Power transmission device

Abstract

The present invention relates to a power transmission device. The power transmission device has: a first clutch member (4a) connected to an output shaft (3); a second clutch member (4b) attached with a driven side clutch plate (7); and a reverse torque transmission cam, which can move the second clutch member (4b) and press the driving side clutch plate (6) and the driven side clutch plate (7) when a rotational force is input to the first clutch member (4a). The power transmission device also includes a damping member (12), which is placed between the first clutch member (4a) and the second clutch member (4b); and can be compressed in the process of the link member (9) moving and the pressure member (5) moving from the non-working position to the working position, so as to allow the link member (9) and the pressure member (5) to move and apply a driving force.

Description

[0001] This application is a divisional application of the invention patent application with the original application number 201980079116.X (International application number: PCT / JP2019 / 047407, application date: December 4, 2019, invention name: power transmission device). Technical Field

[0002] The present invention relates to a power transmission device capable of appropriately transmitting or stopping the transmission of rotational power of an input member to an output member. Background Art

[0003] Generally, a motorcycle has a power transmission device for appropriately transmitting or stopping the driving force of the engine to the transmission and the drive wheel. The power transmission device includes: an input member connected to the engine side; an output member connected to the transmission and the drive wheel side; a clutch member connected to the output member; and a pressure member that can move toward or away from the clutch member. The power transmission device is configured to transmit power by moving the pressure member toward the clutch member to press the driving side clutch plate and the driven side clutch plate against each other, and is configured to stop transmitting power by moving the pressure member away from the clutch member to release the pressing force between the driving side clutch plate and the driven side clutch plate.

[0004] In a conventional power transmission device disclosed in, for example, Patent Document 1, a power transmission device including a weight member is proposed. The weight member can press the driving side clutch plate and the driven side clutch plate against each other by moving from a radially inner position to a radially outer position in a groove portion due to centrifugal force generated when the clutch housing rotates. With the conventional power transmission device, since the clutch housing rotates as the engine is driven, centrifugal force can be applied to the weight member by pressing the driving side clutch plate and the driven side clutch plate against each other and the driving force of the engine can be transmitted to the wheels.

[0005] The existing power transmission device also includes: a release spring, which is compressed when the linkage member moves and the pressure member moves from the non-working position toward the working position, and the release spring can apply an urging force while allowing the linkage member and the pressure member to move until the driving side clutch plate and the driven side clutch plate reach an engaged state before being pressed against each other; and a clutch spring, which is compressed during the movement of the linkage member after the driving side clutch plate and the driven side clutch plate have reached the engaged state, and the clutch spring can apply a pressing force between the driving side clutch plate and the driven side clutch plate while allowing the linkage member to move.

[0006] Reference List

[0007] Patent Literature

[0008] Patent Document 1: Japanese Patent Application Publication No. 2017-155884 Summary of the invention

[0009] Technical issues

[0010] However, the conventional power transmission device has the following problems.

[0011] If the load (maximum load) at which the spring is released has reached the end of its compression (see Fig.32 If the difference between the load (P1 in the figure) and the load (set load) when the compression of the clutch spring starts (see P2 in the figure) is large, then in the process where the linkage member moves and the pressure member moves from the non-working position toward the working position as the engine speed increases, after the compression of the release spring has been completed and before the compression of the clutch spring starts, a dead zone appears that stops the movement of the linkage member (stops at the movement amount α in the figure).

[0012] Then, when the engine speed further increases and the pressing load applied to the linkage member reaches the set load of the clutch spring (at time P2 in the figure), the compression of the clutch spring begins, so the linkage member starts to move again and passes through the dead zone. However, because the clutch plates are pressed against each other and power is transmitted after having passed through the dead zone, a sense of surprise occurs when power is transmitted and operability may be affected.

[0013] The present applicant has studied a power transmission device in which a clutch member is divided into two so that engine braking can be satisfactorily applied. The power transmission device includes: a first clutch member, which is connected to an output member; a second clutch member, to which a driven side clutch plate is attached; and a reverse torque transmission cam, which can press the driving side clutch plate and the driven side clutch plate against each other by moving the second clutch member when a rotational force is input to the first clutch member via the output member. In setting a device for suppressing a sense of surprise, the present applicant has carefully studied the effective use of space obtained by the arrangement of the first clutch member and the second clutch member.

[0014] The present invention has been made in consideration of such circumstances, and its object is to provide a power transmission device that can suppress a sense of surprise during power transmission and can improve operability while effectively utilizing a space obtained by arranging a first clutch member and a second clutch member.

[0015] Solution to the problem

[0016] According to the invention described in the first aspect, a power transmission device includes: a clutch housing, which rotates together with an input member, which is rotated by the driving force of the engine of a vehicle, and a plurality of driving side clutch plates are attached to the clutch housing; a clutch member, a plurality of driven side clutch plates formed alternately with the plurality of driving side clutch plates of the clutch housing are attached to the clutch member, and the clutch member is connected to an output member capable of rotating the wheels of the vehicle; a pressure member, which can be moved between a working position and a non-working position, in which the pressure member presses the plurality of driving side clutch plates and the plurality of driven side clutch plates against each other so as to be able to transmit the driving force of the engine to the wheels, and in which the pressure member releases the pressing force between the plurality of driving side clutch plates and the plurality of driven side clutch plates so as to be able to stop transmitting the driving force of the engine to the wheels; a weight member, which is arranged in a groove extending in the radial direction of the clutch housing, and the weight member is generated due to the rotation of the clutch housing. a linkage member capable of moving from a radially inner position to a radially outer position in the groove portion due to centrifugal force; a linkage member capable of moving the pressure member from the non-working position to the working position when the counterweight member moves from the radially inner position to the radially outer position; a release spring capable of maintaining the pressure member in the non-working position, the release spring being compressed when the linkage member moves and the pressure member moves from the non-working position toward the working position, and the release spring being capable of applying an urging force while allowing the linkage member and the pressure member to move until the plurality of driving side clutch plates and the plurality of driven side clutch plates reach an engaged state before the plurality of driving side clutch plates and the plurality of driven side clutch plates are pressed against each other; and a clutch spring, after the plurality of driving side clutch plates and the plurality of driven side clutch plates have reached the engaged state, the clutch spring being compressed during the movement of the linkage member, and the clutch spring being capable of applying a pressing force between the plurality of driving side clutch plates and the plurality of driven side clutch plates while allowing the linkage member to move.The clutch member includes: a first clutch member, which is connected to the output member; a second clutch member, wherein the plurality of driven side clutch plates are attached to the second clutch member; a reverse torque transmission cam, which is capable of pressing the plurality of driving side clutch plates and the plurality of driven side clutch plates against each other by moving the second clutch member when a rotational force is input to the first clutch member via the output member; and the power transmission device includes a buffer member, which is disposed between the first clutch member and the second clutch member, and the buffer member is capable of applying an urging force by being compressed during the movement of the linkage member and the movement of the pressure member from the non-working position toward the working position, while allowing the linkage member and the pressure member to move.

[0017] According to the invention described in claim 2, in the power transmission device described in claim 1, the buffer member is formed of a spring having a set load such that the spring is compressed before the clutch spring starts to be compressed.

[0018] According to the invention described in claim 3, in the power transmission device according to claim 1 or claim 2, the buffer member is accommodated in an accommodation recess formed in surfaces of the first clutch member and the second clutch member facing each other.

[0019] According to the invention described in claim 4, in the power transmission device according to claim 3, the accommodating recess is constituted by an annular groove, and the buffer member is constituted by a spring having an annular shape conforming to the shape of the groove.

[0020] According to the invention described in the fifth aspect, in the power transmission device according to the fourth aspect, the reverse torque transmission cam is formed into a plurality of annular shapes in the surfaces where the first clutch member and the second clutch member face each other, and the accommodating recess is formed into a concentric circle shape at a position adjacent to the reverse torque transmission cam.

