JP4940650B2 - Vehicle seat adjustment device - Google Patents

Description

  The present invention relates to a vehicle seat adjustment device that adjusts the height of a seat cushion, and more particularly to a clutch device of a vehicle seat adjustment device.

  Conventionally, some vehicle seats are provided with a vehicle seat adjustment device that adjusts the height of the seat cushion. In such a vehicle seat adjustment device, the height of the seat cushion can be adjusted by operating the operation lever while the occupant is on the seat.

For example, in the vehicle seat adjustment device disclosed in Patent Document 1, the height of the seat cushion is adjusted by inputting the input torque in the forward direction or the reverse direction by the operation lever, and the operation lever is released. The first clutch portion and the second clutch portion that hold the position of the seat cushion are provided. When an operating force is input to the operating lever, the operating force is transmitted from the outer ring, to which the operating lever is attached in the first clutch portion, to the inner ring via a roller, and in the second clutch portion, the operating force is applied from the inner ring to the output shaft. Is transmitted, the operating force of the operating lever is transmitted to the output shaft. When the operation lever is not driven, the second clutch portion restricts the rotation of the output shaft.
Japanese Patent Laid-Open No. 2002-54658 (FIG. 1)

  However, in the above-described vehicle seat adjustment device, both the first clutch portion and the second clutch portion are configured such that the force transmission direction is radially inward, so that the return spring for returning the outer ring to the neutral position Is arranged between both clutch parts arranged in the axial direction. For this reason, both clutch parts are spaced apart from each other in the axial direction, and the control member that transmits the rotational force from the first clutch part to the second clutch part becomes longer in the axial direction. For this reason, a large twisting force is applied to the control member during transmission of the force between the two clutch portions. For this reason, the control member needs to be strong enough to withstand a large torsional force. For example, the control member needs to be thickened in the radial direction, leading to an increase in the size of the apparatus.

  Moreover, since the cam surface (inner peripheral surface) of the outer ring receives a force toward the radially outer side via the roller in the first clutch portion, it is necessary to make the outer ring thick so as not to be deformed by the force. There was a problem that the size of the apparatus was increased.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a vehicle seat adjustment device capable of reducing the size of the device.

In order to solve the above-described problem, the invention according to claim 1 is a vehicle seat adjustment device that rotates an output shaft in accordance with an operation of an operation member and moves a seat cushion in the vertical direction by the rotation of the output shaft. An input side member connected to the operation member and pivotally supported by the output shaft; a control member disposed radially outside the input side member; and operating the operation member when the operation member is driven. A force can be transmitted from the input side member to the control member, and when the operation member is returned, a first clutch portion that releases transmission of force between the input side member and the control member; A second clutch portion that allows the operating force of the operating member to be transmitted from the control member to the output shaft, and restricts the rotation of the output shaft when the operating member is not driven; and the radial direction of the control member Outside And a stationary member for restricting the rotation of the output shaft at a time other than the drive operation of the operation member on the inner peripheral surface, and the radius of the portion of the control member containing the first clutch portion is stationary. The control member is supported by the inner peripheral surface of the stationary member in the same manner as the inner peripheral surface of the member, and the control member and the stationary member are arranged on the outer side in the radial direction of the first clutch portion. The gist of the invention is to have stepped portions extending in the radial direction so as to receive a force directed outward in the direction .

According to the above configuration, the force is transmitted from the radially inner side to the radially outer side in the first clutch portion, and the force is transmitted from the radially outer side to the radially inner side in the second clutch portion. Also in the first clutch portion, the radial difference between both clutch portions is smaller than when force is transmitted from the radially outer side toward the radially inner side. For this reason, since the torsional force generated between the two clutch parts when the operating force is transmitted is reduced, the member need not be reinforced in consideration of the torsional force, and the apparatus can be downsized.
Further, by receiving the pressure received by the control member from the first clutch portion on the inner peripheral surface of the stationary member, the control member is prevented from being deformed in the radial direction, and compared with the case where the pressure is received only by the control member. Can be made thinner.
Moreover, since the step part extended in radial direction exists in the site | part which receives the force which goes to the radial direction outer side of a 1st clutch part in a control member, the control member can receive the force suitably. Moreover, since the step part extended in radial direction exists in the site | part which receives the force which goes to the radial direction outer side of a 1st clutch part in a stationary member, a stationary member can receive the force suitably.

According to a second aspect of the present invention, there is provided a vehicle seat adjustment device that rotates an output shaft in accordance with an operation of an operation member and moves a seat cushion in a vertical direction by the rotation of the output shaft. And an input side member pivotally supported by the output shaft, a control member disposed radially outside the input side member, and an operating force of the operating member from the input side member when the operating member is driven. A first clutch portion that cancels transmission of force between the input side member and the control member when the operation member is returned; and an operation force of the operation member when the operation member is driven. A second clutch portion that is capable of transmitting from the control member to the output shaft and restricts the rotation of the output shaft when the operation member is not driven, and the first clutch portion is a cam of the input side member. Front and front A rotating member cam that includes a first rotating body that enables transmission of force between the inner peripheral surface of the control member and the second clutch portion is connected to the inner peripheral surface of the control member and the output shaft. A second rotating body capable of transmitting a force to the surface, and the end of the first rotating body and the end of the second rotating body are arranged so as to be the same or overlap in the axial direction. It is a summary.

According to the above configuration, the force is transmitted from the radially inner side to the radially outer side in the first clutch portion, and the force is transmitted from the radially outer side to the radially inner side in the second clutch portion. Also in the first clutch portion, the radial difference between both clutch portions is smaller than when force is transmitted from the radially outer side toward the radially inner side. For this reason, since the torsional force generated between the two clutch parts when the operating force is transmitted is reduced, the member need not be reinforced in consideration of the torsional force, and the apparatus can be downsized.
Also, the end of the first rotating body provided in the first clutch portion and the end of the second rotating body provided in the second clutch portion are arranged so as to be the same or overlap in the axial direction. Thus, the first clutch part and the second clutch part are arranged close to each other. For this reason, compared with the case where another member is arrange | positioned between a 1st clutch part and a 2nd clutch part, operation between the 1st clutch part and the 2nd clutch part at the time of drive operation of an operation member is carried out The force transmission path is shortened, and the transmission efficiency of operating force is improved.

  According to a third aspect of the present invention, in the vehicle seat adjustment device according to the first or second aspect, the vehicle-side seat adjustment device further includes a return unit that returns the input-side member to a neutral position when the input-side member is released, The gist is that the return means is disposed at a position close to the operation member in the axial direction.

  According to the above configuration, since the return means for returning the input side member to the neutral position is disposed at a position close to the operation member in the axial direction, the urging force of the return means is efficiently transmitted to the input side member.

  According to the vehicle seat adjustment device of the present invention, the device can be miniaturized.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment embodying the invention will be described with reference to the drawings.
The vehicle seat 1 shown in FIGS. 1 and 2 includes a seat cushion 1a and a seat back 1b extending obliquely upward from the upper surface of the rear end of the seat cushion 1a, and moves on lower rails 2a and 2b fixed to the vehicle floor. Supported as possible. A vehicle seat adjustment device 3 that adjusts the height of the seating surface of the seat cushion 1a is provided below the seat cushion 1a.

  Upper rails 4a and 4b are slidably mounted on the lower rails 2a and 2b, respectively. Base frames 5a and 5b of the seat cushion 1a are supported on the upper rails 4a and 4b so as to be movable up and down.

  That is, the lower end portions of the lifter links 6a and 7a are rotatably supported on the front and rear end portions of the upper rail 4a, and the upper end portions of the lifter links 6a and 7a are rotatably connected to the front and rear end portions of the base frame 5a. Yes. Similarly, the lower ends of the lifter links 6b and 7b are rotatably supported on the front and rear ends of the upper rail 4b, and the upper ends of the lifter links 6b and 7b are rotatably connected to the front and rear ends of the base frame 5b. ing. Further, the connecting portions of the lifter links 7 a and 7 b and the base frames 5 a and 5 b are connected by a cylindrical torque rod 8. Accordingly, the base frames 5a and 5b can be moved up and down in conjunction with each other.

  A clutch device 11 constituting the vehicle seat adjusting device 3 is attached to the base frame 5b, an operation lever 12 as an operation member is attached to the clutch device 11, and a pinion gear 13 is attached to the output shaft of the clutch device 11. Is provided. Then, the pinion gear 13 is rotated by the operation of the operation lever 12. At the rear of the clutch device 11, the base frame 5 b rotatably supports the lower portion of the base end side of the sector gear 14, and a tooth portion 14 a that meshes with the pinion gear 13 is formed at the distal end portion of the sector gear 14. The sector gear 14 rotates with the rotation of the pinion gear 13. The upper part of the base end side of the sector gear 14 and the upper end part of the lifter link 7 b are connected by a drive link 15. The drive link 15 is rotatably connected to the sector gear 14 and the lifter link 7b. Accordingly, when the sector gear 14 is rotated, the lifter link 7b is rotated via the drive link 15, the lifter link 7a is rotated via the torque rod 8, and the base frames 5a and 5b are moved up and down in conjunction with each other. The

Next, a specific configuration of the clutch device 11 will be described.
As shown in FIGS. 3 and 4, the clutch device 11 includes a case 21 as a stationary member formed in a substantially cylindrical shape, and the case 21 is formed to protrude radially outward as shown in FIG. 5. The plurality of attachment portions 21a are attached and fixed to the base frame 5b. The case 21 includes a small diameter portion 21b on the operation lever 12 side and a large diameter portion 21c on the counter operation lever 12 side, and a step portion extending in the radial direction between the small diameter portion 21b and the large diameter portion 21c. 21d is formed. An output shaft 22 is disposed inside the case 21, and the output shaft 22 is rotatably supported by the base frame 5b.

  The output shaft 22 is integrally formed with a rotor cam 23 as a rotating member on the operation lever 12 side of the base frame 5b, and a pinion gear 13 is integrally formed on the non-operation lever 12 side of the base frame 5b. The rotor cam 23 is formed in a substantially hexagonal shape, the outer peripheral surface is configured as a cam surface 23a, and a fitting groove 23b is formed at the center position of each side. The output shaft 22 and the rotor cam 23, and the output shaft 22 and the pinion gear 13 may be formed separately and engaged so as to rotate integrally.

  An input side member 24 to which the operation lever 12 shown in FIGS. 1 and 2 is attached is rotatably supported on the output shaft 22. As shown in FIG. 4, the input side member 24 includes an inner ring 25 that is formed in a cylindrical shape and through which the output shaft 22 is inserted, and a plate-like lever engaging portion 26 that extends radially outward from the inner ring 25. It has. As shown in FIG. 6, a plurality (three in the figure) of fitting holes 26 a into which the operation lever 12 is fitted are arranged in the lever engaging portion 26 along the circumferential direction. As a result, the input side member 24 rotates together with the operation lever 12. Further, an elastic body 27 made of a wave spring or a disc spring and washers 28a, 28b are attached to the tip of the output shaft 22 by screws 29, and the input side member 24 is attached in the axial direction by the elastic body 27. It is energized. As shown in FIG. 7, the inner ring 25 has an inner circumference formed in a circular shape and an outer circumference formed in a substantially pentagonal shape in a cross section in which the axes (front and back directions in the figure) are orthogonal to each other. The surface constitutes the cam surface 25a.

  As shown in FIGS. 3 and 4, a return member 31 and a control member 32 are disposed inside the case 21 and outside the input side member 24 in the radial direction. The return member 31 is loosely fitted on the radially outer side of the inner ring 25. The return member 31 includes a cylindrical portion 31a and a plurality of engaging portions 31b that protrude from the cylindrical portion 31a toward the counter-operating lever 12 along the axial direction. The number of the engaging portions 31b corresponds to the shape of the inner ring 25, and in the present embodiment, five are provided and are arranged at equal intervals along the circumferential direction.

  A control member 32 is loosely fitted on the radially outer side of the return member 31. The control member 32 includes an annular outer ring 32a, first engaging portions 32b and second engagement members that are formed so as to protrude from the outer ring 32a toward the counter-operating lever 12 along the axial direction and are alternately disposed along the circumferential direction. And a joint portion 32c. The outer ring 32 a is disposed on the radially outer side of the engaging portion 31 b of the return member 31. The diameter of the outer peripheral surface of the outer ring 32 a is the same as the diameter of the inner peripheral surface of the small diameter portion 21 b of the case 21. That is, the outer peripheral surface of the outer ring 32a is in pressure contact with the inner peripheral surface 21g of the small diameter portion 21b. The first engaging portion 32b is fitted into the fitting groove 23b of the rotor cam 23 with a predetermined backlash. The second engaging portion 32c is formed in an L shape having a step portion 32d extending radially outward from the outer ring 32a, and a portion extending along the axial direction has a diameter larger than that of the first engaging portion 32b. It is arranged outside in the direction.

  As shown in FIGS. 4 and 7, the return member is surrounded by the cam surface 25a of the inner ring 25, the inner peripheral surface of the outer ring 32a of the control member 32, the return member 31 and the rotor cam 23, and arranged along the cam surface 25a. A plurality of (five) spaces are defined by 31 engaging portions 31b. In each space, since the inner peripheral surface of the outer ring 32a is formed in a cylindrical shape and the cam surface 25a of the inner ring 25 is formed in a polygonal shape, the distance between the inner peripheral surface of the outer ring 32a and the cam surface 25a on both sides in the circumferential direction. Is formed with an end portion that becomes gradually narrower. As shown in FIG. 7, each space contains two first rollers 33 as first rotating bodies, and a first backlash stop is provided between the two first rollers 33 housed in each space. A spring 34 is inserted and arranged. As shown in FIG. 3, the first backlash spring 34 includes a spring part 34a disposed between the first rollers 33 and a connecting part 34b that connects the plurality of spring parts 34a. The spring part 34a is urged toward the first roller 33 disposed on both sides in the circumferential direction and in the disposed direction. Accordingly, each spring portion 34a has an inner periphery of the outer ring 32a of the control member 32 that is radially opposed to the cam surface 25a of the inner ring 25 and the cam surface 25a of the inner ring 25. The first roller 33 is urged in the direction of the end portion that becomes a narrow space of a substantially wedge-shaped space formed by the surface.

  3 and FIG. 7, the input side member 24 (inner ring 24), the return member 31, the first roller 33, the first backlash spring 34, and the control member 32 (outer ring) are configured as described above. 32a) constitutes the first clutch part 41. The step portion 21 d of the case 21 and the step portion 32 d of the control member 32 are disposed on the radially outer side of the first clutch portion 41.

  4 and 5, the second engagement of the control member 32 is surrounded by the cam surface 23a of the rotor cam 23, the inner peripheral surface 21e of the case 21 and the base frame 5b, and is arranged along the cam surface 23a. A plurality (six) spaces are partitioned by the portion 32c. In each space, the cam surface 23a of the rotor cam 23 is formed in a polygonal shape, and the inner peripheral surface 21e of the case 21 is formed in a cylindrical shape, so that the distance between the inner peripheral surface 21e and the cam surface 23a is on both sides in the circumferential direction. A gradually narrowing end is formed. Each space accommodates two second rollers 35 as two second rotating bodies. In the present embodiment, the end of the first roller 33 and the end of the second roller 35 are arranged so as to overlap in the axial direction.

  As shown in FIG. 5, a second backlash spring 36 is inserted between the two second rollers 35 housed in each space. As shown in FIG. 3, the second backlash spring 36 includes a spring portion 36a disposed between the second rollers 35 and a connecting portion 36b that connects the plurality of spring portions 36a. Each spring portion 36a is formed by the apex side of the rotor cam 23 whose outer peripheral surface is formed in a substantially polygonal shape, that is, the cam surface 23a of the rotor cam 23 and the inner peripheral surface of the case 21 that is radially opposed to the cam surface 23a. The second rollers 35 are urged in the direction of the end portion that becomes a narrow space of the substantially wedge-shaped space.

  With the above configuration, as shown in FIGS. 3 and 6, the control member 32 (the first engagement portion 32 b and the second engagement portion 32 c), the rotor cam 23, the second roller 35, and the second backlash. A second clutch portion 42 is configured by the stop spring 36 and the case 21. In the present embodiment, the first clutch portion 41 and the second clutch portion 42 are disposed close to each other in the axial direction.

  As shown in FIG. 3, hooks 21 f, 24 a, and 31 c are formed on the case 21, the input side member 24, and the return member 31 so as to overlap in the radial direction, respectively. As shown in FIG. 8, the hook portions 21f, 24a, 31c are engaged with return springs 37, 38 as return means, and are rotated to positions overlapping in the radial direction by the elastic force of the return springs 37, 38. By being biased in this manner, the input side member 24 and the return member 31 are provided to return to the neutral position corresponding to the hook portion 21f of the case 21. In the present embodiment, the return springs 37 and 38 are disposed close to the operation lever 12 in the axial direction.

  As shown in FIG. 4, the base frame 5 b has an auxiliary frame 16 attached at a position where the clutch device 11 is supported. The auxiliary frame 16 has a base end portion fixed to the base frame 5b with, for example, a bolt, and a distal end portion extending in parallel to the base frame 5b with a predetermined interval.

  A through hole is formed in the auxiliary frame 16 to form a first bearing portion 17, and a through hole is formed in the base frame 5 b so that the center line overlaps with the first bearing portion 17, and a second bearing portion is formed. 18 is formed. The diameter of the second bearing portion 18 is larger than the diameter of the first bearing portion 17.

  The output shaft 22 has an intermediate portion rotatably supported by the second bearing portion 18 and a distal end portion rotatably supported by the first bearing portion 17. Further, the tooth portion 14a of the sector gear 14 is meshed with the pinion gear 13 between the auxiliary frame 16 and the base frame 5b.

  As shown in FIG. 4, on the side of the pinion gear 13, two plane portions 22 a that are parallel to each other are formed on the side surface of the distal end portion of the output shaft 22. A spiral spring 39 is disposed around the distal end portion of the output shaft 22, and the inner peripheral side end portion 39a of the spiral spring 39 is formed so as to face substantially parallel as shown in FIG. The tip end portion of the output shaft 22 is fitted so that the flat surface portion 22a is in contact with the inner peripheral end portion 39a of the spiral spring 39, and the outer peripheral end portion 39b of the spiral spring 39 is between the auxiliary frame 16 and the base frame 5b. It is engaged with the latching shaft 40 supported by. Accordingly, the urging force of the spiral spring 39 applies a required rotational torque to the output shaft 22 with the base frame 5b as a fulcrum, and the torque acts in a direction to raise the base frames 5a and 5b.

Next, the operation of the vehicle seat adjustment apparatus including the clutch device 11 as described above will be described.
As shown in FIG. 4, when the user rotates the operation lever 12 in the seat raising direction, the input side member 24 to which the operation lever 12 is attached rotates integrally. By the rotation of the input side member 24, the inner ring 25 shown in FIG. 7 rotates, for example, in the clockwise direction, and the first roller 33 disposed between the cam surface 25a of the inner ring 25 and the outer ring 32a of the control member 32. Engages (bits into) the wedge gap. Thereby, the rotation of the inner ring 25 is transmitted to the control member. As described above, in the first clutch portion 41, the operating force of the operation lever 12 can be transmitted from the input side member 24 to the control member 32 when the operation lever 12 is driven.

  When the control member 32 rotates, the first engaging portion 32b of the control member 32 shown in FIG. 5 engages with the side surface of the fitting groove 23b of the rotor cam 23, and the rotor cam 23 rotates clockwise in the drawing. At this time, the second roller 35 disposed between the cam surface 23a of the rotor cam 23 and the inner peripheral surface 21e of the case 21 is pushed and moved in the rotational direction of the rotor cam 23 by the second engagement portion 32c. Therefore, it does not engage (do not bite) the wedge gap. That is, the output shaft 22 rotates according to the operation of the operation lever 12. As described above, in the second clutch portion 42, the operating force of the operating lever 12 can be transmitted from the control member 32 to the output shaft 22 when the operating lever 12 is driven. Thereby, the sector gear 14 which meshes with the pinion gear 13 of the output shaft 22 is rotated. Based on the rotation of the sector gear 14, the lifter links 7a and 7b are rotated via the drive link 15, and the base frames 5a and 5b are raised. Accordingly, the seat cushion 1a is raised. At this time, since the urging force of the spiral spring 39 acts in the direction of assisting the rotation of the output shaft 22, the operating force of the operating lever 12 is reduced.

  When the operation lever 12 is released, the output shaft 22 rotates counterclockwise in FIG. 5 due to the load due to the weight of the vehicle seat 1 and the weight of the passenger. At this time, the output shaft 22 and the rotor cam 23 are integrally rotated, and the rotor cam 23 is rotated between the cam surface 23a of the rotor cam 23 and the inner peripheral surface 21e of the case 21 as described above. The second roller 35 engages (bits into) the wedge gap. Since the case 21 is fixed to the base frame 5b, the rotation of the output shaft 22 is prevented. That is, in the second clutch portion 42, the rotation of the output shaft 22 is restricted when the operation lever 12 is not driven.

  When the operation lever 12 is released, the return member 31 and the input side member 24 are rotated to the neutral position by the return springs 37 and 38. At this time, the first roller 33 moves in the same direction as the rotation direction of the return member 31 and the input side member 24 by the engaging portion 31b of the return member 31 and does not bite, so that the rotation in the neutral direction is restricted. Not. That is, in the first clutch portion 41, the transmission of force between the input side member 24 and the control member 32 is released when the operation lever 12 is returned.

  The clutch device 11 operates in the same manner as when the operation lever 12 is released when the operation lever 12 rotated in the seat raising direction is rotated to the neutral position. Not regulated. When the operation lever 12 is rotated in the seat lowering direction, the rotation direction is different, but the operation is the same as described above, and thus the description thereof is omitted.

According to the configuration of the present embodiment, the following effects can be obtained.
(1) Since the force is transmitted from the radially inner side to the radially outer side in the first clutch part 41, and the force is transmitted from the radially outer side to the radially inner side in the second clutch part 41, The radial difference between the first clutch portion 41 and the second clutch portion 42 is smaller in the one clutch portion than in the case where force is transmitted from the radially outer side toward the radially inner side. For this reason, since the twisting force generated between the first clutch part 41 and the second clutch part 42 during transmission of the operating force is reduced, it is not necessary to reinforce the control member 32 in consideration of the twisting force, and the device can be downsized. You can plan.

  (2) When the control member is disposed on the radially inner side of the input side member as described in Patent Document 1, the control member is a roller of the second clutch portion located outside the roller from the inside of the roller of the first clutch portion. Therefore, the control member is interposed between the rollers in the axial direction, and the rollers cannot be arranged close to the axial direction. On the other hand, according to the configuration of the present embodiment, since the control member 32 is arranged on the radially outer side of the input side member 24, the first roller 33 of the first clutch portion 41 and the second clutch portion 42 of the second clutch portion 42 are arranged. The control member 32 may not be interposed between the two rollers 35. That is, by arranging the end of the first roller 33 and the end of the second roller 35 so as to overlap, it is easy to arrange the first roller 33 and the second roller 35 close to each other in the axial direction. Can be realized.

  In this way, by arranging the first roller 33 of the first clutch portion 41 and the second roller 35 of the second clutch portion close to each other in the axial direction, the first clutch portion 41, the second clutch portion 42, Compared with the case where another member is disposed between the first clutch portion 41 and the second clutch portion 42 during the driving operation of the operation lever 12, the transmission path of the operation force between the first clutch portion 41 and the second clutch portion 42 is shortened. Transmission efficiency is improved.

  (3) Since the return springs 37 and 38 for returning the input side member 24 to the neutral position are disposed at positions close to the operation lever 12 in the axial direction, the urging force of the return springs 37 and 38 is applied to the input side member 24. The first clutch portion 41 to be transmitted is at a position separated in the axial direction. For this reason, the urging force of the return springs 37 and 38 is efficiently transmitted to the input side member 24.

  (4) Since the step portion 32d extending in the radial direction is present at the portion of the control member 32 that receives the force toward the radially outer side of the first clutch portion 41, the control member can suitably receive the force.

  (5) When the pressure received by the control member 32 from the first clutch portion 41 is received by the inner peripheral surface 21g of the case 21, the radial deformation of the control member 32 is suppressed, and the pressure is received only by the control member 32. In comparison with the control member, the thickness of the control member can be reduced.

  (6) Since the step portion 21d extending in the radial direction is present at the portion of the case 21 that receives the force toward the radially outer side of the first clutch portion 41, the case 21 can suitably receive the force.

Note that the present embodiment is not limited to the above configuration, and may be modified to the following modes.
In the above embodiment, the end portion of the first roller 33 of the first clutch portion 41 and the end portion of the second roller 35 of the second clutch portion 42 are arranged so as to overlap in the axial direction. You may arrange | position so that the end surface of the roller 33 and the end surface of the 2nd roller 35 may become the same position in an axial direction.

  In the above embodiment, the case 21 of the clutch device 11 is directly attached and fixed to the base frame 5b. However, even if the base for supporting the output shaft 22 is provided and the case 21 is fixed to the base, the clutch device 11 is unitized. Good.

  In the above-described embodiment, the seat cushion 1a is urged by the spiral spring 39, but may be urged by another elastic body such as a torsion bar.

The perspective view of a vehicle seat. The perspective view of the vehicle seat adjustment apparatus. The disassembled perspective view of a clutch apparatus. Sectional drawing of a clutch apparatus. AA line sectional view of Drawing 4. Explanatory drawing of an input side member. BB sectional drawing of FIG. Explanatory drawing of a return spring. The front view of a spiral spring.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1a ... Seat cushion, 3 ... Vehicle seat adjustment apparatus, 12 ... Operation lever (operation member), 21 ... Case (stationary member), 21d ... Step part, 21e ... Inner peripheral surface, 23 ... Rotor cam (rotating member), 23a ... cam surface, 24 ... input side member, 22 ... output shaft, 25a ... cam surface, 32 ... control member, 32d ... step portion, 33 ... first roller (first rotating body), 35 ... second roller (first) 2 rotation bodies), 37, 38 ... return spring (return means), 41 ... first clutch portion, 42 ... second clutch portion.

Claims (3)

A vehicle seat adjustment device that rotates an output shaft according to an operation of an operation member and moves a seat cushion in the vertical direction by rotation of the output shaft,
An input side member connected to the operation member and supported by the output shaft;
A control member disposed radially outside the input side member;
When the operation member is driven, the operation force of the operation member can be transmitted from the input side member to the control member, and when the operation member is returned, the force transmission between the input side member and the control member is released. 1 clutch part,
A second clutch portion that allows the operating force of the operating member to be transmitted from the control member to the output shaft during a driving operation of the operating member, and restricts the rotation of the output shaft during a time other than the driving operation of the operating member; ,
A stationary member that is disposed on the radially outer side of the control member and restricts the rotation of the output shaft at a time other than the drive operation of the operation member on the inner peripheral surface;
Bearing the control member on the inner peripheral surface of the stationary member with the radius of the portion of the control member containing the first clutch portion being the same as the inner peripheral surface of the stationary member;
The control member and the stationary member each have a step portion extending in the radial direction so as to receive a force toward the radially outer side of the first clutch portion on the radially outer side of the first clutch portion. Vehicle seat adjustment device. A vehicle seat adjustment device that rotates an output shaft according to an operation of an operation member and moves a seat cushion in the vertical direction by rotation of the output shaft,
An input side member connected to the operation member and supported by the output shaft;
A control member disposed radially outside the input side member;
When the operation member is driven, the operation force of the operation member can be transmitted from the input side member to the control member, and when the operation member is returned, the force transmission between the input side member and the control member is released. 1 clutch part,
A second clutch portion that allows the operating force of the operating member to be transmitted from the control member to the output shaft during a driving operation of the operating member, and restricts the rotation of the output shaft during a time other than the driving operation of the operating member; With
The first clutch portion includes a first rotating body that enables transmission of force between a cam surface of the input side member and an inner peripheral surface of the control member,
The second clutch portion includes a second rotating body that enables transmission of force between an inner peripheral surface of the control member and a cam surface of a rotating member connected to the output shaft,
Wherein an end portion of the first rotating body and the end portion of the second rotating body, car dual seat adjustment mechanism characterized in that it is arranged to the same or overlapping in the axial direction.   2. A return means for returning the input side member to a neutral position when the input side member is released, wherein the return means is disposed at a position close to the operation member in the axial direction. Or the vehicle seat adjustment device according to 2;

Images