JP6655430B2 - Power transmission device - Google Patents

Description

  The present invention relates to a power transmission device that can arbitrarily transmit or cut off the rotational force of an input member to an output member.

  Generally, a power transmission device included in a motorcycle is for transmitting or shutting off the driving force of an engine to a transmission and a driving wheel arbitrarily, and an input member connected to the engine side, and a transmission and a driving wheel side. A connected output member, a clutch member connected to the output member, and a pressure member that can approach or separate from the clutch member, and drive the pressure member by bringing the pressure member close to the clutch member. The power transmission is performed by pressing the side clutch plate and the driven clutch plate in pressure, and the pressure contact force between the drive side clutch plate and the driven side clutch plate is released by separating the pressure member from the clutch member. Thus, the transmission of the power is shut off.

  As a conventional power transmission device, for example, as disclosed in Patent Document 1, the power transmission device is disposed in a groove portion extending in a radial direction of a clutch housing, and the groove portion is formed by centrifugal force accompanying rotation of the clutch housing. A weight member that can press the drive-side clutch plate and the driven-side clutch plate by pressing from the inner-diameter position to the outer-diameter position, and a weight member that is attached to the opening side of the clutch housing and has a groove formed therein. There has been proposed an apparatus having a weight housing accommodated therein. According to such a conventional power transmission device, a centrifugal force can be applied to the weight member by rotating the clutch housing with driving of the engine, and the drive side clutch plate and the driven side clutch plate are brought into pressure contact with each other. The driving force of the engine can be transmitted to the wheels.

JP 2013-221585 A

  In the above-described conventional power transmission device, since the weight housing housing the weight member is attached to the opening side of the clutch housing, the radial and axial dimensions of the weight housing are increased, and the power transmission device is accordingly reduced. There is a problem that the whole becomes large.

  The present invention has been made in view of such circumstances, and even when a weight housing that accommodates a weight member is attached to the opening side of a clutch housing, it is possible to suppress an increase in the radial and axial directions. It is an object of the present invention to provide a power transmission device which can be used.

The invention according to claim 1 is a clutch housing comprising a cup-shaped member having a bottom and rotating together with an input member which is rotated by a driving force of an engine of a vehicle, wherein a plurality of drive-side clutch plates are formed; A plurality of driven clutch plates alternately formed with the driving clutch plate, a clutch member connected to an output member capable of rotating wheels of the vehicle, and press-contacting the driving clutch plate and the driven clutch plate. The driving force of the engine is transmitted to the wheels, and the driving force of the engine is transmitted to the wheels by releasing the pressure contact force between the driving clutch plate and the driven clutch plate. A pressure member movable between a non-operating position and a clutch housing disposed in a radially extending groove of the clutch housing; The groove can be moved from the inner diameter position to the outer diameter position by centrifugal force caused by the rotation of the ring, and the pressure member is moved to the outer diameter position as the groove moves from the inner diameter position to the outer diameter position. A power transmission device comprising: a weight member movable from an operating position to the operating position; and a weight housing attached to an opening side of the clutch housing and having the groove formed therein and housing the weight member. the housing, the weight together, by which the projecting portion is fixed by retaining member abuts while fitting in a predetermined position within the clutch housing having protrusions formed to project laterally from the outer peripheral surface housing is attached to the clutch housing in a state of being locked to the rotation direction and the axial direction, the Weitoha Wall portion of the opening side end portion of the managing and the wall portion of the opening side end portion of the clutch housing is characterized by comprising overlapping.

  According to a second aspect of the present invention, in the power transmission device according to the first aspect, the weight housing is formed of a cup-shaped member having a bottom, and the protruding portion is formed to have a predetermined dimension lower than an opening end of the clutch housing. Is fitted at the side position.

  According to a third aspect of the present invention, in the power transmission device according to the first or second aspect, the pressure member and the weight housing fasten the output member and the clutch member to fasten the entire device to a vehicle. An opening is formed at the opening of the pressure member, and an opening is formed at the opening of the pressure member so that the pressure member can be moved from the operating position to the non-operating position by a manual operation or an actuator. It is characterized by having.

  According to a fourth aspect of the present invention, in the power transmission device according to any one of the first to third aspects, the clutch housing is formed with a notch for fitting the drive-side clutch plate, The protrusion of the weight housing is fitted in the notch.

  According to a fifth aspect of the present invention, in the power transmission device according to any one of the first to fourth aspects, the weight housing has a bulging portion that bulges circumferentially at an opening-side end thereof. The bulging portion abuts a mounting surface formed at an end of the clutch housing on the opening side to position the weight housing in the radial direction.

  According to a sixth aspect of the present invention, in the power transmission device according to the fifth aspect, a mounting groove in which a circlip is fitted is formed in the mounting surface, and the weight is formed by the circlip fitted in the mounting groove. The housing can be prevented from falling off.

  According to a seventh aspect of the present invention, in the power transmission device according to any one of the first to sixth aspects, a slope formed on the clutch member and a slope formed on the pressure member face each other. A press-contact assist cam for increasing a press-contact force between the drive-side clutch plate and the driven-side clutch plate when the rotational force input to the input member is ready to be transmitted to the output member. It is characterized by having.

  According to an eighth aspect of the present invention, in the power transmission device according to any one of the first to seventh aspects, a slope formed on the clutch member and a slope formed on the pressure member face each other. When the rotation of the output member exceeds the rotation speed of the input member and the clutch member and the pressure member rotate relatively, the pressure contact force between the drive side clutch plate and the driven side clutch plate can be released. A back torque limiter cam is provided.

