JP6535346B2 - Power transmission - Google Patents

Description

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

  In general, a power transmission device provided in a motorcycle is for arbitrarily transmitting or interrupting a driving force of an engine to a transmission and driving wheels, and an input member connected to the engine side, a transmission and a driving wheel side, and the like. It has the output member connected, the clutch member connected with the output member, and the pressure member which can be approached or separated with respect to the clutch member, and by driving the pressure member close to 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 drive side clutch plate and the driven side clutch plate In order to block the transmission of the power.

  Further, as disclosed in, for example, Patent Document 1 as a conventional power transmission device, it is disposed in a groove portion extending in the radial direction of the clutch housing, and the groove portion is produced by the centrifugal force accompanying the rotation of the clutch housing. It has been proposed to have a weight member capable of pressing the drive side clutch plate and the driven side clutch plate by moving from the inner diameter side position to the outer diameter side position. According to such a conventional power transmission device, the centrifugal force can be applied to the weight member by the rotation of the clutch housing with the drive 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.

International Publication 2013/183588 Publication

  However, in the above-described conventional power transmission device, when the engine is at a predetermined rotational speed or less and the weight member is at the inner diameter side position, the drive clutch plate and the driven clutch plate are not in pressure contact with each other. There is a problem that the force can not be transmitted to the engine side to cause engine braking. In addition, since the weight member is at the inner diameter side while the vehicle is stopped, there is a problem that it is impossible to provide a mechanism for starting the engine by the kick starter.

  The present invention has been made in view of such circumstances, and when the weight member is at the inner diameter side position, the rotational force on the wheel side can be transmitted to the engine side to produce an engine brake, and a kick starter It is an object of the present invention to provide a power transmission device capable of enabling an engine start by the

  The invention according to claim 1 is formed alternately with a clutch housing which is rotated with an input member which is rotated by a driving force of an engine of a vehicle and in which a plurality of drive side clutch plates are formed, and the drive side clutch plates of the clutch housing. The driving force of the engine is applied to the wheels by bringing the driven clutch plates and the driven clutch plates into pressure contact with a plurality of driven clutch plates, a clutch member connected to an output member capable of rotating the wheels of the vehicle, And a non-operating position capable of releasing transmission of the driving force of the engine to the wheel by releasing the pressure contact force between the drive-side clutch plate and the driven-side clutch plate. The pressure member, which is movable between the two grooves, is disposed in a groove extending in the radial direction of the clutch housing, and a centrifugal force accompanying the rotation of the clutch housing A weight member movable from a radial position to an outer diameter position, and the pressure member moving from the non-operating position to the operating position as the weight member moves from the inner diameter position to the outer diameter position Power transmission device having an interlocking member that can be moved to the first position, the power transmission device being attached to the interlocking member and interrupting power transmission from the input member to the output member when the weight member is at the inner diameter side position And a one-way clutch for transmitting power from the output member to the input member via

  The invention according to claim 2 is characterized in that the power transmission device according to claim 1 is provided with blocking means capable of interrupting the power transmission from the output member to the input member by the one-way clutch.

  The invention according to claim 3 is the power transmission device according to claim 2, further comprising an actuating member operable by manual operation or an actuator to move the pressure member from the actuating position to the actuating position. The shutoff means is characterized in that power transmission from the output member to the input member by the one-way clutch can be shut off by the operation of the actuating member.

  The invention according to claim 4 is characterized in that, in the power transmission device according to claim 2 or claim 3, the blocking means comprises a dog clutch.

  According to a fifth aspect of the present invention, in the power transmission apparatus according to the fourth aspect, the dog clutch is configured to transmit a first fitting surface capable of transmitting power from the input member toward the output member, and from the output member toward the input member. A second fitting surface capable of transmitting power is provided, and the second fitting surface is a tapered surface capable of releasing the fitting when a predetermined load or more is applied.

  According to a sixth aspect of the present invention, in the power transmission apparatus according to the fourth aspect, the dog clutch includes: a first fitting surface capable of transmitting power from the input member toward the output member; A second fitting surface capable of transmitting power is provided, and the first fitting surface is a sloped surface acting in a meshing direction when a load is applied in the axial direction.

  The invention according to claim 7 is the power transmission apparatus according to any one of claims 1 to 6, wherein the sloped surface formed on the clutch member and the sloped surface formed on the pressure member are opposed to each other. A pressure-contacting assist cam for increasing a pressure-contacting force between the drive-side clutch plate and the driven-side clutch plate when the rotational force input to the input member can be transmitted to the output member; It is characterized by being equipped.

  According to an eighth aspect of the present invention, in the power transmission device according to any one of the first to seventh aspects, the sloped surface formed on the clutch member and the sloped surface formed on the pressure member are opposed to each other. The pressure contact force between the drive side clutch plate and the driven side clutch plate can be released when the rotation of the output member exceeds the number of rotations of the input member and the clutch member and the pressure member relatively rotate. A cam for back torque limiter is provided.

