JP6224977B2 - Power transmission device - Google Patents

Description

  The present invention relates to a power transmission device mainly used for a transmission of a vehicle.

  Conventionally, for example, as disclosed in Patent Document 1, vehicles using a dog clutch type transmission have been widely used. In such a dog clutch type transmission, a plurality of dogs are formed on the gear, and a plurality of dogs (engagement bars) are formed on the selector mechanism. Then, the selector mechanism is moved by the shift fork, and a shift is made by switching to a power transmission state in which the dogs are brought close to each other and meshed with each other, or in a disconnected state in which the dogs are separated to release the meshing.

  In the transmission described in Patent Document 1, when switching from the disconnected state to the power transmission state, the dog of the selector mechanism is brought close to the gear dog while the differential rotation is generated between the dogs. At this time, depending on the position of the dogs in the rotation direction, the dog of the selector mechanism may not be sufficiently moved to the dog side of the gear and the dog may be in a shallow meshing state.

  Therefore, in the transmission described in Patent Document 1, a guard arm is provided in the selector mechanism. The guard arm shields part of the plurality of dogs of the selector mechanism, and when the gear dog enters between the plurality of dogs of the selector mechanism, the dog is flipped by the guard arm. The shift fork that moves the selector mechanism is moved by an electric actuator and is urged in the moving direction by a push spring or the like, and the urging force is accumulated while the dog continues to be flipped by the guard arm. . When an urging force exceeding a predetermined value is accumulated, the dog of the gear pushes off the guard arm by the urging force of the spring and enters between the dogs of the selector mechanism, and the dogs mesh with each other.

Special table 2007-504413 gazette

  As described above, in a power transmission mechanism such as a dog clutch type transmission, in the meshing of a rotating body such as a gear and a selector mechanism, depending on the differential rotation of both rotating bodies and the timing at which both rotating bodies are brought close to each other, , It will be in a shallow meshing state. Therefore, the contact area between the dogs is reduced and the surface pressure is increased, so that the strength required for the dogs is increased in order to ensure sufficient safety.

  In addition, as described in Patent Document 1 described above, if a guard arm is provided, it is possible to avoid a situation in which dog engagement becomes shallow. However, since the dog and the guard arm repeatedly collide until the urging force of the spring is sufficiently accumulated, wear and noise increase.

  Accordingly, an object of the present invention is to provide a power transmission device capable of appropriately performing dog meshing while suppressing generation of wear and noise.

In order to solve the above-described problems, a power transmission device according to the present invention includes a first rotating body in which a plurality of first dogs are arranged in a rotation direction, and a plurality of second dogs that can mesh with the first dog in the rotation direction. And when the first rotating body and the second rotating body move relative to each other in the proximity direction, the first dog and the second dog mesh with each other and the second rotating body and the second rotating body are arranged. When the first rotator and the second rotator move relative to each other in a separating direction in which the first rotator and the second rotator move away from each other, the meshing between the first dog and the second dog is released and the first rotator and A power transmission device that is in a disconnected state in which the second rotating body rotates relative to the first rotating body, the regulating unit that rotates integrally with the first rotating body , the integral rotating with the second rotating body, and protruding toward the first rotating body, Cut at least part of the circular outer peripheral surface at the tip in the protruding direction Is out portion is formed, the projecting forward end face, with the disconnected state is positioned on the second rotation side than restricting portion abutting surface located on the first rotation side than the regulating portion in a power transmission state is formed A stopper member provided with a protrusion , and in a process in which the first rotating body and the second rotating body move relative to each other in the proximity direction from the separated state, around the rotation axis of the second rotating body with respect to the first rotating body. When the position is within the restriction range, the contact surface and the restriction portion are in surface contact with each other in the rotation axis direction, the relative movement in the proximity direction is restricted, and the contact surface and the restriction portion are in contact with each other. When the first rotating body and the second rotating body rotate relative to each other and the position around the rotation axis of the second rotating body with respect to the first rotating body is out of the regulation range , the notched portion faces the regulating portion, thereby contacting the The contact between the surface and the restricting portion is released, and the first rotating body and the second rotating body are The first dog and a second dog, characterized in that the meshing relative movement in the approaching direction to al.

  The contact surface may have a length in the rotation direction of the second rotating body.

  The first rotary body is provided with a swingable main body, a cam having a restricting portion at a part of the main body, and the cam has a protruding posture in which the restricting portion protrudes within the rotation locus range of the contact surface; Power that the first dog and the second dog mesh with each other is changed from the rotation trajectory range to the retracted posture in which the restricting portion retracts, and while the contact surface is closer to the second rotating body than the restricting portion. In the transmission state, if the position around the rotation axis of the second rotator with respect to the first rotator is outside the regulation range, the cam is held in the projecting posture, the regulation part enters the notch in the projection, If the position around the rotation axis of the second rotating body with respect to the one rotating body is within the regulation range, the cam may be in contact with the outer peripheral surface of the protruding portion and held in the retracted posture.

  When the contact surface is closer to the first rotating body than the restricting portion, and the position of the second rotating body around the rotation axis with respect to the first rotating body shifts from outside the restricting range to within the restricting range, the abutting portion of the protruding portion The end surface located at the boundary between the surface and the notch may contact the cam, and the cam may be changed from the protruding posture to the retracted posture.

  A plurality of cams may be provided in the rotation direction of the first rotating body.

  The plurality of cams may be provided by shifting the respective restricting portions in the direction of the rotation axis of the first rotating body.

  A stopper member comprising: a hub fixed to the rotation shaft; and a second rotation body, a sleeve that rotates integrally with the hub and is movably assembled in the rotation shaft direction, and has a second dog formed thereon. May be assembled to the hub so as to rotate integrally with the hub and move together with the sleeve in a direction at least close to the first rotating body.

  According to the present invention, dog engagement can be appropriately performed while suppressing the generation of wear and noise.