  According to the first aspect of the present invention, the weight housing has the protruding portion formed to protrude laterally from the outer peripheral surface thereof, and the protruding portion is fitted to a predetermined position in the clutch housing and attached to the clutch housing. Since the wall near the opening end of the weight housing and the wall near the opening end of the clutch housing overlap each other, the weight housing containing the weight member is attached to the opening side of the clutch housing. Also in this case, it is possible to suppress the enlargement in the radial and axial directions.

  According to the invention of claim 2, the weight housing is formed of a cup-shaped member having a bottom, and the protruding portion is fitted to a position on the bottom side of a predetermined dimension from the opening end of the clutch housing. Even when a weight housing accommodating a weight member is attached to the opening side of the above, it is possible to more reliably suppress an increase in the size in the radial and axial directions.

  According to the third aspect of the present invention, the pressure member and the weight housing are formed with an opening through which a fastening means for fastening the output member and the clutch member to attach the entire device to the vehicle can be exposed to the outside. Since the operating member capable of moving the pressure member from the operating position to the non-operating position by being operated by the operation or the actuator is attached to the opening of the pressure member, the operating member is removed and the fastening means is exposed to the outside so that the tool can be moved to the tool. Thus, the fastening can be released, and the work of removing the entire device from the vehicle can be performed more easily.

  According to the fourth aspect of the present invention, the notch for fitting the drive side clutch plate is formed in the clutch housing, and the projection of the weight housing is fitted in the notch. Both the fitting of the drive-side clutch plate and the fitting of the protrusion of the weight housing can be performed on the notch.

  According to the fifth aspect of the present invention, the weight housing is formed with a bulging portion bulging in the circumferential direction at the opening end thereof, and the bulging portion is formed at the opening end of the clutch housing. Since the weight housing is positioned in the radial direction by contacting the mounting surface, the movement of the weight member can be more accurately transmitted to the pressure member, and the reliability of the device can be improved. .

  According to the invention of claim 6, the mounting surface is formed with the mounting groove into which the circlip can be fitted, and the weight housing can be prevented from coming off by the circlip fitted into the mounting groove. The positioning accuracy of the housing with respect to the clutch housing can be further improved.

  According to the seventh aspect of the present invention, the inclined surface formed on the clutch member and the inclined surface formed on the pressure member face each other, and the rotational force input to the input member can be transmitted to the output member. In this case, the cam for pressure assist is provided to increase the pressure contact force between the drive side clutch plate and the driven side clutch plate, so that the cam for pressure contact assist in addition to the pressure contact force accompanying the movement of the weight member due to the centrifugal force is provided. , And the drive-side clutch plate and the driven-side clutch plate can be pressed more smoothly and reliably.

  According to the invention of claim 8, the inclined surface formed on the clutch member and the inclined surface formed on the pressure member are opposed to each other, and the rotation of the output member exceeds the rotation speed of the input member and the clutch member When the pressure member and the pressure member relatively rotate, the back torque limiter cam capable of releasing the pressure contact force between the driving clutch plate and the driven clutch plate is provided, so that when the weight member is at the outer diameter side position, It is possible to prevent excessive power from being transmitted to the engine via the input member.

External view showing a power transmission device according to an embodiment of the present invention. Longitudinal sectional view showing the internal configuration of the power transmission device. A perspective view showing an input gear and a clutch housing in the power transmission device. A perspective view showing a weight housing in the power transmission device. A perspective view showing a clutch member in the power transmission device. A perspective view showing a pressure member in the power transmission device. Front view showing an interlocking member (with a one-way clutch attached) in the power transmission device. A perspective view showing an inner member constituting a one-way clutch attached to the attachment member. 3 views showing the inner member Sectional view showing the fitting surface of the inner member The perspective view which shows the retainer member which comprises the one-way clutch in the same power transmission device. The perspective view which shows the operation member in which the dog clutch in the power transmission device was integrally formed. Longitudinal sectional view showing the operating member Sectional view showing the mating surface of the dog clutch Schematic view for explaining the operation of the press-contact assist cam in the power transmission device. Schematic diagram for explaining the operation of the back torque limiter cam in the power transmission device. Sectional drawing which shows the fitting state of the dog clutch in the same power transmission device Longitudinal sectional view showing the internal configuration of the power transmission device. Longitudinal sectional view showing the internal configuration of the power transmission device. Longitudinal sectional view showing the internal configuration of the power transmission device. Longitudinal sectional view showing the internal configuration of the power transmission device. Longitudinal sectional view showing the internal configuration of the power transmission device. Longitudinal sectional view showing the internal configuration of the power transmission device.

Hereinafter, embodiments of the present invention will be specifically described with reference to the drawings.
The power transmission device according to the present embodiment is disposed in a vehicle such as a two-wheeled vehicle and is for transmitting or shutting off the driving force of the engine to a transmission or a driving wheel side as desired. As shown in FIGS. A clutch housing 2 in which an input gear 1 (input member) that rotates by the driving force of an engine E of the vehicle is formed, and a clutch member 4 connected to an output shaft 3 (output member) that can rotate wheels D of the vehicle. 2, a pressure member 5 attached to the right side of the clutch member 4 in FIG. 2, a plurality of drive-side clutch plates 6 and a plurality of driven-side clutch plates 7, and a rigid ball member capable of rolling in the clutch housing 2 in the radial direction. A weight member 8, an interlocking member 9, an operating member 10 that can be operated manually or by an actuator (not shown), a one-way clutch 11, and a weight housing 12. It is configured.

