WO2017010496A1 - Brake device - Google Patents

Brake device Download PDF

Info

Publication number
WO2017010496A1
WO2017010496A1 PCT/JP2016/070636 JP2016070636W WO2017010496A1 WO 2017010496 A1 WO2017010496 A1 WO 2017010496A1 JP 2016070636 W JP2016070636 W JP 2016070636W WO 2017010496 A1 WO2017010496 A1 WO 2017010496A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
contact
output
brake device
rotating member
Prior art date
Application number
PCT/JP2016/070636
Other languages
French (fr)
Japanese (ja)
Inventor
郭裕之
Original Assignee
テイ・エス テック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2015141996A external-priority patent/JP6613673B2/en
Priority claimed from JP2015252142A external-priority patent/JP6509721B2/en
Application filed by テイ・エス テック株式会社 filed Critical テイ・エス テック株式会社
Priority to CN201680019230.XA priority Critical patent/CN107429768B/en
Priority to EP16824476.2A priority patent/EP3324066B1/en
Priority to US15/561,897 priority patent/US10428882B2/en
Publication of WO2017010496A1 publication Critical patent/WO2017010496A1/en

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
    • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
    • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
    • B60N2/04—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable
    • B60N2/16—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the whole seat being movable height-adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • F16D51/10—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as exclusively radially-movable brake-shoes
    • F16D51/12—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as exclusively radially-movable brake-shoes mechanically actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00

