JP6109613B2 - Brake device - Google Patents

Description

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

  In the height adjustment mechanism for a vehicle seat, the output shaft rotates by operating a lever provided on the input side that swings up and down. However, the weight of the seat and the occupant applies a force to the seat to lower the seat. However, the brake device comprised so that an output shaft may not rotate is used (patent document 1).

  Such a brake device includes an outer ring having a cylindrical inner peripheral surface, a plurality of brake cams (clamping members) opposed to the inner peripheral surface, and an output side rotating member (wing) disposed inside the brake cam. And a bolt). The rotation operation input to the brake cam is transmitted from the brake cam to the operation of the output side rotation member. However, even if the output side rotation member is rotated, the output side rotation member contacts the brake cam and the brake cam is rotated. The force exerted on the brake acts mainly as a force pressing the brake cam against the outer ring, and the rotational force applied to the brake cam by the output side rotating member cannot exceed the frictional force that can be generated between the brake cam and the outer ring. The cam cannot be rotated.

Japanese translation of PCT publication No. 2002-511035

  By the way, as a configuration of the brake device, when a rotational force is applied to the output side rotation member, it is desired to make the configuration in which the brake cam cannot rotate in both one and the other rotation directions (in this specification, “bidirectional type”). And the case where it is desired to configure the brake cam so that it cannot rotate only in one rotational direction (referred to as “one-way type” in this specification). It is advantageous in terms of production if both of these configurations can be realized in a compact manner with minimal changes in parts.

The present invention has been made in view of the above background, and an object of the present invention is to provide a one-way type brake device that can be used as a two-way type brake device with a minimum change in parts. .
Another object of the present invention is to reduce the number of parts and to make the device compact and lightweight.

  In order to achieve the above-described object, the present invention includes an outer ring having a cylindrical inner peripheral surface, and a plurality of outer rings arranged side by side in the radial direction inside the outer ring, and facing the inner peripheral surface. A brake cam having a brake surface that can come into contact with a surface and a cam surface that faces inward in the radial direction and gradually changes in distance from the central axis of the inner peripheral surface, and is arranged on the radially inner side of each brake cam. An output-side rotation member, an input-side rotation member that engages with each of the brake cams in the rotation direction, and an engagement portion that engages with the output-side rotation member so as to rotate integrally with the output-side rotation member; A rotation force transmission member having a transmission portion arranged so as to be able to contact the input side rotation member in one rotation direction with the brake cam, wherein the output side rotation member Gave a rotational force in the one direction of rotation A first contact portion that can contact the cam surface, and a second contact portion that can contact the cam surface when a rotational force is applied in the other rotational direction. When a rotational torque is applied from the input-side rotating member, the output-side rotating member rotates, and when a rotational torque is applied to the output-side rotating member, the transmission unit controls the input-side rotating member with respect to the one rotation direction. With respect to the other rotation direction, the second abutting portion presses the cam surface and the brake surface is pressed against the inner peripheral surface of the outer ring. It is characterized by not being configured.

  According to such a configuration, when a rotational torque is applied to the output side rotation member, the transmission unit rotates the brake cam via the input side rotation member in one rotation direction, and the other rotation direction Since the brake cam does not rotate when the one abutting portion presses the cam surface and the brake surface is pressed against the inner peripheral surface of the outer ring, it can be used as a one-way type brake device. If the state where the rotational force transmitting member engages with the input side rotational member in the rotational direction, such as removing the rotational force transmitting member, is released, the rotational torque is applied to the output side rotational member in one rotational direction. When the first contact portion presses the cam surface and the brake surface is pressed against the inner peripheral surface of the outer ring, the brake cam does not rotate. That is, it can be used as a bidirectional brake device.

  In the brake device described above, the rotational force transmitting member may be configured to be in pressure contact with the inner peripheral surface.

  In the brake device, when the input side rotating member is rotated, a member that generates a frictional force as a resistance (in the present specification, so as not to generate a sudden operation due to the torque already in the output side rotating member). , “Frictional force generating member”) may be provided. In the configuration in which the rotational force transmitting member is in pressure contact with the inner peripheral surface, the rotational force transmitting member can also serve as the frictional force generating member, so that the number of parts can be reduced.

  In the brake device described above, the engagement portion may have a ring shape, and the transmission portion may extend radially outward from the engagement portion.

  According to this, the rotational force transmission member can be reduced in weight by minimizing the weight.

  In addition, the rotational force transmission member may include a friction generating arm that extends radially outward from the ring portion and has a tip portion pressed against the inner peripheral surface.