It is a figure which shows the outline of the transmission for motor vehicles. It is a perspective view of a power transmission device. It is a perspective view which shows the side surface of a power transmission device. It is explanatory drawing for demonstrating mesh | engagement of the 1st dog and the 2nd dog of this embodiment. It is explanatory drawing for demonstrating mesh | engagement of the 1st dog of a comparative example, and a 2nd dog. It is a disassembled perspective view of a power transmission device. It is a 1st figure for demonstrating the integration of the cam to a dog gear. It is a 2nd figure for demonstrating incorporation of the cam to a dog gear. It is a perspective view of a stopper member. It is a perspective view of a hub, a drive side sleeve, a coast side sleeve, and a stopper member. It is a 1st figure for demonstrating mesh | engagement of the dog of a power transmission device. It is a 2nd figure for demonstrating mesh | engagement of the dog of a power transmission device. It is a 3rd figure for demonstrating mesh | engagement of the dog of a power transmission device. It is a 4th figure for demonstrating mesh | engagement of the dog of a power transmission device. It is a figure for demonstrating the contact of a stopper member and a cam.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiments are merely examples for facilitating understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and drawings, elements having substantially the same function and configuration are denoted by the same reference numerals, and redundant description is omitted, and elements not directly related to the present invention are not illustrated. To do.

(Outline of transmission)
FIG. 1 is a diagram showing an outline of a transmission 1 for an automobile. The transmission 1 that transmits the driving force of the engine E to driving wheels includes a main shaft 2 and a counter shaft 3 that are rotatably supported by bearings b held in a transmission case and arranged in parallel to each other. The main shaft 2 is connected to the crankshaft of the engine E through the starting clutch 4 and functions as an input shaft that rotates by the driving force of the engine E transmitted through the starting clutch 4.

  A plurality of (four in this embodiment) main gears 10 are mounted on the main shaft 2 so as to be relatively rotatable. The number of main gears 10 provided on the main shaft 2 is not particularly limited, but here, for convenience of explanation, the four main gears 10 are respectively connected to the first speed main gear 11, the second speed main gear 12, and the third speed main gear 13. This will be described as the 4-speed main gear 14. A plurality (four in this embodiment) of counter gears 20 are mounted on the counter shaft 3 so as not to be relatively rotatable. Here, for convenience of explanation, the four counter gears 20 will be described as a first speed counter gear 21, a second speed counter gear 22, a third speed counter gear 23, and a fourth speed counter gear 24, respectively.

  The first speed counter gear 21 meshes with the first speed main gear 11, and the first speed main gear 11 and the first speed counter gear 21 constitute a first gear train 31 that transmits power between the main shaft 2 and the counter shaft 3. doing. Similarly, the second gear train 32 is constituted by the second gear main gear 12 and the second gear counter gear 22, and the third gear train 33 is constituted by the third gear main gear 13 and the third gear counter gear 23, and the fourth gear main gear 14 and the fourth gear. The counter gear 24 constitutes a fourth gear train 34.

  The first gear train 31 to the fourth gear train 34 have different gear ratios of the main gears 11 to 14 and the counter gears 21 to 24. In the present embodiment, the first gear train 31 is the lowest speed side. Thus, the fourth gear train 34 is on the highest speed side.

  The main shaft 2 is provided with a plurality (two in this embodiment) of power transmission devices 50 (50a, 50b) for switching the power transmission path. The power transmission device 50 has a power transmission state in which any one of the first speed main gear 11 to the fourth speed main gear 14 is integrally rotated with respect to the main shaft 2 or the first speed main gear 11 to the fourth speed main gear 14 with respect to the main shaft 2. Either of the separated state (neutral state) for relative rotation can be selected.

  The power transmission device 50 a is disposed between the first speed main gear 11 and the second speed main gear 12, and the power transmission device 50 b is disposed between the third speed main gear 13 and the fourth speed main gear 14.

  The power transmission device 50 includes a drive-side sleeve 51 and a coast-side sleeve 52 that are movable in the axial direction of the main shaft 2 (hereinafter simply referred to as the axial direction). The drive-side sleeve 51 and the coast-side sleeve 52 have second dogs 51 a and 52 a that protrude from both ends in the axial direction, respectively, and rotate integrally with the main shaft 2.

  Further, the power transmission device 50 includes a dog gear 53 that is connected to each of the first-speed main gear 11 to the fourth-speed main gear 14 and rotates integrally therewith. The dog gear 53 is provided with a first dog 53a that protrudes toward the second dogs 51a and 52a.

  A shift fork 5 is engaged with the drive side sleeve 51 and the coast side sleeve 52, and the shift fork 5 is movable in the axial direction by the electric actuator 6. A coil spring 7 is interposed between the shift fork 5 and the electric actuator 6, and the pressing force in the movable direction of the shift fork 5 is accumulated by the coil spring 7. The action of the coil spring 7 will be described in detail later. Then, the second dogs 51a and 52a and the first dog 53a are engaged with each other or the engagement is released by the movement of the shift fork 5.

  For example, when the first gear train 31 is selected as the power transmission path, the power transmission device 50a is connected to the first dog 53a of the dog gear 53 connected to the first-speed main gear 11 and one of the second dogs 51a and 52a. Mesh. Then, the first-speed main gear 11 is integrally rotated with respect to the main shaft 2. At this time, the power transmission device 50a separates the second gear train 32. In addition, the power transmission device 50b separates the third gear train 33 and the fourth gear train 34. Therefore, in this case, the driving force of the engine E is transmitted to the driving wheels in the order of the arrow through the starting clutch 4 → the main shaft 2 → the first gear train 31 → the counter shaft 3, and the main shaft 2 and the counter shaft 3 Power is transmitted through the first gear train 31 between them.

  In the present embodiment, the main gear 10 is provided so as to be rotatable relative to the main shaft 2, and the counter gear 20 is provided so as not to be rotatable relative to the counter shaft 3. A power transmission device 50 is provided on the main shaft 2. However, on the contrary, the main gear 10 is provided so as not to rotate relative to the main shaft 2, the counter gear 20 is provided relative to the counter shaft 3, and the power transmission device 50 is connected to the counter shaft 3. May be provided.

(Configuration of power transmission device 50)
Next, the configuration of the power transmission device 50 will be described in detail. As described above, the power transmission device 50 is disposed between the two main gears 10, and any one of the main gears 10 disposed on both sides can be in a power transmission state with respect to the main shaft 2. The power transmission device 50 has two mechanisms that are substantially equivalent as mechanisms for bringing the two main gears 10 disposed on both sides into a power transmission state. In the following description, only the mechanism for setting one main gear 10 to a power transmission state with respect to the main shaft 2 in the power transmission device 50 will be illustrated and described, and the other main gear 10 will be in a power transmission state with respect to the main shaft 2. The description of the mechanism to avoid the duplicate description is omitted.

