JP7089180B2 - Brake device and seat - Google Patents

Description

The present invention relates to a brake device capable of stopping the rotation of a shaft with respect to a base plate attached to a seat frame, and a seat provided with the brake device.

A brake device capable of stopping the rotation of a shaft of a rotating member such as a lever of a height adjustment mechanism provided on various seats is known. In a typical height adjustment mechanism, the shaft (output shaft) is rotated by operating a lever provided on the input side to swing up and down, and the height of the seat surface of the seat is adjusted. A brake device is provided so that the shaft does not rotate even if a force for lowering the seat is applied to the shaft due to the weight of the seat and the occupant.

The mechanism of the brake device is housed between the base plate attached to the seat and the cover member. The brake device secures the required structural strength by deforming and caulking a part of the base plate to which the cover member is assembled.

For example, in the brake device described in Patent Document 1, a brake mechanism is housed in a housing having a flange for screwing, and a portion protruding from the housing to the outside (input side) in the rotation axis direction is provided on the cover. The cover is fixed by inserting it through the opening and crimping it.

Further, in the brake device described in Patent Document 2 and Patent Document 3, a claw portion protruding from the stationary side member (side plate) on the brake side to the outside (input side) in the rotation axis direction of the shaft is provided on the cover and the outer ring. The cover is fixed by inserting it into the notch recess and crimping it.

US Pat. No. 6,508,347 Japanese Unexamined Patent Publication No. 2009-210118 Japanese Unexamined Patent Publication No. 2009-299868

Prior art configurations that provide a protrusion for caulking the cover member to the base plate of the brake device (ie, a member located inside the shaft rotation axis and attached to the seat frame) tend to complicate the structure of the base plate. be. In particular, if there is a protruding portion (a portion fixed by caulking) exposed from the cover member to the lever side, the appearance may be impaired and the lever may be interfered with, which is not preferable.

Therefore, it is desired to provide a cover member mounting structure that does not expose the crimped fixing portion to the outside of the cover member without impairing the strength of the crimping fixing structure of the brake device. In the following description, the rotation axis of the shaft may be simply referred to as "axis", the rotation axis direction may be referred to as "axis direction", and the direction orthogonal to the axis direction may be referred to as "diameter direction".

In view of the above background, we propose a new form of a brake device including a base plate, a brake mechanism, and a cover member. The base plate is attached to the seat frame. The brake mechanism can stop the rotation of the shaft, which rotates relative to the base plate. The cover member houses the brake mechanism. The cover member has an outer peripheral portion that covers the outer periphery of the brake mechanism, a side portion that extends from an end portion of the outer peripheral portion far from the base plate in a direction approaching the axis of the shaft, and an extension portion that extends from the outer peripheral portion to the base plate side. .. The extending portion has a caulked portion whose tip is bent toward or away from the axis of the shaft and is caulked to a part of the base plate or the brake mechanism. The base plate has an opening penetrating in the axial direction or a recess recessed toward the side at a position overlapping the caulked portion when viewed from the axial direction of the shaft.

According to such a configuration, since the cover member has an extending portion to be a caulking portion, the base plate can have a simple configuration without a protruding structure for fixing the caulking, and can be caulked from the cover member. The part is not exposed. Further, since at least a part of the caulked portion can be located in the opening or the recess, the size (thickness) of the brake device in the axial direction can be reduced.

Further, the surface of the caulked portion opposite to the side portion may be located on the side portion side of the surface opposite to the side portion of the base plate in the axial direction. With this configuration, the caulked portion does not protrude from the base plate toward the seat frame, so that stable attachment of the base plate to the seat frame can be easily realized with a simple structure.

In the brake device described above, the brake mechanism may include an outer ring fixed to the base plate, and the extending portion may be caulked and fixed to the outer ring. Here, it is preferable that the opening is arranged so as to overlap the outer ring when viewed from the axial direction, and at least a part of the caulked portion is located in the opening. In this way, by adopting a structure in which the extending portion is caulked and fixed to the outer ring, the caulked portion is brought into close contact with the outer ring so as not to protrude in the radial direction, and at least a part of the caulked portion is formed in the opening in the axial direction. Since it is positioned, it is possible to realize a compact device.

In the brake device including the outer ring, the outer ring may be fixed to the base plate at a plurality of fixing portions separated from each other in the rotation direction of the shaft. In this case, the extending portion can be arranged between a pair of fixed portions adjacent to each other in the rotation direction. Further, it is preferable that the extending portion is arranged apart from the fixed portion. With such an arrangement, the cover member can be efficiently mounted and caulked without the extending portion interfering with the fixing portion of the outer ring. The fixed portion may be, for example, a welded portion, but in that case, heat during welding can easily escape due to the presence of an opening or a recess arranged in the portion where the extended portion is caulked and fixed, and the height is high. Since accurate welding can be realized, defects during caulking are less likely to occur, and the cover member can be positioned and fixed with high accuracy.

In the brake device having the plurality of fixed portions described above, the length of the fixed portion may be longer than the length of the extending portion in the rotation direction. By doing so, the attachment strength of the brake mechanism to the base plate can be improved, and the structural strength of the entire brake device can also be improved.

In the various forms of the brake device described above, the cover member may have a plurality of the extending portions. In that case, it is preferable that the axis of the shaft is located between the pair of extension portions among the plurality of extension portions. With such an arrangement, the cover member can be stably attached to the base plate, and the attachment strength can be improved, so that the structural strength of the entire brake device can also be improved.

In the brake device described above, when the base plate has the recess and the extending portion is caulked and fixed to the base plate, it is preferable to configure the base plate so that at least a part of the caulked portion is located in the recess. With this configuration, the brake mechanism can be stably attached to the base plate together with the cover member. Further, the size (thickness) of the brake device in the axial direction can be reduced.

The brake device and the seat frame are provided, and the seat frame has a mounting surface on which the brake device is mounted and a pair of bead portions protruding from the mounting surface, and the caulking portion is between the pair of bead portions. We propose a sheet located in. In the seat configured as described above, the caulked portion can be protected by the bead portion by providing the seat frame with a pair of bead portions so as to sandwich the caulked portion.

A seat provided with the brake device and a seat frame configured such that the surface of the caulked portion opposite to the side portion is located on the side portion side of the surface opposite to the side portion of the base plate in the axial direction. The seat frame has a mounting surface on which the brake device is mounted, the brake device has a surface opposite to the side portion of the base plate in contact with the mounting surface, and the base plate is attached to the seat frame by a fastening member. We propose a sheet that is characterized by being fixed.

According to the sheet configured in this way, the base plate is brought into close contact with the mounting surface by the fastening force of the fastening member, stable mounting is possible, and high mounting strength can be ensured. Further, since the base plate is not deformed at the time of mounting, it is possible to suppress the acceleration of aging deterioration and the increase of strain due to stress.

According to the various aspects of the brake device described above, by providing the cover member with an extending portion that serves as a caulking portion, it is possible to avoid complication of the base plate structure, exposure of the caulked portion from the cover member, and increase in size of the device. Is.

Further, by adopting a configuration that minimizes the protrusion of the crimped portion from the base plate or the cover member, downsizing in the axial direction is possible, so that a compact braking device can be provided.

In addition, the structural strength and rigidity of the brake device (and the place where the brake device is attached to the seat) can be improved.

It is a side view of a vehicle seat. It is an exploded perspective view of a clutch unit (brake device). It is a cross-sectional view of a brake mechanism. FIG. 3 is a cross-sectional view taken along the line ZZ of FIG. 3 of the clutch unit. A side view (a) of the clutch unit viewed from the output side, and a partially enlarged cross-sectional view (b) showing a state in which the extended portion of the cover member is inserted into the opening of the base plate as seen in the YY cross section of FIG. It is a partially enlarged cross-sectional view (c) which shows the state which the extension part was caulked and fixed to the outer ring. It is a side view of a clutch unit. It is the figure which looked at the input side rotating member from the output side. It is the figure which looked at the friction member from the input side. It is a perspective view which saw the clutch unit from the cover member side. (A) A cross-sectional view of the ratchet device and (b) an enlarged view of a protruding portion. It is a figure explaining the operation of a ratchet apparatus, and shows the case where the operation input member is rotated clockwise. It is a figure explaining the operation of a ratchet device, and shows the case where the operation input member is returned counterclockwise. It is a figure explaining the operation of the ratchet device when an unexpected load is applied, and shows the case where the operation input member is rotated clockwise. It is a figure explaining the operation of the ratchet device when an unexpected load is applied, and shows the case where the operation input member is further rotated clockwise. It is a figure explaining the operation of a brake mechanism, and shows the case where a clockwise rotation torque is applied to a shaft. It is a figure explaining the operation of the brake mechanism, and shows the case where the counterclockwise rotation torque is applied to the input side rotation member from the state of FIG. It is a figure explaining the operation of the brake mechanism, and shows the case where the clockwise rotation torque is applied to the input side rotation member from the state of FIG. It is a figure explaining the operation of the brake mechanism, and shows the state which the input side rotating member is further rotated clockwise from the state of FIG. It is a figure explaining the operation of a brake mechanism, and shows the state which applied the excessive rotational torque in the clockwise direction to a shaft. (A) A side view of a side frame to which a clutch unit is attached, and (b) a sectional view thereof XX. It is an enlarged cross-sectional view of the caulking part which shows the 1st modification of the aspect which crimps and fixes the extended part of a cover member. It is (a) enlarged sectional view of (a) enlarged sectional view of the caulked part, and (b) side view seen from the output side which shows the 2nd modification of the aspect of fixing the extended part of a cover member by caulking. It is an enlarged cross-sectional view of the caulking part which shows the 3rd modification of the aspect which crimping and fixing the extended part of a cover member. It is (a) enlarged sectional view of (a) enlarged sectional view of the caulked part, and (b) side view seen from the output side which shows the 4th modification of the aspect of fixing the extended part of a cover member by caulking. It is (a) enlarged sectional view of (a) enlarged sectional view of the caulked part, and (b) side view seen from the output side which shows the 5th modification of the aspect of fixing the extended part of a cover member by caulking.

