JP2018071611A - Torque intermittence mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torque intermittence mechanism in which torque is smoothly transmitted.SOLUTION: A torque intermittence mechanism 1 is configured such that a clutch ring 20 (opposite side rotor) and a gear 30 (rotor) relatively move in an axial direction and engage with each other, to transmit torque. The gear 30 has a plurality high teeth 35 projecting in the axial direction with equal intervals in a peripheral direction and engaging with teeth 25 of the clutch ring 20, and low teeth 36 projecting so as to become lower than the high teeth 35 in the axial direction and engaging with the teeth 25 of the clutch ring 20. Each low tooth 36 approaches one of adjacent high teeth 35 in a circumferential direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a torque interrupting mechanism that interrupts torque between a pair of rotating bodies.

  Patent Document 1 discloses a torque interrupting mechanism including a pair of rotating bodies that face each other and relatively rotate.

  In the torque interrupting mechanism, each rotating body is provided with a plurality of projecting teeth arranged in the circumferential direction. A plurality of projecting teeth are formed on the counterpart rotating body so as to have a height at every predetermined interval in the circumferential direction. The tops of these protruding teeth are formed with curved surfaces.

  During the connection operation of the torque interrupting mechanism, one of the rotating bodies moves in the axial direction and approaches the counterpart rotating body. At this time, the torque is transmitted by the teeth of one of the rotating bodies fitting and meshing between the teeth of the counterpart rotating body.

JP 2007-120723 A

  However, if the projecting teeth of one rotating body collide with the corners of the lower projecting teeth of the counterpart rotating body and are bounced during the connection operation of the torque interrupting mechanism, the engagement between the projecting teeth may be delayed and torque may not be transmitted smoothly. There is.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a torque interrupt mechanism that smoothly transmits torque.

  According to an aspect of the present invention, there is provided a torque interrupting mechanism that transmits torque by causing the rotating body and the counterpart rotating body to move relative to each other in the axial direction, and the rotating body has an equal interval in the circumferential direction. A plurality of high teeth projecting in the axial direction and meshing with the teeth of the mating rotor, and low teeth projecting with a height lower in the axial direction than the high teeth and meshing with the teeth of the mating rotor; And the low teeth are close to one of the adjacent high teeth in the circumferential direction.

  According to the above aspect, at the time of the connection operation of the torque interrupting mechanism, after the tooth of the counterpart rotating body exceeds the high tooth of one rotating body, it is suppressed that it is bounced by hitting the low tooth close to the high tooth. As a result, in the torque interrupting mechanism, the teeth and the high teeth of the counterpart rotating body quickly mesh with each other, and torque is transmitted smoothly.

FIG. 1 is a configuration diagram illustrating a torque interrupting mechanism according to an embodiment of the present invention. FIG. 2 is a developed view of the gear showing the operating state during upshifting. FIG. 3 is an exploded view of the gear showing the operating state during downshifting. FIG. 4 is a developed view of a gear showing a modification of the torque interrupting mechanism. FIG. 5 is a development view of a gear showing a comparative example of the torque interrupting mechanism. FIG. 6 is a developed view of a gear showing another modification of the torque interrupting mechanism. FIG. 7 is a developed view of a gear showing another modification of the torque interrupting mechanism. FIG. 8 is a developed view of a gear showing another modification of the torque interrupting mechanism.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is a configuration diagram illustrating a torque interrupting mechanism 1 according to the present embodiment. For simplification of description, the torque interrupting mechanism 1 is shown with a part thereof omitted.

  The torque interrupting mechanism 1 is provided in a transmission 100 that is mounted on a vehicle. The transmission 100 includes an input-side shaft 2 driven by an engine (not shown) and an output-side shaft (not shown) that drives wheels (not shown). On the shaft 2, a first speed gear 10, a third speed gear 30, a second speed gear (not shown), and a fourth speed gear (not shown) are provided. On the output shaft, counter gears (not shown) that mesh with these gears are provided.

  A torque interrupting mechanism 1 is provided between the shaft 2, the first speed gear 10 and the third speed gear 30. The torque interruption mechanism 1 transmits the torque of the shaft 2 to the first speed gear 10 or the third speed gear 30. Similarly, another torque interrupting mechanism 1 is provided between the shaft 2, the second speed gear, and the fourth speed gear. In the transmission 100, each torque interrupting mechanism 1 selectively connects the first speed gear 10, the third speed gear 30, the second speed gear, and the fourth speed gear to the shaft 2, thereby rotating the shaft 2 to the output side shaft. The transmission ratio to be transmitted to is switched to four stages.

