[0130] 10 counterweight member

[0131] 10a through hole

[0132] 10aa one-side opening

[0133] 10ab other-side opening

[0134] 10b insertion portion

[0135] 10ba end wall surface

[0136] 10c groove

[0137] 11 holding member

[0138] 11a housing portion

[0139] 11aa inner peripheral wall surface

[0140] 11b groove shape

[0141] 11c pressing surface

[0142] 12 crimping member

[0143] 12a slope groove

[0144] 12b groove shape

[0145] 12c pressing surface

[0146] 13 support member

[0147] 13a holding portion

[0148] 14 first spherical member

[0149] 15 second spherical member

[0150] 16 force applying member

[0151] 17 auxiliary clutch plate

[0152] 17a central opening

[0153] 17b pressed surface

[0154] S clutch spring

Claims

1. A power transmitting apparatus, comprising: a clutch member that houses a clutch case in which a plurality of drive-side clutch plates are installed, that rotates together with an input member that rotates by a driving force of an engine of a vehicle, and that is linked to an output member that is capable of rotating a wheel of the vehicle, a plurality of passive-side clutch plates that are alternately formed with the drive-side clutch plates are installed, and a pressure member that is capable of moving between an operating position that is a position in which the drive-side clutch plates and the passive-side clutch plates are pressed to be in a state in which the driving force of the engine is capable of being transmitted to the wheel, and a non-operating position that is a position in which pressing force of the drive-side clutch plates and the passive-side clutch plates is released to be capable of cutting off transmission of the driving force of the engine to the wheel; and a centrifugal clutch unit that includes a counterweight member that is capable of moving from an inner diameter side position to an outer diameter side position by centrifugal force that accompanies rotation of the clutch case, that causes the drive-side clutch plates and the passive-side clutch plates to be pressed to be in a state in which the driving force of the engine is capable of being transmitted to the wheel when the counterweight member is in the outer diameter side position, and that causes the drive-side clutch plates and the passive-side clutch plates to be released from pressing to be capable of cutting off transmission of the driving force of the engine to the wheel when the counterweight member is in the inner diameter side position, wherein the clutch member has: a first clutch member that is linked to the output member; and a second clutch member in which the passive-side clutch plates are installed, the centrifugal clutch unit includes a pressing member that is located between the counterweight member and the second clutch member in an axial direction of the output member, and that moves in a stacking direction of the drive-side clutch plates and the passive-side clutch plates to cause the drive-side clutch plates and the passive-side clutch plates to be pressed when the counterweight member moves from the inner diameter side position to the outer diameter side position, a plurality of protruding portions are formed in the pressing member in a circumferential direction, the pressing member is installed by being fitted in a plurality of cutouts formed in the clutch case by the protruding portions, at least a portion of the centrifugal clutch unit overlaps the clutch member when viewed in a radial direction of the output member, a portion of the pressing member is located at an outer side than the first clutch member in the radial direction and at an inner side than the cutouts in the radial direction, and a portion of the pressing member overlaps the first clutch member when viewed in the radial direction of the output member.

2. The power transmitting apparatus according to claim 1, wherein the centrifugal clutch unit includes a holding member that holds the counterweight member in a manner that is capable of moving between the inner diameter side position and the outer diameter side position, and at least a portion of the holding member overlaps the clutch member when viewed in the radial direction of the output member.

3. The power transmitting apparatus according to claim 2, wherein ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ The clutch member has a protruding portion that extends in the axial direction of the output member and holds the output member, At least a portion of the holding member overlaps the protruding portion when viewed in the radial direction of the output member.

4. The power transmission apparatus according to claim 1, wherein At least a portion of the counterweight member overlaps the clutch member when viewed in the radial direction of the output member.

5. The power transmission apparatus according to claim 4, wherein The clutch member has a protruding portion that extends in the axial direction of the output member and holds the output member, At least a portion of the counterweight member overlaps the protruding portion when viewed in the radial direction of the output member.