Next, an embodiment of the present invention will be described in detail with reference to the drawings as appropriate.
As shown in FIG. 1, the clutch unit 1 embodying one embodiment of the braking device of the present invention has the height of the seat cushion S1 of various vehicle seats (here, vehicle seat S) as an example of the seat. It is applied to a known height adjustment mechanism for adjusting. In the clutch unit 1, a lever 75 is attached to an operation input member 50, and by operating the lever 75, the shaft 30 described later is rotated to drive a height adjustment mechanism, and the height of the seat cushion S1 can be adjusted. Specifically, when the lever 75 is raised from the neutral position N, the seat cushion S1 is raised by a predetermined amount, and when the lever 75 is lowered from the neutral position N, the seat cushion S1 is lowered by a predetermined amount. When the lever 75 is returned from the upper or lower position to the neutral position N, the shaft 30 does not rotate.

As shown in FIGS. 2 to 4, the clutch unit 1 (brake device) is configured such that each member is housed in a housing 100. The housing 100 is composed of a combination of an outer ring 10, a base plate 85, and a cover member 60. Further, in the following description, the left side of FIGS. 2 and 4 in which the cover member 60 and the operation input member 50 are arranged is referred to as an “input side”, and the right side of FIGS. 2 and 4 in which the output gear 35 is arranged is referred to as “input side”. Called "output side".

The clutch unit 1 includes a ratchet device 2 and a brake mechanism 3. The ratchet device 2 is provided on the input side, and transmits / shuts off the input torque due to the swinging operation of the operation input member 50. The brake mechanism 3 is provided on the output side, transmits the input torque from the ratchet device 2 to the output gear 35 of the shaft 30, and cuts off the reverse input torque from the output gear 35, so that the brake mechanism 3 is relative to the base plate 85. The shaft 30 is configured to be able to stop the rotation of the shaft 30.

Explaining the outline of the components of the ratchet device 2 and the brake mechanism 3, the ratchet device 2 includes an operation input member 50, a regulation member 71, a roller 72 as an example of a movable piece, a first return spring 73, and a first return spring 73. 2 The return spring 74, the lever 75, and the retaining plate 77 are provided. Further, the brake mechanism 3 includes an outer ring 10, a brake shoe 20, a shaft 30 as an output side rotating member, an input side rotating member 40, a roller 81, a spring 82, and a friction member as an example of a space holding member. It is equipped with a 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 mechanism 3, and can be referred to as a component of either the ratchet device 2 or the brake mechanism 3.

Next, the details of the configuration of the brake mechanism 3 and the ratchet device 2 will be described.
First, the configuration of the brake mechanism 3 will be described.
The outer ring 10 is made of a ring having a predetermined wall thickness, and has a cylindrical inner peripheral surface 11, a cylindrical outer peripheral surface 12, and a pair of side surfaces 13 and 14 connecting the inner peripheral surface 11 and the outer peripheral surface 12. There is. The pair of side surfaces 13 and 14 are located radially outside the outer ring 10 with respect to the inner peripheral surface 11, and are planes orthogonal to the axis of the inner peripheral surface 11. In the description of the brake mechanism 3, the radial direction and the circumferential direction are based on the inner peripheral surface 11 of the outer ring 10.

The base plate 85, which forms a part of the housing 100 together with the outer ring 10, is a sheet metal member for supporting the brake mechanism 3. The base plate 85 is formed with three mounting holes 85B for mounting the brake mechanism 3 (clutch unit 1) on the frame of the seat cushion S1 (see the side frame FR in FIG. 1). Further, the base plate 85 is formed with a through hole 85A in the center for passing the shaft 30. As shown in FIGS. A hole 85H as an example of an opening is formed in a position of the cover member 60 that overlaps with four caulking portions 62F described later). Further, a spring holding portion 85C extending toward the input side is provided at the lower portion of the base plate 85. Since the outer ring 10 is fixed to the base 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 molding, and is welded to the input side surface of the base plate 85 by welding at the outer peripheral edge 14B of the side surface 14 on the output side (FIGS. 4 to 6). See welded part W).

The brake shoes 20 are members that generate a braking force with the outer ring 10, and three brake shoes 20 are arranged so as to be arranged at equal intervals in the circumferential direction inside the outer ring 10 in the radial direction. The brake shoe 20 includes a main body portion 20A extending in the circumferential direction, and a protruding portion 20B and a protrusion 20C protruding radially outward on the outer periphery of the main body portion 20A.

One protruding portion 20B is provided at both ends in the circumferential direction of the outer periphery of the main body portion 20A. Each protrusion 20B has a brake surface 21 at the tip on the outer side in the radial direction, which faces the inner peripheral surface 11 of the outer ring 10 and is in contact with the inner peripheral surface 11. The brake surface 21 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10, and as shown in FIG. 3, the outer side of the brake surface 21 in the circumferential direction (outside the circumferential direction with respect to each brake shoe 20). ) Is arranged so as to come into contact with the inner peripheral surface 11 of the outer ring 10. As a result, when the brake shoe 20 is urged outward in the radial direction, the contact portion near the outer side 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 center of the outer circumference of the main body 20A in the circumferential direction. A support surface 26 capable of contacting the inner peripheral surface 11 of the outer ring 10 is provided at the radial outer tip of the protrusion 20C. In other words, the support surface 26 is provided in 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 the brake shoe 20 and the shaft 30 are not loaded.

The brake shoe 20 has a cylindrical outer peripheral surface having a diameter smaller than that of 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. Has 22. Further, the brake shoe 20 has an inner side surface 23 facing inward in the radial direction. The brake shoe 20 has an end surface 24 at the end in the circumferential direction, which connects both ends of the inner surface 23 and the ends 21E of the two brake surfaces 21. Further, in the brake shoe 20, a rotational force input surface 25 facing in the circumferential direction is formed at a step between the brake surface 21 and the outer peripheral surface 22.

Each of the inner side surfaces 23 has three surfaces facing the facing surface 36 described later of the shaft 30. Specifically, as shown in FIG. 3, the inner side surface 23 is in first contact with the first contact surface 23A and the first inclined surface 23B arranged counterclockwise with respect to the first contact surface 23A. It has a first inclined surface 23C arranged on the clockwise side of the figure with respect to the surface 23A. The first contact surface 23A is in contact with the roller 81 and is a plane parallel to the direction along the straight line L1 connecting both end portions 21E in the circumferential direction of the pair of brake surfaces 21. The first inclined surfaces 23B and 23C are planes inclined with respect to the first contact surface 23A so as to approach the facing surface 36 as the distance from the first contact surface 23A between them increases.

As shown in FIG. 2, the shaft 30 has a shaft-shaped working portion 31, a flange 32 formed on the output side of the working portion 31, and a small diameter coaxial with the working portion 31 and protruding from the working portion 31 to the input side. 33, and an output gear 35 formed so as to project to the output side of the flange 32. As shown in FIG. 3, the shaft 30 is arranged inside each brake shoe 20 in the radial direction. The output gear 35 projects to the output side through the through hole 85A of the base plate 85 (see FIG. 4).

As shown in FIG. 3, the working 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 facing surfaces 36 are provided on the outer periphery of the working portion 31 corresponding to the inner surface 23 of each brake shoe 20. A pair of rollers 81 are arranged between each inner side surface 23 and each facing surface 36. Further, the curved surface portion 38 is a portion connecting the facing surfaces 36 corresponding to each brake shoe 20, and is one between the pair of facing surfaces 36 adjacent to each other in the circumferential direction of the outer periphery of the working portion 31, for a total of three. There are two. The curved surface portion 38 is formed as a curved surface having an arc shape in a cross-sectional view centered on the center of rotation of the shaft 30.

The facing surface 36 includes a second contact surface 36A, 36B arranged at both ends on the outer side in the circumferential direction of the facing surface 36, and a connecting surface portion 36C connecting the second contact surfaces 36A, 36B at both ends. have. The second contact surface 36A is arranged on the counterclockwise side in the figure with respect to the connection surface portion 36C, and the second contact surface 36B is arranged on the clockwise side in the figure with respect to the connection surface portion 36C. The connection surface portion 36C is a flat surface in which at least the central portion in the circumferential direction 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 shaft 30.

The second contact surfaces 36A and 36B can come into contact with the roller 81 when the brake shoe 20 is not loaded, and are continuous with the inclined portion inclined with respect to the first contact surface 23A and the outside of the inclined portion. It has a curved surface portion arranged in a curved surface. By having such second contact surfaces 36A and 36B, the facing surface 36 includes a portion non-parallel to the first contact surface 23A which is a part of the inner surface 23 of the brake shoe 20.