  According to the invention of claim 1, when the weight member is at the inner diameter side position, it has a one-way clutch for blocking power transmission from the input member to the output member and for performing power transmission from the output member to the input member. Therefore, when the weight member is at the inner diameter side position, the rotational force on the wheel side can be transmitted to the engine side to generate the engine brake, and the engine can be started by the kick starter.

  In addition, while the vehicle is traveling, power transmission from the output member to the input member is performed by the drive-side clutch plate and the driven-side clutch plate in pressure contact when the weight member is at the outer diameter side position. When in the inner diameter position, it is performed by the one-way clutch. Therefore, the power transmission path from the output member to the input member can be varied according to the position of the weight member, and the power transmission from the output member to the input member can be appropriately performed.

  Furthermore, the one-way clutch is attached to the interlocking member, and when the weight member is at the inner diameter side, power transmission from the output member toward the input member is performed via the interlocking member, so that the pressure member is not The function of moving from the operating position to the operating position can be combined with the function of transmitting power from the output member to the input member.

  According to the second aspect of the invention, the shutoff means capable of interrupting the power transmission from the output member to the input member by the one-way clutch is provided, so that the power transmission from the output member to the input member by the one-way clutch is interrupted at necessary timing. can do.

  According to the invention of claim 3, the actuating member is provided which can be actuated manually or by an actuator to move the pressure member from the actuating position to the inoperative position, and the blocking means is a one-way clutch by the actuating member. Since power transmission from the output member to the input member can be interrupted, power transmission from the output member to the input member by the one-way clutch can be interrupted at any timing.

  According to the fourth aspect of the present invention, since the shutoff means comprises a dog clutch, power transmission from the output member to the input member by the one-way clutch and the shutoff of the power transmission can be reliably performed.

  According to the invention of claim 5, the dog clutch comprises: a first fitting surface capable of transmitting power from the input member to the output member; and a second fitting surface capable of transmitting power from the output member to the input member Since the second fitting surface is a tapered surface that can release the fitting when a predetermined load or more is applied, an excessive load is applied to the dog clutch when transmitting power from the output member to the input member. Can be prevented from being damaged or deformed.

  According to the invention of claim 6, the dog clutch comprises: a first fitting surface capable of transmitting power from the input member to the output member; and a second fitting surface capable of transmitting power from the output member to the input member Because the first fitting surface is a sloped surface that acts in the meshing direction when a load is applied in the axial direction, the first fitting surface carelessly separates in the axial direction to transmit power. Can be prevented from being blocked.

  According to the invention of claim 7, the gradient surface formed on the clutch member and the gradient surface formed on the pressure member are configured to be opposed to each other, and the rotational force input to the input member can be transmitted to the output member The cam for pressure contact assist is provided to increase the pressure contact force between the drive side clutch plate and the driven side clutch plate when it becomes, so that the pressure contact assist cam is added to the pressure contact force accompanying the movement of the weight member by the centrifugal force. Thus, the pressure contact force can be applied, and the drive clutch plate and the driven clutch plate can be pressure-welded more smoothly and reliably.

  According to the invention of claim 8, the sloped surface formed on the clutch member and the sloped surface formed on the pressure member are configured to face each other, and the rotation of the output member exceeds the number of rotations of the input member and the clutch member When the weight member is at the outer diameter side position, since the cam for the back torque limiter which can release the pressure contact force between the drive side clutch plate and the driven side clutch plate when the pressure member and the pressure member relatively rotate is provided. It can be avoided that excessive power is transmitted to the engine side via the input member.

An external view showing a power transmission device according to an embodiment of the present invention Longitudinal sectional view showing an internal configuration of the power transmission device The perspective view which shows the input gear and clutch housing in the same power transmission device The perspective view which shows the dog in the same power transmission device Three views showing the dogna Cross section showing the mating surface of the same dogner The perspective view which shows the inner member which comprises the one-way clutch in the same power transmission device Three views showing the inner member Sectional drawing which shows 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 interlocking member in the same power transmission device Partially broken view showing a state in which the one-way clutch and dog inner are assembled to the interlocking member in the power transmission device FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG. 12, showing (a) a dog clutch in a fitted state (b) a state in which the dog clutch is disengaged The perspective view which shows the clutch member in the same power transmission device, a pressure member, and an operation member Schematic diagram for explaining the action of the pressure contact assist cam in the power transmission device Schematic diagram for explaining the action of the back torque limiter cam in the same power transmission device Schematic diagram for explaining the operation of the dog clutch in the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Longitudinal sectional view showing an internal configuration of the power transmission device Timing chart showing the operation contents of the same power transmission device Three views showing a dogger according to another embodiment of the present invention Three views showing an inner member which constitutes a one-way clutch in the other embodiment The perspective view which shows the inner member which comprises the dog inner and one way clutch in the other embodiment. The enlarged view which shows the state which the 1st fitting surface of the dog inner and inner member which concern on the same other embodiment fitted. The schematic diagram which shows the state which the 1st fitting surface of the dog inner and inner member which concern on the same other embodiment fitted.