[0021] Advantageous Effects of the Invention

[0022] Through the invention described in the first aspect, the sense of surprise during power transmission can be suppressed and operability can be improved while effectively utilizing the space obtained by the arrangement of the first clutch member and the second clutch member, because the power transmission device includes a buffer member, which is placed between the first clutch member and the second clutch member, and the buffer member is compressed during the movement of the linkage member and the movement of the pressure member from the non-working position toward the working position, thereby being able to apply a urging force while allowing the linkage member and the pressure member to move.

[0023] According to the invention described in claim 2, the unexpected feeling during power transmission can be more reliably suppressed because the buffer member is composed of a spring having a set load that causes the spring to be compressed before the clutch spring starts to be compressed.

[0024] Through the invention described in the third aspect, position displacement of the buffer member that may occur when the first clutch member moves relative to the second clutch member in the case of a buffer member can be avoided because the buffer member is accommodated in a accommodating recess formed in the surfaces of the first clutch member and the second clutch member facing each other.

[0025] Through the invention described in the fourth aspect, the urging force generated by the buffer member can be applied to the second clutch member, etc. basically evenly, and the urging force can be applied stably because the accommodating recess is composed of an annular groove and the buffer member is composed of a spring having an annular shape that matches the shape of the groove.

[0026] Through the invention described in the fifth aspect, the reverse torque transfer cam can reliably and stably move the second clutch component, and the buffer component can reliably and stably apply the urging force, because the reverse torque transfer cam is formed into a plurality of annular shapes in the surfaces where the first clutch component and the second clutch component face each other, and the accommodating recess is formed into a concentric circle shape at a position adjacent to the reverse torque transfer cam. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] [ Figure 1 ] is an external view of a power transmission device according to an embodiment of the present invention.

[0028] [ Figure 2 ] is a longitudinal sectional view illustrating the internal structure of the power transmission device.

[0029] [ Figure 3 ] is a schematic diagram of the driving side clutch plate, driven side clutch plate, reverse torque transmission cam, etc. of the power transmission device.

[0030] [ Figure 4 ] is a three-dimensional view of the housing portion of the clutch housing of the power transmission device.

[0031] [ Figure 5 ] is a three-dimensional view of the cover portion of the clutch housing of the power transmission device.

[0032] [ Figure 6 ] are three side views of the first clutch component of the power transmission device.

[0033] [ Figure 7 ] is a three-side view of the second clutch component of the power transmission device.

[0034] [ Figure 8 ] is a three-side view of the pressure component of the power transmission device.

[0035] [ Fig. 9 ] is a stereoscopic view illustrating a first clutch member, a second clutch member, a pressure member and a bearing retaining member of the power transmission device before assembly.

[0036] [ Fig.10 ] is a stereoscopic view illustrating a first clutch member, a second clutch member, a pressure member and a bearing retaining member of the power transmission device before assembly.

[0037] [ Fig.11 ] is a stereoscopic view illustrating a first clutch member, a second clutch member, a pressure member and a bearing retaining member of the assembled power transmission device.

[0038] [ Fig.12 ] are three side views of the bearing retaining component of the power transmission device.

[0039] [ Fig.13 ] is a schematic diagram illustrating the function of the pressure-contact assist cam of the power transmission device.

[0040] [ Fig.14 ] is a schematic diagram illustrating the function of the reverse torque limiter cam of the power transmission device.

[0041] [ Fig.15 ] is a plan view of a first clutch member and a second clutch member of a power transmission device assembled together, illustrating a state in which a side surface of a protrusion and a first contact surface (torque transmission portion) are in contact with each other.

[0042] [ Fig.16 ] is a plan view of the first clutch member and the second clutch member of the power transmission device assembled together, illustrating a state in which the other side surface of the protrusion and the second contact surface (movement limiting portion) are in contact with each other.

[0043] [ Fig.17 ] is a schematic diagram illustrating the function of the reverse torque transfer cam of the power transmission device in the state before the reverse torque transfer cam starts to work.

[0044] [ Fig.18 ] is a schematic diagram illustrating the function of the reverse torque transmission cam of the power transmission device in a state after the reverse torque transmission cam has started working.

[0045] [ Fig.19] is a schematic diagram illustrating a buffer member of a power transmission device accommodated in an accommodating recess.

[0046] [ Fig. 20 ] is a schematic diagram illustrating a state in which a release spring of a power transmission device applies an urging force to both a bearing retaining member and a pressure member.

[0047] [ Fig.21 ] is a three-side view of the release spring of the power transmission device.

[0048] [ Fig. 22 ] is a graph showing the movement amount and pressing load of the linkage component of the power transmission device.

[0049] [ Fig.23 ] is a graph showing the movement amount and pressing load of a linkage component of a power transmission device according to another embodiment of the present invention.

[0050] [ Fig.24 ] is a longitudinal sectional view of a power transmission device according to another embodiment of the present invention.

[0051] [ Fig.25 ] is a longitudinal sectional view of a power transmission device according to another embodiment of the present invention.

[0052] [ Fig.26 ] is a longitudinal sectional view of a power transmission device according to another embodiment of the present invention.

[0053] [ Fig. 27 ] is a longitudinal sectional view of a power transmission device according to another embodiment of the present invention (with a buffer member 12').

[0054] [ Fig.28 ] show a plan view and a side view of a buffer component of a power transmission device.

[0055] [ Fig.29 ] is a three-dimensional view of the buffer component of the power transmission device.

[0056] [ Fig.30 ] is a longitudinal sectional view of a power transmission device according to another embodiment of the present invention (a reverse torque transmission cam is provided at the outer edge of the first clutch member 4a, and a buffer member composed of a conical disc spring is provided).

[0057] [ Fig.31 ] is a longitudinal sectional view of a power transmission device according to another embodiment of the present invention (a reverse torque transmission cam is provided at the outer edge of the first clutch member 4a, and a buffer member composed of a wave spring is provided).

[0058] [ Fig.32] is a graph showing the movement amount and pressing load of the linkage component of the existing power transmission device. DETAILED DESCRIPTION

[0059] Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

[0060] The power transmission device according to the present embodiment is a device provided in a vehicle such as a motorcycle, and is used to appropriately transmit or stop the transmission of the driving force of the engine to the transmission or toward the drive wheel side. Figures 1 to 12 As shown, the power transmission device mainly includes: a clutch housing 2, in which an input gear 1 (input member) is formed to rotate by the driving force of the engine of the vehicle; clutch members (a first clutch member 4a and a second clutch member 4b); a pressure member 5 attached to the clutch members (the first clutch member 4a and the second clutch member 4b); Figure 2 on the right side of the figure; a plurality of driving side clutch plates 6; a plurality of driven side clutch plates 7; a weight member 8, which is composed of a steel ball member that can move (roll) in the radial direction in the clutch housing 2; a linkage member 9; and an actuating member 10, which can be actuated by hand or an actuator (not shown). The symbol S in the figure represents a spring damper, the symbol B1 represents a roller bearing, and the symbols B2 and B3 represent thrust bearings, respectively.

[0061] When the driving force (rotational force) transmitted from the engine is input, the input gear 1 can rotate around the output shaft 3. The input gear 1 is coupled to the clutch housing 2 via rivets R or the like. The clutch housing 2 includes a housing portion 2a and a cover portion 2b. The housing portion 2a is composed of a cylindrical member (in Figure 2 The right side of the clutch housing 2 is open) and is connected to the input gear 1, and the cover portion 2b is attached to close the opening of the housing portion 2a. Due to the driving force of the engine, the clutch housing 2 can rotate with the rotation of the input gear 1.

[0062] like Figure 4 As shown in FIG. 1 , a plurality of cutouts 2aa are formed in the housing portion 2a of the clutch housing 2 so as to be arranged in the circumferential direction, and a plurality of drive side clutch plates 6 are attached to fit into the cutouts 2aa. Each drive side clutch plate 6 is composed of a substantially annular plate, is configured to be rotatable along with the rotation of the clutch housing 2, and is axially ( Figure 2 ) in the left or right direction.