As shown in FIG. 3, a pair of rollers 81 are arranged between the inner side surface 23 of each brake shoe 20 and the facing surfaces 36 of the shaft 30. Here, of the pair of rollers arranged between each inner side surface 23 and each facing surface 36, the one arranged on the counterclockwise side in FIG. 3 is referred to as the roller 81A, and the one arranged on the clockwise side is referred to as the roller 81A. It is a roller 81B. When the brake shoe 20 and the shaft 30 are not loaded, the roller 81A is sandwiched between the first contact surface 23A and the second contact surface 36A, and the roller 81B is in contact with the first contact surface 23A. And are in contact with the second contact surface 36B in a state of being sandwiched between them. By arranging the roller 81 between the inner side surface 23 and the facing surface 36 in this way, in the brake mechanism 3, the load is transmitted between the inner side surface 23 and the facing surface 36 via the roller 81. ..

The spring 82 is a compression coil spring, and is provided one by one between the pair of rollers 81A and 81B. The spring 82 separates the pair of rollers 81A and 81B in the circumferential direction and urges the narrow side of the space formed between the inner side surface 23 and the facing surface 36.

When the inner side surface 23 and the facing surface 36 apply rotational torque to the brake shoe 20 by the input side rotating member 40, the inner side surface 23 pushes the facing surface 36 via the roller 81 to rotate the shaft 30, while the rotational torque is applied to the shaft 30. However, the facing surface 36 pushes 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. That is, the second contact surface 23A with respect to the first contact surface 23A so that the first contact surface 23A of the inner surface 23 and the second contact surfaces 36A and 36B of the facing surface 36 and the roller 81 come into contact with each other so as to function as such. The inclination angles and positions of the contact surfaces 36A and 36B are adjusted.

The input-side rotating member 40 shown in FIG. 2 is rotatable around an axis such as the outer ring 10 and the shaft 30, receives the rotational output of the ratchet device 2, and abuts on the brake shoe 20 of the brake mechanism 3 in the circumferential direction to brake. It is a member capable of applying a rotational torque to the shoe 20. The input-side rotating member 40 has a cylindrical pressure-receiving ring portion 41, a plurality of engaging legs 42 protruding from the pressure-receiving ring portion 41 toward the output side, and a pressure receiving ring portion 41 from near the center in the axial direction to the inside in the radial direction. Formed in the center of the plate-shaped portion 43 extending toward the plate-shaped portion 43, the holding portion 44 (see FIG. 7) protruding from the output-side surface of the plate-shaped portion 43 toward the output side in the axial direction of the shaft 30, and the plate-shaped portion 43. It is configured to have a through hole 45 formed therein. The inner peripheral surface 41A of the pressure receiving ring portion 41 is an example of a load input surface and has a circular cross section.

Three pairs of engaging 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 arranged between the protrusion 20C and the counterclockwise protrusion 20B of FIG. 3, and the protrusion 20C and the clockwise protrusion of FIG. It comprises an engaging leg 42B disposed between the portions 20B. The sizes of the protrusions 20B, the protrusions 20C and the engaging legs 42A and 42B are set between the protrusions 20B and the protrusions 20C and the engaging legs 42A and 42B so that play can be performed in the rotation direction (circumferential direction). ing. The engaging legs 42A and 42B are formed in substantially the same shape. The play in the rotation direction (circumferential direction) of the brake shoe 20 with respect to the input-side rotating member 40 (engaging legs 42A, 42B) is, for example, 4 °.

The holding portion 44 is a portion that prevents the roller 81 from falling off from between the inner side surface 23 and the facing surface 36, and is arranged between the rollers 81 in the circumferential direction. Specifically, the pair of rollers 81A and 81B corresponding to each brake shoe 20 are arranged adjacent to each other on both sides in the circumferential direction, and a total of three rollers 81A and 81B are provided.

The holding portion 44 is arranged apart from the roller 81 in a state where no load is input to the input side rotating member 40 and the shaft 30. More specifically, the holding portion 44 refers to the roller 81 adjacent to the upstream side in the rotational direction of the rotational torque, in the present embodiment, with respect to the roller 81B in a state where the rotational torque in the normal use range is input to the shaft 30. Arranged to be non-contact.

Further, the holding portion 44 rotates the input-side rotating member 40 in the same rotational direction as the rotational torque of the shaft 30 from the state where the rotational torque is input to the shaft 30, and brings it into contact with the brake shoe 20 in the circumferential direction. At the time point, the roller 81 adjacent to the downstream side in the rotation direction is arranged so as not to be in contact with the roller 81A in the present embodiment.

Further, the holding portion 44 contacts the roller 81 adjacent to the downstream side in the rotating direction of the holding portion 44 in a state where the input side rotating member 40 abuts on the brake shoe 20 in the circumferential direction to rotate the brake shoe 20. Arranged to do. However, the holding portion 44 may not be in contact with the roller 81 in a state where the brake shoe 20 is rotated by the input side rotating member 40.

As shown in FIG. 7, the through hole 45 allows the working portion 31 of the shaft 30 to be inserted into the through hole 45, and has three circumferential surface portions 46 along the curved surface portion 38 of the working portion 31 and each circumference on the inner circumference thereof. It is arranged between the surface portions 46 and has three convex surface portions 47 protruding inward in the radial direction with respect to the circumferential surface portion 46. Each convex surface portion 47 has a top portion 47A protruding most radially inward, a release surface 47B adjacent to the clockwise side (counterclockwise side in FIG. 3) with respect to the top portion 47A, and a counterclockwise portion in FIG. It has a flank 47C adjacent to the clockwise side (clockwise in FIG. 3).

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

In the flank 47C, the size of the angle of the facing surface 36 with respect to the connection surface portion 36C is large with respect to the connection surface portion 36C of the release surface 47B in a state where no load is input to the input side rotating member 40 and the shaft 30 from the outside. It is formed larger than the halfbeak. The flank 47C has a shape that does not abut on the connection surface portion 36C when the input-side rotating member 40 is rotated in the clockwise direction of FIG. 3 and brought into contact with the brake shoe 20 in the circumferential direction. However, the size of the angle of the flank 47C with respect to the connection surface portion 36C is the same as the size of the angle of the release surface 47B with respect to the connection surface portion 36C, and the release surface 47B is the clockwise direction of the input side rotating member 40 in FIG. It may have the same function as.

The friction member 90 shown in FIG. 2 is a member that generates an auxiliary braking force for suppressing the sudden start of operation of the shaft 30 at the moment when the braking force of the brake mechanism 3 is cut off.
As shown in FIG. 8, the friction member 90 includes a first ring portion 91, a second ring portion 92, a connecting portion 93 connecting the first ring portion 91 and the second ring portion 92, and a second ring portion. It has a plurality of protruding portions 94 as an example of a pressure contact portion and an engaging portion protruding from 92, and a gap holding portion 95 protruding from the first ring portion 91.

As shown in FIG. 3, the space holding portion 95 is a portion arranged between the brake shoes 20 in the circumferential direction to hold the space between the brake shoes 20 in the rotational direction, and is in accordance with the number of the brake shoes 20. Multiple, here three are provided. Each interval holding portion 95 is arranged in a substantially triangular space surrounded by two brake shoes 20 adjacent to each other in the circumferential direction and the holding portion 44. That is, since the space holding portion 95 is arranged by effectively utilizing the space between the two brake shoes 20 and the holding portion 44, it is possible to suppress the increase in size of the brake mechanism 3.

As shown in FIG. 8, the first ring portion 91 is a portion that connects a plurality of spacing holding portions 95 and integrally rotatably holds the spacing holding portion 95. The first ring portion 91 has a fitting hole 91A having the same shape as the contour of the cross section of the working portion 31, and the fitting hole 91A and the working portion 31 are fitted so that the first ring portion 91 does not rotate relative to the shaft 30. It has become like.
The second ring portion 92 is a portion that integrally and rotatably holds the plurality of protruding portions 94, and is arranged radially outside the first ring portion 91.

The protruding portion 94 protrudes outward in the radial direction of the outer ring 10 and toward the input side in the axial direction of the shaft 30. The protruding portion 94 is a pressure contact surface 94A whose outer surface in the radial direction is pressure-contacted with the inner peripheral surface 11 of the outer ring 10. The pressure contact surface 94A is formed so that its diameter is slightly larger than the inner diameter of the inner peripheral surface 11. On the other hand, the diameter of the outer peripheral surface 92A other than the protruding portion 94 of the second ring portion 92 is smaller than the inner diameter of the inner peripheral surface 11 of the outer ring 10. Therefore, when the friction member 90 is combined with the outer ring 10, only the pressure contact surface 94A is pressed against the inner peripheral surface 11, and the outer peripheral surface 92A is separated from the inner peripheral surface 11.

Further, in the protruding portion 94, a portion protruding in the axial direction from the second ring portion 92 engages with the brake shoe 20 in the circumferential direction. As shown in FIG. 3, the protrusions 94 are arranged between the pair of protrusions 20B in one brake shoe 20. More specifically, the protrusion 94 is a first protrusion 94X arranged between the protrusion 20C of the brake shoe 20 and the protrusion 20B arranged on the clockwise side of FIG. 3 with respect to the protrusion 20C. And a second protrusion 94Y arranged between the protrusion 20C of the brake shoe 20 and the protrusion 20B arranged on the counterclockwise side of FIG. 3 with respect to the protrusion 20C. As shown in FIG. 8, the first protrusion 94X has a first engagement surface 94B at the clockwise end of FIG. 8, and the second protrusion 94Y is the counterclockwise end of FIG. The portion has a second engaging surface 94C. As shown in FIG. 3, both the first engaging surface 94B and the second engaging surface 94C input the rotational force of the protruding portion 20B of the brake shoe 20 in a state where no load is input to the input side rotating member 40. It is separated from the surface 25.