  According to this, since the rotational force transmitting member can also function as a frictional force generating member, the number of parts can be reduced.

  Furthermore, the rotational force transmitting member can be configured with a constant thickness by a plate material.

  According to this structure, a rotational force transmission member can be comprised compactly. Moreover, when the function of a rotational force transmission member is lost, it can respond by cutting an unnecessary part or replacing with a washer. Alternatively, even if the rotational force transmitting member is simply omitted, the brake device can be used in a bidirectional type without significant influence.

  In the brake device described above, the transmission unit may be configured to be in contact with the input-side rotation member in the rotation direction and sandwich the input-side rotation member with the brake cam.

  According to this configuration, when the output-side rotation member is rotated in one rotation direction, there is no play between the transmission unit and the input-side rotation member, and the rotation force can be transmitted immediately.

  According to the configuration of the first aspect, when rotational torque is applied to the output-side rotation member, the transmission unit rotates the brake cam via the input-side rotation member in one rotation direction, and the other rotation direction. Since the brake cam does not rotate when the first contact portion presses the cam surface and the brake surface is pressed against the inner peripheral surface of the outer ring, it can be used as a one-way type brake device. On the other hand, if the state in which the rotational force transmitting member engages the input side rotational member in the rotational direction with the brake cam, such as removing the rotational force transmitting member, is released, it can be used as a bidirectional brake device. .

  According to the structure of Claim 2, since a rotational force transmission member can serve as a frictional force generation member, the number of parts can be reduced.

  According to the structure of Claim 3, a rotational force transmission member can be made into the minimum weight, and weight reduction can be achieved.

  According to the structure of Claim 4, since a rotational force transmission member can serve as a frictional force generation member, the number of parts can be reduced.

  According to the structure of Claim 5, a rotational force transmission member can be comprised compactly.

  According to the structure of Claim 6, when rotating the output side rotation member in one rotation direction, a rotational force can be transmitted immediately.

It is a side view of a vehicle seat. It is a disassembled perspective view of a clutch unit. It is a cross-sectional view of a brake device. FIG. 4 is a ZZ sectional view of the clutch unit in FIG. 3. 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) Enlarged front view showing the press-fitted state of the restricting portion and the fitting hole, and (b) YY sectional view of FIG. 7 (a) showing the press-fitted state of the restricting portion and the fitting hole. It is a figure explaining operation | movement of a ratchet apparatus, and shows the case where an operation input member is rotated clockwise. It is a figure explaining operation | movement of a ratchet apparatus, and shows the case where an operation input member is returned counterclockwise. It is a figure explaining operation | movement of a brake device, and shows the case where a clockwise rotational force is given to an output ring. It is a figure explaining operation | movement of a brake device, and shows the case where a counterclockwise rotational force is given to the output ring. It is a figure explaining operation | movement of a brake device, and shows the case where a clockwise rotational force is given to the output side rotation member. It is a figure explaining operation | movement of a brake device, and shows the case where a counterclockwise rotational force is given to the output side rotation member. It is a figure explaining operation | movement of the brake device when a friction ring is changed, and shows the case where clockwise rotational force is given to an output ring. It is a figure explaining operation | movement of the brake device at the time of changing a friction ring, and shows the case where a counterclockwise rotational force is given to the output side rotation member.

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

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

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

  The outline of the components of the ratchet device 2 and the brake device 3 will be described. The ratchet device 2 includes an operation input member 50, a regulating member 71, an output ring 40 as an input side rotation member of the brake device 3, and a movable piece. The roller 72 as an example and the return spring 73 are provided. The brake device 3 also functions as an outer ring 10, a brake cam 20 as an example of a brake force generating member, a spring 81 as an example of an urging member, an output side rotating member 30, and a rotational force transmitting member. A friction ring 82 and a washer 75 are provided. The output ring 40 is an output member of the ratchet device 2 and an input member of the brake device 3, and can be referred to as any part of the ratchet device 2 and the brake device 3.

Next, details of the configurations of the brake device 3 and the ratchet device 2 will be described.
First, the configuration of the brake device 3 will be described.
The outer ring 10 is made of a ring having a predetermined thickness, and has an 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. 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.

  A 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.

  The outer ring 10 is formed by punching a thick plate by press molding. As shown in FIGS. 4 and 6, the input side surface 13 is an inner peripheral edge 13A which is an inner peripheral edge and an outer peripheral edge. The outer peripheral edge 13B has a sagging shape formed at the time of punching. On the other hand, the output side surface 14 does not have a sagging shape on the inner peripheral edge 14A and the outer peripheral edge 14B. The outer ring 10 is welded to the input side surface of the mounting plate 85 by laser welding at the outer peripheral edge 14B of the output side surface 14 that does not have this sagging shape. For this reason, while the adhesiveness of the side surface 14 and the attachment plate 85 is high, since the outer periphery 14B is also closely_contact | adhered with the attachment plate 85, it can weld favorably.