[0063] In addition, if Figure 5As shown in FIG. 1 , a plurality of grooves 2ba extending in the radial direction of the cover portion 2b are formed in the bottom surface of the cover portion 2b of the clutch housing 2. The weight member 8 is provided in each of the plurality of grooves 2ba. When the clutch housing 2 is stopped (engine stopped or idling) and the clutch housing 2 is rotating at a low speed, the weight member 8 is located at a radially inner position ( Figure 2 When the clutch housing 2 rotates at a high speed, the weight member 8 is located at the radially outer side.

[0064] A plurality of driven side clutch plates 7 formed alternately with the driving side clutch plates 6 of the clutch housing 2 are attached to the clutch member (the first clutch member 4a and the second clutch member 4b). The clutch member is coupled to the output shaft 3 (output member) capable of rotating the wheels of the vehicle. The clutch member is constituted by assembling the first clutch member 4a and the second clutch member 4b.

[0065] like Figure 6 As shown, the first clutch member 4a is composed of a disc-shaped member, and a flange surface 4ac is formed along the peripheral portion of the disc-shaped member. The first clutch member 4a is configured so that the output shaft 3 is inserted into the insertion hole 4ad formed at the center thereof (see Figure 2 and Figure 6 ), and the first clutch member 4a and the output shaft 3 are coupled to each other in the rotation direction because the gears respectively formed therein are meshed with each other. Figure 6 , Fig. 9 and Fig.10 As shown, in the first clutch member 4a, an inclined surface 4aa constituting a pressure-contact assist cam and an inclined surface 4ab constituting a reverse torque limiter cam are formed.

[0066] like Figure 7 As shown, the second clutch member 4b is composed of an annular member and is configured so that the driven side clutch plate 7 is attached to the spline fitting portion 4ba (see FIG. 4 ) formed in the outer peripheral surface thereof by spline fitting. Figure 2 and Figure 7 ).like Figures 9 to 11 As shown, the pressure member 5 is assembled with the clutch members (the first clutch member 4a and the second clutch member 4b). A plurality of driving side clutch plates 6 and driven side clutch plates 7 in an alternately stacked state are attached to the flange surface 5c (see Figure 2 and Figure 8 ) and the flange surface 4ac of the first clutch member 4a (see Figure 2 and Figure 6 )between.

[0067] like Figure 8As shown, the pressure member 5 is composed of a disc-shaped member, and a flange surface 5c is formed along its peripheral portion. The pressure member 5 can be in the working position and the non-working position (see Figure 2 ), in the working position, the pressure member 5 presses the driving side clutch plate 6 and the driven side clutch plate 7 against each other so as to transmit the driving force of the engine to the wheels, and in the non-working position, the pressure member 5 releases the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7 so as to stop transmitting the driving force of the engine to the wheels.

[0068] More specifically, if Figure 7 , Fig. 9 and Fig.10 As shown, the spline fitting portion 4ba formed in the second clutch member 4b has a protrusion / recess shape integrally formed along substantially the entire circumference of the outer peripheral side surface of the second clutch member 4b. When the driven side clutch plate 7 is fitted into the groove of the spline fitting portion 4ba, the movement of the driven side clutch plate 7 in the rotational direction is restricted, while the movement of the driven side clutch plate 7 in the axial direction relative to the second clutch member 4b is allowed, and the driven side clutch plate 7 can rotate together with the second clutch member 4b.

[0069] The driven side clutch plates 7 and the driving side clutch plates 6 are alternately stacked, and the clutch plates 6 and 7 can be pressed against each other, or the pressing force between them can be released. That is, both the clutch plates 6 and 7 are allowed to slide in the axial direction of the second clutch member 4b. Figure 2 When the pressure member 5 moves leftward in the middle and its flange surface 5c moves toward the flange surface 4ac of the first clutch member 4a, the clutch plates 6 and 7 are pressed against each other to transmit the rotational force of the clutch housing 2 to the output shaft 3 via the second clutch member 4b and the first clutch member 4a. Figure 2 When the clutch housing 2 moves to the right and its flange surface 5c and the flange surface 4ac of the first clutch member 4a become separated from each other, the pressing force between the clutch plates 6 and 7 is released, and the first clutch member 4a and the second clutch member 4b stop following the rotation of the clutch housing 2 and stop transmitting the rotational force to the output shaft 3.

[0070] When the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other, the rotational force (engine driving force) input to the clutch housing 2 is transmitted to the wheel side via the output shaft 3 (output member). When the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is released, the rotational force (engine driving force) input to the clutch housing 2 can be prevented from being transmitted to the output shaft 3 (output member).

[0071] In addition, if Figure 6 , Figure 8 , Fig. 9 and Fig.10 As shown, in the present embodiment, inclined surfaces 4aa and 4ab are formed in the first clutch member 4a, and inclined surfaces 5a and 5b facing the inclined surfaces 4aa and 4ab are formed in the pressure member 5. That is, the inclined surface 4aa and the inclined surface 5a are in contact with each other to constitute a crimping auxiliary cam, and the inclined surface 4ab and the inclined surface 5b are in contact with each other to constitute a reverse torque limiter cam.

[0072] like Fig.13 As shown in FIG. 1 , when the engine speed increases and the rotational force input to the input gear 1 and the clutch housing 2 becomes capable of being transmitted to the output shaft 3 via the first clutch member 4a and the second clutch member 4b, a rotational force in direction a is applied to the pressure member 5 (the weight member 8 is in a radially outer position). Therefore, due to the action of the crimping auxiliary cam, a force in direction c in the figure is generated in the pressure member 5. Therefore, the flange surface 5c of the pressure member 5 is further in the direction toward the flange surface 4ac of the first clutch member 4a ( Figure 2 The driving side clutch plate 6 and the driven side clutch plate 7 are moved to the left in the middle, and the pressure member 5 increases the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7.

[0073] On the other hand, when the vehicle is running, when the speed of the output shaft 3 exceeds the speed of the input gear 1 and the clutch housing 2 and a Fig.14 When a reverse torque in direction b occurs, due to the action of the reverse torque limiter cam, the pressure member 5 moves in direction d in the figure to release the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7. Thus, damage to the power transmission device and the power source (engine side) caused by the reverse torque can be avoided.

[0074] The weight member 8 is disposed in a groove portion 2ba extending in the radial direction of the clutch housing 2 (in this embodiment, the cover portion 2b). The weight member 8 is moved from a radially inner position (see FIG. 1 ) in the groove portion 2ba by the centrifugal force generated when the clutch housing 2 rotates. Figure 2 ) is moved to the radially outer position to press the driving side clutch plate 6 and the driven side clutch plate 7 against each other. That is, the rolling surface (bottom surface) of the groove portion 2ba for the weight member 8 to roll has an upward slope from the radially inner position to the radially outer position. When the clutch housing 2 stops, the weight member 8 is maintained at the radially inner position due to the urging force of the release spring m. When the clutch housing 2 rotates, centrifugal force is applied to the weight member 8, and when the clutch housing 2 reaches a predetermined rotation speed, the weight member 8 is moved to the radially outer position along the upward slope.

[0075] The linkage member 9 is composed of an annular member provided in the clutch housing 2 (cover 2b). The linkage member 9 is engaged with a groove formed in the inner peripheral surface of the cover 2b and can rotate together with the clutch housing 2 and can rotate when the clutch housing 2 is in the clutch housing 2. Figure 2 When the weight member 8 moves from the radially inner position to the radially outer position, the linkage member 9 overcomes the urging force of the release spring m. Figure 2 The pressure member 5 can be moved to the left in the working position, and the pressure member 5 can be pressed to move the pressure member 5 from the non-working position to the working position.