  FIG. 2 is a perspective view of the power transmission device 50. As shown in FIG. 2, the power transmission device 50 includes a substantially cylindrical hub 54 that is fixed to the main shaft 2 and rotates integrally with the main shaft 2. A plurality of grooves 54 a extending in the axial direction are formed on the outer peripheral surface of the hub 54 at equal intervals in the circumferential direction of the main shaft 2 (hereinafter simply referred to as the circumferential direction).

  The dog gear 53 (first rotating body) has a through hole 53b penetrating in the axial direction. The dog gear 53 is disposed so as to face the hub 54 in the axial direction with the main shaft 2 inserted through the through hole 53 b. A plurality (three in this case) of first dogs 53 a protruding toward the hub 54 are arranged at equal intervals in the circumferential direction (rotational direction) on the outer peripheral side of the dog gear 53.

  The drive side sleeve 51 (second rotating body) and the coast side sleeve 52 (second rotating body) have annular ring portions 51b and 52b, and the hub 54 is inserted through the centers of the ring portions 51b and 52b. Here, the coast side sleeve 52 is disposed closer to the dog gear 53 than the drive side sleeve 51.

  The drive side sleeve 51 and the coast side sleeve 52 have key portions 51c and 52c, respectively. The key portions 51 c and 52 c protrude from the ring portions 51 b and 52 b inward in the radial direction of the ring portions 51 b and 52 b and extend in the axial direction toward the dog gear 53. A plurality of key portions 51c, 52c are arranged at equal intervals in the circumferential direction (rotation direction), and second dogs 51a, 52a meshing with the first dog 53a are formed at the tips of the key portions 51c, 52c, respectively. ing.

  Here, since the coast side sleeve 52 is disposed closer to the dog gear 53 than the drive side sleeve 51, the key portion 52c is shorter in the axial direction than the key portion 51c.

  The key portions 51c and 52c are respectively fitted in the grooves 54a of the hub 54, and the drive side sleeve 51 and the coast side sleeve 52 are configured such that the key portions 51c and 52c slide in the grooves 54a of the hub 54. Move in the axial direction.

  Further, since the key portions 51 c and 52 c are fitted in the grooves 54 a of the hub 54, the drive-side sleeve 51 and the coast-side sleeve 52 are restricted from rotating relative to the hub 54 and integrated with the main shaft 2 and the hub 54. It will rotate.

  FIG. 3 is a perspective view showing a side surface of the power transmission device 50. FIG. 3A shows a state where the second dogs 51a and 52a of the drive side sleeve 51 and the coast side sleeve 52 and the first dog 53a of the dog gear 53 are not meshed with each other. FIG. 3B shows a state in which the second dogs 51 a and 52 a of the drive side sleeve 51 and the coast side sleeve 52 are engaged with the first dog 53 a of the dog gear 53.

  In the state shown in FIG. 3A, the drive side sleeve 51 and the coast side sleeve 52 rotate together with the main shaft 2 together with the hub 54. On the other hand, the dog gear 53 is rotatable relative to the main shaft 2.

  Then, the shift fork 5 described above moves the drive side sleeve 51 and the coast side sleeve 52 to the dog gear 53 side. Then, as shown in FIG. 3B, the second dogs 51 a and 52 a of the drive side sleeve 51 and the coast side sleeve 52 enter the circumferential gaps of the plurality of first dogs 53 a provided on the dog gear 53.

  In this way, when the dog gear 53 and the drive-side sleeve 51 are relatively moved in the proximity direction close to each other from FIG. 3A to FIG. 3B, the first dog 53a and the second dog 51a are engaged with each other. The first dog 53a and the second dogs 51a and 52a are in a power transmission state in which they rotate together.

  Further, when the dog gear 53 and the drive side sleeve 51 are relatively moved in the separating direction away from each other from FIG. 3B to FIG. 3A, the dog gear 53 and the drive side sleeve 51 are disengaged to release the first dog. 53a and the second dogs 51a and 52a are in a separated state in which they rotate relative to each other.

  FIG. 4 is an explanatory diagram for explaining the meshing of the first dog 53a and the second dogs 51a and 52a of the present embodiment. As shown in FIG. 4A, the first dog 53a includes a trailing surface 53af positioned on the front side in the rotational direction of the dog gear 53 (main gear 10), and a leading surface 53ar positioned on the rear side in the rotational direction. ing. The first dog 53a has a wide distal end shape in which the width of the dog gear 53 (main gear 10) in the rotation direction (vertical direction in FIG. 4A) is wider on the distal end side than on the proximal end side. .

  The second dog 51a includes a leading claw 51r that can engage with the leading surface 53ar of the first dog 53a at the end of the dog gear 53. The leading claw 51r is formed in a tapered shape so as to engage with the leading surface 53ar in a surface contact state.

  On the other hand, in the second dog 52a, the trailing claw 52f on the dog gear 53 side can be engaged with the trailing surface 53af of the first dog 53a. The trailing claw 52f is formed in a tapered shape so as to engage with the trailing surface 53af in a surface contact state.

  Then, as shown in FIG. 4B, the second dogs 51a and 52a move to the dog gear 53 side. For example, in the upshift when the vehicle is accelerated by the engine E, the second dog 51a of the drive side sleeve 51 and the second dog 52a of the coast side sleeve 52 are moved in this order.

  Then, the leading surface 53ar of the dog gear 53 and the leading claw 51r of the second dog 51a are engaged. As a result, the power is transmitted from the main shaft 2 to the counter shaft 3 (accelerated state). At this time, the dog gear 53 and the second dog 52a are maintained in a non-engaged state.

  Further, in the downshift at the time of deceleration of the vehicle due to the rotational moment on the engine E side (so-called engine braking), the second dog 52a of the coast side sleeve 52 and the second dog 51a of the drive side sleeve 51 move to the dog gear 53 side in this order. To do. Then, as shown in FIG. 4C, the trailing surface 53af of the dog gear 53 and the trailing claw 52f of the second dog 52a are engaged. As a result, a state (deceleration state) in which a force for suppressing the inertial force on the drive wheel side is transmitted from the main shaft 2 to the counter shaft 3 is obtained. At this time, the dog gear 53 and the second dog 51a are maintained in a disengaged state.

  In the present embodiment, “acceleration” means a state in which the vehicle is accelerated by the driving force of the engine E, and does not mean a state in which the vehicle is accelerated by its own weight when going down a hill, for example. “Deceleration” refers to a vehicle deceleration state caused by engine braking, and does not refer to a state where the vehicle decelerates when going up a hill, for example.