  As shown in FIG. 6, this welding is performed over the entire circumference of the 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.

Further, this laser welding is performed from the side of the mounting plate 85 where the outer ring 10 is disposed, and thus the weld bead 85L is less likely to protrude from the outer (output side) surface of the mounting plate 85.
Therefore, it is not necessary to remove the weld bead 85L, or it is not necessary to keep other parts away in consideration of the protrusion of the weld bead 85L.

  Returning to FIG. 2, the brake cams 20 are members that generate a braking force with the outer ring 10, and three brake cams 20 are arranged inside the outer ring 10 at equal intervals in the circumferential direction. The brake cam 20 includes a main body portion 20A that extends in the circumferential direction, and a protruding portion 20B that protrudes radially outward from both circumferential ends of the main body portion 20A. A brake surface 21 facing the inner peripheral surface 11 of the outer ring 10 is provided at the radially outer end of the protruding portion 20B. The brake surface 21 has a cylindrical surface having the same radius as the inner peripheral surface 11 of the outer ring 10, and is in close contact with the inner peripheral surface 11 of the outer ring 10 when the brake cam 20 is biased radially outward. It has become.

  The brake cam 20 has a cylindrical outer peripheral surface 22 having a smaller diameter than the brake surface 21 between the pair of brake surfaces 21. Further, the radially inner surface of the brake cam 20 is a plane that faces the central axis of the outer ring 10. This plane is a cam surface 23 in which the distance from the central axis of the inner peripheral surface 11 (that is, the central axis of the output-side rotating member 30) is gradually changing, and is in contact with the output-side rotating member 30 described later. Is arranged. And the brake cam 20 has the end surface 24 which connects the both ends of the cam surface 23, and the edge part of the two brake surfaces 21 in the edge part of the circumferential direction. Further, the brake cam 20 is formed with a rotational force input surface 25 facing the circumferential direction at a step between the brake surface 21 and the outer peripheral surface 22.

  As shown in FIG. 3, the end surface 24 has an end surface 24A and an end surface 24B facing in the clockwise direction. The end face 24A and the end face 24B facing each other are not parallel, but are inclined so as to be separated from each other toward the outer side in the radial direction. In the present embodiment, the end surfaces 24A and 24B are also inclined with respect to the radial direction. A spring 81 made of a compression coil spring is disposed between the opposed end surfaces 24A and 24B with an initial load applied, and an end surface 24A as a first support surface of the first brake cam supports one end thereof. The end surface 24B as the second support surface of the second brake cam supports the other end. The end surface 24A and the end surface 24B are inclined so as to be separated from each other toward the outer side in the radial direction, so that the spring 81 autonomously moves to the outer side in the radial direction and contacts the inner peripheral surface 11 of the outer ring 10. The position is stabilized by being surrounded and supported by the inner peripheral surface 11, the end surface 24A and the end surface 24B from the periphery. Further, since the spring 81 biases the brake cams 20 apart from each other, the play of the brake cam 20 and the outer ring 10 is eliminated, and the balance of the arrangement of the brake cams 20 is not easily lost.

  As shown in FIG. 4, the brake cam 20 has an output side surface slidably disposed on the mounting plate 85, and a brake surface 21 is slidably disposed on the inner peripheral surface 11 of the outer ring 10. Yes. Here, as described above, since the outer ring 10 and the mounting plate 85 are laser welded along the outer peripheral edge 14B of the outer ring 10, the inner peripheral surface 11 and the input side surface of the mounting plate 85 are formed. The weld bead 85L does not protrude from the corner, and the smooth operation of the brake cam 20 can be ensured.

  Returning to FIG. 2, the output-side rotating member 30 has a shaft-like action portion 31, a flange 32 formed on the output side of the action portion 31, and protrudes from the action portion 31 to the input side, and is coaxial with the action portion 31. A small-diameter support shaft portion 33 and an output gear 35 formed to project to the output side of the flange 32 are provided. The output gear 35 protrudes to the output side through the through hole 85 </ b> A of the mounting plate 85.