[0076] The actuating member 10 can be operated by hand or by an actuator (see Figure 2 ) operating member, and the pressing force of the pressure member 5 between the driving side clutch plate 6 and the driven side clutch plate 7 can be released ( Figure 2 When a shift operation is performed, for example, by operating a clutch pedal, a clutch lever, etc. of the vehicle or by the operation of an actuator, the actuating member 10 moves in a direction to the right. Figure 2 The actuating member 10 moves rightward to contact the pressure member 5 via the bearing holding member C and moves the pressure member 5 from the working position to the non-working position. Therefore, by releasing the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7, the actuating member 10 can disengage the clutch (stop transmitting power).

[0077] like Figure 2 As shown, the bearing holding member C is coupled to the actuating member 10 and holds the bearing B1 interposed between the actuating member 10 and the pressure member 5. Fig.12 As shown in FIG. 1 , the bearing holding member C is composed of a cylindrical member with one end open, and includes an open end Ca and a top Cb located on the opposite side of the open end Ca. The bearing B1 according to the present embodiment is attached to the top Cb side in the bearing holding member C, and the cylindrical portion extends from the diameter-enlarged portion toward the open end Ca. In addition, although a ball bearing is used as the bearing B1 according to the present embodiment, another bearing such as a needle bearing may be used, for example.

[0078] In addition, if Figure 2 and Fig. 20 As shown, the opening end Ca of the bearing holding member C according to the present embodiment is assembled and attached to the recess 4d formed in the clutch member (first clutch member 4a), and is assembled with the inner peripheral wall surface 4da of the recess 4d by a socket joint (fitting joint). The recess 4d is composed of a circular recess, the shape of which is similar to the outer shape of the opening end Ca and has substantially the same size as the opening end Ca (strictly speaking, the size is slightly larger than the opening end Ca). By assembling the bearing holding member C into the recess 4d, positioning and centering are performed relative to the power transmission device.

[0079] In the shifting operation, when the actuating member 10 is moved in the gear shifting operation by, for example, operating a clutch pedal, a clutch lever, etc. of the vehicle or by the operation of an actuator, Figure 2 When the bearing retaining member C moves to the right, the bearing retaining member C moves together and contacts the pressure member 5 to move the pressure member 5 from the working position to the non-working position. Therefore, by releasing the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7, the clutch is disengaged (power transmission is stopped).

[0080] The release spring m can hold the pressure member 5 in the non-operating position and be compressed when the linkage member 9 moves and the pressure member 5 moves from the non-operating position toward the operating position. The release spring m can apply an urging force while allowing the linkage member 9 and the pressure member 5 to move until the driving side clutch plate 6 and the driven side clutch plate 7 reach an engaged state before being pressed against each other (a state in which the distance between the driving side clutch plate 6 and the driven side clutch plate 7 is zero and immediately before power transmission is performed due to pressing).

[0081] In addition, if Fig.21 As shown, the release spring m according to the present embodiment is composed of a conical disc spring, which can generate an urging force due to the displacement between the middle portion ma and the peripheral portion mb. Figure 2 and Fig. 20 As shown in FIG. 1 , the middle portion ma is attached to the top Cb of the bearing holding member C, and the peripheral portion mb is attached to the pressure member 5. The pressure member 5 has a protrusion 5d protruding in an annular shape, and the peripheral portion mb of the release spring m is engaged with and attached to the annular member g (e.g., a circlip, etc.) attached to the protrusion 5d. Therefore, the release spring m according to the present embodiment is attached to both the bearing holding member C and the pressure member 5, and the urging force (at Fig. 20 An urging force in the orientation indicated by number a2 in the figure) is applied to the pressure member 5, and an urging force (an urging force in the orientation indicated by symbol a1 in the figure) can be applied to the bearing holding member C to transmit the urging force to the actuating member 10.

[0082] The clutch spring 11 is composed of a coil spring placed between the linkage member 9 and the pressure member 5. When the linkage member 9 moves, the clutch spring 11 can press the pressure member 5 to move the pressure member 5 in the direction in which the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other. In addition, when the actuating member 10 is working, the clutch spring 11 can absorb the pressing force applied by the pressure member 5 to the linkage member 9.

[0083] The clutch spring 11 according to the present embodiment moves with the pressure member 5 without being compressed (deformed) until the driving side clutch plate 6 and the driven side clutch plate 7 reach the above-mentioned engagement state. After the driving side clutch plate 6 and the driven side clutch plate 7 have reached the engagement state, the clutch spring 11 is compressed during the movement of the linkage member 9, and a pressing force can be applied between the driving side clutch plate 6 and the driven side clutch plate 7 while allowing the linkage member 9 to move.

[0084] That is, when the weight member 8 moves from the radially inner position to the radially outer position and the linkage member 9 is pressed by the weight member 8 when the clutch housing 2 rotates, the pressing force is transmitted to the pressure member 5 via the clutch spring 11, causing the pressure member 5 to rotate. Figure 2 1 and 10. When the actuating member 10 is actuated in this state, although the pressure member 5 moves rightward in the figure due to the pressing force of the actuating member 10, the pressing force applied to the linkage member 9 is absorbed by the clutch spring 11, and the position of the linkage member 9 (the position of the weight member 8) is maintained.

[0085] Here, the power transmission device according to the present embodiment includes a reverse torque transmission cam (cam surfaces K1 and T1) which can move the second clutch member 4b to press the driving side clutch plate 6 and the driven side clutch plate 7 against each other when a rotational force is input to the first clutch member 4a via the output shaft 3 (output member). Figure 6 , Figure 7 , Fig. 9 and Fig.10 As shown, the reverse torque transmission cam is constituted by cam surfaces ( K1 , T1 ) formed integrally in the mating surfaces (mating surfaces when engaged) of the first clutch member 4 a and the second clutch member 4 b , respectively.

[0086] like Figure 6 and Fig. 9 As shown, the cam surface K1 is composed of a plurality of inclined surfaces formed along the entire circumference of the radial inner side of the flange surface 4ac of the first clutch member 4a (the mating surface with the second clutch member 4b). The cam surface K1 is formed in one end surface of each of the plurality of grooves K formed annularly along the peripheral portion of the first clutch member 4a. That is, a plurality of grooves K are formed in the first clutch member 4a so as to be arranged in its circumferential direction, and one end surface of each groove K is an inclined surface of the cam surface K1 constituting the reverse torque transmission cam. The other end surface of each groove K is a wall surface K2 extending in the axial direction of the first clutch member 4a.

[0087] like Figure 7 and Fig.10 As shown, the cam surface T1 is composed of a plurality of inclined surfaces formed along the entire circumference of the bottom surface of the second clutch member 4b (the mating surface with the first clutch member 4a). The cam surface T1 is formed in one end surface of each of the plurality of protrusions T formed annularly along the bottom surface of the second clutch member 4b. That is, a plurality of protrusions T are formed in the second clutch member 4b so as to be arranged in its circumferential direction, and one end surface of each protrusion T is an inclined surface of the cam surface T1 constituting the reverse torque transmission cam. The other end surface of each protrusion T is a wall surface T2 extending in the axial direction of the second clutch member 4b.

[0088] like Fig.17 As shown in FIG. 1 , when the protrusion T is fitted into the groove portion K to combine the first clutch member 4a and the second clutch member 4b with each other, the cam surface K1 and the cam surface T1 face each other to constitute a reverse torque transmission cam, and the wall surface K2 and the wall surface T2 face each other with a predetermined distance therebetween. When a rotational force is input to the first clutch member 4a via the output shaft 3, because the first clutch member 4a rotates relative to the second clutch member 4b, as shown in FIG. Fig.18 As shown, due to the cam action of the cam surface K1 and the cam surface T1, the second clutch member 4b is relative to the first clutch member 4a. Figure 2 and Fig.18 Move right in the middle.

[0089] like Figure 7 As shown, the pressing portion 4bb is formed in the second clutch member 4b on the extension line of the spline fitting portion 4ba. Figure 2 When the pressure member 5 moves rightward in the middle, the pressing portion 4bb presses the driven side clutch plate 7 on the leftmost side in the figure in the same direction, which is one of the driving side clutch plate 6 and the driven side clutch plate 7 attached in a stacked state. Therefore, even when the pressure member 5 is in the non-operating position, the driving side clutch plate 6 and the driven side clutch plate 7 can be pressed against each other, and when a rotational force is input from the output shaft 3 (output member), the rotational force can be transmitted to the engine side to apply engine braking.