Definitions

  • the present invention relates to a brake device used in a vehicle seat height adjustment mechanism or the like.
  • the output shaft rotates by operating a lever provided on the input side that swings up and down.
  • the weight of the seat and the occupant applies a force to the seat to lower the seat.
  • a brake device configured to prevent the output shaft from rotating is used.
  • the brake device of Patent Document 1 three brake shoes (brake cams) are arranged in the circumferential direction on the inner side of the outer ring, and the output-side rotating member is disposed on the inner side in the radial direction of the brake shoe. .
  • the output side rotating member has an opposing surface (a surface facing the brake shoe) in which a part of the outer peripheral surface of the cylinder is cut with a flat surface.
  • the brake device of Patent Document 2 includes an outer ring having a cylindrical inner peripheral surface, a plurality of brake shoes (clamping members) facing the inner peripheral surface, and an output-side rotation disposed inside the brake shoe. And a member (a pinion having a wing).
  • the clamping member is provided in two stages along the axial direction of the pinion. Specifically, a pair of clamping members are provided at one position in the axial direction of the pinion so as to sandwich the central axis of the pinion, and the pair of clamping members are arranged in two stages (two pairs) in the axial direction of the pinion. ), That is, a total of four are provided.
  • Two of the four clamping members (one of the first stage and one of the second stage) stop the rotation of the pinion in the positive direction, and the other two (the remaining one and the second stage).
  • the remaining one of the stages) is designed to stop the rotation of the pinion in the reverse direction.
  • JP 2014-185669 A Japanese translation of PCT publication No. 2002-511035
  • Patent Document 1 when an excessive rotational torque is applied to the output-side rotating member, a portion between the pair of brake surfaces of the cam surface is strongly pressed toward the outside in the radial direction. A large bending load is applied, and in some cases, the brake shoe may be deformed or cracked. Also, when the braking force is generated by the weight of the vehicle seat, that is, when the rotational torque is input from the vehicle seat to the output side rotating member, operate the operation lever to lower the vehicle seat. Then, there is a moment when the contact between the brake shoe and the output side rotating member disappears, so that the braking force may be lost and the vehicle seat may be lowered at a stroke.
  • Patent Document 2 since only one clamping member generates a braking force among two clamping members in one stage with respect to one rotational direction, a stable and sufficient braking force is generated. For this, it is necessary to provide two clamping members. Therefore, there has been a problem that the size of the brake device in the axial direction becomes large.
  • the inventors of the present application have come up with the present invention in the course of research to provide a brake device capable of reducing the load applied to the brake shoe.
  • a brake device includes an outer ring having a cylindrical inner peripheral surface, a plurality of outer rings arranged in a radial direction inside the outer ring in a circumferential direction, and facing the inner peripheral surface.
  • a brake shoe having a pair of brake surfaces that can come into contact with an inner peripheral surface and an inner surface facing the inner side in the radial direction, and an inner surface facing each other on the outer periphery and facing the inner side surface
  • An output-side rotating member having a surface, and an input-side rotating member capable of giving a rotational torque to the output-side rotating member by contacting the brake shoe or the output-side rotating member in a circumferential direction, Even when a rotational torque is applied to the rotating member, in at least one rotation direction, the opposing surface presses the inner surface and the brake surface is pressed against the inner peripheral surface of the outer ring.
  • Shoe is configured so as not to rotate, the brake shoes, between the pair of braking surface, it has a contactable support surface on the inner peripheral surface
  • the support surface of the brake shoe is the inner peripheral surface of the outer ring.
  • the load applied to the portion between the pair of brake surfaces of the brake shoe can be supported by the outer ring.
  • the support surface may be separated from the inner peripheral surface in a state where no load is applied to the brake shoe.
  • the brake shoe may have a protrusion protruding on the outer periphery, and the support surface may be provided on the protrusion.
  • the rigidity of the brake shoe can be improved, the load on the brake shoe can be further reduced.
  • the position where the support surface comes into contact with the inner peripheral surface becomes clear, so that more stable operation can be performed.
  • the support surface may be provided in the center between the pair of brake surfaces.
  • the brake shoe can be stably supported when the support surface comes into contact with the inner peripheral surface, the load applied to the brake shoe can be further reduced.
  • the support surface may have a shape along the inner peripheral surface.
  • the position where the bending stress of the brake shoe is maximized can be supported, so that the load applied to the brake shoe can be further reduced.
  • the facing surface includes a portion that is not parallel to the inner surface
  • the brake device includes a movable piece disposed between the inner surface and the facing surface, and the movable piece.
  • a biasing member that biases the narrow side of the space formed between the inner side surface and the opposing surface, and a load is transmitted between the inner side surface and the opposing surface via the movable piece. It can be set as a structure.
  • the brake shoe when rotational torque is applied to the output side rotation member, the brake shoe does not rotate because the movable piece presses the inner surface and the brake surface is pressed against the inner peripheral surface in at least one rotation direction.
  • the movable piece when the brake shoe is rotated in one rotation direction or the other rotation direction by the input side rotation member, the movable piece is biased to the narrow side of the space formed between the inner surface and the opposing surface. Therefore, the movable piece can be maintained in a state where it is always sandwiched between the inner side surface and the opposing surface, that is, in a state where the movable piece is in contact therewith, and the brake force can be prevented from being released all at once. Thereby, a stable operation can be performed.
  • the support surface is arranged at a position intersecting with a straight line connecting the center of the inner peripheral surface and the movable piece when viewed in the axial direction of the output-side rotating member. be able to.
  • the support surface comes into contact with the inner peripheral surface on the opposite side of the radial direction of the brake shoe from the portion pressed by the movable piece, the load applied to the brake shoe from the movable piece is efficiently absorbed by the support surface. Can support well. Thereby, the load concerning a brake shoe can be reduced more.
  • the inner side surface has a first contact surface that can contact the movable piece and is parallel to a direction connecting both ends of the pair of brake surfaces in the circumferential direction.
  • the opposing surface may have a second contact surface that can contact the movable piece and is inclined with respect to the first contact surface when no load is applied to the brake shoe.
  • the movable piece presses the inner surface of the brake shoe and the brake surface is pressed against the inner peripheral surface of the outer ring in at least one rotation direction.
  • the brake shoe does not rotate.
  • the movable piece is placed on the narrow side of the space formed between the inner surface and the opposed surface of the output side rotation member. Since it is energized, the movable piece can always be held between the inner surface and the opposite surface, that is, in contact with these, and the brake force can be prevented from being released at once. it can.
  • the braking force can be generated by each of the plurality of brake shoes arranged in the circumferential direction, it is possible to suppress an increase in the size in the axial direction. As a result, the size in the axial direction can be reduced, and stable operation can be performed.
  • the movable piece is sandwiched between and in contact with the first contact surface on the inner surface and the second contact surface that is inclined with respect to the first contact surface on the opposite surface, so that the movable piece is movable. The piece can be held stably and play of the movable piece can be suppressed.
  • the second contact surface includes an inclined portion that passes through the center of the inner peripheral surface and is inclined so as to approach the first contact surface as the distance from the reference plane orthogonal to the first contact surface increases. It can be.
  • the second contact surface may have a first curved surface portion that protrudes toward the brake shoe when viewed along the axial direction of the output-side rotating member.
  • the second contact surface can be configured to have a smaller radius of curvature the further away from the reference plane.
  • the output side rotation member when the output side rotation member further rotates, the increase in the angle formed by the first contact surface and the second contact surface can be further suppressed and maintained in a more appropriate range. Brake force can be generated.
  • the pinching angle which is the angle formed between the tangential plane of the second contact surface and the first contact surface at the point where the second contact surface and the movable piece contact each other, is the rotational torque input to the output side rotating member.
  • the second contact surface may be formed so as to decrease after increasing as the rotation angle of the output side rotation member increases.
  • the maximum value of the included angle is desirably 7.55 degrees or less.
  • the pinching angle does not become too large. It is suppressed that it slides and moves to the wide side between an inner surface and an opposing surface.
  • the second contact surface may be arranged one by one at both ends on the outer side in the circumferential direction on the facing surface.
  • the brake shoe when rotational torque is given to the output side rotation member, the brake shoe can be configured not to rotate in both the one rotation direction and the other rotation direction.
  • the facing surface may have a connection surface portion that connects the second contact surfaces at both ends.
  • the facing surface may be configured to have a recess in the connection portion between the second contact surface and the connection surface portion.
  • the movable piece can be assembled along the concave portion with the concave portion as a mark, and after the movable piece is assembled, the movable piece can be temporarily fixed by fitting the movable piece into the concave portion. It is easy to assemble the biasing member between them. That is, the movable piece and the urging member can be easily assembled.
  • connection surface portion may have a flat surface portion.
  • connection surface portion has a surface that is convex toward the brake shoe side and a configuration that has a surface that is concave toward the side opposite to the brake shoe side
  • a moderately sized space can be secured between the surface portion and the brake shoe.
  • the biasing member arranged in the space can be easily assembled.
  • the output-side rotating member may have a second curved surface portion that connects the opposing surfaces corresponding to the brake shoes.
  • the movable piece may be a roller.
  • the load resistance can be increased as compared with the case where a sphere is used as the movable piece, and since the operation is smoother than that in the case of a polygon, a stable operation can be realized.
  • the input-side rotating member can have an engaging portion that can engage with the output-side rotating member and transmit the rotational torque.
  • the engaging portion can directly engage with the output-side rotating member and transmit torque to the output-side rotating member, the rotational force is applied to the output-side rotating member from the outside.
  • the rotational force is input to the input side rotating member in the direction opposite to the above, the rotational force input to the output side rotating member can be directly supported by the input side rotating member and the output side rotating member can be rotated. Therefore, the brake force is not suddenly lost and the output side rotating member does not rotate in an unintended direction, and a stable operation can be realized.
  • the input side rotating member is set as the rotational torque. It is desirable that the engaging portion is arranged so that the engaging portion engages with the output-side rotating member before the input-side rotating member engages with the brake shoe when rotated in the reverse direction.
  • the input-side rotating member starts to rotate the output-side rotating member by engaging the engaging portion and the output-side rotating member without rotating the brake shoe that is applied with a large frictional force with the outer ring. For this reason, the output-side rotating member can be started to rotate with a small initial load, and the catching feeling can be suppressed.
  • FIG. 4 is a ZZ sectional view of the clutch unit of FIG. It is the figure which looked at the input side rotation member from the output side. It is a cross-sectional view of a ratchet device. It is the perspective view which looked at the clutch unit from the cover member side.
  • a clutch unit 1 As shown in FIG. 1, a clutch unit 1 according to an embodiment including the brake device of the present invention is a known height adjuster for adjusting the height of a seat cushion S1 of a vehicle seat S as an example of a vehicle seat. Applies to the mechanism.
  • a lever LV is attached to the operation input member 50, and the height of the seat cushion S 1 can be adjusted by driving a height adjustment mechanism by rotating an output side rotation member 30 described later by operating the lever LV. is there.
  • the clutch unit 1 is configured by housing each member in a housing 100.
  • the housing 100 is configured by a combination of the outer ring 10, the mounting plate 85 and the cover member 60.
  • the left side in FIG. 2 where the cover member 60 and the operation input member 50 are arranged is referred to as “input side”
  • the right side in FIG. 2 where the output side rotation member 30 is arranged is referred to as “output side”. Called.
  • the clutch unit 1 is provided on the input side, and transmits and blocks the input torque generated by the swinging operation of the operation input member 50.
  • the clutch unit 1 is provided on the output side, and the input torque from the ratchet device 2 is output to the output side rotating member. 30 and a brake device 3 for cutting off the reverse input torque from the output gear 35.
  • the ratchet device 2 includes an operation input member 50, a regulating member 71, a roller 72, and a return spring 73.
  • the brake device 3 includes an outer ring 10, a brake shoe 20, an output side rotating member 30, an input side rotating member 40, a roller 81 as an example of a movable piece, and a spring 82 as an example of an urging member.
  • a friction ring 83 and a washer 75 are provided.
  • the input side rotating member 40 is an output member of the ratchet device 2 and an input member of the brake device 3, and can be referred to as any part of the ratchet device 2 and the brake device 3.
  • the outer ring 10 is formed of a ring having a predetermined thickness, and includes a cylindrical inner peripheral surface 11, a cylindrical outer peripheral surface 12, and a pair of side surfaces 13 and 14 that connect the inner peripheral surface 11 and the outer peripheral surface 12. Yes.
  • the pair of side surfaces 13 and 14 are located on the radially outer side of the outer ring 10 with respect to the inner peripheral surface 11, and are flat surfaces orthogonal to the axis of the inner peripheral surface 11. In the present specification, the radial direction and the circumferential direction are based on the outer ring 10.
  • the mounting plate 85 that constitutes a part of the housing 100 together with the outer ring 10 is a sheet metal member for supporting the brake device 3.
  • the attachment plate 85 is formed with two attachment holes 85B as attachment portions for attaching the brake device 3 to the frame of the seat cushion S1.
  • the mounting plate 85 has a through hole 85 ⁇ / b> A through which the output side rotation member 30 is passed. Since the outer ring 10 is fixed to the attachment plate 85, the clutch unit 1 can be attached to various devices.
  • the outer ring 10 is formed by punching a thick plate by press molding, and is welded to the input side surface of the mounting plate 85 at the outer peripheral edge 14B of the output side surface 14 by laser welding. As shown in FIG. 9, this welding is performed over the entire circumference of the side surface 14 (outer peripheral edge 14B). Since the mounting plate 85 is welded over the entire circumference of the side surface 14 of the outer ring 10, the strength of welding can be increased and the outer ring 10 can be reinforced by the mounting plate 85. The side surface 14 and the mounting plate 85 are welded along the outermost peripheral portion of the annular side surface 14, so that the welding holding force against the force in the rotational direction is high.
  • the brake shoes 20 are members that generate a braking force with the outer ring 10, and three brake shoes 20 are arranged on the inner side in the radial direction of the outer ring 10 at equal intervals in the circumferential direction.
  • the brake shoe 20 includes a main body portion 20A that extends in the circumferential direction, and a protruding portion 20B and a protrusion 20C that protrude outward in the radial direction on the outer periphery of the main body portion 20A.
  • Each protrusion 20B is provided at each circumferential end of the outer periphery of the main body 20A.
  • Each protrusion 20 ⁇ / b> B has a brake surface 21 that faces the inner peripheral surface 11 of the outer ring 10 and can contact the inner peripheral surface 11 at the distal end on the radially outer side.
  • the brake surface 21 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10 and contacts the inner peripheral surface 11 of the outer ring 10 near the outer side in the circumferential direction of the brake surface 21 as shown in FIG.
  • the protrusion 20C is provided at the circumferential center of the outer periphery of the main body 20A.
  • a support surface 26 capable of abutting on the inner peripheral surface 11 of the outer ring 10 is provided at the radially outer end of the protrusion 20C.
  • the support surface 26 is provided at the center between the pair of brake surfaces 21.
  • the support surface 26 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10, and has a cylindrical surface shape along the inner peripheral surface 11 of the outer ring 10.
  • the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10 in a state where no load is applied to the brake shoe 20 and the output-side rotating member 30.
  • the brake shoe 20 includes a cylindrical outer peripheral surface having a smaller diameter than the brake surface 21 between one of the pair of brake surfaces 21 and the support surface 26 and between the other of the pair of brake surfaces 21 and the support surface 26. 22. Further, the brake shoe 20 has an inner side surface 23 facing inward in the radial direction. And the brake shoe 20 has the end surface 24 which connects the both ends of the inner surface 23, and the edge part 21E of the two brake surfaces 21 in the edge part of the circumferential direction. Further, the brake shoe 20 has a rotational force input surface 25 facing the circumferential direction at a step between the brake surface 21 and the outer peripheral surface 22.
  • the support surface 26 is at least partially within the same range as the pair of brake surfaces 21 in the axial direction of the output side rotation member 30. That is, there is at least one plane orthogonal to the output side rotation member 30 that passes through the pair of brake surfaces 21 and the support surface 26 together.
  • the thickness of the pair of protrusions 20B and the thickness of the protrusions 20C are substantially equal (see FIG. 2), and the support surface 26 in the axial direction of the output-side rotating member 30 is substantially the entire pair. Within the same range as the brake surface 21.
  • Each of the inner side surfaces 23 has three surfaces that are opposed to a later-described facing surface 36 of the output side rotating member 30.
  • the inner side surface 23 includes a first contact surface 23A, a first inclined surface 23B disposed on the counterclockwise side of the drawing with respect to the first contact surface 23A, It has the 1st inclined surface 23C arrange
  • the first contact surface 23A is in contact with the roller 81 and has a direction along a straight line L1 (see FIG. 3) connecting the circumferential ends 21E of the pair of brake surfaces 21 (see FIG. 4A). It is a plane parallel to the connection direction indicated by the arrow.
  • the first inclined surfaces 23B and 23C are flat surfaces that are inclined with respect to the first contact surface 23A so as to approach the facing surface 36 (the lower side in the figure) as they move away from the first contact surface 23A between them. .
  • the output side rotation member 30 includes a shaft-like action part 31, a flange 32 formed on the output side of the action part 31, and projects from the action part 31 to the input side.
  • a coaxial and small-diameter support shaft portion 33 protrudes from the support shaft portion 33 to the input side, is coaxial with the support shaft portion 33, has a small-diameter shaft portion 37, and protrudes to the output side of the flange 32.
  • An output gear 35 is provided.
  • the output side rotation member 30 is disposed on the radially inner side of each brake shoe 20. The output gear 35 protrudes to the output side through the through hole 85 ⁇ / b> A of the mounting plate 85.
  • the action portion 31 has a facing surface 36 facing the inner side surface 23 of the brake shoe 20 and a curved surface portion 38 as an example of a second curved surface portion on the outer periphery thereof.
  • Three opposing surfaces 36 are provided on the outer periphery of the action portion 31 corresponding to the inner surface 23 of each brake shoe 20.
  • the curved surface portion 38 is a portion that connects the facing surfaces 36 corresponding to the brake shoes 20, and there is a total of 3 one pair between the facing surfaces 36 adjacent to each other in the circumferential direction of the outer periphery of the action portion 31.
  • the curved surface portion 38 is formed as a curved surface having a circular arc shape in sectional view with the rotation center of the output side rotation member 30 as the center.
  • the facing surface 36 includes second contact surfaces 36 ⁇ / b> A and 36 ⁇ / b> B arranged one by one on both ends of the facing surface 36 in the circumferential direction, and each second contact on both ends.
  • a connecting surface portion 36C that connects the surfaces 36A and 36B.
  • the second contact surface 36A is disposed on the counterclockwise side in the drawing with respect to the connection surface portion 36C
  • the second contact surface 36B is disposed on the clockwise side in the drawing with respect to the connection surface portion 36C.
  • the second contact surfaces 36A and 36B are capable of contacting the roller 81 in a state where no load is applied to the brake shoe 20, and are inclined with respect to the first contact surface 23A and outside the inclined portion 361.
  • a curved surface portion 362 as an example of a first curved surface portion, which are arranged continuously.
  • the inclined portion 361 passes through the center 11C (see FIG. 3) of the inner peripheral surface 11 of the outer ring 10 and approaches the first contact surface 23A (upper side in the drawing) as the distance from the reference plane PL orthogonal to the first contact surface 23A increases. It is inclined to.
  • the curved surface portion 362 is a convex shape that is convex toward the brake shoe 20 when viewed along the axial direction of the output-side rotating member 30, and the curved surface has a curvature radius that decreases as the distance from the reference plane PL increases. Yes.
  • the facing surface 36 includes a portion non-parallel to the first contact surface 23 ⁇ / b> A that is a part of the inner surface 23 of the brake shoe 20.
  • the second contact surfaces 36A and 36B are formed by the first contact surface 23A and the tangential plane of the second contact surfaces 36A and 36B at the point where the second contact surfaces 36A and 36B contact the roller 81.
  • the pinching angle ⁇ (see FIG. 3 for the pinching angle ⁇ ) increases and then decreases as the rotation angle of the output side rotation member 30 increases when the rotation torque is input to the output side rotation member 30. It is formed as follows.
  • the roller 81 slides between the first contact surface 23A and the second contact surfaces 36A, 36B, and the first contact surface 23A and the second contact surfaces 36A, 36B It is desirable that the maximum value is 7.55 degrees or less because it is easy to move to the wide side of the space between.
  • connection surface portion 36C has a flat surface portion 36D provided at the center portion in the circumferential direction and inclined portions 36E provided at both end portions in the circumferential direction.
  • the plane portion 36D is a plane orthogonal to the reference plane PL in a state where no load is input to the brake shoe 20 and the output side rotating member 30. Accordingly, the flat portion 36D is arranged in parallel with the first contact surface 23A in a state where no load is input to the brake shoe 20 and the output-side rotating member 30.
  • the inclined portion 36E is inclined so as to be away from the first contact surface 23A from the end of the flat surface portion 36D toward the inner end in the circumferential direction of the second contact surfaces 36A and 36B as the distance from the reference plane PL increases. Yes.
  • the opposing surface 36 is a recessed portion formed by the end portion on the inner side in the circumferential direction of the second contact surfaces 36A and 36B and the inclined portion 36E at the connection portion between the second contact surfaces 36A and 36B and the connection surface portion 36C. 36F.
  • the distance between the first contact surface 23A and the connection surface portion 36C (plane portion 36D) is smaller than the diameter of the roller 81. But the space
  • a pair of rollers 81 is disposed between the inner surface 23 of each brake shoe 20 and each opposing surface 36 of the output side rotating member 30.
  • the roller 81A is the one disposed on the counterclockwise side in FIG. 3 and the one disposed on the clockwise side in FIG. Let it be a roller 81B.
  • the roller 81A is in contact with the first contact surface 23A and the second contact surface 36A, and the roller 81B is in contact with the first contact surface 23A.
  • roller 81 is disposed between the inner surface 23 and the facing surface 36, so that in the brake device 3, a load is transmitted between the inner surface 23 and the facing surface 36 via the roller 81.
  • the springs 82 are compression coil springs, and are provided one by one between the pair of rollers 81A and 81B.
  • the spring 82 urges the pair of rollers 81 ⁇ / b> A and 81 ⁇ / b> B toward the narrow side of the space formed between the inner surface 23 and the facing surface 36 by separating them in the circumferential direction.
  • the input side rotating member 40 shown in FIG. 2 can rotate around the axes of the outer ring 10 and the output side rotating member 30, receives the rotational output of the ratchet device 2, and hits the brake shoe 20 of the brake device 3 in the circumferential direction. It is a member that can contact and give rotational torque to the brake shoe 20.
  • the input-side rotating member 40 includes a cylindrical pressure-receiving ring portion 41, a plurality of engagement legs 42 that protrude from the pressure-receiving ring portion 41 toward the output side, and a radially inner side from the vicinity of the axial center of the pressure-receiving ring portion 41.
  • a plate-like portion 43 extending toward the output side, a holding portion 44 see FIG.
  • the inner peripheral surface 41A of the pressure receiving ring portion 41 has a circular cross section.
  • Three pairs of engagement legs 42 are provided at equal intervals corresponding to each brake shoe 20, and are arranged between the inner peripheral surface 11 of the outer ring 10 and the outer peripheral surface 22 of the brake shoe 20.
  • the pair of engaging legs 42 includes an engaging leg 42A disposed between the protrusion 20C and the anticlockwise protrusion 20B of FIG. 3, and the protrusion 20C and the clockwise protrusion of FIG.
  • the engaging leg 42B is disposed between the portions 20B.
  • the sizes of the protrusion 20B, the protrusion 20C and the engagement legs 42A and 42B are set so that slight play can be made in the circumferential direction.
  • Each engagement leg 42A, 42B is formed in substantially the same shape.
  • the holding portion 44 is a portion that suppresses the roller 81 from falling off between the inner surface 23 and the facing surface 36, and is disposed adjacent to the circumferential direction of the roller 81. Specifically, a pair of rollers 81A and 81B corresponding to each brake shoe 20 are disposed adjacent to both sides in the circumferential direction, and a total of three are provided.
  • the holding portion 44 is disposed away from the roller 81 in a state where no load is input to the input side rotating member 40 and the output side rotating member 30. More specifically, the holding unit 44 is a roller 81 adjacent to the upstream side in the rotation direction of the rotation torque in a state where the rotation torque in the normal use range is input to the output side rotation member 30. It arrange
  • the holding unit 44 rotates the input-side rotating member 40 in the same rotational direction as the rotational torque of the output-side rotating member 30 from the state where the rotating torque is input to the output-side rotating member 30, so At the time of contact in the direction, the roller 81 adjacent to the downstream side in the rotation direction, in this embodiment, is arranged so as not to contact the roller 81A.
  • the holding portion 44 contacts the roller 81 adjacent to the downstream side in the rotation direction of the holding portion 44 in a state where the input-side rotating member 40 is in contact with the brake shoe 20 in the circumferential direction to rotate the brake shoe 20.
  • the holding portion 44 may be in non-contact with the roller 81 in a state where the brake shoe 20 is rotated by the input side rotation member 40.
  • the through hole 45 allows the action part 31 of the output side rotation member 30 to be inserted, and on its inner periphery, three circumferential surface parts 46 along the curved surface part 38 of the action part 31, and It has 3 convex surface parts 47 which are arrange
  • Each convex surface portion 47 includes a top portion 47A that protrudes inward in the radial direction, a release surface 47B that is adjacent to the top portion 47A on the clockwise side in FIG. 7 (counterclockwise side in FIG. 3), and a counterclockwise direction in FIG. And a flank 47C adjacent to the rotation side (clockwise side in FIG. 3).
  • the release surface 47B is arranged to face the facing surface 36, and the input of the clockwise rotational torque in FIG. 3 to the output side rotating member 30 due to the weight of the occupant sitting on the vehicle seat S is input.
  • the side rotation member 40 is rotated in the rotation direction opposite to the rotation torque (counterclockwise direction in FIG. 3) and brought into contact with the brake shoe 20 in the circumferential direction, the counter surface 36 rotates in the opposite direction substantially simultaneously. It has a shape that can transmit rotational torque in the direction.
  • the clearance surface 47C has an angle of the release surface 47B with respect to the flat surface portion 36D (see FIG. 4) of the opposing surface 36 in a state in which no load is input from the outside to the input side rotation member 40 and the output side rotation member 30.
  • the flank 47C has the same angle with respect to the flat surface portion 36D as the angle with respect to the flat surface portion 36D of the release surface 47B, and the release surface 47B in the clockwise direction of the input side rotation member 40 in FIG. It may have the same function.
  • the friction ring 83 is a member that generates friction for suppressing the sudden start of the operation of the output side rotating member 30 at the moment when the braking force of the brake device 3 is broken.
  • the friction ring 83 includes a ring portion 83A having a hole that substantially matches the outer periphery of the action portion 31 of the output-side rotating member 30, and a radially outer portion extending from the ring portion 83A.
  • Three friction generating arms 83B that are in pressure contact are provided.
  • the friction ring 83 is configured to rotate integrally with the output-side rotating member 30 when the hole of the ring portion 83 ⁇ / b> A is engaged with the action portion 31.
  • the friction ring 83 is disposed on the output side of the brake shoe 20.
  • the friction generating arm 83B is inclined with respect to the radial direction so as to be located in the clockwise direction in FIG. For this reason, when the friction ring 83 rotates in the clockwise direction in FIG. 3, the friction ring 83 is likely to bite against the inner peripheral surface 11, so that a larger frictional force can be generated than when the friction ring 83 rotates counterclockwise. Therefore, when the clutch unit 1 is applied to the brake of the height adjustment mechanism of the vehicle seat S, the vehicle seat S is assembled so that it is lowered when the output side rotation member 30 rotates in the clockwise direction of FIG. And the undesired descent
  • the washer 75 has a hole 75 ⁇ / b> A having a diameter slightly smaller than the outer diameter of the shaft portion 37 of the output side rotating member 30, and the hole 75 ⁇ / b> A is press-fitted into the shaft portion 37 (see FIG. 6). ).
  • the outer diameter of the washer 75 is larger than the support hole 64 of the cover member 60 described later, so that the output-side rotating member 30 cannot be pulled out to the output side by the washer 75.
  • the operation input member 50 engages with the lever LV and can swing integrally with the lever LV, and moves integrally with the input side rotation member 40 via the roller 72.
  • the operation input member 50 includes a cam plate portion 51 and two lever engaging portions 52 extending from the cam plate portion 51 to the input side.
  • the cam plate portion 51 has three small-diameter portions 53 and three large-diameter portions 54 arranged alternately on the outer peripheral surface, and the small-diameter portion 53 and the large-diameter portion 54 are made of a plane.
  • the facing surface 55 is connected. Since there are six places where the small-diameter portion 53 and the large-diameter portion 54 are switched, six opposing surfaces 55 are formed correspondingly.
  • the facing surface 55 is formed so that the distance from the central axis gradually changes.
  • a roller 72 is disposed between each facing surface 55 and the inner peripheral surface 41A of the pressure receiving ring portion 41, respectively. As will be understood from the description of the operation described later, the roller 72 engages and disengages the operation input member 50 and the input side rotation member 40 to transmit and block input torque.
  • a total of six rollers 72 are arranged corresponding to the opposing surfaces 55. As shown in FIG. 6, the facing surface 55 is longer in the direction than half of the axial length of the roller 72, and contacts the roller 72 in a range including the central portion (refer to the center line C ⁇ b> 1) in the axial direction of the roller 72. Arranged to be possible. Thereby, the opposing surface 55 can stably hold the roller 72 between the pressure receiving ring portion 41.
  • the regulating member 71 is a member that regulates the position of the roller 72, and includes a side wall portion 71 ⁇ / b> A that covers the output side surface of the plurality of rollers 72, and the side wall portion 71 ⁇ / b> A. And three restricting portions 71B extending from the outer peripheral edge toward the input side.
  • the restricting portion 71 ⁇ / b> B is longer than the length of the roller 72 in the axial direction, and its tip is press-fitted into the fitting hole 66 of the cover member 60.
  • the restricting portion 71 ⁇ / b> B is disposed at the same rotational position on the radially outer side of the large-diameter portion 54 when the lever LV is not operated, and the opposing surface 55 and the pressure-receiving ring portion 41.
  • the movement of the roller 72 between them in the circumferential direction is restricted.
  • return springs 73 made of compression coil springs are arranged with an initial load applied. For this reason, at the time of non-operation of FIG. 8, each roller 72 is in contact with the restricting portion 71B.
  • the restricting portion 71 ⁇ / b> B is disposed so as to include a position where the center of the roller 72 is located in the radial direction of the outer ring 10, and is in contact with the most protruding portion of the roller 72 in the circumferential direction. Thereby, the control part 71B can support the roller 72 stably.
  • the roller 72 is shown in contact with the restricting portion 71B, but the roller 72 is slightly separated from the restricting portion 71B by being sandwiched between the opposing surface 55 and the inner peripheral surface 41A. It may be.
  • the lever engaging portion 52 extends from the cam plate portion 51 with an arcuate cross section.
  • the lever engaging portion 52 is engaged with the lever LV (not shown).
  • the cover member 60 includes a disk-shaped side wall portion 61, a cylindrical outer peripheral portion 62 that extends from the outer peripheral edge of the side wall portion 61 to the output side, and a flange 63 that extends radially outward from the output-side end portion of the outer peripheral portion 62. And comprising. As shown in FIGS. 6 and 9, the flange 63 is fitted to the side surface 13 of the outer ring 10 and welded to the side surface 13 by laser welding along the outer peripheral edge thereof. The outer ring 10 is reinforced by welding the cover member 60 in this way. This welding is performed over the entire circumference of the flange 63.
  • the side wall 61 has a circular support hole 64 at its center, two arc holes 65 extending in an arc shape around the support hole 64, and a position radially outside the arc hole 65. And three fitting holes 66 arranged at equal intervals in the circumferential direction are formed.
  • the support hole 64 is a portion that fits with the support shaft portion 33 of the output side rotation member 30 and pivotally supports the output side rotation member 30.
  • the arc hole 65 is provided corresponding to the lever engaging portion 52 of the operation input member 50, and is formed in an arc shape in a wider angle range than the lever engaging portion 52. As a result, the arc hole 65 receives the lever engaging portion 52, and the lever engaging portion 52 can move within the arc hole 65 within a predetermined angle range.
  • the fitting holes 66 are three through holes provided corresponding to the three regulating portions 71 ⁇ / b> B of the regulating member 71, and are fitted with the cover member 60 so that the regulating member 71 does not rotate relative to the cover member 60. Has been. Since the regulating member 71 and the cover member 60 are fitted at a plurality of locations, the regulation member 71 can be firmly regulated to rotate.
  • the roller 72 In the neutral position shown in FIG. 8, the roller 72 is located between the inner peripheral surface 41 ⁇ / b> A of the input side rotating member 40 and the opposing surface 55 of the operation input member 50, but there is a slight gap between them. It is not pinched by.
  • the roller 72 is pressed against the restricting portion 71B by a return spring 73.
  • the operation input member 50 is slightly swung clockwise by the operation of the lever LV, the facing surface 55 rotates clockwise to contact the roller 72, and the roller 72 moves between the inner peripheral surface 41 ⁇ / b> A and the facing surface 55. It is pinched.
  • the operation input member 50 and the input side rotation member 40 can rotate integrally. Therefore, as shown in FIG. 10, if the operation input member 50 is rotated clockwise, the input side rotation member 40 and the operation input member 50 are rotated clockwise while being integrated. That is, the input torque obtained by rotating the operation input member 50 is transmitted to the input side rotation member 40.
  • the output side rotation member 30 when the output side rotation member 30 is given a rotation torque in the clockwise direction in the drawing, that is, a rotation torque in the normal use range, by the weight of the occupant sitting on the vehicle seat S, the output side rotation member 30 slightly rotates clockwise, and the distance between the second contact surface 36A (one of the pair of second contact surfaces 36A and 36B of the one opposing surface 36 on the counterclockwise side) and the first contact surface 23A is narrow.
  • the pressures of the roller 81A one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side
  • the second contact surface 36A, and the first contact surface 23A are increased.
  • the roller 81A When the roller 81A is in contact with the first inclined surface 23B in a state where no load is input to the output-side rotating member 30, the roller 81A rolls between the facing surface 36 and the inner side surface 23, When it moves to a position in contact with the first contact surface 23A, the pressure between the second contact surface 36A and the first contact surface 23A is sufficiently increased and stops against the opposing surface 36 and the inner surface 23.
  • the second contact surface 36B one of the pair of second contact surfaces 36A, 36B of the one opposing surface 36 on the clockwise side
  • the roller 81B (one of the pair of rollers 81 corresponding to one brake shoe 20 on the clockwise side) is strongly sandwiched between the second contact surface 36B and the first contact surface 23A. You can roll without being caught.
  • the brake shoe 20 has the pair of brake surfaces 21 pressed against the inner peripheral surface 11 of the outer ring 10 with the force F3.
  • a frictional force is generated between the brake surface 21 and the inner peripheral surface 11, so that the output side rotating member 30 does not rotate. That is, a braking force that prevents the vehicle seat S from being lowered is generated.
  • the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.
  • the roller 81B is slightly separated from the holding portion 44 adjacent in the rotation direction of the output side rotation member 30, that is, the clockwise direction. Therefore, not only the roller 81A is sandwiched between the facing surface 36 and the inner side surface 23, but also the roller 81B can be maintained between the facing surface 36 and the inner side surface 23 by the biasing force of the spring 82. Thereby, even if the brake shoe 20 is rotated in any direction thereafter, the frictional force between the brake shoe 20 and the outer ring 10 can be maintained, so that an unexpected release of the braking force can be suppressed.
  • the input side rotating member 40 When the input side rotating member 40 is rotated counterclockwise by operating the lever LV to raise the height of the vehicle seat S from the brake state of FIG. 12, as shown in FIG. 13, the input side rotating member 40
  • the engaging leg 42A contacts the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the end on the counterclockwise side.
  • the release surface 47B of the input side rotation member 40 comes into contact with the flat surface portion 36D of the opposing surface 36 at substantially the same time, so that the counterclockwise rotation torque can be transmitted to the output side rotation member 30.
  • the brake shoe 20 and the output side rotating member 30 are relatively opposite to the case where the output side rotating member 30 is rotated clockwise in FIG. To work. That is, as shown in FIG. 15, the brake shoe 20 is slightly rotated clockwise, and the first contact surface 23A and the second contact surface 36B (the pair of second contact surfaces 36A and 36B of one opposing surface 36 is a timepiece). By reducing the distance between the one on the rotation side), the roller 81B (one of the rollers 81 corresponding to one brake shoe 20 on the clockwise side), the first contact surface 23A and the second contact surface 36B. Increased pressure.
  • roller 81B rolls between the opposing surface 36 and the inner side surface 23 and moves to a position in contact with the first contact surface 23A.
  • the pressure between 36 ⁇ / b> B and the first contact surface 23 ⁇ / b> A is sufficiently increased and stops against the facing surface 36 and the inner surface 23.
  • the roller 81A (one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side) is located between the first contact surface 23A and the second contact surface 36A. You can roll while the pressure of the water gradually decreases. And in the state of FIG. 15, the holding
  • the holding portion 44 is not in contact with the roller 81A, so that the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force.
  • the roller 81A that has generated the braking force is not pushed by the holding portion 44, the braking force is prevented from being unexpectedly weakened.
  • the holding portion 44 comes into contact with the roller 81A. Even in a case where the inner surface 23 and the facing surface 36 are fixed due to some circumstances, the roller 81A is separated from the inner surface 23 and the facing surface 36 to release the braking force, thereby realizing a stable operation. be able to.
  • 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
  • the roller 81B pushes the second contact surface 36B with the force F23.
  • the output side rotation member 30 rotates clockwise in the figure.
  • the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.
  • the brake shoe 20 is deformed so that the main body portion 20 ⁇ / b> A bends radially outward, and the support surface 26 contacts the inner peripheral surface 11 of the outer ring 10.
  • the support surface 26 of the brake shoe 20 is supported by the outer ring 10, and further deformation is suppressed, so that the load on the brake shoe 20 can be reduced.
  • the roller 81 pushes the inner side surface 23 of the brake shoe 20 so that the brake surface 21 is moved.
  • the brake shoe 20 does not rotate by being pressed against the inner peripheral surface 11 of the outer ring 10.
  • the roller 81 is formed between the inner surface 23 and the facing surface 36 of the output side rotation member 30. Since one of the rollers 81 is always sandwiched between the inner surface 23 and the facing surface 36, that is, in contact with these, since it is biased to the narrow side of the space, it can be maintained.
  • the brake force can be generated by each of the plurality of brake shoes 20 arranged in the circumferential direction, it is possible to suppress an increase in the size of the brake device 3 in the axial direction. As a result, the size in the axial direction can be reduced, and stable operation can be performed.
  • the roller 81 is sandwiched between the first contact surface 23A of the inner surface 23 and the second contact surfaces 36A and 36B of the facing surface 36 that are inclined with respect to the first contact surface 23A, and comes into contact therewith. As a result, the roller 81 can be stably held and play of the roller 81 can be suppressed.
  • the second contact surfaces 36A and 36B have curved surfaces that are convex toward the brake shoe 20, the first contact surface 23A and the second contact surface 23A when the output-side rotating member 30 is further rotated.
  • An increase in the angle formed by the contact surfaces 36A, 36B (specifically, the tangential plane in contact with the contact portion between the second contact surfaces 36A, 36B and the roller 81) can be suppressed and maintained in an appropriate range.
  • the roller 81 is restrained from moving to the wide side between the first contact surface 23A and the second contact surfaces 36A, 36B, so that the roller 81 is moved to the first contact surface 23A and the second contact surfaces 36A, 36B. It can be maintained in a state of being sandwiched between (a state in which the pressure is increased). Thereby, since a braking force can be maintained, a braking force can be generated stably.
  • the second contact surfaces 36A and 36B have a radius of curvature that decreases with distance from the reference plane PL. Therefore, the first contact surface 23A and the second contact surface when the output-side rotating member 30 rotates further.
  • the increase in the angle formed by 36A and 36B can be further suppressed and maintained in a more appropriate range.
  • the pinching angle ⁇ increases and then decreases, thereby suppressing the pinching angle ⁇ from becoming excessive.
  • the sliding movement between the first contact surface 23A and the second contact surfaces 36A, 36B is suppressed.
  • the roller 81 can be satisfactorily maintained in a state of being sandwiched between the first contact surface 23A and the second contact surfaces 36A, 36B, so that the braking force can be generated more stably.
  • the second contact surfaces 36A and 36B are arranged one by one at both ends of the facing surface 36, when rotational torque is applied to the output-side rotating member 30, one rotational direction and the other rotational direction In both cases, a configuration in which the brake shoe 20 does not rotate can be realized.
  • the roller 81 can be assembled along the recess 36F using the recess 36F as a mark. After the assembly, the roller 81 can be temporarily fixed by fitting the roller 81 into the recess 36F, so that the spring 82 is easily assembled between the two rollers 81. That is, according to the brake device 3, the roller 81 and the spring 82 can be easily assembled.
  • the connecting surface portion 36C has a flat flat surface portion 36D
  • the connecting surface portion 36C has a surface that protrudes toward the brake shoe side instead of the flat surface portion 36D, or on the side opposite to the brake shoe side.
  • a space having an appropriate size can be secured between the connection surface portion 36C and the brake shoe 20.
  • positioned in the said space can be assembled
  • the movable piece is the roller 81
  • the load resistance can be increased by increasing the contact area with the inner side surface 23 and the facing surface 36 as compared with the case where a sphere is used as the movable piece.
  • the movable piece is the roller 81, the operation is smoother than that of the polygonal shape, and thus a stable operation can be realized.
  • the support surface 26 is separated from the inner peripheral surface 11 in a state where no load is applied to the brake shoe 20, when the excessive torque is not applied to the output side rotation member 30, that is, normally When a rotational torque in the use range is applied, the braking force is generated by the pair of brake surfaces 21 provided at both ends in the circumferential direction of the outer periphery of the brake shoe 20, so that the braking force can be stabilized.
  • an excessive rotational torque is applied to the output-side rotating member 30 and the support surface 26 contacts the inner peripheral surface 11, excessive bending of the brake shoe 20 can be suppressed. The force received from the can is received firmly, and a large braking force can be generated.
  • the rigidity of the brake shoe 20 can be improved. In this way, the load applied to the brake shoe 20 can be further reduced by improving the rigidity of the brake shoe 20 itself. Further, when the support surface 26 comes into contact with the inner peripheral surface 11, the position where the support surface 26 and the inner peripheral surface 11 come into contact becomes clear, so that a more stable operation can be performed.
  • the support surface 26 is provided at the center between the pair of brake surfaces 21, the position where the bending stress of the brake shoe 20 is maximized when the support surface 26 abuts against the inner peripheral surface 11 is supported. can do. Thereby, the load applied to the brake shoe 20 can be further reduced.
  • the brake shoe 20 can be stably supported when the support surface 26 abuts against the inner peripheral surface 11. Thereby, the load applied to the brake shoe 20 can be further reduced.
  • the input-side rotating member 40 has a through hole 45 having a substantially circular outline, and three engaging portions 45 ⁇ / b> A are formed to protrude from the inner peripheral surface thereof.
  • the engaging portions 45A are arranged at equal intervals in the circumferential direction, and are adjacent to the second contact surface 36A in FIG. 17 on the counterclockwise side (clockwise side in FIG. 18). For this reason, the input-side rotating member 40 can be engaged with the action portion 31 of the output-side rotating member 30 in the circumferential direction at the engaging portion 45 ⁇ / b> A to transmit the rotational torque to the output-side rotating member 30. Yes.
  • the engaging leg 42A and the holding portion 44 protruding toward the output side are slightly different in arrangement or size from the first embodiment. Specifically, the holding portion 44 is slightly larger in the circumferential direction than in the first embodiment. Further, the engaging leg 42 ⁇ / b> A and the engaging portion 45 ⁇ / b> A cause the input-side rotating member 40 to rotate when the rotating torque is input to the output-side rotating member 30 and the rotating torque is received by the braking force of the brake shoe 20.
  • the engaging portion 45A is arranged to engage with the output-side rotating member 30 before the engaging leg 42A of the input-side rotating member 40 engages with the brake shoe 20 when rotated in the opposite direction. Yes.
  • the brake device 3 configured as described above will be described.
  • the output side rotating member 30 is given a rotational torque in the clockwise direction in the figure by the weight of the occupant sitting on the vehicle seat S.
  • the side rotating member 30 is slightly rotated clockwise.
  • the second contact surface 36A pushes the roller 81A with the force F1
  • the roller 81A pushes the first contact surface 23A with the force F2.
  • the brake shoe 20 has the pair of brake surfaces 21 pressed against the inner peripheral surface 11 of the outer ring 10 with the force F3.
  • a frictional force is generated between the brake surface 21 and the inner peripheral surface 11, so that the output side rotating member 30 does not rotate. That is, a braking force that prevents the vehicle seat S from being lowered is generated.
  • the roller 81B is slightly separated from the holding portion 44 adjacent to the rotation direction of the output side rotation member 30, that is, the clockwise direction. Therefore, not only the roller 81A is sandwiched between the facing surface 36 and the inner side surface 23, but also the roller 81B can be maintained between the facing surface 36 and the inner side surface 23 by the biasing force of the spring 82. Thereby, even if the brake shoe 20 is rotated in any direction thereafter, the frictional force between the brake shoe 20 and the outer ring 10 can be maintained, so that an unexpected release of the braking force can be suppressed.
  • the operation up to this point is the same as in the first embodiment (see FIG. 12).
  • the rotation of the output side rotating member 30 is started simultaneously with the release of the braking force via the roller 81A, so that a large load is not necessary when the output side rotating member 30 is started to rotate, and the start of rotation is caught. A feeling can be suppressed.
  • the output side rotating member 30 is rotated counterclockwise because the engaging portion 45A is engaged with the action portion 31 as shown in FIG.
  • the brake shoe 20 rotates counterclockwise as the engaging leg 42A pushes the rotational force input surface 25 while rotating.
  • the engaging portion 45A can directly engage the output-side rotating member 30 and transmit the rotational torque to the output-side rotating member 30, so that the output-side rotating member
  • rotational torque is input to the input side rotating member 40 in a direction against the rotational torque in a state in which rotational torque is input from the outside to the input 30, the rotational torque input to the output side rotating member 30 is directly input to the input side.
  • the output side rotation member 30 can be rotated by being supported by the rotation member 40. Therefore, the brake force is not suddenly lost and the output side rotation member 30 does not rotate in an unintended direction, and a stable operation can be realized.
  • the output side rotation member 30 can be started to rotate with a small initial load, and a feeling of catching can be suppressed.
  • each brake shoe 20 includes two protrusions 20C protruding outward in the radial direction between a pair of protrusions 20B (a pair of brake surfaces 21) on the outer periphery of the main body 20A.
  • a support surface 26 is provided at the radially outer tip of each protrusion 20C. That is, in the brake device 3 of FIG. 24, two support surfaces 26 are provided on each brake shoe 20.
  • the support surface 26 is disposed at a position intersecting with a straight line connecting the center 11 ⁇ / b> C of the inner peripheral surface 11 and the roller 81 as viewed along the axial direction of the output-side rotating member 30.
  • the support surface 26A disposed on the counterclockwise side is disposed at a position intersecting with a straight line L2 connecting the center 11C and the center of the roller 81A
  • the support surface 26B disposed on the clockwise side is formed with the center 11C. It is arranged at a position that intersects a straight line L3 connecting the centers of the rollers 81B.
  • the inner surface 23 has the first contact surface 23A and the first inclined surfaces 23B, 23C, and the second contact surfaces 36A, 36B are closer to the first contact surface 23A as they are separated from the reference plane PL.
  • the present invention is not limited to this.
  • the first inclined surfaces 23B and 23C may not be provided, and the second contact surfaces 36G and 36H are inclined so as to move away from the first contact surface 23A as the distance from the reference plane PL increases. May be.
  • each brake shoe 20 of the brake device 3 in FIG. The recess has an inner surface 23 on the bottom surface, the inner surface 23 can contact the roller 81, and is parallel to the direction connecting both ends in the circumferential direction of the pair of brake surfaces 21.
  • the circumferential surface of the recess is a spring support surface 28 that supports the spring 82.
  • the output-side rotating member 30 has an opposing surface 36 that opposes the inner surface 23 on the outer periphery, and the opposing surface 36 slopes away from the first contact surface 23A as the distance from the reference plane PL increases. , 36H.
  • a pair of rollers 81 is disposed between the inner surface 23 of each brake shoe 20 and the corresponding opposing surface 36.
  • One spring 82 is provided corresponding to each roller 81, and is disposed between the spring support surface 28 and the corresponding roller 81. The spring 82 urges the corresponding roller 81 toward the narrow side of the space formed between the inner surface 23 and the facing surface 36, that is, toward the circumferential center of the facing surface 36.
  • the interval between the second contact surface 36H and the first contact surface 23A is widened, but the roller 81B is placed on the narrow side of the space formed between the first contact surface 23A and the second contact surface 36H by the spring 82.
  • the first contact surface 23A and the second contact surface 36H are maintained in contact with each other.
  • the roller 81B pushes the second contact surface 36H with the force F53.
  • the input-side rotating member 40 contacts the rotational force input surface 25 and presses the brake shoe 20.
  • a force F53 is immediately generated, and the output side rotating member 30 is rotated clockwise by this force.
  • the roller 81 can be prevented from playing between the inner side surface 23 and the opposed surface 36, and a stable operation can be realized.
  • the inner side surface 23 with which the roller 81 contacts is configured by a combination of planes.
  • the inner surface 23 may be a combination of curved surfaces, and the portion in contact with the rollers 81 may be a smooth curved surface as a whole. May be.
  • the opposing surface 36 which the roller 81 contacts had the 2nd contact surface 36A inclined with respect to the 1st contact surface 23A of the inner surface 23, the opposing surface is the whole, It may be a plane parallel to the first contact surface.
  • the facing surface 36 is interposed via the roller 81 regardless of whether the rotational direction is the clockwise direction or the counterclockwise direction.
  • the brake shoe 20 is configured not to rotate by pressing the inner side surface 23 and pressing the brake surface 21 against the inner peripheral surface 11 of the outer ring 10, it is not limited to this.
  • FIG. 27 when the roller 81B or the second contact surface 36B corresponding to the roller 81B is eliminated and rotational torque is applied to the output-side rotating member 30, one rotational direction, specifically, FIG.
  • the opposing surface 36 presses the inner side surface 23 (first contact surface 23A) through the roller 81A and the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10.
  • the brake shoe 20 may be configured not to rotate.
  • the output side rotation member 30 of the brake device 3 of FIG. 27 is provided with three engagement portions 39 that protrude radially outward. Thereby, when the output side rotation member 30 is rotated in the counterclockwise direction in the figure, the brake shoe 20 is rotated by the engagement portion 39 pushing the brake shoe 20 in the counterclockwise direction. ing.
  • the roller 81B is not in contact with the holding portion 44 in a state where the rotational torque in the normal use range is applied to the output-side rotating member 30 (see FIG. 12).
  • the roller 81B may be slightly in contact with the holding portion 44. Even in this case, as the brake shoe 20 is rotated in the clockwise direction, while the other roller 81A is sandwiched between the opposing surface 36 and the inner side surface 23, the one roller 81B and the inner side surface 23 are opposed to each other. If the surface 36 can obtain a contact state, there is no practical problem.
  • the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10, but is not limited to this.
  • the support surface may be slightly in contact with the inner peripheral surface in a state where the rotation torque in the normal use range is applied to the output side rotation member. .
  • the support surface may not have a shape along the inner peripheral surface of the outer ring.
  • the input-side rotating member 40 is provided with the engaging portion 45A that engages with the output-side rotating member 30 only for rotation in one direction, but the engaging portion 45A is provided on the output side for both rotations. It can also be provided to engage with the rotating member 30.
  • each characteristic element of the said embodiment and modification can be implemented in combination.
  • the output side rotation member 30 has a curved surface (curved surface portion 38) that connects the facing surfaces 36, but the portion that connects the facing surfaces may be a flat surface.
  • the compression coil spring is exemplified as the urging member, but a torsion spring, a leaf spring, rubber or the like may be used.
  • the roller 81 is exemplified as the movable piece.
  • the movable piece may be a sphere, a polygonal column, or a column having an elliptical cross section.
  • three brake shoes 20 are provided, but the number of brake shoes may be two or four or more.
  • the brake device 3 includes the roller 81 as the movable piece and the spring 82 as the biasing member, and the load is transmitted between the inner side surface 23 and the facing surface 36 via the roller 81.
  • the present invention is not limited to this.
  • the configuration may be such that the inner surface and the facing surface are in direct contact with each other and the load is directly transmitted between them without providing the movable piece and the urging member.
  • the brake shoe 20 has the support surface 26 between the pair of brake surfaces 21, but the brake shoe has a configuration that does not include a support surface or a protrusion on which the support surface is provided. It doesn't matter.
  • the brake device 3, the ratchet device 2, and the clutch unit 1 are not only used for the height adjustment mechanism of the vehicle seat S, but can be arbitrarily applied to other devices.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)

Abstract

A brake device (3) is provided with: an outer ring (10) that has a cylindrical inner peripheral surface (11); a plurality of brake shoes (20) that are arrayed on the radial inner side of the outer ring (10) in the circumferential direction and each of which has a pair of brake surfaces (21) that oppose the inner peripheral surface (11) and that can be brought into contact with the inner peripheral surface (11) and an inner surface (23) that is directed radially inward; an output-side rotary member (30) that is disposed at the radial inner side of the respective brake shoes (20) and that has, on the outer periphery thereof, opposing surfaces (36) that oppose the inner surfaces (23) of the brake shoes (20); and input-side rotary members (40) that can give rotation torques to the brake shoes (20) by abutting against the brake shoes (20) in the circumferential direction. The brake shoes (20) each have, between the pair of brake surfaces (21), a supporting surface (26) that can abut against the inner peripheral surface (11).

