JP7256323B2 - power transmission device - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device capable of optionally transmitting or blocking the torque of an input member to an output member.

In general, a power transmission device provided in a motorcycle is for arbitrarily transmitting or interrupting the driving force of the engine to the transmission and the drive wheels. It has a coupled output member, a clutch member coupled with the output member, and a pressure member that can approach or separate from the clutch member. The side clutch plate and the driven side clutch plate are brought into pressure contact to transmit power, and the pressure member is separated from the clutch member to release the pressure contact force between the driving side clutch plate and the driven side clutch plate. By doing so, the transmission of the power is cut off.

As a conventional power transmission device, for example, as disclosed in Patent Document 1, centrifugal force associated with rotation of the clutch housing moves the drive-side clutch plate and the driven clutch plate from the inner-diameter side position to the outer-diameter side position of the groove. A proposal has been made to provide a weight member that can be brought into pressure contact with the side clutch plate. According to such a conventional power transmission device, centrifugal force can be applied to the weight member by rotating the clutch housing as the engine is driven. The driving force of the engine can be transmitted to the wheels.

Further, in the conventional power transmission device, when the pressure member is in the operating position, an operating member capable of moving the pressure member to the non-operating position by a speed change operation is connected to the operating member, and the operating member and the pressure member are connected to each other. and a bearing holding member that holds the bearing interposed between the member. When a shift operation is performed manually or by an actuator, the operating member moves and presses the pressure member via the bearing holding member, releasing the pressure contact force of the clutch plate and interrupting power transmission. ing.

JP 2017-155884 A

However, the conventional power transmission device described above has the following problems.
The bearing holding member is attached to a projecting portion extending from the clutch member, and slides along the projecting portion in accordance with a shift operation to move the pressure member and release the pressing force of the clutch plate. Therefore, it is difficult to assemble to the projecting portion, and there is a possibility that sliding on the projecting portion may become unstable during gear shift operation.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and provides a power transmission device in which a bearing holding member can be easily assembled and in which the bearing holding member can be operated stably during a gear shift operation. to provide.

According to a first aspect of the present invention, there is provided a clutch member that rotates together with an input member that is rotated by the driving force of a vehicle engine and that is housed in a clutch housing to which a plurality of drive-side clutch plates are attached, wherein the drive-side clutch plates. and a plurality of driven-side clutch plates alternately formed, and a clutch member connected to an output member capable of rotating a wheel of a vehicle, and the drive-side clutch plate and the driven-side clutch plate are pressed against each other. an operating position in which the driving force of the engine can be transmitted to the wheels; and a pressure contact force between the driving side clutch plate and the driven side clutch plate is released so that the driving force of the engine is transmitted to the wheels. a pressure member movable between a non-operating position and a non-operating position capable of blocking the clutch housing; a weight member movable from an inner diameter side position to an outer diameter side position by centrifugal force accompanying rotation of the clutch housing; an operating member capable of moving the pressure member in a direction to release the pressure contact force between the clutch plate and the driven clutch plate; a bearing that supports the operating member; and a bearing holding member that holds the bearing, A bearing holding member comprising a cylindrical member having an open end, the open end of which is fitted into the clutch member to apply a biasing force from the pressure member to the bearing holding member in a direction toward the clutch member. and a spring that presses against the drive-side clutch plate and the driven-side clutch plate as the weight member moves from the inner diameter side position to the outer diameter side position. The bearing holding member is configured to switch from a non-operating state to an operating state in which the driving force of the engine can be transmitted to the wheels by being pressed against each other, and to move the pressure member in the axial direction of the output member. a state in which the open end is fitted into the clutch member when the pressure member moves in the axial direction of the output member as the weight member moves from the inner diameter side position to the outer diameter side position; is configured to maintain

According to a second aspect of the present invention, there is provided a clutch member that rotates together with an input member that rotates under the driving force of a vehicle engine and that is accommodated in a clutch housing to which a plurality of drive-side clutch plates are attached, the drive-side clutch plates. and a plurality of driven-side clutch plates alternately formed, and a clutch member connected to an output member capable of rotating a wheel of a vehicle, and the drive-side clutch plate and the driven-side clutch plate are pressed against each other. an operating position in which the driving force of the engine can be transmitted to the wheels; and a pressure contact force between the driving side clutch plate and the driven side clutch plate is released so that the driving force of the engine is transmitted to the wheels. a pressure member movable between a non-operating position and a non-operating position capable of blocking the clutch housing; a weight member movable from an inner diameter side position to an outer diameter side position by centrifugal force accompanying rotation of the clutch housing; an operating member capable of moving the pressure member in a direction to release the pressure contact force between the clutch plate and the driven clutch plate; a bearing that supports the operating member; and a bearing holding member that holds the bearing, A bearing holding member comprising a cylindrical member having an open end, the open end of which is fitted into the clutch member to apply a biasing force from the pressure member to the bearing holding member in a direction toward the clutch member. and a spring that presses against the drive-side clutch plate and the driven-side clutch plate as the weight member moves from the inner diameter side position to the outer diameter side position. The bearing holding member is configured to switch from a non-operating state to an operating state in which the driving force of the engine can be transmitted to the wheels by being pressed against each other, and to move the pressure member in the axial direction of the output member. and a position relative to the clutch member is not changed when the pressure member moves in the axial direction of the output member as the weight member moves from the inner diameter side position to the outer diameter side position. is configured to

According to the inventions of claims 1 and 2, the bearing holding member can be easily assembled, and the bearing holding member can be operated stably during a shift operation.