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 blocking the driving force of the engine to the transmission or the drive wheel side as shown in FIGS. A clutch housing 2 in which an input gear 1 (input member) is formed to be rotated by a driving force of a vehicle engine E, and a clutch member 4 connected to an output shaft 3 (output member) capable of rotating the vehicle wheel D; 2, a pressure member 5 mounted on the left side of the clutch member 4 in FIG. 2, a plurality of drive clutch plates 6 and a plurality of driven clutch plates 7, and a rigid ball member capable of rolling in the clutch housing 2 in the radial direction. , The interlocking member 9, the actuating member 10 which can be operated by manual operation or an actuator (not shown), the one-way clutch 11, and the dog clutch (shutoff means). It is mainly composed to Doguin'na 12.

  The input gear 1 is rotatable about the output shaft 3 when the 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. The clutch housing 2 is, as shown in FIG. 3, formed of a cylindrical case member opened at the right end side in the figure, and is rotated with the rotation of the input gear 1 by the driving force of the engine E. A drive clutch plate 6 is formed. Each of the drive side clutch plates 6 is formed of a plate member formed in a substantially annular shape, and is configured to rotate along with the rotation of the clutch housing 2 and to slide in an axial direction (left and right direction in FIG. 2) There is.

  Further, as shown in FIGS. 2 and 3, the clutch housing 2 is formed with a plurality of groove portions 2 a extending in the radial direction of the clutch housing 2 on the bottom surface thereof. A weight member 8 is disposed in each of the groove portions 2a, and when the clutch housing 2 is stopped (engine stopped or idling) and rotated at a low speed, the weight member 8 is located on the inner diameter side (FIG. 2). When the clutch housing 2 is rotated at a high speed, the weight member 8 is set to the outer diameter side position (position shown in FIG. 19).

  The base end 4d of the clutch member 4 is connected to the tip end of the output shaft 3 (output member), and the output shaft 3 is also rotated when the clutch member 4 is rotated. A pressure member 5 is attached to the clutch member 4, and a plurality of drive clutch plates 6 and a driven clutch plate 7 are provided between the flange surface 5 c of the pressure member 5 and the flange surface 4 c of the clutch member 4. It is attached.

  The pressure member 5 causes the driving side clutch plate 6 and the driven side clutch plate 7 to be in pressure contact with each other to make the driving force of the engine E transmittable to the wheel D (see FIG. 19). It is movable between the inoperative positions (see FIG. 2) which can release the pressure contact force between 6 and the driven side clutch plate 7 to block the transmission of the driving force of the engine E to the wheel D. . As shown in FIG. 14, a spline 5d extending in the axial direction (left and right direction in the figure) is formed on the outer peripheral side surface of the pressure member 5, and the driven clutch plate 7 is fitted into the spline It is formed.

  More specifically, as shown in the figure, the splines 5 d formed on the pressure member 5 are configured to have a concavo-convex shape formed integrally over substantially the entire periphery of the outer peripheral side surface of the pressure member 5. By fitting the driven side clutch plate 7 into the concave groove forming the spline 5d, the movement in the rotational direction is restricted while permitting the axial movement of the driven side clutch plate 7 with respect to the pressure member 5, It is configured to be able to rotate with the pressure member 5.

  The driven side clutch plates 7 are alternately stacked with the drive side clutch plates 6 so that the adjacent clutch plates 6 and 7 can press-contact or release the press-contact force. That is, the both clutch plates 6 and 7 are allowed to slide in the axial direction of the pressure member 5, and the pressure member 5 moves to the right in FIG. 2 and the flange surface 5c and the flange surface of the clutch member 4 are moved. When 4c approaches, both clutch plates 6 and 7 are in pressure contact, 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 in the left side in FIG. When the flange surface 5c and the flange surface 4c of the clutch member 4 are separated, the pressing force of the both clutch plates 6 and 7 is released and the clutch member 4 does not follow the rotation of the clutch housing 2 and stops. The transmission of the rotational force to the output shaft 3 is not performed.

  Thus, in a state where the drive side clutch plate 6 and the driven side clutch plate 7 are in pressure contact, the rotational force (the driving force of the engine) input to the clutch housing 2 is transmitted via the output shaft 3 (output member) The rotational force (the driving force of the engine) input to the clutch housing 2 is transmitted to the output shaft 3 (the power 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). Can be blocked from being transmitted to the member.

  Furthermore, in the present embodiment, as shown in FIG. 14, while the inclined surfaces 4 a and 4 b are formed in the clutch member 4, the inclined surface 5 a facing the inclined surfaces 4 a and 4 b is formed on the pressure member 5. , 5b are formed. That is, the sloped surface 4a and the sloped surface 5a are in contact with each other to form a pressure contact assist cam, and the sloped surfaces 4b and 5b are in contact with each other to form a back torque limiter cam.

  Then, the rotational speed of the engine E is increased, and the rotational force input to the input gear 1 and the clutch housing 2 can be transmitted to the output shaft 3 through the pressure member 5 and the clutch member 4 (the weight member is on the outer diameter side When it comes to the position, as shown in FIG. 15, the rotational force in the direction a is applied to the pressure member 5, so that the pressure member 5 operates in the direction c in FIG. Power is generated. As a result, the pressure member 5 is moved in the direction (the right side in FIG. 2) in which the flange surface 5 c is closer to the flange surface 4 c of the clutch member 4, and the driving clutch plate 6 and the driven clutch plate 7 Pressure contact force is increased.