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

As shown in FIG. 8, the connecting portion 93 includes a meandering connecting portion 93A, 93B and a plate-shaped connecting portion 93C. Three connecting portions 93A are provided in a U-shape that opens in the clockwise direction in the figure, and the connecting portions 93B are arranged adjacent to the connecting portion 93A in the clockwise direction and open in the counterclockwise direction. Three are provided in the shape. The plate-shaped connecting portion 93C is arranged between the connecting portion 93A and the connecting portion 93A adjacent to the connecting portion 93B on the clockwise side.
The connecting portions 93A and 93B have a thin shape that can be flexed and deformed, and the connecting portion 93C has a wide plate shape that is less likely to be flexed and deformed than the connecting portions 93A and 93B.
As described above, the first ring portion 91 and the second ring portion 92 are not formed as an integral plate as a whole, but are connected by a plurality of connecting portions 93, so that the first ring portion 91 and the second ring portion 92 are connected to the first ring portion 91. When a rotational torque is input to one of the second ring portions 92, the connecting portion 93 can be slightly bent. Therefore, it is easy for the friction member 90 to have both the function of generating the auxiliary braking force and the function of balancing the positions of the plurality of brake shoes 20 in the circumferential direction.

The material constituting the friction member 90 is not particularly limited, but the friction member 90 is made of, for example, a resin. When the friction member 90 is made of resin, a complicated shape can be easily formed, and since noise is less likely to be generated when sliding with the inner peripheral surface 11, the operation of the brake mechanism 3 can be made quiet.

The friction member 90 is arranged on the output side of the brake shoe 20. Then, the friction member 90 is press-fitted inside the outer ring 10, and each protrusion 94 is arranged between the protrusion 20B and the protrusion 20C of the brake shoe 20. Further, each protruding portion 94 is formed in substantially the same range as the engaging legs 42A and 42B in the rotation direction. Therefore, the play in the rotation direction (circumferential direction) of the brake shoe 20 with respect to each protrusion 94 is, for example, 4 °.

It is desirable that the play of the brake shoe 20 with respect to the space holding portion 95 of the friction member 90 in the rotation direction (circumferential direction) is larger than 0 ° and smaller than 3.4 °. The play in the circumferential direction of the brake shoe 20 with respect to the friction member 90 is smaller than the play in the circumferential direction of the brake shoe 20 with respect to the input side rotating member 40.

The washer 76 has a hole 76A having a diameter slightly smaller than the outer diameter of the support shaft portion 33 of the shaft 30, and the hole 76A is press-fitted into the support shaft portion 33 (see FIG. 4). The outer diameter of the washer 76 is larger than the support hole 64 of the cover member 60 described later, and the washer 76 prevents the shaft 30 from coming off to the output side.

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 75 and can be swung together with the lever 75 within a predetermined angle range from the neutral position. The operation input member 50 is a member that transmits the rotation torque from the lever 75 to the input side rotation member 40 via the roller 72 by moving integrally with the input side rotation member 40 via the roller 72. Therefore, the operation input member 50 includes a cam plate portion 51 and two lever engaging portions 52 as attachment portions for the lever 75 extending from the cam plate portion 51 to the input side.

As shown in FIG. 10A, the cam plate portion 51 extends continuously in the circumferential direction from the three arc-shaped small diameter portions 53 and the small diameter portion 53 on the outer peripheral surface, and has a diameter gradually larger than that of the small diameter portion 53. It has an enlarged working surface 55. The cam plate portion 51 has three protruding portions 54 protruding from the working surface 55 so as to approach the inner peripheral surface 41A of the pressure receiving ring portion 41 which is a load input surface. The small diameter portions 53 and the protruding portions 54 are alternately arranged in the circumferential direction, and the working surfaces 55 are arranged at a total of six positions between the protruding portions 54 and the small diameter portions 53 in the circumferential direction. In the description of the ratchet device 2, the radial direction and the circumferential direction are used with reference to the load input surface, here, the inner peripheral surface 41A.

The working surface 55 is radially opposed to the inner peripheral surface 41A. Further, the working surface 55 is not parallel to the inner peripheral surface 41A, and is formed so that the distance from the inner peripheral surface 41A becomes narrower as it approaches the protruding portion 54.
Further, a hole 56 through which the shaft 30 passes is formed in the center of the cam plate portion 51.

A roller 72 is arranged between each working surface 55 and the inner peripheral surface 41A of the pressure receiving ring portion 41, respectively. As can be seen in the operation description described later, the roller 72 engages and disengages the operation input member 50 and the input side rotating member 40 to transmit and disconnect the input torque. A total of six rollers 72 are arranged corresponding to each working surface 55. As shown in FIG. 4, the working surface 55 is longer in the axial direction than half of the axial length of the roller 72 and abuts on the roller 72 in a range including the central portion in the axial direction of the roller 72 (see the center line C1). Arranged as possible. As a result, the working surface 55 can stably sandwich the roller 72 with the pressure receiving ring portion 41.

As shown in FIG. 10B, the protruding portion 54 is a stepped surface 54A extending from the working surface 55 so as to approach the inner peripheral surface 41A, and an input side rotating member from an end portion of the stepped surface 54A near the inner peripheral surface 41A. It has a top surface 54B extending in the rotational direction of 40, and a corner portion 54C connecting the stepped surface 54A and the top surface 54B. The stepped surface 54A is inclined with respect to the working surface 55 so as to be separated from the roller 72 toward the outer side in the radial direction. Further, in the present embodiment, the protrusion amount of the protrusion 54 is relatively small, and the protrusion 54 has a shape in which the roller 72 and the corner portion 54C are in contact with each other. Specifically, the protruding portion 54 has a shape in contact with the movable piece at a position closer to the working surface 55 than the center 72A of the roller 72 in the radial direction. The corner portion 54C includes a shape having a roundness of a size required for manufacturing.

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 is one side of the operation input member 50 in the rotation axis direction with respect to the plurality of rollers 72. It is configured to include a side wall portion 71A arranged on the output side, and three regulation portions 71B extending from the outer peripheral edge of the side wall portion 71A toward the input side. The restricting portion 71B is longer than the axial length of the roller 72, and its tip is press-fitted into the fitting hole 66 of the cover member 60. Further, the regulating member 71 has a hole 71C in the center through which the shaft 30 passes.

As shown in FIG. 10A, the regulating portion 71B is arranged at the same rotational position on the radial outer side of the protruding portion 54 when the lever 75 is not operated, and the working surface 55 and the pressure receiving ring portion are arranged. The movement of the roller 72 between 41 in the circumferential direction is restricted. A first return spring 73 made of a compression coil spring is arranged between the two rollers 72 arranged between the adjacent regulating portions 71B with an initial load applied to each of them. Therefore, each roller 72 is in contact with the regulation portion 71B when the roller 72 is not operated in FIG. 10 (a). Here, the regulating portion 71B is arranged so as to include a portion where the center of the roller 72 is located in the radial direction of the outer ring 10, and is in contact with the portion of the roller 72 that protrudes most in the circumferential direction. As a result, the regulating unit 71B can stably support the roller 72. In FIG. 10A, the roller 72 is shown in contact with the regulating portion 71B, but the roller 72 is sandwiched between the working surface 55 and the inner peripheral surface 41A, so that the roller 72 is sandwiched from the regulating portion 71B. It may be slightly apart.

As shown in FIG. 2, the lever engaging portion 52 has an arcuate cross section and protrudes from the cam plate portion 51 in the axial direction of the shaft 30. Each lever engaging portion 52 has a screw hole 52A on the end face in the axial direction. Further, each lever engaging portion 52 has a fan shape when viewed from the axial direction, and has a side surface 52B extending in the radial direction (see FIG. 10A).

As shown in FIG. 2, the cover member 60 has a disc-shaped side portion 61, an outer peripheral portion 62 extending from the outer peripheral edge of the side portion 61 to the output side in the axial direction of the shaft 30, and an output from the outer peripheral portion 62. It is provided with a plurality of extending portions 62E extending to the side (base plate side). As shown in FIG. 4, the cover member 60 houses the ratchet device 2 and the brake mechanism 3 inside the cover member 60.

The outer peripheral portion 62 covers the outer periphery of the ratchet device 2 and the brake mechanism 3, and the side portion 61 extends from the end portion of the outer peripheral portion 62 far from the base plate 85 toward the axis 30X of the shaft 30.
The side portion 61 has a direction intersecting the axial direction of the shaft 30, and in the present embodiment, has a direction orthogonal to the axial direction.

As shown in FIG. 4, the outer peripheral portion 62 includes a small diameter portion 62A extending from the side portion 61, a flange portion 62B extending radially from the output side end of the small diameter portion 62A, and an outer peripheral edge of the flange portion 62B. It has a large diameter portion 62C extending to the output side. The large diameter portion 62C is fitted to the outside of the outer peripheral surface 12 of the outer ring 10 and fixed to the outer ring 10.
The outer peripheral portion 62 is arranged between the first return spring 73 and the second return spring 74, thereby suppressing the interference between the first return spring 73 and the second return spring 74.

The extending portion 62E has a caulking portion 62F whose tip is bent in a direction approaching the axis 30X of the shaft 30 and is caulked and fixed to the outer ring 10 forming a part of the brake mechanism 3. As shown in FIG. 5A, four caulking portions 62F (extending portions 62E) are arranged at equal intervals in the circumferential direction along the side surface 14 on the output side welded to the base plate 85 of the outer ring 10. Have been placed. In this way, since the even number of caulking portions 62F are arranged rotationally symmetric with respect to the axis 30X, all the caulking portions 62F have a pair of caulking portions 62F at positions that are axially symmetric with respect to the axis 30X. do.