Description

ブレーキ装置Brake device
　本発明は、車両用シートのハイトアジャスト機構などに使用されるブレーキ装置に関する。 The present invention relates to a brake device used in a vehicle seat height adjustment mechanism or the like.
　車両用シートのハイトアジャスト機構には、入力側に設けられた上下に揺動させるレバーの操作によって出力軸が回転するが、シートおよび乗員の重みによってシートが下がろうとする力が出力軸に掛かっても、出力軸が回転しないように構成されたブレーキ装置が用いられている。 In the height adjustment mechanism for a vehicle seat, the output shaft rotates by operating a lever provided on the input side that swings up and down. However, the weight of the seat and the occupant applies a force to the seat to lower the seat. However, a brake device configured to prevent the output shaft from rotating is used.
　例えば、特許文献１のブレーキ装置は、外輪の内側にブレーキシュー（ブレーキカム）が周方向に３つ並んで設けられ、このブレーキシューの径方向の内側に、出力側回転部材が配置されている。出力側回転部材は、円柱の外周面の一部を平面でカットした形の対向面（ブレーキシューに対向する面）を有しており、出力側回転部材に回転トルクが入力されたときには、この対向面の端の角部がブレーキシューに当接することで、ブレーキシューを径方向外側に押し、ブレーキシューと外輪の間で摩擦力を発生して出力側回転部材の回転を止めるようになっている。 For example, in the brake device of Patent Document 1, three brake shoes (brake cams) are arranged in the circumferential direction on the inner side of the outer ring, and the output-side rotating member is disposed on the inner side in the radial direction of the brake shoe. . The output side rotating member has an opposing surface (a surface facing the brake shoe) in which a part of the outer peripheral surface of the cylinder is cut with a flat surface. When rotational torque is input to the output side rotating member, The corner of the opposite surface abuts against the brake shoe, pushing the brake shoe radially outward and generating frictional force between the brake shoe and the outer ring to stop the rotation of the output side rotating member. Yes.
　また、特許文献２のブレーキ装置は、円筒状の内周面を有する外輪と、この内周面に対向する複数のブレーキシュー（クランピング部材）と、ブレーキシューの内側に配置された出力側回転部材（ウィングを有するピニオン）とが設けられている。ここで、クランピング部材は、ピニオンの軸方向に沿って２段設けられている。具体的には、クランピング部材は、ピニオンの軸方向の１つの位置においてピニオンの中心軸を挟んで一対設けられ、この一対のクランピング部材が、ピニオンの軸方向に並んで２段（二対）、すなわち、計４つ設けられている。 Further, the brake device of Patent Document 2 includes an outer ring having a cylindrical inner peripheral surface, a plurality of brake shoes (clamping members) facing the inner peripheral surface, and an output-side rotation disposed inside the brake shoe. And a member (a pinion having a wing). Here, the clamping member is provided in two stages along the axial direction of the pinion. Specifically, a pair of clamping members are provided at one position in the axial direction of the pinion so as to sandwich the central axis of the pinion, and the pair of clamping members are arranged in two stages (two pairs) in the axial direction of the pinion. ), That is, a total of four are provided.
　そして、４つのクランピング部材のうちの２つ（１段目の１つと２段目の１つ）が、ピニオンの正方向の回転を止め、残りの２つ（１段目の残り１つと２段目の残り１つ）のクランピング部材がピニオンの逆方向の回転を止めるようになっている。 Two of the four clamping members (one of the first stage and one of the second stage) stop the rotation of the pinion in the positive direction, and the other two (the remaining one and the second stage). The remaining one of the stages) is designed to stop the rotation of the pinion in the reverse direction.
特開２０１４－１８５６６９号公報JP 2014-185669 A 特表２００２－５１１０３５号公報Japanese translation of PCT publication No. 2002-511035
　ところで、特許文献１の構成においては、出力側回転部材に過大な回転トルクが与えられると、カム面の一対のブレーキ面の間の部分が径方向外側に向けて強く押されるので、ブレーキシューに大きな曲げ荷重が掛かり、場合によっては、ブレーキシューが変形したり、ひび割れたりする可能性が考えられる。また、車両用シートの重みでブレーキ力を発生しているとき、つまり、出力側回転部材に車両用シートから回転トルクが入力されているときに、操作レバーを操作して車両用シートを下げようとすると、ブレーキシューと出力側回転部材の接触が無くなる瞬間があるため、ブレーキ力が抜けて車両用シートが一気に下がるおそれがあった。 By the way, in the configuration of Patent Document 1, when an excessive rotational torque is applied to the output-side rotating member, a portion between the pair of brake surfaces of the cam surface is strongly pressed toward the outside in the radial direction. A large bending load is applied, and in some cases, the brake shoe may be deformed or cracked. Also, when the braking force is generated by the weight of the vehicle seat, that is, when the rotational torque is input from the vehicle seat to the output side rotating member, operate the operation lever to lower the vehicle seat. Then, there is a moment when the contact between the brake shoe and the output side rotating member disappears, so that the braking force may be lost and the vehicle seat may be lowered at a stroke.
　一方、特許文献２の構成においては、一の回転方向に関しては１段の２つのクランピング部材のうち、１つのクランピング部材しかブレーキ力を発生しないため、安定した充分なブレーキ力を発生するためには、クランピング部材を２段設ける必要がある。そのため、ブレーキ装置の軸方向の大きさが大きくなるという問題があった。 On the other hand, in the configuration of Patent Document 2, since only one clamping member generates a braking force among two clamping members in one stage with respect to one rotational direction, a stable and sufficient braking force is generated. For this, it is necessary to provide two clamping members. Therefore, there has been a problem that the size of the brake device in the axial direction becomes large.
　以上の背景に鑑み、本願の発明者らは、ブレーキシューに掛かる負荷を低減することができるブレーキ装置を提供する研究の過程で本発明を創案するに到った。 In view of the above background, the inventors of the present application have come up with the present invention in the course of research to provide a brake device capable of reducing the load applied to the brake shoe.
　本発明の一ないし複数の実施態様によるブレーキ装置は、円筒状の内周面を有する外輪と、前記外輪の径方向内側に周方向に複数並んで配置され、前記内周面に対向して当該内周面と接触可能な一対のブレーキ面と前記径方向内側を向く内側面とを有するブレーキシューと、前記各ブレーキシューの前記径方向内側に配置され、外周に、前記内側面に対向する対向面を有する出力側回転部材と、前記ブレーキシューまたは前記出力側回転部材に周方向で当接して前記出力側回転部材に回転トルクを与えることが可能な入力側回転部材とを備え、前記出力側回転部材に回転トルクを与えても、少なくとも一方の回転方向については、前記対向面が前記内側面を押して前記ブレーキ面が前記外輪の前記内周面に押し付けられることで前記ブレーキシューが回転しないように構成され、前記ブレーキシューは、前記一対のブレーキ面の間に、前記内周面に当接可能な支持面を有する。 A brake device according to one or more embodiments of the present invention includes an outer ring having a cylindrical inner peripheral surface, a plurality of outer rings arranged in a radial direction inside the outer ring in a circumferential direction, and facing the inner peripheral surface. A brake shoe having a pair of brake surfaces that can come into contact with an inner peripheral surface and an inner surface facing the inner side in the radial direction, and an inner surface facing each other on the outer periphery and facing the inner side surface An output-side rotating member having a surface, and an input-side rotating member capable of giving a rotational torque to the output-side rotating member by contacting the brake shoe or the output-side rotating member in a circumferential direction, Even when a rotational torque is applied to the rotating member, in at least one rotation direction, the opposing surface presses the inner surface and the brake surface is pressed against the inner peripheral surface of the outer ring. Shoe is configured so as not to rotate, the brake shoes, between the pair of braking surface, it has a contactable support surface on the inner peripheral surface.
　このような構成によれば、出力側回転部材に回転トルクが与えられて出力側回転部材の対向面によってブレーキシューの内側面が押された場合において、ブレーキシューの支持面が外輪の内周面に当接したときには、ブレーキシューの一対のブレーキ面の間の部分に掛かる負荷を外輪で支持することができる。これにより、ブレーキシューに掛かる負荷を低減することができる。 According to such a configuration, when rotational torque is applied to the output-side rotating member and the inner surface of the brake shoe is pushed by the opposing surface of the output-side rotating member, the support surface of the brake shoe is the inner peripheral surface of the outer ring. When it comes into contact with, the load applied to the portion between the pair of brake surfaces of the brake shoe can be supported by the outer ring. Thereby, the load concerning a brake shoe can be reduced.
　前記したブレーキ装置において、前記支持面は、前記ブレーキシューに負荷が掛かっていない状態において前記内周面から離間している構成とすることができる。 In the brake device described above, the support surface may be separated from the inner peripheral surface in a state where no load is applied to the brake shoe.
　これによれば、出力側回転部材に過大な回転トルクが与えられていないときには、一対のブレーキ面でブレーキ力が発生するので、ブレーキ力を安定させることができる。一方で、出力側回転部材に過大な回転トルクが与えられて支持面が内周面に当接したときには、ブレーキシューの過大な撓みを抑制できるので、内側面が対向面から受ける力をしっかり受け止め、大きなブレーキ力を発生させることができる。また、入力側回転部材によりブレーキシューに周方向に回転トルクを与えるときには、支持面と内周面とが擦れないので、支持面などの摩耗を抑制することができるとともに、良好な動作をすることができる。 According to this, when an excessive rotational torque is not applied to the output side rotating member, a braking force is generated on the pair of braking surfaces, so that the braking force can be stabilized. On the other hand, when an excessive rotational torque is applied to the output side rotating member and the support surface comes into contact with the inner peripheral surface, excessive braking of the brake shoe can be suppressed, so that the inner surface receives the force received from the opposing surface firmly. A large braking force can be generated. In addition, when the rotational torque is applied to the brake shoe in the circumferential direction by the input side rotating member, the support surface and the inner peripheral surface are not rubbed, so that wear of the support surface and the like can be suppressed and a good operation can be performed. Can do.
　前記したブレーキ装置において、前記ブレーキシューは、外周において突出する突起を有し、前記支持面は、前記突起に設けられている構成とすることができる。 In the brake device described above, the brake shoe may have a protrusion protruding on the outer periphery, and the support surface may be provided on the protrusion.
　これによれば、ブレーキシューの剛性を向上させることができるので、ブレーキシューに掛かる負荷をより低減することができる。また、支持面が内周面に当接するときに、支持面と内周面が当接する位置がはっきりするので、より安定した動作をすることができる。 According to this, since the rigidity of the brake shoe can be improved, the load on the brake shoe can be further reduced. In addition, when the support surface comes into contact with the inner peripheral surface, the position where the support surface comes into contact with the inner peripheral surface becomes clear, so that more stable operation can be performed.
　前記したブレーキ装置において、前記支持面は、前記一対のブレーキ面の間における中央に設けられている構成とすることができる。 In the brake device described above, the support surface may be provided in the center between the pair of brake surfaces.
　これによれば、支持面が内周面に当接したときに、ブレーキシューを安定して支持することができるので、ブレーキシューに掛かる負荷をより低減することができる。 According to this, since the brake shoe can be stably supported when the support surface comes into contact with the inner peripheral surface, the load applied to the brake shoe can be further reduced.
　前記したブレーキ装置において、前記支持面は、前記内周面に沿った形状を有する構成とすることができる。 In the brake device described above, the support surface may have a shape along the inner peripheral surface.
　これによれば、支持面が内周面に当接したときに、ブレーキシューの曲げ応力が最大となる位置を支持することができるので、ブレーキシューに掛かる負荷をより低減することができる。 According to this, when the support surface comes into contact with the inner peripheral surface, the position where the bending stress of the brake shoe is maximized can be supported, so that the load applied to the brake shoe can be further reduced.
　前記したブレーキ装置において、前記対向面は、前記内側面に非平行な部分を含み、当該ブレーキ装置は、前記内側面と前記対向面の間に配置される可動片と、前記可動片を、前記内側面と前記対向面の間に形成される空間の狭い側に付勢する付勢部材とをさらに備え、前記内側面と前記対向面との間で、前記可動片を介して荷重が伝達される構成とすることができる。 In the brake device described above, the facing surface includes a portion that is not parallel to the inner surface, and the brake device includes a movable piece disposed between the inner surface and the facing surface, and the movable piece. A biasing member that biases the narrow side of the space formed between the inner side surface and the opposing surface, and a load is transmitted between the inner side surface and the opposing surface via the movable piece. It can be set as a structure.
　これによれば、出力側回転部材に回転トルクが与えられると、少なくとも一方の回転方向については、可動片が内側面を押してブレーキ面が内周面に押し付けられることでブレーキシューが回転しない。この状態において、入力側回転部材によりブレーキシューを一方の回転方向または他方の回転方向に回転させると、可動片が内側面と対向面の間に形成される空間の狭い側に付勢されているため、可動片を、常に内側面と対向面の間に挟まれた状態、つまり、これらに接触した状態に維持することができ、ブレーキ力が一気に抜けることを抑制することができる。これにより、安定した動作をすることができる。 According to this, when rotational torque is applied to the output side rotation member, the brake shoe does not rotate because the movable piece presses the inner surface and the brake surface is pressed against the inner peripheral surface in at least one rotation direction. In this state, when the brake shoe is rotated in one rotation direction or the other rotation direction by the input side rotation member, the movable piece is biased to the narrow side of the space formed between the inner surface and the opposing surface. Therefore, the movable piece can be maintained in a state where it is always sandwiched between the inner side surface and the opposing surface, that is, in a state where the movable piece is in contact therewith, and the brake force can be prevented from being released all at once. Thereby, a stable operation can be performed.
　前記したブレーキ装置において、前記支持面は、前記出力側回転部材の軸方向に沿って見て、前記内周面の中心と前記可動片を結ぶ直線に交差する位置に配置されている構成とすることができる。 In the brake device described above, the support surface is arranged at a position intersecting with a straight line connecting the center of the inner peripheral surface and the movable piece when viewed in the axial direction of the output-side rotating member. be able to.
　これによれば、ブレーキシューの、可動片によって押される部分とは径方向の略反対側で、支持面が内周面に当接するので、可動片からブレーキシューに掛かった荷重を支持面で効率良く支持することができる。これにより、ブレーキシューに掛かる負荷をより低減することができる。 According to this, since the support surface comes into contact with the inner peripheral surface on the opposite side of the radial direction of the brake shoe from the portion pressed by the movable piece, the load applied to the brake shoe from the movable piece is efficiently absorbed by the support surface. Can support well. Thereby, the load concerning a brake shoe can be reduced more.
　前記した可動片と付勢部材とを備えた構成において、内側面が、可動片と接触可能であるとともに一対のブレーキ面の周方向の両端部を繋いだ方向に平行な第１接触面を有し、対向面が、ブレーキシューに負荷が掛かっていない状態において可動片と接触可能であるとともに第１接触面に対して傾斜した第２接触面を有するようにしてもよい。 In the configuration including the movable piece and the urging member described above, the inner side surface has a first contact surface that can contact the movable piece and is parallel to a direction connecting both ends of the pair of brake surfaces in the circumferential direction. The opposing surface may have a second contact surface that can contact the movable piece and is inclined with respect to the first contact surface when no load is applied to the brake shoe.
　このような構成によれば、出力側回転部材に回転トルクが与えられると、少なくとも一方の回転方向については、可動片がブレーキシューの内側面を押してブレーキ面が外輪の内周面に押し付けられることでブレーキシューが回転しない。この状態において、入力側回転部材によりブレーキシューを一方の回転方向または他方の回転方向に回転させると、可動片が内側面と出力側回転部材の対向面の間に形成される空間の狭い側に付勢されているため、可動片を、常に内側面と対向面の間に挟まれた状態、つまり、これらに接触した状態に維持することができ、ブレーキ力が一気に抜けることを抑制することができる。また、周方向に並んだ複数のブレーキシューのそれぞれでブレーキ力を発生できるので、軸方向の大きさが大きくなるのを抑制することができる。これらにより、軸方向の大きさを小さくすることができるとともに、安定した動作をすることができる。また、可動片が、内側面の第１接触面と、対向面の、第１接触面に対して傾斜した第２接触面との間に挟まれて、これらに接触していることで、可動片を安定して保持することができるとともに、可動片のガタを抑制することができる。 According to such a configuration, when rotational torque is applied to the output-side rotation member, the movable piece presses the inner surface of the brake shoe and the brake surface is pressed against the inner peripheral surface of the outer ring in at least one rotation direction. The brake shoe does not rotate. In this state, when the brake shoe is rotated in one rotation direction or the other rotation direction by the input side rotation member, the movable piece is placed on the narrow side of the space formed between the inner surface and the opposed surface of the output side rotation member. Since it is energized, the movable piece can always be held between the inner surface and the opposite surface, that is, in contact with these, and the brake force can be prevented from being released at once. it can. In addition, since the braking force can be generated by each of the plurality of brake shoes arranged in the circumferential direction, it is possible to suppress an increase in the size in the axial direction. As a result, the size in the axial direction can be reduced, and stable operation can be performed. In addition, the movable piece is sandwiched between and in contact with the first contact surface on the inner surface and the second contact surface that is inclined with respect to the first contact surface on the opposite surface, so that the movable piece is movable. The piece can be held stably and play of the movable piece can be suppressed.
　前記したブレーキ装置において、第２接触面は、内周面の中心を通り、第１接触面に直交する基準平面から離れるほど第１接触面に近づくように傾斜した傾斜部を有している構成とすることができる。 In the brake device described above, the second contact surface includes an inclined portion that passes through the center of the inner peripheral surface and is inclined so as to approach the first contact surface as the distance from the reference plane orthogonal to the first contact surface increases. It can be.
　前記したブレーキ装置において、第２接触面は、出力側回転部材の軸方向に沿って見て、ブレーキシューに向けて凸となる第１曲面部を有する構成とすることができる。 In the brake device described above, the second contact surface may have a first curved surface portion that protrudes toward the brake shoe when viewed along the axial direction of the output-side rotating member.
　出力側回転部材に回転トルクが与えられて出力側回転部材が少し回転したときに、第１接触面と第２接触面の間隔が狭くなると、可動片と、第１接触面および第２接触面との圧力が高まる。この状態から、与えられた回転トルクが過大であるなどして、出力側回転部材がさらに回転した場合、第２接触面が平面であると、第１接触面と第２接触面がなす角度が大きくなり、場合によっては、可動片が第１接触面と第２接触面の間の広い側に動いて圧力が低下し、ブレーキ力が低下する可能性がある。そこで、第２接触面がブレーキシューに向けて凸となる第１曲面部を有する構成とすることで、出力側回転部材がさらに回転した場合の、第１接触面と第２接触面がなす角度の増加を抑えて適正な範囲に維持することができる。これにより、可動片を第１接触面と第２接触面との間に挟まれた状態（圧力が高まった状態）に維持できるので、ブレーキ力を維持することができ、安定してブレーキ力を発生させることができる。 When a rotational torque is applied to the output-side rotating member and the output-side rotating member rotates slightly, if the distance between the first contact surface and the second contact surface becomes narrow, the movable piece, the first contact surface, and the second contact surface And pressure increases. From this state, when the output side rotating member is further rotated due to an excessive rotational torque or the like, if the second contact surface is a plane, the angle formed by the first contact surface and the second contact surface is In some cases, the movable piece moves to the wide side between the first contact surface and the second contact surface, the pressure decreases, and the braking force may decrease. Therefore, the angle formed between the first contact surface and the second contact surface when the output-side rotating member is further rotated by adopting a configuration in which the second contact surface has the first curved surface portion that is convex toward the brake shoe. Can be maintained within an appropriate range while suppressing an increase in Thereby, since the movable piece can be maintained in a state sandwiched between the first contact surface and the second contact surface (a state in which the pressure is increased), the braking force can be maintained, and the braking force can be stably maintained. Can be generated.
　前記したブレーキ装置において、第２接触面は、基準平面から離れるほど曲率半径が小さい構成とすることができる。 In the brake device described above, the second contact surface can be configured to have a smaller radius of curvature the further away from the reference plane.
　これによれば、出力側回転部材がさらに回転した場合の、第１接触面と第２接触面がなす角度の増加をより抑えて、より適正な範囲に維持することができるので、より安定してブレーキ力を発生させることができる。 According to this, when the output side rotation member further rotates, the increase in the angle formed by the first contact surface and the second contact surface can be further suppressed and maintained in a more appropriate range. Brake force can be generated.
　前記したブレーキ装置においては、第２接触面と可動片が接触する点における第２接触面の接平面と第１接触面とのなす角である挟み角が、出力側回転部材に回転トルクが入力されたときの出力側回転部材の回転角度の増加に伴い、増加した後、減少するように第２接触面が形成されていてもよい。この場合、挟み角の最大値は７．５５度以下であることが望ましい。 In the brake device described above, the pinching angle, which is the angle formed between the tangential plane of the second contact surface and the first contact surface at the point where the second contact surface and the movable piece contact each other, is the rotational torque input to the output side rotating member. The second contact surface may be formed so as to decrease after increasing as the rotation angle of the output side rotation member increases. In this case, the maximum value of the included angle is desirably 7.55 degrees or less.
　これによれば、出力側回転部材に大きな回転トルクが入力されて徐々にブレーキシューに対する出力側回転部材の回転変位量が増加しても、挟み角が大きくなりすぎることがないので、可動片が内側面と対向面の間の広い側に滑って移動することが抑制される。 According to this, even when a large rotational torque is input to the output side rotating member and the rotational displacement amount of the output side rotating member with respect to the brake shoe gradually increases, the pinching angle does not become too large. It is suppressed that it slides and moves to the wide side between an inner surface and an opposing surface.
　前記したブレーキ装置において、第２接触面は、対向面における周方向の外側の両端部に１つずつ配置されている構成とすることができる。 In the brake device described above, the second contact surface may be arranged one by one at both ends on the outer side in the circumferential direction on the facing surface.
　これによれば、出力側回転部材に回転トルクが与えられた場合、一方の回転方向および他方の回転方向の両方について、ブレーキシューが回転しない構成とすることができる。 According to this, when rotational torque is given to the output side rotation member, the brake shoe can be configured not to rotate in both the one rotation direction and the other rotation direction.
　前記したブレーキ装置において、対向面は、両端部の各第２接触面を繋ぐ接続面部を有する構成とすることができる。 In the brake device described above, the facing surface may have a connection surface portion that connects the second contact surfaces at both ends.
　これによれば、接続面部を有する分、一方の第２接触面に接触可能な可動片と、他方の第２接触面に接触可能な可動片との間に空間を確保できるので、当該空間に配置される付勢部材を容易に組み付けることができる。 According to this, since a space can be secured between the movable piece that can be in contact with one second contact surface and the movable piece that can be in contact with the other second contact surface by the amount of the connection surface portion, The urging member to be arranged can be easily assembled.
　前記したブレーキ装置において、対向面は、第２接触面と接続面部との接続部分に凹部を有する構成とすることができる。 In the above-described brake device, the facing surface may be configured to have a recess in the connection portion between the second contact surface and the connection surface portion.
　これによれば、凹部を目印として凹部に沿って可動片を組み付けることができるとともに、可動片を組み付けた後は可動片が凹部に嵌ることで可動片を仮止めできるので、２つの可動片の間に付勢部材を組み付けやすい。つまり、可動片や付勢部材を容易に組み付けることができる。 According to this, the movable piece can be assembled along the concave portion with the concave portion as a mark, and after the movable piece is assembled, the movable piece can be temporarily fixed by fitting the movable piece into the concave portion. It is easy to assemble the biasing member between them. That is, the movable piece and the urging member can be easily assembled.
　前記したブレーキ装置において、接続面部は平面部を有する構成とすることができる。 In the brake device described above, the connection surface portion may have a flat surface portion.
　これによれば、接続面部の一部が、ブレーキシュー側に向けて凸となる面を有する構成や、ブレーキシュー側とは反対側に向けて凹となる面を有する構成と比較して、接続面部とブレーキシューの間に適度な大きさの空間を確保することができる。これにより、当該空間に配置される付勢部材を容易に組み付けることができる。 According to this, compared with a configuration in which a part of the connection surface portion has a surface that is convex toward the brake shoe side and a configuration that has a surface that is concave toward the side opposite to the brake shoe side, A moderately sized space can be secured between the surface portion and the brake shoe. Thereby, the biasing member arranged in the space can be easily assembled.
　前記したブレーキ装置において、出力側回転部材は、各ブレーキシューに対応した各対向面を繋ぐ第２曲面部を有する構成とすることができる。 In the brake device described above, the output-side rotating member may have a second curved surface portion that connects the opposing surfaces corresponding to the brake shoes.
　前記したブレーキ装置において、可動片はローラである構成とすることができる。 In the brake device described above, the movable piece may be a roller.
　これによれば、可動片として球を用いる場合よりも耐荷重を上げることができ、多角形の場合よりも滑らかな動作となるので、安定した動作を実現することができる。 According to this, the load resistance can be increased as compared with the case where a sphere is used as the movable piece, and since the operation is smoother than that in the case of a polygon, a stable operation can be realized.
　前記したブレーキ装置において、入力側回転部材は、出力側回転部材に係合して回転トルクを伝達可能な係合部を有することができる。 In the brake device described above, the input-side rotating member can have an engaging portion that can engage with the output-side rotating member and transmit the rotational torque.
　これによれば、係合部が出力側回転部材に直接係合して出力側回転部材にトルクを伝達できるので、出力側回転部材に外部から回転力が入力されている状態において、その回転力に逆らう方向に入力側回転部材に回転力を入力すると、出力側回転部材に入力されている回転力を直接入力側回転部材で支えて出力側回転部材を回転させることができる。そのため、不意にブレーキ力が抜けて出力側回転部材が意図せぬ方向に回ることが無く、安定した動作を実現することができる。 According to this, since the engaging portion can directly engage with the output-side rotating member and transmit torque to the output-side rotating member, the rotational force is applied to the output-side rotating member from the outside. When the rotational force is input to the input side rotating member in the direction opposite to the above, the rotational force input to the output side rotating member can be directly supported by the input side rotating member and the output side rotating member can be rotated. Therefore, the brake force is not suddenly lost and the output side rotating member does not rotate in an unintended direction, and a stable operation can be realized.
　また、係合部が設けられたブレーキ装置においては、出力側回転部材に回転トルクが入力されていて当該回転トルクをブレーキシューのブレーキ力により受け止めている状態において、入力側回転部材を回転トルクと逆向きに回転させたときに、入力側回転部材がブレーキシューに係合するよりも先に係合部が出力側回転部材に係合するように係合部が配置されていることが望ましい。 Further, in the brake device provided with the engaging portion, when the rotational torque is input to the output side rotating member and the rotational torque is received by the braking force of the brake shoe, the input side rotating member is set as the rotational torque. It is desirable that the engaging portion is arranged so that the engaging portion engages with the output-side rotating member before the input-side rotating member engages with the brake shoe when rotated in the reverse direction.
　これによれば、入力側回転部材は、外輪との間で大きな摩擦力が掛かっているブレーキシューを回すことなく、係合部と出力側回転部材の係合で出力側回転部材を回し始める。このため、小さな初期荷重で出力側回転部材を回転させはじめることができ、引っかかり感を抑制することができる。 According to this, the input-side rotating member starts to rotate the output-side rotating member by engaging the engaging portion and the output-side rotating member without rotating the brake shoe that is applied with a large frictional force with the outer ring. For this reason, the output-side rotating member can be started to rotate with a small initial load, and the catching feeling can be suppressed.
乗物用シートの側面図である。It is a side view of a vehicle seat. クラッチユニットの分解斜視図である。It is a disassembled perspective view of a clutch unit. ブレーキ装置の横断面図である。It is a cross-sectional view of a brake device. ブレーキシューの内側面付近の拡大図（ａ）と、出力側回転部材の対向面付近の拡大図（ｂ）である。It is an enlarged view (a) near the inner surface of the brake shoe, and an enlarged view (b) near the opposing surface of the output side rotating member. 出力側回転部材の回転角度と挟み角の関係を示す図である。It is a figure which shows the relationship between the rotation angle of an output side rotation member, and a clamping angle. クラッチユニットの、図３のＺ－Ｚ断面図である。FIG. 4 is a ZZ sectional view of the clutch unit of FIG. 入力側回転部材を出力側から見た図である。It is the figure which looked at the input side rotation member from the output side. ラチェット装置の横断面図である。It is a cross-sectional view of a ratchet device. クラッチユニットをカバー部材側から見た斜視図である。It is the perspective view which looked at the clutch unit from the cover member side. ラチェット装置の動作を説明する図であり、操作入力部材を時計回りに回転させた場合を示す。It is a figure explaining operation | movement of a ratchet apparatus, and shows the case where an operation input member is rotated clockwise. ラチェット装置の動作を説明する図であり、操作入力部材を反時計回りに戻した場合を示す。It is a figure explaining operation | movement of a ratchet apparatus, and shows the case where an operation input member is returned counterclockwise. ブレーキ装置の動作を説明する図であり、出力側回転部材に時計回りの回転トルクを与えた場合を示す。It is a figure explaining operation | movement of a brake device, and shows the case where clockwise rotation torque is given to the output side rotation member. ブレーキ装置の動作を説明する図であり、図１２の状態から、入力側回転部材に反時計回りの回転トルクを与えた場合を示す。It is a figure explaining operation | movement of a brake device, and shows the case where a counterclockwise rotational torque is given to the input side rotation member from the state of FIG. ブレーキ装置の動作を説明する図であり、図１２の状態から、入力側回転部材に時計回りの回転トルクを与えた場合を示す。It is a figure explaining operation | movement of a brake device, and shows the case where clockwise rotation torque is given to the input side rotation member from the state of FIG. ブレーキ装置の動作を説明する図であり、図１４の状態から、入力側回転部材を時計回りにさらに回転させた状態を示す。It is a figure explaining operation | movement of a brake device, and shows the state which rotated the input side rotation member further clockwise from the state of FIG. ブレーキ装置の動作を説明する図であり、出力側回転部材に時計回り方向の過大な回転トルクを与えた状態を示す。It is a figure explaining operation | movement of a brake device, and shows the state which gave the excessive rotational torque of the clockwise direction to the output side rotation member. 第２実施形態における入力側回転部材を出力側から見た図である。It is the figure which looked at the input side rotation member in 2nd Embodiment from the output side. 第２実施形態に係るブレーキ装置の横断面図である。It is a cross-sectional view of a brake device according to a second embodiment. 第２実施形態に係るブレーキ装置の動作を説明する図であり、出力側回転部材に時計回りの回転トルクを与えた場合を示す。It is a figure explaining operation | movement of the brake device which concerns on 2nd Embodiment, and shows the case where clockwise rotation torque is given to the output side rotation member. 第２実施形態に係るブレーキ装置の動作を説明する図であり、図１９の状態から、入力側回転部材に反時計回りの回転トルクを与え、一方のローラを解除した場合を示す。It is a figure explaining operation | movement of the brake device which concerns on 2nd Embodiment, and shows the case where a counterclockwise rotational torque is given to an input side rotation member from the state of FIG. 19, and one roller is cancelled | released. 第２実施形態に係るブレーキ装置の動作を説明する図であり、図２０の状態から、さらに入力側回転部材に反時計回りの回転トルクを与え、係合部が出力側回転部材に係合した状態を示す。It is a figure explaining operation | movement of the brake device which concerns on 2nd Embodiment, gave the counterclockwise rotation torque to the input side rotation member further from the state of FIG. 20, and the engaging part engaged with the output side rotation member. Indicates the state. 第２実施形態に係るブレーキ装置の動作を説明する図であり、図２１の状態から、さらに入力側回転部材に反時計回りの回転トルクを与え、係合脚がブレーキシューに係合した状態を示す。It is a figure explaining operation | movement of the brake device which concerns on 2nd Embodiment, and gives the counterclockwise rotational torque to the input side rotation member from the state of FIG. 21, and shows the state which the engagement leg engaged with the brake shoe. . 第２実施形態に係るブレーキ装置の動作を説明する図であり、図２２の状態から、さらに入力側回転部材に反時計回りの回転トルクを与え、出力側回転部材が回転した状態を示す。It is a figure explaining operation | movement of the brake device which concerns on 2nd Embodiment, and gives the counterclockwise rotational torque to the input side rotation member further from the state of FIG. 22, and shows the state which the output side rotation member rotated. 第１の変形例に係るブレーキ装置の横断面図である。It is a transverse cross section of the brake equipment concerning the 1st modification. 第２の変形例に係るブレーキ装置の横断面図である。It is a cross-sectional view of the brake device which concerns on a 2nd modification. 第２の変形例に係るブレーキ装置において、図２５の状態から、入力側回転部材に時計回りの回転トルクを与えた場合を示す。In the brake device according to the second modification, a case where a clockwise rotational torque is applied to the input side rotation member from the state of FIG. 25 will be described. 第３の変形例に係るブレーキ装置の横断面図である。It is a cross-sectional view of a brake device according to a third modification.
　次に、本発明の実施形態について、適宜図面を参照しながら詳細に説明する。
［第１実施形態］
　図１に示すように、本発明のブレーキ装置を備える一実施形態のクラッチユニット１は、乗物用シートの一例としての車両用シートＳのシートクッションＳ１の高さを調整するための公知のハイトアジャスト機構に適用されるものである。クラッチユニット１は、操作入力部材５０にレバーＬＶが取り付けられ、レバーＬＶの操作により、後述する出力側回転部材３０を回転させてハイトアジャスト機構を駆動してシートクッションＳ１の高さを調整可能である。具体的には、レバーＬＶを中立位置Ｎから上げると、シートクッションＳ１が所定量上がり、レバーＬＶを中立位置Ｎから下げると、シートクッションＳ１が所定量下がるようになっている。なお、レバーＬＶを、上または下の位置から中立位置Ｎに戻すときには、出力側回転部材３０が回転しないようになっている。 Next, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
[First Embodiment]
As shown in FIG. 1, a clutch unit 1 according to an embodiment including the brake device of the present invention is a known height adjuster for adjusting the height of a seat cushion S1 of a vehicle seat S as an example of a vehicle seat. Applies to the mechanism. In the clutch unit 1, a lever LV is attached to the operation input member 50, and the height of the seat cushion S 1 can be adjusted by driving a height adjustment mechanism by rotating an output side rotation member 30 described later by operating the lever LV. is there. Specifically, when the lever LV is raised from the neutral position N, the seat cushion S1 is raised by a predetermined amount, and when the lever LV is lowered from the neutral position N, the seat cushion S1 is lowered by a predetermined amount. When the lever LV is returned from the upper or lower position to the neutral position N, the output-side rotating member 30 is not rotated.