  As shown in FIG. 3, the action part 31 has a substantially cylindrical shape as a whole, and this cylindrical shape has a slightly larger diameter than a circle inscribed in the three cam surfaces 23. The action portion 31 has a facing surface 34 formed of a flat surface facing the three cam surfaces 23 with a slight clearance from the cam surfaces 23. A gentle angle at the boundary between the cylindrical outer peripheral surface 31A and the opposing surface 34 of the action portion 31 is a portion that comes into contact with the cam surface 23 when attempting to rotate the brake cam 20 or the output side rotating member 30. In FIG. 3, there are a second contact portion 36 </ b> A corresponding to the counterclockwise edge portion of the facing surface 34 and a first contact portion 36 </ b> B corresponding to the clockwise edge portion. The first abutting portion 36B can abut on the cam surface 23 when the output-side rotating member 30 is rotated counterclockwise (one rotation direction), and the second abutting portion 36A When the rotational force is applied clockwise (the other rotation direction) to the side rotation member 30, it can come into contact with the cam surface 23.

  As shown in FIG. 2, the friction ring 82 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 released. This is a member that transmits the counterclockwise rotational force of the output side rotation member 30 to the brake cam 20 via the output ring 40. The friction ring 82 is an example of an engagement portion having a ring shape that is formed by punching a plate material (metal plate) having a constant thickness and has a hole that matches the outer periphery of the action portion 31 of the output-side rotating member 30. An example of a ring portion 82A, a friction generating arm 82B extending radially outward from the ring portion 82A, and having a tip portion pressed against the inner peripheral surface 11 of the outer ring 10, and a transmission portion extending radially outward from the ring portion 82A As a rotational force transmission arm 82C.

  The friction ring 82 is configured to rotate integrally with the output-side rotation member 30 when the hole of the ring portion 82 </ b> A engages with the action portion 31. The brake cam 20 is arranged so as to be displaced in the rotational axis direction, and partially overlaps the brake cam 20 when viewed from the axial direction, as shown in FIG.

  The friction generating arm 82B is inclined with respect to the radial direction so as to be positioned in the clockwise direction in FIG. Therefore, when the friction ring 82 rotates in the clockwise direction of FIG. 3, the friction ring 82 is likely to bite against the inner peripheral surface 11, so that a larger frictional force can be generated than when the friction ring 82 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.

  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 rotation member 30, and the hole 75 </ b> A is press-fitted into the shaft portion 37 (see FIG. 4). ). 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.

  Three rotational force transmission arms 82C are provided, and each of them is arranged so as to be able to abut on an engaging leg 42 of the output ring 40, which will be described later, in a counterclockwise direction.

Next, the configuration of the ratchet device 2 will be described.
As shown in FIG. 2, the output ring 40 can rotate around axes such as the outer ring 10 and the output side rotation member 30, and the rotation output of the ratchet device 2 is engaged with the brake cam 20 of the brake device 3 and transmitted. It is a member to do. The output ring 40 is manufactured by sheet metal processing of a metal plate, and includes a thin plate-shaped pressure receiving ring portion 41 and a plurality of engagement legs 42 protruding from the pressure receiving ring portion 41 toward the output side. . The inner peripheral surface 41A of the pressure receiving ring portion 41 has a circular cross section.

  Six engagement legs 42 are provided at equal intervals, and are arranged so that two each are inserted between a pair of protrusions 20B in one brake cam 20, as shown in FIG. That is, the size of the space between the pair of projecting portions 20B of the brake cam 20 is set as such, so that a slight play can be made between the projecting portion 20B and the engaging leg 42. The engaging leg 42 can engage with the rotational force input surface 25 of the brake cam 20 in the rotational direction.

  The rotational force transmitting arm 82C described above is provided adjacent to the clockwise side of the engaging leg 42 located on the counterclockwise side of the two engaging legs 42 disposed between the pair of protrusions 20B. . The rotational force transmitting arm 82 </ b> C contacts the engaging leg 42 in a rotational direction in a slightly bent state, and sandwiches the engaging leg 42 with the protruding portion 20 </ b> B of the brake cam 20. Thereby, the play of the output ring 40 is prevented.

  As shown in FIG. 2, the operation input member 50 engages with the lever LV and can swing integrally with the lever LV, and also engages with the output ring 40 via a roller 72 as a movable piece. , A member that transmits the rotational torque from the lever LV to the output ring 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.

  As shown in FIG. 5, 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 portions 53 and the large-diameter portions 54 are made of a plane. The cam surface 55 is connected. Since there are six places where the small diameter portion 53 and the large diameter portion 54 are switched, six cam surfaces 55 are formed correspondingly. The cam surface 55 is formed so that the distance from the central axis gradually changes.

  A roller 72 is disposed between the cam surface 55 and the inner peripheral surface 41 </ b> A of the pressure receiving ring portion 41. 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 output ring 40 to transmit and block input torque. A total of six rollers 72 are arranged corresponding to the cam surface 55. As shown in FIG. 4, the cam 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. As a result, the cam surface 55 can stably hold the roller 72 between the pressure receiving ring portion 41 and the cam surface 55.

  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 71B 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 as will be described later.

  As shown in FIG. 5, 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 cam 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, each roller 72 is in contact with the restricting portion 71B during the non-operation of FIG. 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. 5, 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 cam 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).

  As shown in FIG. 2, the cover member 60 includes a disc-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 an end portion on the output side of the outer peripheral portion 62. And a flange 63 extending outward in the radial direction. As shown in FIGS. 4 and 6, 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 diameter of the flange 63 is slightly smaller than the diameter of the outer ring 10 and is located on the radially inner side of the outer peripheral surface of the outer ring 10. As a result, the weld bead 60L is unlikely to protrude from the outer peripheral surface of the outer ring 10, so there is no need to remove the protruding weld bead 60L by polishing, and in consideration of interference between other parts and the weld bead 60L. It is no longer necessary to separate the parts. Further, the cover member 60 reinforces the outer ring 10 by being welded to the outer ring 10 along the outer peripheral edge thereof, and contributes to reducing the stress applied to the outer periphery of the outer ring 10. Thereby, the brake device 3 can generate a large braking force.

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

  The fitting holes 66 are three through holes provided corresponding to the three regulating portions 71 </ b> 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.

  As shown in FIG. 6 and FIGS. 7A and 7B, the fitting hole 66 has two protrusions protruding at the center in the circumferential direction so as to sandwich the restriction portion 71B toward the inside of the fitting hole 66. A portion 66A is provided. In the fitting holes 66 other than the protruding portions 66A, the radial gap is slightly larger than the plate thickness of the restricting portion 71B, and the gap between the protruding portions 66A is slightly smaller than the plate thickness of the restricting portion 71B. . The restricting portion 71B is press-fitted into the fitting hole 66 by inserting the tip portion between the two projecting portions 66A. As a result, the restricting member 71 is covered by a moderate press-fitting load. It is firmly fixed to 60. As shown in FIG. 7B, the tip of the restricting portion 71 </ b> B does not protrude from the outer surface 61 </ b> A of the side wall portion 61. Thereby, interference with the front-end | tip of the control part 71B and another component can be suppressed.

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. 5, the roller 72 is positioned between the inner peripheral surface 41 </ b> A of the output ring 40 and the cam surface 55 of the operation input member 50. It has not been done. 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 cam surface 55 rotates clockwise to contact the roller 72, and the roller 72 moves between the inner peripheral surface 41 </ b> A and the cam surface 55. It is pinched. Thereby, the operation input member 50 and the output ring 40 can rotate integrally.
Therefore, as shown in FIG. 8, if the operation input member 50 is rotated clockwise, the output ring 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 output ring 40.

  When the lever LV is swung counterclockwise from the state shown in FIG. 8 to return to the neutral position, the cam surface 55 escapes counterclockwise from the roller 72, and the roller 72 is located on the cam surface 55 and the inner peripheral surface 41A. Since it is not clamped, as shown in FIG. 9, the operation input member 50 is rotated toward the neutral position while the output ring 40 is stationary. That is, the input torque when returning the operation input member 50 is not transmitted to the output ring 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.

  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.

The operation of the brake device 3 when the output ring 40 is rotated by operating the lever LV will be described.
As shown in FIG. 10, when a clockwise rotational torque (input torque) is input from the output ring 40 as the input side rotating member, the three engaging legs 42 push the rotational force transmitting arm 82C clockwise. The output-side rotating member 30 engaged with the friction ring 82 rotates clockwise. Further, the other three engaging legs 42 of the output ring 40 come into contact with the rotational force input surface 25, and when the rotational force input surface 25 is pressed, the brake cam 20 rotates clockwise. As a result, when the output ring 40 is rotated clockwise, the output ring 40, the brake cam 20 and the output side rotating member 30 are integrally rotated clockwise.

  In the present embodiment, no rotational force is transmitted from the brake cam 20 to the output side rotation member 30, but when a relatively large play is provided between the rotational force transmission arm 82C and the engagement leg 42. Each cam surface 23 of the brake cam 20 abuts on the first abutting portion 36 </ b> B of the output side rotating member 30, so that a clockwise rotational force is applied to the output side rotating member 30.

  As shown in FIG. 11, when counterclockwise rotational torque is input from the output ring 40, the three engagement legs 42 of the output ring 40 abut against the rotational force input surface 25 and push the rotational force input surface 25. Then, the brake cam 20 rotates, and further, the cam surface 23 of the brake cam 20 contacts the second contact portion 36A and pushes the output-side rotating member 30, whereby the output-side rotating member 30 rotates. That is, the output ring 40, the brake cam 20, and the output-side rotating member 30 are integrally rotated clockwise. In the case of counterclockwise rotation, the engaging leg 42 does not push the rotational force transmitting arm 82C, so that the rotational force is not transmitted to the output side rotating member 30 via the friction ring 82.

Next, a case where a rotational force (reverse input torque) is input to the output side rotating member 30 will be described.
As shown in FIG. 12, when the rotational force in the clockwise direction in the figure is applied to the output side rotation member 30, the three second contact portions 36A come into contact with the corresponding cam surfaces 23 of the brake cams 20, and the cams Push the surface 23 radially outward. In accordance with the force F1 pushing the cam surface 23, the frictional force F2 acting at the contact point acts to slightly rotate the brake cam 20 counterclockwise.

  Further, the force F <b> 1 generates a force F <b> 3 that presses the brake cam 20 against the inner peripheral surface 11 of the outer ring 10 at the brake surface 21. Then, in accordance with this force F3, a frictional force F4 that resists the force to rotate the brake cam 20 clockwise acts between the inner peripheral surface 11 and the brake surface 21. In the brake device 3 of the present embodiment, the force to rotate the brake cam 20 by the frictional force F2 clockwise cannot exceed the frictional force F4, so that the output side rotating member 30, the brake cam 20 and the output The ring 40 cannot rotate with respect to the outer ring 10. That is, even if a clockwise rotational torque is applied to the output side rotation member 30, the brake cam 20 cannot rotate because the brake surface 21 is pressed against the inner peripheral surface 11. In this way, the brake device 3 can generate a braking force. In addition, when the rotational force in the clockwise direction is applied to the output-side rotating member 30 in this way, the vehicle seat S is applied with a force to lower the vehicle seat S due to the weight of the passenger sitting on the vehicle seat S. is there.

  As shown in FIG. 13, when a rotational force in the counterclockwise direction in the drawing is applied to the output side rotating member 30, three rotational force transmissions of the friction ring 82 that can rotate integrally with the output side rotating member 30 are transmitted. The arm 82C pushes the engagement leg 42 of the output ring 40 counterclockwise, and the engagement leg 42 pushes the rotational force input surface 25 of the brake cam 20 counterclockwise. That is, the rotational force transmission arm 82 </ b> C rotates the brake cam 20 via the output ring 40, whereby the output side rotation member 30 can rotate. Here, the rotational force transmitting arm 82 </ b> C and the brake cam 20 sandwich the engaging leg 42. For this reason, the rotational force transmission arm 82C does not play due to contact with the engaging leg 42. Therefore, when the rotational force in the counterclockwise direction is applied to the output ring 40, the rotational force transmission arm 82C starts to rotate immediately without being caught. In addition, when the rotational force in the counterclockwise direction is applied to the output side rotation member 30 in this manner, a force for lifting the vehicle seat S by hand or the like is applied regardless of the height adjustment mechanism.

  As described above, according to the clutch unit 1 (brake device 3) of the present embodiment, when the operation input member 50 is swung clockwise or counterclockwise from the neutral position, the output-side rotating member 30 rotates clockwise. Or rotate counterclockwise. Then, when a rotational force is applied to the output side rotation member 30, in the clockwise direction, the brake force is generated and thus the rotation does not rotate, and in the counterclockwise direction, the brake force is released and the rotation is performed. That is, the brake device 3 can be used as a one-way type brake (one-way clutch).

Next, it will be described that the brake device 3 can be used in a bidirectional type by changing the friction ring 82 of the brake device 3 partially.
As shown in FIG. 14, when the rotational force transmitting arm 82C is eliminated from the friction ring 82 and the friction ring 82 is used only as a frictional force generating member, the output ring 40 is rotated in the clockwise direction with reference to FIG. As described above, when the cam surface 23 of the brake cam 20 contacts the first contact portion 36B, the output-side rotating member 30 can rotate. However, since there is no rotational force transmission arm 82C, the rotational force is not transmitted to the output side rotation member 30 via the rotational force transmission arm 82C.

  When the output ring 40 is rotated counterclockwise, the cam surface 23 of the brake cam 20 contacts the second contact portion 36A in the same manner as described with reference to FIG. The member 30 can rotate.

  On the other hand, as shown in FIG. 15, when a rotational force in the counterclockwise direction in the drawing is applied to the output-side rotating member 30, the three first abutting portions 36B abut against the corresponding cam surface 23 of each brake cam 20. Then, the cam surface 23 is pushed radially outward. Then, in the same manner as described with reference to FIG. 12, a frictional force F4 that resists the force to rotate the brake cam 20 counterclockwise is provided between the inner peripheral surface 11 and the brake surface 21. Works. Since the force to rotate the brake cam 20 by the frictional force F2 counterclockwise cannot exceed the frictional force F4, the output side rotating member 30, the brake cam 20 and the output ring 40 are Can not rotate. That is, even if a counterclockwise rotational torque is applied to the output side rotating member 30, the brake cam 20 cannot rotate. In this way, the brake device 3 can generate a braking force.

  When a clockwise rotational force is applied to the output side rotating member 30, a braking force is generated in the same manner as described with reference to FIG. 12, and the output side rotating member 30 cannot rotate. .

  Thus, when the rotational force transmission arm 82C is eliminated, the brake device 3 can be used as a bidirectional brake. That is, the brake device 3 according to the present embodiment is configured so that the torque transmission arm 82C is cut, the friction ring 82 itself is omitted, or the friction ring 82 is replaced with a simple washer. It can be used as a bidirectional brake.

  And in the brake device 3 of this embodiment, since a frictional force generation member serves as a rotational force transmission member, the number of parts can be reduced.

  In the present embodiment, since the rotational force transmitting member is composed of the ring portion 82A and the rotational force transmitting arm 82C, the rotational force transmitting member can be reduced in weight with a minimum weight.

  Furthermore, since the friction ring 82 as the rotational force transmitting member is formed of a plate material with a constant thickness, the rotational force transmitting member can be configured compactly. Moreover, when the function of a rotational force transmission member is lost, it can respond by cutting an unnecessary part or replacing with a washer. Alternatively, even if the rotational force transmitting member is simply omitted, the brake device 3 can be used in a bidirectional type without significant influence.

Moreover, according to the clutch unit 1 in this embodiment, there can exist the following other effects.
In the brake device 3, the spring 81 biases the brake cams 20 apart from each other, so that the play between the brake cam 20 and the outer ring 10 is eliminated, and the balance of the arrangement of the brake cams 20 is not easily lost. As a result, the adhesion between the brake cam 20 and the inner peripheral surface 11 of the outer ring 10 is improved, so that a frictional force is efficiently generated between the brake cam 20 and the inner peripheral surface 11 and the braking force is efficiently generated. Can be generated. For this reason, according to the brake device 3, it is possible to efficiently generate a braking force and to reduce the size and weight of the brake device 3. Furthermore, in the brake device 3, since the three brake cams 20 are provided, the cam surface 23 of the brake cam 20 grips the output side rotation member 30 from three directions when rotational torque is applied to the brake cam 20. The shaft center of the output side rotation member 30 is stable, and a stable operation can be performed.

  In particular, in the present embodiment, the balance of the arrangement of the brake cams 20 can be further improved by providing the springs 81 between the brake cams 20.

  Further, since the spring 81 can contact the end surfaces 24A, 24B and the inner peripheral surface 11 at three locations and can autonomously stabilize the position thereof, the brake cam 20 is provided with a projection or the like for regulating the position of the spring 81. There is no need, and a simple configuration can be obtained.

  And the brake device 3 can simplify the shape of the outer ring | wheel 10 by fixing the mounting plate 85 and the outer ring | wheel 10 which are components which comprise a part of housing 100 not by crimping but by welding. Thereby, the outer ring 10 to which a large stress is applied can be reduced in weight by a simple cylindrical shape which is mechanically advantageous.

  In particular, since this welding is performed by laser welding, it is possible to efficiently generate a braking force by suppressing distortion of the shape of the outer ring 10 due to heat during welding, and to suppress a decrease in strength due to heat. As a result, the outer ring 10 can have a sufficient margin for strength. Further, since the cover member 60 and the outer ring 10 are fixed by welding without being caulked, the shape of the outer ring 10 can be further simplified. Thereby, the outer ring 10 to which a large stress is applied can be reduced in weight as a mechanically advantageous shape.