As shown in FIGS. 4, 5 (a), and 6, the outer ring 10 is welded to the base plate 85 at four welded portions W as an example of a plurality of fixed portions separated from each other in the rotational direction of the shaft 30. .. The caulking portion 62F (extending portion 62E) is arranged between a pair of welded portions W adjacent to each other in the rotational direction so as to be separated from the welded portion W. Further, the length L1 of the welded portion W in the rotation direction is longer than the length L2 of the caulked portion 62F (extending portion 62E) in the rotation direction.

As shown in FIG. 2, the side portion 61 has a circular support hole 64 in the center, two arc holes 65 extending in an arc shape around the support hole 64, and positions radially outside the arc hole 65. Further, three fitting holes 66 arranged at equal intervals in the circumferential direction, and a first convex portion 67A and a second convex portion 67B protruding toward the inside of the housing 100 are formed.
The support hole 64 is a portion that fits with the support shaft portion 33 of the shaft 30 and pivotally supports the shaft 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 accepts the lever engaging portion 52, and the lever engaging portion 52 can move in the arc hole 65 within a predetermined angle range.
The first convex portion 67A is slidable with the operation input member 50, and the second convex portion 67B is slidable with the pressure receiving ring portion 41 of the input side rotating member 40. Suppress directional play.

The fitting holes 66 are three through holes provided corresponding to the three regulating portions 71B of the regulating member 71 (see also FIG. 2) so that the regulating member 71 does not rotate relative to the cover member 60. It is fitted with the cover member 60. Since the regulating member 71 and the cover member 60 are fitted at a plurality of locations, the rotation of the regulating member 71 can be firmly regulated.

At the time of manufacturing the clutch unit 1, when the cover member 60 is attached to the outer ring 10 welded to the base plate 85, first, as shown in FIG. 5B, the large diameter portion 62C of the outer peripheral portion 62 is attached. It is fitted to the outside of the outer peripheral surface 12 of the outer ring 10, and the extending portion 62E is inserted into the corresponding hole 85H. Then, as shown in FIG. 5 (c), the side portion 61 is pushed toward the output side in the axial direction of the shaft 30 with a predetermined load, and the second convex portion 67B (see FIG. 2) is brought into contact with the input side rotating member 40 while being brought into contact with the input side rotating member 40. The extension portion 62E is caulked and fixed to the outer ring 10. At this time, using a caulking tool, the tip of the extending portion 62E is bent from the output side of the base plate 85 to form the caulking portion 62F.

The entire caulking portion 62F formed by caulking the tip of the extending portion 62E is located in the hole 85H. Specifically, the surface 62S facing the output side of the caulked portion 62F (opposite the side portion 61) is the surface 85S facing the same output side of the base plate 85 (opposite the side portion 61) in the axial direction. It is in the same position.

The first convex portion 67A (see FIG. 2) suppresses the operation input member 50 from playing in the axial direction between the side wall portion 71A of the regulating member 71 and the side portion 61 of the cover member 60. Therefore, when the restricting portion 71B is press-fitted into the fitting hole 66, the restricting portion 71B is press-fitted with a load such that the first convex portion 67A and the operation input member 50 come into light contact with each other.

Returning to FIG. 2, the second return spring 74 extends radially outward from the coil portion 74A, the first arm 74B extending radially outward from one end of the coil portion 74A, and the other end of the coil portion 74A. It is a torsion spring having a second arm 74C.

The coil portion 74A is arranged on the outer side in the radial direction of the outer peripheral portion 62 of the cover member 60. As shown in FIG. 4, the first return spring 73 and the second return spring 74 are on one plane orthogonal to the rotation axis of the operation input member 50, and in FIG. 4, on the plane passing through the center line C1 described above. Located in. Therefore, the first return spring 73 and the second return spring 74 do not generate a force to twist the operation input member 50, and the operation input member 50 can be smoothly returned to the neutral position.

As shown in FIG. 2, the lever 75 outputs from the main body portion 75A extending to the left and right in FIG. 2, the spring engaging portion 75B extending from the lower end portion of the main body portion 75A to the output side, and the upper end portion of the main body portion 75A. It has a cover portion 75C extending to the side. The main body portion 75A is located on the input side with respect to the coil portion 74A of the second return spring 74. The first arm 74B and the second arm 74C of the second return spring 74 engage with the spring engaging portion 75B.
A state in which a circular through hole 75D through which the support shaft portion 33 of the shaft 30 passes and two engagement holes 75E with which the two lever engaging portions 52 of the operation input member 50 are engaged are connected to the main body portion 75A. Is formed of. As shown in FIG. 10A, the engagement hole 75E has an edge portion 75F extending in the radial direction. The lever engaging portion 52 is press-fitted into the engaging hole 75E so that the edge portion 75F of the engaging hole 75E sandwiches the lever engaging portion 52 in the rotational direction of the operation input member 50. That is, by this press-fitting, the edge portion 75F and the side surface 52B of the lever engaging portion 52 are constantly in a state of pressure contact, and the lever 75 does not play in the rotational direction with respect to the operation input member 50. Thereby, the operation feeling of the lever 75 can be improved.

As shown in FIG. 9, the spring engaging portion 75B has the same size as the spring holding portion 85C of the base plate 85 in the circumferential direction. The spring engaging portion 75B is arranged outside the spring holding portion 85C in the radial direction at a position corresponding to the spring holding portion 85C in the circumferential direction. Further, the spring engaging portion 75B and the cover portion 75C are located on the radial outer side of the coil portion 74A of the second return spring 74 to prevent the coil portion 74A from coming off.

The first arm 74B and the second arm 74C of the second return spring 74 are rotationally engaged with the spring holding portion 85C of the base plate 85 and the spring engaging portion 75B of the lever 75. When the lever 75 is not operated, the first arm 74B and the second arm 74C are urged in a direction approaching each other, sandwiching the spring holding portion 85C and the spring engaging portion 75B. That is, the lever 75 is constantly urged toward the neutral position shown in FIG. 9 by the second return spring 74.

The retaining plate 77 has two holes 77A corresponding to the screw holes 52A and a center hole 77B corresponding to the through hole 75D of the lever 75. The center hole 77B prevents the washer 76 (see FIG. 2) from interfering with the retaining plate 77.
Then, the retaining plate 77 is fixed to the operation input member 50 by the two bolts 78 passing through the holes 77A and being fastened to the screw holes 52A. This prevents the lever 75 from coming off the operation input member 50.

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. 10A, the roller 72 is located between the inner peripheral surface 41A of the input side rotating member 40 and the working surface 55 of the operation input member 50, but there is a slight gap between them. Yes, they are not sandwiched between them. The roller 72 is urged toward the regulation portion 71B by a first return spring 73 made of a compression coil spring. As a result, the first return spring 73 urges the posture of the operation input member 50 to the neutral position. Further, the second return spring 74 sandwiches the spring engaging portion 75B and the spring holding portion 85C between the first arm 74B and the second arm 74C. Due to this holding force, the position of the spring engaging portion 75B in the rotation direction is aligned with the spring holding portion 85C. That is, the second return spring 74 urges the postures of the lever 75 and the operation input member 50 to the neutral position.

When the load applied to the input side rotating member 40 is less than a predetermined value, when the lever 75 is lowered from the neutral position and the operation input member 50 is slightly swung in the clockwise direction, the working surface 55 rotates clockwise. Then, it comes into contact with the roller 72, and the roller 72 is sandwiched between the inner peripheral surface 41A and the working surface 55. As a result, the operation input member 50 and the input side rotating member 40 can rotate integrally in response to the swing operation of the operation input member 50.
Therefore, as shown in FIG. 11, if the operation input member 50 is rotated clockwise, the input side rotating member 40 and the operation input member 50 rotate clockwise while being integrated. That is, the input torque obtained by rotating the operation input member 50 is transmitted to the input side rotating member 40.

At this time, the spring engaging portion 75B of the lever 75 moves the second arm 74C in the clockwise direction against the urging force of the second return spring 74. Conversely, the second arm 74C urges the spring engaging portion 75B in the counterclockwise direction.

When the lever 75 is swung counterclockwise from the state shown in FIG. 11 to return it from the lower position to the neutral position, the working surface 55 escapes counterclockwise from the roller 72, and as shown in FIG. 12, the input side. The operation input member 50 rotates toward the neutral position while the rotating member 40 is stationary. That is, the input torque when returning the operation input member 50 is not transmitted to the input side rotating member 40 and is cut off. The operation input member 50 is assisted in operating toward the neutral position by the urging force of the first return spring 73 and the second return spring 74, and is maintained in the neutral position.

The operation of raising the lever 75 from the neutral position to the upper position and returning it from the upper position to the neutral position is the same as the case of the above-mentioned downward swing, and thus the description thereof will be omitted.

When the load applied to the input side rotating member 40 is more than a predetermined value, such as when an object is caught in the mechanism for moving the seat up and down, the lever 75 is lowered from the neutral position and the operation input member 50 is slightly shaken in the clockwise direction. When it is moved, as shown in FIG. 13, the pressure receiving ring portion 41 cannot be rotated only by sandwiching the roller 72 between the working surface 55 and the inner peripheral surface 41A, and the operation input is performed while the pressure receiving ring portion 41 is stopped. Only the member 50 rotates clockwise. When the operation input member 50 is swung clockwise with an input torque equal to or higher than a predetermined value as it is, the portion of the pressure receiving ring portion 41 in contact with the roller 72 bends outward in the radial direction. Then, the protruding portion 54 of the operation input member 50 comes into contact with the roller 72. At this time, in the present embodiment, the corner portion 54C of the protruding portion 54 comes into contact with the roller 72 at a position closer to the working surface 55 than the center 72A of the roller 72 (see FIG. 10B).