　図２に示すように、クラッチユニット１は、ハウジング１００に各部材が収納されて構成されている。なお、ハウジング１００は、外輪１０、取付板８５およびカバー部材６０の組合せにより構成されている。また、以下の説明では、カバー部材６０および操作入力部材５０が配置される図２の左側を「入力側」と称し、出力側回転部材３０が配置される図２の右側を「出力側」と称する。 As shown in FIG. 2, the clutch unit 1 is configured by housing each member in a housing 100. The housing 100 is configured by a combination of the outer ring 10, the mounting plate 85 and the cover member 60. In the following description, the left side in FIG. 2 where the cover member 60 and the operation input member 50 are arranged is referred to as “input side”, and the right side in FIG. 2 where the output side rotation member 30 is arranged is referred to as “output side”. Called.
　クラッチユニット１は、入力側に設けられ、操作入力部材５０の揺動動作による入力トルクを伝達・遮断するラチェット装置２と、出力側に設けられ、ラチェット装置２からの入力トルクを出力側回転部材３０の出力ギヤ３５に伝達するとともに、出力ギヤ３５からの逆入力トルクを遮断するブレーキ装置３とを備えてなる。 The clutch unit 1 is provided on the input side, and transmits and blocks the input torque generated by the swinging operation of the operation input member 50. The clutch unit 1 is provided on the output side, and the input torque from the ratchet device 2 is output to the output side rotating member. 30 and a brake device 3 for cutting off the reverse input torque from the output gear 35.
　ラチェット装置２とブレーキ装置３の構成部品の概略を説明すると、ラチェット装置２は、操作入力部材５０と、規制部材７１と、ローラ７２と、リターンスプリング７３とを備えてなる。また、ブレーキ装置３は、外輪１０と、ブレーキシュー２０と、出力側回転部材３０と、入力側回転部材４０と、可動片の一例としてのローラ８１と、付勢部材の一例としてのスプリング８２と、フリクションリング８３と、ワッシャ７５とを備えてなる。なお、入力側回転部材４０は、ラチェット装置２の出力部材であるとともに、ブレーキ装置３の入力部材であり、ラチェット装置２とブレーキ装置３のいずれの部品ともいうことができる。 The outline of the components of the ratchet device 2 and the brake device 3 will be described. The ratchet device 2 includes an operation input member 50, a regulating member 71, a roller 72, and a return spring 73. The brake device 3 includes an outer ring 10, a brake shoe 20, an output side rotating member 30, an input side rotating member 40, a roller 81 as an example of a movable piece, and a spring 82 as an example of an urging member. A friction ring 83 and a washer 75 are provided. The input side rotating member 40 is an output member of the ratchet device 2 and an input member of the brake device 3, and can be referred to as any part of the ratchet device 2 and the brake device 3.
　次に、ブレーキ装置３およびラチェット装置２の構成の詳細を説明する。
　まず、ブレーキ装置３の構成について説明する。
　外輪１０は、所定肉厚のリングからなり、円筒状の内周面１１と、円筒状の外周面１２と、内周面１１と外周面１２を繋ぐ一対の側面１３，１４とを有している。一対の側面１３，１４は、内周面１１よりも外輪１０の径方向外側に位置し、内周面１１の軸線に対し直交する平面となっている。なお、本明細書において、径方向および周方向は、外輪１０を基準とする。 Next, details of the configurations of the brake device 3 and the ratchet device 2 will be described.
First, the configuration of the brake device 3 will be described.
The outer ring 10 is formed of a ring having a predetermined thickness, and includes a cylindrical inner peripheral surface 11, a cylindrical outer peripheral surface 12, and a pair of side surfaces 13 and 14 that connect the inner peripheral surface 11 and the outer peripheral surface 12. Yes. The pair of side surfaces 13 and 14 are located on the radially outer side of the outer ring 10 with respect to the inner peripheral surface 11, and are flat surfaces orthogonal to the axis of the inner peripheral surface 11. In the present specification, the radial direction and the circumferential direction are based on the outer ring 10.
　外輪１０とともにハウジング１００の一部を構成する取付板８５は、ブレーキ装置３を支持するための板金部材である。取付板８５は、シートクッションＳ１のフレームなどにブレーキ装置３を取り付けるための取付部として取付孔８５Ｂが２つ形成されている。また、取付板８５は、中央に出力側回転部材３０を通すための貫通孔８５Ａが形成されている。外輪１０は、取付板８５と固定されていることで、クラッチユニット１は、いろいろな装置に取り付けることが可能である。 The mounting plate 85 that constitutes a part of the housing 100 together with the outer ring 10 is a sheet metal member for supporting the brake device 3. The attachment plate 85 is formed with two attachment holes 85B as attachment portions for attaching the brake device 3 to the frame of the seat cushion S1. In addition, the mounting plate 85 has a through hole 85 </ b> A through which the output side rotation member 30 is passed. Since the outer ring 10 is fixed to the attachment plate 85, the clutch unit 1 can be attached to various devices.
　外輪１０は、厚板をプレス成形により打ち抜くことで成形されており出力側の側面１４の外周縁１４Ｂにおいて、レーザ溶接により、取付板８５の入力側の面と溶接されている。この溶接は、図９に示すように、側面１４（外周縁１４Ｂ）の全周に渡ってなされている。取付板８５が外輪１０の側面１４の全周に渡って溶接されていることで、溶接の強度を高めるとともに、外輪１０を取付板８５により補強することができる。そして、側面１４と取付板８５は、環状の側面１４における最外周部分に沿って溶接されていることで、回転方向の力に対する溶接の保持力が高くなっている。 The outer ring 10 is formed by punching a thick plate by press molding, and is welded to the input side surface of the mounting plate 85 at the outer peripheral edge 14B of the output side surface 14 by laser welding. As shown in FIG. 9, this welding is performed over the entire circumference of the side surface 14 (outer peripheral edge 14B). Since the mounting plate 85 is welded over the entire circumference of the side surface 14 of the outer ring 10, the strength of welding can be increased and the outer ring 10 can be reinforced by the mounting plate 85. The side surface 14 and the mounting plate 85 are welded along the outermost peripheral portion of the annular side surface 14, so that the welding holding force against the force in the rotational direction is high.
　図２に戻り、ブレーキシュー２０は、外輪１０との間でブレーキ力を発生する部材であり、外輪１０の径方向内側に周方向に等間隔で並ぶように３つ配置されている。ブレーキシュー２０は、周方向に延びる本体部２０Ａと、本体部２０Ａの外周において径方向外側に突出する突出部２０Ｂおよび突起２０Ｃとを有して構成されている。 Returning to FIG. 2, the brake shoes 20 are members that generate a braking force with the outer ring 10, and three brake shoes 20 are arranged on the inner side in the radial direction of the outer ring 10 at equal intervals in the circumferential direction. The brake shoe 20 includes a main body portion 20A that extends in the circumferential direction, and a protruding portion 20B and a protrusion 20C that protrude outward in the radial direction on the outer periphery of the main body portion 20A.
　突出部２０Ｂは、本体部２０Ａの外周の周方向両端部に１つずつ設けられている。各突出部２０Ｂは、径方向外側の先端に、外輪１０の内周面１１に対向して当該内周面１１と接触可能なブレーキ面２１を有している。このブレーキ面２１は、外輪１０の内周面１１と略同じ曲率であり、図３に示すように、ブレーキ面２１のうち、円周方向の外側付近で外輪１０の内周面１１に接触するように配置されている。これにより、ブレーキシュー２０が径方向外側に付勢されたときには、ブレーキ面２１の周方向外側付近の接触部が外輪１０の内周面１１に押し付けられるようになっている。 One protrusion 20B is provided at each circumferential end of the outer periphery of the main body 20A. Each protrusion 20 </ b> B has a brake surface 21 that faces the inner peripheral surface 11 of the outer ring 10 and can contact the inner peripheral surface 11 at the distal end on the radially outer side. The brake surface 21 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10 and contacts the inner peripheral surface 11 of the outer ring 10 near the outer side in the circumferential direction of the brake surface 21 as shown in FIG. Are arranged as follows. Thereby, when the brake shoe 20 is urged radially outward, the contact portion in the vicinity of the outer periphery in the circumferential direction of the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10.
　突起２０Ｃは、本体部２０Ａの外周の周方向中央部に設けられている。突起２０Ｃの径方向外側の先端には、外輪１０の内周面１１に当接可能な支持面２６が設けられている。別の言い方をすれば、支持面２６は、一対のブレーキ面２１の間における中央に設けられている。この支持面２６は、外輪１０の内周面１１と略同じ曲率であり、外輪１０の内周面１１に沿った円筒面形状を有している。支持面２６は、ブレーキシュー２０および出力側回転部材３０に負荷が掛かっていない状態において、外輪１０の内周面１１から離間している。 The protrusion 20C is provided at the circumferential center of the outer periphery of the main body 20A. A support surface 26 capable of abutting on the inner peripheral surface 11 of the outer ring 10 is provided at the radially outer end of the protrusion 20C. In other words, the support surface 26 is provided at the center between the pair of brake surfaces 21. The support surface 26 has substantially the same curvature as the inner peripheral surface 11 of the outer ring 10, and has a cylindrical surface shape along the inner peripheral surface 11 of the outer ring 10. The support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10 in a state where no load is applied to the brake shoe 20 and the output-side rotating member 30.
　ブレーキシュー２０は、一対のブレーキ面２１の一方と支持面２６との間、および、一対のブレーキ面２１の他方と支持面２６との間に、ブレーキ面２１より小径の円筒面状の外周面２２を有している。また、ブレーキシュー２０は、径方向内側を向く内側面２３を有している。そして、ブレーキシュー２０は、周方向の端部に内側面２３の両端部と２つのブレーキ面２１の端部２１Ｅとを繋ぐ端面２４を有している。また、ブレーキシュー２０は、ブレーキ面２１と外周面２２との間の段差に、周方向を向く回転力入力面２５が形成されている。 The brake shoe 20 includes a cylindrical outer peripheral surface having a smaller diameter than the brake surface 21 between one of the pair of brake surfaces 21 and the support surface 26 and between the other of the pair of brake surfaces 21 and the support surface 26. 22. Further, the brake shoe 20 has an inner side surface 23 facing inward in the radial direction. And the brake shoe 20 has the end surface 24 which connects the both ends of the inner surface 23, and the edge part 21E of the two brake surfaces 21 in the edge part of the circumferential direction. Further, the brake shoe 20 has a rotational force input surface 25 facing the circumferential direction at a step between the brake surface 21 and the outer peripheral surface 22.
　支持面２６は、出力側回転部材３０の軸方向において、少なくとも一部が一対のブレーキ面２１と同じ範囲内にある。つまり、一対のブレーキ面２１と支持面２６をともに通過する出力側回転部材３０に直交する平面が少なくとも１つ存在する。本実施形態では、一対の突出部２０Ｂの厚みと突起２０Ｃの厚みが略等しくなっており（図２参照）、出力側回転部材３０の軸方向において、支持面２６は、その略全体が一対のブレーキ面２１と同じ範囲内にある。 The support surface 26 is at least partially within the same range as the pair of brake surfaces 21 in the axial direction of the output side rotation member 30. That is, there is at least one plane orthogonal to the output side rotation member 30 that passes through the pair of brake surfaces 21 and the support surface 26 together. In the present embodiment, the thickness of the pair of protrusions 20B and the thickness of the protrusions 20C are substantially equal (see FIG. 2), and the support surface 26 in the axial direction of the output-side rotating member 30 is substantially the entire pair. Within the same range as the brake surface 21.
　内側面２３は、それぞれ、出力側回転部材３０の後述する対向面３６に対向する３つの面を有している。詳しくは、図４（ａ）に示すように、内側面２３は、第１接触面２３Ａと、第１接触面２３Ａに対して図の反時計回り側に配置された第１傾斜面２３Ｂと、第１接触面２３Ａに対して図の時計回り側に配置された第１傾斜面２３Ｃとを有している。第１接触面２３Ａは、ローラ８１と接触可能であるととともに、一対のブレーキ面２１の周方向の両端部２１Ｅ同士を繋いだ直線Ｌ１（図３参照）に沿った方向（図４（ａ）に矢印で示した接続方向）に平行な平面となっている。第１傾斜面２３Ｂ，２３Ｃは、これらの間にある第１接触面２３Ａから離れるにつれて対向面３６（図の下側）に近づくように第１接触面２３Ａに対して傾斜した平面となっている。 Each of the inner side surfaces 23 has three surfaces that are opposed to a later-described facing surface 36 of the output side rotating member 30. Specifically, as shown in FIG. 4A, the inner side surface 23 includes a first contact surface 23A, a first inclined surface 23B disposed on the counterclockwise side of the drawing with respect to the first contact surface 23A, It has the 1st inclined surface 23C arrange | positioned with respect to the 1st contact surface 23A in the clockwise direction of a figure. The first contact surface 23A is in contact with the roller 81 and has a direction along a straight line L1 (see FIG. 3) connecting the circumferential ends 21E of the pair of brake surfaces 21 (see FIG. 4A). It is a plane parallel to the connection direction indicated by the arrow. The first inclined surfaces 23B and 23C are flat surfaces that are inclined with respect to the first contact surface 23A so as to approach the facing surface 36 (the lower side in the figure) as they move away from the first contact surface 23A between them. .
　図２に示すように、出力側回転部材３０は、軸状の作用部３１と、この作用部３１の出力側に形成されたフランジ３２と、作用部３１から入力側に突出し、作用部３１と同軸で小径の支持軸部３３と、支持軸部３３から入力側に突出し、支持軸部３３と同軸で支持軸部３３より小径の軸部３７と、フランジ３２の出力側に突出して形成された出力ギヤ３５とを備えて構成されている。出力側回転部材３０は、各ブレーキシュー２０の径方向内側に配置されている。出力ギヤ３５は、取付板８５の貫通孔８５Ａを通して出力側に突出している。 As shown in FIG. 2, the output side rotation member 30 includes a shaft-like action part 31, a flange 32 formed on the output side of the action part 31, and projects from the action part 31 to the input side. A coaxial and small-diameter support shaft portion 33, protrudes from the support shaft portion 33 to the input side, is coaxial with the support shaft portion 33, has a small-diameter shaft portion 37, and protrudes to the output side of the flange 32. An output gear 35 is provided. The output side rotation member 30 is disposed on the radially inner side of each brake shoe 20. The output gear 35 protrudes to the output side through the through hole 85 </ b> A of the mounting plate 85.
　図３に示すように、作用部３１は、その外周に、ブレーキシュー２０の内側面２３に対向する対向面３６と、第２曲面部の一例としての曲面部３８とを有している。対向面３６は、各ブレーキシュー２０の内側面２３に対応して作用部３１の外周に３つ設けられている。また、曲面部３８は、各ブレーキシュー２０に対応した各対向面３６を繋ぐ部分であり、作用部３１の外周の周方向に隣り合う一対の対向面３６の間に１つずつ、合計で３つ設けられている。曲面部３８は、出力側回転部材３０の回転中心を中心とする断面視円弧形状の曲面として形成されている。 As shown in FIG. 3, the action portion 31 has a facing surface 36 facing the inner side surface 23 of the brake shoe 20 and a curved surface portion 38 as an example of a second curved surface portion on the outer periphery thereof. Three opposing surfaces 36 are provided on the outer periphery of the action portion 31 corresponding to the inner surface 23 of each brake shoe 20. Further, the curved surface portion 38 is a portion that connects the facing surfaces 36 corresponding to the brake shoes 20, and there is a total of 3 one pair between the facing surfaces 36 adjacent to each other in the circumferential direction of the outer periphery of the action portion 31. One is provided. The curved surface portion 38 is formed as a curved surface having a circular arc shape in sectional view with the rotation center of the output side rotation member 30 as the center.
　図４（ｂ）に示すように、対向面３６は、当該対向面３６における周方向の外側の両端部に１つずつ配置された第２接触面３６Ａ，３６Ｂと、両端部の各第２接触面３６Ａ，３６Ｂを繋ぐ接続面部３６Ｃとを有している。第２接触面３６Ａは、接続面部３６Ｃに対して図の反時計回り側に配置され、第２接触面３６Ｂは、接続面部３６Ｃに対して図の時計回り側に配置されている。 As shown in FIG. 4B, the facing surface 36 includes second contact surfaces 36 </ b> A and 36 </ b> B arranged one by one on both ends of the facing surface 36 in the circumferential direction, and each second contact on both ends. A connecting surface portion 36C that connects the surfaces 36A and 36B. The second contact surface 36A is disposed on the counterclockwise side in the drawing with respect to the connection surface portion 36C, and the second contact surface 36B is disposed on the clockwise side in the drawing with respect to the connection surface portion 36C.
　第２接触面３６Ａ，３６Ｂは、ブレーキシュー２０に負荷が掛かっていない状態において、ローラ８１と接触可能であるとともに、第１接触面２３Ａに対して傾斜した傾斜部３６１と、傾斜部３６１の外側に連続して配置された、第１曲面部の一例としての曲面部３６２とを有している。傾斜部３６１は、外輪１０の内周面１１の中心１１Ｃ（図３参照）を通り、第１接触面２３Ａに直交する基準平面ＰＬから離れるほど第１接触面２３Ａ（図の上側）に近づくように傾斜している。また、曲面部３６２は、出力側回転部材３０の軸方向に沿って見て、ブレーキシュー２０に向けて凸となる凸形状であり、基準平面ＰＬから離れるほど曲率半径が小さくなる曲面となっている。このような第２接触面３６Ａ，３６Ｂを有することで、対向面３６は、ブレーキシュー２０の内側面２３の一部である第１接触面２３Ａに対して非平行な部分を含んでいる。 The second contact surfaces 36A and 36B are capable of contacting the roller 81 in a state where no load is applied to the brake shoe 20, and are inclined with respect to the first contact surface 23A and outside the inclined portion 361. And a curved surface portion 362 as an example of a first curved surface portion, which are arranged continuously. The inclined portion 361 passes through the center 11C (see FIG. 3) of the inner peripheral surface 11 of the outer ring 10 and approaches the first contact surface 23A (upper side in the drawing) as the distance from the reference plane PL orthogonal to the first contact surface 23A increases. It is inclined to. Further, the curved surface portion 362 is a convex shape that is convex toward the brake shoe 20 when viewed along the axial direction of the output-side rotating member 30, and the curved surface has a curvature radius that decreases as the distance from the reference plane PL increases. Yes. By having such second contact surfaces 36 </ b> A and 36 </ b> B, the facing surface 36 includes a portion non-parallel to the first contact surface 23 </ b> A that is a part of the inner surface 23 of the brake shoe 20.
　図５に示すように、第２接触面３６Ａ，３６Ｂは、第２接触面３６Ａ，３６Ｂとローラ８１が接触する点における第２接触面３６Ａ，３６Ｂの接平面と第１接触面２３Ａとのなす角である挟み角α（挟み角αについて図３参照）が、出力側回転部材３０に回転トルクが入力されたときの出力側回転部材３０の回転角度の増加に伴い、増加した後、減少するように形成されている。この挟み角αは、７．５５度を超えると、ローラ８１が第１接触面２３Ａおよび第２接触面３６Ａ，３６Ｂとの間で滑って第１接触面２３Ａと第２接触面３６Ａ，３６Ｂとの間の空間の広い側へ移動し易いため、最大値が７．５５度以下であることが望ましい。 As shown in FIG. 5, the second contact surfaces 36A and 36B are formed by the first contact surface 23A and the tangential plane of the second contact surfaces 36A and 36B at the point where the second contact surfaces 36A and 36B contact the roller 81. The pinching angle α (see FIG. 3 for the pinching angle α) increases and then decreases as the rotation angle of the output side rotation member 30 increases when the rotation torque is input to the output side rotation member 30. It is formed as follows. When the sandwiching angle α exceeds 7.55 degrees, the roller 81 slides between the first contact surface 23A and the second contact surfaces 36A, 36B, and the first contact surface 23A and the second contact surfaces 36A, 36B It is desirable that the maximum value is 7.55 degrees or less because it is easy to move to the wide side of the space between.
　図４（ｂ）に示すように、接続面部３６Ｃは、周方向の中央部に設けられた平面部３６Ｄと、周方向の両端部に設けられた傾斜部３６Ｅとを有している。平面部３６Ｄは、ブレーキシュー２０および出力側回転部材３０に荷重が入力されていない状態において、基準平面ＰＬに対して直交する平面となっている。これにより、平面部３６Ｄは、ブレーキシュー２０および出力側回転部材３０に荷重が入力されていない状態において、第１接触面２３Ａと平行に配置される。傾斜部３６Ｅは、基準平面ＰＬから離れるほど、言い換えれば、平面部３６Ｄの端から第２接触面３６Ａ，３６Ｂの周方向内側の端に向けて、第１接触面２３Ａから離れるように傾斜している。これにより、対向面３６は、各第２接触面３６Ａ，３６Ｂと接続面部３６Ｃとの接続部分に、第２接触面３６Ａ，３６Ｂの周方向内側の端部と傾斜部３６Ｅとによって形成される凹部３６Ｆを有している。なお、ブレーキシュー２０および出力側回転部材３０に荷重が入力されていない状態において、第１接触面２３Ａと接続面部３６Ｃ（平面部３６Ｄ）の間隔は、ローラ８１の直径よりも小さくなっている。もっとも、第１接触面２３Ａと接続面部３６Ｃの間隔は、ローラ８１の直径以上であってもよい。 As shown in FIG. 4B, the connection surface portion 36C has a flat surface portion 36D provided at the center portion in the circumferential direction and inclined portions 36E provided at both end portions in the circumferential direction. The plane portion 36D is a plane orthogonal to the reference plane PL in a state where no load is input to the brake shoe 20 and the output side rotating member 30. Accordingly, the flat portion 36D is arranged in parallel with the first contact surface 23A in a state where no load is input to the brake shoe 20 and the output-side rotating member 30. The inclined portion 36E is inclined so as to be away from the first contact surface 23A from the end of the flat surface portion 36D toward the inner end in the circumferential direction of the second contact surfaces 36A and 36B as the distance from the reference plane PL increases. Yes. Thereby, the opposing surface 36 is a recessed portion formed by the end portion on the inner side in the circumferential direction of the second contact surfaces 36A and 36B and the inclined portion 36E at the connection portion between the second contact surfaces 36A and 36B and the connection surface portion 36C. 36F. In the state where no load is input to the brake shoe 20 and the output-side rotating member 30, the distance between the first contact surface 23A and the connection surface portion 36C (plane portion 36D) is smaller than the diameter of the roller 81. But the space | interval of the 1st contact surface 23A and the connection surface part 36C may be more than the diameter of the roller 81. FIG.
　図３に示すように、ローラ８１は、各ブレーキシュー２０の内側面２３と出力側回転部材３０の各対向面３６の間に一対ずつ配置されている。ここでは、各内側面２３と各対向面３６の間に配置された一対のローラのうち、図３の反時計回り側に配置された方をローラ８１Ａとし、時計回り側に配置された方をローラ８１Ｂとする。ブレーキシュー２０および出力側回転部材３０に負荷が掛かっていない状態において、ローラ８１Ａは、第１接触面２３Ａと第２接触面３６Ａに挟まれた状態でこれらに接触し、ローラ８１Ｂは、第１接触面２３Ａと第２接触面３６Ｂに挟まれた状態でこれらに接触している。このように、内側面２３と対向面３６の間にローラ８１が配置されることで、ブレーキ装置３では、内側面２３と対向面３６との間で、ローラ８１を介して荷重が伝達される。 As shown in FIG. 3, a pair of rollers 81 is disposed between the inner surface 23 of each brake shoe 20 and each opposing surface 36 of the output side rotating member 30. Here, of the pair of rollers disposed between each inner surface 23 and each facing surface 36, the roller 81A is the one disposed on the counterclockwise side in FIG. 3 and the one disposed on the clockwise side in FIG. Let it be a roller 81B. In a state in which no load is applied to the brake shoe 20 and the output-side rotating member 30, the roller 81A is in contact with the first contact surface 23A and the second contact surface 36A, and the roller 81B is in contact with the first contact surface 23A. These are in contact with each other in a state of being sandwiched between the contact surface 23A and the second contact surface 36B. As described above, the roller 81 is disposed between the inner surface 23 and the facing surface 36, so that in the brake device 3, a load is transmitted between the inner surface 23 and the facing surface 36 via the roller 81. .
　スプリング８２は、圧縮コイルバネであり、一対のローラ８１Ａ，８１Ｂの間に１つずつ設けられている。スプリング８２は、一対のローラ８１Ａ，８１Ｂを互いに周方向に離間させて、内側面２３と対向面３６の間に形成される空間の狭い側に付勢している。 The springs 82 are compression coil springs, and are provided one by one between the pair of rollers 81A and 81B. The spring 82 urges the pair of rollers 81 </ b> A and 81 </ b> B toward the narrow side of the space formed between the inner surface 23 and the facing surface 36 by separating them in the circumferential direction.
　内側面２３および対向面３６は、入力側回転部材４０によりブレーキシュー２０に回転トルクを与えるとローラ８１を介して内側面２３が対向面３６を押して出力側回転部材３０が回転する一方、出力側回転部材３０に回転トルクを与えても、ローラ８１を介して対向面３６が内側面２３を押してブレーキ面２１が外輪１０の内周面１１に押し付けられることでブレーキシュー２０が回転しないように構成されている。すなわち、そのように機能するように、内側面２３の第１接触面２３Ａおよび対向面３６の第２接触面３６Ａ，３６Ｂと、ローラ８１とが接触するように、第１接触面２３Ａに対する第２接触面３６Ａ，３６Ｂの傾斜角や位置などが調整されている。 When the inner side surface 23 and the opposite surface 36 are given rotational torque to the brake shoe 20 by the input side rotation member 40, the inner side surface 23 pushes the opposite surface 36 via the roller 81 and the output side rotation member 30 is rotated. Even when rotational torque is applied to the rotating member 30, the opposing surface 36 presses the inner side surface 23 via the roller 81 and the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10, so that the brake shoe 20 does not rotate. Has been. That is, the second contact surface 23 </ b> A with respect to the first contact surface 23 </ b> A so that the first contact surface 23 </ b> A of the inner surface 23 and the second contact surfaces 36 </ b> A and 36 </ b> B of the opposing surface 36 are in contact with each other so The inclination angles and positions of the contact surfaces 36A and 36B are adjusted.
　図２に示す入力側回転部材４０は、外輪１０および出力側回転部材３０などの軸周りに回転可能であり、ラチェット装置２の回転出力を受け、ブレーキ装置３のブレーキシュー２０に周方向で当接してブレーキシュー２０に回転トルクを与えることが可能な部材である。入力側回転部材４０は、円筒状の受圧リング部４１と、受圧リング部４１から出力側に向けて突出した複数の係合脚４２と、受圧リング部４１の軸方向の中央付近から径方向内側へ向かって延びる板状部４３と、板状部４３の出力側の面から出力側へ向かって伸びる保持部４４（図７参照）と、板状部４３の中央に形成された貫通孔４５を備えて構成されている。受圧リング部４１の内周面４１Ａは、円形断面を有している。 The input side rotating member 40 shown in FIG. 2 can rotate around the axes of the outer ring 10 and the output side rotating member 30, receives the rotational output of the ratchet device 2, and hits the brake shoe 20 of the brake device 3 in the circumferential direction. It is a member that can contact and give rotational torque to the brake shoe 20. The input-side rotating member 40 includes a cylindrical pressure-receiving ring portion 41, a plurality of engagement legs 42 that protrude from the pressure-receiving ring portion 41 toward the output side, and a radially inner side from the vicinity of the axial center of the pressure-receiving ring portion 41. A plate-like portion 43 extending toward the output side, a holding portion 44 (see FIG. 7) extending from the output-side surface of the plate-like portion 43 toward the output side, and a through-hole 45 formed at the center of the plate-like portion 43. Configured. The inner peripheral surface 41A of the pressure receiving ring portion 41 has a circular cross section.
　係合脚４２は、各ブレーキシュー２０に対応して等間隔で３対設けられており、外輪１０の内周面１１とブレーキシュー２０の外周面２２との間に配置されている。一対の係合脚４２は、図３に示すように、突起２０Ｃと図３の反時計回り側の突出部２０Ｂの間に配置される係合脚４２Ａと、突起２０Ｃと図３の時計回り側の突出部２０Ｂの間に配置される係合脚４２Ｂからなる。突出部２０Ｂおよび突起２０Ｃと、係合脚４２Ａ，４２Ｂとの間には、周方向に僅かな遊びができるように、突出部２０Ｂ、突起２０Ｃおよび係合脚４２Ａ，４２Ｂの大きさが設定されている。各係合脚４２Ａ，４２Ｂは、略同じ形状で形成されている。 Three pairs of engagement legs 42 are provided at equal intervals corresponding to each brake shoe 20, and are arranged between the inner peripheral surface 11 of the outer ring 10 and the outer peripheral surface 22 of the brake shoe 20. As shown in FIG. 3, the pair of engaging legs 42 includes an engaging leg 42A disposed between the protrusion 20C and the anticlockwise protrusion 20B of FIG. 3, and the protrusion 20C and the clockwise protrusion of FIG. The engaging leg 42B is disposed between the portions 20B. Between the protrusion 20B and the protrusion 20C and the engagement legs 42A and 42B, the sizes of the protrusion 20B, the protrusion 20C and the engagement legs 42A and 42B are set so that slight play can be made in the circumferential direction. . Each engagement leg 42A, 42B is formed in substantially the same shape.
　保持部４４は、内側面２３と対向面３６の間からローラ８１が脱落するのを抑制する部分であり、ローラ８１の周方向に隣接して配置されている。具体的には、各ブレーキシュー２０に対応する一対のローラ８１Ａ，８１Ｂの周方向の両側に隣接して配置され、全部で３つ設けられている。 The holding portion 44 is a portion that suppresses the roller 81 from falling off between the inner surface 23 and the facing surface 36, and is disposed adjacent to the circumferential direction of the roller 81. Specifically, a pair of rollers 81A and 81B corresponding to each brake shoe 20 are disposed adjacent to both sides in the circumferential direction, and a total of three are provided.
　保持部４４は、入力側回転部材４０および出力側回転部材３０に荷重が入力されていない状態において、ローラ８１から離間して配置されている。より詳細には、保持部４４は、出力側回転部材３０に通常使用範囲の回転トルクが入力されている状態において、当該回転トルクの回転方向の上流側に隣接するローラ８１、本実施形態ではローラ８１Ｂに対し非接触であるように配置されている。 The holding portion 44 is disposed away from the roller 81 in a state where no load is input to the input side rotating member 40 and the output side rotating member 30. More specifically, the holding unit 44 is a roller 81 adjacent to the upstream side in the rotation direction of the rotation torque in a state where the rotation torque in the normal use range is input to the output side rotation member 30. It arrange | positions so that it may be non-contact with respect to 81B.
　また、保持部４４は、出力側回転部材３０に回転トルクが入力されている状態から、入力側回転部材４０を出力側回転部材３０の回転トルクと同じ回転方向に回転させてブレーキシュー２０に周方向で当接させた時点において、当該回転方向の下流側に隣接するローラ８１、本実施形態ではローラ８１Ａに対し非接触であるように配置されている。 In addition, the holding unit 44 rotates the input-side rotating member 40 in the same rotational direction as the rotational torque of the output-side rotating member 30 from the state where the rotating torque is input to the output-side rotating member 30, so At the time of contact in the direction, the roller 81 adjacent to the downstream side in the rotation direction, in this embodiment, is arranged so as not to contact the roller 81A.
　また、保持部４４は、入力側回転部材４０がブレーキシュー２０に周方向で当接してブレーキシュー２０を回転させている状態において、保持部４４の回転方向下流側に隣接するローラ８１に対し接触するように配置されている。もっとも、保持部４４は、入力側回転部材４０によりブレーキシュー２０を回転させている状態において、ローラ８１に対し非接触であってもよい。 Further, the holding portion 44 contacts the roller 81 adjacent to the downstream side in the rotation direction of the holding portion 44 in a state where the input-side rotating member 40 is in contact with the brake shoe 20 in the circumferential direction to rotate the brake shoe 20. Are arranged to be. However, the holding portion 44 may be in non-contact with the roller 81 in a state where the brake shoe 20 is rotated by the input side rotation member 40.
　図７に示すように、貫通孔４５は、出力側回転部材３０の作用部３１が挿通可能であり、その内周に、作用部３１の曲面部３８に沿った３つの円周面部４６と、各円周面部４６の間に配置され、円周面部４６に対し、径方向内側に突出した３つの凸面部４７とを有する。各凸面部４７は、最も径方向内側に突出した頂部４７Ａと、頂部４７Ａに対して図７の時計回り側（図３では反時計回り側）に隣接した解除面４７Ｂと、図７の反時計回り側（図３では時計回り側）に隣接した逃げ面４７Ｃとを有する。 As shown in FIG. 7, the through hole 45 allows the action part 31 of the output side rotation member 30 to be inserted, and on its inner periphery, three circumferential surface parts 46 along the curved surface part 38 of the action part 31, and It has 3 convex surface parts 47 which are arrange | positioned between each circumferential surface part 46, and protruded to radial direction inner side with respect to the circumferential surface part 46. As shown in FIG. Each convex surface portion 47 includes a top portion 47A that protrudes inward in the radial direction, a release surface 47B that is adjacent to the top portion 47A on the clockwise side in FIG. 7 (counterclockwise side in FIG. 3), and a counterclockwise direction in FIG. And a flank 47C adjacent to the rotation side (clockwise side in FIG. 3).
　解除面４７Ｂは、対向面３６と対向して配置され、車両用シートＳに座った乗員の重みによる図３の時計回り方向の回転トルクが出力側回転部材３０に入力されている状態から、入力側回転部材４０を当該回転トルクと逆の回転方向（図３の反時計回り方向）に回転させてブレーキシュー２０に周方向で当接させた時点において、略同時に対向面３６に当該逆の回転方向の回転トルクを伝達可能な形状を有している。 The release surface 47B is arranged to face the facing surface 36, and the input of the clockwise rotational torque in FIG. 3 to the output side rotating member 30 due to the weight of the occupant sitting on the vehicle seat S is input. When the side rotation member 40 is rotated in the rotation direction opposite to the rotation torque (counterclockwise direction in FIG. 3) and brought into contact with the brake shoe 20 in the circumferential direction, the counter surface 36 rotates in the opposite direction substantially simultaneously. It has a shape that can transmit rotational torque in the direction.
　逃げ面４７Ｃは、入力側回転部材４０および出力側回転部材３０に外部から荷重が入力されていない状態において、対向面３６の平面部３６Ｄ（図４参照）に対する角度の大きさが解除面４７Ｂの平面部３６Ｄに対する角度の大きさよりも大きく形成され、入力側回転部材４０を図３の時計回り方向に回転させてブレーキシュー２０に周方向で当接された時点において平面部３６Ｄに当接しない形状となっている。もっとも、逃げ面４７Ｃは、平面部３６Ｄに対する角度の大きさが解除面４７Ｂの平面部３６Ｄに対する角度の大きさと同じであって、図３における入力側回転部材４０の時計回り方向について、解除面４７Ｂと同様の機能を有していてもよい。 The clearance surface 47C has an angle of the release surface 47B with respect to the flat surface portion 36D (see FIG. 4) of the opposing surface 36 in a state in which no load is input from the outside to the input side rotation member 40 and the output side rotation member 30. A shape that is formed larger than the angle with respect to the flat surface portion 36D, and does not contact the flat surface portion 36D when the input side rotating member 40 is rotated clockwise in FIG. It has become. However, the flank 47C has the same angle with respect to the flat surface portion 36D as the angle with respect to the flat surface portion 36D of the release surface 47B, and the release surface 47B in the clockwise direction of the input side rotation member 40 in FIG. It may have the same function.
　図２に示すように、フリクションリング８３は、ブレーキ装置３のブレーキ力が切れた瞬間に急激に出力側回転部材３０の動作が開始するのを抑制するためのフリクションを発生する部材である。フリクションリング８３は、出力側回転部材３０の作用部３１の外周に略合致した孔を有するリング部８３Ａと、リング部８３Ａから径方向外側に延出し、先端部が外輪１０の内周面１１に圧接する３つの摩擦発生アーム８３Ｂとを備える。フリクションリング８３は、リング部８３Ａの孔が作用部３１と係合することで、出力側回転部材３０と一体に回転するようになっている。また、図６に示すように、フリクションリング８３は、ブレーキシュー２０の出力側に配置されている。 As shown in FIG. 2, the friction ring 83 is a member that generates friction for suppressing the sudden start of the operation of the output side rotating member 30 at the moment when the braking force of the brake device 3 is broken. The friction ring 83 includes a ring portion 83A having a hole that substantially matches the outer periphery of the action portion 31 of the output-side rotating member 30, and a radially outer portion extending from the ring portion 83A. Three friction generating arms 83B that are in pressure contact are provided. The friction ring 83 is configured to rotate integrally with the output-side rotating member 30 when the hole of the ring portion 83 </ b> A is engaged with the action portion 31. As shown in FIG. 6, the friction ring 83 is disposed on the output side of the brake shoe 20.
　図３に示すように、摩擦発生アーム８３Ｂは、径方向外側へ行くほど、図３における時計回り方向に位置するように、径方向に対して傾斜している。このため、フリクションリング８３は、図３の時計回り方向に回転するときには、内周面１１に食い付きやすいので、反時計回りに回転するときよりも大きな摩擦力を発生することができる。そのため、車両用シートＳのハイトアジャスト機構のブレーキにクラッチユニット１を適用する場合には、出力側回転部材３０が図３の時計回り方向に回転するときに車両用シートＳが下降するように組み付けると、車両用シートＳの望ましくない下降を効果的に抑制することができる。 As shown in FIG. 3, the friction generating arm 83B is inclined with respect to the radial direction so as to be located in the clockwise direction in FIG. For this reason, when the friction ring 83 rotates in the clockwise direction in FIG. 3, the friction ring 83 is likely to bite against the inner peripheral surface 11, so that a larger frictional force can be generated than when the friction ring 83 rotates counterclockwise. Therefore, when the clutch unit 1 is applied to the brake of the height adjustment mechanism of the vehicle seat S, the vehicle seat S is assembled so that it is lowered when the output side rotation member 30 rotates in the clockwise direction of FIG. And the undesired descent | fall of the vehicle seat S can be suppressed effectively.
　図２に戻り、ワッシャ７５は、出力側回転部材３０の軸部３７の外径よりも僅かに小さい直径の孔７５Ａを有し、この孔７５Ａが軸部３７に圧入されている（図６参照）。ワッシャ７５の外径は、後述するカバー部材６０の支持孔６４より大きく、ワッシャ７５により出力側回転部材３０が出力側に抜けないようになっている。 Returning to FIG. 2, the washer 75 has a hole 75 </ b> A having a diameter slightly smaller than the outer diameter of the shaft portion 37 of the output side rotating member 30, and the hole 75 </ b> A is press-fitted into the shaft portion 37 (see FIG. 6). ). The outer diameter of the washer 75 is larger than the support hole 64 of the cover member 60 described later, so that the output-side rotating member 30 cannot be pulled out to the output side by the washer 75.