[0090] In particular, the reverse torque transmission cam according to the present embodiment can cause the second clutch member 4b to move in a direction toward the linkage member 9 ( Figure 2 In other words, when the reverse torque transmission cam starts to work and causes the second clutch member 4b to move upward to the right in the middle, the contact between the linkage member 9 and the weight member 8 is maintained. Figure 2When the clutch plate 6 and the driven clutch plate 7 are moved to the right in the middle, the reverse torque transmission cam presses the driving side clutch plate 6 and the driven side clutch plate 7 against each other and presses the pressure member 5 in the same direction. Therefore, the pressing force is transmitted to the linkage member 9 via the clutch spring 11, and the contact between the linkage member 9 and the weight member 8 is maintained.

[0091] If the linkage member 9 and the weight member 8 are separated from each other when the reverse torque transmission cam is in operation, even when the weight member 8 subsequently moves between the radially inner position and the radially outer position as the clutch housing 2 rotates, the linkage member 9 cannot follow the movement. In contrast, in the present embodiment, the contact between the linkage member 9 and the weight member 8 can be maintained even when the reverse torque transmission cam is in operation, so the linkage member 9 can stably follow the movement of the weight member 8.

[0092] In addition, the plurality of cam surfaces K1 and T1 of the reverse torque transmission cam according to the present embodiment are formed along the annular shape of the driven side clutch plate 7 attached to the second clutch member 4b. That is, the cam surfaces K1 and T1 are formed along the projected image shape (annular shape) of the driven side clutch plate 7, and when the reverse torque transmission cam is in operation, the driven side clutch plate 7 is pressed by the pressing portion 4bb. Therefore, due to the cam action of the reverse torque transmission cam, the pressing portion 4bb can apply a substantially uniform pressing force to the driven side clutch plate 7, and can more effectively press the driving side clutch plate 6 and the driven side clutch plate 7 against each other.

[0093] In addition, the reverse torque transmission cam (the cam composed of the cam surface K1 and the cam surface T1) according to the present embodiment can start operating before the reverse torque limiter cam (the cam composed of the inclined surface 4ab and the inclined surface 5b) starts operating. That is, the gap between the cam surface K1 and the cam surface T1 (the size of the gap) is smaller than the gap between the inclined surface 4ab and the inclined surface 5b (the size of the gap), and the reverse torque transmission cam can start operating before the reverse torque limiter cam starts operating.

[0094] In addition, the power transmission device according to the present embodiment includes: a torque transmission portion, which is formed in each of the first clutch member 4a and the second clutch member 4b, and can transmit the rotational force that has been transmitted to the second clutch member 4b to the first clutch member 4a without using a reverse torque transmission cam (cam surface K1 and cam surface T1); and a movement amount limiting portion, which is formed in each of the first clutch member 4a and the second clutch member 4b, and limits the movement amount of the second clutch member 4b due to the reverse torque transmission cam (cam surface K1 and cam surface T1).

[0095] That is, Figure 6 and Fig. 9 As shown, a plurality of (three in the present embodiment) protrusions F are integrally formed in the first clutch member 4a so as to be arranged at regular intervals in the circumferential direction. Figure 7 and Fig. 9 As shown, the inwardly extending protrusion G is integrally formed in the second clutch member 4b. Fig.15 and Fig.16 As shown, when the first clutch member 4a and the second clutch member 4b are assembled together, a protrusion F is placed between the two protrusions G, one side surface F1 of the protrusion F and a contact surface (first contact surface G1) of one of the protrusions G face each other, and the other side surface F2 of the protrusion F and a contact surface (second contact surface G2) of the other protrusion G face each other.

[0096] One side surface F1 of the protrusion F formed in the first clutch member 4a and the first contact surface G1 of the protrusion G formed in the second clutch member 4b constitute a torque transmission portion according to the present embodiment. Fig.15 As shown in FIG. 1 , when the pressure member 5 moves to the working position to press the driving side clutch plate 6 and the driven side clutch plate 7 against each other and engage the clutch (transmit the driving force), the wall surface K2 of the groove portion K and the wall surface T2 of the protrusion T of the reverse torque transmission cam are kept in a separated state (see FIG. 1 ). Fig.17 ), one side surface F1 of the protrusion F and the first contact surface G1 of the protrusion G are in contact with each other, and the rotational force of the second clutch member 4b can be received and transmitted to the first clutch member 4a.

[0097] The other side surface F2 of the protrusion F formed in the first clutch member 4a and the second contact surface G2 of the other protrusion G formed in the second clutch member 4b constitute the movement amount limiting portion according to the present embodiment. That is, when the rotational force is input to the first clutch member 4a via the output shaft 3, the first clutch member 4a and the second clutch member 4b rotate relative to each other. Therefore, the second clutch member 4b moves due to the cam action of the cam surface K1 of the groove portion K and the cam surface T1 of the protrusion T of the reverse torque transmission cam (see Fig.18 ). When the movement amount reaches the set value, Fig.16 As shown, the other side surface F2 of the protrusion F and the second contact surface G2 of the protrusion G are in contact with each other, and the rotation of the second clutch member 4b relative to the first clutch member 4a is restricted, so when the reverse torque transfer cam works, the movement amount of the second clutch member 4b can be limited.

[0098] In the present embodiment, the protrusion F is formed in the first clutch member 4a, and the protrusion G is formed in the second clutch member 4b. Alternatively, the protrusion G may be formed in the first clutch member 4a, and the protrusion F may be formed in the second clutch member 4b. In this case, one side surface F1 of the protrusion F formed in the second clutch member 4b and the first contact surface G1 of one protrusion G formed in the first clutch member 4a constitute the torque transmission portion according to the present embodiment. The other side surface F2 of the protrusion F formed in the second clutch member 4b and the second contact surface G2 of the other protrusion G formed in the first clutch member 4a constitute the movement amount limiting portion according to the present embodiment.

[0099] Next, the function of the reverse torque transmission cam in the present embodiment will be described.

[0100] like Figure 2 As shown, when the engine is stopped or idling, since the driving force of the engine is not transmitted to the input gear 1, or the rotation speed of the input gear 1 is low, the weight member 8 is in the radially inner position, and the pressure member 5 is in the non-operating position. At this time, when the rotational force is input to the first clutch member 4a via the output shaft 3 (output member), due to the cam action of the reverse torque transmission cam, the second clutch member 4b moves rightward in the figure, and the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other to transmit the rotational force to the engine side.

[0101] When the vehicle starts to move after having stopped or idling, the rotation speed of the input gear 1 changes from a low rotation speed to a high rotation speed (intermediate rotation speed range), the weight member 8 is located between the radially inner position and the radially outer position, and the pressure member 5 is located in the working position. At this time, when the rotational force is input to the first clutch member 4a via the output shaft 3 (output member), for example, when the accelerator pedal is released on a downhill slope, the second clutch member 4b moves rightward in the figure due to the cam action of the reverse torque transmission cam, and the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other to transmit the rotational force to the engine side.

[0102] After the vehicle starts, when the vehicle accelerates and runs in the high speed range, since the rotation speed of the input gear 1 is high, the weight member 8 is located in the radially outer position, and the pressure member 5 is located in the working position. At this time, when the rotational force is input to the first clutch member 4a via the output shaft 3 (output member) in response to downshifting, etc., the second clutch member 4b moves rightward in the figure due to the cam action of the reverse torque transmission cam, and the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other to transmit the rotational force to the engine side.