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

  The weight member 8 is disposed in the groove portion 2a extending in the radial direction of the clutch housing 2, and the centrifugal force accompanying the rotation of the clutch housing 2 causes an outer diameter from the inner diameter side position (see FIG. 2) of the groove portion 2a. By moving to the side position (see FIG. 19), the drive clutch plate 6 and the driven clutch plate 7 can be brought into pressure contact with each other. That is, the rolling surface (bottom surface) of the weight member 8 in the groove portion 2a has an upward slope from the inner diameter position to the outer diameter position, and the weight member 8 is not shown when the clutch housing 2 is stopped. While being held at the inner diameter side position by the pressing force of the biasing means, when the clutch housing 2 is rotated, a centrifugal force is applied to the weight member 8 to move along the upward slope (see FIG. 18). By reaching a predetermined number of rotations, it is moved to the outer diameter side position (see FIG. 19). The biasing means (not shown) is bent until the separation distance between the drive clutch plate 6 and the driven clutch plate 7 becomes zero, and thereafter the elastic member 13 is flexed to bend the drive clutch plate 6 and the driven clutch. The plate 7 is to be fastened. Further, at the time of gear change, both the biasing means (not shown) and the elastic member 13 will bend, and the pressure member 5 will move.

  As shown in FIG. 11, the interlocking member 9 is an annular member having a hole 9a at its center and a plurality of convex portions 9b formed at its outer peripheral edge, and the convex portion 9b is a wall portion of the clutch housing 2 The clutch housing 2 is engaged with and coupled to a notch 2b (see FIG. 3) formed therein, and is rotatable with the clutch housing 2 and movable in the lateral direction in FIGS. The interlocking member 9 moves to the right in FIG. 2 against the biasing force of the elastic member 13 as the weight member 8 moves from the inner diameter side position to the outer diameter side position, and presses the pressure member 5. It is configured to be moved from the inoperative position to the operative position.

  The elastic member 13 (clutch spring) is formed of a coil spring interposed between the interlocking member 9 and the pressure member 5, and presses the pressure member 5 with the movement of the interlocking member 9 to drive the clutch plate 6. The pressure member 5 can be moved in the direction in which the driven side clutch plate 7 is in pressure contact with it, and the pressing force of the pressure member 5 on the interlocking member 9 can be absorbed when the operation member 10 is operated. As shown in FIG. 2, a thrust bearing B2 is interposed between the elastic member 13 and the interlocking member 9 and assembled.

  That is, when the weight member 8 is moved from the inner diameter side position to the outer diameter side position with the rotation of the clutch housing 2 and the interlocking member 9 is pressed by the weight member 8, the pressing force is pressed via the elastic member 13. The pressure member 5 is transmitted to the member 5, and as shown in FIGS. 18 and 19, the pressure member 5 is moved to the right in the figure to bring the drive side clutch plate 6 and the driven side clutch plate 7 into pressure contact. When 10 is operated, as shown in FIG. 20, although the pressure member 5 moves to the left in the figure by the pressure of the operation member 10, the pressure on the interlocking member 9 is absorbed by the elastic member 13 and the interlocking is performed. The position of the member 9 (the position of the weight member 8) is held.

  The actuating member 10 has an external shape as shown in FIG. 14 and is operated by an operating means T (see FIG. 2) which can be operated manually or by an actuator, and the actuating clutch plate 6 and the driven clutch plate 7 The pressure member 5 can be moved in a direction (left side in FIG. 2) in which the pressure contact force can be released. The operating means T can be moved to the left side in FIG. 2 by, for example, the operation of a clutch pedal, a clutch lever or the like included in the vehicle, or the operation of an actuator, and on the inner race side of the bearing B1 attached to the actuating member 10. It abuts, and the operation member 10 can be pressed to the left in the figure.

  More specifically, the actuating member 10 is disposed between the pressure member 5 and a biasing means (not shown), and when it is pressed to the left in FIG. It moves against the biasing force of the biasing means and abuts against the pressure member 5 so that the pressure member 5 can be moved in the same direction. Furthermore, a stopper 14 is formed on the clutch member 4. The stopper 14 abuts on the actuating member 10 biased by biasing means (not shown), and restricts further movement to the right (opposite side) in FIG.

  As a result, the actuating member 10 is held in a position in contact with the stopper 14 at the time of non-operation, and moves against the biasing force of the biasing means when pressed and operated by the operating means T The pressure member 5 is in contact with the pressure member 5 so as to move in the same direction. Thus, while the separation dimension between the actuating member 10 and the operating means T is maintained when the actuating member 10 is not in operation, the actuating member 10 is allowed to operate in the actuating state.

  Here, when the weight member 8 is at the inner diameter side position, the power transmission device according to the present embodiment blocks the power transmission from the input gear 1 (input member) to the output shaft 3 (output member) and the output shaft A one-way clutch 11 is provided to transmit power from 3 (output member) to the input gear 1 (input member). The one-way clutch 11 is attached to the interlocking member 9, and includes an inner member 11a, a retainer member 11b, a roller 11c, and a spring 11d.