1 is an external view showing a power transmission device according to an embodiment of the present invention; A longitudinal sectional view showing the internal configuration of the same power transmission device Schematic diagram showing a drive-side clutch plate, a driven-side clutch plate, a back torque transmission cam, etc., in the same power transmission device. FIG. 2 is a perspective view showing a housing portion of a clutch housing in the same power transmission device; FIG. 2 is a perspective view showing a cover portion of a clutch housing in the same power transmission device; A three-sided view showing the first clutch member in the same power transmission device. A three-sided view showing a second clutch member in the same power transmission device. A three-sided view showing a pressure member in the same power transmission device. FIG. 4 is a perspective view showing a state before assembly of the first clutch member, the second clutch member, the pressure member, and the bearing holding member in the same power transmission device; FIG. 4 is a perspective view showing a state before assembly of the first clutch member, the second clutch member, the pressure member, and the bearing holding member in the same power transmission device; FIG. 4 is a perspective view showing a state after assembly of the first clutch member, the second clutch member, the pressure member, and the bearing holding member in the same power transmission device; A three-sided view showing a bearing holding member in the same power transmission device. Schematic diagram for explaining the action of the press contact assist cam in the same power transmission device. Schematic diagram for explaining the action of the back torque limiter cam in the same power transmission device. FIG. 4 is a plan view showing a state in which the first clutch member and the second clutch member are assembled in the same power transmission device, and shows a state in which one side surface of the convex portion and the first contact surface (torque transmission portion) are in contact with each other; FIG. 10 is a view showing a state where the first clutch member and the second clutch member are assembled in the same power transmission device, and is a plane showing a state where the other side surface of the convex portion and the second contact surface (movement limit portion) are in contact; figure FIG. 4 is a diagram for explaining the action of the back torque transmission cam in the power transmission device, and is a schematic diagram showing a state before the back torque transmission cam is actuated; FIG. 4 is a diagram for explaining the action of the back torque transmission cam in the power transmission device, and is a schematic diagram showing a state after the back torque transmission cam is actuated; Schematic diagram showing a state in which a buffer member in the same power transmission device is housed in a housing recess. FIG. 2 is a schematic diagram for explaining that a release spring in the same power transmission device applies a biasing force to both a bearing holding member and a pressure member; A three-sided view showing a release spring in the same power transmission device. Graph showing the movement amount and pressing load of the interlocking member in the same power transmission device Graph showing movement amount and pressing load of an interlocking member in a power transmission device according to another embodiment of the present invention FIG. 4 is a vertical cross-sectional view showing a power transmission device according to another embodiment of the present invention; FIG. 4 is a perspective view showing a bearing holding member according to another embodiment of the present invention; A longitudinal sectional view showing a power transmission device to which the same bearing holding member is attached A longitudinal sectional view showing a power transmission device to which the same bearing holding member is attached (the operating member is locked from the opposite side) FIG. 2 is a vertical cross-sectional view showing a power transmission device to which the same bearing holding member is attached (the operating member is locked from the opposite side and does not have a buffer member); FIG. 2 is a vertical cross-sectional view showing a power transmission device to which the same bearing holding member is attached (the operating member is locked from the opposite side and the clutch member is integrated); Graph showing movement amount and pressing load of interlocking member in power transmission device without cushioning member

Hereinafter, embodiments of the present invention will be specifically described with reference to the drawings.
A power transmission device according to the present embodiment is provided in a vehicle such as a two-wheeled vehicle to arbitrarily transmit or block the driving force of an engine to a transmission or driving wheels. , a clutch housing 2 formed with an input gear 1 (input member) that rotates by the driving force of a vehicle engine, clutch members (first clutch member 4a and second clutch member 4b), and clutch members (first clutch member 2, a plurality of drive-side clutch plates 6 and a plurality of driven-side clutch plates 7 move radially in the clutch housing 2. It is mainly composed of a weight member 8 made of a movable steel ball member, an interlocking member 9, and an operating member 10 that can be operated manually or by an actuator (not shown). In the drawing, symbol S indicates a spring damper, symbol B1 indicates a roller bearing, and symbols B2 and B3 indicate thrust bearings.

The input gear 1 is rotatable about an output shaft 3 when a driving force (rotational force) transmitted from the engine is input, and is connected to the clutch housing 2 by a rivet R or the like. The clutch housing 2 is composed of a cylindrical member with an opening on the right side in FIG. 2, and includes a housing portion 2a connected to the input gear 1 and a cover portion 2b attached so as to cover the opening of the housing portion 2a. , and can be rotated together with the rotation of the input gear 1 by the driving force of the engine.

As shown in FIG. 4, the housing portion 2a of the clutch housing 2 is formed with a plurality of notches 2aa extending in the circumferential direction. 6 is installed. Each of the drive-side clutch plates 6 is made of a plate material formed in a substantially annular shape, and is configured to rotate together with the rotation of the clutch housing 2 and to be slidable in the axial direction (horizontal direction in FIG. 2). there is

Further, as shown in FIG. 5, the cover portion 2b of the clutch housing 2 is formed with a plurality of groove portions 2ba extending in the radial direction of the cover portion 2b on the bottom surface thereof. A weight member 8 is disposed in each of the grooves 2ba, and when the clutch housing 2 is stopped (engine stopped or idling) and rotated at a low speed, the weight member 8 is positioned on the inner diameter side (Fig. 2 ), and when the clutch housing 2 rotates at high speed, the weight member 8 is set to the outer diameter side position.

The clutch members (the first clutch member 4a and the second clutch member 4b) are attached with a plurality of driven-side clutch plates 7 alternately formed with the drive-side clutch plates 6 of the clutch housing 2, and rotate the wheels of the vehicle. It is connected to the output shaft 3 (output member) to be obtained, and is constructed by assembling two members, a first clutch member 4a and a second clutch member 4b.

As shown in FIG. 6, the first clutch member 4a is a disk-shaped member having a flange surface 4ac formed along its peripheral edge. ) is inserted through the output shaft 3, and the formed gears are engaged with each other to be connected in the rotational direction. As shown in FIGS. 6, 9 and 10, the first clutch member 4a is formed with a sloped surface 4aa forming a pressure assist cam and a sloped surface 4ab forming a back torque limiter cam.

As shown in FIG. 7, the second clutch member 4b is made of an annular member. It is configured to be installed in 9 to 11, a pressure member 5 is assembled to the clutch members (first clutch member 4a and second clutch member 4b). ) and the flange surface 4ac (see FIGS. 2 and 6) of the first clutch member 4a, a plurality of drive-side clutch plates 6 and driven-side clutch plates 7 are alternately mounted in a stacked state.

As shown in FIG. 8, the pressure member 5 is a disk-shaped member having a flange surface 5c formed along the peripheral edge thereof. and the pressure contact force between the drive-side clutch plate 6 and the driven-side clutch plate 7 is released to cut off the transmission of the engine drive force to the wheels. It is movable between an available non-actuated position (see FIG. 2).