[0103] Here, the present embodiment includes a buffer member 12, which is placed between the first clutch member 4a and the second clutch member 4b, and the buffer member 12 can apply an urging force by being compressed (spring deformation) during the movement of the linkage member 9 and the movement of the pressure member 5 from the non-operating position toward the operating position, while allowing the linkage member 9 and the pressure member 5 to move. The buffer member 12 is composed of a spring with a set load, which makes the spring compressed before the clutch spring 11 starts to be compressed. Figure 2 , Figure 3 and Fig.21 As shown, the buffer member 12 is assembled by being accommodated in an accommodating recess 4c formed in surfaces of the first clutch member 4a and the second clutch member 4b facing each other (specifically, a surface of the first clutch member 4a facing the second clutch member 4b).

[0104] More specifically, if Figure 6 As shown, the receiving recess 4c is composed of an annular groove, and the buffer member 12 is composed of a conical disc spring having an annular shape that conforms to the shape of the groove. Fig.19 As shown, the accommodating recess 4c is composed of a groove having a radially inner wall surface 4ca and a radially outer wall surface 4cb; and the buffer member 12 composed of an annular spring conforms to the shape of the groove and is fitted into the accommodating recess 4c.

[0105] As described above, the reverse torque transmission cam according to the present embodiment is formed in a plurality of annular shapes in the surfaces of the first clutch member 4a and the second clutch member 4b facing each other. Figure 6 As shown, the accommodating recess 4c is formed in a concentric shape at a position adjacent to the reverse torque transmission cam (in the present embodiment, radially inward of the position where the reverse torque transmission cam is formed). In the present embodiment, the accommodating recess 4c is formed in a concentric shape at a position radially inward of the position of the reverse torque transmission cam. However, the accommodating recess 4c may be formed in a concentric shape at a position radially outward of the position of the reverse torque transmission cam. In this case, as Fig.24 As shown, the buffer member 12 may be configured to apply an urging force to a portion (disc pack) where the driving side clutch plates 6 and the driven side clutch plates 7 are stacked in a direction in which the driving side clutch plates 6 and the driven side clutch plates 7 are pressed against each other.

[0106] Next, the function of the buffer member 12 according to the present embodiment will be described in comparison with a conventional device not having the buffer member 12 .

[0107] First, refer to Fig.32The function of the case where the buffer member 12 is not provided compared with the present embodiment is described by using a graph (a graph having a movement amount (mm) of the linkage member 9 along the horizontal axis and a pressing load (N) generated in the linkage member 9 along the vertical axis). Fig.32 In the graph of , P1 represents the pressing load of the linkage member 9 when the deformation (compression) of the release spring m is maximum (when the maximum load of the release spring m is reached), and P2 represents the pressing load of the linkage member 9 when the clutch spring 11 begins to deform (when the set load of the clutch spring 11 is reached). Fig. 22 and Fig.23 In FIG. 1 , P3 represents the pressing load of the interlocking member 9 when the buffer member 12 starts to deform (when the set load of the buffer member 12 is reached).

[0108] In the process that the engine speed increases and the counterweight member 8 moves from the radially inner position to the radially outer position to move the linkage member 9, the release spring m is deformed and the clutch spring 11 is not deformed (that is, the linkage member 9 and the pressure member 5 move together) until the movement amount of the linkage member 9 reaches α, and, when the movement amount of the linkage member 9 reaches α, although the pressing load (N) increases from P1 to P2, the linkage member 9 stops moving and becomes a dead zone.

[0109] When the pressing load (N) reaches P2 (the set load of the clutch spring 11) from this state, the clutch spring 11 starts to deform, and the pressing load (N) increases with the movement of the linkage member 9. Therefore, the linkage member 9 and the pressure member 5 stop until the pressing load (N) reaches P2 from P1, and once the pressing load (N) reaches P2, the clutch spring 11 starts to be compressed, the clutch plates (the driving side clutch plate 6 and the driven side clutch plate 7) are pressed against each other to transmit power, and thus a sense of surprise is generated when power is transmitted.

[0110] In contrast, the present embodiment includes a buffer member 12, which is composed of a spring having a set load (the set load is set to P3) so that the spring is compressed before the clutch spring 11 starts to be compressed during the movement of the linkage member 9. Fig. 22 As shown, the cushioning member 12 starts to be compressed (starts to be deformed) when the movement amount of the interlocking member 9 reaches β, and the compression continues until the pressing load reaches P2.

[0111] That is, according to the curve diagram, in the process that the linkage member 9 moves as the engine speed increases and the counterweight member 8 moves from the radially inner position to the radially outer position, the buffer member 12 begins to be compressed when the movement amount of the linkage member 9 becomes β and the pressing load (N) reaches P3, and then, when the movement amount of the linkage member 9 reaches α and the pressing load (N) becomes P2, the clutch spring 11 begins to deform (begins to be compressed).

[0112] Therefore, when the linkage member 9 starts to move, the pressing load (N) becomes the set load of the release spring m, and the release spring m starts to deform (starts to be compressed). When the movement amount of the linkage member 9 reaches β, the buffer member 12 starts to deform (starts to be compressed). Subsequently, when the movement amount of the linkage member 9 reaches α, the release spring m reaches the maximum load and the pressing load (N) reaches the set load (P2) of the clutch spring 11, whereby the clutch spring 11 starts to deform (starts to be compressed). Until the clutch spring 11 reaches the maximum load (the upper limit of the working load), the clutch spring 11 continues to be compressed (continues to deform) due to the movement of the linkage member 9.

[0113] Therefore, when the movement amount of the linkage member 9 is between β and α, the buffer member 12 is continuously compressed (deformed) to allow the linkage member 9 to move during the process of increasing the pressing load from P3 to P2. Therefore, the dead zone of the existing device can be reduced, and the weight member 8 and the linkage member 9 can be moved smoothly and continuously. Therefore, the impact when the clutch is engaged can be suppressed, and the unexpected feeling when the power is transmitted can be suppressed.

[0114] like Fig. 22 As shown in FIG. 1 , the cushioning member 12 is configured to be continuously compressed (continue to deform) when the pressing load (N) is between P3 and P2. Fig.23 As shown, the buffer member 12 can be set so that: from the time when the movement amount of the linkage member 9 becomes β and the pressing load (N) reaches P3, the buffer member 12 starts to be compressed (begins to deform); and the buffer member 12 is continuously compressed (continues to deform) until the pressing load (N) becomes P4 which is lower than P2. Even in this case, because the existing dead zone can be reduced than before, the weight member 8 and the linkage member 9 can be moved smoothly and continuously to suppress the impact when the clutch is engaged and suppress the unexpected feeling when the power is transmitted.

[0115] The present embodiment includes a buffer member 12, which is interposed between the first clutch member 4a and the second clutch member 4b, and the buffer member 12 can apply an urging force by being compressed in the process of the linkage member 9 moving and the pressure member 5 moving from the non-operating position toward the operating position, while allowing the linkage member 9 and the pressure member 5 to move. Therefore, through the present embodiment, it is possible to suppress the sense of surprise during power transmission and improve operability while effectively utilizing the space obtained by the arrangement of the first clutch member 4a and the second clutch member 4b.

[0116] The buffer member 12 according to the present embodiment is composed of a spring having a set load that causes the spring to be compressed before the clutch spring 11 starts to be compressed. Therefore, the unexpected feeling during power transmission can be more reliably suppressed. In particular, by appropriately setting the set load and the working load of the buffer member 12, the feeling during power transmission (drive start feeling) can be set in various ways according to the type of vehicle to which the present device is applied.

[0117] In addition, the buffer member 12 according to the present embodiment is accommodated in the accommodating recess 4c, which is formed in the surfaces of the first clutch member 4a and the second clutch member 4b facing each other. Therefore, the positional displacement of the buffer member 12 that may occur in the case involving the buffer member 12 when the first clutch member 4a moves relative to the second clutch member 4b can be avoided. The accommodating recess 4c according to the present embodiment is formed in the surface of the first clutch member 4a facing the second clutch member 4b. However, the accommodating recess 4c may be formed in the surface of the second clutch member 4b facing the first clutch member 4a.