  As shown in FIGS. 7 and 8, the inner member 11a is an annular member having a surface 11ab on which a plurality of outer peripheral wall surfaces 11aa, a first fitting surface K1 and a second fitting surface K3 (see FIG. 9) are formed. A plurality of rollers 11c and springs 11d are attached between the outer peripheral wall surface 11aa and the inner peripheral wall surfaces of the interlocking member 9 and the retainer member 11b. That is, as shown in FIG. 10, the retainer member 11b is formed with a plurality of attachment portions 11ba, and the proximal end of the spring 11d to which the roller 11c is fixed at the tip is attached to the attachment portion 11ba When 11b is assembled to the inner member 11a and the interlocking member 9, as shown in FIGS. 12 and 13, the roller 11c is positioned between the outer peripheral wall surface 11aa of the inner member 11a and the inner peripheral surface of the interlocking member 9. There is.

  Further, as shown in FIG. 12, the outer wall surface 11aa of the inner member 11a is formed with a cam that fits with the roller 11c that rotates in one direction and does not fit with the roller 11c that rotates in the other direction. There is. Thereby, when the number of rotations of the clutch housing 2 is higher than the number of rotations of the output shaft 3 (that is, at the time of power transmission from the input gear 1 toward the output shaft 3), the inner member 11a and the interlocking member 9 are relative in the other direction. Although rotation is attempted, the roller 11 c is not fitted to the cam, and the one-way clutch 11 idles to prevent power transmission. 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, at the time of power transmission from the output shaft 3 toward the input gear 1), the inner member 11a and the interlocking member 9 try to relatively rotate in one direction. Because of this, the roller 11c is engaged with the cam, and power transmission is performed by the one-way clutch 11.

  As shown in FIGS. 4 and 5, the dog inner 12 is a cylindrical member having a through hole 12a and a flange 12b formed therein, and the inner peripheral wall surface of the through hole 12a is a base end portion of the clutch member 4 A spline is formed which can be spline-fitted in the rotational direction with respect to 4d. That is, the dog inner 12 rotates with the clutch member 4 and is slidable in the axial direction with respect to the clutch member 4. A disc spring 17 is disposed at a position adjacent to the flange 12b of the dog inner 12 (left side in FIG. 2), and when the dog inner 12 moves toward the disc spring 17, the biasing force of the disc spring 17 is applied. Is configured to be given.

  Further, the dog inner 12 and the inner member 11 a constitute a dog clutch (cut-off means) which can cut off power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11. Specifically, in a state in which the inner member 11a constituting the one-way clutch 11 and the dog inner 12 are assembled to the flange portion 12b of the dog inner 12, the first fitting surface is formed on the surface 12 ba facing the surface 11 ab of the inner member 11 a. A plurality of K2 and second fitting surfaces K4 are formed, and on the surface 11ab of the inner member 11a, as shown in FIG. 9, each of the first fitting surface K2 and the second fitting surface K4 in the dogner 12 A plurality of first fitting surfaces K1 and second fitting surfaces K3 which can be fitted to each other are formed.

  The first fitting surface (K1, K2) can transmit the power from the input gear 1 to the output shaft 3 by fitting as shown in FIG. 17 (a), and the second fitting surface (K3, K2) K4) is supposed to be able to transmit the power from the output shaft 3 to the input gear 1 by fitting as shown in FIG. 17 (b). Thus, the dog inner 12 and the inner member 11 a are in proximity (that is, as shown in FIG. 13A, the surface 12 ba of the dog inner 12 and the surface 11 ab of the inner member 11 a abut each other) Power transmission is performed by fitting K1 and K2) or the second fitting surface (K3 and K4), and the dog inner 12 and the inner member 11a are separated (that is, as shown in FIG. 13B), Power transmission is achieved by disengaging the first fitting surface (K1, K2) or the second fitting surface (K3, K4) by separating the surface 12ba of the dog inner 12 and the surface 11ab of the inner member 11a). It is configured to be shut off.

  Furthermore, as shown in FIGS. 6 and 9, the second fitting surface (K3, K4) according to the present embodiment is a tapered surface inclined at a predetermined angle α with respect to the fitting direction, and a load of a predetermined amount or more It is configured to be able to release the fit when the (excessive moment load) is applied. That is, when transmitting power from the output shaft 3 to the input gear 1, as shown in FIG. 17B, the second fitting surfaces (K3, K4) formed in a tapered shape abut and fit Therefore, when a predetermined load or more (excessive moment load) is applied in the power transmission direction, the second fitting surfaces (K3, K4) slide relative to each other, and move in the direction in which the fitting is released. It is

  Furthermore, a release pin 18 intervenes between the dog inner 12 and the operating member 10, and when the operating member 10 is operated by the operating means T, the dog inner 12 is inserted into the plate via the release pin 18 It can be moved against the biasing force of the spring 17, and by the movement, the surface 12ba of the dog inner 12 is separated from the surface 11ab of the inner member 11a, and the first fitting surface (K1, K2) or the second The fitting of the fitting surfaces (K3, K4) is released. Thus, power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 can be cut off by the operation of the actuating member 10. When the operating member 10 is returned to the initial position, the dog inner 12 returns to the original position by the biasing force of the disc spring 17, and the first fitting surface (K1, K2) or the second fitting surface (K3, K4) The fitting of the is to be done again.