  The torque interrupting mechanism 1 includes a first speed gear 10, a third speed gear 30, and a clutch ring 20 that meshes with one of them as a rotating body that is supported by the shaft 2 and relatively rotates.

  The shaft 2 has a cylindrical clutch cam 27. A V-shaped groove 28 extending in a V shape is formed on the outer periphery of the clutch cam 27.

  The disc-shaped clutch ring 20 includes an inner periphery that is slidably fitted to the outer periphery of the clutch cam 27, a protrusion 29 that engages with the V-shaped groove 28, and an outer peripheral end that engages with the shift fork 3 of the transmission 100. Part. When the shift operation of the transmission 100 is performed, the shift fork 3 moves in the axial direction, so that the clutch ring 20 moves along the V-shaped groove 28.

  The clutch ring 20 has a plurality of teeth 21 and 25 projecting axially from both end surfaces. “Axial direction” means the direction in which the rotation axis extends. The teeth 21 protrude leftward in FIG. 1 from the end face facing the first speed gear 10. The tooth 25 protrudes rightward in FIG. 1 from the end face facing the third speed gear 30.

  The first speed gear 10 has a plurality of high teeth 15 and low teeth (not shown) protruding in the axial direction (rightward in FIG. 1) from the end face facing the clutch ring 20. Similarly, the third-speed gear 30 has a plurality of high teeth 35 and low teeth 36 (see FIG. 2) that protrude in the axial direction (leftward in FIG. 1) from the end surface facing the clutch ring 20.

  Next, the shift operation of the transmission 100 will be described.

  At the first speed position of the transmission 100, as shown in FIG. 1, the high teeth 15 or the low teeth of the first speed gear 10 and the teeth 21 of the clutch ring 20 mesh with each other, and torque from the shaft 2 is transmitted to the first speed gear 10. Is done.

  When an upshift operation is performed from the first speed position, the position is switched to the second speed position, and torque from the shaft 2 is transmitted to the second speed gear (not shown). At this time, the clutch ring 20 in the 1st speed position moves to the right in FIG. 1 along the V-shaped groove 28 by the circulating torque acting on the meshing portion with the 1st speed gear 10. Move away from the speed gear 10. Thus, the clutch ring 20 is disengaged from the first-speed gear 10 and held in the neutral position.

  When an upshift operation is performed from the second speed position, the position is switched to the third speed position, and torque from the shaft 2 is transmitted to the third speed gear 30. At this time, the clutch ring 20 in the neutral position is moved rightward in FIG. Thereby, the teeth 25 of the clutch ring 20 mesh with the high teeth 35 or the low teeth 36 of the third speed gear 30, and the torque from the shaft 2 is transmitted to the third speed gear 30.

  In this manner, in the transmission 100, the torque is interrupted when the clutch ring 20 (the counterpart rotating body) and the third speed gear 30 (the rotating body) having a rotational speed difference move relative to each other and mesh with each other. Transmitted without.

  Next, the tooth shape of the third speed gear 30 (hereinafter simply referred to as “gear 30”) will be described with reference to FIG. FIG. 2 is a developed view showing a developed section of the gear 30 extending in the circumferential direction. The “circumferential direction” means a direction around the rotation axis.

  The gear 30 has an end face 30a facing the clutch ring 20 and a plurality of high teeth 35 and low teeth 36 protruding in the axial direction from the end face 30a. The end surface 30a extends in a planar shape orthogonal to the rotation axis. The low teeth 36 protrude with a lower height in the axial direction than the high teeth 35.

  The plurality of high teeth 35 are evenly spaced in the circumferential direction of the gear 30 and are formed along the radiation R. The radiation R is a straight line extending in the radial direction about the rotation axis of the gear 30.

  One low tooth 36 is provided between the adjacent high teeth 35. That is, the high teeth 35 and the low teeth 36 protrude so as to be alternately arranged in the circumferential direction of the gear 30.