[0118] In addition, the accommodating recess 4c according to the present embodiment is composed of an annular groove, and the buffer member 12 is composed of a spring having an annular shape that matches the shape of the groove. Therefore, the urging force generated by the buffer member 12 can be applied to the second clutch member 4b and the like substantially uniformly, and the urging force can be applied stably. The reverse torque transmission cam according to the present embodiment is formed into a plurality of annular shapes in the surfaces facing each other of the first clutch member 4a and the second clutch member 4b, and the accommodating recess 4c is formed into a concentric circle shape at a position adjacent to the reverse torque transmission cam. Therefore, the reverse torque transmission cam can be made to reliably and stably move the second clutch member 4b, and the buffer member 12 can be made to reliably and stably apply the urging force.

[0119] In addition, the bearing holding member C according to the present embodiment is composed of a cylindrical member with one end open, and the open end Ca is assembled and attached to the recess 4d formed in the clutch member (first clutch member 4a) (attached in a socket-engaged state). Therefore, it is easy to assemble the bearing holding member C, and the bearing holding member C can be stably operated when performing a shift operation.

[0120] The power transmission device includes: a release spring m, which can apply an urging force to the pressure member 5 while allowing the linkage member 9 and the pressure member 5 to move until the driving side clutch plate 6 and the driven side clutch plate 7 reach an engaged state before the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other; and the release spring m is attached to the bearing holding member C and the pressure member 5, applies an urging force to the pressure member 5, and can apply the urging force to the bearing holding member C to transmit the urging force to the actuating member 10. Therefore, the release spring m can also be used as a spring for preventing backlash of the shift operating device, and the number of components can be reduced.

[0121] Furthermore, the release spring m according to the present embodiment is composed of a conical disc spring that can generate an urging force due to displacement between the middle portion ma and the peripheral portion mb, the middle portion ma being attached to the bearing holding member C, and the peripheral portion mb being attached to the pressure member 5. Therefore, the urging force of the release spring m can be stably applied to both the bearing holding member C and the pressure member 5.

[0122] In addition, the clutch member according to the present embodiment includes: a first clutch member 4a coupled to the output shaft 3 (output member); a second clutch member 4b to which a driven side clutch plate 7 is attached; and a reverse torque transmission cam, which can press the driving side clutch plate 6 and the driven side clutch plate 7 against each other by moving the second clutch member 4b when a rotational force is input to the first clutch member 4a via the output shaft 3 (output member); and a recess 4d is formed in the first clutch member 4a. Therefore, it is possible to avoid the bearing holding member C from interfering with the movement of the second clutch member 4b due to the reverse torque transmission cam, and it is possible to enable the reverse torque transmission cam to smoothly move each of the bearing holding member C and the second clutch member 4b.

[0123] Through the above-described embodiment, the reverse torque transmission cam can move the second clutch member 4b in the direction toward the linkage member 9 to maintain the contact between the linkage member 9 and the weight member 8. Therefore, the driving side clutch plate 6 and the driven side clutch plate 7 can be pressed against each other to transmit the rotational force of the wheel side to the engine side to apply the engine brake, and actuation can be stably performed by the weight member 8 when the engine brake is applied.

[0124] The reverse torque transmission cam according to the present embodiment is composed of cam surfaces (K1, T1) formed integrally in the first clutch member 4a and the second clutch member 4b, respectively, and the cam surfaces (K1, T1) are formed in the mating surfaces of the first clutch member 4a and the second clutch member 4b, respectively. Therefore, the reverse torque transmission cam can reliably and smoothly move the second clutch member 4b.

[0125] Furthermore, the power transmission device includes a pressure-contact assisting cam which is constituted by the inclined surface 4aa of the first clutch member 4a and the inclined surface 5a of the pressure member 5 which face each other, and which increases the pressure-contacting force between the driving side clutch plate 6 and the driven side clutch plate 7 when the rotational force input to the input gear 1 (input member) becomes transmittable to the output shaft 3 (output member). Therefore, in addition to the pressure-contacting force generated by the movement of the weight member 8 by the centrifugal force, the pressure-contacting force due to the pressure-contact assisting cam can be applied, and the driving side clutch plate 6 and the driven side clutch plate 7 can be pressed against each other more smoothly and more reliably.

[0126] In addition, the power transmission device includes a reverse torque limiter cam which is composed of the inclined surface 4ab of the first clutch member 4a and the inclined surface 5b of the pressure member 5 facing each other, and when the rotation speed of the output shaft 3 (output member) exceeds the rotation speed of the input gear 1 (input member) and the clutch member (first clutch member 4a) and the pressure member 5 rotate relative to each other, the reverse torque limiter cam can release the pressing force between the driving side clutch plate 6 and the driven side clutch plate 7. Therefore, when the weight member 8 is in the radially outer position, it is possible to avoid excessive driving force being transmitted to the engine side via the input gear 1, and the reverse torque transmission cam can be reliably actuated because the reverse torque transmission cam is actuated before the reverse torque limiter cam starts to work.

[0127] In addition, the present embodiment includes: a reverse torque transmission cam that can move the second clutch member 4b to press the driving side clutch plate 6 and the driven side clutch plate 7 against each other when the rotational force is input to the first clutch member 4a via the output shaft 3 (output member); and a torque transmission portion that is formed in each of the first clutch member 4a and the second clutch member 4b and can transmit the rotational force that has been transmitted to the second clutch member 4b to the first clutch member 4a without using the reverse torque transmission cam (cam surface K1 and cam surface T1). Therefore, the engine brake can be applied by pressing the driving side clutch plate 6 and the driven side clutch plate 7 against each other to transmit the rotational force of the wheel side to the engine side, and the power transmission can be stably performed when the weight member 8 moves to the radially outer position and the pressure member 5 moves to the working position.

[0128] In addition, the power transmission device includes a movement amount limiting portion that is formed in each of the first clutch member 4a and the second clutch member 4b and limits the movement amount of the second clutch member 4b due to the reverse torque transmission cam. Therefore, the reverse torque transmission cam can move the second clutch member 4b within a set range.

[0129] Furthermore, the protrusion F is formed in any one of the first clutch member 4a and the second clutch member 4b, the torque transmission portion is composed of one side surface F1 of the protrusion F and a first contact surface G1 that receives the rotational force by contacting the one side surface F1, and the movement amount limiting portion is composed of the other side surface F2 of the protrusion F and a second contact surface G2 that can limit the movement amount by contacting the other side surface F2. Therefore, the protrusion F can be used as a torque transmission portion and a movement amount limiting portion at the same time.

[0130] So far, the present embodiment has been described. However, the present invention is not limited to these. For example, Fig.25 and Fig.26 As shown, the present invention can be applied to a power transmission device in which a weight member 8 is movably provided in the housing portion 2a of the clutch housing 2. As in the above-described embodiment, the power transmission device includes a first clutch member 4a, a second clutch member 4b, a reverse torque transmission cam, and a buffer member 12 interposed between the first clutch member 4a and the second clutch member 4b.

[0131] Fig.25 An embodiment is shown in which the damping member 12 is attached to the surface of the first clutch member 4a facing the second clutch member 4b. Fig.26An embodiment is shown in which a buffer member 12 that applies an urging force to a portion (disc pack) of the first clutch member 4a where the driving side clutch plate 6 and the driven side clutch plate 7 are stacked is attached to the surface. The bearing holding member C' can be moved by the actuating member 10', and the release spring m' is composed of a coil spring attached to both the bearing holding member C' and the pressure member 5.

[0132] In addition, instead of the buffer member 12 composed of a conical disc spring, another elastic member may be used. Fig. 27 As shown, a buffer member 12' composed of a wave spring can be disposed in the receiving recess 4c. Fig.28 and Fig.29 As shown, the wave spring is composed of a C-shaped member having a cutout portion 12'a in a portion of the ring, and the wave spring has a wave shape relative to the thickness direction t and can generate elastic force. The wave spring is placed between the first clutch member 4a and the second clutch member 4b, and the wave spring can be compressed during the movement of the linkage member 9 and the movement of the pressure member 5 from the non-operating position to the operating position, thereby applying an urging force while allowing the linkage member 9 and the pressure member 5 to move.