  The input gear 1 is rotatable about an output shaft 3 when a driving force (rotational force) transmitted from the engine E is input, and is connected to the clutch housing 2 by a rivet R or the like. As shown in FIG. 3, the clutch housing 2 is formed of a cup-shaped member having a bottom and an opening on the right end side in the figure, and rotates with the rotation of the input gear 1 by the driving force of the engine E. A plurality of notches 2a are formed in the direction, and the drive-side clutch plates 6 are fitted into the notches 2a, respectively. Each of the drive-side clutch plates 6 is made of a substantially annular plate material, is configured to rotate with the rotation of the clutch housing 2, and to slide in the axial direction (the left-right direction in FIG. 2). I have.

  As shown in FIGS. 2 and 4, the weight housing 12 is formed of a cup-shaped member having a bottom, is attached to the opening side (the right side in FIG. 2) of the clutch housing 2, and is configured to be able to rotate together with the clutch housing 2. In addition, a plurality of grooves 12a extending in the radial direction of the weight housing 12 are formed on the bottom surface. The weight members 8 are accommodated in the grooves 12a, respectively. When the clutch housing 2 and the weight housing 12 are stopped (the engine is stopped or idling) and rotated at a low speed, the weight members 8 are positioned at the inner diameter side. (The position shown in FIG. 2), and when the clutch housing 2 and the weight housing 12 rotate at a high speed, the weight member 8 is set to the outer diameter side position (the position shown in FIG. 19). .

  Furthermore, as shown in FIGS. 2 and 4, the weight housing 12 according to the present embodiment has a bulging portion 12e bulging in the circumferential direction at an opening end Q thereof, and the bulging portion 12e. The weight housing 12 is positioned in the radial direction by contacting the mounting surface 2b (see FIG. 3) formed at the opening end P of the clutch housing 2. The mounting surface 12e is a surface obtained by cutting the vicinity of the opening end P after the weight housing 12 is formed.

  As shown in FIGS. 2 and 3, the mounting surface 12e is formed with a mounting groove 2c into which the circlip 17 can be inserted, and the circlip 17 inserted into the mounting groove 2c allows the weight housing 12 to be pulled out. It is possible to stop. That is, the weight housing 12 is mounted on the mounting surface 12 e formed on the clutch housing 2 and is positioned in the radial direction, and is positioned by the circlip 17 in the axial direction.

  The clutch member 4 has a spline formed in its central hole 4c fitted and connected to a spline formed at the tip of the output shaft 3 (output member). The output shaft 3 is configured to rotate when the clutch member 4 rotates. That is, the clutch member 4 and the output shaft 3 are connected in the rotational direction by spline fitting and fastened by the nut N, and the whole power transmission device is attached to the vehicle by such fastening. .

  A pressure member 5 is attached to the clutch member 4, and a plurality of drive-side clutch plates 6 and driven-side clutch plates 7 are provided between a flange surface 5 c of the pressure member 5 and a flange surface 4 d of the clutch member 4. Is attached. The pressure member 5 has an operating position (see FIG. 19) in which the drive side clutch plate 6 and the driven side clutch plate 7 are brought into pressure contact with each other so that the driving force of the engine E can be transmitted to the wheels D. 6 can be moved between a non-operating position (see FIG. 2) where the pressing force between the driven clutch plate 6 and the driven side clutch plate 7 is released to prevent the driving force of the engine E from being transmitted to the wheels D. .

  More specifically, as shown in FIG. 5, a spline extending in the axial direction (horizontal direction in FIG. 5) is formed on the outer peripheral side surface 4e of the clutch member 4, and the driven clutch plate 7 is formed on the spline. Is formed by fitting. That is, the spline formed on the outer peripheral side surface 4e of the clutch member 4 has an uneven shape integrally formed over substantially the entire periphery of the outer peripheral side surface 4e of the clutch member 4, as shown in FIG. When the driven clutch plate 7 is fitted into the groove forming the spline, the movement of the driven clutch plate 7 in the rotational direction is restricted while allowing the axial movement of the driven clutch plate 7 with respect to the clutch member 4. It is configured to be able to rotate with the clutch member 4.

  The driven-side clutch plates 7 are alternately laminated with the drive-side clutch plates 6, so that the adjacent clutch plates 6, 7 can be pressed or released. That is, the two clutch plates 6, 7 are allowed to slide in the axial direction of the clutch member 4, and the pressure member 5 moves to the left in FIG. When 4d approaches, the two clutch plates 6 and 7 are pressed against each other, and the rotational force of the clutch housing 2 is transmitted to the clutch member 4 and the output shaft 3 via the pressure member 5, and the pressure member 5 is moved to the right side in FIG. When the flange surface 5c and the flange surface 4d of the clutch member 4 are separated from each other, the pressing force of the two clutch plates 6, 7 is released, and the clutch member 4 stops following the rotation of the clutch housing 2 and stops. The transmission of the rotational force to the output shaft 3 is not performed.

  In a state where the driving-side clutch plate 6 and the driven-side clutch plate 7 are pressed against each other, the rotational force (the driving force of the engine) input to the clutch housing 2 is transmitted to the wheels via the output shaft 3 (the output member). While the torque is transmitted to the D side and the pressure contact between the drive side clutch plate 6 and the driven side clutch plate 7 is released, the rotational force (drive force of the engine) input to the clutch housing 2 is output to the output shaft 3 (output). ) Can be blocked.

  Further, in the present embodiment, as shown in FIGS. 5 and 6, the clutch member 4 is formed with inclined surfaces 4a and 4b, and the pressure member 5 is provided with the inclined surfaces 4a and 4b. Surfaces 5a and 5b are formed. In other words, the slope 4a and the slope 5a are in contact with each other to form a press-contact assist cam, and the slope 4b and the slope 5b are in contact with each other to form a back torque limiter cam.

