JP2017065411A - Seat drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a seat drive device of which enhancement of operability is enabled.SOLUTION: A seat drive device comprises: a slide operation handle 53S which is rotatably connected to a body case 17, which extends above a seat, and which makes a clutch mechanism corresponding to a slide mechanism as to be in a connection state in association with rotation thereof; a tilt operation handle 53T and a lifter operation handle 53L which are rotatably connected to the body case 17, and which make the clutch mechanism corresponding a tilt mechanism and to a lifter mechanism respectively as to be in a connection state; a linkage lever 99; a tilt relay lever 58T and a lifter relay lever 58L which are rotatably connected to the tilt operation handle 53T and the linkage lever 99 respectively, and which extend upwards in the front and rear of the seat with respect to the slide operation handle 53S; and a movement operation knob 100 provided with a slide guide recess 101S in which tips of the tilt relay lever 58T and the lifter relay lever 58L are respectively rotatably supported, and in which a slide guide protrusion 60S is inserted.SELECTED DRAWING: Figure 11

Description

  The present invention relates to a sheet driving apparatus.

  Conventionally, as a sheet drive device, for example, a device described in Patent Document 1 is known. The seat drive device selectively selects a rotation motor, a plurality of operation members individually disposed corresponding to the plurality of position adjustment mechanisms, and a position adjustment mechanism corresponding to any one of the plurality of operation members. A plurality of clutch mechanisms connectable to the rotary motor, and a switch for energizing the rotary motor with a polarity corresponding to the operation direction in accordance with an operation of any of the plurality of operation members.

JP 2013-107624 A

  By the way, in Patent Document 1, since a plurality of operation members are individually provided corresponding to a plurality of position adjustment mechanisms, it is necessary to change to a corresponding operation member in accordance with one position adjustment mechanism to be operated. There is. In addition, since the arrangement and the operation direction of the operation member do not coincide with the operation of adjusting the position of the sheet by the position adjustment mechanism, the operability is impaired because it is difficult to understand intuitively.

  An object of the present invention is to provide a seat driving device that can improve operability.

  A seat driving device that solves the above-described problem is housed in a housing, and includes a plurality of clutch mechanisms that can selectively connect a slide mechanism, a tilt mechanism, and a lifter mechanism to a rotary motor, and the housing around the axis extending in one direction. A slide operation handle that is pivotably connected and extends above the seat, has a slide guide protrusion at the tip, and moves the clutch mechanism corresponding to the slide mechanism in connection with the rotation, and the one-way A tilt operation handle and a lifter operation handle that are rotatably connected to the housing around an axis extending in parallel with each other, and that bring the clutch mechanism corresponding to the tilt mechanism and the lifter mechanism into a connected state with the rotation, Around the axis extending in parallel with one direction, the tilt operation handle and the lifter operation handle are rotatably connected respectively, Tilt relay lever and lifter relay lever extending upward and forward of the seat operation handle, respectively, and the tip of the tilt relay lever and lifter relay lever pivoting about an axis extending parallel to the one direction, respectively. Movement in which a slide guide recess is formed, which is supported freely and in which the slide guide protrusion is relatively movable in the circumferential direction around each of the two end portions and is immovable in the longitudinal direction of the seat. And an operation knob.

  According to this configuration, when the movement operation knob is moved in the front-rear direction of the seat, the slide guide concave portion presses the slide guide protrusion, so that the slide operation handle rotates about the axis. As a result, the clutch mechanism corresponding to the slide mechanism is in a connected state, and the front-rear position of the seat is adjusted.

  Further, when the movement operation knob is rotated so that the front end portion of the movement operation knob moves up and down with the tip end portion of the lifter relay lever as a fulcrum, the slide guide recess is moved with respect to the slide guide protrusion. Meanwhile, the tilt operation handle and the tilt relay lever rotate. Then, when the tilt operation handle is rotated about its axis, the clutch mechanism corresponding to the tilt mechanism is connected, and the vertical position of the front end portion with respect to the rear end portion of the seat is adjusted.

  Further, when the movement operation knob is rotated so that the rear end portion of the movement operation knob moves up and down with the tip end portion of the tilt relay lever as a fulcrum, the slide guide recess moves with respect to the slide guide protrusion. The lifter operation handle and the lifter relay lever are rotated while being lifted. Then, when the lifter operation handle rotates around its axis, the clutch mechanism corresponding to the lifter mechanism is brought into a connected state, and the vertical position of the seat is adjusted.

  As described above, the operation direction of the moving operation knob matches the operation of adjusting the position of the sheet by each of the slide mechanism, the tilt mechanism, and the lifter mechanism, so that it is easy to understand intuitively. Can be improved.

  In the seat driving device, each of the tilt relay lever and the lifter relay lever has a tilt guide protrusion and a lifter guide protrusion at the tip, and is fixed to the housing, and the tilt guide protrusion is the lifter guide. A tilt guide recess inserted movably in the circumferential direction around the protrusion and in the front-rear direction of the seat, and the lifter guide protrusion is movable in the circumferential direction around the tilt guide protrusion and in the front-rear direction of the seat It is preferable to provide a guide plate in which a lifter guide recess is inserted.

  According to this configuration, when the movement operation knob is rotated about the tip end portion (lifter guide protrusion) of the lifter relay lever, the tilt guide protrusion is formed by the tilt guide recess. The movement in the circumferential direction around the center is guided. Therefore, the clutch mechanism corresponding to the tilt mechanism can be more reliably connected with the rotation of the tilt operation handle.

  Further, when the movement operation knob is turned about the tip (tilt guide protrusion) of the tilt relay lever, the lifter guide protrusion is centered on the tilt guide protrusion by the lifter guide recess. Circumferential movement is guided. Accordingly, the clutch mechanism corresponding to the lifter mechanism can be more reliably connected as the lifter operation handle rotates.

  When the movement operation knob is operated to move in the front-rear direction of the seat, the tilt guide protrusion and the lifter guide protrusion move the tilt guide recess and the lifter guide recess in the front-rear direction of the seat, respectively. Therefore, the movement operation of the movement operation knob in the longitudinal direction of the seat, that is, the operation of the clutch mechanism corresponding to the slide mechanism is not hindered.

  In the seat driving device, it is preferable that the guide plate is formed with a slide front / rear guide recess that allows the slide guide protrusion to move in the front / rear direction of the seat and restricts the movement in the vertical direction.

  According to this configuration, when the slide guide recess moves in the vertical direction in accordance with the turning operation of the moving operation knob using either the tilt guide protrusion or the lifter guide protrusion as a fulcrum, Accordingly, the slide guide protrusion can be restricted by the slide front / rear guide recess from moving in the vertical direction. Therefore, the swing of the slide operation handle and the malfunction of the slide mechanism due to this can be suppressed.

  When the movement operation knob is operated to move in the front-rear direction of the seat, the slide guide protrusion is guided by the slide front-rear guide recess to move in the front-rear direction. Therefore, the clutch mechanism corresponding to the slide mechanism can be more reliably connected as the slide operation handle rotates.

  The present invention has an effect of improving operability.

1 is a perspective view of an 8-way power seat to which an embodiment of a seat driving device is applied. The disassembled perspective view which shows the structure about the seat drive device of the embodiment. The disassembled perspective view which shows the structure about the seat drive device of the embodiment. The disassembled perspective view which shows the structure about the seat drive device of the embodiment. Sectional drawing which shows the structure about the sheet | seat drive device of the embodiment. The enlarged view of FIG. The perspective view which shows the structure about the sheet | seat drive device of the embodiment. The top view which shows the structure about the sheet | seat drive device of the embodiment. (A), (b) is a perspective view which shows a 1st cam member and a 2nd cam member. FIG. 3 is an equivalent circuit diagram illustrating an electrical configuration of the seat driving device according to the embodiment. (A), (b) is A arrow directional view of FIG. (A), (b) is a figure equivalent to FIG. 11 which shows the effect | action about the sheet | seat drive device of the embodiment. (A), (b) is a figure equivalent to FIG. 11 which shows the effect | action about the sheet | seat drive device of the embodiment. (A), (b) is a figure equivalent to FIG. 11 which shows the effect | action about the sheet | seat drive device of the embodiment.

