JP7317452B2 - Torque transmission direction switching type ratchet type clutch - Google Patents

Description

The present invention relates to a torque transmission direction switching ratchet clutch used as a torque transmission device or a backstop in vehicles, industrial machines, and the like.

Conventionally, in a clutch using a ratchet mechanism, when the ratchet mechanism is engaged, that is, a pawl member provided on either the outer ring or the inner ring and a tooth portion of, for example, a spline provided on the other of the outer ring or the inner ring. There is a problem that impact noise is generated or vibration is transmitted to the drive shaft side due to the impact at the time of meshing.

For example, in Patent Document 1, in order to suppress such impact noise and vibration, a recess on the inner ring side into which the pawl member on the outer ring side is fitted, or an impact absorbing member is provided between the drive shaft and the inner ring. A ratchet-type one-way clutch is described.

Japanese Patent Application Laid-Open No. 2003-056605

In recent years, such a torque transmission direction switching type ratchet type clutch has been increasingly used in a power transmission mechanism for transmitting the driving force of an electric motor in a vehicle using an electric motor as a power source of the drive device. . Since electric motors are excellent in quietness during operation, there is a demand for further reduction of the above-mentioned impact noise and vibration of ratchet-type clutches.

The present invention has been made in view of such circumstances. An object of the present invention is to provide a ratchet clutch.

In order to solve the above problems, the torque transmission direction switching ratchet type clutch according to the present invention includes:
an outer ring;
an inner ring arranged radially inside the outer ring so as to be coaxial with the axis of the outer ring and relatively rotatable;
a ratchet mechanism capable of engaging the outer ring and the inner ring so as to transmit torque;
a switching mechanism capable of switching torque transmission directions between the outer ring and the inner ring;
The ratchet mechanism includes a plurality of tooth portions provided at equal intervals in the circumferential direction on either the inner peripheral portion of the outer ring or the outer peripheral portion of the inner ring;
A plurality of first teeth are provided on the other of the inner circumference of the outer ring and the outer circumference of the inner ring, and engage with the teeth to lock relative rotation of the inner ring with respect to the outer ring in the first rotational direction. a claw member;
A plurality of second teeth are provided on either the inner peripheral portion of the outer ring or the outer peripheral portion of the inner ring, and engage with the tooth portion to lock the relative rotation of the inner ring with respect to the outer ring in the second rotational direction. a claw member;
When any one of the plurality of first pawl members meshes with the tooth portion, the other first pawl members move away from the meshing position with the tooth portion at different angles in increments of 1°. It is characterized by being arranged.

According to the present invention, it is possible to provide a torque transmission direction switching ratchet type clutch that can reduce impact noise and vibration caused by impact when the ratchet mechanism engages without using a shock absorbing member or the like.

FIG. 1 is a cross-sectional view perpendicular to the axial direction of a torque transmission direction switching ratchet type clutch according to an embodiment. FIG. 2 is a cross-sectional view similar to FIG. 1, showing the arrangement of the first and second pawl members.

A torque transmission direction switching ratchet type clutch according to an embodiment of the present invention will be described below with reference to the drawings.

First, the direction of the torque transmission direction switching ratchet type clutch in this embodiment will be defined. In this embodiment, the "center axis" refers to the center axis of the torque transmission direction switching ratchet type clutch, that is, the center axis of the outer ring and the inner ring, and the axial direction, radial direction, and circumferential direction refer to the axial direction with respect to the center axis. , radial direction, and circumferential direction. 1 and 2, the front side of the paper is defined as one side in the axial direction, the back side of the paper is defined as the other side in the axial direction, and the direction of rotation to the right as viewed in the paper is defined as one side in the circumferential direction or clockwise. The direction of leftward rotation is defined as the other side in the circumferential direction or the counterclockwise direction. In the following description, "torque transmission direction switching type ratchet type clutch" is abbreviated as "switching type ratchet type clutch".