　次に、ラチェット装置２の構成について説明する。
　図２に示すように、操作入力部材５０は、レバーＬＶと係合してレバーＬＶと一体に揺動可能であるとともに、ローラ７２を介して入力側回転部材４０と一体に動くようになることで、入力側回転部材４０にレバーＬＶからの回転トルクを伝達する部材である。このため、操作入力部材５０は、カム板部５１と、このカム板部５１から入力側に延出した２つのレバー係合部５２とを備えてなる。 Next, the configuration of the ratchet device 2 will be described.
As shown in FIG. 2, the operation input member 50 engages with the lever LV and can swing integrally with the lever LV, and moves integrally with the input side rotation member 40 via the roller 72. Thus, it is a member that transmits the rotational torque from the lever LV to the input side rotating member 40. Therefore, the operation input member 50 includes a cam plate portion 51 and two lever engaging portions 52 extending from the cam plate portion 51 to the input side.
　図８に示すように、カム板部５１は、外周面に３箇所の小径部５３と３箇所の大径部５４が交互に配置されており、小径部５３と大径部５４を平面からなる対向面５５が接続している。小径部５３と大径部５４の切り替わりの箇所は６箇所あるので、これに対応して対向面５５は６つ形成されている。対向面５５は、中心軸からの距離が徐々に変化するように形成されている。 As shown in FIG. 8, the cam plate portion 51 has three small-diameter portions 53 and three large-diameter portions 54 arranged alternately on the outer peripheral surface, and the small-diameter portion 53 and the large-diameter portion 54 are made of a plane. The facing surface 55 is connected. Since there are six places where the small-diameter portion 53 and the large-diameter portion 54 are switched, six opposing surfaces 55 are formed correspondingly. The facing surface 55 is formed so that the distance from the central axis gradually changes.
　各対向面５５と受圧リング部４１の内周面４１Ａとの間には、それぞれ、ローラ７２が配置されている。ローラ７２は、後述する動作説明で分かるように、操作入力部材５０および入力側回転部材４０に対し係合・離脱することで入力トルクの伝達・遮断を行うものである。ローラ７２は、各対向面５５に対応して計６つ配置されている。対向面５５は、図６に示すように、ローラ７２の軸方向長さの半分よりその方向に長く、ローラ７２の軸方向における中心部（中心線Ｃ１参照）を含む範囲でローラ７２と当接可能に配置されている。これにより、対向面５５は、受圧リング部４１との間で安定してローラ７２を挟持することができる。 A roller 72 is disposed between each facing surface 55 and the inner peripheral surface 41A of the pressure receiving ring portion 41, respectively. As will be understood from the description of the operation described later, the roller 72 engages and disengages the operation input member 50 and the input side rotation member 40 to transmit and block input torque. A total of six rollers 72 are arranged corresponding to the opposing surfaces 55. As shown in FIG. 6, the facing surface 55 is longer in the direction than half of the axial length of the roller 72, and contacts the roller 72 in a range including the central portion (refer to the center line C <b> 1) in the axial direction of the roller 72. Arranged to be possible. Thereby, the opposing surface 55 can stably hold the roller 72 between the pressure receiving ring portion 41.
　ここで、図２に戻り、規制部材７１について説明すると、規制部材７１は、ローラ７２の位置を規制する部材であり、複数のローラ７２の出力側の側面を覆う側壁部７１Ａと、側壁部７１Ａの外周縁から入力側に向けて延出した３つの規制部７１Ｂとを備えて構成されている。規制部７１Ｂは、ローラ７２の軸方向の長さよりも長く、その先端がカバー部材６０の嵌合穴６６に圧入嵌合している。 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 includes a side wall portion 71 </ b> A that covers the output side surface of the plurality of rollers 72, and the side wall portion 71 </ b> A. And three restricting portions 71B extending from the outer peripheral edge toward the input side. The restricting portion 71 </ b> B is longer than the length of the roller 72 in the axial direction, and its tip is press-fitted into the fitting hole 66 of the cover member 60.
　図８に示すように、規制部７１Ｂは、レバーＬＶを操作していない非作動時において大径部５４の径方向外側で同じ回転位置に配置されており、対向面５５と受圧リング部４１の間にあるローラ７２の周方向についての移動を規制している。隣接する規制部７１Ｂの間に配置された２つのローラ７２の間には、圧縮コイルバネからなるリターンスプリング７３がそれぞれ初期荷重を与えられて配置されている。このため、図８の非作動時において、各ローラ７２は規制部７１Ｂに接している。ここで、規制部７１Ｂは、外輪１０の径方向において、ローラ７２の中心が位置するところを含むように配置され、ローラ７２の、周方向に最も出っ張っているところに接している。これにより、規制部７１Ｂは、ローラ７２を安定して支持することができる。なお、図８においては、ローラ７２を、規制部７１Ｂに接した状態で表しているが、ローラ７２は、対向面５５と内周面４１Ａに挟持されることで、規制部７１Ｂから僅かに離れていてもよい。 As shown in FIG. 8, the restricting portion 71 </ b> B is disposed at the same rotational position on the radially outer side of the large-diameter portion 54 when the lever LV is not operated, and the opposing surface 55 and the pressure-receiving ring portion 41. The movement of the roller 72 between them in the circumferential direction is restricted. Between the two rollers 72 arranged between the adjacent regulating portions 71B, return springs 73 made of compression coil springs are arranged with an initial load applied. For this reason, at the time of non-operation of FIG. 8, each roller 72 is in contact with the restricting portion 71B. Here, the restricting portion 71 </ b> B is disposed so as to include a position where the center of the roller 72 is located in the radial direction of the outer ring 10, and is in contact with the most protruding portion of the roller 72 in the circumferential direction. Thereby, the control part 71B can support the roller 72 stably. In FIG. 8, the roller 72 is shown in contact with the restricting portion 71B, but the roller 72 is slightly separated from the restricting portion 71B by being sandwiched between the opposing surface 55 and the inner peripheral surface 41A. It may be.
　図２に示すように、レバー係合部５２は、円弧状の断面でカム板部５１から延出している。レバー係合部５２は、レバーＬＶと係合している（図示省略）。 As shown in FIG. 2, the lever engaging portion 52 extends from the cam plate portion 51 with an arcuate cross section. The lever engaging portion 52 is engaged with the lever LV (not shown).
　カバー部材６０は、円板状の側壁部６１と、側壁部６１の外周縁から出力側に延びる円筒状の外周部６２と、外周部６２の出力側の端部から径方向外側に広がるフランジ６３とを備えてなる。フランジ６３は、図６および図９に示すように、外輪１０の側面１３に合わされ、その外周縁に沿って側面１３とレーザ溶接により溶接されている。外輪１０は、このようにカバー部材６０が溶接されることで補強されている。この溶接は、フランジ６３の全周に渡ってなされている。 The cover member 60 includes a disk-shaped side wall portion 61, a cylindrical outer peripheral portion 62 that extends from the outer peripheral edge of the side wall portion 61 to the output side, and a flange 63 that extends radially outward from the output-side end portion of the outer peripheral portion 62. And comprising. As shown in FIGS. 6 and 9, the flange 63 is fitted to the side surface 13 of the outer ring 10 and welded to the side surface 13 by laser welding along the outer peripheral edge thereof. The outer ring 10 is reinforced by welding the cover member 60 in this way. This welding is performed over the entire circumference of the flange 63.
　図２に示すように、側壁部６１には、その中心に円形の支持孔６４と、支持孔６４の周囲で円弧形状に延びる２つの円弧孔６５と、円弧孔６５よりも径方向外側に位置し、周方向に３つ等間隔で配置された嵌合穴６６とが形成されている。
　支持孔６４は、出力側回転部材３０の支持軸部３３と嵌合し、出力側回転部材３０を軸支する部分である。
　円弧孔６５は、操作入力部材５０のレバー係合部５２に対応して設けられ、レバー係合部５２よりも広い角度範囲で円弧状に形成されている。これにより、円弧孔６５は、レバー係合部５２を受け入れるとともに、レバー係合部５２が円弧孔６５の中において所定角度範囲で移動することが可能となっている。 As shown in FIG. 2, the side wall 61 has a circular support hole 64 at its center, two arc holes 65 extending in an arc shape around the support hole 64, and a position radially outside the arc hole 65. And three fitting holes 66 arranged at equal intervals in the circumferential direction are formed.
The support hole 64 is a portion that fits with the support shaft portion 33 of the output side rotation member 30 and pivotally supports the output side rotation member 30.
The arc hole 65 is provided corresponding to the lever engaging portion 52 of the operation input member 50, and is formed in an arc shape in a wider angle range than the lever engaging portion 52. As a result, the arc hole 65 receives the lever engaging portion 52, and the lever engaging portion 52 can move within the arc hole 65 within a predetermined angle range.
　嵌合穴６６は、規制部材７１の３つの規制部７１Ｂに対応して３つ設けられた貫通孔であり、規制部材７１がカバー部材６０に対し相対回転しないように、カバー部材６０と嵌合されている。規制部材７１とカバー部材６０とは、複数箇所で嵌合していることで、規制部材７１の回転の規制をしっかりと行うことができる。 The fitting holes 66 are three through holes provided corresponding to the three regulating portions 71 </ b> B of the regulating member 71, and are fitted with the cover member 60 so that the regulating member 71 does not rotate relative to the cover member 60. Has been. Since the regulating member 71 and the cover member 60 are fitted at a plurality of locations, the regulation member 71 can be firmly regulated to rotate.
　次に、以上のように構成されたクラッチユニット１の動作について説明する。
　まず、ラチェット装置２の動作について説明する。
　図８に示す中立位置において、ローラ７２は、入力側回転部材４０の内周面４１Ａと操作入力部材５０の対向面５５の間に位置するが、これらの間には僅かな隙間があり、これらに挟持されてはいない。ローラ７２は、リターンスプリング７３により規制部７１Ｂに押し付けられている。レバーＬＶの操作により操作入力部材５０を時計回り方向に少し揺動させると、対向面５５が時計回りに回動してローラ７２に接し、内周面４１Ａと対向面５５の間でローラ７２が挟持される。これにより、操作入力部材５０と入力側回転部材４０は一体に回転できるようになる。
　そのため、図１０に示すように、操作入力部材５０を時計回りに回していけば、入力側回転部材４０と操作入力部材５０とが一体になったまま、時計回りに回動する。すなわち、操作入力部材５０を回動させた入力トルクが入力側回転部材４０に伝達される。 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. 8, the roller 72 is located between the inner peripheral surface 41 </ b> A of the input side rotating member 40 and the opposing surface 55 of the operation input member 50, but there is a slight gap between them. It is not pinched by. The roller 72 is pressed against the restricting portion 71B by a return spring 73. When the operation input member 50 is slightly swung clockwise by the operation of the lever LV, the facing surface 55 rotates clockwise to contact the roller 72, and the roller 72 moves between the inner peripheral surface 41 </ b> A and the facing surface 55. It is pinched. Thereby, the operation input member 50 and the input side rotation member 40 can rotate integrally.
Therefore, as shown in FIG. 10, if the operation input member 50 is rotated clockwise, the input side rotation member 40 and the operation input member 50 are rotated clockwise while being integrated. That is, the input torque obtained by rotating the operation input member 50 is transmitted to the input side rotation member 40.
　図１０の状態からレバーＬＶを反時計回りに揺動させて中立位置に戻すときには、ローラ７２から対向面５５が反時計回りに逃げていき、ローラ７２は対向面５５と内周面４１Ａには挟持されないので、図１１に示すように、入力側回転部材４０が静止したまま、操作入力部材５０が中立位置に向けて回動する。すなわち、操作入力部材５０を戻すときの入力トルクは入力側回転部材４０には伝達されず、遮断される。操作入力部材５０は、リターンスプリング７３の付勢力により中立位置に向けて操作するのが補助されるとともに、中立位置に維持される。 When the lever LV is swung counterclockwise from the state shown in FIG. 10 to return to the neutral position, the facing surface 55 escapes counterclockwise from the roller 72, and the roller 72 is placed on the facing surface 55 and the inner peripheral surface 41A. Since it is not pinched, as shown in FIG. 11, the operation input member 50 rotates toward the neutral position while the input side rotation member 40 is stationary. That is, the input torque when returning the operation input member 50 is not transmitted to the input side rotation member 40 but is blocked. The operation input member 50 is assisted to operate toward the neutral position by the urging force of the return spring 73 and is maintained at the neutral position.
　レバーＬＶを中立位置から上に上げ、また、上の位置から中立位置に戻すときの動作は、上述の下への揺動の場合と同様であるので説明を省略する。 The operation for raising the lever LV from the neutral position and returning the lever LV from the upper position to the neutral position is the same as that in the case of the downward swing described above, and a description thereof will be omitted.
　次に、ブレーキ装置３の動作について説明する。
　図１２に示すように、車両用シートＳに座った乗員の重みにより出力側回転部材３０に、図における時計回り方向の回転トルク、つまり、通常使用範囲の回転トルクを与えると、出力側回転部材３０が時計回りに少し回転し、第２接触面３６Ａ（一の対向面３６の一対の第２接触面３６Ａ，３６Ｂのうち反時計回り側の１つ）と第１接触面２３Ａの間隔が狭くなることで、ローラ８１Ａ（一のブレーキシュー２０に対応する一対のローラ８１のうち反時計回り側の１つ）と第２接触面３６Ａおよび第１接触面２３Ａの圧力が高まる。なお、出力側回転部材３０に荷重が入力されていない状態において、ローラ８１Ａが第１傾斜面２３Ｂに接していた場合には、ローラ８１Ａは、対向面３６と内側面２３の間を転がって、第１接触面２３Ａに接する位置まで移動したところで第２接触面３６Ａおよび第１接触面２３Ａとの間の圧力が充分に高まって対向面３６および内側面２３に対して止まる。一方、出力側回転部材３０が時計回りに回転するにつれ、第２接触面３６Ｂ（一の対向面３６の一対の第２接触面３６Ａ，３６Ｂのうち時計回り側の１つ）と第１接触面２３Ａの間隔が広くなるため、ローラ８１Ｂ（一のブレーキシュー２０に対応する一対のローラ８１のうち時計回り側の１つ）は、第２接触面３６Ｂと第１接触面２３Ａの間で強く挟まれることなく転がることができる。 Next, the operation of the brake device 3 will be described.
As shown in FIG. 12, when the output side rotation member 30 is given a rotation torque in the clockwise direction in the drawing, that is, a rotation torque in the normal use range, by the weight of the occupant sitting on the vehicle seat S, the output side rotation member 30 slightly rotates clockwise, and the distance between the second contact surface 36A (one of the pair of second contact surfaces 36A and 36B of the one opposing surface 36 on the counterclockwise side) and the first contact surface 23A is narrow. Thus, the pressures of the roller 81A (one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side), the second contact surface 36A, and the first contact surface 23A are increased. When the roller 81A is in contact with the first inclined surface 23B in a state where no load is input to the output-side rotating member 30, the roller 81A rolls between the facing surface 36 and the inner side surface 23, When it moves to a position in contact with the first contact surface 23A, the pressure between the second contact surface 36A and the first contact surface 23A is sufficiently increased and stops against the opposing surface 36 and the inner surface 23. On the other hand, as the output side rotation member 30 rotates clockwise, the second contact surface 36B (one of the pair of second contact surfaces 36A, 36B of the one opposing surface 36 on the clockwise side) and the first contact surface. Since the distance between the two contact surfaces 23A is increased, the roller 81B (one of the pair of rollers 81 corresponding to one brake shoe 20 on the clockwise side) is strongly sandwiched between the second contact surface 36B and the first contact surface 23A. You can roll without being caught.
　このとき、第２接触面３６Ａは、ローラ８１Ａを力Ｆ１で押し、ローラ８１Ａは、第１接触面２３Ａを力Ｆ２で押す。これにより、ブレーキシュー２０は、一対のブレーキ面２１が外輪１０の内周面１１に力Ｆ３で押し付けられる。その結果、ブレーキ面２１と内周面１１の間で摩擦力が発生するので、出力側回転部材３０が回転しない。すなわち、車両用シートＳが下がるのを阻止するブレーキ力が発生する。そして、このような、出力側回転部材３０に通常使用範囲の回転トルクを与えた状態においては、支持面２６は、外輪１０の内周面１１から離間している。 At this time, the second contact surface 36A pushes the roller 81A with the force F1, and the roller 81A pushes the first contact surface 23A with the force F2. As a result, the brake shoe 20 has the pair of brake surfaces 21 pressed against the inner peripheral surface 11 of the outer ring 10 with the force F3. As a result, a frictional force is generated between the brake surface 21 and the inner peripheral surface 11, so that the output side rotating member 30 does not rotate. That is, a braking force that prevents the vehicle seat S from being lowered is generated. In such a state where the rotational torque in the normal use range is applied to the output side rotation member 30, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.
　また、このとき、ローラ８１Ｂは、出力側回転部材３０の回転方向、つまり、時計回り方向に隣接する保持部４４から僅かに離間している。そのため、ローラ８１Ａが対向面３６と内側面２３に挟まれているだけでなく、スプリング８２の付勢力によりローラ８１Ｂも対向面３６と内側面２３に挟まれた状態を維持することができる。これにより、その後、ブレーキシュー２０をいずれの方向に回転しても、ブレーキシュー２０と外輪１０の間の摩擦力を維持できるので、予期せぬブレーキ力の解除を抑制することができる。 At this time, the roller 81B is slightly separated from the holding portion 44 adjacent in the rotation direction of the output side rotation member 30, that is, the clockwise direction. Therefore, not only the roller 81A is sandwiched between the facing surface 36 and the inner side surface 23, but also the roller 81B can be maintained between the facing surface 36 and the inner side surface 23 by the biasing force of the spring 82. Thereby, even if the brake shoe 20 is rotated in any direction thereafter, the frictional force between the brake shoe 20 and the outer ring 10 can be maintained, so that an unexpected release of the braking force can be suppressed.
　図１２のブレーキ状態から、車両用シートＳの高さを上げるためにレバーＬＶを操作して入力側回転部材４０を反時計回りに回転させると、図１３に示すように、入力側回転部材４０の係合脚４２Ａが反時計回り側の端部でブレーキシュー２０の回転力入力面２５に周方向で当接する。この時点において、略同時に入力側回転部材４０の解除面４７Ｂが対向面３６の平面部３６Ｄに接して反時計回り方向の回転トルクを出力側回転部材３０に伝達可能となる。これにより、ブレーキシュー２０のブレーキ面２１が外輪１０の内周面１１に強く押し付けられていた場合においても、ブレーキ力を解除して、入力側回転部材４０を回して車両用シートＳを上げ始めるときの引っかかり感を抑制することができる。 When the input side rotating member 40 is rotated counterclockwise by operating the lever LV to raise the height of the vehicle seat S from the brake state of FIG. 12, as shown in FIG. 13, the input side rotating member 40 The engaging leg 42A contacts the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the end on the counterclockwise side. At this time, the release surface 47B of the input side rotation member 40 comes into contact with the flat surface portion 36D of the opposing surface 36 at substantially the same time, so that the counterclockwise rotation torque can be transmitted to the output side rotation member 30. As a result, even when the brake surface 21 of the brake shoe 20 is strongly pressed against the inner peripheral surface 11 of the outer ring 10, the brake force is released and the input side rotating member 40 is turned to start raising the vehicle seat S. It is possible to suppress the feeling of catching when.
　そして、さらに入力側回転部材４０を反時計回りに回転させると、係合脚４２Ａが回転力入力面２５を力Ｆ１１で押すことでブレーキシュー２０が反時計回り方向に回転し、第１接触面２３Ａがローラ８１Ａを力Ｆ１２で押し、ローラ８１Ａが第２接触面３６Ａを力Ｆ１３で押す。この力Ｆ１３により、出力側回転部材３０が図の反時計回りに回転する。このときも、支持面２６は、外輪１０の内周面１１から離間している。 Then, when the input side rotation member 40 is further rotated counterclockwise, the engagement leg 42A pushes the rotational force input surface 25 with the force F11, whereby the brake shoe 20 rotates counterclockwise, and the first contact surface 23A. Presses the roller 81A with the force F12, and the roller 81A presses the second contact surface 36A with the force F13. By this force F13, the output side rotation member 30 rotates counterclockwise in the figure. Also at this time, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.
　また、図１２のブレーキ状態から、車両用シートＳの高さを下げるためにレバーＬＶを操作して入力側回転部材４０を時計回りに回転させると、図１４に示すように、入力側回転部材４０の係合脚４２Ｂが時計回り側の端部でブレーキシュー２０の回転力入力面２５に周方向で当接する。このとき、保持部４４は、回転方向下流側（時計回り方向側）に隣接するローラ８１Ａに対して非接触である。そして、さらに入力側回転部材４０を時計回りに回転させると、係合脚４２Ｂが回転力入力面２５を力Ｆ２１で押し、ブレーキシュー２０が時計回り方向に回転し始める。 In addition, when the input side rotation member 40 is rotated clockwise by operating the lever LV to lower the height of the vehicle seat S from the brake state of FIG. 12, as shown in FIG. 14, the input side rotation member Forty engagement legs 42B abut on the rotational force input surface 25 of the brake shoe 20 in the circumferential direction at the clockwise end. At this time, the holding portion 44 is not in contact with the roller 81A adjacent to the downstream side in the rotation direction (clockwise direction side). When the input side rotation member 40 is further rotated clockwise, the engaging leg 42B pushes the rotational force input surface 25 with the force F21, and the brake shoe 20 starts to rotate clockwise.
　ブレーキシュー２０が図１４の状態から時計回り方向に回転すると、ブレーキシュー２０と出力側回転部材３０は、図１２において出力側回転部材３０を時計回り方向に回転させた場合と相対的に逆の動作をする。すなわち、図１５に示すように、ブレーキシュー２０が時計回りに少し回転し、第１接触面２３Ａと第２接触面３６Ｂ（一の対向面３６の一対の第２接触面３６Ａ，３６Ｂのうち時計回り側の１つ）の間隔が狭くなることで、ローラ８１Ｂ（一のブレーキシュー２０に対応する一対のローラ８１のうち時計回り側の１つ）と第１接触面２３Ａおよび第２接触面３６Ｂの圧力が高まる。なお、ローラ８１Ｂが第１傾斜面２３Ｃに接していた場合でも、ローラ８１Ｂは、対向面３６と内側面２３の間を転がって、第１接触面２３Ａに接する位置まで移動したところで第２接触面３６Ｂおよび第１接触面２３Ａとの間の圧力が充分に高まって対向面３６および内側面２３に対して止まる。一方、ブレーキシュー２０が時計回りに回転するにつれ、第１接触面２３Ａと第２接触面３６Ａ（一の対向面３６の一対の第２接触面３６Ａ，３６Ｂのうち反時計回り側の１つ）の間隔が広くなるため、ローラ８１Ａ（一のブレーキシュー２０に対応する一対のローラ８１のうち反時計回り側の１つ）は、第１接触面２３Ａと第２接触面３６Ａの間でこれらとの圧力が徐々に下がっていきながら転がることができる。そして、図１５の状態では、保持部４４は、回転方向下流側に隣接するローラ８１Ａに接触して、ローラ８１Ａを時計回り方向に押している。 When the brake shoe 20 rotates clockwise from the state of FIG. 14, the brake shoe 20 and the output side rotating member 30 are relatively opposite to the case where the output side rotating member 30 is rotated clockwise in FIG. To work. That is, as shown in FIG. 15, the brake shoe 20 is slightly rotated clockwise, and the first contact surface 23A and the second contact surface 36B (the pair of second contact surfaces 36A and 36B of one opposing surface 36 is a timepiece). By reducing the distance between the one on the rotation side), the roller 81B (one of the rollers 81 corresponding to one brake shoe 20 on the clockwise side), the first contact surface 23A and the second contact surface 36B. Increased pressure. Even when the roller 81B is in contact with the first inclined surface 23C, the roller 81B rolls between the opposing surface 36 and the inner side surface 23 and moves to a position in contact with the first contact surface 23A. The pressure between 36 </ b> B and the first contact surface 23 </ b> A is sufficiently increased and stops against the facing surface 36 and the inner surface 23. On the other hand, as the brake shoe 20 rotates clockwise, the first contact surface 23A and the second contact surface 36A (one of the pair of second contact surfaces 36A and 36B of the one opposing surface 36 on the counterclockwise side) Therefore, the roller 81A (one of the pair of rollers 81 corresponding to one brake shoe 20 on the counterclockwise side) is located between the first contact surface 23A and the second contact surface 36A. You can roll while the pressure of the water gradually decreases. And in the state of FIG. 15, the holding | maintenance part 44 contacts the roller 81A adjacent to the rotation direction downstream, and is pushing the roller 81A clockwise.
　このように、図１４の状態では、保持部４４がローラ８１Ａに対して非接触であることで、第１接触面２３Ａと第２接触面３６Ｂの間にローラ８１Ｂが充分な力で挟まれる前には、ブレーキ力を発生していたローラ８１Ａが保持部４４に押されないので予期せずブレーキ力が弱まることが抑制される。一方、図１５に示すように、ローラ８１Ｂが第１接触面２３Ａと第２接触面３６Ｂに充分な力で挟まれた後は、保持部４４がローラ８１Ａに接触するので、仮に、ローラ８１Ａが内側面２３と対向面３６の間で何らかの事態により固着したような場合であっても、ローラ８１Ａを内側面２３と対向面３６の間から離してブレーキ力を解除し、安定した動作を実現することができる。 As described above, in the state shown in FIG. 14, the holding portion 44 is not in contact with the roller 81A, so that the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force. In this case, since the roller 81A that has generated the braking force is not pushed by the holding portion 44, the braking force is prevented from being unexpectedly weakened. On the other hand, as shown in FIG. 15, after the roller 81B is sandwiched between the first contact surface 23A and the second contact surface 36B with sufficient force, the holding portion 44 comes into contact with the roller 81A. Even in a case where the inner surface 23 and the facing surface 36 are fixed due to some circumstances, the roller 81A is separated from the inner surface 23 and the facing surface 36 to release the braking force, thereby realizing a stable operation. be able to.
　そして、図１５に示すように、係合脚４２Ｂが回転力入力面２５を力Ｆ２１で押し、第１接触面２３Ａがローラ８１Ｂを力Ｆ２２で押し、ローラ８１Ｂが第２接触面３６Ｂを力Ｆ２３で押す。この力Ｆ２３により、出力側回転部材３０が図の時計回りに回転する。このときも、支持面２６は、外輪１０の内周面１１から離間している。 Then, as shown in FIG. 15, the engaging leg 42B pushes the rotational force input surface 25 with the force F21, the first contact surface 23A pushes the roller 81B with the force F22, and the roller 81B pushes the second contact surface 36B with the force F23. Push. By this force F23, the output side rotation member 30 rotates clockwise in the figure. Also at this time, the support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10.
　一方、出力側回転部材３０に、通常使用範囲より大きい過大な時計回り方向の回転トルクが入力された場合、図１６に示すように、通常使用範囲の回転トルクを与えた場合よりも、出力側回転部材３０が時計回りに大きく回転し、第２接触面３６Ａと第１接触面２３Ａの間隔がより狭くなることで、ローラ８１Ａと第２接触面３６Ａおよび第１接触面２３Ａの圧力がより高まる。このとき、第２接触面３６Ａは、ローラ８１Ａを大きな力Ｆ３１で押し、ローラ８１Ａは、第１接触面２３Ａを大きな力Ｆ３２で押す。これにより、ブレーキシュー２０は、本体部２０Ａが径方向外側に撓むように変形し、支持面２６が外輪１０の内周面１１に当接する。その結果、ブレーキシュー２０は、支持面２６が外輪１０によって支持されることになり、それ以上の変形が抑制されるため、当該ブレーキシュー２０に掛かる負荷を低減することができる。 On the other hand, when the rotation torque in the clockwise direction that is larger than the normal use range is input to the output-side rotation member 30, as shown in FIG. The rotation member 30 rotates greatly in the clockwise direction, and the distance between the second contact surface 36A and the first contact surface 23A becomes narrower, so that the pressure on the roller 81A, the second contact surface 36A, and the first contact surface 23A is further increased. . At this time, the second contact surface 36A pushes the roller 81A with a large force F31, and the roller 81A pushes the first contact surface 23A with a large force F32. As a result, the brake shoe 20 is deformed so that the main body portion 20 </ b> A bends radially outward, and the support surface 26 contacts the inner peripheral surface 11 of the outer ring 10. As a result, the support surface 26 of the brake shoe 20 is supported by the outer ring 10, and further deformation is suppressed, so that the load on the brake shoe 20 can be reduced.
　また、過大な時計回り方向の回転トルクが入力されて出力側回転部材３０が時計回りに大きく回転した場合には、第２接触面３６Ｂと第１接触面２３Ａとの間が広がってローラ８１Ｂがこれらの間で遊ぶことがある。このような場合、ローラ８１Ｂは、回転方向下流側、ここでは時計回り方向に隣接する保持部４４に当接する。これにより、保持部４４がローラ８１Ｂを支持するので、内側面２３と対向面３６の間からローラ８１Ｂが脱落することが抑制される。 Further, when an excessive clockwise rotational torque is input and the output-side rotating member 30 is greatly rotated clockwise, the space between the second contact surface 36B and the first contact surface 23A widens, and the roller 81B You may play between these. In such a case, the roller 81B abuts on the holding portion 44 adjacent to the downstream side in the rotation direction, here, the clockwise direction. Thereby, since the holding part 44 supports the roller 81B, it is suppressed that the roller 81B falls out between the inner surface 23 and the opposing surface 36.
　以上においては、出力側回転部材３０に時計回り方向の回転トルクが入力されてブレーキ力が発生した後、入力側回転部材４０を時計回り方向または反時計回り方向に回転させた場合について説明した。クラッチユニット１を車両用シートＳに適用した場合には、出力側回転部材３０には、時計回り方向の回転トルクしか入力されないので、上述のようにしか動作しないが、仮に、出力側回転部材３０に反時計回り方向の回転トルクが入力されてブレーキ力が発生した後、入力側回転部材４０を時計回り方向または反時計回り方向に回転させた場合は、ブレーキシュー２０、出力側回転部材３０および入力側回転部材４０は、鏡像対称（図３で線対称）に構成されているので、上述と回転方向が異なるだけで、同様の動作が実現される。 In the above description, the case where the input side rotating member 40 is rotated in the clockwise direction or the counterclockwise direction after the rotational torque in the clockwise direction is input to the output side rotating member 30 and the braking force is generated has been described. When the clutch unit 1 is applied to the vehicle seat S, only the rotational torque in the clockwise direction is input to the output-side rotating member 30 and thus operates only as described above. When the input side rotating member 40 is rotated clockwise or counterclockwise after a counterclockwise rotational torque is input to generate a braking force, the brake shoe 20, the output side rotating member 30 and Since the input-side rotating member 40 is configured to be mirror-image symmetric (axisymmetric in FIG. 3), the same operation is realized only by the rotation direction being different from that described above.
　以上説明した本実施形態のクラッチユニット１に適用されたブレーキ装置３によれば、出力側回転部材３０に回転トルクが与えられると、ローラ８１がブレーキシュー２０の内側面２３を押してブレーキ面２１が外輪１０の内周面１１に押し付けられることでブレーキシュー２０が回転しない。この状態において、入力側回転部材４０によりブレーキシュー２０を一方の回転方向または他方の回転方向に回転させると、ローラ８１が内側面２３と出力側回転部材３０の対向面３６の間に形成される空間の狭い側に付勢されているため、いずれかのローラ８１を常に内側面２３と対向面３６の間に挟まれた状態、つまり、これらに接触した状態に維持することができる。このため、ブレーキ力が一気に抜けることを抑制することができる。また、周方向に並んだ複数のブレーキシュー２０のそれぞれでブレーキ力を発生できるので、ブレーキ装置３の軸方向の大きさが大きくなるのを抑制することができる。これらにより、軸方向の大きさを小さくすることができるとともに、安定した動作をすることができる。 According to the brake device 3 applied to the clutch unit 1 of the present embodiment described above, when rotational torque is applied to the output-side rotating member 30, the roller 81 pushes the inner side surface 23 of the brake shoe 20 so that the brake surface 21 is moved. The brake shoe 20 does not rotate by being pressed against the inner peripheral surface 11 of the outer ring 10. In this state, when the brake shoe 20 is rotated in one rotation direction or the other rotation direction by the input side rotation member 40, the roller 81 is formed between the inner surface 23 and the facing surface 36 of the output side rotation member 30. Since one of the rollers 81 is always sandwiched between the inner surface 23 and the facing surface 36, that is, in contact with these, since it is biased to the narrow side of the space, it can be maintained. For this reason, it can suppress that brake force falls off at a stretch. In addition, since the brake force can be generated by each of the plurality of brake shoes 20 arranged in the circumferential direction, it is possible to suppress an increase in the size of the brake device 3 in the axial direction. As a result, the size in the axial direction can be reduced, and stable operation can be performed.
　また、ローラ８１が、内側面２３の第１接触面２３Ａと、対向面３６の、第１接触面２３Ａに対して傾斜した第２接触面３６Ａ，３６Ｂとの間に挟まれて、これらに接触していることで、ローラ８１を安定して保持することができるとともに、ローラ８１のガタを抑制することができる。 In addition, the roller 81 is sandwiched between the first contact surface 23A of the inner surface 23 and the second contact surfaces 36A and 36B of the facing surface 36 that are inclined with respect to the first contact surface 23A, and comes into contact therewith. As a result, the roller 81 can be stably held and play of the roller 81 can be suppressed.
　ところで、前述したとおり、出力側回転部材３０に回転トルクが与えられて出力側回転部材３０が少し回転したときに、第１接触面２３Ａと第２接触面３６Ａ，３６Ｂの間隔が狭くなると、ローラ８１と、第１接触面２３Ａおよび第２接触面３６Ａ，３６Ｂとの圧力が高まる。この状態から、与えられた回転トルクが過大であるなどして、出力側回転部材３０がさらに回転した場合、仮に、第２接触面が平面であると、第１接触面と第２接触面がなす角度が大きくなり、場合によっては、ローラが第１接触面と第２接触面の間の広い側に動いて圧力が低下し、ブレーキ力が低下する可能性がある。一方、本実施形態では、第２接触面３６Ａ，３６Ｂがブレーキシュー２０に向けて凸となる曲面を有するので、出力側回転部材３０がさらに回転した場合の、第１接触面２３Ａと、第２接触面３６Ａ，３６Ｂ（詳しくは、第２接触面３６Ａ，３６Ｂとローラ８１の接触部分に接する接平面）がなす角度の増加を抑えて適正な範囲に維持することができる。これにより、ローラ８１が第１接触面２３Ａと第２接触面３６Ａ，３６Ｂの間の広い側に動くことが抑制されるので、ローラ８１を第１接触面２３Ａと第２接触面３６Ａ，３６Ｂとの間に挟まれた状態（圧力が高まった状態）に維持することができる。これにより、ブレーキ力を維持することができるため、安定してブレーキ力を発生させることができる。 By the way, as described above, when a rotational torque is applied to the output-side rotating member 30 and the output-side rotating member 30 rotates a little, the distance between the first contact surface 23A and the second contact surfaces 36A, 36B becomes narrower. The pressure between the first contact surface 23A and the second contact surfaces 36A and 36B increases. From this state, when the output side rotating member 30 is further rotated due to an excessive rotational torque or the like, if the second contact surface is a flat surface, the first contact surface and the second contact surface are The angle formed may increase, and in some cases, the roller may move to the wide side between the first contact surface and the second contact surface, reducing the pressure and reducing the braking force. On the other hand, in the present embodiment, since the second contact surfaces 36A and 36B have curved surfaces that are convex toward the brake shoe 20, the first contact surface 23A and the second contact surface 23A when the output-side rotating member 30 is further rotated. An increase in the angle formed by the contact surfaces 36A, 36B (specifically, the tangential plane in contact with the contact portion between the second contact surfaces 36A, 36B and the roller 81) can be suppressed and maintained in an appropriate range. As a result, the roller 81 is restrained from moving to the wide side between the first contact surface 23A and the second contact surfaces 36A, 36B, so that the roller 81 is moved to the first contact surface 23A and the second contact surfaces 36A, 36B. It can be maintained in a state of being sandwiched between (a state in which the pressure is increased). Thereby, since a braking force can be maintained, a braking force can be generated stably.
　特に、本実施形態では、第２接触面３６Ａ，３６Ｂは、基準平面ＰＬから離れるほど曲率半径が小さいので、出力側回転部材３０がさらに回転した場合の、第１接触面２３Ａと第２接触面３６Ａ，３６Ｂがなす角度の増加をより抑えて、より適正な範囲に維持することができる。また、本実施形態では、出力側回転部材３０の回転角度の増加に伴い、挟み角αが増加した後、減少することで、挟み角αが過大になることが抑制されるので、ローラ８１が第１接触面２３Ａおよび第２接触面３６Ａ，３６Ｂとの間で滑って移動することが抑制される。これにより、ローラ８１を第１接触面２３Ａと第２接触面３６Ａ，３６Ｂとの間に挟まれた状態に良好に維持できるので、より安定してブレーキ力を発生させることができる。 In particular, in the present embodiment, the second contact surfaces 36A and 36B have a radius of curvature that decreases with distance from the reference plane PL. Therefore, the first contact surface 23A and the second contact surface when the output-side rotating member 30 rotates further. The increase in the angle formed by 36A and 36B can be further suppressed and maintained in a more appropriate range. In the present embodiment, as the rotation angle of the output side rotation member 30 increases, the pinching angle α increases and then decreases, thereby suppressing the pinching angle α from becoming excessive. The sliding movement between the first contact surface 23A and the second contact surfaces 36A, 36B is suppressed. As a result, the roller 81 can be satisfactorily maintained in a state of being sandwiched between the first contact surface 23A and the second contact surfaces 36A, 36B, so that the braking force can be generated more stably.
　また、第２接触面３６Ａ，３６Ｂが対向面３６の両端部に１つずつ配置されているので、出力側回転部材３０に回転トルクが与えられた場合、一方の回転方向および他方の回転方向の両方について、ブレーキシュー２０が回転しない構成を実現することができる。 In addition, since the second contact surfaces 36A and 36B are arranged one by one at both ends of the facing surface 36, when rotational torque is applied to the output-side rotating member 30, one rotational direction and the other rotational direction In both cases, a configuration in which the brake shoe 20 does not rotate can be realized.
　また、対向面３６が接続面部３６Ｃを有する分、一方の第２接触面３６Ａに接触可能なローラ８１Ａと、他方の第２接触面３６Ｂに接触可能なローラ８１Ｂとの間に空間を確保することができる。これにより、当該空間に配置されるスプリング８２を容易に組み付けることができる。 In addition, a space is ensured between the roller 81A that can contact one of the second contact surfaces 36A and the roller 81B that can contact the other second contact surface 36B, because the facing surface 36 has the connection surface portion 36C. Can do. Thereby, the spring 82 arrange | positioned in the said space can be assembled | attached easily.