Hereinafter, an embodiment of the seat driving device will be described. Hereinafter, the front-rear direction of the seat is referred to as “front-rear direction”.
As shown in FIG. 1, a pair of lower rails 1 that are arranged side by side in the width direction of the seat and extend in the front-rear direction are fixed to the floor of the vehicle, and an upper rail 2 is disposed in front and rear of each of the lower rails 1. It is mounted to move in the direction.

  A bracket 3 made of a plate material is erected on each of the upper rails 2. Each of the brackets 3 supports a seat 6 that forms a seating portion for an occupant via a front link 4 and a rear link 5 disposed at the front and rear portions. The seat 6 is supported by a seat cushion 7 that forms a seating surface, a seat back 8 that is tiltably (rotatably) supported at the rear end of the seat cushion 7, and an upper end of the seat back 8. A headrest 9 is provided.

  The seat 6 can be adjusted in its longitudinal position by relatively moving the lower rail 1 and the upper rail 2 on both sides, and can be adjusted in its vertical position by raising and lowering the front link 4 and the rear link 5 on both sides. is there. Further, the seat 6 can adjust the inclination angle of the front portion with respect to the rear portion of the seat cushion 7 and can adjust the inclination angle of the seat back 8 with respect to the seat cushion 7. Thereby, the seated person of the said sheet | seat 6 can adjust the position of a line of sight according to the physique, for example.

  A driving device 10 is attached to a side portion of one side of the seat cushion 7 (right side toward the front of the seat). As shown in FIG. 2, the drive device 10 includes a rotary motor 11 made of, for example, a brush motor, and a rotary shaft 11a whose axis extends substantially in the sheet width direction via an input torque cable 12 coaxial with the rotary shaft 11a. Drive coupled.

  Specifically, the drive device 10 includes a pair of main body cases 16 and 17 that are divided into two in the axial direction of the rotation shaft 11a. The main body cases 16 and 17 are fastened by four screws 19 that pass through these four corners in parallel with the axial direction of the rotary shaft 11a.

  The main body case 16 on the side of the rotary motor 11 is provided with a substantially cylindrical holding portion 16a that is concentric with the input torque cable 12 (rotating shaft 11a). An annular bearing 21 is fitted into the holding portion 16a, and a bottomed substantially cylindrical plug PL is screwed. A base end portion of a worm 22 disposed coaxially with the input torque cable 12 is pivotally supported on the bearing 21. The worm 22 is connected to the input torque cable 12 inserted through the plug PL at its base end portion so as to rotate integrally. The tip of the worm 22 is pivotally supported by the main body case 17 on the side away from the rotary motor 11.

  A pair of worm wheels 23, 24 whose axes extend in the front-rear direction on the upper and lower sides of the worm 22 are disposed in the main body cases 16, 17. The worm wheels 23 and 24 mesh with the worm 22 at different twist positions, and are set to a reduction ratio of 1 or more equivalent to each other.

  As shown in FIGS. 7 and 8, one worm wheel 23 has a gear portion 25 that meshes with the worm 22 on the upper side of the worm 22, and protrudes from the rear and front sides of the gear portion 25 so as to protrude from the main body case. It has a pair of shaft parts 26 pivotally supported by 16 and 17, and also has a pair of fitting parts 27 projected from the rear and front sides of both shaft parts 26, respectively. The outer shape of each fitting portion 27 has a substantially three-blade shape in which a cylindrical shape and three circular arc column shapes extending radially from the cylindrical shape at equal angular intervals are combined. The same applies to the other worm wheel 24, and its gear portion 25 meshes with the lower worm 22.

  Further, as shown in FIG. 2, the main body cases 16 and 17 are arranged so that the lifter shaft 31L and the tilt shaft 31T are symmetrical with each other coaxially with the worm wheel 23 on the rear side and the front side of the worm wheel 23. Each is pivotally supported. The lifter shaft 31L is linked to a lifter mechanism M1 that adjusts the vertical position of the seat 6, and the tilt shaft 31T is linked to a tilt mechanism M2 that adjusts the inclination angle of the front portion with respect to the rear portion of the seat cushion 7. Yes.

  Further, the recliner shaft 31 </ b> R and the slide shaft 31 </ b> S are axially supported by the body cases 16 and 17 so as to be coaxial with the worm wheel 24 on the rear side and the front side of the worm wheel 24. The recliner shaft 31R is linked to a recliner mechanism M3 that adjusts the inclination angle of the seat back 8 with respect to the seat cushion 7, and the slide shaft 31S is linked to a slide mechanism M4 that adjusts the front-rear position of the seat 6.

  Therefore, when any one of the lifter shaft 31L, the tilt shaft 31T, the recliner shaft 31R, and the slide shaft 31S rotates, the corresponding lifter mechanism M1, tilt mechanism M2, recliner mechanism M3, or slide mechanism M4 operates. The required sheet position is adjusted. That is, this embodiment is a so-called 8-way power seat that can adjust the forward and reverse seat positions in each of the lifter mechanism M1, the tilt mechanism M2, the recliner mechanism M3, and the slide mechanism M4.

  The lifter shaft 31L, the tilt shaft 31T, the recliner shaft 31R, and the slide shaft 31S have the same structure except for their arrangement. Therefore, the lifter shaft 31L is represented below. Then, the peripheral structure will be described.

  As shown in FIGS. 7 and 8, the lifter shaft 31 </ b> L has a substantially cylindrical shape, and the tip portion extending from the bearing portion of the main body cases 16, 17 to the side facing the worm wheel 23 is on the output shaft side. The fitting part 32 is formed. The lifter shaft 31 </ b> L has an outward flange 33 projecting from an axially intermediate portion adjacent to the bearing portions of the main body cases 16 and 17.

  A cylindrical member 35 is interposed between the fitting portion 27 of the worm wheel 23 and the flange 33 of the lifter shaft 31L. The cylindrical member 35 includes a cylindrical portion 36 and a flange-shaped pressing piece 37 that protrudes radially outward from the tip of the cylindrical portion 36 that faces the lifter shaft 31L. An output shaft side fitting portion 32 is fitted into the cylindrical member 35 so as to rotate integrally with the lifter shaft 31L and move in the axial direction with respect to the lifter shaft 31L. A fitting hole 38 that can be fitted to is formed. The cylindrical member 35 moves to the worm wheel 23 side in the axial direction, thereby fitting the fitting hole 38 with the fitting portion 27 so as to rotate integrally with the worm wheel 23.

  That is, the rotation of the worm wheel 23 can be transmitted to the lifter shaft 31L via the tubular member 35 by fitting the fitting portion 27 and the fitting hole 38 with the movement of the tubular member 35. 27 and the fitting hole 38 are disengaged, the transmission to the lifter shaft 31L via the cylindrical member 35 becomes impossible. As described above, the lifter mechanism M1 is operated by rotating the lifter shaft 31L. The fitting portion 27 of the worm wheel 23, the output shaft side fitting portion 32 of the lifter shaft 31L, and the cylindrical member 35 constitute a clutch mechanism that selectively connects the worm wheel 23 and the lifter shaft 31L.

  The output shaft side fitting portion 32 of the lifter shaft 31 </ b> L is inserted through a compression spring 39 formed of a coil spring interposed between the cylindrical member 35 and the flange 33 on the inner peripheral side of the pressing piece 37. The cylindrical member 35 is always attached to the side where the fitting hole 38 is fitted to the fitting portion 27 of the worm wheel 23 by the compression spring 39, that is, the side where the rotation of the worm wheel 23 can be transmitted to the lifter shaft 31L. It is energized. In other words, in a state in which the rotation of the worm wheel 23 cannot be transmitted to the lifter shaft 31L, the tubular member 35 is located on the side where the fitting portion 27 and the fitting hole 38 are disengaged against the urging force of the compression spring 39. Will be moving.

  Similar clutch mechanisms for selectively connecting the worm wheel 23 and the tilt shaft 31T, the worm wheel 24 and the recliner shaft 31R, and the worm wheel 24 and the slide shaft 31S are also configured.

  The cylindrical portion 36 of each cylindrical member 35 is loosely inserted into the mediating member 40 supported by the main body case 16. That is, as shown in FIGS. 5 and 6, the main body case 16 extends in the vertical direction (direction perpendicular to the drawings) between the pressing pieces 37 of the adjacent cylindrical members 35 and the worm wheel 23 (24). A substantially semicircular groove-like bearing groove 16b is formed.