Then, as shown in FIG. 14, the protruding portion 54 comes into contact with the roller 72 and pushes the roller 72, so that the roller 72 slides with respect to the inner peripheral surface 41A. Therefore, even when the lever 75 is forcibly operated with an excessive input torque, the pressure receiving ring portion 41 may bend more than the state in which the roller 72 is in contact with the protruding portion 54 as shown in FIGS. 13 and 14. It is possible to prevent the pressure receiving ring portion 41 from being damaged and the ratchet device 2 from being damaged.

Even when the lever 75 is raised from the neutral position, the load applied to the pressure receiving ring portion 41 may be greater than or equal to a predetermined value, such as when the occupant sitting on the vehicle seat S is extremely heavy. Since it is the same as the case of swinging downward except that the rotation direction is opposite, the description thereof will be omitted.

Next, the operation of the brake mechanism 3 will be described.
As shown in FIG. 15, when the rotation torque in the clockwise direction in the figure, that is, the rotation torque in the normal use range is applied to the shaft 30 by the weight of the occupant sitting on the vehicle seat S, the shaft 30 slightly rotates clockwise. The roller 81A rotates and the distance between the second contact surface 36A (one of the pair of second contact surfaces 36A and 36B of the one facing surface 36 on the counterclockwise side) and the first contact surface 23A becomes narrower. (One of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side) and the pressure of the second contact surface 36A and the first contact surface 23A increase. When the roller 81A is in contact with the first inclined surface 23B in a state where no load is input to the shaft 30, the roller 81A rolls between the facing surface 36 and the inner side surface 23 and makes first contact. After moving to a position in contact with the surface 23A, the pressure between the second contact surface 36A and the first contact surface 23A sufficiently increases and stops with respect to the facing surface 36 and the inner surface surface 23. On the other hand, as the shaft 30 rotates clockwise, the distance between the second contact surface 36B (one of the pair of second contact surfaces 36A and 36B of the one facing surface 36 on the clockwise side) and the first contact surface 23A. The roller 81B (one of the pair of rollers 81 corresponding to one brake shoe 20 on the clockwise side) is not strongly pinched between the second contact surface 36B and the first contact surface 23A. Can roll.

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, in the brake shoe 20, the pair of brake surfaces 21 are pressed against the inner peripheral surface 11 of the outer ring 10 by 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 shaft 30 does not rotate. That is, a braking force that prevents the vehicle seat S from lowering is generated. Then, in such a state where the shaft 30 is subjected to the rotational torque in the normal use range, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.

Further, at this time, the roller 81B is slightly separated from the holding portion 44 adjacent to the shaft 30 in the rotational direction, that is, in 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 in a state of being sandwiched between the facing surface 36 and the inner side surface 23 by the urging force of the spring 82. As a result, the frictional force between the brake shoe 20 and the outer ring 10 can be maintained regardless of which direction the brake shoe 20 is subsequently rotated, so that unexpected release of the braking force can be suppressed.

From the brake state of FIG. 15, when the lever 75 is operated to rotate the input side rotating member 40 counterclockwise in order to raise the height of the vehicle seat S, the input side rotating member 40 is rotated as shown in FIG. The engaging leg 42A of the brake shoe 20 abuts on the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the end on the counterclockwise side. At this point, the release surface 47B of the input side rotating member 40 comes into contact with the connecting surface portion 36C of the facing surface 36 at substantially the same time, and the rotational torque in the counterclockwise direction can be transmitted to the shaft 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 braking force is released and the input side rotating member 40 is rotated to start raising the vehicle seat S. It is possible to suppress the feeling of being caught at times.

Then, when the input side rotating member 40 is further rotated counterclockwise, the engaging leg 42A pushes the rotational force input surface 25 with the force F11, so that the brake shoe 20 rotates counterclockwise and the first contact surface 23A. Pushes the roller 81A with the force F12, and the roller 81A pushes the second contact surface 36A with the force F13. This force F13 causes the shaft 30 to rotate 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.

Further, when the input side rotating member 40 is rotated clockwise by operating the lever 75 in order to lower the height of the vehicle seat S from the braking state of FIG. 15, as shown in FIG. 17, the input side rotating member The engaging leg 42B of 40 abuts on the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the end on the clockwise side. At this time, the holding portion 44 is not in contact with the roller 81A adjacent to the downstream side (clockwise direction side) in the rotation direction. Then, when the input side rotating 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 shown in FIG. 17, the brake shoe 20 and the shaft 30 operate in the opposite direction to the case where the shaft 30 is rotated in the clockwise direction in FIG. That is, as shown in FIG. 18, the brake shoe 20 rotates slightly clockwise, and the watch among the first contact surface 23A and the second contact surface 36B (the pair of second contact surfaces 36A and 36B of the one facing surface 36). By narrowing the distance between the (one on the rotating side), the roller 81B (one of the pair of rollers 81 corresponding to one brake shoe 20 on the clockwise side) and the first contact surface 23A and the second contact surface 36B. Pressure increases. Even when the roller 81B is in contact with the first inclined surface 23C, the roller 81B rolls between the facing surface 36 and the inner surface surface 23 and moves to a position where it is in contact with the first contact surface 23A. The pressure between the 36B and the first contact surface 23A is sufficiently increased to stop 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 facing surface 36 on the counterclockwise side). The rollers 81A (one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side) are placed between the first contact surface 23A and the second contact surface 36A. You can roll while the pressure of the brake gradually decreases. Then, in the state of FIG. 18, the holding portion 44 contacts the roller 81A adjacent to the downstream side in the rotation direction and pushes the roller 81A in the clockwise direction.

Further, in the process of rotating the brake shoe 20 from the state of FIG. 17 to the state of FIG. 18, the gap between the protrusion 20B of the brake shoe 20 and the second protrusion 94Y of the friction member 90 is blocked, that is, the protrusion 20B is the second protrusion. Engage with portion 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, since the friction member 90 is pressed against the inner peripheral surface 11 of the outer ring 10 at the protruding portion 94, resistance (auxiliary braking force) is given to the rotation of the brake shoe 20. Therefore, 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 weight of the occupant prevents the brake shoe 20 from suddenly rotating clockwise.

Further, in the state of FIG. 17, since the holding portion 44 is not in contact with the roller 81A, before the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force. Since the roller 81A that generated the braking force is not pushed by the holding portion 44, it is suppressed that the braking force is unexpectedly weakened.

On the other hand, as shown in FIG. 18, 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 if the roller 81A is stuck between the inner side surface 23 and the facing surface 36 due to some reason, the roller 81A is separated from between the inner side surface 23 and the facing surface 36 to release the braking force and realize stable operation. be able to.

Then, as shown in FIG. 18, 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. This force F23 causes the shaft 30 to rotate 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 excessive clockwise rotation torque larger than the normal use range is input to the shaft 30, the shaft 30 rotates clockwise as compared with the case where the rotation torque in the normal use range is applied as shown in FIG. As the distance between the second contact surface 36A and the first contact surface 23A becomes narrower, the pressure between the roller 81A and the second contact surface 36A and the first contact surface 23A becomes higher. 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 20A bends outward in the radial direction, and the support surface 26 comes into contact with 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 applied to the brake shoe 20 can be reduced.

Further, when an excessive clockwise rotation torque is input and the shaft 30 is greatly rotated clockwise, the space between the second contact surface 36B and the first contact surface 23A expands, and the roller 81B is between them. I sometimes play with. In such a case, the roller 81B comes into contact with the holding portion 44 adjacent to the downstream side in the rotation direction, here in the clockwise direction. As a result, the holding portion 44 supports the roller 81B, so that the roller 81B is prevented from falling off from between the inner side surface 23 and the facing surface 36.

In the above, 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 shaft 30 and the braking force is generated has been described. When the clutch unit 1 is applied to the vehicle seat S, since only the rotational torque in the clockwise direction is input to the shaft 30, it operates only as described above, but it is assumed that the shaft 30 operates in the counterclockwise direction. When the input-side rotating member 40 is rotated clockwise or counterclockwise after the rotational torque is input and the braking force is generated, the brake shoe 20 and the shaft 30 are substantially mirror-symmetrical (line in FIG. 3). Since it is configured (symmetrically), substantially the same operation is realized only by the difference in the rotation direction from the above.

The structure of the side frame FR as an example of the seat frame on which the clutch unit 1 (brake device) of the present embodiment is mounted will be described below. As shown in FIGS. 20A and 20B, the side frame FR includes a mounting surface SF to which the base plate 85 of the clutch unit 1 is mounted and a bead portion FB protruding from the peripheral edge of the mounting surface SF toward the input side. And have. The clutch unit 1 is arranged between the upper and lower bead portions FB of the side frame FR. As shown in FIG. 20B, the crimped portion 62F of the cover member 60 is located between the upper and lower pair of bead portions FB.

Then, the mounting hole 85B (see FIG. 2) provided in the base plate 85 of the clutch unit 1 is aligned with the nut 85N welded to the side frame FR, and the bolt 85F is screwed and fastened. The bolt 85F and the nut 85N are examples of fastening members.

By providing the side frame FR with a pair of bead portions FB so as to sandwich the caulked portion 62F, the rigidity of the side frame FR, in particular, the clutch unit 1 mounting portion is improved, and the caulked portion 62F is protected. There is.