  Then, the rotational speed of the engine E 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 pressure member 5 and the clutch member 4 (when the weight member is on the outer diameter side). 15), the rotational force in the direction a is applied to the pressure member 5 as shown in FIG. 15, and the pressure-contact assist cam acts on the pressure member 5 in the direction c in FIG. To generate force. As a result, the pressure member 5 moves in a direction (the left side in FIG. 2) in which the flange surface 5c is closer to the flange surface 4d of the clutch member 4, and the drive side clutch plate 6 and the driven side clutch plate 7 Is increased.

  On the other hand, when the rotation of the output shaft 3 exceeds the number of rotations of the input gear 1 and the clutch housing 2 during running of the vehicle, and a back torque in the direction b in FIG. 16 is generated, the back torque limiter cam acts. The pressure member 5 is moved in the direction d in the figure to release the pressure contact force between the driving side clutch plate 6 and the driven side clutch plate 7. As a result, it is possible to avoid problems with the power transmission device and the power source (engine side) due to the back torque.

  The weight member 8 is disposed in a groove 12a extending in the radial direction of the weight housing 12, and the inner circumferential position of the groove 12a due to centrifugal force caused by the rotation of the clutch housing 2 and the weight housing 12 (see FIG. 2). The drive clutch plate 6 and the driven clutch plate 7 can be pressed into contact with each other by moving from the position to the outer diameter side position (see FIG. 19). That is, the rolling surface (bottom surface) of the weight member 8 in the groove 12a is inclined upward from the inner diameter position to the outer diameter position, and the weight member 8 is stopped when the clutch housing 2 and the weight housing 12 are stopped. When the clutch housing 2 and the weight housing 12 rotate, a centrifugal force is applied to the weight member 8 to move the weight member 8 along an upward slope (see FIG. 18), and the clutch housing 2 and the weight housing 12 are rotated. When 12 reaches a predetermined number of revolutions, it is moved to the outer diameter side position (see FIG. 19).

  As shown in FIG. 7, the interlocking member 9 is formed of an annular member in which a hole 9 a is formed in the center and a plurality of protrusions 9 b protrude from the outer peripheral edge, and the protrusion 9 b is formed in the weight housing 12. Each is fitted and connected to a groove shape 12d (see FIG. 4) formed in the axial direction, is rotatable together with the weight housing 12, and is movable in the left-right direction in FIG. The interlocking member 9 moves to the left in FIG. 2 against the urging force of the elastic member 13 as the weight member 8 moves from the inner diameter position to the outer diameter position, and presses the pressure member 5. It is configured to be able to move from the inoperative position to the operating position.

  The elastic member 13 (clutch spring) is composed of a coil spring interposed between the interlocking member 9 (specifically, the auxiliary member F attached to the interlocking member 9) and the pressure member 5. The pressure member 5 can be moved in the direction of pressing the drive-side clutch plate 6 and the driven-side clutch plate 7 by pressing the pressure member 5 along with the movement of the pressure member 5. It can absorb the pressing force on the interlocking member 9. As shown in FIG. 2, a thrust bearing B2 is interposed between the elastic member 13 and the auxiliary member F attached to the interlocking member 9.

  That is, when the weight member 8 moves from the inner diameter position to the outer diameter position with the rotation of the clutch housing 2 and the weight housing 12 and the interlocking member 9 is pressed by the weight member 8, the pressing force is reduced by the elastic member 13. 18 and 19, the pressure member 5 is moved to the left in the drawing to press the drive-side clutch plate 6 and the driven-side clutch plate 7 into pressure contact with each other, as shown in FIGS. When the actuating member 10 is actuated at, as shown in FIG. 22, the pressure member 5 moves rightward in the figure by the axial movement of the actuating member 10, but the pressing force against the interlocking member 9 is applied to the elastic member 13. Thus, the position of the interlocking member 9 (the position of the weight member 8) is maintained.

  In the interlocking member 9 according to the present embodiment, a housing portion 9c for housing the one-way clutch 11 is formed on the periphery of a hole 9a formed in the center thereof. When the weight member 8 is at the inner diameter side position, the one-way clutch 11 cuts off power transmission from the input gear 1 (input member) to the output shaft 3 (output member), and also receives input from the output shaft 3 (output member). The power is transmitted to the gear 1 (input member), and includes an inner member 11a, a retainer member 11b, a roller 11c, and a spring 11d.

  As shown in FIGS. 8 and 9, the inner member 11a is formed of an annular member having an outer peripheral wall surface 11aa and a surface 11ab on which a plurality of fitting surfaces Ka (see FIG. 10) are formed, and is interlocked with the outer peripheral wall surface 11aa. A plurality of rollers 11c and springs 11d are mounted between the member 9 and the inner peripheral wall surface of the retainer member 11b. That is, as shown in FIG. 11, the retainer member 11b is formed with a plurality of attachment portions 11ba, and the base end of a spring 11d having a roller 11c fixed to the distal end is attached to the attachment portion 11ba. When the inner member 11b is assembled to the inner member 11a and the interlocking member 9, the roller 11c is located between the outer peripheral wall surface 11aa of the inner member 11a and the inner peripheral surface of the interlock member 9 as shown in FIG.