  On the other hand, the mediating member 40 has a substantially dominant-arc-shaped shaft portion 41 that is pivotally supported by the bearing groove 16b, and has a substantially rectangular frame shape that crosses the tubular portion 36 of the tubular member 35 in a direction substantially orthogonal to the axial direction. A main body 42 is provided. A cylindrical portion 36 is loosely inserted into the mediating member 40 in a substantially circular insertion hole 42 a formed in the main body portion 42. Therefore, the mediating member 40 can rotate within a certain range around the bearing groove 16 b without being obstructed by the cylindrical portion 36. The circumferential direction in the rotation range is along the moving direction that matches the axial direction of the cylindrical member 35.

  Then, as shown on the left side in FIG. 6, when the main body 42 of the mediating member 40 spreads along the pressing piece 37 of the cylindrical member 35, the cylindrical member 35 is urged by the compression spring 39 to be fitted therein. The hole 38 is fitted with the fitting part 27 of the worm wheel 23 (24). On the other hand, as shown on the right side in FIG. 6, when the main body portion 42 of the mediating member 40 rotates about the shaft portion 41 in a direction away from the worm wheel 23 (24), the pressing piece 37 is pressed by the main body portion 42. The cylindrical member 35 moves in the axial direction against the urging force of the compression spring 39, and the fitting hole 38 is removed from the fitting portion 27 of the worm wheel 23 (24).

  As shown in FIG. 3, the main body case 17 has a pair of support shaft portions 17a and 17b arranged in parallel in the front-rear direction on the opposite side of the main body case 16 in parallel with the axial direction of the worm 22 (rotating shaft 11a). It protrudes toward you. Further, the main body case 17 is provided with substantially circular columnar guide portions 17c and 17d concentrically with the support shaft portion 17a on the upper and lower sides thereof, and concentrically with the support shaft portion 17b on the upper and lower sides thereof. Substantially arc column-shaped guide portions 17e and 17f are projected. The main body case 17 is provided with a switch cam support shaft portion 17 g that is concentric with the worm 22 and faces away from the main body case 16. The center of the switch cam support shaft portion 17g is disposed at the center between the support shaft portions 17a and 17b.

  Further, the body case 17 is formed with substantially circular bearing holes 17h on the upper side and the lower side between the support shaft portion 17a and the switch cam support shaft portion 17g. Also, similar bearing holes 17h are formed on the upper and lower sides between the support shaft portion 17b and the switch cam support shaft portion 17g, respectively. A pair of first cam members 51 are pivotally supported in the upper bearing holes 17h, and a pair of second cam members 52 are pivotally supported in the lower bearing holes 17h. .

  As shown in FIG. 9A, the first cam member 51 has a substantially cylindrical large-diameter shaft portion 51a that is pivotally supported by the bearing hole 17h, and substantially protrudes into the main body case 17 from the bearing hole 17h. It has an egg-shaped cam portion 51b, and further has a flange portion 51c that protrudes from the bearing hole 17h to the outside of the main body case 17 and slidably contacts the outer periphery of the bearing hole 17h. The first cam member 51 has a gear portion 51d disposed outside the main body case 17 adjacent to the flange portion 51c, and is disposed further outside the main body case 17 adjacent to the gear portion 51d. It has a cylindrical portion 51e, and further has a substantially cylindrical small-diameter shaft portion 51f having a diameter smaller than that of the cylindrical portion 51e.

  As shown in FIGS. 7 and 8, the first cam member 51 on the lifter shaft 31 </ b> L side contacts or is close to the outer peripheral surface of the tubular portion 36 of the tubular member 35 in the cam portion 51 b and is separated from the shaft portion 41. It arrange | positions so that contact | abutting to the front-end | tip part 43 of the mediation member 40 of the side is possible. That is, the first cam member 51 is arranged so that the pressing piece 37 of the cylindrical member 35 can be pressed via the mediating member 40 in the cam portion 51b. Then, the rotational position in which the longitudinal direction of the cam portion 51b coincides with the axial direction of the cylindrical member 35 or the like, that is, the rotational position at which the cylindrical member 35 is most separated from the worm wheel 23 (hereinafter referred to as the "neutral position" of the first cam member 51). The fitting hole 38 of the cylindrical member 35 is removed from the fitting portion 27 of the worm wheel 23 against the urging force of the compression spring 39.

  Further, as shown on the left side in FIG. 6, the first cam member 51 is a cylindrical member that is urged by the compression spring 39 when the longitudinal direction of the cam portion 51 b deviates from the axial direction of the cylindrical member 35 or the like as it rotates. The cylinder member 35 is allowed to move so that the fitting hole 38 of the 35 fits with the fitting part 27 of the worm wheel 23. On the other hand, the 1st cam member 51 resists the urging | biasing force of the compression spring 39 by pressing the press piece 37 of the cylinder member 35 via the mediation member 40 by the cam part 51b with rotation to a neutral position. The cylinder member 35 is moved to remove the fitting hole 38 of the cylinder member 35 from the fitting portion 27 of the worm wheel 23. The operation of the first cam member 51 on the tilt shaft 31T side is the same.

  On the other hand, as shown in FIG. 9B, the second cam member 52 has a substantially cylindrical large-diameter shaft portion 52a that is pivotally supported by the bearing hole 17h, and projects into the main body case 17 from the bearing hole 17h. And a flange portion 52c that protrudes from the bearing hole 17h to the outside of the main body case 17 and slidably contacts the outer peripheral edge of the bearing hole 17h. Further, the second cam member 52 has a cylindrical portion 52d disposed outside the main body case 17 adjacent to the flange portion 52c, and is disposed further outside the main body case 17 adjacent to the cylindrical portion 52d. It has a gear portion 52e, and further has a substantially cylindrical small-diameter shaft portion 52f having a diameter smaller than that of the cylindrical portion 52d. That is, the first and second cam members 51 and 52 have the same shape except that the gear portions 51d and 52e and the cylindrical portions 51e and 52d are arranged to be staggered in the axial direction. ing.

  The second cam member 52 on the recliner shaft 31R side is in contact with or close to the outer peripheral surface of the cylindrical portion 36 of the cylindrical member 35 in the cam portion 52b, and the distal end portion of the intermediate member 40 on the side separated from the shaft portion 41. 43 is arranged so as to be able to come into contact with 43. That is, the second cam member 52 is disposed so that the pressing piece 37 of the cylindrical member 35 can be pressed via the mediating member 40 in the cam portion 52b. Then, the rotational position where the longitudinal direction of the cam portion 52b coincides with the axial direction of the cylindrical member 35 or the like, that is, the rotational position where the cylindrical member 35 is most separated from the worm wheel 24 (hereinafter referred to as the “neutral position” of the second cam member 52). The fitting hole 38 of the cylindrical member 35 is removed from the fitting portion 27 of the worm wheel 24 against the urging force of the compression spring 39.

  Further, when the second cam member 52 rotates and the longitudinal direction of the cam portion 52b deviates from the axial direction of the cylindrical member 35 or the like, the fitting hole 38 of the cylindrical member 35 urged by the compression spring 39 forms the worm wheel. The cylinder member 35 is allowed to move so as to be fitted to the 24 fitting portions 27. On the other hand, the second cam member 52 resists the urging force of the compression spring 39 by pressing the pressing piece 37 of the cylindrical member 35 via the mediating member 40 by the cam portion 52b as the second cam member 52 rotates to the neutral position. The cylinder member 35 is moved to remove the fitting hole 38 of the cylinder member 35 from the fitting portion 27 of the worm wheel 24. The operation of the second cam member 52 on the slide shaft 31S side is the same.

  As shown in FIG. 3, a lifter operation handle 53L is pivotally supported at the base end of the support shaft 17a. The lifter operating handle 53L includes a gear portion 54L that meshes with the gear portion 51d of the first cam member 51 and runs idle in the position of the columnar portion 52d of the second cam member 52. Accordingly, for example, when the lifter operation handle 53L is rotated, the first cam member 51 (cam portion 51b) is rotated by the rotation transmission between the gear portions 54L and 51d. Thereby, the cylindrical member 35 moves to an axial direction in the above-mentioned aspect.