More specifically, as shown in FIGS. 7, 9 and 10, the spline fitting portion 4ba formed on the second clutch member 4b is integrally formed along substantially the entire circumference of the outer peripheral side surface of the second clutch member 4b. The driven side clutch plate 7 is fitted into the concave groove forming the spline fitting portion 4ba so that the driven side clutch plate 7 is axially aligned with the second clutch member 4b. It is configured so that it can rotate together with the second clutch member 4b while permitting the movement in the direction and restricting the movement in the rotational direction.

The driven-side clutch plates 7 and the drive-side clutch plates 6 are alternately laminated so that the adjacent clutch plates 6, 7 can press or release the pressing force. That is, both clutch plates 6 and 7 are allowed to slide in the axial direction of the second clutch member 4b, and the pressure member 5 moves leftward in FIG. When the flange surface 4ac comes close to the clutch plates 6 and 7, 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. When the member 5 moves to the right in FIG. 2 and the flange surface 5c and the flange surface 4ac of the first clutch member 4a are separated from each other, the pressing forces of the clutch plates 6 and 7 are released and the first clutch member 4a and the second clutch member 4a are separated. The clutch member 4b no longer follows the rotation of the clutch housing 2, and transmission of rotational force to the output shaft 3 is no longer performed.

With the drive-side clutch plate 6 and the driven-side clutch plate 7 pressed against each other, the rotational force (driving force of the engine) input to the clutch housing 2 is applied to the wheels via the output shaft 3 (output member). In addition, the rotational force (driving force of the engine) input to the clutch housing 2 is transmitted to the output shaft 3 (output member ) can be blocked.

Furthermore, in this embodiment, as shown in FIGS. and 4ab are formed. That is, the inclined surfaces 4aa and 5a are in contact with each other to form a press assist cam, and the inclined surfaces 4ab and 5b are in contact with each other to form a back torque limiter cam.

Then, the rotational speed of the engine increases, and 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 (weight member 8). is the outer diameter side position), as shown in FIG. A force is generated in the c direction in the figure. As a result, the pressure member 5 moves in a direction (left side in FIG. 2) in which the flange surface 5c thereof approaches the flange surface 4ac of the first clutch member 4a (left side in FIG. 2), so that the driving side clutch plate 6 and the driven side clutch plate 6 are separated. 7 to increase the pressure contact force.

On the other hand, while the vehicle is running, when the rotation speed of the output shaft 3 exceeds the rotation speed of the input gear 1 and the clutch housing 2 and back torque is generated in the direction b in FIG. , the pressure member 5 is moved in the direction d in FIG. As a result, problems with the power transmission device and the power source (engine side) due to back torque can be avoided.

The weight member 8 is arranged in a groove portion 2ba extending in the radial direction of the clutch housing 2 (the cover portion 2b in this embodiment), and the inner diameter of the groove portion 2ba is increased by the centrifugal force accompanying the rotation of the clutch housing 2. By moving from the side position (see FIG. 2) to the outer diameter side position, the driving side clutch plate 6 and the driven side clutch plate 7 can be brought into pressure contact. That is, the rolling surface (bottom surface) of the weight member 8 in the groove portion 2ba is inclined upward from the inner diameter side position toward the outer diameter side position. When the clutch housing 2 rotates, centrifugal force is applied to the weight member 8 to move it along an upward slope, and the clutch housing 2 reaches a predetermined number of revolutions. is moved to the outer diameter side position.

The interlocking member 9 is an annular member disposed in the clutch housing 2 (the cover member 2b), and is fitted and connected to a groove formed in the inner peripheral surface of the cover member 2b. 2 and can move in the horizontal direction in FIG. As the weight member 8 moves from the inner diameter side position to the outer diameter side position, the interlocking member 9 moves leftward in FIG. can be moved from the inoperative position to the operative position by

The actuating member 10 consists of a member (see FIG. 2) that can be operated manually or by an actuator, and is a pressure member that moves in a direction (right side in FIG. 2) to release the pressure contact force between the drive-side clutch plate 6 and the driven-side clutch plate 7. 5 can be moved. The operating member 10 is moved to the right side in FIG. By moving the pressure member 5 from the operating position to the non-operating position, the pressure contact force between the drive-side clutch plate 6 and the driven-side clutch plate 7 can be released to turn off the clutch (cut off power transmission). It's like

As shown in FIG. 2, the bearing holding member C is connected to the operating member 10 and holds the bearing B1 interposed between the operating member 10 and the pressure member 5. As shown in FIG. , a cylindrical member with one end open, and is configured to have an open end Ca and a top portion Cb opposite to the open end Ca. The bearing B1 according to this embodiment is attached to the top portion Cb side inside the bearing holding member C, and has a cylindrical portion extending from the enlarged diameter portion to the open end portion Ca. A ball bearing is used as the bearing B1 according to this embodiment, but other bearings such as a needle bearing may be used.

Furthermore, as shown in FIGS. 2 and 20, the bearing holding member C according to the present embodiment is attached by fitting its open end Ca into the recess 4d formed in the clutch member (first clutch member 4a). It is fitted to the inner peripheral wall surface 4da of the recess 4d by spigot fitting. The recess 4d is a circular recess having approximately the same size (strictly speaking, slightly larger than the opening end Ca) following the outer shape of the opening end Ca, and the bearing holding member C is fitted into the recess 4d. The mating provides positioning and centering with respect to the power transmission.

Thus, when the operating member 10 moves to the right side in FIG. 2 due to the operation of a clutch pedal or clutch lever provided in the vehicle or the actuation of an actuator during a shift operation, the bearing holding member C interlocks with the pressure member 5. By contacting and moving the pressure member 5 from the operating position to the non-operating position, the pressure contact force between the driving side clutch plate 6 and the driven side clutch plate 7 is released to turn off the clutch (cut off power transmission). .

The release spring m can hold the pressure member 5 at the non-operating position, and is compressed as the interlocking member 9 moves to move the pressure member 5 from the non-operating position toward the operating position. The engaged state before the discs 6 and the driven-side clutch discs 7 are pressed against each other (the state immediately before the separation distance between the driving-side clutch discs 6 and the driven-side clutch discs 7 becomes zero and power is transmitted by pressing). The urging force can be applied while allowing the movement of the interlocking member 9 and the pressure member 5 until it reaches.

Further, the release spring m according to this embodiment is, as shown in FIG. , the central portion ma is attached to the top portion Cb of the bearing holding member C, and the peripheral edge portion mb is attached to the pressure member 5. As shown in FIG. The pressure member 5 has an annular projecting portion 5d, and the peripheral edge portion mb of the release spring m is engaged with a ring-shaped member g (for example, a circlip) attached to the projecting portion 5d. and attached. As a result, the release spring m according to the present embodiment is attached across both the bearing holding member C and the pressure member 5, and exerts a biasing force (biasing force in the direction indicated by symbol a2 in FIG. 20) on the pressure member 5. At the same time, a biasing force (biasing force in the direction indicated by reference numeral a1 in the drawing) is applied to the bearing holding member C to transmit the biasing force to the operating member 10 .

The clutch spring 11 is a coil spring interposed between the interlocking member 9 and the pressure member 5. As the interlocking member 9 moves, the clutch spring 11 presses the pressure member 5 to separate the driving side clutch plate 6 and the driven side clutch plate 6. The pressure member 5 can be moved in a direction to press the actuating member 10 against the interlocking member 9, and the pressing force of the pressure member 5 against the interlocking member 9 can be absorbed when the actuating member 10 is actuated.

In addition, the clutch spring 11 according to the present embodiment moves integrally with the pressure member 5 without being compressed (without bending) until the drive-side clutch plate 6 and the driven-side clutch plate 7 reach the above-described fastening state. At the same time, after the drive-side clutch plate 6 and the driven-side clutch plate 7 have reached the engaged state, the interlocking member 9 moves and is compressed in the process of further movement of the pressure member 5, allowing the interlocking member 9 to move. It is constructed so as to apply pressure contact force to the drive-side clutch plate 6 and the driven-side clutch plate 7 .

That is, when the weight member 8 moves from the inner diameter side position to the outer diameter side position as the clutch housing 2 rotates, and when the interlocking member 9 is pressed by the weight member 8 , the pressing force is applied via the clutch spring 11 . 2 to press the drive-side clutch plate 6 and the driven-side clutch plate 7 into pressure contact with each other, and in this state, when the operating member 10 is operated, the operating member 10, the pressure member 5 moves to the right in FIG. It is.

Here, in the power transmission device according to the present embodiment, when rotational force is input to the first clutch member 4a through the output shaft 3 (output member), the second clutch member 4b is moved to move the driving side clutch plate. 6 and the driven side clutch plate 7 are provided with cams for back torque transmission (cam surfaces K1, T1). As shown in FIGS. 6, 7, 9 and 10, such a back torque transmission cam is a cam surface formed integrally with the mating surfaces of the first clutch member 4a and the second clutch member 4b (the mating surfaces when combined). (K1, T1).

As shown in FIGS. 6 and 9, a plurality of cam surfaces K1 are formed along the entire circumference of the flange surface 4ac formed on the first clutch member 4a on the inner diameter side (the mating surface with the second clutch member 4b). It is formed on one end face of a plurality of annular grooves K formed along the peripheral edge of the first clutch member 4a. That is, a plurality of grooves K are formed in the first clutch member 4a along its circumferential direction, and one end surface of each groove K is formed as a sloped surface to form the cam surface K1 of the back torque transmission cam. I'm doing it. The other end surface of each groove K is a wall surface K2 extending in the axial direction of the first clutch member 4a.

As shown in FIGS. 7 and 10, the cam surface T1 consists of a plurality of sloped 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). It is formed on one end face of a plurality of annular protrusions T formed along the bottom surface of the second clutch member 4b. That is, the second clutch member 4b is formed with a plurality of projections T along its circumferential direction, and one end surface of each projection T is formed as a sloped surface to form a cam surface T1 of the back torque transmission cam. It constitutes The other end surface of each projecting portion T is a wall surface T2 extending in the axial direction of the second clutch member 4b.

When the protrusion T is fitted into the groove K and the first clutch member 4a and the second clutch member 4b are combined, as shown in FIG. The wall surface K2 and the wall surface T2 face each other with a predetermined distance therebetween. Thus, when a rotational force is input to the first clutch member 4a through the output shaft 3, the first clutch member 4a rotates relative to the second clutch member 4b. , the cam action of the cam surface K1 and the cam surface T1 moves the second clutch member 4b to the right in FIGS.

On the other hand, as shown in FIG. 7, the second clutch member 4b is formed with a pressing portion 4bb extending from the spline fitting portion 4ba. When the second clutch member 4b moves rightward in FIG. Of the drive-side clutch plate 6 and the driven-side clutch plate 7 mounted in a stacked state, the leftmost driven-side clutch plate 7 in the figure is pressed in the same direction. As a result, even when the pressure member 5 is in the non-operating position, the drive-side clutch plate 6 and the driven-side clutch plate 7 can be pressed against each other. The rotational force can be transmitted to the engine side to generate engine braking.

In particular, the back torque transmission cam according to the present embodiment moves the second clutch member 4b in a direction toward the interlocking member 9 (right side in FIG. It is configured to be able to maintain contact. That is, when the back torque transmission cam is actuated to move the second clutch member 4b toward the right side in FIG. Since it presses in the direction, the pressing force is transmitted to the interlocking member 9 via the clutch spring 11, and the abutment between the interlocking member 9 and the weight member 8 is maintained.

If the interlocking member 9 and the weight member 8 are separated from each other when the back torque transmission cam is actuated, the weight member 8 will move between the inner diameter side position and the outer diameter side position as the clutch housing 2 rotates. Although there are cases where the interlocking member 9 cannot follow the movement even if it moves between Since the contact with the member 8 can be maintained, the interlocking member 9 can stably follow the movement of the weight member 8 .

Further, a plurality of cam surfaces K1 and T1, which constitute the back torque transmitting 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 shape (annular shape) of the driven-side clutch plate 7 pressed by the pressing portion 4bb when the back torque transmitting cam operates. As a result, due to the action of the back torque transmission cam, the pressing portion 4bb can apply a substantially uniform pressing force to the driven side clutch plate 7, and the driving side clutch plate 6 and the driven side clutch plate 7 can be more efficiently connected. 7 can be press-contacted.