  Further, as shown in FIG. 7, a cam is formed on the outer peripheral wall surface 11aa of the inner member 11a so as to be fitted with the roller 11c which rotates relatively in one direction and not fitted with the roller 11c which rotates relatively in the other direction. I have. Accordingly, when the rotation speed of the clutch housing 2 is higher than the rotation speed of the output shaft 3 (that is, at the time of power transmission from the input gear 1 to the output shaft 3), the inner member 11a and the interlocking member 9 are relatively moved in the other direction. The roller 11c does not engage with the cam, but the one-way clutch 11 idles so that power transmission is not performed. On the other hand, when the rotation speed of the output shaft 3 is higher than the rotation speed of the housing 2 (that is, during power transmission from the output shaft 3 to the input gear 1), the inner member 11a and the interlocking member 9 relatively rotate in one direction. Therefore, the power is transmitted by the one-way clutch 11 by the engagement of the roller 11c with the cam.

  The actuating member 10 has an external shape as shown in FIG. 12 and is actuated by operating means T (see FIG. 2) which can be operated manually or by an actuator, so that the drive side clutch plate 6 and the driven side clutch plate 7 The pressure member 5 can be moved in a direction in which the pressing force can be released (right side in FIG. 2). The operating means T is movable to the right in the axial direction in FIG. 2 by, for example, operating a clutch pedal or a clutch lever provided in the vehicle or operating an actuator. The operating means T is provided on the inner race side of the bearing B1 attached to the operating member 10. And the operating member 10 can be pressed rightward in FIG.

  More specifically, the operating member 10 is composed of a component attached to an opening 5d formed at the center of the pressure member 5, rotates together with the pressure member 5, and has an axis (rotation axis) with respect to the pressure member 5. ). Further, the actuating member 10 according to the present embodiment can move the pressure member 5 in the same direction by moving in the axial direction of the pressure member 5, and includes a holding portion 10a that holds the bearing B1 and a one-way clutch 11. A dog clutch 10b (blocking means) that can block power transmission from the output shaft 3 (output member) to the input gear 1 (input member) is integrally formed. A disc spring 14 is mounted between the operating member 10 and the circlip 16 fixed to the clutch member 4, and the operating member 10 is urged to the right in FIG. It is assembled in.

  Thus, when the operating member 10 is pressed to the right in FIG. 2 by the operating means T (or actuator), for example, during a gear shift, the operating member 10 resists the urging force of the disc spring 14 in the opening 5 d of the pressure member 5. It moves, and in the moving process, comes into contact with the circlip 15 fixed to the pressure member 5, and the pressure member 5 can be moved in the same direction from the non-operation position to the operation position.

  Here, as shown in FIGS. 12 and 13, a dog clutch 10b (cutoff means) is integrally formed on the base end side of the operating member 10 according to the present embodiment. The dog clutch 10b can interrupt power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11, and is engaged with a fitting surface Ka (see FIG. 10) formed on the one-way clutch 11 (the inner member 11a). It has a fitting surface Kb (see FIG. 14).

  That is, when the operating member 10 is not operated, the fitting surface Kb of the dog clutch 10b formed on the operating member 10 meshes with the fitting surface Ka of the one-way clutch 11, as shown in FIG. (Engaged state), the power transmission from the output shaft 3 to the input gear 1 is performed by the one-way clutch 11, and when the operating member 10 is operated, as shown in FIG. 11, the engagement between the fitting surface Kb and the fitting surface Ka is released, so that power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 can be cut off.

  Further, when the clutch housing 2 and the weight housing 12 reach a predetermined number of rotations and the weight member 8 moves from the inner diameter position to the outer diameter position, as shown in FIG. Since the clutch 11 is separated from the dog clutch 10b of the operating member 10, the engagement (fitting) between the fitting surface Ka and the fitting surface Kb is released. Thereby, the power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 can be cut off by moving the weight member 8 from the inner diameter side position to the outer diameter side position.

  In addition, in the present embodiment, the pressure member 5 and the weight housing 12 are provided with openings (nuts N) for fastening the output member and the clutch member to expose the fastening means (nut N) for attaching the entire device to the vehicle. An opening 5d of the pressure member 5 and an opening 12b) of the weight housing 12 are formed, and the operating member 10 is attached to the opening 5d of the pressure member 5. In particular, in the present embodiment, an opening through which a nut N for attaching the entire power transmission device to a vehicle (the output shaft 3 of the vehicle) can be exposed to the outside is provided in addition to the pressure member 5 and the weight housing 12, as well as the interlocking member 9 (hole 9a). ), Etc., so that when the operating member 10 is removed, the nut N faces the outside through the openings and holes.

  On the other hand, as shown in FIG. 4, the weight housing 12 according to the present embodiment has a plurality of protrusions 12c formed to protrude laterally from the outer peripheral surface thereof in the circumferential direction, and as shown in FIG. The portion 12c is fitted to a predetermined position in the clutch housing 2 and attached to the clutch housing 2. The wall La near the opening end Q of the weight housing 12 and the wall near the opening end P of the clutch housing 2. The portion Lb is overlapped. Specifically, as shown in FIG. 3, the clutch housing 2 is formed with a plurality of notches 2 a in the circumferential direction for fitting the driving-side clutch plate 6, and the notch 2 a The projection 12c is fitted and assembled, whereby the outer peripheral surface of the wall La near the opening end Q of the weight housing 12 and the inner periphery of the wall Lb near the opening end P of the clutch housing 12 are assembled. The walls (La, Lb) are overlapped so that they face each other.

  In addition, the protrusion 12c according to the present embodiment is fitted into the notch 2a at a position on the bottom side (left side in FIG. 2) of a predetermined dimension from the opening end P (opening end face) of the clutch housing 2, and the clutch 2 A circlip 17 attached to the inner circumferential surface of the housing 2 prevents the circlip 17 from coming off. That is, the drive side clutch plate 6 stacked with the driven side clutch plate 7 is fitted into the notch 2a of the clutch housing 2, and the weight housing 12 is provided on the opening side end P side of the notch 2a. Are fitted and fixed by the circlip 17.