  A torsion spring 55 is wound around the support shaft portion 17a on the inner peripheral side of the lifter operation handle 53L. The base portions of the hook portions 55a at both ends of the torsion spring 55 come into contact with the stopper portions of the lifter operation handle 53L and are prevented from rotating, and the tip portions of the hook portions 55a are positioned by the guide portions 17c and 17d. The lifter operation handle 53L is held by a torsion spring 55 at a predetermined initial position extending rearward of the support shaft portion 17a. At this time, the first cam member 51 that rotates integrally with the lifter operation handle 53L is set to be disposed at the neutral position. The biasing force of the torsion spring 55 that holds the lifter operation handle 53L in the initial position moves the tubular member 35 so that the fitting hole 38 of the tubular member 35 is fitted with the fitting portion 27 of the worm wheel 23. It is set larger than the urging force of the compression spring 39.

  Accordingly, normally, the lifter operation handle 53L is held at the initial position, and accordingly, the first cam member 51 is disposed at the neutral position. That is, normally, the rotation transmission between the worm wheel 23 and the lifter shaft 31L via the cylindrical member 35 is held in a state incapable of being transmitted. When the lifter operation handle 53L is turned against the urging force of the torsion spring 55, the first cam member 51 is released from the neutral position due to the turning of the first cam member 51, and the compression spring 39 is rotated. Due to the urging force, the cylindrical member 35 moves so that the fitting hole 38 of the cylindrical member 35 is fitted to the fitting portion 27 of the worm wheel 23. Thereby, the rotation of the worm wheel 23 can be transmitted to the lifter shaft 31L via the cylindrical member 35.

  A recliner operation handle 53R is pivotally supported at the tip of the support shaft 17a. The recliner operation handle 53 </ b> R has a gear portion 54 </ b> R that meshes with the gear portion 52 e of the second cam member 52 and idles at the position of the columnar portion 51 e of the first cam member 51. Therefore, for example, when the recliner operation handle 53R is rotated, the second cam member 52 (cam portion 52b) is rotated by the rotation transmission between the gear portions 54R and 52e. Thereby, the cylindrical member 35 moves to an axial direction in the above-mentioned aspect.

  A torsion spring 56 is wound around the support shaft portion 17a on the inner peripheral side of the recliner operation handle 53R. The base portions of the hook portions 56a at both ends of the torsion spring 56 come into contact with the stopper portions of the recliner operation handle 53R and are prevented from rotating, and the tip portions of the hook portions 56a are positioned by the guide portions 17c and 17d. The recliner operation handle 53R is held by a torsion spring 56 at a predetermined initial position extending above the support shaft portion 17a. At this time, the second cam member 52 that rotates integrally with the recliner operation handle 53R is set to be disposed at the neutral position. The biasing force of the torsion spring 56 that holds the recliner operation handle 53R in the initial position moves the tubular member 35 so that the fitting hole 38 of the tubular member 35 is fitted with the fitting portion 27 of the worm wheel 24. It is set larger than the urging force of the compression spring 39.

  Therefore, normally, the recliner operation handle 53R is held at the initial position, and accordingly, the second cam member 52 is disposed at the neutral position. That is, normally, the rotation transmission between the worm wheel 24 and the recliner shaft 31 </ b> R via the cylindrical member 35 is held in a state incapable of being transmitted. When the recliner operation handle 53R is turned against the urging force of the torsion spring 56, the second cam member 52 is released from the neutral position by the rotation of the second cam member 52, and the compression spring 39 is rotated. Due to this urging force, the cylindrical member 35 moves so that the fitting hole 38 of the cylindrical member 35 is fitted to the fitting portion 27 of the worm wheel 24. Thereby, the rotation of the worm wheel 24 can be transmitted to the recliner shaft 31 </ b> R via the cylindrical member 35.

  On the other hand, a tilt operation handle 53T as a tilt operation handle is pivotally supported at the base end portion of the support shaft portion 17b. The tilt operation handle 53T has a gear portion 54T that meshes with the gear portion 51d of the first cam member 51 and runs idle in the position of the columnar portion 52d of the second cam member 52. The operation of the tilt operation handle 53T is the same as the operation of the lifter operation handle 53L. That is, normally, rotation transmission between the worm wheel 23 and the tilting shaft 31T via the cylindrical member 35 is held in an impossible state. When the tilt operation handle 53T is rotated against the urging force of the torsion spring 55, the first cam member 51 is released from the neutral position by the rotation of the first cam member 51, and the compression spring 39 is rotated. The cylindrical member 35 moves so that the fitting hole 38 of the cylindrical member 35 is fitted into the fitting portion 27 of the worm wheel 23 by the urging force. As a result, the rotation of the worm wheel 23 can be transmitted to the tilting shaft 31T via the cylindrical member 35.

  Further, a slide operation handle 53S as a slide operation handle is pivotally supported at the distal end portion of the support shaft portion 17b. The sliding operation handle 53S has a gear portion 54S that meshes with the gear portion 52e of the second cam member 52 and runs idle in the position of the columnar portion 51e of the first cam member 51. The operation of the slide operation handle 53S is the same as the operation of the recliner operation handle 53R. That is, normally, the rotation transmission between the worm wheel 24 and the slide shaft 31S via the cylindrical member 35 is held in a state incapable of being transmitted. When the sliding operation handle 53S is rotated against the urging force of the torsion spring 56, the second cam member 52 is moved from the neutral position by the rotation of the second cam member 52, and the compression spring 39 is rotated. Due to this urging force, the cylindrical member 35 moves so that the fitting hole 38 of the cylindrical member 35 is fitted to the fitting portion 27 of the worm wheel 24. Thereby, the rotation of the worm wheel 24 can be transmitted to the sliding shaft 31S via the cylindrical member 35.

  As shown in FIG. 3, the switch cam support shaft portion 17g includes a plurality of substantially chipped gear lifter switch cam members 61L, a tilt switch cam member 61T, and a recliner in order from the proximal end to the distal end. A switch cam member 61R and a slide switch cam member 61S are pivotally supported. These switch cam members 61L, 61T, 61R, and 61S mesh with the gear portions 54L, 54T, 54R, and 54S of the operation handles 53L, 53T, 53R, and 53S, respectively. Accordingly, when any of the operation handles 53L, 53T, 53R, 53S is rotated, the corresponding switch cam members 61L, 61T, 61R, 61S are rotated.

  As shown in FIG. 4, the drive device 10 includes a cover 18 that forms a casing together with main body cases 16 and 17. The cover 18 is fastened to the main body case 17 by tightening two screws 20 penetrating in parallel to the axial direction of the rotary shaft 11a in the state in which the main body case 17 is covered from the outside to the both support shaft portions 17a and 17b. Has been. Thereby, the operation handles 53L, 53T, 53R, 53S are positioned in the axial direction. At this time, the switch cam members 61L, 61T, 61R, and 61S are positioned in the axial direction by fitting the tip of the switch cam support shaft portion 17g to the cover 18. Further, each of the first cam member 51 and the second cam member 52 is positioned in the axial direction by the small-diameter shaft portions 51f and 52f being pivotally supported by the cover 18.

  The cover 18 supports a switch lever 70 that is rotatable around axes extending in parallel with the axes below the switch cam members 61L, 61T, 61R, 61S. The switch lever 70 has a symmetrical shape and can be engaged with all the switch cam members 61L, 61T, 61R, 61S. A return spring 77 made of, for example, a torsion spring is wound around the center of the switch lever 70. The switch lever 70 is released from all the switch cam members 61L, 61T, 61R, 61S when all the operation handles 53L, 53T, 53R, 53S are in the corresponding initial positions. At this time, the switch lever 70 is held at a predetermined initial rotation position (neutral position) by being biased by the return spring 77. The switch lever 70 engages and rotates when the corresponding switch cam member 61L, 61T, 61R, 61S rotates as one of the operation handles 53L, 53T, 53R, 53S rotates. .

  As shown in FIG. 3, a support frame 80 is disposed below the switch lever 70. The support frame 80 has a pair of support pieces 80a and 80b that are opposed to each other in the front-rear direction as it goes upward from the lower end portion, and has a substantially V shape, and is fastened to the cover 18 at the lower end portion. .