　また、対向面３６が第２接触面３６Ａ，３６Ｂと接続面部３６Ｃとの接続部分に凹部３６Ｆを有するので、凹部３６Ｆを目印として凹部３６Ｆに沿ってローラ８１を組み付けることができるとともに、ローラ８１を組み付けた後はローラ８１が凹部３６Ｆに嵌ることでローラ８１を仮止めできるので、２つのローラ８１の間にスプリング８２を組み付けやすい。つまり、ブレーキ装置３によれば、ローラ８１やスプリング８２を容易に組み付けることができる。 Further, since the opposing surface 36 has a recess 36F at the connection portion between the second contact surfaces 36A, 36B and the connection surface portion 36C, the roller 81 can be assembled along the recess 36F using the recess 36F as a mark. After the assembly, the roller 81 can be temporarily fixed by fitting the roller 81 into the recess 36F, so that the spring 82 is easily assembled between the two rollers 81. That is, according to the brake device 3, the roller 81 and the spring 82 can be easily assembled.
　また、接続面部３６Ｃが平坦な平面部３６Ｄを有するので、接続面部３６Ｃが、平面部３６Ｄの代わりに、ブレーキシュー側に向けて凸となる面を有する構成や、ブレーキシュー側とは反対側に向けて凹となる面を有する構成と比較して、接続面部３６Ｃとブレーキシュー２０の間に適度な大きさの空間を確保することができる。これにより、当該空間に配置されるスプリング８２を容易に組み付けることができる。 Further, since the connecting surface portion 36C has a flat flat surface portion 36D, the connecting surface portion 36C has a surface that protrudes toward the brake shoe side instead of the flat surface portion 36D, or on the side opposite to the brake shoe side. Compared to the configuration having a concave surface, a space having an appropriate size can be secured between the connection surface portion 36C and the brake shoe 20. Thereby, the spring 82 arrange | positioned in the said space can be assembled | attached easily.
　また、可動片がローラ８１であるため、可動片として球を用いる場合よりも、内側面２３や対向面３６との接触面積が大きくなることで、耐荷重を上げることができる。また、可動片がローラ８１であることで、多角形の場合よりも滑らかな動作となるので、安定した動作を実現することができる。 Further, since the movable piece is the roller 81, the load resistance can be increased by increasing the contact area with the inner side surface 23 and the facing surface 36 as compared with the case where a sphere is used as the movable piece. In addition, since the movable piece is the roller 81, the operation is smoother than that of the polygonal shape, and thus a stable operation can be realized.
　また、出力側回転部材３０に過大な回転トルクが与えられ、出力側回転部材３０の対向面３６によってローラ８１を介してブレーキシュー２０の内側面２３が径方向外側に押された場合には、ブレーキシュー２０の支持面２６が外輪１０の内周面１１に当接するので、ブレーキシュー２０の一対のブレーキ面２１の間の部分に掛かる負荷を外輪１０で支持することができる。これにより、ブレーキシュー２０に掛かる負荷を低減することができる。 Further, when an excessive rotational torque is given to the output side rotating member 30, and the inner side surface 23 of the brake shoe 20 is pushed radially outward by the opposing surface 36 of the output side rotating member 30 via the roller 81, Since the support surface 26 of the brake shoe 20 contacts the inner peripheral surface 11 of the outer ring 10, the load applied to the portion between the pair of brake surfaces 21 of the brake shoe 20 can be supported by the outer ring 10. Thereby, the load applied to the brake shoe 20 can be reduced.
　また、支持面２６は、ブレーキシュー２０に負荷が掛かっていない状態においては内周面１１から離間しているので、出力側回転部材３０に過大な回転トルクが与えられていないとき、つまり、通常使用範囲の回転トルクが与えられているときには、ブレーキシュー２０の外周の周方向両端部に設けられた一対のブレーキ面２１でブレーキ力が発生するため、ブレーキ力を安定させることができる。一方で、出力側回転部材３０に過大な回転トルクが与えられて支持面２６が内周面１１に当接したときには、ブレーキシュー２０の過大な撓みを抑制できるので、内側面２３が対向面３６から受ける力をしっかり受け止め、大きなブレーキ力を発生させることができる。また、入力側回転部材４０によりブレーキシュー２０に周方向に通常使用範囲の回転トルクを与え、ブレーキシュー２０を回転させるときには、支持面２６と内周面１１とが擦れないので、支持面２６などの摩耗を抑制することができるとともに、良好な動作をすることができる。 Further, since the support surface 26 is separated from the inner peripheral surface 11 in a state where no load is applied to the brake shoe 20, when the excessive torque is not applied to the output side rotation member 30, that is, normally When a rotational torque in the use range is applied, the braking force is generated by the pair of brake surfaces 21 provided at both ends in the circumferential direction of the outer periphery of the brake shoe 20, so that the braking force can be stabilized. On the other hand, when an excessive rotational torque is applied to the output-side rotating member 30 and the support surface 26 contacts the inner peripheral surface 11, excessive bending of the brake shoe 20 can be suppressed. The force received from the can is received firmly, and a large braking force can be generated. Further, when the rotational torque in the normal use range is given to the brake shoe 20 in the circumferential direction by the input side rotating member 40 and the brake shoe 20 is rotated, the support surface 26 and the inner peripheral surface 11 are not rubbed. It is possible to suppress wear and to perform a good operation.
　また、ブレーキシュー２０が、支持面２６が設けられる突起２０Ｃを有するので、ブレーキシュー２０の剛性を向上させることができる。そして、このように、ブレーキシュー２０自身の剛性が向上することで、当該ブレーキシュー２０に掛かる負荷をより低減することができる。また、支持面２６が内周面１１に当接するときに、支持面２６と内周面１１が当接する位置がはっきりするので、より安定した動作をすることができる。 Further, since the brake shoe 20 has the protrusion 20C provided with the support surface 26, the rigidity of the brake shoe 20 can be improved. In this way, the load applied to the brake shoe 20 can be further reduced by improving the rigidity of the brake shoe 20 itself. Further, when the support surface 26 comes into contact with the inner peripheral surface 11, the position where the support surface 26 and the inner peripheral surface 11 come into contact becomes clear, so that a more stable operation can be performed.
　また、支持面２６が一対のブレーキ面２１の間における中央に設けられているので、支持面２６が内周面１１に当接したときに、ブレーキシュー２０の曲げ応力が最大となる位置を支持することができる。これにより、ブレーキシュー２０に掛かる負荷をより低減することができる。 Further, since the support surface 26 is provided at the center between the pair of brake surfaces 21, the position where the bending stress of the brake shoe 20 is maximized when the support surface 26 abuts against the inner peripheral surface 11 is supported. can do. Thereby, the load applied to the brake shoe 20 can be further reduced.
　また、支持面２６が内周面１１に沿った形状を有するので、これによっても、支持面２６が内周面１１に当接したときに、ブレーキシュー２０を安定して支持することができる。これにより、ブレーキシュー２０に掛かる負荷をより低減することができる。 In addition, since the support surface 26 has a shape along the inner peripheral surface 11, the brake shoe 20 can be stably supported when the support surface 26 abuts against the inner peripheral surface 11. Thereby, the load applied to the brake shoe 20 can be further reduced.
［第２実施形態］
　次に、本発明の第２実施形態について説明する。第２実施形態においては、第１実施形態と異なる部分についてのみ説明し、同様の部分については説明を省略する。
　図１７および図１８に示すように、入力側回転部材４０は、貫通孔４５が略円形の輪郭を有しており、その内周面に３つの係合部４５Ａが突出して形成されている。係合部４５Ａは、周方向に等間隔に配置され、図１７において第２接触面３６Ａに対して反時計回り側（図１８において時計回り側）に隣接している。このため、入力側回転部材４０は、係合部４５Ａにおいて出力側回転部材３０の作用部３１に周方向で係合して、出力側回転部材３０に回転トルクを伝達することが可能となっている。 [Second Embodiment]
Next, a second embodiment of the present invention will be described. In the second embodiment, only different parts from the first embodiment will be described, and description of similar parts will be omitted.
As shown in FIGS. 17 and 18, the input-side rotating member 40 has a through hole 45 having a substantially circular outline, and three engaging portions 45 </ b> A are formed to protrude from the inner peripheral surface thereof. The engaging portions 45A are arranged at equal intervals in the circumferential direction, and are adjacent to the second contact surface 36A in FIG. 17 on the counterclockwise side (clockwise side in FIG. 18). For this reason, the input-side rotating member 40 can be engaged with the action portion 31 of the output-side rotating member 30 in the circumferential direction at the engaging portion 45 </ b> A to transmit the rotational torque to the output-side rotating member 30. Yes.
　また、出力側に向けて突出した係合脚４２Ａと保持部４４は、第１実施形態に対して僅かに配置または大きさが異なっている。具体的には、保持部４４は、第１実施形態よりも僅かに周方向の大きさが大きい。また、係合脚４２Ａおよび係合部４５Ａは、出力側回転部材３０に回転トルクが入力されていて当該回転トルクをブレーキシュー２０のブレーキ力により受け止めている状態において、入力側回転部材４０を回転トルクと逆向きに回転させたときに、入力側回転部材４０の係合脚４２Ａがブレーキシュー２０に係合するよりも先に係合部４５Ａが出力側回転部材３０に係合するように配置されている。 Further, the engaging leg 42A and the holding portion 44 protruding toward the output side are slightly different in arrangement or size from the first embodiment. Specifically, the holding portion 44 is slightly larger in the circumferential direction than in the first embodiment. Further, the engaging leg 42 </ b> A and the engaging portion 45 </ b> A cause the input-side rotating member 40 to rotate when the rotating torque is input to the output-side rotating member 30 and the rotating torque is received by the braking force of the brake shoe 20. The engaging portion 45A is arranged to engage with the output-side rotating member 30 before the engaging leg 42A of the input-side rotating member 40 engages with the brake shoe 20 when rotated in the opposite direction. Yes.
　以上のように構成されたブレーキ装置３の作用効果について説明する。
　図１８に示すような、ブレーキ装置３に荷重が掛かっていない状態から、車両用シートＳに座った乗員の重みにより出力側回転部材３０に、図における時計回り方向の回転トルクを与えると、出力側回転部材３０が時計回りに少し回転する。すると、図１９に示すように、第２接触面３６Ａは、ローラ８１Ａを力Ｆ１で押し、ローラ８１Ａは、第１接触面２３Ａを力Ｆ２で押す。これにより、ブレーキシュー２０は、一対のブレーキ面２１が外輪１０の内周面１１に力Ｆ３で押し付けられる。その結果、ブレーキ面２１と内周面１１の間で摩擦力が発生するので、出力側回転部材３０が回転しない。すなわち、車両用シートＳが下がるのを阻止するブレーキ力が発生する。 The effects of the brake device 3 configured as described above will be described.
When no torque is applied to the brake device 3 as shown in FIG. 18, the output side rotating member 30 is given a rotational torque in the clockwise direction in the figure by the weight of the occupant sitting on the vehicle seat S. The side rotating member 30 is slightly rotated clockwise. Then, as shown in FIG. 19, the second contact surface 36A pushes the roller 81A with the force F1, and the roller 81A pushes the first contact surface 23A with the force F2. As a result, the brake shoe 20 has the pair of brake surfaces 21 pressed against the inner peripheral surface 11 of the outer ring 10 with the force F3. As a result, a frictional force is generated between the brake surface 21 and the inner peripheral surface 11, so that the output side rotating member 30 does not rotate. That is, a braking force that prevents the vehicle seat S from being lowered is generated.
　このとき、ローラ８１Ｂは、出力側回転部材３０の回転方向、つまり、時計回り方向に隣接する保持部４４から僅かに離間している。そのため、ローラ８１Ａが対向面３６と内側面２３に挟まれているだけでなく、スプリング８２の付勢力によりローラ８１Ｂも対向面３６と内側面２３に挟まれた状態を維持することができる。これにより、その後、ブレーキシュー２０をいずれの方向に回転しても、ブレーキシュー２０と外輪１０の間の摩擦力を維持できるので、予期せぬブレーキ力の解除を抑制することができる。
　ここまでの作用は、第１実施形態（図１２参照）と同様である。 At this time, the roller 81B is slightly separated from the holding portion 44 adjacent to the rotation direction of the output side rotation member 30, that is, the clockwise direction. Therefore, not only the roller 81A is sandwiched between the facing surface 36 and the inner side surface 23, but also the roller 81B can be maintained between the facing surface 36 and the inner side surface 23 by the biasing force of the spring 82. Thereby, even if the brake shoe 20 is rotated in any direction thereafter, the frictional force between the brake shoe 20 and the outer ring 10 can be maintained, so that an unexpected release of the braking force can be suppressed.
The operation up to this point is the same as in the first embodiment (see FIG. 12).
　図１９のブレーキ状態から、車両用シートＳの高さを上げるためにレバーＬＶを操作して入力側回転部材４０を反時計回りに回転させると、図２０に示すように、保持部４４がローラ８１Ｂに当接し、ローラ８１Ｂがスプリング８２の付勢力によって第１接触面２３Ａと第２接触面３６Ｂに挟持された状態が解除される。 When the lever LV is operated to raise the height of the vehicle seat S from the brake state of FIG. 19 and the input side rotation member 40 is rotated counterclockwise, the holding portion 44 is moved to the roller as shown in FIG. The state where the roller 81B is in contact with 81B and is held between the first contact surface 23A and the second contact surface 36B by the biasing force of the spring 82 is released.
　図２０の状態からさらに入力側回転部材４０を反時計回りに回転させると、図２１に示すように係合部４５Ａが出力側回転部材３０の作用部３１に係合する。これにより、出力側回転部材３０が時計回りに回転しようとしても係合部４５Ａが作用部３１を支えるので、出力側回転部材３０は回転することがない。すなわち、予期せず出力側回転部材３０が回転し、シートクッションＳ１がずり落ちることが抑制される。
　そして、係合部４５Ａが作用部３１を押圧することで出力側回転部材３０を回転させる。これにより、ローラ８１Ａが第１接触面２３Ａと第２接触面３６Ａに挟まれてブレーキ力を発生する状態が解除される。すなわち、出力側回転部材３０の回転は、ローラ８１Ａを介したブレーキ力を解除するのと同時に開始されるため、出力側回転部材３０を回し始めるときに大きな荷重が必要ではなく、回し始めの引っかかり感を抑制することができる。 When the input side rotation member 40 is further rotated counterclockwise from the state of FIG. 20, the engaging portion 45 </ b> A is engaged with the action portion 31 of the output side rotation member 30 as shown in FIG. 21. Thereby, even if the output side rotation member 30 tries to rotate clockwise, the engaging portion 45A supports the action portion 31, and therefore the output side rotation member 30 does not rotate. That is, it is possible to prevent the output side rotation member 30 from rotating unexpectedly and the seat cushion S1 from sliding down.
And 45 A of engaging parts press the action part 31, and rotate the output side rotation member 30. FIG. Accordingly, the state in which the roller 81A is sandwiched between the first contact surface 23A and the second contact surface 36A and generates a braking force is released. That is, the rotation of the output side rotating member 30 is started simultaneously with the release of the braking force via the roller 81A, so that a large load is not necessary when the output side rotating member 30 is started to rotate, and the start of rotation is caught. A feeling can be suppressed.
　図２１の状態からさらに入力側回転部材４０を反時計回りに回転させると、図２２に示すように、入力側回転部材４０の係合脚４２Ａが反時計回り側の端部でブレーキシュー２０の回転力入力面２５に周方向で当接する。これによりブレーキシュー２０が反時計回りに回転し始める。図２０から図２１にかけては、保持部４４がローラ８１Ｂを押し動かすことで、ローラ８１Ａとローラ８１Ｂが近づくのであるが、図２２の状態からは、ブレーキシュー２０の回転に伴ってローラ８１Ａも反時計回りに回転し始めるため、ローラ８１Ａとローラ８１Ｂが近づき過ぎてスプリング８２が詰まることを防止することができる。 When the input side rotating member 40 is further rotated counterclockwise from the state of FIG. 21, the engagement leg 42A of the input side rotating member 40 rotates the brake shoe 20 at the counterclockwise end as shown in FIG. It abuts on the force input surface 25 in the circumferential direction. As a result, the brake shoe 20 starts to rotate counterclockwise. From FIG. 20 to FIG. 21, the holding portion 44 pushes and moves the roller 81B, so that the roller 81A and the roller 81B approach each other. However, from the state of FIG. Since it starts to rotate clockwise, it can be prevented that the roller 81A and the roller 81B are too close to each other and the spring 82 is clogged.
　そして、さらに入力側回転部材４０を反時計回りに回転させると、図２３に示すように、係合部４５Ａが作用部３１に係合していることで出力側回転部材３０が反時計回りに回転するとともに、係合脚４２Ａが回転力入力面２５を押すことでブレーキシュー２０が反時計回り方向に回転する。 When the input side rotating member 40 is further rotated counterclockwise, the output side rotating member 30 is rotated counterclockwise because the engaging portion 45A is engaged with the action portion 31 as shown in FIG. The brake shoe 20 rotates counterclockwise as the engaging leg 42A pushes the rotational force input surface 25 while rotating.
　なお、図１９のブレーキ状態から、車両用シートＳの高さを下げるためにレバーＬＶを操作して入力側回転部材４０を時計回りに回転させた場合や、出力側回転部材３０に、通常使用範囲より大きい過大な時計回り方向の回転トルクが入力された場合の動作については第１実施形態と同様であるので説明を省略する。 In the brake state of FIG. 19, when the input side rotating member 40 is rotated clockwise by operating the lever LV to lower the height of the vehicle seat S, or when the input side rotating member 30 is normally used. Since the operation in the case where an excessive clockwise rotational torque larger than the range is input is the same as in the first embodiment, the description thereof is omitted.
　以上のようにして、本実施形態のブレーキ装置３によれば、係合部４５Ａが出力側回転部材３０に直接係合して出力側回転部材３０に回転トルクを伝達できるので、出力側回転部材３０に外部から回転トルクが入力されている状態において、その回転トルクに逆らう方向に入力側回転部材４０に回転トルクを入力すると、出力側回転部材３０に入力されている回転トルクを直接、入力側回転部材４０で支えて出力側回転部材３０を回転させることができる。そのため、不意にブレーキ力が抜けて出力側回転部材３０が意図せぬ方向に回ることが無く、安定した動作を実現することができる。 As described above, according to the brake device 3 of the present embodiment, the engaging portion 45A can directly engage the output-side rotating member 30 and transmit the rotational torque to the output-side rotating member 30, so that the output-side rotating member When rotational torque is input to the input side rotating member 40 in a direction against the rotational torque in a state in which rotational torque is input from the outside to the input 30, the rotational torque input to the output side rotating member 30 is directly input to the input side. The output side rotation member 30 can be rotated by being supported by the rotation member 40. Therefore, the brake force is not suddenly lost and the output side rotation member 30 does not rotate in an unintended direction, and a stable operation can be realized.
　また、ブレーキ装置３によれば、小さな初期荷重で出力側回転部材３０を回転させ始めることができ、引っかかり感を抑制することができる。 Moreover, according to the brake device 3, the output side rotation member 30 can be started to rotate with a small initial load, and a feeling of catching can be suppressed.
　以上に本発明の実施形態について説明したが、本発明は、前記した実施形態に限定されることなく適宜変形して実施することができる。
　例えば、前記実施形態においては、支持面２６が、各ブレーキシュー２０に１つだけ設けられていたが、支持面は、各ブレーキシューに複数設けられていてもよい。例えば、図２４に示すブレーキ装置３では、各ブレーキシュー２０は、本体部２０Ａの外周における、一対の突出部２０Ｂ（一対のブレーキ面２１）の間に、径方向外側に突出する２つの突起２０Ｃを有し、各突起２０Ｃの径方向外側の先端に支持面２６が設けられている。つまり、図２４のブレーキ装置３では、支持面２６が、各ブレーキシュー２０に２つずつ設けられている。このブレーキ装置３において、支持面２６は、出力側回転部材３０の軸方向に沿って見て、内周面１１の中心１１Ｃとローラ８１を結ぶ直線に交差する位置に配置されている。詳しくは、反時計回り側に配置される支持面２６Ａは、中心１１Ｃとローラ８１Ａの中心を結ぶ直線Ｌ２に交差する位置に配置され、時計回り側に配置される支持面２６Ｂは、中心１１Ｃとローラ８１Ｂの中心を結ぶ直線Ｌ３に交差する位置に配置されている。このようなブレーキ装置３によれば、出力側回転部材３０に過大な回転トルクが与えられた場合には、ブレーキシュー２０の外周の、内側面２３のローラ８１によって押される部分とは径方向の略反対側の位置で、支持面２６が内周面１１に当接するので、ローラ８１からブレーキシュー２０に掛かった荷重を支持面２６で効率良く支持することができる。これにより、ブレーキシュー２０に掛かる負荷をより低減することができる。 Although the embodiment of the present invention has been described above, the present invention is not limited to the above-described embodiment and can be appropriately modified and implemented.
For example, in the above embodiment, only one support surface 26 is provided for each brake shoe 20, but a plurality of support surfaces may be provided for each brake shoe. For example, in the brake device 3 shown in FIG. 24, each brake shoe 20 includes two protrusions 20C protruding outward in the radial direction between a pair of protrusions 20B (a pair of brake surfaces 21) on the outer periphery of the main body 20A. And a support surface 26 is provided at the radially outer tip of each protrusion 20C. That is, in the brake device 3 of FIG. 24, two support surfaces 26 are provided on each brake shoe 20. In the brake device 3, the support surface 26 is disposed at a position intersecting with a straight line connecting the center 11 </ b> C of the inner peripheral surface 11 and the roller 81 as viewed along the axial direction of the output-side rotating member 30. Specifically, the support surface 26A disposed on the counterclockwise side is disposed at a position intersecting with a straight line L2 connecting the center 11C and the center of the roller 81A, and the support surface 26B disposed on the clockwise side is formed with the center 11C. It is arranged at a position that intersects a straight line L3 connecting the centers of the rollers 81B. According to such a brake device 3, when an excessive rotational torque is applied to the output side rotation member 30, the portion of the outer periphery of the brake shoe 20 that is pressed by the roller 81 on the inner side surface 23 is in the radial direction. Since the support surface 26 abuts on the inner peripheral surface 11 at a substantially opposite position, the load applied to the brake shoe 20 from the roller 81 can be efficiently supported by the support surface 26. Thereby, the load applied to the brake shoe 20 can be further reduced.
　また、前記実施形態においては、内側面２３が第１接触面２３Ａと第１傾斜面２３Ｂ，２３Ｃを有し、第２接触面３６Ａ，３６Ｂが基準平面ＰＬから離れるほど第１接触面２３Ａに近づくように傾斜する構成であったが、これに限定されるものではない。例えば、図２５に示すように、第１傾斜面２３Ｂ，２３Ｃは無くても構わないし、第２接触面３６Ｇ，３６Ｈは、基準平面ＰＬから離れるほど第１接触面２３Ａから遠ざかるように傾斜していてもよい。詳しくは、図２５のブレーキ装置３の各ブレーキシュー２０は、径方向内側に符号を省略して示す凹部を有している。そして、当該凹部は、底面が内側面２３となっており、内側面２３は、ローラ８１と接触可能であるととともに、一対のブレーキ面２１の周方向の両端部同士を繋いだ方向に平行な第１接触面２３Ａを有している。また、凹部の周方向の面は、スプリング８２を支持するスプリング支持面２８となっている。出力側回転部材３０は、外周に、内側面２３に対向する対向面３６を有し、対向面３６は、基準平面ＰＬから離れるほど第１接触面２３Ａから遠ざかるように傾斜した第２接触面３６Ｇ，３６Ｈを有している。ローラ８１は、各ブレーキシュー２０の内側面２３と、対応する対向面３６の間に一対ずつ配置されている。スプリング８２は、各ローラ８１に対応して１つずつ設けられ、スプリング支持面２８と、対応するローラ８１との間に配置されている。スプリング８２は、対応するローラ８１を、内側面２３と対向面３６の間に形成される空間の狭い側、すなわち、対向面３６の周方向中央に向けて付勢している。 In the embodiment, the inner surface 23 has the first contact surface 23A and the first inclined surfaces 23B, 23C, and the second contact surfaces 36A, 36B are closer to the first contact surface 23A as they are separated from the reference plane PL. However, the present invention is not limited to this. For example, as shown in FIG. 25, the first inclined surfaces 23B and 23C may not be provided, and the second contact surfaces 36G and 36H are inclined so as to move away from the first contact surface 23A as the distance from the reference plane PL increases. May be. Specifically, each brake shoe 20 of the brake device 3 in FIG. The recess has an inner surface 23 on the bottom surface, the inner surface 23 can contact the roller 81, and is parallel to the direction connecting both ends in the circumferential direction of the pair of brake surfaces 21. It has a first contact surface 23A. The circumferential surface of the recess is a spring support surface 28 that supports the spring 82. The output-side rotating member 30 has an opposing surface 36 that opposes the inner surface 23 on the outer periphery, and the opposing surface 36 slopes away from the first contact surface 23A as the distance from the reference plane PL increases. , 36H. A pair of rollers 81 is disposed between the inner surface 23 of each brake shoe 20 and the corresponding opposing surface 36. One spring 82 is provided corresponding to each roller 81, and is disposed between the spring support surface 28 and the corresponding roller 81. The spring 82 urges the corresponding roller 81 toward the narrow side of the space formed between the inner surface 23 and the facing surface 36, that is, toward the circumferential center of the facing surface 36.
　出力側回転部材３０に、図における時計回り方向の通常使用範囲の回転トルクを与えると、第２接触面３６Ｇと第１接触面２３Ａの間隔が狭くなることで、ローラ８１Ａと第２接触面３６Ａおよび第１接触面２３Ａの圧力が高まる。これにより、第２接触面３６Ｇがローラ８１Ａを力Ｆ４１で押し、ローラ８１Ａが第１接触面２３Ａを力Ｆ４２で押すことで、各ブレーキシュー２０の一対のブレーキ面２１が外輪１０の内周面１１に力Ｆ４３で押し付けられ、ブレーキ力が発生する。このとき、第２接触面３６Ｈと第１接触面２３Ａの間隔は広くなるが、ローラ８１Ｂは、スプリング８２により第１接触面２３Ａと第２接触面３６Ｈの間に形成される空間の狭い側に付勢されることで、第１接触面２３Ａと第２接触面３６Ｈに接触した状態に維持される。 When a rotational torque in the normal use range in the clockwise direction in the drawing is applied to the output-side rotating member 30, the distance between the second contact surface 36G and the first contact surface 23A becomes narrow, so that the roller 81A and the second contact surface 36A And the pressure of 23 A of 1st contact surfaces increases. As a result, the second contact surface 36G pushes the roller 81A with the force F41, and the roller 81A pushes the first contact surface 23A with the force F42, so that the pair of brake surfaces 21 of each brake shoe 20 become the inner peripheral surface of the outer ring 10. 11 is pressed with a force F43 to generate a braking force. At this time, the interval between the second contact surface 36H and the first contact surface 23A is widened, but the roller 81B is placed on the narrow side of the space formed between the first contact surface 23A and the second contact surface 36H by the spring 82. By being urged, the first contact surface 23A and the second contact surface 36H are maintained in contact with each other.
　図２５のブレーキ状態から、入力側回転部材４０を反時計回り方向に回転させると、係合脚４２Ａが回転力入力面２５に当接してブレーキシュー２０を反時計回り方向に押し、ブレーキシュー２０が反時計回りに回転する。そして、第１接触面２３Ａがローラ８１Ａを押し、ローラ８１Ａが第２接触面３６Ｇを押すことで、出力側回転部材３０が反時計回りに回転する。一方、図２５のブレーキ状態から、入力側回転部材４０を時計回り方向に回転させると、図２６に示すように、係合脚４２Ｂが回転力入力面２５に当接してブレーキシュー２０を力Ｆ５１で時計回り方向に押し、ブレーキシュー２０が時計回りに回転する。そして、第１接触面２３Ａがローラ８１Ｂを力Ｆ５２で押し、ローラ８１Ｂが第２接触面３６Ｈを力Ｆ５３で押す。前述したとおり、ブレーキ状態において、ローラ８１Ｂは、第１接触面２３Ａと第２接触面３６Ｈに接触しているので、入力側回転部材４０が回転力入力面２５に当接してブレーキシュー２０を押すと、即座に力Ｆ５３が発生して、この力により出力側回転部材３０が時計回りに回転する。このように、このブレーキ装置３によれば、ローラ８１が内側面２３と対向面３６の間で遊ぶのを抑制して、安定した動作を実現することができる。 When the input side rotation member 40 is rotated counterclockwise from the brake state of FIG. 25, the engaging leg 42A abuts against the rotational force input surface 25 and pushes the brake shoe 20 counterclockwise. Rotates counterclockwise. Then, when the first contact surface 23A presses the roller 81A and the roller 81A presses the second contact surface 36G, the output-side rotating member 30 rotates counterclockwise. On the other hand, when the input side rotation member 40 is rotated clockwise from the brake state of FIG. 25, the engagement leg 42B comes into contact with the rotational force input surface 25 as shown in FIG. Pushing in the clockwise direction causes the brake shoe 20 to rotate clockwise. Then, the first contact surface 23A pushes the roller 81B with the force F52, and the roller 81B pushes the second contact surface 36H with the force F53. As described above, in the brake state, since the roller 81B is in contact with the first contact surface 23A and the second contact surface 36H, the input-side rotating member 40 contacts the rotational force input surface 25 and presses the brake shoe 20. Then, a force F53 is immediately generated, and the output side rotating member 30 is rotated clockwise by this force. Thus, according to the brake device 3, the roller 81 can be prevented from playing between the inner side surface 23 and the opposed surface 36, and a stable operation can be realized.
　前記実施形態では、ローラ８１が接触する内側面２３が、平面の組合せにより構成されていたが、曲面の組合せであってもよいし、ローラ８１と接触する部分が、全体として滑らかな曲面であってもよい。また、前記実施形態では、ローラ８１が接触する対向面３６が内側面２３の第１接触面２３Ａに対して傾斜した第２接触面３６Ａを有していたが、対向面は、その全体が、第１接触面に対して平行な平面であってもよい。 In the above-described embodiment, the inner side surface 23 with which the roller 81 contacts is configured by a combination of planes. However, the inner surface 23 may be a combination of curved surfaces, and the portion in contact with the rollers 81 may be a smooth curved surface as a whole. May be. Moreover, in the said embodiment, although the opposing surface 36 which the roller 81 contacts had the 2nd contact surface 36A inclined with respect to the 1st contact surface 23A of the inner surface 23, the opposing surface is the whole, It may be a plane parallel to the first contact surface.
　また、前記実施形態においては、出力側回転部材３０に回転トルクを与えた場合に、その回転方向が時計回り方向および反時計回り方向のいずれであっても、ローラ８１を介して対向面３６が内側面２３を押してブレーキ面２１が外輪１０の内周面１１に押し付けられることでブレーキシュー２０が回転しないように構成されていたが、これに限定されるものではない。例えば、図２７に示すように、ローラ８１Ｂや、ローラ８１Ｂに対応する第２接触面３６Ｂを無くし、出力側回転部材３０に回転トルクを与えた場合、一方の回転方向、具体的には、図の時計回り方向についてのみ、ローラ８１Ａを介して対向面３６（第２接触面３６Ａ）が内側面２３（第１接触面２３Ａ）を押してブレーキ面２１が外輪１０の内周面１１に押し付けられることでブレーキシュー２０が回転しないように構成されていてもよい。なお、図２７のブレーキ装置３の出力側回転部材３０には、径方向外側に突出する３つの係合部３９が設けられている。これにより、出力側回転部材３０を図の反時計回り方向に回転させた場合には、係合部３９がブレーキシュー２０を反時計回り方向に押すことで、ブレーキシュー２０が回転するようになっている。 In the above-described embodiment, when a rotational torque is applied to the output-side rotating member 30, the facing surface 36 is interposed via the roller 81 regardless of whether the rotational direction is the clockwise direction or the counterclockwise direction. Although the brake shoe 20 is configured not to rotate by pressing the inner side surface 23 and pressing the brake surface 21 against the inner peripheral surface 11 of the outer ring 10, it is not limited to this. For example, as shown in FIG. 27, when the roller 81B or the second contact surface 36B corresponding to the roller 81B is eliminated and rotational torque is applied to the output-side rotating member 30, one rotational direction, specifically, FIG. Only in the clockwise direction, the opposing surface 36 (second contact surface 36A) presses the inner side surface 23 (first contact surface 23A) through the roller 81A and the brake surface 21 is pressed against the inner peripheral surface 11 of the outer ring 10. The brake shoe 20 may be configured not to rotate. In addition, the output side rotation member 30 of the brake device 3 of FIG. 27 is provided with three engagement portions 39 that protrude radially outward. Thereby, when the output side rotation member 30 is rotated in the counterclockwise direction in the figure, the brake shoe 20 is rotated by the engagement portion 39 pushing the brake shoe 20 in the counterclockwise direction. ing.
　前記実施形態においては、通常使用範囲の回転トルクが出力側回転部材３０に与えられている状態（図１２参照）において、ローラ８１Ｂが保持部４４と非接触とされていたが、この状態において、ローラ８１Ｂが保持部４４に多少接していても構わない。この場合であっても、ブレーキシュー２０を時計回り方向に回転させるのに伴い、他方のローラ８１Ａが対向面３６と内側面２３に挟まれている間に一方のローラ８１Ｂと内側面２３および対向面３６が接触状態を得ることできるのであれば、実用上問題はない。 In the embodiment, the roller 81B is not in contact with the holding portion 44 in a state where the rotational torque in the normal use range is applied to the output-side rotating member 30 (see FIG. 12). The roller 81B may be slightly in contact with the holding portion 44. Even in this case, as the brake shoe 20 is rotated in the clockwise direction, while the other roller 81A is sandwiched between the opposing surface 36 and the inner side surface 23, the one roller 81B and the inner side surface 23 are opposed to each other. If the surface 36 can obtain a contact state, there is no practical problem.
　また、前記実施形態においては、出力側回転部材３０に荷重が入力されていない状態や、通常使用範囲の回転トルクが出力側回転部材３０に与えられている状態（図１２～図１５参照）において、支持面２６が外輪１０の内周面１１から離間していたが、これに限定されるものではない。例えば、ブレーキシューが回転するときの動作を妨げないのであれば、出力側回転部材に通常使用範囲の回転トルクが与えられている状態において、支持面が内周面に多少接していても構わない。また、支持面は、外輪の内周面に沿った形状でなくても構わない。 Further, in the above-described embodiment, in a state where no load is input to the output side rotating member 30, or in a state where the rotational torque in the normal use range is applied to the output side rotating member 30 (see FIGS. 12 to 15). The support surface 26 is separated from the inner peripheral surface 11 of the outer ring 10, but is not limited to this. For example, as long as the operation when the brake shoe rotates is not hindered, the support surface may be slightly in contact with the inner peripheral surface in a state where the rotation torque in the normal use range is applied to the output side rotation member. . Further, the support surface may not have a shape along the inner peripheral surface of the outer ring.
　前記第２実施形態においては、入力側回転部材４０に、一方向の回転についてのみ出力側回転部材３０と係合する係合部４５Ａを設けたが、係合部４５Ａを両方の回転について出力側回転部材３０と係合するように設けることもできる。また、前記実施形態および変形例の各特徴的要素は組み合わせて実施することができる。 In the second embodiment, the input-side rotating member 40 is provided with the engaging portion 45A that engages with the output-side rotating member 30 only for rotation in one direction, but the engaging portion 45A is provided on the output side for both rotations. It can also be provided to engage with the rotating member 30. Moreover, each characteristic element of the said embodiment and modification can be implemented in combination.
　また、前記実施形態において、出力側回転部材３０は、対向面３６を繋ぐ部分が曲面（曲面部３８）であったが、対向面を繋ぐ部分は、平面であっても構わない。 Further, in the above-described embodiment, the output side rotation member 30 has a curved surface (curved surface portion 38) that connects the facing surfaces 36, but the portion that connects the facing surfaces may be a flat surface.
　また、前記実施形態においては、付勢部材として圧縮コイルバネを例示したが、トーションバネや板バネ、ゴムなどであっても構わない。 In the above embodiment, the compression coil spring is exemplified as the urging member, but a torsion spring, a leaf spring, rubber or the like may be used.
　前記実施形態においては、可動片としてローラ８１を例示したが、可動片は、球や多角柱、楕円断面の柱状であっても構わない。 In the above embodiment, the roller 81 is exemplified as the movable piece. However, the movable piece may be a sphere, a polygonal column, or a column having an elliptical cross section.
　前記実施形態においては、ブレーキシュー２０は３つ設けられていたが、ブレーキシューは、２つでも、４つ以上であってもよい。 In the above embodiment, three brake shoes 20 are provided, but the number of brake shoes may be two or four or more.
　前記実施形態においては、ブレーキ装置３が、可動片としてのローラ８１と、付勢部材としてのスプリング８２を備え、内側面２３と対向面３６との間で、ローラ８１を介して荷重が伝達される構成であったが、これに限定されるものではない。例えば、可動片と付勢部材を備えずに、内側面と対向面とが直接接触して、これらの間で直接荷重が伝達される構成であっても構わない。 In the embodiment, the brake device 3 includes the roller 81 as the movable piece and the spring 82 as the biasing member, and the load is transmitted between the inner side surface 23 and the facing surface 36 via the roller 81. However, the present invention is not limited to this. For example, the configuration may be such that the inner surface and the facing surface are in direct contact with each other and the load is directly transmitted between them without providing the movable piece and the urging member.
　前記実施形態においては、ブレーキシュー２０が一対のブレーキ面２１の間に支持面２６を有していたが、ブレーキシューは、支持面や、当該支持面が設けられる突起を備えない構成であっても構わない。 In the above embodiment, the brake shoe 20 has the support surface 26 between the pair of brake surfaces 21, but the brake shoe has a configuration that does not include a support surface or a protrusion on which the support surface is provided. It doesn't matter.
　また、ブレーキ装置３、ラチェット装置２およびクラッチユニット１は、車両用シートＳのハイトアジャスト機構に用いられるだけでなく、他の装置に任意に適用することができる。 Further, the brake device 3, the ratchet device 2, and the clutch unit 1 are not only used for the height adjustment mechanism of the vehicle seat S, but can be arbitrarily applied to other devices.