[0133] In the power transmission device shown in the figure, the bearing holding member C has a plurality of (three in the present embodiment) communication holes Cc formed in the side wall thereof, and allows the oil supplied to the inside of the bearing holding member C to flow to the outside via the oil flow path r. The actuating member 10" is engaged with the roller bearing B1 of the bearing holding member C, and the actuating member 10" can move the pressure member 5 between the working position and the non-working position by moving in the left-right direction in the figure due to the operation of the driver or the operation of the actuator.

[0134] In addition, if Fig.30 As shown, a reverse torque transmission cam (cam surface K1 and cam surface T1) can be provided in the outer peripheral portion of each of the first clutch member 4a and the second clutch member 4b. With this power transmission device, since the reverse torque transmission cam is provided in the outer peripheral portion of each of the first clutch member 4a and the second clutch member 4b, the effect of the cam can be enhanced, and the moving force of the second clutch member 4b can be set larger. In this figure, a buffer member 12 composed of a conical disc spring is provided on the radial inner side of the reverse torque transmission cam (cam surface K1 and cam surface T1). However, a buffer member 12' composed of a wave spring instead of a conical disc spring can be provided (such as Fig.31 shown).

[0135] In the present embodiment, the bearing retaining member C is composed of a cylindrical member with one end open, and the open end Ca is assembled and attached to the recess 4d formed in the clutch member (first clutch member 4a). However, a bearing retaining member having another shape may be used, and an attachment structure different from the configuration (so-called socket joint) of assembling the bearing retaining member into the recess formed in the clutch member may be used. Note that the power transmission device according to the present invention can be applied to various multi-disc clutch power transmission devices in addition to motorcycles, automobiles, three-wheeled or four-wheeled ATVs, general-purpose machines, etc.

[0136] Industrial Applicability

[0137] The clutch member can be applied to a power transmission device having a different external shape or having another additional function, as long as the power transmission device includes: a first clutch member, which is connected to an output member; a second clutch member, to which a driven side clutch plate is attached; a reverse torque transmission cam, which is capable of pressing the driving side clutch plate and the driven side clutch plate against each other by moving the second clutch member when a rotational force is input to the first clutch member via the output member; and a buffer member, which is placed between the first clutch member and the second clutch member, and which is capable of applying an urging force by being compressed during the movement of the linkage member and the movement of the pressure member from a non-working position to a working position, while allowing the linkage member and the pressure member to move.

[0138] Reference numerals list

[0139] 1 Input gear (input component)

[0140] 2 Clutch housing

[0141] 2a Housing

[0142] 2b Cover

[0143] 3 Output shaft (output component)

[0144] 4a First clutch member

[0145] 4aa Inclined surface (crimp assist cam)

[0146] 4ab Inclined surface (reverse torque limiter cam)

[0147] 4ac flange surface

[0148] 4ad Insertion hole

[0149] 4b Second clutch member

[0150] 4ba spline fitting part

[0151] 4bb Pressing part

[0152] 4c Accommodating recess

[0153] 4d concavity

[0154] 4da Inner wall surface

[0155] 5 Pressure components

[0156] 5a Inclined surface (crimp assist cam)

[0157] 5b Inclined surface (reverse torque limiter cam)

[0158] 5c Flange surface

[0159] 6 Drive side clutch plate

[0160] 7 Driven side clutch plate

[0161] 8. Counterweight component

[0162] 9 Linkage components

[0163] 10 Actuating member

[0164] 11 Clutch spring

[0165] 12 Buffer member (conical disc spring)

[0166] 12' buffer member (wave spring)

[0167] 12'a Incision

[0168] C Bearing retaining member

[0169] Ca Open end

[0170] Cb Top

[0171] Cc connecting hole

[0172] K slot

[0173] K1 Cam surface

[0174] K2 wall surface

[0175] T-tab

[0176] T1 Cam surface

[0177] T2 wall surface

[0178] F protrusion

[0179] G Protrusion

[0180] G1 First contact surface

[0181] G2 Second contact surface

[0182] m Release spring

[0183] r Oil flow path

Claims

1. A power transmission device, comprising: a clutch member accommodated in a clutch housing that rotates together with an input member that is rotated by a driving force of an engine of a vehicle, and to which a plurality of driving-side clutch plates are attached, to which a plurality of driven-side clutch plates that are formed alternately with the plurality of driving-side clutch plates are attached, and which is coupled to an output member capable of rotating wheels of the vehicle; a pressure member movable between an operating position and a non-operating position, wherein at the operating position, the pressure member presses the plurality of driving side clutch plates and the plurality of driven side clutch plates against each other so as to enable the driving force of the engine to be transmitted to the wheels, and at the non-operating position, the pressure member releases the pressing force between the plurality of driving side clutch plates and the plurality of driven side clutch plates so as to stop transmitting the driving force of the engine to the wheels; a weight member movable from a radially inner position to a radially outer position due to a centrifugal force generated when the clutch housing rotates; a linkage member capable of moving the pressure member from the non-operating position to the operating position when the weight member moves from the radially inner position to the radially outer position, Wherein, the clutch component further comprises: a first clutch member coupled to the output member; a second clutch member to which the plurality of driven side clutch plates are attached; and a reverse torque transmission cam capable of pressing the plurality of driving side clutch plates and the plurality of driven side clutch plates against each other by moving the second clutch member when a rotational force is input to the first clutch member via the output member; and A buffer member is disposed between the first clutch member and the second clutch member, and the buffer member is capable of applying an urging force by being compressed during the movement of the linkage member and the movement of the pressure member from the non-working position toward the working position, while enabling the linkage member and the pressure member to move.

2. The power transmission device according to claim 1, wherein: The buffer member is constituted by a spring having a set load such that the spring is compressed before the clutch spring starts to be compressed.

3. The power transmission device according to claim 1 or 2, wherein: The buffer member is accommodated in an accommodation recess formed in surfaces of the first clutch member and the second clutch member facing each other.

4. The power transmission device according to claim 3, in, The receiving recess is formed by an annular groove, and The buffer member is composed of a spring having an annular shape that matches the groove.

5. The power transmission device according to claim 4, wherein: The reverse torque transmission cams are formed in a plurality of annular shapes in the surfaces of the first clutch member and the second clutch member facing each other, and the accommodating recesses are formed in concentric circle shapes at positions adjacent to the reverse torque transmission cams.

6. A power transmission device, comprising: a clutch member accommodated in a clutch housing that rotates together with an input member that is rotated by a driving force of an engine of a vehicle, and to which a plurality of driving-side clutch plates are attached, to which a plurality of driven-side clutch plates that are formed alternately with the plurality of driving-side clutch plates are attached, and which is coupled to an output member capable of rotating wheels of the vehicle; a weight member movable from a radially inner position to a radially outer position due to a centrifugal force generated when the clutch housing rotates; a linkage member, the linkage member switching the plurality of driving side clutch plates and the plurality of driven side clutch plates from a non-operating state to an operating state, in which the pressing force is released, and in which the plurality of driving side clutch plates and the plurality of driven side clutch plates are pressed against each other to be able to transmit the driving force of the engine to the wheels, Wherein, the clutch component further comprises: a first clutch member coupled to the output member; a second clutch member to which the plurality of driven side clutch plates are attached; and a reverse torque transmission cam capable of pressing the plurality of driving side clutch plates and the plurality of driven side clutch plates against each other by moving the second clutch member when a rotational force is input to the first clutch member via the output member; a buffer member capable of applying an urging force and causing the linkage member to move during the process in which the linkage member moves and the plurality of driving side clutch plates and the plurality of driven side clutch plates are switched from the non-operating state to the operating state, The reverse torque transmission cam includes a first portion having a first cam surface and a second portion having a second cam surface, the second cam surface facing the first cam surface when the second portion is arranged to face the first portion, and The second portion extends in an axial direction of the output member and overlaps the buffer member when viewed from a radial direction of the output member.

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