  A first switch structure 86 and a second switch structure 87 are supported on both support pieces 80a and 80b, respectively. Each of the first switch structure 86 and the second switch structure 87 includes a button (not shown) that can be engaged with the switch lever 70. For example, when the switch lever 70 rotates in the clockwise direction in the drawing, the button of the first switch structure 86 is pressed on the switch lever 70 accordingly. On the contrary, when the switch lever 70 is rotated counterclockwise in the drawing, the button of the second switch structure 87 is pressed on the switch lever 70 accordingly.

  As shown in FIG. 10, each of the first switch structure 86 and the second switch structure 87 is electrically connected to the contacts CH1 and CH2 electrically connected to the high potential + V of the DC power source and to the low potential GND. It includes an electric circuit composed of connected contacts CL1 and CL2 and movable terminals MT1 and MT2 connected to different terminals of the rotary motor 11. Both the movable terminals MT1, MT2 are interlocked with the buttons of the first and second switch structures 86, 87, respectively, and are usually electrically connected to the contacts CL1, CL2 on the low potential GND side. Both the movable terminals MT1 and MT2 are electrically connected to the high potential + V side contacts CH1 and CH2 by pressing the buttons of the first and second switch structures 86 and 87, respectively. Accordingly, when the switch lever 70 is rotated clockwise in accordance with the rotation operation of any one of the operation handles 53L, 53T, 53R, 53S, the movable terminal MT1 of the first switch structure 86 that is pressed down is raised. The rotary motor 11 is energized with one polarity by being electrically connected to the contact CH1 on the potential + V side. On the other hand, when the switch lever 70 rotates counterclockwise, the movable terminal MT2 of the second switch structure 87 where the button is pressed is electrically connected to the contact CH2 on the high potential + V side. The rotary motor 11 is energized with polarity.

  That is, the first switch structure 86 and the second switch structure 87 energize the rotary motor 11 with the polarity according to the operation direction in accordance with the rotation operation of any one of the operation handles 53L, 53T, 53R, 53S. Includes switch. In other words, the switch related to the energization of the rotary motor 11 is constituted by an electric circuit of the first switch structure 86 and the second switch structure 87 which are independent of each other in correspondence with both polarities.

  As shown in FIGS. 4 and 11 (a) and 11 (b), a substantially groove-like connecting portion 57L projects outward from the tip of the lifter operation handle 53L substantially parallel to the axis thereof. Yes. The connecting portion 57L reaches the cover 18 and is disposed adjacent to the rear thereof, and comes into sliding contact with the cover 18 as the lifter operation handle 53L rotates. And the front-end | tip part (rear end part) of the substantially rod-shaped interlocking lever 99 extended in the front-back direction on the outer side of the cover 18 is connected with the connection part 57L. The central portion of the interlocking lever 99 in the longitudinal direction pivotally supports the head portion of the screw 20 fastened to the support shaft portion 17a. Therefore, the interlocking lever 99 rotates integrally with the lifter operation handle 53L substantially around the support shaft portion 17a. The lifter operation handle 53L and the interlocking lever 99 constitute a lifter operation handle.

  Similarly, a substantially groove-shaped connecting portion 57T protrudes outward from the distal end portion of the tilt operation handle 53T substantially parallel to the axis. The connecting portion 57T reaches the cover 18 and is disposed adjacent to the front thereof, and comes into sliding contact with the cover 18 as the tilt operation handle 53T rotates.

  The recliner operation handle 53R has a substantially crank-shaped lever protrusion 59R protruding upward and outward. The upper end portion of the lever protruding piece 59R reaches the cover 18 and is disposed adjacent to the upper portion thereof, and a recliner operation knob 105 having a substantially backrest shape is fixed thereto.

  Similarly, the sliding operation handle 53S is provided with a substantially crank-shaped lever protruding piece 59S protruding upward and outward. The upper end portion of the lever projecting piece 59S reaches the cover 18 and is adjacently disposed above it. The lever protrusion piece 59S is provided with a slide guide protrusion 60S that extends through the upper end parallel to the axis of the lever protrusion piece 59S.

  The front end (front end) of the interlocking lever 99 is rotatably connected to the front end (lower end) of a substantially rod-shaped lifter relay lever 58L extending in the vertical direction. The lifter relay lever 58L is provided with a lifter guide protrusion 60L that extends through the tip (upper end) in parallel with the axis thereof. The separation distance from the axis of the lifter relay lever 58L to the center line of the lifter guide protrusion 60L is set equal to the separation distance from the axis of the slide operation handle 53S to the center line of the slide guide protrusion 60S.

  A distal end portion (lower end portion) of a substantially rod-shaped tilt relay lever 58T extending in the vertical direction is rotatably connected to the connecting portion 57T of the tilt operation handle 53T. The tilt relay lever 58T is provided with a tilt guide protrusion 60T that passes through the tip (upper end) parallel to the axis thereof. The separation distance from the axis of the tilt relay lever 58T to the center line of the tilt guide protrusion 60T is also set equal to the separation distance from the axis of the slide operation handle 53S to the center line of the slide guide protrusion 60S.

  The guide protrusions 60L, 60T, 60S are connected to a substantially trapezoidal movement operation knob 100 extending in the front-rear direction. That is, the lifter guide protrusion 60L and the tilt guide protrusion 60T are rotatably supported by the rear end portion and the front end portion of the movement operation knob 100, respectively. In addition, a substantially drum-shaped slide guide recess 101S that is recessed outward and communicates in the vertical direction is formed at the center of the movement operation knob 100 in the front-rear direction, and the slide guide protrusion 101S is formed in the slide guide recess 101S. 60S is arranged.

  When the lifter operation handle 53L and the tilt operation handle 53T are in the corresponding initial positions, the lifter relay lever 58L and the tilt relay lever 58T are connected to the moving operation knob 100 in a posture in which the lifter relay lever 58L and the tilt relay lever 58T stand up and down in parallel with each other. ing. When the slide operation handle 53S is in the corresponding initial position, the slide guide protrusion 60S is disposed at the center in the vertical direction of the slide guide recess 101S, and the lever protrusion 59S includes the lifter relay lever 58L and the like. Stands up and down in parallel. In this state, the front end of the movement operation knob 100 is lifted and lowered by using the lifter guide protrusion 60L as a fulcrum, or the rear end of the movement operation knob 100 is lifted and lowered by using the tilt guide protrusion 60T as a fulcrum. In addition, the slide guide recess 101S is movable with respect to the slide guide protrusion 60S without interfering with the slide guide protrusion 60S.

  A guide plate 90 made of, for example, a metal plate, which extends over substantially the entire length in the front-rear direction, is fastened to the upper end portion of the main body case 17. The guide plate 90 is bent in a substantially crank shape upward and outward, and its upper end reaches the upper end of each of the lever projecting piece 59S, the lifter relay lever 58L, and the tilt relay lever 58T. Adjacent inside.

  The guide plate 90 is formed with a substantially crown-shaped guide hole 91 through which the guide protrusions 60L, 60T, 60S are inserted in the thickness direction. The guide hole 91 is a circumferential lifter guide substantially along the front-rear direction centering on the axis on the interlocking lever 99 side of the lifter relay lever 58L in a state where all of the operation handles 53L, 53T, 53S are in the corresponding initial positions. A lifter front / rear guide hole 92L that allows the protrusion 60L to move is provided. Further, in this state, the guide hole 91 permits the movement of the circumferential slide guide protrusion 60S along the substantially front-rear direction centered on the axis of the slide operation handle 53S and restricts the vertical movement. A slide front / rear guide hole 92S is provided as a guide recess. Further, the guide hole 91 is a tilt front / rear guide hole that permits the movement of the tilt guide projection 60T in the circumferential direction along the substantially front / rear direction centering on the axis of the tilt operation lever 53T side of the tilt relay lever 58T in this state. 92T.