In this embodiment, the inner ring is on the input side, the outer ring is on the output side, and a switchable ratchet clutch capable of transmitting torque from the inner ring to the outer ring will be described as an example. Regarding the direction of rotation of the switching ratchet type clutch, the direction of rotation of the inner ring with respect to the outer ring will be described, but the rotation of the outer ring and the rotation of the inner ring are relative. Also, in the following description, the unit of angle is expressed as "°".

FIG. 1 is a cross-sectional view orthogonal to the axial direction of a switching ratchet type clutch according to the embodiment, showing a state seen from one side in the axial direction.

A switchable ratchet-type clutch 1 according to this embodiment includes an annular outer ring 3 and an annular clutch disposed radially inward with respect to the outer ring 3 coaxially with a central axis C of the outer ring 3 and rotatable relative to the outer ring 3 . and a torque transmission mechanism that enables torque transmission between the outer ring 3 and the inner ring 5 . The torque transmission mechanism in this embodiment is a ratchet mechanism, and includes a plurality of first pawl members 7 and a plurality of second pawl members 9 provided on the inner peripheral portion of the outer ring 3 .

A plurality of tooth portions 13 projecting radially outward and extending in the axial direction are formed on the outer peripheral portion of the inner ring 5 at equal intervals along the entire circumference. The teeth 13 constitute ratchet teeth with which the first pawl member 7 and the second pawl member 9 mesh. Specifically, the wall surface on the other side in the circumferential direction of the tooth portion 13 constitutes a first engaging portion 13a with which the first pawl member 7 meshes, and the wall surface on the one side in the circumferential direction of the tooth portion 13 constitutes a second engaging portion 13a. A second meshing portion 13b with which the pawl member 9 meshes is formed.

As shown in FIG. 1, 36 teeth 13 are formed in this embodiment. Therefore, in a cross section orthogonal to the axial direction, the central angle with respect to the pitch of the tooth portions 13 adjacent in the circumferential direction is 10° when the central axis C is the center. In other words, the circumferential distance between the centers of circumferentially adjacent tooth portions 13 is defined as an arc, and the central angle for this arc when centered on the central axis C is 10°. Therefore, in a cross section orthogonal to the axial direction, the circumferential distance between the first meshing portions 13a adjacent in the circumferential direction is defined as an arc, and the central angle of this arc when centered on the central axis C is 10°. Similarly, the circumferential distance between the second meshing portions 13b adjacent in the circumferential direction is defined as an arc, and the central angle of this arc when centered on the central axis C is 10°.

A shaft hole 15 is formed on the inner peripheral side of the inner ring 5 , and a drive shaft 17 is fitted concentrically with the inner ring 5 in the shaft hole 15 . The drive shaft 17 is connected to a driving device such as an electric motor (not shown) through a gear mechanism (not shown). The drive shaft 17 and the inner ring 5 rotate together. The drive shaft 17 may be connected to the shaft hole 15 by spline fitting.

A plurality of protrusions 21 projecting radially outward and extending in the axial direction are provided at predetermined intervals in the circumferential direction on the outer peripheral surface of the outer ring 3 . The outer ring 3 is fixed to the driven-side member so as not to rotate relative to the driven-side member by fitting the protrusions 21 into the fitting portions of the driven-side member (not shown).

A plurality of first claw members 7 and a plurality of second claw members 9 are provided on the inner peripheral portion of the outer ring 3 at predetermined intervals along the circumferential direction. In this embodiment, ten first claw members 7 are provided, and two second claw members 9 are provided. The arrangement state of the first claw member 7 and the second claw member 9 will be described later.

The first pawl member 7 is held by a holding portion 25 provided on the inner peripheral portion of the outer ring 3 . The holding portion 25 is a recess opening inwardly on the inner peripheral surface of the outer ring 3 . The first pawl member 7 has a predetermined circumferential length. The first pawl member 7 is attached to the holding portion 25 of the outer ring 3 so as to be capable of radially swinging around the tip of a protruding portion 7a formed at the other circumferential side end portion so as to protrude to the other side in the circumferential direction. held. The first pawl member 7 has a portion on one side in the axial direction of the inner diameter side surface facing the outer peripheral surface of the inner ring 5, that is, the tooth portion 13 in the radial direction. When the first pawl member 7 swings radially inward, the inner diameter side portion of the tip portion on one side in the circumferential direction meshes with the first meshing portion 13 a of the tooth portion 13 of the inner ring 5 .