Next, the operation of the power transmission device according to the present embodiment will be described.
When the engine E of the vehicle is stopped or idling, the driving force of the engine E is not transmitted to the input gear 1 or the rotation speed of the input gear 1 is low, and therefore, as shown in FIG. The side position and the pressure member 5 are in the non-operation position. At this time, the clutch is turned off (the pressure contact between the driving side clutch plate 6 and the driven side clutch plate 7 is released), the one-way clutch 11 is turned off (the state where power is not transmitted), and the dog clutch 10b is turned on (the power is transmitted). In this state, the pressure assist cam is off, the back torque limiter cam is off, and the operating member 10 is inactive.

  When the vehicle starts after the vehicle is stopped or idling, the rotation speed of the input gear 1 shifts from a low rotation to a high rotation (middle rotation range). Therefore, as shown in FIG. The position is between the position and the outer diameter side position, and the pressure member 5 is between the non-operation position and the operation position. At this time, the clutch is turned on (a state in which the pressure contact between the driving-side clutch plate 6 and the driven-side clutch plate 7 is started), the one-way clutch 11 is turned off (a state in which power is not transmitted), and the dog clutch 10b is turned off (a power is not transmitted). State), the cam for press-contact assist is on, the cam for the back torque limiter is off, and the operating member 10 is inactive.

  When the vehicle accelerates after starting and travels in a high-speed range, since the rotation speed of the input gear 1 is high, as shown in FIG. The member 5 is in the operating position. At this time, the clutch is turned on (a state in which the driving-side clutch plate 6 and the driven-side clutch plate 7 are pressed against each other), the one-way clutch 11 is turned off (a state where power is not transmitted), and the dog clutch 10b is turned off (a state where power is not transmitted). State), the cam for press-contact assist is on, the cam for the back torque limiter is off, and the operating member 10 is inactive.

  When the vehicle shifts in a high-speed range, as shown in FIG. 20, the operating member 10 operates and moves to the right in FIG. Note that the weight member 8 is held at the outer diameter side position, and the pressure member 5 is in the non-operation position. At this time, the clutch is off (the pressure contact between the driving-side clutch plate 6 and the driven-side clutch plate 7 is released), the one-way clutch 11 is off (the state where power is not transmitted), and the dog clutch 10b is off (the power is not transmitted). State), the cam for press-contact assist is off, the cam for back torque limiter is on, and the operating member 10 is operated.

  When the vehicle decelerates in a low speed range, the rotation speed of the input gear 1 becomes lower than the rotation speed of the output shaft 3, so that as shown in FIG. Inactive position. At this time, the clutch is turned off (the pressure contact between the driving-side clutch plate 6 and the driven-side clutch plate 7 is released), the one-way clutch 11 is turned on (a state where power can be transmitted), and the dog clutch 10b is turned on (the power is transmitted). State), the pressure assist cam is off, the back torque limiter cam is off, and the operating member 10 is inactive.

  When the vehicle shifts in a low speed range, the operating member 10 operates as shown in FIG. In addition, the weight member 8 is set to the inner diameter side position, and the pressure member 5 is set to the non-operation position. At this time, the clutch is off (the pressure contact between the driving-side clutch plate 6 and the driven-side clutch plate 7 is released), the one-way clutch 11 is off (the state where power is not transmitted), and the dog clutch 10b is off (the power is not transmitted). State), the cam for pressure assist is off, the cam for the back torque limiter is off, and the operating member 10 is in operation.

  Further, when the vehicle travels downhill or starts the engine E by a kick starter, as shown in FIG. 23, the weight member 8 is at the inner diameter side position, and the pressure member 5 is at the non-operation position. . At this time, the clutch is turned off (the pressure contact between the driving-side clutch plate 6 and the driven-side clutch plate 7 is released), the one-way clutch 11 is turned on (a state where power can be transmitted), and the dog clutch 10b is turned on (the power is transmitted). State), the pressure assist cam is off, the back torque limiter cam is off, and the operating member 10 is inactive.

  According to the present embodiment, when the weight member 8 is at the inner diameter side position, power transmission from the input gear 1 (input member) to the output shaft 3 (output member) is cut off, and the output shaft 3 And a dog clutch 10b (interruption means) capable of interrupting the transmission of power from the output shaft 3 to the input gear 1 by the one-way clutch 11 and a dog clutch 10b (interruption) provided to the operating member 10. Since the (means) is integrally formed, even if the weight member 8 is at the inner diameter side position, it is possible to satisfactorily cause engine braking and suppress an increase in the number of parts.

  In addition, according to the present embodiment, when the weight member 8 is at the inner diameter position, power transmission from the input gear 1 (input member) to the output shaft 3 (output member) is cut off, and the input from the output shaft 3 is stopped. Since the one-way clutch 11 for transmitting power toward the gear 1 is provided, when the weight member 8 is at the inner diameter side position, the rotational force on the wheel D side can be transmitted to the engine E side to cause engine braking. At the same time, the engine can be started by the kick starter.

  Further, during traveling of the vehicle, the power transmission from the output shaft 3 (output member) to the input gear 1 (input member) is performed when the weight member 8 is at the outer diameter side, and the drive-side clutch plate 6 and the pressure-contacted clutch plate 6 are pressed. This is performed by the one-way clutch 11 when the weight member 8 is located at the inner diameter side position, while being performed by the driven-side clutch plate 7. Therefore, the power transmission path from the output shaft 3 to the input gear 1 can be made different depending on the position of the weight member 8, and the power transmission from the output shaft 3 to the input gear 1 can be appropriately performed.