  In addition, the guide hole 91 is formed in a circumferential direction substantially along the vertical direction with the tilt guide protrusion 60T of the lifter guide protrusion 60L as a fulcrum in a state where all of the operation handles 53L, 53T, 53S are in the corresponding initial positions. A lifter upper and lower guide hole 93L that allows movement is provided. The lifter up / down guide hole 93L constitutes a lifter guide recess together with the lifter front / rear guide hole 92L. In addition, the guide hole 91 has a tilt vertical guide hole 93T that allows movement in the circumferential direction along a substantially vertical direction with the lifter guide protrusion 60L of the tilt guide protrusion 60T as a fulcrum in this state. The tilt up / down guide hole 93T constitutes a tilt guide recess together with the tilt front / rear guide hole 92T.

The drive device 10 is basically covered with an appropriate decorative member (not shown) in a state where only the movement operation knob 100 and the recliner operation knob 105 are exposed.
Next, the operation of this embodiment will be described. The following operation starts from a state in which all of the operation handles 53L, 53T, 53S are in the corresponding initial positions. Accordingly, the rotation of the worm wheel 23 cannot be transmitted to the lifter shaft 31L and the tilt shaft 31T, and the rotation of the worm wheel 24 cannot be transmitted to the recliner shaft 31R and the slide shaft 31S. 11 is disconnected from the DC power source via the first and second switch structures 86 and 87.

  As shown in FIG. 12A, when the movement operation knob 100 is rotated so that the rear end portion of the movement operation knob 100 rises with the tilt guide protrusion 60T as a fulcrum, the slide guide recess 101S is moved into the slide guide protrusion 101S. The lifter guide protrusion 60L moves upward while moving upward with respect to the portion 60S. At this time, the upward and downward movement of the slide guide protrusion 60S is restricted by the slide front / rear guide hole 92S of the guide plate 90, and the upward movement of the lifter guide protrusion 60L is guided by the lifter vertical guide hole 93L. In particular, when the lifter guide protrusion 60L enters above the lifter front / rear guide hole 92L, movement of the lifter guide protrusion 60L in the front-rear direction is restricted. Accordingly, the lifter relay lever 58L and the interlocking lever 99 (and the lifter operation handle 53L) rotate. That is, the movement operation knob 100, the lifter relay lever 58L, the interlocking lever 99, and the like constitute a four-bar rotation chain in which the axis centers of the tilt guide protrusion 60T and the lifter operation handle 53L are fixed ends. At this time, the lifter operating handle 53L rotates together with the interlocking lever 99 counterclockwise in the figure from the corresponding initial position, so that the rotation of the worm wheel 23 is performed via the corresponding cylindrical member 35 (clutch mechanism) as described above. Can be transmitted to the lifter shaft 31L. At the same time, as the lifter switch cam member 61L meshes with the lifter operation handle 53L, the switch lever 70 pressed by the lifter switch cam member 61L rotates, so that the rotation motor 11 and The DC power supply is connected with a reverse polarity, and the rotary motor 11 rotates in the corresponding direction.

  When the rotary motor 11 rotates, the rotation is transmitted to the lifter shaft 31L via the input torque cable 12, the worm 22, the worm wheel 23, and the cylindrical member 35. Then, the lifter mechanism M1 operates so that the seat 6 is raised by the rotation of the lifter shaft 31L.

  On the other hand, as shown in FIG. 12B, when the movement operation knob 100 is rotated so that the rear end portion of the movement operation knob 100 is lowered with the tilt guide protrusion 60T as a fulcrum, the slide guide recess 101S is slid. While moving downward with respect to the guide protrusion 60S, the lifter guide protrusion 60L moves downward. At this time, the downward movement of the slide guide protrusion 60S is regulated by the slide front / rear guide hole 92S of the guide plate 90, and the downward movement of the lifter guide protrusion 60L is guided by the lifter vertical guide hole 93L. Particularly, when the lifter guide protrusion 60L enters below the lifter front / rear guide hole 92L, the movement of the lifter guide protrusion 60L in the front-rear direction is restricted. Accordingly, the lifter operation handle 53L rotates together with the interlocking lever 99 in the illustrated clockwise direction from the corresponding initial position in accordance with the above, whereby the rotation of the worm wheel 23 is performed via the corresponding cylindrical member 35 (clutch mechanism). Can be transmitted to the lifter shaft 31L. At the same time, the switch lever 70 pressed by the lifter switch cam member 61L is rotated in accordance with the rotation of the lifter switch cam member 61L engaged with the lifter operation handle 53L. A DC power supply is connected with a positive polarity, and the rotary motor 11 rotates in the corresponding direction.

  When the rotary motor 11 rotates, the rotation is transmitted to the lifter shaft 31L via the input torque cable 12, the worm 22, the worm wheel 23, and the cylindrical member 35. Then, the lifter mechanism M1 is operated by the rotation of the lifter shaft 31L so that the seat 6 is lowered.

  Further, as shown in FIG. 13A, when the movement operation knob 100 is rotated so that the front end portion of the movement operation knob 100 rises with the lifter guide protrusion 60L as a fulcrum, the slide guide recess 101S is moved to the slide guide. While moving upward relative to the protrusion 60S, the tilt guide protrusion 60T moves upward. At this time, the upward movement of the slide guide protrusion 60S is restricted by the slide front / rear guide hole 92S of the guide plate 90, and the upward movement of the tilt guide protrusion 60T is guided by the tilt vertical guide hole 93T. In particular, when the tilt guide protrusion 60T enters above the tilt front / rear guide hole 92T, movement of the tilt guide protrusion 60T in the front-rear direction is restricted. Accordingly, the tilt relay lever 58T and the tilt operation handle 53T are rotated. That is, the movement operation knob 100, the tilt relay lever 58T, and the tilt operation handle 53T constitute a four-bar rotation chain having the lifter guide protrusion 60L and the tilt operation handle 53T as fixed ends. At this time, the tilt operation handle 53T is rotated counterclockwise in the drawing from the corresponding initial position, so that the rotation of the worm wheel 23 is performed via the corresponding cylinder member 35 (clutch mechanism) as described above. It becomes possible to transmit to 31T. At the same time, the switch lever 70 pressed by the tilt switch cam member 61T rotates with the rotation of the tilt switch cam member 61T engaged with the tilt operation handle 53T. The DC power supply is connected with a reverse polarity, and the rotary motor 11 rotates in the corresponding direction.

  When the rotary motor 11 rotates, the rotation is transmitted to the tilt shaft 31T via the input torque cable 12, the worm 22, the worm wheel 23, and the cylindrical member 35. Then, the tilt mechanism M2 is moved so that the tilt angle of the front portion with respect to the rear portion of the seat cushion 7 is directed upward by the rotation of the tilt shaft 31T, that is, the front end portion is raised with respect to the rear end portion of the seat 6. Operate.

  On the other hand, as shown in FIG. 13B, when the movement operation knob 100 is rotated so that the front end portion of the movement operation knob 100 is lowered with the lifter guide protrusion 60L as a fulcrum, the slide guide recess 101S is moved to the slide guide. While moving downward with respect to the protrusion 60S, the tilt guide protrusion 60T moves downward. At this time, the downward movement of the slide guide protrusion 60S is regulated by the slide front / rear guide hole 92S of the guide plate 90, and the downward movement of the tilt guide protrusion 60T is guided by the tilt vertical guide hole 93T. In particular, when the tilt guide protrusion 60T enters below the tilt front / rear guide hole 92T, movement of the tilt guide protrusion 60T in the front-rear direction is restricted. Accordingly, the tilt operation handle 53T is rotated clockwise from the corresponding initial position in accordance with the above, so that the rotation of the worm wheel 23 is performed via the corresponding cylindrical member 35 (clutch mechanism). It becomes possible to transmit to 31T. At the same time, the switch lever 70 pressed by the tilt switch cam member 61T rotates with the rotation of the tilt switch cam member 61T engaged with the tilt shaft 31T. The power source is connected with positive polarity, and the rotary motor 11 rotates in the corresponding direction.

  When the rotary motor 11 rotates, the rotation is transmitted to the tilt shaft 31T via the input torque cable 12, the worm 22, the worm wheel 23, and the cylindrical member 35. Then, the tilt mechanism M2 is moved so that the tilt angle of the front portion with respect to the rear portion of the seat cushion 7 is directed downward by the rotation of the tilt shaft 31T, that is, the front end portion is lowered with respect to the rear end portion of the seat 6. Operate.

  Further, as shown in FIG. 14A, when the movement operation knob 100 is moved forward, the slide guide protrusion 60S pressed against the slide guide recess 101S moves forward. At this time, the lifter guide protrusion 60L, the tilt guide protrusion 60T, and the slide guide protrusion 60S are guided to move forward by the lifter front / rear guide hole 92L, the tilt front / rear guide hole 92T, and the slide front / rear guide hole 92S, respectively. In particular, the lifter guide protrusion 60L and the tilt guide protrusion 60T enter the front of the lifter vertical guide hole 93L and the tilt vertical guide hole 93T, respectively, so that the lifter guide protrusion 60L and the tilt guide protrusion 60T are in the vertical direction. Movement to is regulated. Accordingly, the lifter relay lever 58L, the tilt relay lever 58T, and the slide operation handle 53S rotate in the clockwise direction in the drawing. Each of the lifter relay lever 58L and the tilt relay lever 58T constitutes a so-called parallel motion mechanism using the moving operation knob 100 as an intermediate node together with the sliding operation handle 53S and the moving operation knob 100. Accordingly, the interlock lever 99 (lifter operation handle 53L) and tilt operation handle 53T do not rotate by the rotation of the lifter relay lever 58L and the tilt relay lever 58T.

  As the slide operation handle 53S rotates in the clockwise direction in the drawing, the rotation of the worm wheel 24 can be transmitted to the slide shaft 31S via the corresponding cylindrical member 35 (clutch mechanism) as described above. At the same time, the switch lever 70 pressed by the slide switch cam member 61S rotates with the rotation of the slide switch cam member 61S meshing with the slide operation handle 53S. A DC power supply is connected with a positive polarity, and the rotary motor 11 rotates in the corresponding direction.

  When the rotary motor 11 rotates, the rotation is transmitted to the slide shaft 31S via the input torque cable 12, the worm 22, the worm wheel 24, and the cylindrical member 35. Then, the slide mechanism M4 operates so that the seat 6 moves forward by the rotation of the slide shaft 31S.

  On the other hand, as shown in FIG. 14B, when the movement operation knob 100 is moved backward, the slide guide protrusion 60S pressed by the slide guide recess 101S moves backward. At this time, the lifter guide protrusion 60L, the tilt guide protrusion 60T, and the slide guide protrusion 60S are guided to move backward by the lifter front / rear guide hole 92L, the tilt front / rear guide hole 92T, and the slide front / rear guide hole 92S, respectively. In particular, the lifter guide protrusion 60L and the tilt guide protrusion 60T enter the rear of the lifter vertical guide hole 93L and the tilt vertical guide hole 93T, respectively, so that the lifter guide protrusion 60L and the tilt guide protrusion 60T are in the vertical direction. Movement to is regulated. Accordingly, the lifter relay lever 58L, the tilt relay lever 58T, and the slide operation handle 53S rotate counterclockwise in the drawing. It goes without saying that the interlocking lever 99 (lifter operation handle 53L) and tilt operation handle 53T are not rotated by the rotation of the lifter relay lever 58L and the tilt relay lever 58T.

  By rotating the slide operation handle 53S counterclockwise in the drawing, the rotation of the worm wheel 24 can be transmitted to the slide shaft 31S via the corresponding cylindrical member 35 (clutch mechanism). At the same time, the switch lever 70 pressed by the slide switch cam member 61S is rotated along with the rotation of the slide switch cam member 61S engaged with the slide operation handle 53S. The DC power supply is connected with a reverse polarity, and the rotary motor 11 rotates in the corresponding direction.

  When the rotary motor 11 rotates, the rotation is transmitted to the slide shaft 31S via the input torque cable 12, the worm 22, the worm wheel 24, and the cylindrical member 35. Then, the slide mechanism M4 operates so that the seat 6 moves rearward by the rotation of the slide shaft 31S.

  When the operation force of the moving operation knob 100 is released after any of the lifter mechanism M1, the tilt mechanism M2, and the slide mechanism M4 is actuated, the corresponding operation handles 53L, 53T, 53S return to the initial positions, as described above. Rotational transmission via the cylindrical member 35 becomes impossible. At the same time, the switch cam members 61L, 61T, 61S rotate with the return of the corresponding operation handles 53L, 53T, 53S to the initial positions, and the connection between the rotary motor 11 and the power source is cut off. Thereby, rotation of the rotary motor 11 stops.

  When the recliner operation knob 105 is moved forward or backward, the recliner operation handle 53R rotates so as to tilt forward or backward. Accordingly, the rotation of the worm wheel 24 can be transmitted to the recliner shaft 31R via the corresponding cylindrical member 35 (clutch mechanism). At the same time, as the recliner switch cam member 61R meshes with the recliner operation handle 53R, the switch lever 70 pressed by the recliner switch cam member 61R rotates to rotate with a polarity corresponding to the operation direction. The motor 11 and the DC power source are connected, and the rotary motor 11 rotates in the corresponding direction. The rotation is transmitted to the recliner shaft 31R via the input torque cable 12, the worm 22, the worm wheel 24, and the cylindrical member 35, so that the recliner mechanism M3 is tilted forward or backward. Operate.

  After the operation of the recliner mechanism M3, by releasing the operation force of the recliner operation knob 105, it becomes impossible to transmit the rotation through the cylindrical member 35, and the connection between the rotary motor 11 and the power source is cut off. Nor.

As described above in detail, according to the present embodiment, the following effects can be obtained.
(1) In the present embodiment, when the movement operation knob 100 is moved in the front-rear direction of the seat, the slide guide recess 101S presses the slide guide protrusion 60S, so that the slide operation handle 53S rotates around its axis. To do. As a result, the clutch mechanism corresponding to the slide mechanism M4 is in the connected state, and the front-rear position of the seat is adjusted.

  Further, when the movement operation knob 100 is rotated so that the front end portion of the movement operation knob 100 moves up and down with the tip of the lifter relay lever 58L (lifter guide protrusion 60L) as a fulcrum, the slide guide recess 101S is moved into the slide guide protrusion 101S. The tilt operation handle 53T and the tilt relay lever 58T are rotated while being moved relative to the portion 60S. Then, when the tilt operation handle 53T is rotated about its axis, the clutch mechanism corresponding to the tilt mechanism M2 is in the connected state, and the vertical position of the front end portion with respect to the rear end portion of the seat 6 is adjusted.

  Further, when the movement operation knob 100 is rotated so that the rear end portion of the movement operation knob 100 moves up and down with the tip end portion (tilt guide protrusion 60T) of the tilt relay lever 58T as a fulcrum, the slide guide recess 101S is moved to the slide guide. The lifter operation handle 53L and the lifter relay lever 58L rotate while being moved with respect to the protrusion 60S. Then, when the lifter operation handle 53L rotates around its axis, the clutch mechanism corresponding to the lifter mechanism M1 is in the connected state, and the vertical position of the seat 6 is adjusted.

  As described above, the operation direction of the moving operation knob 100 matches the operation of the position adjustment of the seat 6 by each of the slide mechanism M4, the tilt mechanism M2, and the lifter mechanism M1, and becomes intuitively easy to understand. It can be improved further.

  (2) In the present embodiment, when the moving operation knob 100 is turned about the tip of the lifter relay lever 58L (lifter guide protrusion 60L), the tilt guide protrusion 60T is lifted by the lift guide guide 93T. Movement in the circumferential direction around the protrusion 60L is guided. Accordingly, the clutch mechanism corresponding to the tilt mechanism M2 can be more reliably connected as the tilt operation handle 53T rotates. At the same time, it is possible to more reliably energize the rotary motor 11 via the lifter switch cam member 61L and the like.

  Further, when the moving operation knob 100 is turned about the tip of the tilt relay lever 58T (tilt guide protrusion 60T), the lifter guide protrusion 60L is centered on the tilt guide protrusion 60T by the lifter vertical guide hole 93L. The movement in the circumferential direction is guided. Therefore, the clutch mechanism corresponding to the lifter mechanism M1 can be more reliably connected as the interlocking lever 99 and the lifter operation handle 53L rotate. At the same time, it is possible to more reliably energize the rotary motor 11 via the tilt switch cam member 61T and the like.