Figure 5 is an explanatory diagram for explaining a first dog D ₁ and second meshing dog D ₂ of the comparative example. Here, as shown in FIG. 5 (a), when the direction of the second dog D ₂ is rotating at a speed higher than the first dog D _1, the drive-side sleeve by a shift fork (not shown) to Dogugiya DG side Take the case of moving as an example.

FIG 5 (b) as shown in the, if reaching the second dog D ₂ until the main body of Dogugiya DG without colliding with the first dog D _1, similarly to the state shown in FIG. 4 (b), the second The dog D ₂ and the first dog D ₁ are appropriately meshed. However, the second dog D ₂ by the moving timing of the first differential rotation and shift forks of the dog D _1, as shown in FIG. 5 (c), the second dog D ₂ is first second dog dog D ₁ Colliding with the surface on the D ₂ side, the second dog D ₂ is bounced from the first dog D ₁ .

Similar to the shift fork 5 shown in FIG. 1, a coil spring is interposed between the shift fork of the comparative example and an electric actuator (not shown). When the second dog D ₂ is bounced, the displacement of the shift fork due to the bounce of the second dog D ₂ is absorbed by the expansion and contraction of the coil spring, and the second dog D ₂ is again moved by the repulsive force of the coil spring. It moves toward the main body of the dog gear DG. A second dog D ₂ to the first dog D ₁ is engaged, the collision is repeated.

A second dog D ₂ are repelled from the first dog D _1, while stagnating without being first dog D ₁ engaged, the electric actuator continues to displace the shift fork so as to movable, shift by the coil spring The pressing force in the moving direction of the fork is accumulated. The increased biasing force of the coil spring gradually, since the second dog D ₂ is the speed of moving in the first dog D ₁ side rises, the second dog D ₂ does not collide with the first dog D ₁ It becomes easy to reach the main body of the dog gear DG. Nevertheless, the second dog D ₂ by the moving timing of the first differential rotation and shift forks of the dog D _1, as shown in FIG. 5 (d), before the second dog D ₂ reaches the body of Dogugiya DG first and dog D ₁ and meshing, resulting in a shallow meshing state.

Thus, in the comparative example, when the second dog D ₂ and the first dog D ₁ mesh, the second dog D ₂ and the first dog D ₁ repeatedly collide to generate wear and noise, There has been a problem that the surface pressure acting on the meshing portion increases due to the shallow meshing state. Hereinafter, the structure of the power transmission device 50 of the present embodiment that solves such a problem will be described in detail.

  FIG. 6 is an exploded perspective view of the power transmission device 50. As shown in FIG. 6, the power transmission device 50 is provided with a guard mechanism 55 in addition to the drive side sleeve 51, the coast side sleeve 52, the dog gear 53, and the hub 54 described above.

  The guard mechanism 55 includes a cam 56, a return spring 57, a plate 58, a snap ring 59, and a stopper member 60. In the dog gear 53, an accommodation chamber 53c that is recessed in the axial direction is formed on the inner circumference side of the first dog 53a and on the outer circumference side of the through hole 53b, and the cam 56 and the return spring 57 are placed in the accommodation chamber 53c. It is housed and rotates integrally with the dog gear 53.

  After the cam 56 and the return spring 57 are attached, the plate 58 covers the storage chamber 53c, so that the cam 56 and the return spring 57 are prevented from falling off from the storage chamber 53c. A hole 58a penetrating in the axial direction is formed in the plate 58, and an annular protrusion of a stopper member 60 described later is inserted through the hole 58a.

  The snap ring 59 is formed with a notch 59a. When the snap ring 59 is pressed inward in the radial direction, the notch 59a is elastically deformed in the direction of reduction, and the outer diameter of the snap ring 59 is reduced. After the plate 58 is fitted into the storage chamber 53c, the snap ring 59 is provided on the inner peripheral surface of the storage chamber 53c while pressing the end surface 58b of the plate 58 and elastically deforming the snap ring 59 to reduce the outer diameter. Fit into the groove 53d.

  When the elastic deformation of the snap ring 59 is released and the snap ring 59 returns to the original outer diameter, the snap ring 59 is hardly detached from the groove 53d by the elastic force. Thus, the plate 58 is sealed inside the accommodation chamber 53c by the snap ring 59.

  The stopper member 60 has a plate-like main body 60 a, and the main body 60 a is located between the plate 58 and the hub 54. The outer diameter of the main body 60 a is smaller than the inner diameters of the ring portions 51 b and 52 b of the drive side sleeve 51 and the coast side sleeve 52. The stopper member 60 has a protrusion 61. A plurality of protrusions 61 are formed in the circumferential direction, and each protrudes radially outward from the main body 60a, and a part of the protrusions 61 protrude toward the hub 54 side.

  FIG. 7 is a first view for explaining the incorporation of the cam 56 into the dog gear 53. FIG. 7A shows a perspective view of the dog gear 53 incorporating the cam 56, and FIG. The side view which looked at the dog gear 53 incorporating the cam 56 from the radial direction outer side is shown. However, in FIGS. 7A and 7B, the plate 58 and the snap ring 59 are excluded, and in FIG. 7B, the dog gear 53 is indicated by a broken line.

  As shown in FIG. 7A, the cam 56 has an annular main body portion 56b in which a hole 56a penetrating in the axial direction is formed, and extends in a radial direction of the hole 56a in a part of the main body portion 56b. Have two arms 56c and 56d. Two cams 56 are provided in the accommodation chamber 53 c of the dog gear 53 in the circumferential direction (rotational direction) of the dog gear 53.

  Two holes pass through the bottom surface of the accommodation chamber 53c of the dog gear 53 in parallel to the axial direction, and a pin 56e is inserted into each hole. The pin 56e protrudes from the bottom surface of the storage chamber 53c, and the hole 56a of the cam 56 is fitted into this protruding portion. Therefore, the cam 56 is rotatable around the axis of the pin 56e.

  In addition, two rectangular holes 53e are formed on the bottom surface of the accommodation chamber 53c of the dog gear 53 at a position approximately 180 degrees apart in the circumferential direction of the dog gear 53, and a return spring 57 is fitted into the hole 53e. One end of the return spring 57 biases the plate 57 b, and the plate 57 b faces the tip of one arm 56 c of the cam 56.