  In addition, the ratchet device 2 according to the present embodiment can be easily assembled because the regulating member 71 is prevented from rotating relative to the cover member 60 by fitting with the cover member 60 and does not require welding. . The regulating member 71 regulates the movement of the roller 72 in the circumferential direction and covers the side surface on the output side of the roller 72, and does not apply a large load. Function can be demonstrated. In particular, in the present embodiment, the restricting portion 71B is press-fitted into the fitting hole 66 of the cover member 60, so that it can be firmly fixed.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and can be appropriately modified and implemented.
For example, in the above embodiment, the rotational force transmitting member also serves as the frictional force generating member. However, the frictional generating arm 82B may be omitted and the rotational force transmitting member may function only as the rotational force transmitting member. Moreover, although the rotational force transmission member was comprised from the ring part 82A and the rotational force transmission arm 82C, the shape is not specifically limited. Further, the rotational force transmitting member and the input side rotating member (output ring 40) may be separated from each other in the rotational direction at normal times. That is, the play may be provided so that it is engaged only when a rotational force is applied to the output side rotation member 30 without being engaged at the normal time.

  In the above-described embodiment, the spring 81 is configured as a coil spring as an example of the biasing member, but may be a leaf spring or a sponge-like member. Moreover, when providing an urging member between each brake cam 20, they can also be connected together and can be comprised as one component.

  The movable piece used in the ratchet device 2 is not limited to the roller 72, and the shape is not limited as long as it is a small piece that can be engaged with and detached from the cam surface 55 and the inner peripheral surface 41 </ b> A, and may be a sphere or a wedge.

  In the embodiment, the fitting hole 66 is a through hole, but may be a hole with a bottom. Moreover, although the regulation part 71B and the fitting hole 66 were press-fitted and fitted, they may be fitted without being press-fitted.

  In the above-described embodiment, the outer ring 10 also serves as a part of the housing 100. However, the present invention is not limited to this, and a housing separate from the brake-side outer ring may be used.

  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.

DESCRIPTION OF SYMBOLS 1 Clutch unit 2 Ratchet device 3 Brake device 10 Outer ring 11 Inner peripheral surface 12 Outer peripheral surface 13 Side surface 14 Side surface 20 Brake cam 20A Main body portion 20B Protruding portion 21 Brake surface 23 Cam surface 24 (24A, 24B) End surface 25 Rotational force input surface 30 Output side rotation member 31 Action portion 31A Outer peripheral surface 34 Opposing surface 35 Output gear 36A Second contact portion 36B First contact portion 40 Output ring 41 Pressure receiving ring portion 41A Inner peripheral surface 42 Engagement leg 50 Operation input member 51 Cam plate portion 52 Lever engaging portion 55 Cam surface 60 Cover member 60L Weld bead 61 Side wall portion 63 Flange 66 Fitting hole 71 Restriction member 71A Side wall portion 71B Restriction portion 72 Roller 73 Return spring 81 Spring 82 Friction ring 82A Ring portion 82B Friction generating arm 82C Times Force transmitting arm 85 mounting plate 85L weld bead 90 the side frame 100 housing S vehicle seat

Claims (6)

An outer ring having a cylindrical inner peripheral surface;
Plurally arranged in the circumferential direction on the radially inner side of the outer ring, facing the inner circumferential surface and facing the inner circumferential surface, and facing the radially inner side from the central axis of the inner circumferential surface A brake cam having a cam surface with a gradually changing distance;
An output-side rotating member disposed on the radially inner side of each brake cam;
An input-side rotation member that engages with each of the brake cams in the rotation direction;
Between the engaging portion engaged with the output side rotating member and the brake cam so as to rotate integrally with the output side rotating member, the brake cam is disposed so as to be able to contact the input side rotating member. A rotational force transmission member having a transmission part, and a brake device comprising:
The output-side rotating member includes a first contact portion that can contact the cam surface when a rotational force is applied in the one rotational direction, and the cam surface when a rotational force is applied in the other rotational direction. A second abutting portion that can abut against
When rotational torque is applied to the brake cam from the input-side rotating member, the output-side rotating member rotates. The brake cam is rotated via a side rotation member, and the second rotation portion presses the cam surface and the brake surface is pressed against the inner peripheral surface of the outer ring with respect to the other rotation direction. A brake device configured to prevent the brake cam from rotating.   The brake device according to claim 1, wherein the rotational force transmitting member is in pressure contact with the inner peripheral surface.   The brake device according to claim 1, wherein the engaging portion has a ring shape, and the transmission portion extends radially outward from the engaging portion.   4. The brake device according to claim 3, wherein the rotational force transmission member includes a friction generating arm that extends radially outward from the engagement portion and has a distal end pressed against the inner peripheral surface.   The brake device according to any one of claims 1 to 4, wherein the rotational force transmission member is formed of a plate material with a constant thickness.   The said transmission part contacts the said input side rotation member in the rotation direction, and has pinched | interposed the said input side rotation member between the said brake cams. The brake device according to any one of claims.

Images