Claims (21)

  1. 　円筒状の内周面を有する外輪と、
    　前記外輪の径方向内側に周方向に複数並んで配置され、前記内周面に対向して当該内周面と接触可能な一対のブレーキ面と前記径方向内側を向く内側面とを有するブレーキシューと、
    　前記各ブレーキシューの前記径方向内側に配置され、外周に、前記内側面に対向する対向面を有する出力側回転部材と、
    　前記ブレーキシューまたは前記出力側回転部材に周方向で当接して前記出力側回転部材に回転トルクを与えることが可能な入力側回転部材とを備え、
    　前記内側面および前記対向面は、前記出力側回転部材に回転トルクを与えても、少なくとも一方の回転方向については、前記対向面が前記内側面を押して前記ブレーキ面が前記外輪の前記内周面に押し付けられることで前記ブレーキシューが回転しないように構成され、
    　前記ブレーキシューは、前記一対のブレーキ面の間に、前記内周面に当接可能な支持面を有することを特徴とするブレーキ装置。     An outer ring having a cylindrical inner peripheral surface;
    A plurality of brake shoes arranged side by side in the circumferential direction on the radially inner side of the outer ring and having a pair of brake surfaces facing the inner circumferential surface and capable of contacting the inner circumferential surface, and an inner side surface facing the radially inner side When,
    An output-side rotating member that is disposed on the radially inner side of each of the brake shoes and has an opposing surface that faces the inner surface on the outer periphery;
    An input side rotation member capable of giving a rotational torque to the output side rotation member by contacting the brake shoe or the output side rotation member in a circumferential direction;
    Even if the inner side surface and the opposing surface give rotational torque to the output side rotating member, the opposing surface presses the inner side surface and the brake surface is the inner peripheral surface of the outer ring in at least one rotation direction. Configured so that the brake shoe does not rotate when pressed against
    The brake device, wherein the brake shoe has a support surface that can contact the inner peripheral surface between the pair of brake surfaces.
  2. 　前記支持面は、前記ブレーキシューに負荷が掛かっていない状態において前記内周面から離間していることを特徴とする請求項１に記載のブレーキ装置。 The brake device according to claim 1, wherein the support surface is separated from the inner peripheral surface in a state where no load is applied to the brake shoe.
  3. 　前記ブレーキシューは、外周において突出する突起を有し、
    　前記支持面は、前記突起に設けられていることを特徴とする請求項１に記載のブレーキ装置。     The brake shoe has a protrusion protruding at the outer periphery,
    The brake device according to claim 1, wherein the support surface is provided on the protrusion.
  4. 　前記支持面は、前記一対のブレーキ面の間における中央に設けられていることを特徴とする請求項１に記載のブレーキ装置。 The brake device according to claim 1, wherein the support surface is provided at a center between the pair of brake surfaces.
  5. 　前記支持面は、前記内周面に沿った形状を有することを特徴とする請求項１から請求項４のいずれか１項に記載のブレーキ装置。 The brake device according to any one of claims 1 to 4, wherein the support surface has a shape along the inner peripheral surface.
  6. 　前記内側面と前記対向面の間に配置される可動片と、前記可動片を、前記内側面と前記対向面の間に形成される空間の狭い側に付勢する付勢部材とをさらに備え、
    　前記対向面は、前記内側面に非平行な部分を含み、
    　前記内側面と前記対向面との間で、前記可動片を介して荷重が伝達されることを特徴とする請求項１に記載のブレーキ装置。     A movable piece disposed between the inner surface and the facing surface; and a biasing member that biases the movable piece toward a narrow side of a space formed between the inner surface and the facing surface. ,
    The opposing surface includes a portion non-parallel to the inner surface;
    The brake device according to claim 1, wherein a load is transmitted between the inner side surface and the opposing surface via the movable piece.
  7. 　前記支持面は、前記出力側回転部材の軸方向に沿って見て、前記内周面の中心と前記可動片を結ぶ直線に交差する位置に配置されていることを特徴とする請求項６に記載のブレーキ装置。 The said support surface is arrange | positioned in the position which cross | intersects the straight line which connects the center of the said internal peripheral surface and the said movable piece seeing along the axial direction of the said output side rotation member. The brake device described.
  8. 　前記内側面は、前記可動片と接触可能であるとともに前記一対のブレーキ面の前記周方向の両端部を繋いだ方向に平行な第１接触面を有し、
    　前記対向面は、前記ブレーキシューに負荷が掛かっていない状態において前記可動片と接触可能であるとともに前記第１接触面に対して傾斜した第２接触面を有することを特徴とする請求項６に記載のブレーキ装置。     The inner side surface has a first contact surface that can contact the movable piece and is parallel to a direction connecting both ends in the circumferential direction of the pair of brake surfaces,
    The said opposing surface has a 2nd contact surface which can contact with the said movable piece in the state in which the load is not applied to the said brake shoe, and inclined with respect to the said 1st contact surface. The brake device described.
  9. 　前記第２接触面は、前記内周面の中心を通り、前記第１接触面に直交する基準平面から離れるほど前記第１接触面に近づくように傾斜した傾斜部を有していることを特徴とする請求項８に記載のブレーキ装置。 The second contact surface includes an inclined portion that passes through the center of the inner peripheral surface and is inclined so as to approach the first contact surface as the distance from the reference plane orthogonal to the first contact surface increases. The brake device according to claim 8.
  10. 　前記第２接触面は、前記出力側回転部材の軸方向に沿って見て、前記ブレーキシューに向けて凸となる第１曲面部を有することを特徴とする請求項９に記載のブレーキ装置。 The brake device according to claim 9, wherein the second contact surface has a first curved surface portion that is convex toward the brake shoe when viewed along the axial direction of the output-side rotating member.
  11. 　前記第２接触面は、前記基準平面から離れるほど曲率半径が小さいことを特徴とする請求項１０に記載のブレーキ装置。 The brake device according to claim 10, wherein the radius of curvature of the second contact surface decreases with increasing distance from the reference plane.
  12. 　前記第２接触面と前記可動片が接触する点における前記第２接触面の接平面と前記第１接触面とのなす角である挟み角が、前記出力側回転部材に回転トルクが入力されたときの前記出力側回転部材の回転角度の増加に伴い、増加した後、減少するように前記第２接触面が形成されていることを特徴とする請求項１０または請求項１１に記載のブレーキ装置。 A pinch angle formed by a tangential plane of the second contact surface and the first contact surface at a point where the second contact surface and the movable piece are in contact with each other is a rotational torque input to the output-side rotating member. The brake device according to claim 10 or 11, wherein the second contact surface is formed so as to decrease after increasing as the rotation angle of the output-side rotating member increases. .
  13. 　前記挟み角の最大値は７．５５度以下であることを特徴とする請求項１２に記載のブレーキ装置。 The brake device according to claim 12, wherein the maximum value of the included angle is 7.55 degrees or less.
  14. 　前記第２接触面は、前記対向面における前記周方向の外側の両端部に１つずつ配置されていることを特徴とする請求項９に記載のブレーキ装置。 10. The brake device according to claim 9, wherein the second contact surfaces are arranged one by one at both ends of the outer surface in the circumferential direction on the facing surface.
  15. 　前記対向面は、前記両端部の各前記第２接触面を繋ぐ接続面部を有することを特徴とする請求項１４に記載のブレーキ装置。 The brake device according to claim 14, wherein the facing surface has a connection surface portion that connects the second contact surfaces of the both end portions.
  16. 　前記対向面は、前記第２接触面と前記接続面部との接続部分に凹部を有することを特徴とする請求項１５に記載のブレーキ装置。 The brake device according to claim 15, wherein the facing surface has a recess in a connection portion between the second contact surface and the connection surface portion.
  17. 　前記接続面部は平面部を有することを特徴とする請求項１５または請求項１６に記載のブレーキ装置。 The brake device according to claim 15 or 16, wherein the connection surface portion has a flat surface portion.
  18. 　前記出力側回転部材は、各前記ブレーキシューに対応した各前記対向面を繋ぐ第２曲面部を有することを特徴とする請求項８に記載のブレーキ装置。 The brake device according to claim 8, wherein the output side rotation member has a second curved surface portion that connects the opposing surfaces corresponding to the brake shoes.
  19. 　前記可動片はローラであることを特徴とする請求項８に記載のブレーキ装置。 The brake device according to claim 8, wherein the movable piece is a roller.
  20. 　前記入力側回転部材は、前記出力側回転部材に係合して回転トルクを伝達可能な係合部を有することを特徴とする請求項８に記載のブレーキ装置。 The brake device according to claim 8, wherein the input-side rotating member has an engaging portion that can engage with the output-side rotating member and transmit a rotational torque.
  21. 　前記出力側回転部材に回転トルクが入力されていて当該回転トルクを前記ブレーキシューのブレーキ力により受け止めている状態において、前記入力側回転部材を前記回転トルクと逆向きに回転させたときに、前記入力側回転部材が前記ブレーキシューに係合するよりも先に前記係合部が前記出力側回転部材に係合するように前記係合部が配置されていることを特徴とする請求項２０に記載のブレーキ装置。
          In a state where rotational torque is input to the output-side rotating member and the rotational torque is received by the braking force of the brake shoe, when the input-side rotating member is rotated in a direction opposite to the rotational torque, 21. The engagement portion is disposed so that the engagement portion engages with the output-side rotation member before the input-side rotation member engages with the brake shoe. The brake device described.
PCT/JP2016/070636 2015-07-16 2016-07-13 Brake device WO2017010496A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201680019230.XA CN107429768B (en) 2015-07-16 2016-07-13 Brake apparatus
EP16824476.2A EP3324066B1 (en) 2015-07-16 2016-07-13 Brake device
US15/561,897 US10428882B2 (en) 2015-07-16 2016-07-13 Brake device