  The tip of the other arm 56d (regulator) of the cam 56 is located on the radially inner side of the dog gear 53 with respect to the tip of the arm 56c. An annular cylindrical portion 53f is formed at the edge of the through hole 53b of the dog gear 53, and the tip of the arm 56d receives the urging force of the return spring 57 acting via the plate 57b, and the cylindrical portion of the dog gear 53 It is pressed against 53f. When the cam 56 rotates in the direction indicated by the arrow in FIG. 7A according to the operation of a stopper member 60 described later, the tip of the arm 56c presses the return spring 57 and contracts the return spring 57. The tip of the arm 56d swings toward the radially outer side of the dog gear 53.

  When the pressing of the stopper member 60 to the cam 56 is released, the cam 56 rotates in the direction opposite to the direction indicated by the arrow in FIG. Return to the initial position shown in (a).

The two cams 56 are arranged with their arms 56d shifted in the axial direction. Specifically, as shown in FIG. 7B as heights L ₁ and L ₂ , the two cams 56 have different heights protruding in the axial direction from the bottom surface of the accommodation chamber 53 c of the dog gear 53. Hereinafter, of the two cams 56, the cam 56 having a high axial direction is referred to as a first cam 56f, and the cam 56 having a low axial height is referred to as a second cam 56g.

  FIG. 8 is a second view for explaining the incorporation of the cam 56 into the dog gear 53, and shows the state where the cam 56 is incorporated into the dog gear 53 and sealed by the plate 58 and the snap ring 59. For ease of understanding, the plate 58 is indicated by hatching.

  As shown in FIG. 8, the tip of the arm 56 d of the cam 56 is located on the radially inner side of the dog gear 53 with respect to the inner diameter of the hole 58 a of the plate 58. That is, the tip of the arm 56 d of the cam 56 is exposed from the hole 58 a of the plate 58.

  FIG. 9 is a perspective view of the stopper member 60, FIG. 9A shows a perspective view of the stopper member 60 viewed from the hub 54 side, and FIG. 9B shows the stopper member 60 with the dog gear 53. The perspective view seen from the side is shown.

  As shown in FIG. 9A, the main body 60a of the stopper member 60 is formed with an insertion hole 60b penetrating in the axial direction and through which the main shaft 2 is inserted. The protrusions 61 are classified into three types having different lengths in the axial direction, and the first protrusion 61a, the second protrusion 61b, and the third protrusion 61c are arranged in descending order of the length in the axial direction. , Two each. The third protrusion 61c has an axial length equal to that of the main body 60a, that is, does not protrude in the axial direction, and the first protrusion 61a and the second protrusion 61b protrude in the axial direction, respectively. 54 is fitted into the groove 54a.

  Further, as shown in FIG. 6, the partition 54 b formed between the grooves 54 a adjacent to each other in the circumferential direction of the hub 54 has a shaft end portion 54 c that protrudes in the axial direction from the main body of the hub 54 on the dog gear 53 side. Yes. The third protrusion 61 c of the stopper member 60 is fitted in the gap between the shaft end portions 54 c adjacent to each other in the circumferential direction of the hub 54. The gap into which the third protrusion 61c is fitted is continuous with the groove 54a, and there is no problem even if it is substantially part of the groove 54a. Therefore, hereinafter, the gap between the shaft end portions 54c adjacent to each other in the circumferential direction of the hub 54 and the groove 54a are not distinguished from each other and are simply referred to as the groove 54a.

  As shown in FIG. 9B, the edge of the insertion hole 60 b in the main body 60 a of the stopper member 60 is an annular protrusion 60 c that protrudes in the axial direction toward the dog gear 53. The annular protrusion 60c has an outer diameter smaller than the inner diameter of the hole 58a of the plate 58 described above, and can be inserted into the hole 58a. In addition, the tip of the arm 56d of the cam 56 described above is located on the radially inner side of the dog gear 53 with respect to the outer diameter of the annular protrusion 60c when not pressed from the stopper member 60. That is, the annular protrusion 60c faces the tip of the arm 56d of the cam 56 in the axial direction.

  A part of the circular outer peripheral surface of the annular protrusion 60c is formed with a notch 60d at the tip in the protruding direction. Further, the contact surface 60f (indicated by hatching in FIG. 9B), which is the front end surface of the annular projection 60c in the projecting direction (on the dog gear 53 side), is approximately 290 degrees in the rotational direction of the dog gear 53. Have

  Then, in the annular protrusion 60c, the portion located at the boundary between the contact surface 60f of the annular protrusion 60c and the cutout portion 60d has a width r (in the radial direction) of the contact surface 60f toward the cutout portion 60d. A tapered portion 60e (end surface) in which the thickness is gradually reduced is formed.

  10 is a perspective view of the hub 54, the drive side sleeve 51, the coast side sleeve 52, and the stopper member 60. FIG. 10A shows the hub 54, the drive side sleeve 51, the coast side sleeve 52, and The stopper member 60 is shown in an exploded manner in the axial direction of the main shaft 2, and FIG. 10B is a perspective view showing a state in which the drive side sleeve 51, the coast side sleeve 52, and the stopper member 60 are assembled. Show. For ease of understanding, the hub 54 is not shown in FIG. Moreover, in FIG.10 (b), the stopper member 60 is shown by hatching.

  As described above, the protrusion 61 of the stopper member 60 is fitted in the groove 54 a of the hub 54. Further, the key portion 51 c of the drive side sleeve 51 and the key portion 52 c of the coast side sleeve 52 are also fitted in the groove 54 a of the hub 54. Therefore, the stopper member 60, the drive side sleeve 51, and the coast side sleeve 52 rotate integrally with the hub 54.

  The ring portion 51b of the drive-side sleeve 51 and the ring portion 52b of the coast-side sleeve 52 are formed with locking portions 51d and 52d that protrude radially inward. The locking portions 51d and 52d are arranged at positions where the axial thickness is equal to the ring portions 51b and 52b, and the circumferential positions of the ring portions 51b and 52b are different from the key portions 51c and 52c. , 52b are formed two by two apart from each other in the circumferential direction.

  The locking portions 51 d and 52 d are fitted in the groove 54 a of the hub 54. At this time, the locking part 51d is fitted in the same groove 54a as the second protrusion 61b. The locking portion 52d is fitted in the same groove 54a as the third protrusion 61c. That is, as shown in FIG. 10B, the locking part 51d is arranged to face the second protrusion 61b in the axial direction, and the locking part 52d is opposite to the third protrusion 61c in the axial direction. Arranged.