As described above, the surface 62S facing the output side of the caulking portion 62F is at the same position as the surface 85S of the base plate 85 in the axial direction (see also FIG. 5C), and the caulking portion 62F is from the base plate 85. Since it does not protrude to the output side (mounting surface SF side), the surface 85S of the base plate 85 is in close contact with the mounting surface SF of the side frame FR due to the fastening force of the bolt 85F and the nut 85N, enabling stable mounting and high mounting. Strength can be secured. Further, since the base plate 85 is not deformed at the time of attachment, it is possible to suppress the acceleration of aging deterioration and the increase of strain due to stress.

According to the brake mechanism 3 applied to the clutch unit 1 of the present embodiment described above, when a rotational torque is applied to the shaft 30, the roller 81 pushes the inner surface 23 of the brake shoe 20 and the brake surface 21 is the outer ring 10. The brake shoe 20 does not rotate because it is pressed against the inner peripheral surface 11. In this state, when the brake shoe 20 is rotated in one rotation direction or the other rotation direction by the input side rotating member 40, the space formed between the inner side surface 23 and the facing surface 36 of the shaft 30 is narrow. Since it is urged to the side, one of the rollers 81 can always be maintained in a state of being sandwiched between the inner side surface 23 and the facing surface 36, that is, in a state of being in contact with them. Therefore, it is possible to prevent the braking force from being released at once. Further, since the braking force can be generated by each of the plurality of brake shoes 20 arranged in the circumferential direction, it is possible to suppress the increase in the size of the brake mechanism 3 in the axial direction. As a result, the size in the axial direction can be reduced and stable operation can be performed.

Then, even when the friction member 90 engages with the brake shoe 20 and the braking force generated on the brake surface 21 of the brake shoe 20 is reduced, the frictional force of the friction member 90 assists the brake shoe 20. It acts as a braking force. Therefore, even if the braking force of the brake shoe 20 is reduced when the lever 75 is used to lower the vehicle seat S, it is possible to prevent the shaft 30 from suddenly rotating due to this auxiliary braking force. can. Then, by engaging the protruding portion 94 provided on the outer peripheral portion of the friction member 90 with the brake shoe 20, the portion where the frictional force is generated and the engaging portion that engages with the brake shoe 20 and transmits the force are reached. Since the distance is small, the auxiliary braking force can be efficiently transmitted to the brake shoe 20.

Further, since the second ring portion 92 is close to the inner peripheral surface 11 of the outer ring 10, the frictional force can be efficiently generated and transmitted 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 circumference, the pressure contact force may vary due to an error in the diameters of the friction member 90 and the inner peripheral surface 11, or the friction member 90 may be distorted. However, since the protruding portion 94 of the outer peripheral portion of the friction member 90 partially contacts the inner peripheral surface 11, a stable frictional force can be generated.

Further, as described above, the friction member 90 in the present embodiment can be made of resin because the frictional force can be efficiently transmitted to the brake shoe 20. As a result, it is possible to suppress the generation of sound when the brake mechanism 3 is operated.

Further, the friction member 90 has an interval holding portion 95, and the interval holding portion 95 maintains the balance of the positions of the plurality of brake shoes 20 in the circumferential direction, so that the braking force is stable and the input side rotation. The torque when the brake shoe 20 is rotated by the member 40 is stable. Further, since the friction member 90 which is the interval holding member is a member different from the input side rotating member 40, the operation of the friction member 90 does not affect the input side rotating member 40, and the braking force is stabilized. Further, the operation of the brake shoe 20 slightly moving due to the torque input to the shaft 30 is not easily transmitted to the input side rotating member 40, and the operator does not feel uncomfortable. Therefore, the operability of the brake mechanism 3 is improved.

Further, the play in the circumferential direction of the brake shoe 20 with respect to the friction member 90 is smaller than the play in the circumferential direction of the brake shoe 20 with respect to the input side rotating member 40, so that the play in the circumferential direction of the input side rotating member 40 and the brake shoe 20 is smaller. It is possible to secure the braking force, stabilize the braking force, and improve the operability.

Then, when a large resistance is applied to the rotation of the input side rotating member 40 which is the output member of the ratchet device 2, when the operation input member 50 is rotated, the protruding portion 54 comes into contact with the roller 72. By pushing the roller 72, the roller 72 slides on the inner peripheral surface 41A of the pressure receiving ring portion 41. Therefore, after the protruding portion 54 comes into contact with the roller 72, the load applied to the pressure receiving ring portion 41 does not increase any more. Therefore, damage to the ratchet device 2 can be suppressed.

Further, since the protruding portion 54 has a shape in which the corner portion 54C is in contact with the roller 72, the amount of protrusion of the protruding portion 54 from the working surface 55 can be reduced to suppress an increase in the weight of the ratchet device 2.

Further, by adopting the roller 72 as the movable piece of the ratchet device 2, the operation of the ratchet device 2 can be smoothed and the surface pressure applied to the movable piece can be reduced.

In the above embodiment, the clutch unit 1 houses a base plate 85 attached to the side frame FR, a brake mechanism 3 capable of stopping the rotation of the shaft 30 that rotates relative to the base plate 85, and a brake mechanism 3. The cover member 60 includes an outer peripheral portion 62 that covers the outer periphery of the brake mechanism 3, and a side portion 61 that extends from an end portion of the outer peripheral portion 62 far from the base plate 85 toward the axis 30X of the shaft 30. The extension portion 62E has an extension portion 62E extending from the outer peripheral portion 62 toward the base plate 85 side, and the extension portion 62E is a part of the brake mechanism 3 (outer ring 10) with the tip bent in a direction approaching the axis 30X of the shaft 30. The base plate 85 has a caulking portion 62F fixed to the caulking portion 62F, and the base plate 85 has a hole 85H penetrating in the axial direction at a position overlapping the caulking portion 62F when viewed from the axial direction of the shaft 30. Therefore, since the cover member 60 has an extension portion 62E that serves as a caulking portion 62F, the base plate 85 can have a simple configuration without a protruding structure for fixing the caulking. Further, since there is no protruding portion exposed from the cover member 60, there are few parts that easily interfere with each other when operating the lever without spoiling the appearance.

Further, since the entire caulking portion 62F is arranged in the hole 85H, the size (thickness) in the axial direction of the device can be reduced.

Since the extending portion 62E is caulked and fixed to the outer ring 10, the caulking portion 62F is brought into close contact with the outer ring 10 so as not to protrude in the radial direction. Further, the surface 62S on the side opposite to the side portion 61 of the caulking portion 62F is at the same position as the surface 85S on the side opposite to the side portion 61 of the base plate 85 in the axial direction, and the caulking portion 62F is from the base plate 85 to the side frame. It does not protrude to the FR side. Therefore, stable attachment of the base plate 85 to the side frame FR can be easily realized with a simple structure, and the size of the device can be suppressed.

The outer ring 10 is welded and fixed to the base plate 85 at a plurality of welded portions W (fixed portions) separated from each other in the rotation direction of the shaft 30, and the extension portion 62E (caulking portion 62F) is a pair of welded portions adjacent to each other in the rotation direction. Since the extending portion 62E is arranged between the Ws at a distance from the welded portion W, the extending portion 62E does not easily interfere with the welded portion W of the outer ring 10, and the cover member 60 can be efficiently mounted and caulked and fixed. Further, when the outer ring 10 is welded to the base plate 85, the presence of the hole 85H (opening) arranged at the place where the caulking is fixed enables good heat dissipation efficiency and high-precision welding can be realized. Therefore, defects during caulking fixing are unlikely to occur, and the cover member 60 can be positioned and fixed with high accuracy.

Further, since the length L1 of the welded portion W is longer than the length L2 of the extending portion 62E in the rotation direction, the attachment strength of the brake mechanism 3 to the base plate 85 can be improved, and eventually the entire clutch unit 1 can be improved. The structural strength can be improved.

Further, since the plurality of extension portions 62E are arranged so that the axis 30X of the shaft 30 is located between the pair of extension portions 62E, the attachment strength of the cover member 60 to the base plate 85 is further improved. The structural strength of the entire clutch unit 1 can be further improved.

Although one embodiment of the present invention has been described above, the present invention can be appropriately modified and implemented without being limited to the above-described embodiment.
For example, in the above embodiment, the caulked portion 62F is entirely located in the hole 85H of the base plate 85, and the surface 62S of the caulked portion 62F opposite to the side portion 61 of the base plate 85 in the axial direction. An example is shown in which the surface 62S is located at the same position as the surface 85S on the side opposite to the side portion 61, but the surface 62S is located at a position farther from the side portion 61 than the surface 85S as in the first modification shown in FIG. There may be.

In the first modification, the outer peripheral portion 62 including the extending portion 62E of the cover member 60 uses a plate material slightly thicker than the base plate 85, thereby increasing the strength of the cover member and the caulking portion 62F. As a result, although it slightly protrudes from the base plate 85 toward the side frame FR side, the base plate 85 is brought into close contact with the side frame FR by providing an opening or a recess in the region corresponding to the protruding surface 62S in the side frame FR. be able to.

Also in the first modification, since a part of the caulking portion 62F is located in the hole 85H of the base plate 85, the size (thickness) of the clutch unit 1 in the axial direction can be reduced.

In the second modification shown in FIG. 22, a recess 85R recessed toward the side portion 61 is formed along the hole 85H of the base plate 85. The extending portion 62E of the cover member 62 is inserted into the hole 85H, and the tip thereof is bent in a direction away from the axis 30X of the shaft 30 and is caulked and fixed to the recess 85R of the base plate 85.