Furthermore, the back torque transmission cam (the cam composed of the cam surface K1 and the cam surface T1) according to the present embodiment operates the back torque limiter cam (the cam composed of the inclined surface 4ab and the inclined surface 5b). It is configured to be operable before. That is, the clearance (gap dimension) between the cam surfaces K1 and T1 is set smaller than the clearance (gap dimension) between the slope surfaces 4ab and 5b. The back torque transmission cam can be operated at this time.

Further, in the power transmission device according to the present embodiment, the torque transmitted to the second clutch member 4b is transferred to the back torque transmission cam (cam surface K1) formed in the first clutch member 4a and the second clutch member 4b, respectively. and cam surface T1), and a back torque transmitting cam (a cam surface K1 and a cam surface and a movement limiter for limiting the amount of movement of the second clutch member 4b by T1).

That is, as shown in FIGS. 6 and 9, the first clutch member 4a is integrally formed with a plurality of (three in this embodiment) projections F at equal intervals in the circumferential direction. As shown in FIGS. 7 and 9, the member 4b is integrally formed with a projecting portion G extending inward. When the first clutch member 4a and the second clutch member 4b are assembled, as shown in FIGS. 15 and 16, one projection F is sandwiched between two projections G. One side surface F1 of the portion F and the contact surface (first contact surface G1) of one protrusion G face each other, and the other side surface F2 of the protrusion F and the contact surface (second contact surface G1) of the other protrusion G It is configured to face the contact surface G2).

Thus, the one side surface F1 of the protrusion F formed on the first clutch member 4a and the first contact surface G1 of the projection G formed on the second clutch member 4b are the torque forces according to the present embodiment. It constitutes the transmission part. That is, when the pressure member 5 moves to the operating position and the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other to turn on the clutch (transmit the driving force), the wall surface K2 of the groove K in the back torque transmitting cam and the As shown in FIG. 15, one side face F1 of the protrusion and the first contact surface G1 of the protrusion G abut against each other while maintaining the separation state of the protrusion T from the wall surface T2 (see FIG. 17). The rotational force of the second clutch member 4b can be received and transmitted to the first clutch member 4a.

Further, the other side surface F2 of the protrusion F formed on the first clutch member 4a and the second contact surface G2 of the other protrusion G formed on the second clutch member 4b correspond to the movement amount according to the present embodiment. Constructs the restriction part. That is, when a rotational force is input to the first clutch member 4a through the output shaft 3, the first clutch member 4a and the second clutch member 4b rotate relative to each other. The second clutch member 4b is moved by the action of the cam between the cam surface K1 and the cam surface T1 of the projecting portion T (see FIG. 18). Then, when the amount of movement reaches the set value, as shown in FIG. 16, the other side surface F2 of the convex portion and the second contact surface G2 of the projecting portion G come into contact with each other, and the second clutch member 4a contacts the first clutch member 4a. Since the relative rotation of the member 4b is restricted, it is possible to limit the amount of movement of the second clutch member 4b when the back torque transmission cam is actuated.

In the present embodiment, the protrusion F is formed on the first clutch member 4a and the protrusion G is formed on the second clutch member 4b. Instead, the protrusion G is formed on the first clutch member 4b. , and the projection F may be formed on the second clutch member 4b. In this case, the one side face F1 of the projection F formed on the second clutch member 4b and the first contact surface G1 of the one projection G formed on the first clutch member 4a are the torque forces according to the present embodiment. The other side surface F2 of the convex portion F formed on the second clutch member 4b and the second contact surface G2 of the other projecting portion G formed on the first clutch member 4b constitute a transmission portion. It constitutes a movement amount limiting unit according to the form.

Next, the action of the back torque transmission cam in this embodiment will be described.
When the engine is stopped or idling, 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. Therefore, as shown in FIG. At the same time, the pressure member 5 is at the non-operating position. At this time, when a rotational force is input to the first clutch member 4a through the output shaft 3 (output member), the action of the back torque transmission cam causes the second clutch member 4b to move rightward in the drawing, The drive-side clutch plate 6 and the driven-side clutch plate 7 are pressed against each other to transmit rotational force to the engine side.

When the vehicle starts after stopping or idling, the rotation speed of the input gear 1 shifts from low rotation to high rotation (middle rotation range). and the pressure member 5 is at the operating position. At this time, when a rotational force is input to the first clutch member 4a through the output shaft 3 (output member) such as when the accelerator is turned off on a downhill, the action of the back torque transmission cam causes the second clutch member. 4b moves to the right in the figure, and the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other to transmit torque to the engine side.

When the vehicle is accelerated and runs in a high-speed range after starting, the rotation speed of the input gear 1 is high. ing. At this time, when a rotational force is input to the first clutch member 4a through the output shaft 3 (output member) due to a shift down or the like, the action of the back torque transmission cam causes the second clutch member 4b to rotate. It moves to the right, and the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other to transmit torque to the engine side.

Here, in the present embodiment, the interlocking member 9 is interposed between the first clutch member 4a and the second clutch member 4b, and is compressed in the process of moving the pressure member 5 from the non-operating position to the operating position. It is provided with a buffer member 12 that can apply an urging force while permitting movement of the interlocking member 9 and the pressure member 5 by bending the spring. The cushioning member 12 consists of a spring set to a load that is compressed before the clutch spring 11 starts to compress, and as shown in FIGS. It is housed and assembled in a housing recess 4c formed in a facing surface (specifically, a surface of the first clutch member 4a facing the second clutch member 4b).

More specifically, as shown in FIG. 6, the accommodation recess 4c is formed by a groove formed in an annular shape, and the cushioning member 12 is formed by a disk spring or a wave formed in an annular shape following the shape of the groove. It consists of springs such as springs. As shown in FIG. 19, the accommodation recess 4c is formed of a groove having an inner diameter side wall surface 4ca and an outer diameter side wall surface 4cb, and a cushioning member 12 made of an annular spring follows the shape of the groove. It's designed to fit.