  When the drive side sleeve 51 moves in the axial direction toward the dog gear 53 side (lower left side in FIG. 10B), the second protrusion 61 b of the stopper member 60 is pressed against the locking part 51 d of the drive side sleeve 51. It is. Therefore, the stopper member 60 moves to the dog gear 53 side in conjunction with the drive side sleeve 51.

  Further, when the coast side sleeve 52 moves in the axial direction toward the dog gear 53 side, the third protrusion 61 c of the stopper member 60 is pushed by the locking portion 52 d of the coast side sleeve 52. Therefore, the stopper member 60 moves to the dog gear 53 side in conjunction with the coast side sleeve 52.

  Further, as shown in FIG. 10 (b), a protrusion 62 that protrudes further than the first protrusion 61a is formed at the tip of one of the two first protrusions 61a on the radially inner side of the ring part 51b. Has been. As shown in FIG. 10A, a recess 54 d into which the protrusion 62 is fitted is formed in one groove 54 a of the plurality of grooves 54 a of the hub 54. A return spring 63 shown in FIG. 10B is fitted into the recess 54 d on the dog gear 53 side from the protrusion 62.

  Therefore, as described above, when the stopper member 60 moves to the dog gear 53 side in conjunction with the drive side sleeve 51 and the coast side sleeve 52, the return spring 63 contracts. When the drive side sleeve 51 and the coast side sleeve 52 return to their original positions, the stopper member 60 also returns to its original position by the urging force of the return spring 63.

  As described above, the stopper member 60 is assembled to the hub 54 so as to move integrally with the drive side sleeve 51 and the coast side sleeve 52 in a direction close to and away from the dog gear 53.

  FIGS. 11-14 is a figure for demonstrating mesh | engagement of the dog of the power transmission device 50, and mesh | engagement of a dog progresses in order of FIG. 11, FIG. 12, FIG. 13, FIG. In each of FIGS. 11 to 14, (a) shows a side view of the power transmission device 50, and (b) shows an enlarged view excluding the hub 54, the plate 58, the snap ring 59, and the dog gear 53 from (a). Show. Further, (c) is a perspective view of the power transmission device 50 as viewed from the dog gear 53 side, with the dog gear 53 being excluded, and (d) is a front view of (c). In order to facilitate understanding, in (b), the first cam 56f and the second cam 56g are hatched.

  Here, when the vehicle is accelerated by the engine E, the drive-side sleeve 51 is moved toward the dog gear 53 by the shift fork 5, and the second dog 51 a of the drive-side sleeve 51 meshes with the first dog 53 a of the dog gear 53. The movement up to will be described as an example.

  As shown in FIG. 11A, the first dog 53a of the dog gear 53, the second dog 51a of the drive side sleeve 51, and the second dog 52a of the coast side sleeve 52 are separated in the axial direction. Is also not engaged (disengaged state).

  A differential rotation occurs between the dog gear 53 and the hub 54, and the cam 56 and the stopper member 60 shown in FIGS. 11B to 11D rotate relative to each other. That is, the contact surface 60f of the annular protrusion 60c rotates relative to the cam 56. Further, the annular protrusion 60 c (contact surface 60 f) rotates integrally with the drive side sleeve 51.

  Also, as shown in FIGS. 11C and 11D, the tip of each arm 56d of the cam 56 (the first cam 56f and the second cam 56g) is brought into contact with the contact surface 60f of the annular protrusion 60c of the stopper member 60. , Facing in the axial direction. That is, the arm 56d of the first cam 56f protrudes (protruding posture) within the rotation locus range of the contact surface 60f of the annular protrusion 60c.

  In the state of FIG. 11 (b), the contact surface 60f of the annular protrusion 60c is located farther from the arm 56d of the two cams 56 on the drive side sleeve 51 side. The arms 56d of the two cams 56 are held in a protruding posture.

  The stopper member 60 moves to the dog gear 53 side in conjunction with the drive-side sleeve 51, but the contact surface 60 f of the annular protrusion 60 c of the stopper member 60 is higher in the axial direction than the cam 56. When it comes into contact with the first cam 56f, it stops (see FIG. 12B).

  In the present embodiment, the contact surface 60f of the annular protrusion 60c or the area where the arm 56d of the cam 56 faces in the axial direction on the radially outer side of the contact surface 60f (indicated by hatching in FIG. 11D) is restricted. This is called a range. Here, since two cams 56 are provided, the restriction ranges are set for the first cam 56f and the second cam 56g, respectively.

  For example, in the stage before the first dog 53a and the second dogs 51a, 52a mesh with each other, the position around the rotation axis of the drive-side sleeve 51 with respect to the dog gear 53 (hereinafter simply referred to as a phase difference) is within the regulation range. The contact surface 60f of the annular protrusion 60c and the arm 56d of the first cam 56f come into contact with each other, and the relative movement in the proximity direction is restricted.

  Since a differential rotation occurs between the dog gear 53 and the hub 54, the stopper member 60 rotates relative to the first cam 56f. At this time, the arm 56d of the first cam 56f and the contact surface 60f of the stopper member 60 are in surface contact with each other, and slide with each other with relative rotation.

  Then, as shown in FIGS. 12C and 12D, the tip of the arm 56d of the first cam 56f reaches a position facing the notch 60d of the annular protrusion 60c of the stopper member 60 in the axial direction ( Out of regulation range).

  Then, the stopper member 60 can move to the dog gear 53 side (the front side in FIG. 12D) without being blocked by the first cam 56f. As a result, the drive-side sleeve 51 slightly moves toward the dog gear 53 side.

  Thus, outside the regulation range, the notch 60d faces the arm 56d of the cam 56, so that the contact between the contact surface 60f of the annular protrusion 60c and the arm 56d of the cam 56 is released.

  Thereafter, from the state shown in FIG. 12D, when the stopper member 60 rotates relative to the cam 56, the arm 56d of the first cam 56f contacts the tapered portion 60e of the annular protrusion 60c. The arm 56d of the first cam 56f is guided to the radially outer side of the annular protrusion 60c by the taper portion 60e and swings clockwise in FIG. 12D against the urging force of the return spring 57 ( Rotate.

  As a result, as shown in FIGS. 13C and 13D, the arm 56d of the first cam 56f is in contact with the outer peripheral surface of the annular protrusion 60c, and the stopper member 60 is rotated in accordance with the relative rotation. The outer peripheral surface of 60c is slid. Thus, the arm 56d of the first cam 56f retreats from the rotation locus range of the contact surface 60f of the annular protrusion 60c (retreat posture).