The holding portion 25 is provided with a coil-shaped spring 27 that always biases the first pawl member 7 radially inward, that is, in a direction in which it meshes with the tooth portion 13 of the inner ring 5 . The first pawl member 7 meshes with the toothed portion 13 of the inner ring 5 to lock the rotation of the inner ring 5 with respect to the outer ring 3 in the counterclockwise direction, that is, in the other rotational direction in the circumferential direction. It is possible to rotate in one direction, that is, in the circumferential direction.

The second pawl member 9 is held by a holding portion 29 provided on the inner peripheral portion of the outer ring 3 . The holding portion 29 is a recess opening inwardly on the inner peripheral surface of the outer ring 3 . The second pawl member 9 has a predetermined circumferential length. The second pawl member 9 is attached to the holding portion 29 of the outer ring 3 so as to be capable of radially swinging around the tip of a protruding portion 9a formed at one end portion in the circumferential direction so as to protrude to the one side in the circumferential direction. held. The second pawl member 9 has a portion on one axial side of the inner diameter side surface facing the outer peripheral surface of the inner ring 5, that is, the tooth portion 13 in the radial direction. When the second pawl member 9 swings radially inward, the inner diameter side portion of the distal end portion on the other side in the circumferential direction meshes with the second meshing portion 13 b of the tooth portion 13 of the inner ring 5 .

The holding portion 29 is provided with a coil-shaped spring 31 that always biases the second pawl member 9 radially inward, that is, in a direction in which it meshes with the tooth portion 13 of the inner ring 5 . The second pawl member 9 engages with the toothed portion 13 of the inner ring 5 to lock the clockwise rotation of the inner ring 5 with respect to the outer ring 3, that is, in one of the circumferential directions. It is possible to rotate in the other direction, that is, in the circumferential direction.

In this manner, the first pawl member 7 and the second pawl member 9 held by the holding portions 25 and 29 of the outer ring 3, the springs 27 and 31, and the inner ring 5 in which the tooth portions 13 are formed form the ratchet. Mechanism is constructed.

In the switching ratchet type clutch 1 according to this embodiment, an annular switching plate 35 is arranged coaxially with the inner ring 5 and adjacent to the other side of the inner ring 5 in the axial direction. The switching plate 35 is a member for switching the locking direction of rotation of the inner ring 5 with respect to the outer ring 3 . In other words, the switching plate 35 is a member for switching the transmission direction of torque from the inner ring 5 to the outer ring 3 . The switching plate 35 is provided so as to be rotatable around the central axis C. As shown in FIG.

The outer peripheral surface of the switching plate 35 faces the inner peripheral surface of the outer ring 3 in the radial direction. In addition, the outer peripheral surface of the switching plate 35 radially faces the other portion of the inner diameter side surfaces of the first and second claw members 7 and 9 in the axial direction. A plurality of protruding portions 37 are provided on the outer peripheral surface of the switching plate 35 so as to smoothly protrude radially outward and have a predetermined length in the circumferential direction. These protrusions 37 are provided in one-to-one correspondence with the first claw member 7 and the second claw member 9 .

The protruding portion 37 of the switching plate 35 is radially opposed to the inner peripheral surface of the outer ring 3 with a small gap therebetween. When the protruding portion 37 is positioned on the inner diameter side of the first or second claw member 7 or 9 corresponding to the rotation of the switching plate 35, the projection 37 is positioned on the inner diameter side surface of the first or second claw member 7 or 9. By contacting the portion on the other side of the direction, the inner diameter side surfaces of the first or second pawl members 7 and 9 are pushed up and held toward the outer diameter side of the tooth portion 13 of the inner ring 5 . As a result, the protruding portion 37 prevents the engagement between the first or second pawl member 7 , 9 and the tooth portion 13 of the inner ring 5 .