Thus, in the back torque transmission cam according to the present embodiment, as described above, a plurality of annular cams are formed on the surfaces where the first clutch member 4a and the second clutch member 4b face each other. , is concentrically formed at a position adjacent to the back torque transmission cam (in the present embodiment, on the inner diameter side from the formation position of the back torque transmission cam), as shown in FIG. In the present embodiment, the accommodation recess 4c is formed concentrically on the inner diameter side from the formation position of the back torque transmission cam, but is formed concentrically on the outer diameter side from the formation position of the back torque transmission cam. In this case, as shown in FIG. 24, the cushioning member 12 is provided with a portion (disc pack) where the driving side clutch plates 6 and the driven side clutch plates 7 are stacked. And, it may be constructed so as to apply an urging force in the direction of press-contacting the driven side clutch plate 7 .

Next, the action of the cushioning member 12 according to this embodiment will be described in comparison with a conventional cushioning member 12 not provided.
First, with regard to the action when the cushioning member 12 is not provided as in this embodiment, the graph in FIG. ) will be used for explanation. In the graph of FIG. 30, P1 is the pressing load of the interlocking member 9 at the time when the amount of deflection (compression) of the release spring m becomes maximum (at the time when the maximum load of the release spring m is reached), and P2 is the clutch spring. 22 and 23, P3 in the graphs of FIGS. reached)).

In the process of moving the interlocking member 9 by moving the weight member 8 from the inner diameter side position to the outer diameter side position as the engine speed increases, the release spring m is released until the movement amount of the interlocking member 9 reaches α. While the clutch spring 11 is bent, the clutch spring 11 is in a non-flexed state (that is, the interlocking member 9 and the pressure member 5 move together). Although it rises to P2, the interlocking member 9 stops moving and becomes a dead zone region.

When the pressing load (N) reaches P2 (the set load of the clutch spring 11) from such a state, the clutch spring 11 begins to bend, and the pressing load (N) increases as the interlocking member 9 moves. . Therefore, the interlocking member 12 and the pressure member 5 are stopped until the pressing load (N) reaches from P1 to P2. And, since the driven-side clutch plate 7) is pressed against each other and the power is transmitted, there was a sense of abruptness during the power transmission.

On the other hand, in the present embodiment, in the process of moving the interlocking member 9, the spring is set to a load that is compressed before the clutch spring 11 starts to be compressed (a spring whose set load is set to P3). Since the cushioning member 12 is provided, as shown in FIG. 22, from the time when the movement amount of the interlocking member 9 reaches β, the cushioning member 12 starts to be compressed (starts to bend), and until the pressing load reaches P2. Compression will continue.

That is, according to this graph, in the process of moving the interlocking member 9 by moving the weight member 8 from the inner diameter side position to the outer diameter side position as the number of rotations of the engine increases, the movement amount of the interlocking member 9 is β When the pressing load (N) reaches P3, the cushioning member 12 is compressed. After that, the moving amount of the interlocking member 9 reaches α and the pressing load (N) reaches P2. , the clutch spring 11 begins to bend (begins to be compressed).

As described above, when the interlocking member 9 starts to move, the pressing load (N) becomes the set load of the release spring m, and the release spring m begins to bend (compression starts). , the buffer member 12 begins to bend (compression starts), and when the movement amount of the interlocking member 9 reaches α, the release spring m reaches its maximum load and the pressing load (N) changes to the set load (P2 ), the clutch spring 11 begins to bend (starts to be compressed). The clutch spring 11 continues to compress (continue to bend) due to the movement of the interlocking member 9 until it reaches the maximum load (the upper limit of the operating load).

Therefore, when the amount of movement of the interlocking member 9 is between β and α, the cushioning member 12 is continuously compressed (flexed) in the process of increasing the pressing load from P3 to P2, allowing the interlocking member 9 to move. Therefore, the conventional dead zone area can be reduced, and the weight member 8 and the interlocking member 9 can be moved smoothly and continuously. Therefore, it is possible to suppress the shock when the clutch is engaged and suppress the feeling of abruptness when power is transmitted.

As shown in FIG. 22, the cushioning member 12 described above is continuously compressed (continued to flex) when the pressing load (N) is between P3 and P2, but as shown in FIG. Then, when the moving amount of the interlocking member 9 becomes β and the pressing load (N) reaches P3, the cushioning member 12 starts to compress (start bending), and the pressing load (N) reaches P4, which is lower than P2. The cushioning member 12 may be set to be continuously compressed (continue to flex) until a point in time. Even in this case, it is possible to reduce the dead zone region that has conventionally occurred, so that the weight member 8 and the interlocking member 9 can be moved smoothly and continuously, and the shock at the time of clutch engagement can be suppressed. Abrupt feeling during power transmission can be suppressed.

According to the present embodiment, interlocking member 9 interposed between first clutch member 4a and second clutch member 4b compresses pressure member 5 in the process of moving from the non-operating position to the operating position. Since the cushioning member 12 that can apply the biasing force while allowing the movement of the interlocking member 9 and the pressure member 5 is provided, the space obtained by arranging the first clutch member 4a and the second clutch member 4b can be effectively utilized. It is possible to improve the operability by suppressing the abrupt feeling at the time of power transmission.

In addition, since the cushioning member 12 according to the present embodiment is made of a spring set to a load that is compressed before the clutch spring 11 starts to compress, it is possible to more reliably suppress an abrupt feeling during power transmission. In particular, by arbitrarily setting the set load and operating load of the buffer member 12, it is possible to variously set the feeling during power transmission (start feeling) according to the form of the vehicle to which it is applied.

Furthermore, since the cushioning member 12 according to the present embodiment is housed in the housing recess 4c formed in the facing surfaces of the first clutch member 4a and the second clutch member 4b, the buffer member 12 is the second clutch member 4a with respect to the first clutch member 4a. When the clutch member 4b is moved, it is possible to prevent the shock absorbing member 12 from being caught and causing a positional deviation. Note that the accommodation recess 4c according to the present embodiment is formed on the surface of the first clutch member 4a that faces the second clutch member 4b. may be formed.