  Thus, after the contact surface 60f of the annular protrusion 60c moves to the dog gear 53 side with respect to the arm 56d of the first cam 56f, it shifts from outside the restriction range to within the restriction range. At this time, the tapered portion 60e comes into contact with the first cam 56f, and the first cam 56f is changed from the protruding posture to the retracted posture.

  As described above, the arm 56d of the first cam 56f has a protruding posture in which the arm 56d of the cam 56 protrudes within the rotation locus range of the contact surface 60f of the annular protrusion 60c and the contact surface 60f of the annular protrusion 60c. It changes to the retreat posture which retreats from the rotation locus range.

  FIG. 15 is a view for explaining the contact between the stopper member 60 and the cam 56, excluding the hub 54, the plate 58, the snap ring 59, and the dog gear 53 from the side view of the power transmission device 50. In order to facilitate understanding, the first cam 56f and the second cam 56g are indicated by hatching.

  As shown in the order of FIGS. 15A, 15 </ b> B, and 15 </ b> C, the annular protrusion 60 c contacts the first cam 56 f and then contacts the second cam 56 g, so that the stopper member 60 and the drive-side sleeve 51 The movement toward the dog gear 53 stops again.

  Thus, while the stopper member 60 is stopped by the first cam 56f and the second cam 56g, the amount of movement by the electric actuator 6 is absorbed by the coil spring 7. The coil spring 7 accumulates a pressing force in the movable direction of the shift fork 5. And the urging | biasing force of the coil spring 7 increases gradually, and the speed which the drive side sleeve 51 moves to the dog gear 53 side rises.

  Similarly to the first cam 56f, when the tip of the arm 56d of the second cam 56g reaches a position facing the notch 60d of the annular protrusion 60c of the stopper member 60 in the axial direction, the second cam 56g prevents the second cam 56g. The stopper member 60 can be moved to the dog gear 53 side (the front side in FIG. 12D) without being moved.

  As a result, as shown in FIG. 13A, the drive-side sleeve 51 moves to the dog gear 53 side to a position where the first dog 53a and the second dog 51a mesh with each other with a sufficient depth. At this time, the moving speed of the drive-side sleeve 51 is sufficiently increased by the biasing force of the coil spring 7, so that it is difficult for the second dog 51a to collide with the first dog 53a in a shallow engagement state, and the first dog 53a and the first dog 53a It becomes easy to move to a position where the two dogs 51a mesh with each other with a sufficient depth.

  Then, as shown in FIGS. 13C and 13D, the arm 56d of the second cam 56g comes into contact with the tapered portion 60e of the annular protrusion 60c. Similarly to the first cam 56f, the arm 56d of the second cam 56g is guided radially outward of the annular protrusion 60c by the tapered portion 60e, and resists the urging force of the return spring 57 in FIG. Oscillate clockwise. As a result, as shown in FIGS. 14C and 14D, the arm 56d of the second cam 56g slides on the outer peripheral surface of the annular protrusion 60c.

  In this way, as shown in FIG. 14A, the first dog 53a of the dog gear 53 and the second dog 51a of the drive side sleeve 51 mesh with each other, and the dog gear 53 and the drive side sleeve 51 rotate integrally. .

  At this time, as shown in FIG. 14D, in the power transmission state in which the first dog 53a and the second dog 51a mesh with each other, the phase difference is within the regulation range. In this case, the arm 56d of each of the two cams 56 is held in the retracted position by contacting the outer peripheral surface of the annular protrusion 60c.

  If the phase difference is outside the regulation range in the power transmission state, the cam 56 is held in the protruding posture, and the arm 56d of the cam 56 enters the notch 60d of the annular protrusion 60c.

  Then, after the first dog 53a of the dog gear 53 and the second dog 51a of the drive side sleeve 51 are engaged with each other, the second dogs 51a and 52a engaged with the first dog 53a are switched in the switching between the acceleration state and the deceleration state. Switch. At this time, the cam 56 and the stopper member 60 are slightly rotated relative to each other. At other times, if there is no gear change, the cam 56 and the stopper member 60 rotate integrally, and the cam 56 is held in the retracted position (or protruding position) as shown in FIGS. Will remain.

  In the above-described embodiment, when the vehicle is accelerated by the engine E, the drive side sleeve 51 is moved toward the dog gear 53 by the shift fork 5, and the second dog 51 a of the drive side sleeve 51 is moved to the first dog 53 a of the dog gear 53. The movement until meshing with will be described as an example. However, during engine braking, the shift fork 5 causes the coast side sleeve 52 to move toward the dog gear 53 and the second dog 52a of the coast side sleeve 52 meshes with the first dog 53a of the dog gear 53. Device 50 functions similarly.

  As described above, the power transmission device 50 according to the present embodiment is configured such that the shaft between the dog gear 53 and the drive-side sleeve 51 (coast-side sleeve 52) by the stopper member 60 and the cam 56 while the phase difference is within the regulation range. Movement in the proximity direction in the direction is restricted. During this time, the pressing force in the movable direction of the shift fork 5 is accumulated by the coil spring 7, and therefore, when it is out of the regulation range, the dog gear 53 and the drive side sleeve 51 (coast side sleeve 51) are caused by the accumulated biasing force. 52) approach quickly. Therefore, it is possible to avoid the situation where the first dog 53a of the dog gear 53 and the second dogs 51a and 52a of the drive side sleeve 51 and the coast side sleeve 52 are in a shallow mesh state, and to properly perform the meshing of the dog. Become.

  While the phase difference is within the regulation range and the pressing force in the moving direction of the shift fork 5 is accumulated by the coil spring 7, the contact surface 60f of the stopper member 60 and the arm 56d of the cam 56 are mutually connected. Since they remain in contact without striking each other, both wear and noise are suppressed.

  Further, for example, when the dog gear 53 and the drive side sleeve 51 (coast side sleeve 52) are close to each other, the arm 56d of the first cam 56f may accidentally face the notch 60d of the annular protrusion 60c. In this case, the contact surface 60f of the annular protrusion 60c and the arm 56d of the first cam 56f are not contacted, and the first cam 56f does not function.

  Even in such a case, in this embodiment, since the plurality of cams 56 having different axial heights are provided, at least the arm 56d of the second cam 56g is in contact with the contact surface 60f of the annular protrusion 60c. Touched. Therefore, the axial movement of the dog gear 53 and the drive side sleeve 51 (coast side sleeve 52) is restricted until the phase difference is outside the restriction range for the second cam 56g, and the coil spring 7 is pushed. It is possible to accumulate pressure.