In the second modification, the recess 85R of the base plate 85 is located at a position overlapping the caulking portion 62F when viewed in the axial direction of the shaft 30, and the entire caulking portion 62F is located in the recess 85R. Similarly, a configuration is realized in which the surface 62S on the side opposite to the side portion 61 of the caulking portion 62F is at the same position as the surface 85S on the side opposite to the side portion 61 of the base plate 85 in the axial direction.

The depth of the recess 85R may be larger than that illustrated in the second modification. For example, in the third modification shown in FIG. 23, the surface 62S on the side opposite to the side portion 61 of the caulking portion 62F is on the side of the surface 85S on the side opposite to the side portion 61 of the base plate 85 in the axial direction. The recess 85R is deeply recessed from the surface 85S so as to be located on the portion 61 side.

The fourth modification shown in FIG. 24 is a embodiment in which the tip of the extending portion 62E is bent in a direction approaching the axis 30X of the shaft 30 and is caulked and fixed to the outer ring 10 as exemplified in the above embodiment and the first modification. A hole 85H is provided at a position overlapping the caulked portion 62F of the base plate 85 when viewed from the axial direction of the shaft 30, and a recess 10R is provided in the outer ring 10 so that the caulked portion 62F does not protrude from the base plate 85 toward the side frame FR side. This is a realized example. Also in this form, the size (thickness) in the axial direction of the device can be suppressed.

In the above-described embodiment and modification, the base plate 85 has an example in which the opening penetrating the shaft 30 in the axial direction is a hole 85H, but as in the fifth modification shown in FIG. 25, the opening is a notch 85D. It may be.

As described above, even in the second to fifth modifications, since the caulked portion 62F does not protrude from the base plate 85 to the side frame FR side, stable attachment of the base plate 85 to the side frame FR can be easily realized with a simple structure. At the same time, it is possible to suppress the increase in size of the device.

In the above embodiment, the input side rotating member 40 rotates the shaft 30 via the brake shoe 20 and the roller 81, but the input side rotating member 40 directly engages with the shaft 30 to transmit the rotational torque. It may be configured as. In this case, the shape of the through hole 45 of the input side rotating member 40 and the shape and arrangement of the engaging leg 42 are adjusted so that the through hole 42 is sufficiently engaged with the brake shoe 20 in the rotational direction. The edge of the 45 may be engaged so as to transmit a sufficient rotational torque to the acting portion 31 of the shaft 30.

Further, various configurations can be adopted for transmitting the force between the brake shoe 20 and the shaft 30. For example, in the above embodiment, the shaft 30 presses the brake shoe 20 radially outward via the roller 81 as a movable piece, but the movable piece may not be present, and the shaft 30 is radially outward. It may be configured to have a protrusion protruding from the brake shoe 20 so as to press the brake shoe 20 with this protrusion.

Further, in the above-described embodiment, the support surface 26 is an outer ring in a state where no load is input to the shaft 30 or when a rotational torque in a normal use range is applied to the shaft 30 (see FIGS. 15 to 18). Although it was separated from the inner peripheral surface 11 of 10, the present invention is not limited to this. For example, 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 shaft as long as it does not interfere with the operation when the brake shoe rotates. Further, the support surface does not have to have a shape along the inner peripheral surface of the outer ring.

In the above embodiment, the side portion 61 of the cover member 60 is orthogonal to the axial direction, but may be slightly inclined.

In the above embodiment, the roller 72 is exemplified as the movable piece, but the movable piece may be a sphere, a polygonal prism, or a columnar having 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 a support surface 26 between the pair of brake surfaces 21, but the brake shoe does not have a support surface or a protrusion on which the support surface is provided. It doesn't matter.

In the above embodiment, the pressure receiving ring portion 41 of the input side rotating member 40 is arranged on the radial outer side of the operation input member 50, but in reverse of this, the operation input member 50 has an inner peripheral surface. The input-side rotating member 40 has an outer peripheral surface as a load input surface, and a movable piece such as a roller may be arranged between the inner peripheral surface and the outer peripheral surface thereof.

In the above embodiment, four caulking portions 62F (extending portions 62E) are arranged so as to be arranged at equal intervals in the circumferential direction, but the number of caulking portions may be, for example, an odd number. Often, the arrangement does not have to be evenly spaced.

In the above embodiment, the outer ring 10 is fixed to the base plate 85 at a plurality of welded portions W separated from each other in the rotation direction of the shaft 30, but the fixing method of the outer ring is not limited to welding, but is limited to welding or the like. It can also be fixed. The arrangement of the fixing portion and the length in the rotation direction are also appropriately selected as long as they do not interfere with the caulking portion 62F of the cover member 60 and the required strength can be secured.

In the above embodiment, the caulking portion 62F is arranged between the pair of upper and lower bead portions FB provided on the side frame FR, but a pair of bead portions are formed on the left and right sides of the caulking portion 62F. This can also improve the rigidity of the clutch unit mounting location. Alternatively, a bead portion may be arranged at a position adjacent to each caulking portion 62F to protect the caulking portion 62F.

In the above embodiment, the surface 85S of the base plate 85 of the clutch unit 1 including the brake mechanism comes into contact with the mounting surface SF of the side frame FR, and the base plate 85 is fixed to the side frame FR by bolts 85F and nuts 85N as fastening members. Although the above-mentioned configuration is illustrated, the fastening member for fixing the base plate 85 is not limited to the illustrated form, and may be, for example, a rivet or the like.

In the above embodiment, the vehicle seat S mounted on an automobile is exemplified as a seat provided with a brake device, but the seat is a vehicle mounted on a vehicle other than an automobile, for example, a railroad vehicle, a ship, an aircraft, or the like. It may be a sheet for use. Further, the seat provided with the brake device is not limited to a seat for a vehicle, and may be a seat used in, for example, a theater or a home.

Further, the brake mechanism 3, the ratchet device 2, and the clutch unit 1 are not only used for the height adjustment mechanism of the seat, but also arbitrarily applied to other devices having a brake mechanism capable of stopping the rotation of the shaft, such as an armrest. can do. Therefore, the seat frame to which the base plate is attached is not limited to the side frame FR of the seat cushion S1. The configurations of the embodiments and modifications described above are applicable to braking devices attached to any frame element of the seat.

Further, each element described in the above-described embodiment and modification may be arbitrarily combined and carried out.

1 Clutch unit (brake device)
3 Brake mechanism 10 Outer ring 30 Shaft 30X Axis line 60 Cover member 61 Side part 62 Outer part 62E Extension part 62F Caulking part 62S Surface 85 Base plate 85D Notch (opening)
85H hole (opening)
85R Recess 85S Surface 85F Bolt (fastening member)
85N nut (fastening member)
FR side frame (seat frame)
FB bead part SF mounting surface S Vehicle seat (seat)
W Welded part (fixed part)

Claims (11)

The base plate that can be attached to the seat frame and
A brake mechanism that can stop the rotation of the shaft that rotates relative to the base plate,
A cover member for accommodating the brake mechanism is provided.
The cover member extends from an outer peripheral portion covering the outer periphery of the brake mechanism, a side portion extending from an end portion of the outer peripheral portion far from the base plate toward the axis of the shaft, and an outer peripheral portion toward the base plate side. Has an extension and
The extending portion has a caulked portion whose tip is bent in a direction toward or away from the axis of the shaft and is caulked and fixed to the base plate or a part of the brake mechanism.
The brake device is characterized in that the base plate has an opening penetrating in the axial direction or a recess recessed toward the side portion at a position overlapping the caulked portion when viewed from the axial direction of the shaft. The brake device according to claim 1, wherein at least a part of the caulked portion is located in the opening or the recess. Claim 1 is characterized in that the surface of the caulked portion opposite to the side portion is located on the side portion side of the surface of the base plate opposite to the side portion in the axial direction. Alternatively, the brake device according to claim 2. The brake mechanism includes an outer ring fixed to the base plate.
The extending portion is caulked and fixed to the outer ring.
The opening is arranged so as to overlap the outer ring when viewed from the axial direction.
The brake device according to any one of claims 1 to 3, wherein at least a part of the caulked portion is located in the opening. The outer ring is fixed to the base plate at a plurality of fixing portions separated from each other in the rotational direction of the shaft.
The brake device according to claim 4, wherein the extending portion is arranged between a pair of the fixing portions adjacent to each other in the rotation direction. The brake device according to claim 5, wherein the extending portion is separated from the fixed portion. The brake device according to claim 5 or 6, wherein the length of the fixed portion is longer than the length of the extended portion in the rotation direction. The cover member has a plurality of the extending portions, and the cover member has a plurality of the extending portions.
The brake device according to any one of claims 1 to 7, wherein the axis of the shaft is located between the pair of extension portions among the plurality of extension portions. The base plate has the recess and
The extending portion is caulked and fixed to the base plate.
The brake device according to any one of claims 1 to 3, wherein at least a part of the caulked portion is located in the recess. A seat including the brake device and the seat frame according to any one of claims 1 to 9.
The seat frame has a mounting surface on which the brake device is mounted and a pair of bead portions protruding from the mounting surface.
The caulked portion is a sheet characterized in that it is located between the pair of bead portions. A seat provided with the brake device and the seat frame according to claim 3.
The seat frame has a mounting surface on which the brake device is mounted.
The brake device is
The surface of the base plate opposite to the side is in contact with the mounting surface.
A sheet characterized in that the base plate is fixed to the seat frame by a fastening member.

Images