  With the above configuration, the interval between the high teeth 35 adjacent to each other in the circumferential direction is increased, and a path in which the teeth 25 of the clutch ring 20 mesh with the high teeth 35 is provided in a wide range. And the backlash (gap | interval) which the tooth | gear 25 of the clutch ring 20 meshes with the high tooth 35 or the low tooth 36 is set appropriately by setting the space | interval of the adjacent high tooth 35 and the low tooth 36 arbitrarily.

  The low teeth 36 are arranged so as to approach the high teeth 35 on the rear side (left side in FIG. 2) in the rotation direction with respect to the center line K of the adjacent high teeth 35. The center line K is radiation having an equal interval with respect to the adjacent high teeth 35 in the circumferential direction of the gear 30.

  The frame-shaped high teeth 35 are a torque receiving portion 35a that rises from the end face 30a, a corner portion 35b that bends from the tip of the torque receiving portion 35a, and a top portion 35c that extends to face the clutch ring 20 with the corner portion 35b as one end. And a corner portion 35d which bends at the other end of the top portion 35c.

  The torque receiving portion 35a has a surface inclined with respect to the radiation R of the gear 30 so as to face the end surface 30a. Thereby, the meshing state of the high teeth 35 and the teeth 25 of the clutch ring 20 is maintained. The torque receiver 35a may be formed substantially parallel to the radiation R.

  One corner 35b, the top 35c, and the other corner 35d are formed to bulge into a curved surface. Thereby, the impact which arises when the high tooth 35 hits the tooth | gear 25 of the clutch ring 20 is suppressed small.

  The top portion 35c bulges in a mountain shape from the two corner portions 35b and 35d. The corner portion 35b, the apex portion 35c, and the corner portion 35d have a symmetrical shape with respect to the radiation R.

  The low teeth 36 are connected to the high teeth 35 on the rear side in the rotation direction. The low teeth 36 are connected to the corners 35d of the high teeth 35 and extend so as to face the clutch ring 20, the corners 36d as the other ends of the tops 36c, and the corners rising from the end surfaces 30a. A torque receiving portion 36e extending to 36d. The low teeth 36 do not have a corner portion that projects in a manner connected to the rear side in the rotational direction of the top portion 36c.

  The torque receiving portion 36e has a surface inclined with respect to the radiation R so as to face the end surface 30a. Thereby, the meshing state of the low teeth 36 and the teeth 25 of the clutch ring 20 is maintained. The torque receiving portion 36e may be formed substantially parallel to the radiation R.

  The apex portion 36c and the corner portion 36d are formed by inclined surfaces that gradually incline toward the end surface 30a on the front side in the rotational direction (right side in FIG. 2) as the distance from the corner portion 35d of the high tooth 35 increases. Thereby, as shown by an arrow C in FIG. 2, when the teeth 25 of the clutch ring 20 contact the inclined surfaces of the top portion 36c and the corner portion 36d beyond the high teeth 35, the end surface 30a on the front side in the rotational direction along the inclined surface. A force with a velocity component toward is given.

  The top part 36c and the corner part 36d bulge into a curved surface. Thereby, the impact which arises when the tooth | gear 25 of the clutch ring 20 contacts the low tooth | gear 36 at the time of a downshift is suppressed small.

  The low teeth 36 protrude away from the high teeth 35 on the front side in the rotation direction. A valley 37 into which the teeth 25 of the clutch ring 20 enter is formed between the low teeth 36 and the high teeth 35 on the front side in the rotation direction. The opening width of the valley 37 is formed larger than the protruding width of the teeth 25 of the clutch ring 20 in the circumferential direction.

  The torque interrupting mechanism 1 transmits torque when a clutch ring 20 (a counterpart rotating body) and a gear 30 (a rotating body) having a difference in rotational speed move relative to each other in the axial direction and mesh with each other. Next, an operation in which the teeth 25 of the clutch ring 20 mesh with the high teeth 35 or the low teeth 36 of the gear 30 when the torque interrupting mechanism 1 is connected will be described.

  When the transmission 100 is in operation, the clutch ring 20 and the gear 30 are rotating in the direction indicated by the arrow A in FIG. When the transmission 100 is shifted up from the 2nd speed position to the 3rd speed position, the clutch ring 20 with the shift fork 3 in the neutral position is moved in the axial direction as indicated by an arrow B in FIG.