The switching plate 35 changes the circumferential position of the protrusion 37 with respect to the first or second claw members 7 and 9 by rotating. Thereby, the combined state of contact or non-contact of the projecting portion 37 with respect to the first claw member 7 and the second claw member 9 is changed. Specifically, the switching plate 35 switches between four combined states of contact and non-contact of the protruding portion 37 with the first pawl member 7 and the second pawl member 9, thereby rotating the inner ring 5 with respect to the outer ring 3. to switch the lock direction of the

A first combination state of contact or non-contact of the protruding portion 37 with the first or second claw members 7 and 9 is such that the protruding portion 37 corresponding to the second claw member 9 is located on the inner diameter side of the second claw member 9 . , and the projecting portion 37 corresponding to the first claw member 7 is not in contact with the inner diameter side surface of the first claw member 7 . In this state, the protruding portion 37 in contact with the second pawl member 9 contacts the second pawl member 9 in a state in which the spring 31 is compressed, and the surface of the second pawl member 9 on the inner diameter side is held on the outer diameter side of the toothed portion 13 of the inner ring 5 to prevent the meshing between the second pawl member 9 and the toothed portion 13 of the inner ring 5 . On the other hand, in this state, the first pawl member 7 meshes with the toothed portion 13 of the inner ring 5 due to the biasing force of the spring 27 . Here, the switching ratchet type clutch 1 of this embodiment has a configuration in which any one of the ten first pawl members 7 is engaged with the tooth portion 13 of the inner ring 5. It's becoming This configuration will be described later. In this state, the inner ring 5 can rotate in one circumferential direction with respect to the outer ring 3, and is locked against rotation in the other circumferential direction. That is, when the inner ring 5 rotates in the other circumferential direction, the inner ring 5 and the outer ring 3 rotate integrally, and torque is transmitted from the inner ring 5 to the outer ring 3 via the first pawl member 7 . On the other hand, torque is not transmitted from the inner ring 5 to the outer ring 3 even if the inner ring 5 rotates in one direction in the circumferential direction. In the following description, this state will be referred to as the "first state" of the switching ratchet type clutch 1. FIG.

A second combination state of contact or non-contact of the protruding portion 37 with the first or second claw members 7 and 9 is such that the protruding portion 37 corresponding to the first claw member 7 is located on the inner diameter side of the first claw portion 71 . , and the projecting portion 37 corresponding to the second claw member 9 is not in contact with the inner diameter side surface of the second claw member 9 . In this state, the projecting portion 37 in contact with the first pawl member 7 contacts the first pawl member 7 in a state in which the spring 27 is compressed, and the surface of the first pawl member 7 on the inner diameter side is held on the outer diameter side of the toothed portion 13 of the inner ring 5 to prevent the meshing between the first pawl member 7 and the toothed portion 13 of the inner ring 5 . On the other hand, in this state, the second pawl member 9 meshes with the toothed portion 13 of the inner ring 5 by the biasing force of the spring 31 . Therefore, in this state, the inner ring 5 can rotate in the other circumferential direction with respect to the outer ring 3, and is locked against rotation in the one circumferential direction. That is, when the inner ring 5 rotates in one direction in the circumferential direction, the inner ring 5 and the outer ring 3 rotate together, and torque is transmitted from the inner ring 5 to the outer ring 3 via the second pawl member 9 . On the other hand, torque is not transmitted from the inner ring 5 to the outer ring 3 even if the inner ring 5 rotates in the other circumferential direction. In the following description, this state is referred to as the "second state" of the switching ratchet type clutch 1. FIG.

A contact or non-contact third combination state of the protrusion 37 with the first or second claw member 7 or 9 is such that the protrusion 37 corresponding to the first claw member 7 is located on the inner diameter side of the first claw member 7 . , and the projecting portion 37 corresponding to the second claw member 9 is in contact with the inner diameter side surface of the second claw member 9 . In this state, the projecting portion 37 in contact with the first pawl member 7 holds the inner diameter side surface of the first pawl member 7 closer to the outer diameter side than the tooth portion 13 of the inner ring 5, and the first pawl member 7 is held. This prevents the meshing between the member 7 and the toothed portion 13 of the inner ring 5. - 特許庁Further, the protruding portion 37 in contact with the second pawl member 9 holds the inner diameter side surface of the second pawl member 9 closer to the outer diameter side than the tooth portion 13 of the inner ring 5, and the second pawl member 9 and the tooth portion 13 of the inner ring 5 are prevented from meshing with each other. Therefore, in this state, the inner ring 5 is not locked against the outer ring 3 in either the one circumferential direction or the other circumferential direction, and can be rotated either in the one circumferential direction or in the other circumferential direction. be. In other words, torque is not transmitted from the inner ring 5 to the outer ring 3 regardless of whether the inner ring 5 rotates in one circumferential direction or in the other circumferential direction. In the following description, this state will be referred to as the "third state" of the switching ratchet type clutch 1. FIG.

A fourth combination state of contact or non-contact of the protrusion 37 with the first or second pawl member 7, 9 corresponds to the protrusion 37 corresponding to the first pawl member 7 and the second pawl member 9. The protrusions 37 are in contact with neither the first pawl member 7 nor the second pawl member 9 , and all the protrusions 37 face the inner peripheral surface of the outer ring 3 . In this state, the first pawl member 7 and the second pawl member 9 mesh with the teeth 13 of the inner ring 5 by the biasing forces of the springs 27 and 31, respectively. As for the first claw member 7, one of the ten first claw members 7 meshes with the tooth portion 13 of the inner ring 5 in the same manner as in the first state described above. Therefore, in this state, the inner ring 5 is locked against the outer ring 3 against rotation in either of the one circumferential direction and the other circumferential direction. That is, the inner ring 5 and the outer ring 3 rotate integrally regardless of whether the inner ring 5 rotates in one circumferential direction or in the other circumferential direction, and torque is transmitted from the inner ring 5 to the outer ring 3 . In the following description, this state will be referred to as the "fourth state" of the switching ratchet type clutch 1. FIG.

The switching plate 35 is rotated by, for example, an actuator (not shown). In the switching ratchet type clutch 1, an actuator (not shown) rotates the switching plate 35 about the center axis C, thereby causing the protrusion 37 to contact or not contact the first pawl member 7 and the second pawl member 9. Toggling the contact combination state. As a result, the changeable ratchet clutch 1 switches the direction of torque transmission from the inner ring 5 to the outer ring 3 by switching between the first state, the second state, the third state, and the fourth state.

Next, the arrangement state of the first pawl member 7 and the second pawl member 9 of the outer ring 3 will be described.
FIG. 2 is a cross-sectional view similar to FIG. 1, perpendicular to the axial direction, showing the arrangement of the first and second pawl members of the switching ratchet type clutch. FIG. 2 shows the first state of the switching ratchet type clutch 1 described above, that is, the meshing between the second pawl member 9 and the toothed portion 13 of the inner ring 5 is prevented, and the first pawl member 7 is disengaged from the toothed portion. 13, the inner ring 5 can rotate with respect to the outer ring 3 in one circumferential direction, and rotation in the other circumferential direction is locked. 2, illustration of the springs 27 and 31 is omitted.

Hereinafter, for the sake of convenience, the ten first claw members 7 are arranged from 7a to 7j in order from the first claw member 7 positioned at the top in FIG. With reference to the first pawl member 7a, the two second pawl members 9 will be described with reference numerals 9a and 9b in order in the clockwise direction.

In this embodiment, the ten first claw members 7a to 7j are spaced clockwise from the first claw member 7a as shown in FIG. , 7f, 7g, 7h, 7i, and 7j. Further, the second pawl member 9a is arranged between the first pawl members 7e and 7f, and the second pawl member 9b is arranged between the first pawl members 7j and 7a.

As shown in FIG. 2, the first pawl member 7a and the first pawl member 7b, which is clockwise adjacent to the first pawl member 7a, are separated from each other by the center of the first pawl member 7a and the center of the first pawl member 7b in a cross section orthogonal to the axial direction. The circumferential distance in the clockwise direction is defined as an arc, and they are arranged at positions where the central angle with respect to this arc when centering on the central axis C is 32°. Similarly, the first claw member 7b and the first claw member 7c, which is clockwise adjacent to the first claw member 7b, have a center angle of The first claw member 7d, which is arranged at a position of 32° and is adjacent to the first claw member 7c in the clockwise direction, has a circumferential distance in the clockwise direction between the center of the first claw member 7c and the center of the first claw member 7d. The first pawl member 7e, which is adjacent to the first pawl member 7d in the clockwise direction, is arranged at a position where the central angle with respect to the arc of is 32°. It is arranged at a position where the central angle with respect to the arc of the circumferential distance in the clockwise direction is 32°. Thus, the five first pawl members 7a to 7e are each centered relative to the arc of the clockwise circumferential distance between the centers of circumferentially adjacent first pawl members 7. It is positioned at an angle of 32°.

In a cross section perpendicular to the axial direction, the first claw member 7f has an arc defined by a clockwise circumferential distance between the center of the first claw member 7a and the center of the first claw member 7f. It is arranged at a position where the central angle with respect to the arc is 181°.

The first claw member 7f and the first claw member 7g, which is adjacent to the first claw member 7f in the clockwise direction, are arranged so that, in a cross section orthogonal to the axial direction, the center of the first claw member 7f and the center of the first claw member 7g are centered on the central axis C. , and is arranged at a position where the central angle with respect to the arc is 32° when the central axis C is the center. Similarly, the first claw member 7h adjacent to the first claw member 7g in the clockwise direction has a central angle of The first claw member 7i, which is arranged at a position of 32° and is adjacent to the first claw member 7h in the clockwise direction, has a circumferential distance in the clockwise direction between the center of the first claw member 7h and the center of the first claw member 7i. The first claw member 7j adjacent to the first claw member 7i in the clockwise direction is arranged at a position where the central angle with respect to the arc of is 32°. It is arranged at a position where the central angle with respect to the arc of the circumferential distance in the clockwise direction is 32°. Thus, the five first pawl members 7, 7f to 7j, have a central angle with respect to the arc of the clockwise circumferential distance between the centers of circumferentially adjacent first pawl members 7. is arranged at a position of 32°.

In addition, in the cross section perpendicular to the axial direction of the first claw member 7g, when the circumferential distance in the clockwise direction between the center of the first claw member 7b and the center of 7g is defined as an arc, and the central axis line C is set as the center, is arranged at a position where the central angle with respect to this arc is 181°. Similarly, the first claw members 7c and 7h are arranged at positions where the central angle with respect to the arc of the circumferential distance in the clockwise direction between the center of the first claw member 7c and the center of 7h is 181°. The claw members 7d and 7i of the first claw member 7d and 7i are arranged at positions where the central angle with respect to the arc of the circumferential distance in the clockwise direction between the center of the first claw member 7d and the center of the claw member 7i is 181°. 7e and 7j are arranged at positions where the central angle with respect to the arc of the circumferential distance in the clockwise direction between the center of the first claw member 7e and the center of 7j is 181°.

Since the ten first claw members 7a to 7j are arranged in this manner, if the phase of the first claw member 7a is 0°, the phase of the first claw member 7b is 32°, and 7c is 64°, 7d is 96°, 7e is 128°, 7f is 181°, 7g is 213°, and 7h is 245° , the phase of 7i is 277° and the phase of 7j is 309°.