Furthermore, the housing recess 4c according to the present embodiment is formed by a groove formed in an annular shape, and the cushioning member 12 is formed by a spring formed in an annular shape following the shape of the groove. The generated urging force can be applied substantially uniformly to the second clutch member 4b and the like, and the urging force can be applied stably. Further, the back torque transmission cams according to the present embodiment are formed in a plurality of annular shapes on the surfaces where the first clutch member 4a and the second clutch member 4b face each other. , so that the movement of the second clutch member 4b by the back torque transmission cam and the application of the biasing force by the buffer member 12 can be reliably and stably performed.

In addition, the bearing holding member C according to the present embodiment is made of a cylindrical member with one end open, and the open end Ca is fitted into the recess 4d formed in the clutch member (first clutch member 4a). (attached in the spigot state), the assembly of the bearing holding member C can be easily performed, and the bearing holding member C can be operated stably during the shift operation.

In addition, the release spring m can apply an urging force to the pressure member 5 while allowing the movement of the interlocking member 9 and the pressure member 5 until the clutch plate 6 on the drive side and the clutch plate 7 on the driven side reach the engaged state before they are pressed against each other. , and the release spring m is attached across both the bearing holding member C and the pressure member 5 to impart a biasing force to the pressure member 5 and to the bearing holding member C Since the urging force can be transmitted to the operating member 10, the release spring m can also be used as a spring for preventing play in the speed change operation means, and the number of parts can be reduced.

Further, the release spring m according to the present embodiment is a circular disc spring that can generate a biasing force by displacement between the central portion ma and the peripheral portion mb. The central portion ma is attached to the bearing holding member C, Since the peripheral portion mb is attached to the pressure member 5, both the bearing holding member C and the pressure member 5 can be stably applied with the biasing force of the release spring m.

Furthermore, the clutch member according to the present embodiment includes a first clutch member 4a connected to the output shaft 3 (output member), a second clutch member 4b to which the driven side clutch plate 7 is attached, and the output shaft 3 (output member). a back torque transmission cam capable of moving the second clutch member 4b to bring the drive-side clutch plate 6 and the driven-side clutch plate 7 into pressure contact with each other when a rotational force is input to the first clutch member 4a through the member); In addition, since the recess 4d is formed in the first clutch member 4a, it is possible to prevent the bearing holding member C from interfering with the movement of the second clutch member 4b by the back torque transmission cam, and the bearing holding member C and the movement of the second clutch member 4b by the back torque transmission cam can be performed smoothly.

According to the above embodiment, the back torque transmission cam moves the second clutch member 4b in a direction approaching the interlocking member 9 to keep the interlocking member 9 and the weight member 8 in contact with each other. Therefore, by bringing the drive-side clutch plate 6 and the driven-side clutch plate 7 into pressure contact, it is possible to transmit the rotational force of the wheel side to the engine side to generate engine braking, and at the same time, the weight when the engine braking is generated. The operation by the member 8 can be stably performed.

Further, the back torque transmission cam according to the present embodiment is composed of cam surfaces (K1, T1) formed integrally with the first clutch member 4a and the second clutch member 4b, respectively. T1) is formed on the mating surfaces of the first clutch member 4a and the second clutch member 4b, so that the back torque transmission cam can reliably and smoothly move the second clutch member 2b.

Further, a sloped surface 4aa formed on the first clutch member 4a and a sloped surface 5a formed on the pressure member 5 are opposed to each other. (output member), the pressure contact assisting cam for increasing the pressure contact force between the driving side clutch plate 6 and the driven side clutch plate 7 is provided. In addition to the pressure force associated with the movement, the pressure assist cam can apply the pressure force, so that the driving side clutch plate 6 and the driven side clutch plate 7 can be brought into pressure contact more smoothly and reliably.

Further, the inclined surface 4ab formed on the first clutch member 4a and the inclined surface 5b formed on the pressure member 5 are configured to face each other, and the rotation of the output shaft 3 (output member) rotates the input gear 1 (input member). ), the clutch member (first clutch member 4a) and the pressure member 5 rotate relative to each other to release the pressing force between the drive-side clutch plate 6 and the driven-side clutch plate 7. Since the torque limiter cam is provided, when the weight member 8 is located at the outer diameter side position, it is possible to avoid excessive power from being transmitted to the engine through the input gear 1, and a back torque limiter is provided. Since the back torque transmission cam is actuated before the back torque transmission cam is actuated, the back torque transmission cam can be reliably actuated.

In addition, according to the present embodiment, when a rotational force is input to the first clutch member 4a through the output shaft 3 (output member), the second clutch member 4b is moved so that the driving side clutch plate 6 and the driven side clutch plate 6 are moved. A back torque transmission cam capable of pressing the side clutch plate 7 is formed on the first clutch member 4a and the second clutch member 4b, respectively. Since the cam surface K1 and the torque transmitting portion capable of transmitting the torque to the first clutch member 4a without passing through the cam surface K1 and the cam surface T1) are provided, the driving side clutch plate 6 and the driven side clutch plate 7 are pressed against each other, whereby the wheel side rotational force is transmitted. can be transmitted to the engine side to generate engine braking, and the power can be stably transmitted when the weight member 8 moves to the outer diameter side position and the pressure member 5 moves to the operating position. can.

Further, since the first clutch member 4a and the second clutch member 4b are provided with movement amount limiting portions that limit the amount of movement of the second clutch member 4b by the back torque transmission cam, The second clutch member 4b can be moved within a set range.

Further, a convex portion F is formed on either one of the first clutch member 4a and the second clutch member 4b, and the torque transmission portion rotates in contact with one side surface F1 of the convex portion F and the one side surface F1. The movement limiter includes a first contact surface G1 capable of receiving a force, and a second contact surface G2 capable of contacting the other side surface F2 of the projection F and the other side surface F2 to limit the movement amount. Therefore, the convex portion F can perform the functions of the torque transmitting portion and the movement amount limiting portion.

Although the present embodiment has been described above, the present invention is not limited thereto. For example, as shown in FIGS. (3) may be formed so that the oil supplied to the inside can flow out to the outside through the communication hole Cc. The bearing holding member C has a plurality of communication holes Cc as in the above-described embodiment, and its open end Ca is fitted into the recess 4d formed in the clutch member (first clutch member 4a). there is

Thus, if the communication hole Cc is formed in the side wall portion of the bearing holding member C and the oil supplied to the inside can flow out to the outside through the communication hole Cc, the supply of the oil to the clutch housing 2 can be prevented. It can be done smoothly. The position and the number of communication holes Cc formed can be arbitrarily set, but it is preferable that the communication holes Cc open toward the gap between the clutch member 4 and the pressure member 5 as in the present embodiment. In this case, the oil that has flowed out from the communication hole Cc can reach substantially the entire area within the clutch housing 2 .