  When the rotational speed of the clutch ring 20 is higher than that of the gear 30, the teeth 25 of the clutch ring 20 change to the trough 37 after changing the high teeth 35 and the low teeth 36 of the gear 30 as indicated by the arrow C in FIG. Enter. At this time, even if the tooth 25 of the clutch ring 20 hits the top 35c of the high tooth 35 or the top 36c of the low tooth 36 of the gear 30, it smoothly enters the valley 37 and meshes with the high tooth 35 without being greatly repelled. . In this engaged state, the driving torque acting on the shaft 2 is transmitted to the gear 30 through the clutch ring 20.

  On the other hand, when the rotational speed of the clutch ring 20 is lower than that of the gear 30 during the downshift in which the transmission 100 is switched from the 4th speed position to the 2nd speed position, the teeth 25 of the clutch ring 20 are indicated by an arrow D in FIG. Then, it enters the valley 37 and meshes with the low teeth 36. In this meshing state, the coasting torque acting on the shaft 2 is transmitted to the gear 30 via the clutch ring 20.

  As described above, the path through which the teeth 25 of the clutch ring 20 mesh with the high teeth 35 during the upshift is set to a wider range than during the downshift. As a result, the rotational speed difference at which the clutch ring 20 and the gear 30 mesh smoothly is greater during upshifts than during downshifts.

  Next, a modification of the torque interrupting mechanism 1 shown in FIG. 4 will be described.

  As shown in FIG. 4, the low teeth 36 of the gear 30 protrude independently from between the two high teeth 35 arranged in the front and rear in the rotation direction, and are arranged so as to be close to the high teeth 35 on the rear side in the rotation direction. The low teeth 36 have corner portions 36b that project in a manner connected to the rear side in the rotational direction of the top portion 36c.

  A valley 38 is formed between the low teeth 36 and the high teeth 35 on the rear side in the rotation direction. A valley 37 is formed between the low teeth 36 and the high teeth 35 on the front side in the rotation direction. In the circumferential direction of the gear 30 and the clutch ring 20, the opening width “a” of the valley 38 is formed smaller than the protruding width “c” of the teeth 25 of the clutch ring 20. The opening width b of the valley 37 is formed larger than the protruding width c of the teeth 25 of the clutch ring 20.

  In this modification, the corner 36b of the low tooth 36 is close to the high tooth 35 on the rear side in the rotation direction. For this reason, it is avoided that the teeth 25 of the clutch ring 20 collide with the corners 36b of the low teeth 36 after changing the high teeth 35. Then, even if the teeth 25 of the clutch ring 20 hit the top 36c of the low teeth 36, as shown by an arrow E in FIG. 4, the teeth 25 smoothly enter the valleys 37 and mesh with the high teeth 35 without being greatly repelled.

  Next, a comparative example of the torque interruption mechanism 1 shown in FIG. 5 will be described.

  As shown in FIG. 5, the low teeth 36 of the gear 30 project independently from between the pair of high teeth 35 arranged around the center line K and arranged in the front-rear direction.

  A valley 39 is formed between the low teeth 36 and the high teeth 35 on the rear side in the rotation direction. A valley 37 is formed between the low teeth 36 and the high teeth 35 on the front side in the rotation direction. With respect to the circumferential direction of the gear 30, the opening width e of the valleys 37 and 39 is formed to have the same size as the protruding width c of the teeth 25 of the clutch ring 20.

  In this comparative example, the teeth 25 of the clutch ring 20 may hit the corners 36b of the low teeth 36 when the torque interrupting mechanism 1 is connected. In this case, since the teeth 25 of the clutch ring 20 are greatly repelled as indicated by the arrow F in FIG. 4, the probability of entering the valley 37 and meshing with the high teeth 35 is reduced.

  In contrast, in the torque interrupting mechanism 1 shown in FIGS. 1 to 4 of the present embodiment, the low teeth 36 are configured to be close to one of the adjacent high teeth 35 in the circumferential direction.

  With such a configuration, when the torque interrupting mechanism 1 is connected, the teeth 25 of the clutch ring 20 change over the high teeth 35 of the gear 30 and then hit the low teeth 36 that are close to the high teeth 35 in the circumferential direction. It can be suppressed. Thereby, in the torque interrupting mechanism 1, the teeth 25 and the high teeth 35 of the clutch ring 20 are quickly meshed, and torque is smoothly transmitted.

  Next, a modified example of the torque interrupting mechanism 1 shown in FIG. 6 will be described.