  On the other hand, when the clutch housing 2 reaches a predetermined number of rotations and the weight member 8 moves from the inner diameter position toward the outer diameter position, as shown in FIG. 18, the inner member 11a attached to the interlocking member 9 Since they are separated with respect to 12, the fitting of the first fitting surface (K1, K2) or the second fitting surface (K3, K4) is released. As a result, when the weight member 8 moves from the inner diameter position toward the outer diameter position, power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 can be cut off.

Next, the operation of the power transmission device according to the present embodiment will be described based on the timing chart of FIG.
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 number of revolutions of the input gear 1 is low, so as shown in FIG. As well as being in the side position, the pressure member 5 is in the inoperative position. At this time, as shown in (A) and (B) in FIG. 25, the clutch is off (a state in which the pressure contact between the drive clutch plate 6 and the driven clutch plate 7 is released), the one way clutch 11 is off (power is The dog clutch is on (a state where power can be transmitted), the pressure contact assist cam is off, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are off.

  As shown in FIG. 18, the weight member 8 is on the inner diameter side, as the rotational speed of the input gear 1 shifts from low rotation to high rotation (middle rotation range) when the vehicle starts after stopping or idling the vehicle. The pressure member 5 is located between the inoperative position and the operative position, as well as between the position and the outer diameter side position. At this time, as shown in (C) and (D) in FIG. 25, the clutch is on (a state in which the pressure contact between the drive clutch plate 6 and the driven clutch plate 7 is started), the one way clutch 11 is off (power is The dog clutch is off (the power is not transmitted), the pressure-contact assist cam is on, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are off.

  After the vehicle starts moving, when the vehicle accelerates and travels at high speed, the rotational speed of the input gear 1 is high. Therefore, as shown in FIG. The member 5 is in the operating position. At this time, as shown in (E) and (F) in FIG. 25, the clutch is on (a state in which the pressure contact between the drive side clutch plate 6 and the driven side clutch plate 7 is performed), the one way clutch 11 is off (power is The dog clutch is off (the power is not transmitted), the pressure-contact assist cam is on, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are off.

  Also, after the vehicle starts moving, when the vehicle accelerates and decelerates in the high speed range, the number of rotations of the input gear 1 is lower than the number of rotations of the output shaft 3, so as shown in FIG. As well as being in position, the pressure member 5 is in operating position. At this time, as shown in (G) in FIG. 25, the clutch is on (a state in which the driving side clutch plate 6 and the driven side clutch plate 7 are in pressure contact) and the one way clutch 11 is off (a power is not transmitted) The dog clutch is off (the power is not transmitted), the pressure contact assist cam is off, the back torque limiter cam is on, and the actuating member 10 and the release pin 18 are off.

  When the vehicle shifts at a high speed, as shown in FIG. 20, the actuating member 10 is actuated. The weight member 8 is held at the outer diameter side position, and the pressure member 5 is in the non-operating position. At this time, as shown in (H) in FIG. 25, the clutch is off (the pressure contact between the drive side clutch plate 6 and the driven side clutch plate 7 is released), the one way clutch 11 is off (power is not transmitted) , The dog clutch is off (the power is not transmitted), the pressure contact assist cam is off, the back torque limiter cam is on, and the actuating member 10 and the release pin 18 are on.

  When the vehicle travels at a low speed, as shown in FIG. 21, the weight member 8 is positioned between the inner diameter position and the outer diameter position, and the pressure member 5 is positioned between the non-operating position and the operating position. It is done. At this time, as shown by (I) in FIG. 25, the clutch is on (a state in which the drive side clutch plate 6 and the driven side clutch plate 7 are in pressure contact) and the one way clutch 11 is off (a power is not transmitted) The dog clutch is off (the power is not transmitted), the pressure-contact assist cam is on, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are off.

  When the vehicle decelerates in the low speed range, the number of rotations of the input gear 1 is lower than the number of rotations of the output shaft 3. Therefore, as shown in FIG. It is in the inoperative position. At this time, as shown in (J) in FIG. 25, the clutch is off (the state in which the pressure contact between the drive side clutch plate 6 and the driven side clutch plate 7 is released) and the one way clutch 11 is on (power can be transmitted). State), the dog clutch is on (a state in which power can be transmitted), the pressure contact assist cam is off, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are off.

  When the vehicle shifts at a low speed, the actuating member 10 is actuated as shown in FIG. The weight member 8 is at the inner diameter side position, and the pressure member 5 is at the non-operating position. At this time, as shown by (K) in FIG. 25, the clutch is off (the pressure contact between the drive side clutch plate 6 and the driven side clutch plate 7 is released) and the one way clutch 11 is off (power is not transmitted) The dog clutch is off (the power is not transmitted), the pressure-contact assist cam is off, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are on.