The two second claw members 9a and 9b are arranged at symmetrical positions with respect to the central axis C in a cross section orthogonal to the axial direction. That is, the second claw members 9a and 9b define an arc defined by the clockwise circumferential distance between the center of the second claw member 9a and the center of the second claw member 9b. It is arranged at a position where the angle is 180°. With such a configuration, the two second claw members 9a and 9b mesh with the second meshing portion 13b of the tooth portion 13 at the same time. Further, in the above-described fourth state of the switching ratchet type clutch 1, one of the second pawl members 9a and 9b and the first pawl members 7a to 7j is engaged with the tooth portion 13. As shown in FIG.

The changeable ratchet type clutch 1 of the present embodiment is arranged such that the ten first pawl members 7a to 7j are in the phases described above, so that the changeable ratchet type clutch 1 in the above-described first state or In the fourth state, only one of the first pawl members 7a to 7j meshes with the first meshing portion 13a of the tooth portion 13. As shown in FIG. That is, the plurality of tooth portions 13 have a central angle of 10° with respect to the arc of the circumferential distance between the circumferentially adjacent first meshing portions 13a, and any one of the first claw members 7a to 7j, For example, as shown in FIG. 2, when the first pawl member 7a meshes with the first meshing portion 13a, none of the other nine first pawl members 7b to 7j are positioned at phases divisible by 10°. That is, none of the other nine first claw members 7b to 7j mesh with the first meshing portion 13a.

Further, in the present embodiment, the plurality of tooth portions 13 have a central angle of 10° with respect to the arc of the circumferential distance between the first meshing portions 13a adjacent in the circumferential direction, and the phase of the first claw member 7a is 10°. is 0°, when the first claw member 7a meshes with the first meshing portion 13a of the tooth portion 13, the first claw member 7f moves away from the meshing position with the first meshing portion 13a by 1°. placed in Similarly, the first pawl member 7b is arranged at a phase separated by 2° from the meshing position with the first meshing portion 13a, and the first claw member 7g is arranged at a phase 3° from the meshing position with the first meshing portion 13a. The first claw member 7c is arranged in a phase separated from the meshing position with the first meshing portion 13a by 4°, and the first claw member 7h meshes with the first meshing portion 13a. The first claw member 7d is arranged at a phase separated by 5° from the position of engagement with the first engaging portion 13a, and the first claw member 7i is arranged at a phase separated by 6° from the engaging position with the first engaging portion 13a. The first pawl member 7e is arranged in a phase separated by 8° from the position of engagement with the first engagement portion 13a, and the first pawl member 7j is arranged in the phase separated by 8° from the position of engagement with the first engagement portion 13a. It is arranged at a phase separated by 9° from the meshing position with the first meshing portion 13a.

In this way, when any one of the ten first claw members 7a to 7j meshes with the tooth portion 13, the other nine claw members 7a to 7j are arranged at different angles from the meshing position with the tooth portion 13 in increments of 1°. They are arranged in separate phases. In such a configuration, the central angle with respect to the arc of the circumferential distance between the circumferentially adjacent first meshing portions 13a is 10°, and the ten first claw members 7a to 7j are provided. It becomes possible by That is, when m and n are integers, and the central angle with respect to the pitch of the tooth portions 13 adjacent in the circumferential direction is m°, n (where m≦n) first claw members 7 are arranged at a predetermined angle. phase.

Therefore, the changeover ratchet type clutch 1 of the present embodiment, when switching from the second state or the third state described above to the first state or the fourth state, that is, any one of the first pawl members 7a to 7j When the rotation of the inner ring 5 to the other side in the circumferential direction is locked by one, no matter what phase the inner ring 5 is in with respect to the outer ring 3, the inner ring 5 may rotate at most 1° to the other side in the circumferential direction. For example, one of the first pawl members 7a to 7j meshes with the first meshing portion 13a of the tooth portion 13. As shown in FIG.