  Further, the one-way clutch 11 according to the present embodiment is attached to the interlocking member 9, and performs power transmission from the output shaft 3 to the input gear 1 via the interlocking member 9 when the weight member 8 is at the inner diameter position. Therefore, the function of moving the pressure member 5 from the non-operation position to the operation position and the function of transmitting power from the output shaft 3 to the input gear 1 can be combined with the interlocking member 9.

  In particular, since the dog clutch 10b (interrupting means) is integrally formed with the operating member 10, the movement of the pressure member 5 by the operating member 10 and the interruption of the power transmission by the dog clutch 10b can be simultaneously performed by the same member during shifting. As a result, the responsiveness of the dog clutch 10b can be further improved. Further, in the present embodiment, since the shutoff means is constituted by the dog clutch 10b formed on the operating member 10, the power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 and the cutoff of the power transmission are reliably performed. Can be made.

  Further, the pressure member 5 according to the present embodiment can expose a nut N (fastening means) for fastening the output shaft 3 and the clutch member 4 to attach the entire device (the present power transmission device) to the vehicle. Since the opening 5d is formed and the operating member 10 is attached to the opening 5d, the fastening can be released by a tool by removing the operating member 10 and exposing the nut N to the outside, so that the vehicle can be released from the vehicle. The work of removing the entire apparatus can be performed more easily.

  Particularly, in the present embodiment, an opening through which the nut N (fastening means) can be exposed is formed in both the pressure member 5 and the weight housing 12, and the operating member 10 is attached to the opening 5d of the pressure member 5. Thus, the fastening can be released with a tool by removing the operating member 10 and exposing the nut N to the outside, and the work of removing the entire device from the vehicle can be performed more easily.

  Further, the clutch housing 2 according to the present embodiment is formed of a cup-shaped member having a bottom, and the weight housing 12 having the groove 12a is attached to the opening side (the opening end P side) of the clutch housing 2. In addition, a power transmission device in which the weight member 8 is disposed on the opening side of the clutch housing 2 can be provided.

  The actuating member 10 according to the present embodiment moves in the axial direction of the pressure member 5 when it is manually operated or operated by an actuator, and abuts on a circlip 15 fixed to the pressure member 5 during the moving process. Since the pressure member 5 can be moved in the same direction to change from the non-operation position to the operation position, the movement of the operation member 10 can be restricted and the pressure member 5 can be easily moved from the non-operation position to the operation position via the circlip 15. Can be done.

  In addition, according to the present embodiment, the weight housing 12 has the protruding portion 12c formed to protrude laterally from the outer peripheral surface thereof, and the protruding portion 12c is fitted to a predetermined position in the clutch housing 2. Since the wall portion La attached to the clutch housing 2 and near the opening end Q of the weight housing 12 and the wall Lb near the opening end P of the clutch housing 2 overlap each other, the clutch housing 2 Even when the weight housing 12 accommodating the weight member 8 is mounted on the opening side (opening end P side), it is possible to suppress an increase in the size in the radial and axial directions.

  Further, the weight housing 12 according to the present embodiment is formed of a cup-shaped member having a bottom, and the protruding portion 12c is fitted to a position on the bottom side of a predetermined dimension from the opening side end P of the clutch housing 2, so that Even when the weight housing 12 accommodating the weight member 8 is attached to the opening side of the clutch housing 2, it is possible to suppress an increase in the size in the radial and axial directions. Particularly, in the clutch housing 2 according to the present embodiment, the notch 2a for fitting the drive-side clutch plate 6 is formed, and the projection 12c of the weight housing 12 is fitted to the notch 2a. The fitting of the drive-side clutch plate 6 and the fitting of the protruding portion 12c of the weight housing 12 can both be performed in the notch 2a of the clutch housing 2.

  Further, in the weight housing 12 according to the present embodiment, a bulging portion 12e bulging in the circumferential direction is formed at the opening side end portion Q, and the bulging portion 12e is formed on the opening side of the clutch housing 2. Since the weight housing 12 is positioned in the radial direction by contacting the mounting surface 2b formed at the end P, the movement of the weight member 8 can be transmitted to the pressure member 5 more accurately, and the apparatus Can be improved in reliability. In particular, the mounting surface 2b according to this embodiment is provided with a mounting groove 2c into which the circlip 17 can be fitted, and the circlip 17 fitted into the mounting groove 2c can prevent the weight housing 12 from coming off. Therefore, the positioning accuracy of the weight housing 12 with respect to the clutch housing 2 can be further improved.

  Furthermore, in the present embodiment, the inclined surface 4 a formed on the clutch member 4 and the inclined surface 5 a formed on the pressure member 5 are opposed to each other, and the rotational force input to the input gear 1 is applied to the output shaft 3. Is provided for increasing the pressure contact force between the driving-side clutch plate 6 and the driven-side clutch plate 7 when the weight member 8 is moved to a state where the weight member 8 is moved by centrifugal force. In addition to the force, the pressing force by the pressing assist cam can be applied, so that the driving side clutch plate 6 and the driven side clutch plate 7 can be pressed more smoothly and reliably.

  Further, according to the present embodiment, the inclined surface 4b formed on the clutch member 4 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 rotates the rotation of the input gear 1. When the clutch member 4 and the pressure member 5 rotate relative to each other in excess of the number, a cam for a back torque limiter capable of releasing the pressure contact force between the drive side clutch plate 6 and the driven side clutch plate 7 is provided. When the weight member 8 is at the outer diameter position, it is possible to prevent excessive power from being transmitted to the engine E via the input gear 1.