  Furthermore, when the vehicle travels downhill or starts the engine E by a kick starter, as shown in FIG. 24, the weight member 8 is at the inner diameter position and the pressure member 5 is at the non-operating position. . At this time, as shown by (L) and (M) in FIG. 25, the clutch is off (the pressure contact between the drive clutch plate 6 and the driven clutch plate 7 is released), the one way clutch 11 is on (power is The dog clutch is on (a state in which power can be transmitted), the pressure contact assist cam is off, the back torque limiter cam is off, and the actuating member 10 and the release pin 18 are off.

  According to the above 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 to the input gear 1. Since the one-way clutch 11 for transmitting power toward the head 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 and kicking The engine can be started by the starter.

  Furthermore, while the vehicle is traveling, 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 position. It is performed by the driven clutch plate 7 and is performed by the one-way clutch 11 when the weight member 8 is at the inner diameter side position. Therefore, the power transmission path from the output shaft 3 to the input gear 1 can be made different according to 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 when the weight member 8 is at the inner diameter side position, power transmission from the output shaft 3 toward the input gear 1 is performed via the interlocking member 9. Thus, the function of moving the pressure member 5 from the inoperative position to the operative position and the function of transmitting power from the output shaft 3 to the input gear 1 can be combined for the interlocking member 9.

  Furthermore, since the shutoff means capable of interrupting the power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 is provided, the power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 is interrupted at necessary timing. be able to. Furthermore, the operating member 10 is provided which can be operated by a manual operation or an actuator and can move the pressure member 5 from the operating position to the non-operating position, and the blocking means is an output shaft 3 by the one-way clutch 11 by the operation of the operating member. Since it is possible to interrupt the transmission of power from the input gear 1 to the input gear 1, the transmission of power from the output shaft 3 to the input gear 1 by the one-way clutch 11 can be interrupted at any timing.

  In particular, in the present embodiment, since the shutoff means is a dog clutch, power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11 and the shutoff of the power transmission can be reliably performed. In addition, the dog clutch according to the present embodiment can transmit the power from the output shaft 3 to the input gear 1 and the first fitting surface (K1, K2) that can transmit the power from the input gear 1 to the output shaft 3 The second fitting surface (K3, K4) has a second fitting surface (K3, K4), and the second fitting surface (K3, K4) is a tapered surface which can release the fitting when a predetermined load or more is applied. When transmitting the power from the shaft 3 to the input gear 1, it is possible to suppress an excessive load from being applied to the dog clutch and damaging or deforming.

  Furthermore, in the present embodiment, the sloped surface 4a formed on the clutch member 4 and the sloped surface 5a formed on the pressure member 5 are configured to face each other, and the rotational force input to the input gear 1 is output shaft 3 A pressure-contact assist cam for increasing the pressure-contact force between the drive-side clutch plate 6 and the driven-side clutch plate 7 when it can be transferred to the In addition to the force, the pressing force by the pressing assist cam can be applied, and the driving clutch plate 6 and the driven clutch plate 7 can be pressure-contacted more smoothly and surely.

  Furthermore, according to the present embodiment, the sloped surface 4b formed on the clutch member 4 and the sloped surface 5b formed on the pressure member 5 are configured to face each other, and the rotation of the output shaft 3 is the rotation of the input gear 1 As the clutch member 4 and the pressure member 5 are rotated relative to each other by more than the number, the cam for the back torque limiter which can release 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 side position, it can be avoided that an excessive power is transmitted to the engine E side via the input gear 1.

  The present embodiment has been described above, but the present invention is not limited thereto. For example, when the weight member 8 is at the inner diameter side position, the one-way clutch 11 transmits power from the input gear 1 to the output shaft 3 As long as it is capable of transmitting power from the output shaft 3 to the input gear 1 as well as other types of one-way clutches. Similarly, the interrupting means may be any means capable of interrupting the power transmission from the output shaft 3 to the input gear 1 by the one-way clutch 11, and may be another form of interrupting means (frictional clutch etc.) .

  Also, the one-way clutch 11 or the disconnecting means (dog clutch) may be disposed at another position, or the pressure contact assisting cam or the back torque limiter cam may not be disposed. The power transmission device of the present invention can be applied to various multi-plate clutch power transmission devices such as automobiles, three- or four-wheel buggies, and general-purpose machines as well as two-wheeled vehicles.

  Furthermore, as another embodiment of the present invention, as shown in FIGS. 26 to 30, it is provided with a dog clutch configured with a dog inner 12 '(see FIG. 26) and an inner member 11'a (see FIG. 27). It is also good. The dog inner 12 'corresponds to the dog inner 12 of the above embodiment, and has a through hole 12'a in which a spline capable of spline fitting in the rotational direction to the proximal end 4d of the clutch member 4 is formed There is. The inner member 11'a corresponds to the inner member 11a of the above embodiment, and is formed with a cam that fits with the roller 11c that rotates relatively in one direction and does not fit with the roller 11c that rotates relative to the other direction. It has an outer peripheral wall surface 11'aa.