Further, as shown in FIG. 27, for example, the bearing holding member C has an opening formed in the top portion Cb, and the operating member 10 is inserted from the opposite side (right side in the figure) to the roller bearing B1. The pressure member 5 may be movable between the operating position and the non-operating position by being locked and moved in the horizontal direction in the figure by the operation of the driver or the actuation of the actuator. In this case, the oil flow path r can be formed satisfactorily.

For example, as shown in FIG. 28, a power transmission device in which the cushioning member 12 is not formed on the facing surfaces of the first clutch member 4a and the second clutch member 4b, or a bearing holding member C is arranged as shown in FIG. As described above, the bearing holding member C may be arranged in a power transmission device having an integral clutch member 4 (the clutch member 4 that is not divided like the first clutch member 4a and the second clutch member 4b).

Furthermore, in the present embodiment, the cushioning member 12 is composed of a disc spring, a wave spring, or the like, but it may be replaced with another elastic member or the like. In addition to motorcycles, the power transmission device of the present invention can be applied to various multi-plate clutch type power transmission devices such as automobiles, three-wheeled or four-wheeled buggies, and general-purpose machines.

The bearing holding member maintains a state in which the open end is fitted in the clutch member when the pressure member moves in the axial direction of the output member as the weight member moves from the inner diameter side position to the outer diameter side position. Alternatively, if the power transmission device is configured so that the relative position with respect to the clutch member does not change, it can be applied to a power transmission device having a different external shape or having other functions added. .

1 Input gear (input member)
2 clutch housing 2a housing portion 2b cover portion 3 output shaft (output member)
4a First clutch member 4aa Inclined surface (pressure assist cam)
4ab Inclined surface (cam for back torque limiter)
4ac flange surface 4ad insertion hole 4b second clutch member 4ba spline fitting portion 4bb pressing portion 4c housing recess 4d recess 4da inner peripheral wall surface 5 pressure member 5a inclined surface (pressure contact assisting cam)
5b Inclined surface (cam for back torque limiter)
5c Flange surface 6 Drive-side clutch plate 7 Driven-side clutch plate 8 Weight member 9 Interlocking member 10 Actuating member 11 Clutch spring 12 Buffer member C Bearing holding member Ca Opening end portion Cb Top portion Cc Communication hole K Groove portion K1 Cam surface K2 Wall surface T Projection Part T1 Cam surface T2 Wall surface F Projection G Projection G1 First contact surface G2 Second contact surface m Release spring r Oil flow path

Claims (2)

A clutch member that rotates together with an input member that rotates with the driving force of a vehicle engine and is accommodated in a clutch housing to which a plurality of drive-side clutch plates are attached,
a clutch member mounted with a plurality of driven-side clutch plates alternately formed with the drive-side clutch plates and connected to an output member capable of rotating a vehicle wheel;
an operating position in which the drive-side clutch plate and the driven-side clutch plate are brought into pressure contact so that the driving force of the engine can be transmitted to the wheels; and a pressure contact force between the drive-side clutch plate and the driven-side clutch plate. a pressure member movable between a non-operating position capable of releasing the engine driving force from being transmitted to the wheels;
a weight member movable from an inner diameter side position to an outer diameter side position by centrifugal force accompanying rotation of the clutch housing;
an operating member capable of moving the pressure member in a direction capable of releasing pressure contact force between the drive-side clutch plate and the driven-side clutch plate;
a bearing that supports the actuating member;
a bearing holding member for holding the bearing, the bearing holding member comprising a cylindrical member having an open end, the open end of which is fitted into the clutch member;
a spring that applies a biasing force to the bearing holding member in a direction from the pressure member toward the clutch member;
As the weight member moves from the inner diameter side position to the outer diameter side position, the weight member causes the driving side clutch plate and the driven side clutch plate to press against each other from a non-operating state in which the pressing force is released. is configured to switch the driving force of the engine to an operating state in which the driving force can be transmitted to the wheels, and to move the pressure member in the axial direction of the output member,
The bearing holding member is configured such that when the pressure member moves in the axial direction of the output member in accordance with the movement of the weight member from the inner diameter side position to the outer diameter side position, the open end portion of the bearing holding member engages the clutch. A power transmission device configured to remain fitted in a member. A clutch member that rotates together with an input member that rotates with the driving force of a vehicle engine and is accommodated in a clutch housing to which a plurality of drive-side clutch plates are attached,
a clutch member mounted with a plurality of driven-side clutch plates alternately formed with the drive-side clutch plates and connected to an output member capable of rotating a vehicle wheel;
an operating position in which the drive-side clutch plate and the driven-side clutch plate are brought into pressure contact so that the driving force of the engine can be transmitted to the wheels; and a pressure contact force between the drive-side clutch plate and the driven-side clutch plate. a pressure member movable between a non-operating position capable of releasing the engine driving force from being transmitted to the wheels;
a weight member movable from an inner diameter side position to an outer diameter side position by centrifugal force accompanying rotation of the clutch housing;
an operating member capable of moving the pressure member in a direction capable of releasing pressure contact force between the drive-side clutch plate and the driven-side clutch plate;
a bearing that supports the actuating member;
a bearing holding member for holding the bearing, the bearing holding member comprising a cylindrical member having an open end, the open end of which is fitted into the clutch member;
a spring that applies a biasing force to the bearing holding member in a direction from the pressure member toward the clutch member;
As the weight member moves from the inner diameter side position to the outer diameter side position, the weight member causes the driving side clutch plate and the driven side clutch plate to press against each other from a non-operating state in which the pressing force is released. is configured to switch the driving force of the engine to an operating state in which the driving force can be transmitted to the wheels, and to move the pressure member in the axial direction of the output member,
The bearing holding member is adapted to move relative to the clutch member when the pressure member moves in the axial direction of the output member as the weight member moves from the inner diameter side position to the outer diameter side position. A power transmission device that is constructed so that its position does not change.

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