  Although the present embodiment has been described above, the present invention is not limited to these. For example, the shut-off means integrally formed with the operating member 10 is a power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11. Any other means that can shut off the power supply may be used, and other forms of interrupting means (such as a friction clutch) may be used. Further, the pressure assist cam or the back torque limiter cam may not be provided.

  Further, in the present embodiment, the one-way clutch 11 and the dog clutch 10b as the disconnecting means are provided, but they may not be provided, and even if they are provided, the dog clutch 10b The (blocking means) is not limited to being integrally formed, but may be provided separately. The power transmission device of the present invention can be applied to various multi-plate clutch type power transmission devices such as automobiles, three-wheel or four-wheel buggies, and general-purpose machines, in addition to two-wheeled vehicles.

Weight housing and having a protruding portion formed to project laterally from the outer peripheral surface thereof, the weight housing by the protrusion is fixed in contact with the retaining member being fitted in place in the clutch housing A power transmission that is attached to the clutch housing while being locked in the rotation direction and the axial direction, and a wall near the opening end of the weight housing and a wall near the opening end of the clutch housing overlap each other. The present invention can be applied to a device having a different external shape or a device to which another function is added.

1 Input gear (input member)
2 Clutch housing 2a Notch 2b Mounting surface 2c Mounting groove 3 Output shaft (output member)
Reference Signs List 4 clutch members 4a, 4b inclined surface 4c central hole 4d flange surface 4e outer peripheral side surface 5 pressure member 5a, 5b inclined surface 5c flange surface 5d opening 6 drive side clutch plate 7 driven side clutch plate 8 weight member 9 interlocking member 9a hole 9b convex Part 9c Housing part 10 Operating member 10a Holding part 10b Dog clutch (cutoff means)
Reference Signs List 11 One-way clutch 11a Inner member 11b Retainer member 12 Weight housing 12a Groove portion 12b Opening 12c Projection portion 12d Groove shape 12e Swelling portion 13 Elastic member 14 Disc spring 15 Circlip 16 Circlip 17 Circlip N nut (fastening means)
F Mounting member E Engine D Wheel P Open end (of clutch housing) Q Open end (of weight housing)

Claims (8)

A clutch housing comprising a bottomed cup-shaped member, rotating together with an input member rotating by the driving force of the vehicle engine, and having a plurality of drive-side clutch plates formed therein;
A plurality of driven clutch plates alternately formed with a drive clutch plate of the clutch housing;
A clutch member coupled to an output member capable of rotating wheels of the vehicle,
An operating position where the drive-side clutch plate and the driven-side clutch plate are brought into pressure contact with each other so that the driving force of the engine can be transmitted to the wheels, and the pressure-contact force between the drive-side clutch plate and the driven-side clutch plate is released. A pressure member movable between an inoperative position where the driving force of the engine can be blocked from being transmitted to the wheels;
The clutch housing is disposed in a groove extending in the radial direction, and is movable from an inner diameter side position to an outer diameter side position of the groove part by centrifugal force caused by rotation of the clutch housing. Along with moving from the position to the outer diameter side position, a weight member capable of moving the pressure member from the non-operation position to the operation position,
A weight housing that is attached to the opening side of the clutch housing and has the groove formed therein and accommodates the weight member;
In the power transmission device having
The weight housing, which has a projecting portion formed to project laterally from the outer peripheral surface thereof by the protruding portion is fixed in contact with the retaining member being fitted in a predetermined position within the clutch housing The weight housing is attached to the clutch housing in a state where the weight housing is locked in the rotation direction and the axial direction, and a wall near the opening end of the weight housing and a wall near the opening end of the clutch housing are formed. A power transmission device characterized by being overlapped.   2. The weight housing according to claim 1, wherein the weight housing is formed of a cup-shaped member having a bottom, and the protruding portion is fitted at a position on the bottom side of a predetermined dimension from an open end of the clutch housing. 3. Power transmission device.   The pressure member and the weight housing are formed with an opening through which a fastening unit for fastening the output member and the clutch member to attach the entire device to the vehicle can be exposed to the outside, and can be operated manually or by an actuator. 3. The power transmission device according to claim 1, wherein an operating member capable of moving the pressure member from the operating position to the non-operating position is attached to an opening of the pressure member.   The notch for fitting the driving side clutch plate is formed in the clutch housing, and the protrusion of the weight housing is fitted in the notch. A power transmission device according to any one of the above.   The weight housing has a bulging portion bulging in the circumferential direction at an opening end thereof, and the bulging portion abuts a mounting surface formed at the opening end of the clutch housing. The power transmission device according to any one of claims 1 to 4, wherein the weight housing is positioned in a radial direction.   6. The mounting surface according to claim 5, wherein a mounting groove in which a circlip can be fitted is formed on the mounting surface, and the weight housing can be prevented from coming off by the circlip fitted in the mounting groove. Power transmission device.   When the gradient surface formed on the clutch member and the gradient surface formed on the pressure member are opposed to each other, and when the rotational force input to the input member can be transmitted to the output member, The power transmission device according to any one of claims 1 to 6, further comprising a press-contact assist cam for increasing a press-contact force between the drive-side clutch plate and the driven-side clutch plate.   The inclined surface formed on the clutch member and the inclined surface formed on the pressure member are opposed to each other, and the rotation of the output member exceeds the number of rotations of the input member and the clutch member and the pressure member are relatively opposed to each other. 8. A back torque limiter cam capable of releasing a pressure contact force between the driving side clutch plate and the driven side clutch plate when rotated in a specific manner. Power transmission device.

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