  A first fitting surface (K1, K2) and a second fitting surface (K3, K4) are respectively formed on the inner member 11'a and the dogner 12 ', and among these, the first fitting surface (K1) , K2) can transmit power from the input gear 1 to the output shaft 3 by fitting as shown in FIGS. The second fitting surfaces (K3, K4) are separated in a state where the inner member 11'a and the dog inner 12 'are assembled, and a clearance of a predetermined size is formed.

  Here, the first fitting surfaces (K1, K2) according to the present embodiment are inclined surfaces that act in the meshing direction when a load is applied in the axial direction (γ direction in FIG. 30). That is, as shown in FIG. 29, the first fitting surface K1 of the inner member 11'a is inclined by β to the negative side (the opposite side to the case of the cam and the acute angle side) to the axial direction γ Similarly, the first mating surface K2 of the dog inner 12 'is also inclined at an angle β to the negative side (the opposite side to the case of the cam and the acute angle side) with respect to the axial direction γ. (When the load is applied in the axial direction γ (the direction in which the first fitting surfaces K1 and K2 separate) in the fitted state, it acts in the mutually meshing direction (opposite to the case of the cam) ) Is supposed to.

  According to the dog clutch according to such another embodiment, the first fitting surface (K1, K2) capable of transmitting power from the input member (input gear 1) to the output member (output shaft 3), and the output member (2) A second fitting surface (K3, K4) capable of transmitting power from the (output shaft 3) to the input member (input gear 1), and the first fitting surface (K1, K2) has an axial direction Because the sloped surface acts in the meshing direction when a load is applied to γ, the first fitting surface (K1, K2) is inadvertently separated in the axial direction γ and the power transmission is interrupted. Can be prevented. The second fitting surface (K3, K4) may have a slope shape or the like for guiding the dog inner 12 'to the inner member 11'a.

  One-way clutch which is attached to the interlocking member and blocks power transmission from the input member to the output member when the weight member is at the inner diameter side position and performs power transmission from the output member to the input member via the interlocking member The present invention can also be applied to a power transmission device equipped with a device having a different external shape or to which another function is added.

1 Input gear (input member)
2 Clutch housing 3 Output shaft (output member)
4 clutch member 5 pressure member 6 drive side clutch plate 7 driven side clutch plate 8 weight member 9 interlocking member 10 actuation member 11 one-way clutch 12 dog inner (covering means: dog clutch)
13 Elastic member 14 Stopper 15 Washer 16 Retaining ring 17 Disc spring 18 Release pin E Engine D Wheel

Claims (8)

A clutch housing that rotates with an input member that is rotated by a driving force of a vehicle engine and in which a plurality of drive side clutch plates are formed;
A plurality of driven clutch plates alternately formed with the drive clutch plates of the clutch housing;
A clutch member coupled to an output member capable of rotating a vehicle wheel;
The operating position at which the driving force of the engine can be transmitted to the wheels by pressing the driving side clutch plate and the driven side clutch plate into pressure contact, and the pressing force between the driving side clutch plate and the driven side clutch plate is released A pressure member movable between an inoperative position, which can block the transmission of the driving force of the engine to the wheel;
A weight member disposed in a groove portion extending in the radial direction of the clutch housing, and movable from an inner diameter side position of the groove portion to an outer diameter side position by centrifugal force accompanying rotation of the clutch housing;
An interlocking member capable of moving the pressure member from the non-operating position to the operating position as the weight member moves from the inner diameter position to the outer diameter position;
Power transmission device having
When the weight member is attached to the interlocking member and the weight member is at the inner diameter side, power transmission from the input member to the output member is blocked and power transmission from the output member to the input member is performed via the interlocking member A power transmission device comprising a one-way clutch.   2. The power transmission apparatus according to claim 1, further comprising: shutoff means capable of shutting off power transmission from the output member toward the input member by the one-way clutch.   The actuating member is operated by a manual operation or an actuator and can move the pressure member from the actuating position to the inoperative position, and the blocking means is operated from the output member by the one-way clutch by the actuating member. The power transmission device according to claim 2, characterized in that power transmission toward the input member can be shut off.   The power transmission apparatus according to claim 2 or 3, wherein the blocking means comprises a dog clutch.   The dog clutch has a first fitting surface capable of transmitting power from the input member toward the output member, and a second fitting surface capable of transmitting power from the output member toward the input member. The power transmission apparatus according to claim 4, wherein the fitting surface is a tapered surface capable of releasing the fitting when a predetermined load or more is applied.   The dog clutch has a first fitting surface capable of transmitting power from the input member to the output member, and a second fitting surface capable of transmitting power from the output member to the input member. The power transmission device according to claim 4, wherein the fitting surface is a sloped surface acting in a meshing direction when a load is applied in the axial direction.   When the inclined surface formed on the clutch member and the inclined surface formed on the pressure member are opposed to each other, and 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 pressure contact assist cam for increasing a pressure 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 so that the clutch member and the pressure member are relative to each other. The cam for the back torque limiter which can release the press-contacting force of the said drive side clutch plate and the driven side clutch plate when it rotated normally was provided. Power transmission.

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