As described above, in the switching ratchet type clutch 1 of the present embodiment, when the rotation of the inner ring 5 toward the other side in the circumferential direction is locked, the inner ring 5 rotates to the other side in the circumferential direction by 1° or less with respect to the outer ring 3. is locked. That is, the rotation angle of the inner ring 5 until one of the first pawl members 7a to 7j meshes with the tooth portion 13 of the inner ring 5 is 1° or less. As described above, the changeover ratchet type clutch 1 of the present embodiment can greatly reduce the amount of rotation of the inner ring 5 until one of the first pawl members 7a to 7j meshes with the tooth portion 13 of the inner ring 5. Therefore, the impact when the first pawl members 7a to 7j and the tooth portion 13 are meshed can be reduced. As a result, it is possible to reduce impact noise and vibration when the first pawl members 7a to 7j and the toothed portion 13 of the inner ring 5 are meshed with each other.

Therefore, according to the switching ratchet type clutch 1 of the present embodiment, the impact noise and vibration when the ratchet mechanism is engaged can be reduced without using a shock absorbing member or the like. Even if it is used in a vehicle or the like using an electric motor, the quietness of the electric motor is not impaired.

It should be noted that the changeover ratchet clutch 1 according to the present invention is not limited to the above embodiment, and modifications are possible. For example, the changeover ratchet type clutch 1 may be provided with tooth portions on the inner peripheral portion of the outer ring 3 and may be provided with first and second pawl members on the outer peripheral portion of the inner ring 5 .

In the above embodiment, the central angle between the tooth portions 13 adjacent in the circumferential direction is 10° and the number of the first claw members 7 is 10, but other configurations are possible. In this case, the number of teeth 13, the central angle between adjacent teeth 13 in the circumferential direction, and the number of first pawl members 7 are appropriately designed according to the torque capacity to be transmitted between the inner ring 5 and the outer ring 3. , can be set.

1 torque transmission direction switching type ratchet type clutch 3 outer ring 5 inner ring 7 first pawl member 9 second pawl member 13 tooth portion 13a first meshing portion 13b second meshing portion 15 shaft hole 17 drive shafts 25, 29 holding Parts 27, 31 Spring 35 Switching plate 37 Protruding part

Claims (4)

an outer ring;
an inner ring arranged radially inside the outer ring so as to be coaxial with the axis of the outer ring and relatively rotatable;
a ratchet mechanism capable of engaging the outer ring and the inner ring so as to transmit torque;
a switching mechanism capable of switching torque transmission directions between the outer ring and the inner ring;
The ratchet mechanism includes a plurality of tooth portions provided at equal intervals in the circumferential direction on either the inner peripheral portion of the outer ring or the outer peripheral portion of the inner ring;
A plurality of first teeth are provided on the other of the inner circumference of the outer ring and the outer circumference of the inner ring, and engage with the teeth to lock relative rotation of the inner ring with respect to the outer ring in the first rotational direction. a claw member;
A plurality of second teeth are provided on either the inner peripheral portion of the outer ring or the outer peripheral portion of the inner ring, and engage with the tooth portion to lock the relative rotation of the inner ring with respect to the outer ring in the second rotational direction. a claw member;
When any one of the plurality of first pawl members meshes with the tooth portion, the other first pawl members move away from the meshing position with the tooth portion at different angles in increments of 1°. A torque transmission direction switching ratchet type clutch, characterized in that: When locking the relative rotation of the inner ring with respect to the outer ring in the first rotational direction, the first rotation of the inner ring until the tooth portion and any one of the plurality of first pawl members mesh with each other. 2. A torque transmission direction switching ratchet type clutch according to claim 1, wherein the rotation angle in the direction of rotation is 1[deg.] or less. When m and n are integers, each of the plurality of teeth has a central angle of m° with respect to the pitch of the teeth adjacent in the circumferential direction, and the plurality of first claw members are n (however, , m≦n). 2. Two of said second claw members are provided, and said two second claw members are arranged at symmetrical positions with respect to said axis in a cross section perpendicular to said axis. 4. The torque transmission direction switching ratchet type clutch according to any one of items 3 to 4.

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