6. The power transmission apparatus according to claim 1, wherein The centrifugal clutch unit has a spherical member that is able to roll with a portion protruding from an opening of the through-hole formed in the counterweight member, At least a portion of the spherical member overlaps the first clutch member when viewed in the radial direction of the output member.

7. The power transmission apparatus according to claim 1, wherein The clutch member has: a protruding portion that extends in the axial direction of the output member and holds the output member; and an outer peripheral wall that is located radially outward of the protruding portion and extends in the axial direction of the output member, At least a portion of the centrifugal clutch unit overlaps the outer peripheral wall when viewed in the radial direction of the output member.

8. The power transmission apparatus according to claim 7, wherein At least a portion of the pressure member overlaps the outer peripheral wall when viewed in the radial direction of the output member.

9. The power transmission apparatus according to claim 7, wherein The centrifugal clutch unit has a spherical member that is able to roll with a portion protruding from an opening of the through-hole formed in the counterweight member, At least a portion of the spherical member overlaps the outer peripheral wall when viewed in the radial direction of the output member.

10. A power transmission apparatus comprising: a clutch member that is housed in a clutch case that rotates together with an input member that rotates by a driving force of an engine of a vehicle and that is installed with a plurality of driving-side clutch plates, that is installed with a plurality of passive-side clutch plates that are alternately formed with the driving-side clutch plates, and that is linked to an output member that is able to rotate a wheel of the vehicle; a pressure member that is able to move between an operating position that is a position in which the driving-side clutch plates and the passive-side clutch plates are pressed to be in a state in which the driving force of the engine is able to be transmitted to the wheel and a non-operating position that is a position in which the pressing force of the driving-side clutch plates and the passive-side clutch plates is released to be able to cut off the transmission of the driving force of the engine to the wheel; and a centrifugal clutch unit that is able to transmit the driving force of the engine to the wheel when the centrifugal clutch unit is in a state in which the centrifugal clutch unit is able to rotate together with the input member and the output member and the centrifugal clutch unit is in a state in which the centrifugal clutch unit is able to rotate independently of the input member and the output member. A centrifugal clutch unit having a counterweight member that is movable from an inner diameter side position to an outer diameter side position by centrifugal force accompanying rotation of a clutch housing, that causes the driving side clutch plate and the driven side clutch plate to be pressed to be in a state in which the driving force of the engine is able to be transmitted to the wheels when the counterweight member is in the outer diameter side position, and that causes the pressing force of the driving side clutch plate and the driven side clutch plate to be released to be able to cut off the transmission of the driving force of the engine to the wheels when the counterweight member is in the inner diameter side position; and an auxiliary clutch plate that is fixed to the output member, wherein the centrifugal clutch unit has: a pressing member that is moved in a stacking direction of the driving side clutch plate and the driven side clutch plate by the movement of the counterweight member from the inner diameter side position to the outer diameter side position to cause the driving side clutch plate and the driven side clutch plate to be pressed; and a holding member that holds the counterweight member so as to be movable between the inner diameter side position and the outer diameter side position, the auxiliary clutch plate is pressed by a pressing surface of the holding member to transmit the driving force of the engine to the output member when the counterweight member is moved to the outer diameter side position and the pressing member and the holding member are moved in directions away from each other, at least a portion of the centrifugal clutch unit overlaps the auxiliary clutch plate when viewed in a radial direction of the output member.

11. The power transmission apparatus according to claim 10, wherein at least a portion of the holding member overlaps the auxiliary clutch plate when viewed in the radial direction of the output member.

12. The power transmission apparatus according to claim 10, wherein at least a portion of the counterweight member overlaps the auxiliary clutch plate when viewed in the radial direction of the output member.

13. The power transmission apparatus according to claim 10, wherein the centrifugal clutch unit has a spherical member that protrudes from an opening of a through-hole formed in the counterweight member to be able to roll, at least a portion of the spherical member overlaps the auxiliary clutch plate when viewed in the radial direction of the output member.

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