  Further, since the stopper member 60 is formed with the notch 60d, the phase difference when the second dogs 51a and 52a jump into the first dog 53a side is limited to outside the regulation range. When the phase difference is out of the regulation range, the first dog 53a and the second dog 51a, 52a are positioned at a sufficiently wide distance in the relative rotation direction, so that the first dog 53a and the second dog 51a, 52a It is possible to ensure a sufficient depth of engagement.

  Suppose that the number of cams 56 is one, and the second dogs 51a and 52a jump into the first dog 53a side by chance without the arm 56d of the cam 56 and the annular protrusion 60c of the stopper member 60 contacting each other. Even in this case, when the phase difference is outside the regulation range, if the first dog 53a and the second dogs 51a and 52a are positioned at a sufficiently large distance in the relative rotational direction, the first dog 53a and the second dog 53a It is possible to avoid a situation in which the engagement of the two dogs 51a and 52a becomes too shallow.

  In the above-described embodiment, the case where the shift fork 5 is moved by the electric actuator 6 has been described. However, the shift fork 5 may be moved by a manually driven shift lever instead of the electric actuator 6.

  In the above-described embodiment, the case where the plurality of cams 56 are provided has been described. However, only one cam 56 may be provided.

  In the above-described embodiment, the case where the cam 56 is provided in the dog gear 53 and the stopper member 60 rotates integrally with the drive side sleeve 51 and the coast side sleeve 52 has been described. However, the dog gear 53 may be provided with the stopper member 60 and the cam 56 may rotate integrally with the drive side sleeve 51 and the coast side sleeve 52. That is, the dog gear 53 may be the second rotating body, and the drive side sleeve 51 and the coast side sleeve 52 may be the first rotating body.

  In the above-described embodiment, the case where the annular protrusion 60c of the stopper member 60 is formed with the contact surface 60f has been described. However, the contact surface 60f contacts the arm 56d of the cam 56 and is described above. If it functions like this, it may be formed in any member.

  The preferred embodiments of the present invention have been described above with reference to the accompanying drawings. However, the present invention is not limited to the above-described embodiments, and various modifications within the scope described in the claims. Needless to say, the modified examples also belong to the technical scope of the present invention.

  The present invention can be used for a power transmission device mainly used for a transmission of a vehicle.

50, 50a, 50b Power transmission device 51 Drive side sleeve (second rotating body, sleeve)
51a Second dog 52 Coast side sleeve (second rotating body, sleeve)
52a Second dog 53 Dog gear (first rotating body)
53a First dog 54 Hub 56 Cam 56b Main body 56d Arm (regulator)
56f First cam (cam)
56g Second cam (cam)
60 Stopper member 60c Annular projection (protrusion)
60d Notch 60f Contact surface

Claims (7)

A first rotating body in which a plurality of first dogs are arranged in a rotation direction;
A second rotating body in which a plurality of second dogs meshable with the first dog are arranged in a rotation direction;
With
When the first rotating body and the second rotating body move relative to each other in the close direction, the first dog and the second dog mesh with each other, and the first rotating body and the second rotating body rotate together. When the first rotating body and the second rotating body move relative to each other in the separating direction, the meshing of the first dog and the second dog is released, and the first rotating body and the second rotating body are released. A power transmission device in a disconnected state in which the second rotating body rotates relative to the second rotating body;
A restricting portion that rotates integrally with the first rotating body;
While rotating integrally with the second rotator and projecting toward the first rotator, a notch is formed in a part of the circular outer peripheral surface at least at the distal end in the projecting direction, while positioned in the second rotary body side than the regulating unit is disconnected state, a stopper protrusion abutment surface located on the first rotor side than the regulating portion is formed in the power transmission state is provided Members ,
With
In a process in which the first rotating body and the second rotating body are relatively moved in the proximity direction from the separated state, a position around the rotation axis of the second rotating body with respect to the first rotating body is within a regulation range. In addition, the first rotating body is in a state where the contact surface and the restricting portion are in surface contact with each other in the rotation axis direction and relative movement in the proximity direction is restricted, and the corresponding contact surface and the restricting portion are in contact with each other. And the second rotating body rotate relative to each other, and when the position around the rotation axis of the second rotating body with respect to the first rotating body is out of the regulation range, the notch part faces the regulation part. The contact between the contact surface and the restricting portion is released, and the first rotating body and the second rotating body are further moved relative to each other in the proximity direction so that the first dog and the second dog mesh with each other. A power transmission device characterized by that.   The power transmission device according to claim 1, wherein the contact surface has a length in a rotation direction of the second rotating body. A main body is provided on the first rotating body in a swingable manner, and a cam having the restricting portion is provided in a part of the main body,
The cam
Transition from a protruding posture in which the restricting portion protrudes within a rotation locus range of the contact surface and a retracting posture in which the restricting portion retracts from the rotation locus range,
While the contact surface is closer to the second rotating body than the restricting portion, the protruding posture is maintained,
In the power transmission state in which the first dog and the second dog are engaged with each other, if the position around the rotation axis of the second rotating body with respect to the first rotating body is out of the regulation range, the cam is projected. If the restriction portion enters the notch portion of the protrusion and is held in a posture, and the position around the rotation axis of the second rotation body with respect to the first rotation body is within the restriction range, the cam The power transmission device according to claim 1 , wherein the power transmission device is held in the retracted position in contact with an outer peripheral surface of the protruding portion. The contact surface is closer to the first rotating body than the restricting portion, and the position around the rotation axis of the second rotating body with respect to the first rotating body shifts from outside the restricting range to within the restricting range. The end face located at the boundary between the corresponding contact surface and the notch in the projecting portion contacts the cam, and the cam is changed from the projecting posture to the retracted posture. 4. The power transmission device according to 3 . The power transmission device according to claim 3 or 4 , wherein a plurality of the cams are provided in a rotation direction of the first rotating body. The power transmission device according to claim 5 , wherein each of the plurality of cams is provided by shifting each of the restricting portions in a direction of a rotation axis of the first rotating body. A hub fixed to the rotating shaft;
A sleeve that constitutes the second rotating body, rotates integrally with the hub, and is assembled to the hub so as to be movable in a rotation axis direction; and the second dog is formed;
With
The stopper member is
While rotating integrally with the hub, the direction toward the at least the first rotating body, one of the claims 1 to 6, characterized in that mounted to said hub to move said turned sleeve and integral The power transmission device according to claim 1.

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