  As shown in FIG. 6, the high teeth 35 have a torque receiving portion 35 e that receives the coasting torque by the teeth 25 of the clutch ring 20 coming into contact with the low teeth 36. The torque receiving portion 35e is formed so as to extend from the corner portion 35d on the front side in the rotation direction to the top portion 36c of the low tooth 36. The torque receiving portion 35 e has a surface inclined with respect to the radiation R of the gear 30 so as to face the top portion 36 c of the low tooth 36. The torque receiver 35e may be formed substantially parallel to the radiation R. A valley 37 into which the teeth 25 of the clutch ring 20 enter is formed between the low teeth 36 and the high teeth 35 on the front side in the rotation direction. The top portion 36c of the low tooth 36 is formed in a cylindrical surface extending with a certain height in the axial direction.

  In this case, the tooth 25 of the clutch ring 20 moves as shown by an arrow H in FIG. 6 and moves to a position where it abuts on the torque receiving portion 36e of the low tooth 36 and moves as shown by an arrow I in FIG. The coasting torque acting on the shaft 2 is transmitted to the gear 30 both at the position where the high tooth 35 abuts against the torque receiving portion 35e. Thereby, the torque intermittent mechanism 1 increases the probability that the teeth 25 of the clutch ring 20 mesh with the gear 30 when the vehicle is downshifted.

  Next, a modification of the torque interrupting mechanism 1 shown in FIG. 7 will be described.

  As shown in FIG. 7, the gear 30 is formed such that the protruding width c of the low teeth 36 is larger than the protruding width d of the high teeth 35 in the circumferential direction. A valley 37 into which the teeth 25 of the clutch ring 20 enter is formed between the low teeth 36 and the high teeth 35 on the front side in the rotation direction.

  In this case, in the gear 30, the protruding width c of the low teeth 36 is arbitrarily set in the space between the pair of high teeth 35 aligned in the front and rear direction of rotation. Thus, the opening width b of the valley 37 is formed to be larger by the length of the backlash f than the protruding width g of the teeth 25 of the clutch ring 20, thereby reducing the sound generated at the meshing portion of the gear 30 and the clutch ring 20. be able to.

  Next, a modification of the torque interrupting mechanism 1 shown in FIG. 8 will be described.

  As shown in FIG. 8, the apex portion 35 c of the high tooth 35 approaches a lower portion from the corner portion 35 b on the rear side in the rotation direction (left side in FIG. 8) toward the corner portion 35 d on the front side in the rotation direction (right side in FIG. 8). It inclines so that it may approach the top part 36c of the tooth | gear 36 gradually. That is, the high teeth 35 have a top portion 35 c that is inclined toward the adjacent low teeth 36.

  In this case, when the torque interrupting mechanism 1 is connected, the teeth 25 of the clutch ring 20 come close to each other along the inclined surface of the top portion 35c as shown by an arrow J in FIG. It goes to the top 36c of the low teeth 36. Thereby, in the torque interrupting mechanism 1, the teeth 25 and the high teeth 35 of the clutch ring 20 are quickly meshed, and torque is smoothly transmitted.

  As described above, in the present embodiment, the torque interrupting mechanism 1 is configured such that the clutch ring 20 (the counterpart rotating body) and the gear 30 (the rotating body) having a difference in rotational speed are engaged with each other by relatively moving in the axial direction. Transmit torque. The gear 30 protrudes in the axial direction with an equal interval in the circumferential direction, and protrudes with a plurality of high teeth 35 meshing with the teeth 25 of the clutch ring 20 and a height lower than the high teeth 35 in the axial direction. And low teeth 36 that mesh with the 20 teeth 25. The low teeth 36 are close to one of the adjacent high teeth 35 in the circumferential direction.

  According to this, at the time of the connection operation of the torque interrupting mechanism 1, after the teeth 25 of the clutch ring 20 change the high teeth 35 of the gear 30, they are prevented from being hit by the low teeth 36 adjacent to the high teeth 35 in the circumferential direction. It is done. As a result, in the torque interrupting mechanism 1, the teeth 25 and the high teeth 35 of the clutch ring 20 are quickly engaged with each other, and torque is transmitted smoothly (effect corresponding to claim 1).

  The transmission 100 may include a control device (not shown) that automatically performs a shift operation. In this case, the control device does not need to finely align the positions of the clutch ring 20 and the gear 30 in order to operate the torque interrupting mechanism 1, and the required control accuracy does not have to be increased (corresponding to claim 1). Effect).