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2015-141996 2015-07-16
JP2015141996A JP6613673B2 (en) 2015-07-16 2015-07-16 Brake device
JP2015141997 2015-07-16
JP2015-141997 2015-07-16
JP2015252142A JP6509721B2 (en) 2015-07-16 2015-12-24 Brake device
JP2015-252142 2015-12-24

Publications (1)

Publication Number Publication Date
WO2017010496A1 true WO2017010496A1 (en) 2017-01-19

Family

ID=57757488

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/070636 WO2017010496A1 (en) 2015-07-16 2016-07-13 Brake device

Country Status (1)

Country Link
WO (1) WO2017010496A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109667894A (en) * 2017-10-16 2019-04-23 三星电子株式会社 Actuator and exercise aid device including actuator
WO2020225257A1 (en) * 2019-05-08 2020-11-12 Stabilus Gmbh Brake device and method for controlling the brake device

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013253661A (en) * 2012-06-07 2013-12-19 Ts Tech Co Ltd Brake device
JP2014031090A (en) * 2012-08-02 2014-02-20 Ts Tech Co Ltd Brake system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013253661A (en) * 2012-06-07 2013-12-19 Ts Tech Co Ltd Brake device
JP2014031090A (en) * 2012-08-02 2014-02-20 Ts Tech Co Ltd Brake system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3324066A4 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109667894A (en) * 2017-10-16 2019-04-23 三星电子株式会社 Actuator and exercise aid device including actuator
CN109667894B (en) * 2017-10-16 2024-04-26 三星电子株式会社 Actuator and exercise assisting device including the same
WO2020225257A1 (en) * 2019-05-08 2020-11-12 Stabilus Gmbh Brake device and method for controlling the brake device
CN113795684A (en) * 2019-05-08 2021-12-14 斯塔比卢斯有限责任公司 Brake device and method for controlling a brake device
CN113795684B (en) * 2019-05-08 2024-05-03 斯塔比卢斯有限责任公司 Brake device and method for controlling a brake device
US11994185B2 (en) 2019-05-08 2024-05-28 Stabilus Gmbh Brake device and method for controlling the brake device

Similar Documents

Publication Publication Date Title
JP6370715B2 (en) Brake device
EP2261074B1 (en) Seat reclining apparatus for vehicle
JP6109613B2 (en) Brake device
EP3324066B1 (en) Brake device
EP1700737B1 (en) Automotive seat reclining device
JP6262718B2 (en) Brake device
JP2017116000A (en) Brake apparatus
JP2010255837A (en) Clutch device and seat device
WO2017010496A1 (en) Brake device
CN102145663A (en) Angle adjusting device for seat, self-locking mechanism thereof and seat with angle adjusting device
JP2017026140A (en) Brake device
JP6613673B2 (en) Brake device
WO2018025905A1 (en) Brake device and clutch unit
JP7055080B2 (en) Brake device for automobile seats
JP7089180B2 (en) Brake device and seat
JP2019183926A (en) Ratchet device
JP6627806B2 (en) Ratchet device
JP6483174B2 (en) Brake device and manufacturing method thereof
JP6721831B2 (en) Brake device
JP6093215B2 (en) Brake device
JP6792146B2 (en) Ratchet device
JP7368718B2 (en) brake device
WO2021090857A1 (en) Brake device
JP2014185668A (en) Ratchet device and clutch unit
JP2010259556A (en) Reclining device

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16824476

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2016824476

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 15561897

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE