WO2018025905A1

WO2018025905A1 - Brake device and clutch unit

Info

Publication number: WO2018025905A1
Application number: PCT/JP2017/028016
Authority: WO
Inventors: 香取孝宜
Original assignee: テイ・エステック株式会社
Priority date: 2016-08-04
Filing date: 2017-08-02
Publication date: 2018-02-08

Abstract

This brake device (3) is provided with: an outer ring (10); brake shoes (20); an output-side rotary member (30) which is disposed radially inward of the brake shoes (20), and which has counter surfaces (36) that faces respective inner surfaces (23) of the brake shoes (20); and an input-side rotary member (40) that abuts against the brake shoes (20) or the output-side rotary member (30) so as to be able to apply rotary torque to the output-side rotary member (30). The brake device (3) is configured such that a rotational force inputted to the output-side rotary member (30) does not cause the input-side rotary member (40) to rotate at least in one rotational direction. The brake device (3) is further provided with a friction member (90) that has: pressure-contact parts (94) which are pressed against an inner peripheral surface (11); and an engagement part (94) which engages with the brake shoes (20) in a peripheral direction.

Description

Brake device and clutch unit

The present invention relates to a brake device and a clutch unit used for a vehicle seat height adjustment mechanism and the like.

In the height adjustment mechanism for a vehicle seat, the output shaft rotates by operating a lever provided on the input side that swings up and down. However, the weight of the seat and the occupant applies a force to the seat to lower the seat. However, a clutch unit including a brake device configured so that the output shaft does not rotate and a ratchet device for operating the brake device is used. The ratchet device is provided with a return spring for returning the lever to the neutral position.

For example, the brake device of Patent Document 1 includes an outer ring having a cylindrical inner peripheral surface, a plurality of brake shoes facing the inner peripheral surface, and an output-side rotating member arranged inside the brake shoe. Yes.

The brake device is provided with a friction ring in order to suppress the sudden start of the operation of the output side rotating member when the braking force is lost. The friction ring has three friction generating arms that are in pressure contact with the inner peripheral surface of the outer ring, and is engaged with the output side rotating member so as to rotate integrally with the output side rotating member. Thereby, since the frictional force generated between the friction generating arm and the inner peripheral surface of the outer ring becomes a so-called weak auxiliary braking force, the output side rotating member is suppressed from rotating rapidly.

Also, the ratchet device used in the clutch unit of Patent Document 1 has a roller disposed between the operation input member and the output ring, so that the operation input member and the output ring can rotate together. The spring that biases the roller is used as a return spring for returning the lever to the neutral position.

JP 2016-124526 A

However, in the configuration of Patent Document 1, although the friction ring is a thin and small part, force must be transmitted from the inner peripheral surface of the outer ring to the output-side rotating member, so that the force transmission efficiency is not good. . Therefore, there is a possibility that a sufficient frictional force cannot be obtained due to the friction ring sagging.

In the configuration of Patent Document 1, it is difficult to increase the urging force of the return spring from the space where the spring is arranged, and there is a possibility that the force for returning the lever to the neutral position becomes insufficient.

The present invention has been made in view of the above background, and an object of the present invention is to provide a brake device that can stably generate an auxiliary brake force that suppresses abrupt rotation of an output-side rotating member. To do.

Also, an object of the present invention is to facilitate assembly of the brake device.

Also, an object of the present invention is to suppress an increase in the size of the brake device.

Also, an object of the present invention is to suppress the generation of sound when the brake device is operated.

Furthermore, an object of the present invention is to provide a clutch unit having a ratchet device that can smoothly return an operation input member to a neutral position.

Also, an object of the present invention is to suppress an increase in the size of the ratchet device.

In order to achieve the above-described object, the brake device of the present invention includes an outer ring having a cylindrical inner peripheral surface, a plurality of the outer rings arranged in the circumferential direction on the radial inner side of the outer ring, and facing the inner peripheral surface. A brake shoe having a pair of brake surfaces that can come into contact with the peripheral surface and an inner surface facing radially inward, and an output side that is disposed on the radially inner side of each brake shoe and has a facing surface facing the inner surface on the outer periphery A rotating member, and an input-side rotating member capable of giving a rotational torque to the output-side rotating member by contacting the brake shoe or the output-side rotating member, and the rotational force input to the output-side rotating member is at least About one rotation direction, it is comprised so that an input side rotation member may not be rotated.
And a brake device is provided with the friction member which has a press-contact part press-contacted to an internal peripheral surface, and an engaging part engaged with a brake shoe in the circumferential direction.

According to such a configuration, the friction member engages with the brake shoe in the circumferential direction. Since the brake shoe is a member that is in contact with the inner peripheral surface, the distance from the pressure contact portion that generates a frictional force to the engagement portion that engages the brake shoe and transmits the force can be reduced, and the auxiliary brake force can be reduced. It can be efficiently transmitted to the brake shoe. For this reason, the auxiliary brake force can be generated stably.

In the brake device described above, the friction member may have a ring portion at a position closer to the inner peripheral surface than the output-side rotating member, and the press contact portion may be provided to protrude radially outward from the ring portion.

According to such a configuration, since the ring portion is close to the inner peripheral surface, the frictional force can be efficiently generated and transmitted to the brake shoe. In addition, when the friction member is pressed against the inner peripheral surface on the entire circumference, the pressure contact force may vary due to the error in the diameter of the friction member and the inner peripheral surface, or the friction member may be distorted. Since the portion partially contacts the inner peripheral surface, a stable friction force can be generated.

In the brake device described above, the engaging portion can be provided so as to protrude from the ring portion in the axial direction of the output side rotating member.

In the brake device described above, it is desirable that the pressure contact portion and the engagement portion are arranged at the same position in the circumferential direction.

According to such a configuration, the auxiliary brake force due to the frictional force generated at the press contact portion can be efficiently transmitted to the brake shoe through a short path.

In the brake device described above, it is desirable that the friction member has a fitting portion that is fitted to the output side rotating member.

According to such a configuration, the fitting portion can be fitted to the output side rotating member, and the friction member can be temporarily assembled to the output side rotating member, so that the assembly of the brake device is facilitated.

In the brake device having the fitting portion described above, it is desirable that the friction member has a bent connecting portion that connects the fitting portion and the ring portion.

In this way, since the connecting portion that connects the fitting portion and the ring portion is bent, the connecting portion is easily bent, and thus the ring portion and the fitting portion are subjected to a force that is shifted in the rotational direction. Even if it is a case, an excessive force is not applied to a connection part.

In the brake device described above, the brake shoe has a pair of projecting portions projecting radially outward, each brake surface is provided on the projecting portion, and the engaging portion is a pair of projecting portions of one brake shoe. It can be set as the structure arrange | positioned between.

According to such a configuration, since the space between the projecting portions is used for the arrangement of the engaging portions, an increase in the size of the brake device can be suppressed.

In the brake device described above, a movable piece disposed between the inner side surface and the opposed surface, and a biasing member that biases the movable piece to a narrow side of a space formed between the inner side surface and the opposed surface. Furthermore, it can be set as the structure provided.

In the brake device described above, the friction member may be made of resin.

Since the friction member can be provided with the press contact portion and the engagement portion close to each other, the friction member can be made of a resin that is a material having no high strength. Thereby, it can suppress that a sound generate | occur | produces at the time of the action | operation of a brake device.

Further, in the brake device described above, the friction member is a restricting portion provided so as to protrude in the axial direction of the output-side rotating member, and is provided between the plurality of brake shoes and the positional relationship between the plurality of brake shoes. It is possible to further have a restricting part for restricting the above.

According to such a configuration, the positional relationship between the plurality of brake shoes is stabilized, the variation in the operation force is reduced, and the operation feeling can be improved.

In order to achieve the above object, a clutch unit of the present invention includes a brake device and a ratchet device, and the ratchet device is capable of rotating from a neutral position within a predetermined angle range, the operation input member, A second movable piece that is disposed between the input-side rotating members and transmits the rotational torque of the operation input member to the input-side rotating member, and biases the second movable piece to place the operation input member in a neutral position. And a second return spring that has one end engaged with the spring engaging portion of the operation input member and urges the operation input member toward the neutral position. The first return spring and the second return spring are located on one plane orthogonal to the rotation axis of the operation input member.

According to such a configuration, the operation input member can be returned to the neutral position with sufficient force by providing the second return spring in addition to the first return spring. The first return spring and the second return spring are located on one plane perpendicular to the rotation axis of the operation input member, so that the first return spring and the second return spring generate a force that squeezes the operation input member. Without the operation, the operation input member can be smoothly returned to the neutral position.

In the ratchet device described above, it is desirable that a wall portion be disposed between the first return spring and the second return spring.

Since the wall portion is arranged between the first return spring and the second return spring in this way, the first return spring and the second return spring do not interfere with each other, and the operation input member is smoothly returned to the neutral position. be able to.

The above-described ratchet device can include a housing that accommodates the operation input member, the input side rotation member, the second movable piece, and the first return spring. The second return spring is preferably disposed closer to the rotation axis than the first return spring and is accommodated in the housing.

According to such a configuration, the second return spring can be accommodated in the housing, and an increase in the size of the ratchet device can be suppressed.

In the ratchet device having the housing described above, the operation input member may have an operation lever attachment portion, and the spring engagement portion may be arranged at a position different from the attachment portion in the rotation direction of the operation input member.

According to such a configuration, since the operation input member has the attachment portion and the spring engagement portion at different positions in the rotation direction, it is possible to suppress an increase in size in the radial direction. Thereby, the enlargement of a ratchet apparatus can be suppressed.

The ratchet device having the housing described above can further include a regulating member that regulates the position of the second movable piece. In this case, the restricting member is provided on one side of the second movable piece in the rotation axis direction of the operation input member, and is provided to protrude from the side wall portion to the other side in the rotation axis direction. A restricting portion disposed adjacent to the second movable piece in the rotation direction of the member, and a protrusion protruding from the side wall portion to the other side in the rotation axis direction, the other end of the second return spring being hooked And a stop.

According to such a configuration, since the restricting member includes both the restricting portion and the latching portion, an increase in the size of the ratchet device can be suppressed.

In the ratchet device described above, the first return spring may be a compression spring and the second return spring may be a torsion spring.

It is a side view of a vehicle seat. It is a disassembled perspective view of a clutch unit. It is a cross-sectional view of a brake device. It is an enlarged view (a) near the inner surface of the brake shoe, and an enlarged view (b) near the opposing surface of the output side rotating member. It is a figure which shows the relationship between the rotation angle of an output side rotation member, and a clamping angle. FIG. 4 is a ZZ sectional view of the clutch unit of FIG. It is the figure which looked at the input side rotation member from the output side. It is the figure which looked at the friction member from the input side. It is the perspective view which looked at the clutch unit from the cover member side. It is a cross-sectional view of a ratchet device. It is a figure explaining operation | movement of a ratchet apparatus, and shows the case where an operation input member is rotated clockwise. It is a figure explaining operation | movement of a ratchet apparatus, and shows the case where an operation input member is returned counterclockwise. It is a figure explaining operation | movement of a brake device, and shows the case where clockwise rotation torque is given to the output side rotation member. It is a figure explaining operation | movement of a brake device, and shows the case where a counterclockwise rotational torque is given to the input side rotation member from the state of FIG. It is a figure explaining operation | movement of a brake device, and shows the case where clockwise rotational torque is given to the input side rotation member from the state of FIG. FIG. 16 is a diagram for explaining the operation of the brake device, and shows a state in which the input side rotation member is further rotated clockwise from the state of FIG. 15. It is a figure explaining operation | movement of a brake device, and shows the state which gave the excessive rotational torque of the clockwise direction to the output side rotation member. It is a cross-sectional view of a brake device according to a first modification. It is a perspective view of the friction member of the brake device concerning the 2nd modification. It is sectional drawing of the brake device of the state which assembled the friction member of the 2nd modification. It is a disassembled perspective view of the clutch apparatus which concerns on the modification which changed a part of ratchet apparatus. It is a longitudinal cross-sectional view of the clutch unit of a modification. It is a transverse cross section of a ratchet device in a clutch unit of a modification. It is a figure explaining operation | movement of the ratchet apparatus in the clutch unit of a modification, and shows the case where an operation input member is rotated clockwise. It is a figure explaining operation | movement of the ratchet apparatus in the clutch unit of a modification, and shows the case where an operation input member is returned counterclockwise.

Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
As shown in FIG. 1, a clutch unit 1 according to an embodiment including the brake device of the present invention is a known height adjuster for adjusting the height of a seat cushion S1 of a vehicle seat S as an example of a vehicle seat. Applies to the mechanism. In the clutch unit 1, a lever LV is attached to the operation input member 50, and the height of the seat cushion S 1 can be adjusted by driving a height adjustment mechanism by rotating an output side rotation member 30 described later by operating the lever LV. is there. Specifically, when the lever LV is raised from the neutral position N, the seat cushion S1 is raised by a predetermined amount, and when the lever LV is lowered from the neutral position N, the seat cushion S1 is lowered by a predetermined amount. When the lever LV is returned from the upper or lower position to the neutral position N, the output-side rotating member 30 is not rotated.

As shown in FIG. 2, the clutch unit 1 is configured by housing each member in a housing 100. The housing 100 is configured by a combination of the outer ring 10, the mounting plate 85 and the cover member 60. In the following description, the left side in FIG. 2 where the cover member 60 and the operation input member 50 are arranged is referred to as “input side”, and the right side in FIG. 2 where the output side rotation member 30 is arranged is referred to as “output side”. Called.

The clutch unit 1 is provided on the input side, and transmits and blocks the input torque generated by the swinging operation of the operation input member 50. The clutch unit 1 is provided on the output side, and the input torque from the ratchet device 2 is output to the output side rotating member. 30 and a brake device 3 for cutting off the reverse input torque from the output gear 35.

The outline of the components of the ratchet device 2 and the brake device 3 will be described. The ratchet device 2 includes an operation input member 50, a regulating member 71, a roller 72 as an example of a second movable piece, a first return spring 73, The second return spring 74 and the spring engaging member 75 are provided. The brake device 3 includes an outer ring 10, a brake shoe 20, an output-side rotating member 30, an input-side rotating member 40 as an example of a rotating member, a roller 81 as an example of a first movable piece, and a spring 82. And a friction member 90 and a washer 76. The input side rotating member 40 is an output member of the ratchet device 2 and an input member of the brake device 3, and can be referred to as any part of the ratchet device 2 and the brake device 3.

Next, details of the configurations of the brake device 3 and the ratchet device 2 will be described.
First, the configuration of the brake device 3 will be described.
The outer ring 10 is formed of a ring having a predetermined thickness, and includes a cylindrical inner peripheral surface 11, a cylindrical outer peripheral surface 12, and a pair of side surfaces 13 and 14 that connect the inner peripheral surface 11 and the outer peripheral surface 12. Yes. The pair of side surfaces 13 and 14 are located on the radially outer side of the outer ring 10 with respect to the inner peripheral surface 11, and are flat surfaces orthogonal to the axis of the inner peripheral surface 11. In the present specification, the radial direction and the circumferential direction are based on the outer ring 10.

The mounting plate 85 that constitutes a part of the housing 100 together with the outer ring 10 is a sheet metal member for supporting the brake device 3. The attachment plate 85 is formed with two attachment holes 85B for attaching the brake device 3 to the frame of the seat cushion S1. In addition, the mounting plate 85 has a through hole 85 A through which the output side rotation member 30 is passed. Since the outer ring 10 is fixed to the attachment plate 85, the clutch unit 1 can be attached to various devices.

The outer ring 10 is formed by punching a thick plate by press forming, and is welded to the input side surface of the mounting plate 85 at the outer peripheral edge 14B of the output side surface 14 by laser welding.

The brake shoes 20 are members that generate a braking force between the outer ring 10 and three brake shoes 20 are arranged on the inner side in the radial direction of the outer ring 10 at equal intervals in the circumferential direction. The brake shoe 20 includes a main body portion 20A that extends in the circumferential direction, and a protruding portion 20B and a protrusion 20C that protrude outward in the radial direction on the outer periphery of the main body portion 20A.

One protrusion 20B is provided at each circumferential end of the outer periphery of the main body 20A. Each protrusion 20 B has a brake surface 21 that faces the inner peripheral surface 11 of the outer ring 10 and can contact the inner peripheral surface 11 at the distal end on the radially outer side. The brake surface 21 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10 and contacts the inner peripheral surface 11 of the outer ring 10 near the outer side in the circumferential direction of the brake surface 21 as shown in FIG. Are arranged as follows. Thereby, when the brake shoe 20 is urged radially outward, the contact portion in the vicinity of the outer periphery in the circumferential direction of the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10.

The protrusion 20C is provided at the circumferential center of the outer periphery of the main body 20A. A support surface 26 capable of abutting on the inner peripheral surface 11 of the outer ring 10 is provided at the radially outer end of the protrusion 20C. In other words, the support surface 26 is provided at the center between the pair of brake surfaces 21. The support surface 26 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10, and has a cylindrical surface shape along the inner peripheral surface 11 of the outer ring 10. The support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10 in a state where no load is applied to the brake shoe 20 and the output-side rotating member 30.

The brake shoe 20 includes a cylindrical outer peripheral surface having a smaller diameter than the brake surface 21 between one of the pair of brake surfaces 21 and the support surface 26 and between the other of the pair of brake surfaces 21 and the support surface 26. 22. Further, the brake shoe 20 has an inner side surface 23 facing inward in the radial direction. And the brake shoe 20 has the end surface 24 which connects the both ends of the inner surface 23, and the edge part 21E of the two brake surfaces 21 in the edge part of the circumferential direction. Further, the brake shoe 20 has a rotational force input surface 25 facing the circumferential direction at a step between the brake surface 21 and the outer peripheral surface 22.

The support surface 26 is at least partially within the same range as the pair of brake surfaces 21 in the axial direction of the output side rotation member 30. That is, there is at least one plane orthogonal to the output side rotation member 30 that passes through the pair of brake surfaces 21 and the support surface 26 together. In the present embodiment, the thickness of the pair of protrusions 20B and the thickness of the protrusions 20C are substantially equal (see FIG. 2), and the support surface 26 in the axial direction of the output-side rotating member 30 is substantially the entire pair. Within the same range as the brake surface 21.

Each of the inner side surfaces 23 has three surfaces that are opposed to a later-described facing surface 36 of the output side rotating member 30. Specifically, as shown in FIG. 4A, the inner side surface 23 includes a first contact surface 23A, a first inclined surface 23B disposed on the counterclockwise side of the drawing with respect to the first contact surface 23A, It has the 1st inclined surface 23C arrange | positioned with respect to the 1st contact surface 23A in the clockwise direction of a figure. 23 A of 1st contact surfaces can contact with the roller 81, and the direction along the straight line L1 (refer FIG. 3) which connected both the edge parts 21E of the circumferential direction of a pair of brake surface 21 (refer FIG. 4 (FIG. 4). The plane is parallel to the connection direction indicated by the arrow in a). The first

inclined surfaces

23B and 23C are flat surfaces that are inclined with respect to the first contact surface 23A so as to approach the facing surface 36 (the lower side in the figure) as they move away from the first contact surface 23A between them. .

As shown in FIG. 2, the output side rotation member 30 includes a shaft-like action part 31, a flange 32 formed on the output side of the action part 31, and projects from the action part 31 to the input side. A coaxial and small-diameter support shaft portion 33, protrudes from the support shaft portion 33 to the input side, is coaxial with the support shaft portion 33, has a small-diameter shaft portion 37, and protrudes to the output side of the flange 32. An output gear 35 is provided. The output side rotation member 30 is disposed on the radially inner side of each brake shoe 20. The output gear 35 protrudes to the output side through the through hole 85 A of the mounting plate 85.

As shown in FIG. 3, the action portion 31 has a facing surface 36 facing the inner side surface 23 of the brake shoe 20 and a curved surface portion 38 on the outer periphery thereof. Three opposing surfaces 36 are provided on the outer periphery of the action portion 31 corresponding to the inner surface 23 of each brake shoe 20. Further, the curved surface portion 38 is a portion that connects the facing surfaces 36 corresponding to the brake shoes 20, and there is a total of 3 one pair between the facing surfaces 36 adjacent to each other in the circumferential direction of the outer periphery of the action portion 31. One is provided. The curved surface portion 38 is formed as a curved surface having a circular arc shape in sectional view with the rotation center of the output side rotation member 30 as the center.

As shown in FIG. 4B, the facing surface 36 includes second contact surfaces 36 A and 36 B arranged one by one on both ends of the facing surface 36 in the circumferential direction, and each second contact on both ends. A connecting surface portion 36C that connects the

surfaces

36A and 36B. The second contact surface 36A is disposed on the counterclockwise side in the drawing with respect to the connection surface portion 36C, and the second contact surface 36B is disposed on the clockwise side in the drawing with respect to the connection surface portion 36C.

The second contact surfaces 36A and 36B are capable of contacting the roller 81 in a state where no load is applied to the brake shoe 20, and are inclined with respect to the first contact surface 23A and outside the inclined portion 361. And a curved surface portion 362 arranged continuously. The inclined portion 361 is inclined so as to approach the first contact surface 23A (the upper side in the drawing) as it moves away from the reference plane PL orthogonal to the first contact surface 23A through the center 11C of the inner peripheral surface 11 of the outer ring 10. . Further, the curved surface portion 362 is a convex shape that is convex toward the brake shoe 20 when viewed along the axial direction of the output-side rotating member 30, and the curved surface has a curvature radius that decreases as the distance from the reference plane PL increases. Yes. By having such second contact surfaces 36 A and 36 B, the facing surface 36 includes a portion non-parallel to the first contact surface 23 A that is a part of the inner surface 23 of the brake shoe 20.

As shown in FIG. 5, the second contact surfaces 36A and 36B are formed by the first contact surface 23A and the tangential plane of the second contact surfaces 36A and 36B at the point where the second contact surfaces 36A and 36B contact the roller 81. The pinching angle α (see FIG. 3 for the pinching angle α) increases and then decreases as the rotation angle of the output side rotation member 30 increases when the rotation torque is input to the output side rotation member 30. It is formed as follows. When the sandwiching angle α exceeds 7.55 degrees, the roller 81 slides between the first contact surface 23A and the second contact surfaces 36A, 36B, and the first contact surface 23A and the second contact surfaces 36A, 36B It is desirable that the maximum value is 7.55 degrees or less because it is easy to move to the wide side of the space between.

As shown in FIG. 4B, the connection surface portion 36C has a flat surface portion 36D provided at the center portion in the circumferential direction and inclined portions 36E provided at both end portions in the circumferential direction. The plane portion 36D is a plane orthogonal to the reference plane PL in a state where no load is input to the brake shoe 20 and the output side rotating member 30. Accordingly, the flat portion 36D is arranged in parallel with the first contact surface 23A in a state where no load is input to the brake shoe 20 and the output-side rotating member 30. The inclined portion 36E is inclined so as to be away from the first contact surface 23A from the end of the flat surface portion 36D toward the inner end in the circumferential direction of the second contact surfaces 36A and 36B as the distance from the reference plane PL increases. Yes. Thereby, the opposing surface 36 is a recessed portion formed by the end portion on the inner side in the circumferential direction of the second contact surfaces 36A and 36B and the inclined portion 36E at the connection portion between the second contact surfaces 36A and 36B and the connection surface portion 36C. 36F. In the state where no load is input to the brake shoe 20 and the output-side rotating member 30, the distance between the first contact surface 23A and the connection surface portion 36C (plane portion 36D) is smaller than the diameter of the roller 81. But the space | interval of the 1st contact surface 23A and the connection surface part 36C may be more than the diameter of the roller 81. FIG.

As shown in FIG. 3, a pair of rollers 81 is disposed between the inner surface 23 of each brake shoe 20 and each opposing surface 36 of the output side rotating member 30. Here, of the pair of rollers disposed between each inner surface 23 and each facing surface 36, the roller 81A is the one disposed on the counterclockwise side in FIG. 3 and the one disposed on the clockwise side in FIG. Let it be a roller 81B. In a state in which no load is applied to the brake shoe 20 and the output-side rotating member 30, the roller 81A is in contact with the first contact surface 23A and the second contact surface 36A, and the roller 81B is in contact with the first contact surface 23A. These are in contact with each other in a state of being sandwiched between the contact surface 23A and the second contact surface 36B. As described above, the roller 81 is disposed between the inner surface 23 and the facing surface 36, so that in the brake device 3, a load is transmitted between the inner surface 23 and the facing surface 36 via the roller 81. .

The springs 82 are compression coil springs, and are provided one by one between the pair of

rollers

81A and 81B. The spring 82 urges the pair of rollers 81 A and 81 B toward the narrow side of the space formed between the inner surface 23 and the facing surface 36 by separating them in the circumferential direction.

When the inner side surface 23 and the opposite surface 36 are given rotational torque to the brake shoe 20 by the input side rotation member 40, the inner side surface 23 pushes the opposite surface 36 via the roller 81 and the output side rotation member 30 is rotated. Even when rotational torque is applied to the rotating member 30, the opposing surface 36 presses the inner side surface 23 via the roller 81 and the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10, so that the brake shoe 20 does not rotate. Has been. That is, the second contact surface 23 A with respect to the first contact surface 23 A so that the first contact surface 23 A of the inner surface 23 and the second contact surfaces 36 A and 36 B of the opposing surface 36 are in contact with each other so The inclination angles and positions of the contact surfaces 36A and 36B are adjusted.

The input side rotating member 40 shown in FIG. 2 can rotate around the axes of the outer ring 10 and the output side rotating member 30, receives the rotational output of the ratchet device 2, and hits the brake shoe 20 of the brake device 3 in the circumferential direction. It is a member that can contact and give rotational torque to the brake shoe 20. The input-side rotating member 40 includes a cylindrical pressure-receiving ring portion 41, a plurality of engagement legs 42 that protrude from the pressure-receiving ring portion 41 toward the output side, and a radially inner side from the vicinity of the axial center of the pressure-receiving ring portion 41. A plate-like portion 43 extending toward the output side, a holding portion 44 (see FIG. 7) extending from the output-side surface of the plate-like portion 43 toward the output side, and a through-hole 45 formed at the center of the plate-like portion 43. Configured. The inner peripheral surface 41A of the pressure receiving ring portion 41 has a circular cross section.

Three pairs of engagement legs 42 are provided at equal intervals corresponding to each brake shoe 20, and are arranged between the inner peripheral surface 11 of the outer ring 10 and the outer peripheral surface 22 of the brake shoe 20. As shown in FIG. 3, the pair of engaging legs 42 includes an engaging leg 42A disposed between the protrusion 20C and the anticlockwise protrusion 20B of FIG. 3, and the protrusion 20C and the clockwise protrusion of FIG. The engaging leg 42B is disposed between the portions 20B. Between the protrusion 20B and the protrusion 20C and the

engagement legs

42A and 42B, the sizes of the protrusion 20B, the protrusion 20C and the

engagement legs

42A and 42B are set so that slight play can be made in the circumferential direction. . Each

engagement leg

42A, 42B is formed in substantially the same shape.

The holding portion 44 is a portion that suppresses the roller 81 from falling off between the inner surface 23 and the facing surface 36, and is disposed adjacent to the circumferential direction of the roller 81. Specifically, a pair of

rollers

81A and 81B corresponding to each brake shoe 20 are disposed adjacent to both sides in the circumferential direction, and a total of three are provided.

The holding portion 44 is disposed away from the roller 81 in a state where no load is input to the input side rotating member 40 and the output side rotating member 30. More specifically, the holding unit 44 is a roller 81 adjacent to the upstream side in the rotation direction of the rotation torque in a state where the rotation torque in the normal use range is input to the output side rotation member 30. It arrange | positions so that it may be non-contact with respect to 81B.

In addition, the holding unit 44 rotates the input-side rotating member 40 in the same rotational direction as the rotational torque of the output-side rotating member 30 from the state where the rotating torque is input to the output-side rotating member 30, so At the time of contact in the direction, the roller 81 adjacent to the downstream side in the rotation direction, in this embodiment, is arranged so as not to contact the roller 81A.

Further, the holding portion 44 contacts the roller 81 adjacent to the downstream side in the rotation direction of the holding portion 44 in a state where the input-side rotating member 40 is in contact with the brake shoe 20 in the circumferential direction to rotate the brake shoe 20. Are arranged to be. However, the holding portion 44 may be in non-contact with the roller 81 in a state where the brake shoe 20 is rotated by the input side rotation member 40.

As shown in FIG. 7, the through hole 45 allows the action part 31 of the output side rotation member 30 to be inserted, and on its inner periphery, three circumferential surface parts 46 along the curved surface part 38 of the action part 31, and It has 3 convex surface parts 47 which are arrange | positioned between each circumferential surface part 46, and protruded to radial direction inner side with respect to the circumferential surface part 46. As shown in FIG. Each convex surface portion 47 includes a top portion 47A that protrudes inward in the radial direction, a release surface 47B that is adjacent to the top portion 47A on the clockwise side in FIG. 7 (counterclockwise side in FIG. 3), and a counterclockwise direction in FIG. And a flank 47C adjacent to the rotation side (clockwise side in FIG. 3).

The release surface 47B is arranged to face the facing surface 36, and the input of the clockwise rotational torque in FIG. 3 to the output side rotating member 30 due to the weight of the occupant sitting on the vehicle seat S is input. When the side rotation member 40 is rotated in the rotation direction opposite to the rotation torque (counterclockwise direction in FIG. 3) and brought into contact with the brake shoe 20 in the circumferential direction, the counter surface 36 rotates in the opposite direction substantially simultaneously. It has a shape that can transmit rotational torque in the direction.

The clearance surface 47C has an angle of the release surface 47B with respect to the flat surface portion 36D (see FIG. 4) of the opposing surface 36 in a state in which no load is input from the outside to the input side rotation member 40 and the output side rotation member 30. A shape that is larger than the angle with respect to the flat surface portion 36D and that does not contact the flat surface portion 36D when the input side rotation member 40 is rotated clockwise in FIG. It has become. However, the flank 47C has the same angle with respect to the flat surface portion 36D as the angle with respect to the flat surface portion 36D of the release surface 47B, and the release surface 47B in the clockwise direction of the input side rotation member 40 in FIG. It may have the same function.

As shown in FIG. 2, the friction member 90 is a member that generates friction for suppressing the operation of the output-side rotating member 30 from abruptly starting at the moment when the braking force of the brake device 3 is broken.
As shown in FIG. 8, the friction member 90 includes a ring portion 91 disposed closer to the inner peripheral surface 11 of the outer ring 10 than the action portion 31 of the output side rotating member 30, and an output side rotating member than the ring portion 91. A ring-shaped fitting portion 92 located near the rotation axis 30, a bent connecting portion 93 that connects the ring portion 91 and the fitting portion 92, and a pressure contact portion and an engaging portion that protrude from the ring portion 91. And a protrusion 94 as an example.

The protruding portion 94 protrudes on the radially outer side of the outer ring 10 and on the input side in the axial direction of the output side rotating member 30. The protruding portion 94 is a pressure contact surface 94 A in which a radially outer surface is pressed against the inner peripheral surface 11 of the outer ring 10. The diameter of the pressure contact surface 94 A is slightly larger than the inner diameter of the inner peripheral surface 11. On the other hand, the outer peripheral surface 91 A other than the projecting portion 94 of the ring portion 91 has a diameter smaller than the inner diameter of the inner peripheral surface 11 of the outer ring 10. For this reason, when the friction member 90 is combined with the outer ring 10, only the pressure contact surface 94 A is in pressure contact with the inner peripheral surface 11, and the outer peripheral surface 91 A is separated from the inner peripheral surface 11.

Further, in the protruding portion 94, a portion protruding in the axial direction from the ring portion 91 is engaged with the brake shoe 20 in the circumferential direction. The protrusion 94 is disposed between the pair of protrusions 20 B in one brake shoe 20. More specifically, the protrusion 94 is a first protrusion 94X disposed between the protrusion 20C of the brake shoe 20 and the protrusion 20B disposed on the clockwise side of FIG. 3 with respect to the protrusion 20C. And a protrusion 20C of the brake shoe 20 and a second protrusion 94Y disposed between the protrusion 20C and the protrusion 20B disposed counterclockwise in FIG. The first protrusion 94X has a first engagement surface 94B at the end in the clockwise direction of FIG. 8, and the second protrusion 94Y has a second engagement surface at the end in the counterclockwise direction of FIG. 94C. As shown in FIG. 3, the first engaging surface 94B and the second engaging surface 94C are both input to the rotational force of the protruding portion 20B of the brake shoe 20 when no load is input to the input-side rotating member 40. Separated from the surface 25. It is desirable that the gap between the first engagement surface 94B and the second engagement surface 94C and the rotational force input surface 25 be as small as possible within a range that does not hinder the combination of the brake shoe 20 and the friction member 90. In FIG. 3, the friction member 90 is shown only in the vicinity of the ring portion 91 on the outer peripheral portion.

In the present embodiment, both the pressure contact portion and the engagement portion are realized by the protruding portion 94. That is, the press contact portion and the engagement portion are arranged at the same position in the circumferential direction.

The fitting portion 92 has a fitting hole 92 A having the same shape as the contour of the cross section of the action portion 31, and the action portion 31 and the fitting hole 92 A are fitted to each other so as to be relative to the output side rotation member 30. It is designed not to rotate.

The connecting portion 93 has a meandering shape that is meandering. Specifically, the connecting portion 93 connects the U-shaped portion 93A that opens in the clockwise direction in FIG. 8 in the circumferential direction and the radially inner end of the U-shaped portion 93A to the fitting portion 92. It has 1 connection part 93B and 2nd connection part 93C which connects the edge part of the radial direction outer side of U-shaped part 93A with the ring part 91. As shown in FIG. Since the connecting portion 93 is bent in this manner, the connecting portion 93 is easily bent. Therefore, even if the ring portion 91 and the fitting portion 92 are subjected to forces that are shifted from each other in the rotational direction, the connecting portion 93 is connected. Since the portion 93 is bent, an excessive force is not applied to the connecting portion 93, and damage can be suppressed.

Although the material which comprises the friction member 90 is not specifically limited, The friction member 90 consists of resin, for example. If the friction member 90 is made of resin, a complicated shape can be easily formed, and since the sound is hardly generated when sliding with the inner peripheral surface 11, the operation of the brake device 3 can be made quiet.

The friction member 90 is disposed on the output side of the brake shoe 20. The friction member 90 is press-fitted inside the outer ring 10, and each protrusion 94 is disposed between the protrusion 20 B and the protrusion 20 C of the brake shoe 20.

The washer 76 has a hole 76A having a diameter slightly smaller than the outer diameter of the shaft portion 37 of the output-side rotating member 30, and the hole 76A is press-fitted into the shaft portion 37 (see FIG. 6). The outer diameter of the washer 76 is larger than a support hole 64 of the cover member 60 described later, so that the output-side rotating member 30 cannot be pulled out to the output side by the washer 76.

Next, the configuration of the ratchet device 2 will be described.
As shown in FIG. 2, the operation input member 50 engages with the lever LV and can be rotated together with the lever LV within a predetermined angle range from the neutral position. The operation input member 50 is a member that transmits the rotational torque from the lever LV to the input side rotating member 40 via the roller 72 by moving integrally with the input side rotating member 40 via the roller 72. For this reason, the operation input member 50 includes a cam plate portion 51 and two lever engaging portions 52 as attachment portions of the lever LV extending from the cam plate portion 51 to the input side.

As shown in FIG. 10, the cam plate portion 51 has three arc-shaped small-diameter portions 53 and three arc-shaped large-diameter portions 54 arranged alternately on the outer peripheral surface, and the small-diameter portion 53 and the large-diameter portion 54. Are connected to a flat opposing surface 55. Since there are six places where the small-diameter portion 53 and the large-diameter portion 54 are switched, six opposing surfaces 55 are formed correspondingly. The facing surface 55 is formed so that the distance from the central axis gradually changes. In addition, a hole 56 through which the output side rotation member 30 passes is formed at the center of the cam plate portion 51.

A roller 72 is disposed between each facing surface 55 and the inner peripheral surface 41A of the pressure receiving ring portion 41, respectively. As will be understood from the description of the operation described later, the roller 72 engages and disengages the operation input member 50 and the input side rotation member 40 to transmit and block input torque. A total of six rollers 72 are arranged corresponding to the opposing surfaces 55. As shown in FIG. 6, the facing surface 55 is longer in the direction than half of the axial length of the roller 72, and contacts the roller 72 in a range including the central portion (refer to the center line C 1) in the axial direction of the roller 72. Arranged to be possible. Thereby, the opposing surface 55 can stably hold the roller 72 between the pressure receiving ring portion 41.

Here, returning to FIG. 2, the regulating member 71 will be described. The regulating member 71 is a member that regulates the position of the roller 72, and one side of the operation input member 50 in the rotational axis direction with respect to the plurality of rollers 72. The side wall portion 71A disposed on the output side and the three regulating portions 71B extending from the outer peripheral edge of the side wall portion 71A toward the input side are configured. The restricting portion 71 B is longer than the length of the roller 72 in the axial direction, and its tip is press-fitted into the fitting hole 66 of the cover member 60. Further, the regulating member 71 has a hole 71 C through which the output side rotating member 30 passes at the center.

As shown in FIG. 10, the restricting portion 71 B is disposed at the same rotational position on the radially outer side of the large diameter portion 54 when the lever LV is not operated, and the opposing surface 55 and the pressure receiving ring portion 41. The movement of the roller 72 between them in the circumferential direction is restricted. A first return spring 73 made of a compression coil spring is disposed with an initial load applied between two rollers 72 disposed between the adjacent restricting portions 71B. For this reason, each roller 72 is in contact with the restricting portion 71B during the non-operation of FIG. Here, the restricting portion 71 B is disposed so as to include a position where the center of the roller 72 is located in the radial direction of the outer ring 10, and is in contact with the most protruding portion of the roller 72 in the circumferential direction. Thereby, the control part 71B can support the roller 72 stably. In FIG. 10, the roller 72 is shown in contact with the restricting portion 71B, but the roller 72 is slightly separated from the restricting portion 71B by being sandwiched between the opposing surface 55 and the inner peripheral surface 41A. It may be.

As shown in FIG. 2, the lever engaging portion 52 extends from the cam plate portion 51 with an arcuate cross section. Each lever engaging portion 52 has a screw hole 52A, and the lever LV is fixed using the screw hole 52A (not shown).

The cover member 60 includes a disk-shaped side wall portion 61, a cylindrical outer peripheral portion 62 as an example of a wall portion extending from the outer peripheral edge of the side wall portion 61 to the output side, and an end portion on the output side of the outer peripheral portion 62. The flange 63 extends radially outward, and extending

portions

67A and 67B of the flange 63 extending from the left and right end portions in FIG. 2 to the input side. The outer peripheral portion 62 is disposed between the first return spring 73 and the second return spring 74, thereby suppressing interference between the first return spring 73 and the second return spring 74. As shown in FIG. 6, the flange 63 is fitted to the side surface 13 of the outer ring 10, and is welded to the side surface 13 by laser welding along the outer peripheral edge thereof. The outer ring 10 is reinforced by welding the cover member 60 in this way. This welding is performed over the entire circumference of the flange 63.

As shown in FIG. 2, the side wall 61 has a circular support hole 64 at its center, two arc holes 65 extending in an arc shape around the support hole 64, and a position radially outside the arc hole 65. And three fitting holes 66 arranged at equal intervals in the circumferential direction are formed.
The support hole 64 is a portion that fits with the support shaft portion 33 of the output side rotation member 30 and pivotally supports the output side rotation member 30.
The arc hole 65 is provided corresponding to the lever engaging portion 52 of the operation input member 50, and is formed in an arc shape in a wider angle range than the lever engaging portion 52. As a result, the arc hole 65 receives the lever engaging portion 52, and the lever engaging portion 52 can move within the arc hole 65 within a predetermined angle range.

The fitting holes 66 are three through holes provided corresponding to the three regulating portions 71 B of the regulating member 71, and are fitted with the cover member 60 so that the regulating member 71 does not rotate relative to the cover member 60. Has been. Since the regulating member 71 and the cover member 60 are fitted at a plurality of locations, the regulation member 71 can be firmly regulated to rotate.

The one extending portion 67A is a portion that engages with the end portion of the second return spring 74.

The second return spring 74 includes a coil portion 74A, a first arm 74B extending radially outward from one end of the coil portion 74A, and a second arm 74C extending radially outward from the other end of the coil portion 74A. This is a torsion spring.

The coil portion 74A is disposed on the radially outer side of the outer peripheral portion 62 of the cover member 60, and is disposed on the radially inner side with respect to the extending

portions

67A and 67B. As shown in FIG. 6, the first return spring 73 and the second return spring 74 are on one plane orthogonal to the rotational axis of the operation input member 50, and in FIG. 6, on the plane passing through the center line C1. Located in.

As shown in FIG. 2, the spring engaging member 75 includes a main body portion 75 A that extends left and right in FIG. 2, and extending portions 75 B and 75 C that extend from the left and right ends to the output side in FIG. Have. The operation input member 50 is engaged with the second return spring 74 using the spring engagement member 75. The extending portion 75B is an example of a spring engaging portion of an operation input member that is engaged with the first arm 74B or the second arm 74C as an example of one end of the second return spring 74.
The main body portion 75A has a circular through hole 75D through which the support shaft portion 33 of the output side rotation member 30 passes and two engagement holes 75E with which the two lever engagement portions 52 of the operation input member 50 are engaged. It is formed in a connected state. The spring engagement member 75 can rotate integrally with the operation input member 50 by engaging the engagement hole 75E with the lever engagement portion 52. The main body portion 75A is positioned on the input side with respect to the coil portion 74A of the second return spring 74.

As shown in FIG. 9, the extending portion 75B has the same size as the extending portion 67A of the cover member 60 in the circumferential direction. The extending portion 75B is disposed on the radially inner side of the extending portion 67A at a position corresponding to the extending portion 67A in the circumferential direction. Further, the extending portion 75C has the same size as the extending portion 67B of the cover member 60 in the circumferential direction. And the extension part 75C is arrange | positioned in the radial direction inner side of the extension part 67B in the position corresponding to the extension part 67B of the cover member 60 in the circumferential direction. Furthermore, the coil portion 74A of the second return spring 74 is disposed on the radially inner side of the extending

portions

75B and 75C.

The first arm 74B and the second arm 74C of the second return spring 74 are engaged with the extending portion 67A of the cover member 60 and the extending portion 75B of the spring engaging member 75 in the rotational direction. In a state in which the operation input member 50 is not operated, the first arm 74B and the second arm 74C are urged toward each other to sandwich the extending portion 67A and the extending portion 75B. That is, the spring engaging member 75 is always urged toward the neutral position shown in FIG. 9 by the second return spring 74.
The main body 75A and the

extension portions

75B and 75C of the spring engaging member 75 surround the coil portion 74A together with the cover member 60, thereby preventing the coil portion 74A from coming off.

Next, the operation of the clutch unit 1 configured as described above will be described.
First, the operation of the ratchet device 2 will be described.
In the neutral position shown in FIG. 10, the roller 72 is located between the inner peripheral surface 41 A of the input side rotating member 40 and the facing surface 55 of the operation input member 50, but there is a slight gap between them. It is not pinched by. The roller 72 is urged toward the restricting portion 71B by a first return spring 73 made of a compression coil spring. Thereby, the first return spring 73 biases the posture of the operation input member 50 to the neutral position. In addition, the second return spring 74 sandwiches the extending portion 75B and the extending portion 67A between the first arm 74B and the second arm 74C. By this clamping force, the position of the extending portion 75B in the rotational direction is aligned with the extending portion 67A. That is, the second return spring 74 urges the postures of the spring engagement member 75 and the operation input member 50 to the neutral position.

When the lever LV is lowered from the neutral position and the operation input member 50 is slightly swung clockwise, the opposing surface 55 rotates clockwise to contact the roller 72, and the inner peripheral surface 41 A and the opposing surface 55 The roller 72 is sandwiched between them. Thereby, the operation input member 50 and the input side rotation member 40 can rotate integrally.
Therefore, as shown in FIG. 11, when the operation input member 50 is rotated clockwise, the input side rotation member 40 and the operation input member 50 are rotated clockwise while being integrated. That is, the input torque obtained by rotating the operation input member 50 is transmitted to the input side rotation member 40.

At this time, the extending portion 75B of the spring engaging member 75 moves the second arm 74C in the clockwise direction against the urging force of the second return spring 74. In other words, the second arm 74C biases the extending portion 75B in the counterclockwise direction.

When the lever LV is swung counterclockwise from the state shown in FIG. 11 and returned from the lower position to the neutral position, the facing surface 55 escapes counterclockwise from the roller 72, and the roller 72 moves to the inner surface of the facing surface 55. Since it is not clamped by the surface 41A, as shown in FIG. 12, the operation input member 50 is rotated toward the neutral position while the input side rotation member 40 is stationary. That is, the input torque when returning the operation input member 50 is not transmitted to the input side rotation member 40 but is blocked. The operation input member 50 is assisted to operate toward the neutral position by the urging force of the first return spring 73 and the second return spring 74, and is maintained at the neutral position.

The operation for raising the lever LV from the neutral position and returning the lever LV from the upper position to the neutral position is the same as that in the case of the downward swing described above, and a description thereof will be omitted.

Next, the operation of the brake device 3 will be described.
As shown in FIG. 13, when the output side rotation member 30 is given a clockwise rotation torque in the drawing, that is, a rotation torque in the normal use range, by the weight of the passenger sitting on the vehicle seat S, the output side rotation member 30 slightly rotates clockwise, and the distance between the second contact surface 36A (one of the pair of second contact surfaces 36A and 36B of the one opposing surface 36 on the counterclockwise side) and the first contact surface 23A is narrow. Thus, the pressures of the roller 81A (one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side), the second contact surface 36A, and the first contact surface 23A are increased. When the roller 81A is in contact with the first inclined surface 23B in a state where no load is input to the output-side rotating member 30, the roller 81A rolls between the facing surface 36 and the inner side surface 23, When it moves to a position in contact with the first contact surface 23A, the pressure between the second contact surface 36A and the first contact surface 23A is sufficiently increased and stops against the opposing surface 36 and the inner surface 23. On the other hand, as the output side rotation member 30 rotates clockwise, the second contact surface 36B (one of the pair of second contact surfaces 36A, 36B of the one opposing surface 36 on the clockwise side) and the first contact surface. Since the distance between the two contact surfaces 23A is increased, the roller 81B (one of the pair of rollers 81 corresponding to one brake shoe 20 on the clockwise side) is strongly sandwiched between the second contact surface 36B and the first contact surface 23A. You can roll without being caught.

At this time, the second contact surface 36A pushes the roller 81A with the force F1, and the roller 81A pushes the first contact surface 23A with the force F2. As a result, the brake shoe 20 has the pair of brake surfaces 21 pressed against the inner peripheral surface 11 of the outer ring 10 with the force F3. As a result, a frictional force is generated between the brake surface 21 and the inner peripheral surface 11, so that the output side rotating member 30 does not rotate. That is, a braking force that prevents the vehicle seat S from being lowered is generated. In such a state where the rotational torque in the normal use range is applied to the output side rotation member 30, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.

At this time, the roller 81B is slightly separated from the holding portion 44 adjacent in the rotation direction of the output side rotation member 30, that is, the clockwise direction. Therefore, not only the roller 81A is sandwiched between the facing surface 36 and the inner side surface 23, but also the roller 81B can be maintained between the facing surface 36 and the inner side surface 23 by the biasing force of the spring 82. Thereby, even if the brake shoe 20 is rotated in any direction thereafter, the frictional force between the brake shoe 20 and the outer ring 10 can be maintained, so that an unexpected release of the braking force can be suppressed.

When the input side rotating member 40 is rotated counterclockwise by operating the lever LV to raise the height of the vehicle seat S from the brake state of FIG. 13, as shown in FIG. 14, the input side rotating member 40. The engaging leg 42A contacts the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the end on the counterclockwise side. At this time, the release surface 47B of the input side rotation member 40 comes into contact with the flat surface portion 36D of the opposing surface 36 at substantially the same time, so that the counterclockwise rotation torque can be transmitted to the output side rotation member 30. As a result, even when the brake surface 21 of the brake shoe 20 is strongly pressed against the inner peripheral surface 11 of the outer ring 10, the brake force is released and the input side rotating member 40 is turned to start raising the vehicle seat S. It is possible to suppress the feeling of catching when.

Then, when the input side rotation member 40 is further rotated counterclockwise, the engagement leg 42A pushes the rotational force input surface 25 with the force F11, whereby the brake shoe 20 rotates counterclockwise, and the first contact surface 23A. Presses the roller 81A with the force F12, and the roller 81A presses the second contact surface 36A with the force F13. By this force F13, the output side rotation member 30 rotates counterclockwise in the figure. Also at this time, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.

In addition, when the input side rotating member 40 is rotated clockwise by operating the lever LV to lower the height of the vehicle seat S from the brake state of FIG. 13, as shown in FIG. 15, the input side rotating member Forty engagement legs 42B abut on the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the clockwise end. At this time, the holding portion 44 is not in contact with the roller 81A adjacent to the downstream side in the rotation direction (clockwise direction side). When the input side rotation member 40 is further rotated clockwise, the engaging leg 42B pushes the rotational force input surface 25 with the force F21, and the brake shoe 20 starts to rotate clockwise.

When the brake shoe 20 rotates in the clockwise direction from the state of FIG. 15, the brake shoe 20 and the output side rotating member 30 are relatively opposite to the case where the output side rotating member 30 is rotated in the clockwise direction in FIG. To work. That is, as shown in FIG. 16, the brake shoe 20 is slightly rotated clockwise, and the first contact surface 23A and the second contact surface 36B (the pair of second contact surfaces 36A and 36B of the one opposing surface 36 are clocked). By reducing the distance between the one on the rotation side), the roller 81B (one of the rollers 81 corresponding to one brake shoe 20 on the clockwise side), the first contact surface 23A and the second contact surface 36B. Increased pressure. Even when the roller 81B is in contact with the first inclined surface 23C, the roller 81B rolls between the opposing surface 36 and the inner side surface 23 and moves to a position in contact with the first contact surface 23A. The pressure between 36 B and the first contact surface 23 A is sufficiently increased and stops against the facing surface 36 and the inner surface 23. On the other hand, as the brake shoe 20 rotates clockwise, the first contact surface 23A and the second contact surface 36A (one of the pair of second contact surfaces 36A and 36B of the one opposing surface 36 on the counterclockwise side) Therefore, the roller 81A (one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side) is located between the first contact surface 23A and the second contact surface 36A. You can roll while the pressure of the water gradually decreases. In the state of FIG. 16, the holding unit 44 contacts the roller 81 A adjacent on the downstream side in the rotation direction and presses the roller 81 A in the clockwise direction.

Further, in the process of rotating the brake shoe 20 from the state of FIG. 15 to the state of FIG. 16, the gap between the protruding portion 20B of the brake shoe 20 and the second protruding portion 94Y of the friction member 90, that is, the protruding portion 20B is the second protruding portion. Engage with part 94Y and push clockwise. As a result, the friction member 90 rotates clockwise so as to be dragged by the brake shoe 20. At this time, the friction member 90 is in pressure contact with the inner peripheral surface 11 of the outer ring 10 at the protruding portion 94, and thus provides resistance (auxiliary brake force) to the rotation of the brake shoe 20. For this reason, before the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force, the force for sandwiching the roller 81A between the first contact surface 23A and the second contact surface 36A is weakened. Even so, the brake shoe 20 is prevented from suddenly rotating clockwise due to the weight of the occupant.

Further, in the state of FIG. 15, the holding portion 44 is not in contact with the roller 81A, so that the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force. Further, since the roller 81A that has generated the braking force is not pushed by the holding portion 44, the braking force is prevented from being unexpectedly weakened.

On the other hand, as shown in FIG. 16, after the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force, the holding portion 44 comes into contact with the roller 81A. Even in a case where the inner surface 23 and the facing surface 36 are fixed due to some circumstances, the roller 81A is separated from the inner surface 23 and the facing surface 36 to release the braking force, thereby realizing a stable operation. be able to.

Then, as shown in FIG. 16, the engaging leg 42B pushes the rotational force input surface 25 with the force F21, the first contact surface 23A pushes the roller 81B with the force F22, and the roller 81B pushes the second contact surface 36B with the force F23. Push. By this force F23, the output side rotation member 30 rotates clockwise in the figure. Also at this time, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.

On the other hand, when an excessively large rotational torque in the clockwise direction that is larger than the normal use range is input to the output side rotation member 30, as shown in FIG. The rotation member 30 rotates greatly in the clockwise direction, and the distance between the second contact surface 36A and the first contact surface 23A becomes narrower, so that the pressure on the roller 81A, the second contact surface 36A, and the first contact surface 23A is further increased. . At this time, the second contact surface 36A pushes the roller 81A with a large force F31, and the roller 81A pushes the first contact surface 23A with a large force F32. As a result, the brake shoe 20 is deformed so that the main body portion 20 A bends radially outward, and the support surface 26 contacts the inner peripheral surface 11 of the outer ring 10. As a result, the support surface 26 of the brake shoe 20 is supported by the outer ring 10, and further deformation is suppressed, so that the load on the brake shoe 20 can be reduced.

Further, when an excessive clockwise rotational torque is input and the output-side rotating member 30 is greatly rotated clockwise, the space between the second contact surface 36B and the first contact surface 23A widens, and the roller 81B You may play between these. In such a case, the roller 81B abuts on the holding portion 44 adjacent to the downstream side in the rotation direction, here, the clockwise direction. Thereby, since the holding part 44 supports the roller 81B, it is suppressed that the roller 81B falls out between the inner surface 23 and the opposing surface 36.

In the above description, the case where the input side rotating member 40 is rotated in the clockwise direction or the counterclockwise direction after the rotational torque in the clockwise direction is input to the output side rotating member 30 and the braking force is generated has been described. When the clutch unit 1 is applied to the vehicle seat S, only the rotational torque in the clockwise direction is input to the output-side rotating member 30 and thus operates only as described above. When the input side rotating member 40 is rotated clockwise or counterclockwise after a rotational torque in the counterclockwise direction is input to generate a braking force, the brake shoe 20 and the output side rotating member 30 are Since the mirror image is symmetrical (line symmetry in FIG. 3), substantially the same operation is realized only by the rotation direction being different from that described above.

According to the brake device 3 applied to the clutch unit 1 of the present embodiment described above, when rotational torque is applied to the output-side rotating member 30, the roller 81 pushes the inner side surface 23 of the brake shoe 20 so that the brake surface 21 is moved. The brake shoe 20 does not rotate by being pressed against the inner peripheral surface 11 of the outer ring 10. In this state, when the brake shoe 20 is rotated in one rotation direction or the other rotation direction by the input side rotation member 40, the roller 81 is formed between the inner surface 23 and the facing surface 36 of the output side rotation member 30. Since one of the rollers 81 is always sandwiched between the inner surface 23 and the facing surface 36, that is, in contact with these, since it is biased to the narrow side of the space, it can be maintained. For this reason, it can suppress that brake force falls off at a stretch. In addition, since the brake force can be generated by each of the plurality of brake shoes 20 arranged in the circumferential direction, it is possible to suppress an increase in the size of the brake device 3 in the axial direction. As a result, the size in the axial direction can be reduced, and stable operation can be performed.

In addition, the roller 81 is sandwiched between the first contact surface 23A of the inner surface 23 and the second contact surfaces 36A and 36B of the facing surface 36 that are inclined with respect to the first contact surface 23A, and comes into contact therewith. As a result, the roller 81 can be stably held and play of the roller 81 can be suppressed.

Even if the braking force generated on the brake surface 21 of the brake shoe 20 is reduced by the friction member 90 engaging with the brake shoe 20, the frictional force of the friction member 90 assists the brake shoe 20. Acts as a braking force. Therefore, even when the brake force of the brake shoe 20 is lowered when the vehicle seat S is lowered by the lever LV, the output-side rotating member 30 is prevented from rotating suddenly by the auxiliary brake force. can do. And since the protrusion part 94 provided in the outer peripheral part of the friction member 90 and the brake shoe 20 are engaging, the engaging part which engages with the part which generate | occur | produces a frictional force, and the brake shoe 20, and transmits force Therefore, the auxiliary brake force can be transmitted to the brake shoe 20 efficiently.

Further, since the ring portion 91 is close to the inner peripheral surface 11 of the outer ring 10, it can efficiently generate a frictional force and transmit it to the brake shoe 20. Further, when the friction member 90 is in pressure contact with the inner peripheral surface 11 on the entire outer periphery, the pressure contact force varies due to an error in the diameters of the friction member 90 and the inner peripheral surface 11, or the friction member 90 is distorted. Although it is easy to do, since it contacts the inner peripheral surface 11 partially in the protrusion part 94 among the outer periphery of the friction member 90, the stable frictional force can be generate | occur | produced.

In addition, since the press contact portion and the engagement portion of the friction member 90 are provided in the same protrusion 94 and are disposed at the same position in the circumferential direction, the auxiliary brake force due to the friction force generated in the protrusion 94 is short. The route can be efficiently transmitted to the brake shoe 20.

Further, since the friction member 90 has a fitting portion 92 that fits to the output side rotating member 30, the friction member 90 is fitted to the action portion 31 of the output side rotating member 30. The output side rotating member 30 can be temporarily assembled. Thereby, the assembly of the brake device 3 becomes easy.

Moreover, since the connection part 93 which connects the fitting part 92 and the ring part 91 is bent, the connection part 93 is easily bent, so that the ring part 91 and the fitting part 92 are shifted from each other in the rotation direction. Even if a force is applied, an unreasonable force is not applied to the connecting portion 93.

Further, the protrusion 94 is disposed between the protrusions 20B of the brake shoe 20, so that the space between the protrusions 20B can be effectively used and the increase in size of the brake device 3 can be suppressed.

Also, as described above, the friction member 90 in the present embodiment can efficiently transmit the frictional force to the brake shoe 20, and can be made of resin. Thereby, it can suppress that a sound generate | occur | produces at the time of the action | operation of the brake device 3. FIG.

Furthermore, the ratchet device 2 according to the present embodiment includes the second return spring 74 in addition to the first return spring 73, so that the operation input member 50 can be returned to the neutral position with a sufficient force. The first return spring 73 and the second return spring 74 are positioned on a single plane perpendicular to the rotation axis of the operation input member 50, so that the first return spring 73 and the second return spring 74 are operated by the operation input member. Therefore, the operation input member 50 can be smoothly returned to the neutral position without generating a force of 50.

In the ratchet device 2, the outer peripheral portion 62 of the cover member 60 is disposed as a wall portion between the first return spring 73 and the second return spring 74, so that the first return spring 73 and the second return spring 74 are arranged. Without interference, the operation input member 50 can be smoothly returned to the neutral position.

Although one embodiment of the present invention has been described above, the present invention is not limited to the above-described embodiment and can be appropriately modified and implemented.
For example, in the embodiment, the input side rotating member 40 rotates the output side rotating member 30 via the brake shoe 20 and the roller 81, but the input side rotating member 40 is directly related to the output side rotating member 30. In combination, the rotational torque may be transmitted. In this case, the shape of the through hole 45 of the input side rotation member 40 and the shape and arrangement of the engagement leg 42 are adjusted so that the engagement leg 42 is sufficiently engaged with the brake shoe 20 in the rotation direction before the through hole 45 is engaged. The 45 edges may be engaged to such an extent that a sufficient rotational torque is transmitted to the action portion 31 of the output side rotation member 30.

Further, the configuration for transmitting the force between the brake shoe 20 and the output side rotating member 30 can take various configurations. For example, in the above-described embodiment, the output-side rotating member 30 presses the brake shoe 20 radially outward via the roller 81 as the movable piece, but the movable piece may not be provided, and the output-side rotating member 30 may have a protrusion protruding radially outward, and the brake shoe 20 may be pressed by this protrusion.

In the above-described embodiment, when a rotational torque is applied to the output-side rotating member 30, the facing surface 36 is interposed via the roller 81 regardless of whether the rotational direction is the clockwise direction or the counterclockwise direction. Although the brake shoe 20 is configured not to rotate by pressing the inner side surface 23 and pressing the brake surface 21 against the inner peripheral surface 11 of the outer ring 10, it is not limited to this. For example, as shown in FIG. 18, when the roller 81B or the second contact surface 36B corresponding to the roller 81B is eliminated and rotational torque is applied to the output-side rotating member 30, one rotational direction, specifically, FIG. Only in the clockwise direction, the opposing surface 36 (second contact surface 36A) presses the inner side surface 23 (first contact surface 23A) through the roller 81A and the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10. The brake shoe 20 may be configured not to rotate. Note that the output-side rotating member 30 of the brake device 3 of FIG. 18 is provided with three engaging portions 39 that protrude radially outward. Thereby, when the output side rotation member 30 is rotated in the counterclockwise direction in the figure, the brake shoe 20 is rotated by the engagement portion 39 pushing the brake shoe 20 in the counterclockwise direction. ing.

Further, the friction member may have a shape as shown in the second modification of the brake device of FIGS. 19 and 20.
As shown in FIG. 19, the friction member 90 of this modification has three restricting portions 195 protruding to the input side. As shown in FIG. 20, the restricting portion 195 is disposed between the three brake shoes 20. The three restricting portions 195 are arranged at equal intervals in the circumferential direction and have the same size and shape. The restricting portion 195 has a role of restricting the positional relationship between the three brake shoes 20. The distance between each brake shoe 20 and the restricting portion 195 in a state where no load is input to the brake device 3 is, for example, 0 to 0.5 mm, preferably 0.1 to 0.4 mm. .3 mm can be set. The restricting portion 195 has a substantially trapezoidal shape in accordance with the triangular gap formed between the holding portion 44 and the two brake shoes 20, but the shape of the restricting portion 195 is not particularly limited.

Further, as shown in FIG. 19, the friction member 90 has connecting portions 193A to 193C having a shape different from that of the connecting portion 93 of the embodiment. The connection portion 93 of the above embodiment is provided with six U-shaped ones that open in the clockwise direction when viewed from the input side. However, in the friction member 90 of this modified example, the U-shape that opens in the clockwise direction is provided. Three U-shaped connecting portions 193A, three U-shaped connecting portions 193B that are arranged adjacent to each other in the clockwise direction of the three connecting portions 193A and that open in the counterclockwise direction, and a plate-shaped connection Part 193C. The connecting portion 193C is disposed between the connecting portion 193B and the connecting portion 193A adjacent to the connecting portion 193B in the clockwise direction.
The connecting

portions

193A and 193B have a thin shape that can be bent and deformed, and the connecting portion 193C has a wide plate shape that is not easily bent and deformed.

According to the friction member 90 in the second modified example having the above-described configuration, the positional relationship between the three brake shoes 20 is difficult to be shifted and stable, so that the braking force generated by the brake shoe 20 is stabilized. Further, since the positional relationship of the brake shoe 20 is stabilized, the load when releasing the braking force is also stabilized. For this reason, the variation of the operation force when the lever is operated is reduced, and the operation feeling can be improved.

In the above-described embodiment, the second return spring 74 is disposed outside the housing 100 on the outer side in the radial direction of the first return spring 73. However, the second return spring is an operation input member rather than the first return spring. It can also be set as the structure arrange | positioned near the 50 rotation axis line (diameter direction inner side), and accommodated in the housing. 21 to 25 are diagrams for explaining this modification.

As shown in FIG. 21, in the ratchet device 2 of this modification, a second return spring 174 having a small diameter is provided instead of the second return spring 74. The spring engaging member 75 is not provided.

The second return spring 174 has a coil portion 174A, a first arm 174B, and a second arm 174D. The coil portion 174 A has a diameter smaller than the diameter of the outer peripheral portion 62 of the cover member 60 and the hole 56 of the cam plate portion 51. The first arm 174B extends upward from the input side end of the coil portion 174A in FIG. The second arm 174D extends upward in FIG. 21 from the output side end of the coil portion 174A. The end 174C of the first arm 174B is bent toward the output side in the axial direction. The end 174E of the second arm 174D is bent toward the input side in the axial direction.

As shown in FIG. 22, the second return spring 174 is disposed inside the first return spring 73 in the radial direction, and the first return spring 73 and the second return spring 174 are on the rotation axis of the operation input member 50. On one orthogonal plane, in FIG. 22, it lies on a plane passing through the center line C1.

As shown in FIG. 21, the operation input member 50 has the lever engaging portion 52 located on the left and right in FIG. 21, and the arc hole 65 of the cover member 60 located at a position corresponding to the lever engaging portion 52. Yes. The cover member 60 is not provided with the extending

portions

67A and 67B, unlike the above embodiment.

The operation input member 50 is provided with a protruding portion 57 that protrudes radially inward from the upper and lower positions in FIG. 21 on the inner peripheral surface of the hole 56. That is, the protruding portion 57 is arranged at a position different from the lever engaging portion 52 in the rotation direction of the operation input member 50. Of the projecting portions 57, the upper projecting portion 57 is engaged with the first arm 174B and the second arm 174D of the second return spring 174. In this modification, the operation input member 50 is an example of a wall portion located between the first return spring 73 and the second return spring 174.

The restricting member 71 is provided with a protruding portion 71D that protrudes from the upper and lower positions in FIG. 21 to the input side, which is the other side in the rotation axis direction, of the periphery of the hole 71C. As shown in FIG. 23, the protrusion 71 D is located on the radially inner side of the protrusion 57 of the operation input member 50. Of the protrusions 71D, the upper protrusion 71D is an example of a latching part, and the first arm 174B and the second arm 174D of the second return spring 174 can be engaged with each other.

In the ratchet device 2 of the modified example configured as described above, as shown in FIG. 23, the first arm 174B and the second arm 174D sandwich the projecting portion 57 when the lever is not operated, and the projecting portion 57 The portion 71D is located between the first arm 174B and the second arm 174D. Thereby, the protrusion 57 is aligned with the position of the protrusion 71D. That is, the operation input member 50 (lever) is held at the neutral position.

23, when the lever is lowered, the first arm 174B is pushed and moved clockwise by the protrusion 57 as shown in FIG. On the other hand, the second arm 174D is engaged with the protrusion 71D and remains in the original position. In this state, the second return spring 174 urges the protruding portion 57 counterclockwise by the first arm 174B by the elastic recovery force. That is, the operation input member 50 is urged toward the neutral position.

When the lever is returned to the neutral position from the state of FIG. 24, the operation input member 50 rotates while being urged counterclockwise by the first arm 174B, and returns to the neutral position as shown in FIG. .

When the lever is raised from the neutral position and then returned to the lower position, the operation is the reverse of the above. The second arm 174D urges the protrusion 57 clockwise, and the operation input member 50 is urged toward the neutral position.

According to such a ratchet device 2, since the second return spring 174 is accommodated in the housing 100, the ratchet device 2 can be prevented from being enlarged in the radial direction.

Further, since the protruding portion 57 is arranged at a position different from the lever engaging portion 52 in the rotation direction of the input side rotating member 40, the operation input member 50 can be prevented from being enlarged.

Furthermore, since the restricting member 71 includes both the restricting portion 71B and the protruding portion 71D as the latching portion, it is possible to suppress an increase in the size of the ratchet device 2 as compared with the case where these are provided in different parts. .

In the embodiment, the roller 81B is not in contact with the holding portion 44 in a state where the rotational torque in the normal use range is applied to the output-side rotating member 30 (see FIG. 13). The roller 81B may be in contact with the holding unit 44. Even in this case, as the brake shoe 20 is rotated in the clockwise direction, while the other roller 81A is sandwiched between the opposing surface 36 and the inner side surface 23, the one roller 81B and the inner side surface 23 are opposed to each other. If the surface 36 can obtain a contact state, there is no practical problem.

In the above-described embodiment, in a state where no load is input to the output-side rotating member 30, or in a state where rotational torque in the normal use range is applied to the output-side rotating member 30 (see FIGS. 13 to 16). The support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10, but is not limited to this. For example, as long as the operation when the brake shoe rotates is not hindered, the support surface may be in contact with the inner peripheral surface in a state where the rotation torque in the normal use range is applied to the output side rotation member. Further, the support surface may not have a shape along the inner peripheral surface of the outer ring.

In the above embodiment, a compression coil spring is used as the first return spring 73 and a torsion spring is used as the second return spring 74. However, the types of these springs are not particularly limited.

In the above-described embodiment, the friction member 90 has the fitting portion 92 that is fitted to the output-side rotating member 30, but the fitting portion 92 may be omitted.

In the above embodiment, the roller 72 is exemplified as the second movable piece. However, the second movable piece may be a sphere, a polygonal column, or a column having an elliptical cross section. Similarly, the roller 81 exemplified as the first movable piece may have a spherical shape, a polygonal column, or a column shape with an elliptical cross section.

In the above embodiment, three brake shoes 20 are provided, but the number of brake shoes may be two or four or more.

In the above embodiment, the brake shoe 20 has the support surface 26 between the pair of brake surfaces 21, but the brake shoe has a configuration that does not include a support surface or a protrusion on which the support surface is provided. It doesn't matter.

In the embodiment, the pressure receiving ring portion 41 of the input side rotation member 40 is disposed on the radially outer side of the operation input member 50. However, the operation input member 50 has an inner peripheral surface by reversing this. The input-side rotating member 40 may have an outer peripheral surface, and a movable piece such as a roller may be disposed between the inner peripheral surface and the outer peripheral surface.

Further, the brake device 3, the ratchet device 2, and the clutch unit 1 are not only used for the height adjustment mechanism of the vehicle seat S, but can be arbitrarily applied to other devices.

Further, the elements described in the above-described embodiments and modifications may be implemented in any combination.

Claims

An outer ring having a cylindrical inner peripheral surface;
A plurality of brake shoes arranged side by side in the circumferential direction on the radially inner side of the outer ring and having a pair of brake surfaces facing the inner circumferential surface and capable of contacting the inner circumferential surface, and an inner side surface facing the radially inner side When,
An output-side rotating member disposed on the radially inner side of each of the brake shoes and having an opposing surface on the outer periphery facing the inner surface;
An input-side rotation member capable of giving a rotational torque to the output-side rotation member by contacting the brake shoe or the output-side rotation member;
The rotational force input to the output-side rotating member is a brake device configured not to rotate the input-side rotating member for at least one rotation direction,
A brake device comprising: a friction member having a pressure contact portion pressed against the inner peripheral surface; and an engagement portion engaged with the brake shoe in the circumferential direction.
The friction member has a ring portion at a position closer to the inner peripheral surface than the output-side rotating member, and the pressure contact portion is provided to protrude outward in the radial direction from the ring portion. Item 4. The brake device according to item 1.
The brake device according to claim 2, wherein the engaging portion is provided so as to protrude from the ring portion in an axial direction of the output-side rotating member.
The brake device according to claim 3, wherein the pressure contact portion and the engagement portion are arranged at the same position in the circumferential direction.
The brake device according to any one of claims 2 to 4, wherein the friction member includes a fitting portion that is fitted to the output-side rotation member.
The brake device according to claim 5, wherein the friction member has a bent connecting portion that connects the fitting portion and the ring portion.
The brake shoe has a pair of protrusions protruding outward in the radial direction, and each of the brake surfaces is provided on the protrusion,
The brake device according to any one of claims 1 to 6, wherein the engaging portion is disposed between a pair of the protruding portions of one brake shoe.
A first movable piece disposed between the inner surface and the opposing surface;
The urging member for urging the first movable piece toward a narrow side of a space formed between the inner side surface and the opposing surface is further provided. The brake device according to item 1.
The brake device according to any one of claims 1 to 8, wherein the friction member is made of resin.
The friction member is a restricting portion provided to protrude in the axial direction of the output-side rotating member, and is provided between the plurality of brake shoes to restrict the positional relationship between the plurality of brake shoes. The brake device according to claim 1, further comprising a portion.
A clutch unit comprising the brake device according to claim 1 and a ratchet device,
The ratchet device
An operation input member capable of rotating within a predetermined angle range from the neutral position;
A second movable piece that is disposed between the operation input member and the input side rotation member and transmits a rotational torque of the operation input member to the input side rotation member;
A first return spring that biases the operation input member toward the neutral position by biasing the second movable piece;
A second return spring that has one end engaged with a spring engaging portion of the operation input member and biases the operation input member toward the neutral position;
The clutch unit, wherein the first return spring and the second return spring are located on a single plane perpendicular to the rotation axis of the operation input member.
The clutch unit according to claim 11, wherein a wall portion is disposed between the first return spring and the second return spring.
A housing for housing the operation input member, the input side rotation member, the second movable piece, and the first return spring;
The clutch unit according to claim 11 or 12, wherein the second return spring is disposed closer to the rotation axis than the first return spring and is accommodated in the housing. .
The operation input member has an operation lever mounting portion,
The clutch unit according to claim 13, wherein the spring engaging portion is disposed at a position different from the attachment portion in the rotation direction of the operation input member.
A regulating member that regulates the position of the second movable piece;
The regulating member is provided on a side wall portion disposed on one side of the second movable piece in the rotation axis direction of the operation input member, and provided to protrude from the side wall portion to the other side in the rotation axis direction, A restricting portion disposed adjacent to the second movable piece in the rotation direction of the operation input member; and provided at the other end of the second return spring provided to protrude from the side wall portion to the other side in the rotation axis direction. The clutch unit according to claim 13 or 14, further comprising a latching portion for latching.
The first return spring is a compression spring;
The clutch unit according to any one of claims 11 to 15, wherein the second return spring is a torsion spring.