  1 to 3 is configured such that the high teeth 35 and the low teeth 36 that are adjacent to each other in the circumferential direction are connected to each other.

  By configuring in this way, the corners of the low teeth 36 connected to the high teeth 35 are not provided with corners that protrude to face the teeth 25 of the clutch ring 20. Therefore, it is avoided that the teeth 25 of the clutch ring 20 collide with the low teeth 36 close to the high teeth 35 during the connection operation of the torque interrupting mechanism 1 (effect corresponding to claim 2).

  Further, in the torque interrupting mechanism 1 shown in FIG. 6, the high teeth 35 have a torque receiving portion 35 e that receives torque when the teeth 25 of the clutch ring 20 come into contact with a portion connected to the low teeth 36.

  According to this, at the time of connecting operation of the torque interrupting mechanism 1, the tooth 25 of the clutch ring 20 is in contact with the torque receiving portion 36e of the low tooth 36 as shown by a two-dot chain line in FIG. As shown, the coasting torque acting on the shaft 2 is transmitted to the gear 30 both at the position where it abuts against the torque receiving portion 35e of the high tooth 35. As a result, the torque interrupting mechanism 1 increases the probability that the teeth 25 of the clutch ring 20 mesh with the gear 30 when the vehicle is downshifted (effect corresponding to claim 3).

  Further, the gear 30 shown in FIG. 7 is formed such that the protruding width c of the low teeth 36 is larger than the protruding width d of the high teeth 35 in the circumferential direction, and the high teeth 35 on the front side in the rotational direction adjacent to the low teeth 36 in the circumferential direction. In between, there is a trough 37 in which the teeth 25 of the clutch ring 20 are fitted.

  According to this, the gear 30 can reduce the sound produced in the meshing part of the gear 30 and the clutch ring 20 by appropriately setting the opening width b of the valley 37 (corresponding to claim 4). effect).

  Further, the high teeth 35 shown in FIG. 8 have a top portion 35 c that is inclined toward the adjacent low teeth 36.

  According to this, at the time of the connection operation of the torque interrupting mechanism 1, the teeth 25 of the clutch ring 20 hit the apex portion 35 c of the inclined high teeth 35 and head toward the apex portion 36 c of the low teeth 36 that are close to each other. And torque is transmitted smoothly (effect corresponding to claim 5).

  As mentioned above, although embodiment of this invention was described, the said embodiment showed only a part of application example of this invention, and the meaning which limits the technical scope of this invention to the specific structure of the said embodiment. Absent.

  The present invention is suitable as a torque interrupting mechanism provided in a transmission, but is not limited thereto, and can also be applied to a torque interrupting mechanism provided in other machines and equipment.

1 Torque interrupting mechanism 20 Clutch ring (partner rotating body)
25 teeth 30 gear (rotating body)
35 High tooth 35e Torque receiving part 36 Low tooth 36c Top part 37 Valley

Claims (5)

A torque interrupting mechanism that transmits torque by rotating and meshing with each other and the rotating body and the counterpart rotating body in an axial direction;
The rotating body is
A plurality of high teeth protruding in the axial direction with an equal interval in the circumferential direction and meshing with the teeth of the counterpart rotating body;
Projecting with a height lower in the axial direction than the high teeth, and having low teeth meshing with the teeth of the counterpart rotating body,
The low-tooth is close to one of the high teeth adjacent in the circumferential direction. The torque interrupting mechanism according to claim 1,
One of the said high teeth and the said low teeth are mutually connected, The torque interruption mechanism characterized by the above-mentioned. The torque interrupting mechanism according to claim 2,
The high-tooth has a torque receiving portion that receives torque when a tooth of the counterpart rotating body comes into contact with a portion connected to the low-tooth. The torque interrupting mechanism according to any one of claims 1 to 3,
The rotating body is
The protruding width of the low teeth in the circumferential direction is formed larger than the protruding width of the high teeth,
A torque interrupting mechanism comprising a trough in which the teeth of the counterpart rotating body are fitted between the low teeth and the other of the high teeth adjacent in the circumferential direction. The torque interrupting mechanism according to any one of claims 1 to 4,
The high tooth has a top portion that is inclined toward the low tooth adjacent to the high tooth.

Images