  When the moving operation knob 100 is moved in the front-rear direction, the tilt guide protrusion 60T and the lifter guide protrusion 60L move the tilt front-rear guide hole 92T and the lifter front-rear guide hole 92L in the front-rear direction, respectively. Therefore, the movement operation of the movement operation knob 100 in the front-rear direction, that is, the operation of the clutch mechanism corresponding to the slide mechanism M4 is not hindered.

  (3) In the present embodiment, when the slide guide recess 101S moves in the vertical direction along with the turning operation of the movement operation knob 100 using either one of the tilt guide protrusion 60T and the lifter guide protrusion 60L as a fulcrum. Accordingly, the slide guide protrusion 60S can be restricted from moving in the vertical direction by the slide front / rear guide hole 92S. Therefore, the swing of the slide operation handle 53S and the malfunction of the slide mechanism M4 due to the swing can be suppressed.

  When the movement operation knob 100 is moved in the front-rear direction, the slide guide protrusion 60S is guided in the front-rear direction movement by the slide front-rear guide hole 92S. Therefore, the clutch mechanism corresponding to the slide mechanism M4 can be more reliably connected with the rotation of the slide operation handle 53S. At the same time, it is possible to more reliably energize the rotary motor 11 via the slide switch cam member 61S and the like.

  (4) In the present embodiment, each of the tilt relay lever 58T and the lifter relay lever 58L, the slide operation handle 53S, and the movement operation knob 100 constitute a parallel motion mechanism that uses the movement operation knob 100 as an intermediate node. Therefore, even if the tilt guide protrusion 60T and the lifter guide protrusion 60L move in the front-rear direction as the movement operation knob 100 moves in the front-rear direction, and the tilt relay lever 58T and the lifter relay lever 58L swing, It is possible to suppress transmission of the swing to the tilt operation handle 53T and the lifter operation handle 53L.

  (5) In the present embodiment, when the recliner operation knob 105 is moved in the front-rear direction, the recliner operation handle 53R rotates (tilts) about its axis. As a result, the clutch mechanism corresponding to the recliner mechanism M3 is in the connected state, the seat back 8 is tilted forward or backward, and the tilt angle is adjusted. As described above, the operation direction of the recliner operation knob 105 matches the operation of the seat position adjustment by the recliner mechanism M3 and becomes intuitively easy to understand, so that the operability can be further improved.

  (6) In the present embodiment, any operation of the lifter mechanism M1, the tilt mechanism M2, and the slide mechanism M4 can be performed only by operating the movement operation knob 100, so that troublesomeness such as changing the operation knob can be reduced.

  (7) In this embodiment, the movement operation knob 100 and the recliner operation knob 105 that are recognized and operated by the user have the same arrangement and operation direction as those of a general power seat (for example, a by-wire type power seat). Thereby, the uncomfortable feeling of operation accompanying the replacement with the drive device 10 can be eliminated.

  (8) In the present embodiment, since the plurality of position adjusting mechanisms (M1 to M4) can be selectively operated with one rotary motor 11, the electrical configuration can be further simplified. Each of the plurality of cylindrical members 35 and the like (clutch mechanism) includes an output shaft (lifter shaft 31L, tilt shaft 31T, recliner shaft 31R, slide shaft 31S) to the corresponding position adjustment mechanism (M1 to M4). ) And the worm wheels 23 and 24 (so-called shaft coupling). For this reason, each of the plurality of cylindrical members 35 and the like (clutch mechanism) can be collectively arranged around the output shaft and the like, and the entire apparatus can be further downsized. Furthermore, the number of functions related to the position adjustment of the sheet (the number of position adjusting mechanisms) can be increased by the number of output shafts (four), so that the restriction on the number of functions can be further relaxed.

In addition, you may change the said embodiment as follows.
-In the said embodiment, the relationship between the operation direction of the movement operation knob 100 and the recliner operation knob 105, and the polarity of the rotation motor 11 energized in connection with this may be mutually reverse. In short, the position adjustment mechanism (M1 to M4) may be linked to operate in accordance with the operation direction of the movement operation knob 100 and the recliner operation knob 105.

  In the above-described embodiment, the operation handles 53L, 53T, 53R, and 53S may be pivotally supported so that they all rotate around different rotation axes, or all rotate around the same rotation axis. It may be pivotally supported.

In the embodiment, the recliner mechanism M3 and the recliner operation handle 53R related to the operation thereof may be omitted.
In the above-described embodiment, the guide plate 90 is omitted, and the tilt guide protrusion 60T and the lifter guide are moved with respect to the movement operation knob 100 when the movement operation knob 100 is moved in the front-rear direction to operate the slide mechanism M4. You may support the protrusion 60L to the movement operation knob 100 so that it can move relatively to the front-back direction. In this case, the slide operation handle 53S that moves the slide guide protrusion 60S with respect to the slide guide recess 101S of the movement operation knob 100 that holds the position in the up-down direction during the movement operation in the front-rear direction constitutes a so-called slider crank chain. .

  In the embodiment, the front and rear guide holes 92L, 92S, and 92T of the guide hole 91 may be in communication with each other or may be independent. Further, the slide front / rear guide hole 92S may be omitted, and the slide guide protrusion 60S may be moved in the front / rear direction.

In the embodiment, a non-penetrating guide recess having the same shape may be employed instead of the guide hole 91.
In the embodiment described above, the guide plate 90 (guide hole 91) may be omitted, and the tilt guide protrusion 60T and the lifter guide protrusion 60L may be moved in a random manner.

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(A) In the seat driving device,
Each of the tilt relay lever and the lifter relay lever, the slide operation handle, and the movement operation knob are configured as a parallel movement mechanism that uses the movement operation knob as an intermediate node.

  According to this configuration, the tilt guide protrusion and the lifter guide protrusion move in the front-rear direction of the sheet as the movement operation knob moves in the front-rear direction, and the tilt relay lever and the lifter relay move. Even if the lever swings, it is possible to suppress the swing from being transmitted to the tilt operation handle and the lifter operation handle.

(B) In the seat driving device,
A clutch mechanism housed in the housing and capable of selectively connecting a recliner mechanism to the rotary motor;
Around the axis extending in one direction, is pivotally connected to the housing and extends upward behind the lifter relay lever seat, and has a recliner operation knob at the tip, and the recliner mechanism is attached to the revolving mechanism. A seat drive device comprising: a recliner operation handle for bringing the corresponding clutch mechanism into a connected state.

  According to this configuration, when the recliner operation knob is operated to move in the front-rear direction of the seat, the recliner operation handle rotates (tilts) about its axis. As a result, the clutch mechanism corresponding to the recliner mechanism is in a connected state, and the seat back is tilted forward or backward, and the tilt angle is adjusted. Thus, the operation direction of the recliner operation knob matches the operation of the seat position adjustment by the recliner mechanism and becomes intuitively easy to understand, so that the operability can be further improved.

  M1 ... Lifter mechanism, M2 ... Tilt mechanism, M3 ... Recliner mechanism, M4 ... Slide mechanism, 6 ... Seat, 8 ... Seat back, 11 ... Rotation motor, 16, 17 ... Body case (housing), 27 ... Fitting part ( Clutch mechanism), 32 ... output shaft side fitting portion (clutch mechanism), 35 ... cylindrical member (clutch mechanism), 53L ... lifter operation handle (lifter operation handle), 53R ... recliner operation handle (recliner operation handle), 53S ... Slide operation handle (slide operation handle), 53T ... Tilt operation handle (tilt operation handle), 58L ... Lifter relay lever, 58T ... Tilt relay lever, 60L ... Lifter guide projection, 60S ... Slide guide projection, 60T: Tilt guide projection, 90 ... Guide plate, 91 ... Guide hole, 92L ... Front / rear lifter 92S ... Slide front / rear guide hole (slide front / rear guide recess), 92T ... Tilt front / rear guide hole (tilt guide recess), 93L ... Lifter vertical guide hole (lifter guide concave), 93T ... Tilt vertical guide Hole (tilt guide recess), 99 ... interlocking lever (lifter operation handle), 100 ... movement operation knob, 101S ... slide guide recess, 105 ... recliner operation knob.

Claims (3)

A plurality of clutch mechanisms housed in a housing and capable of selectively connecting a slide mechanism, a tilt mechanism and a lifter mechanism to a rotary motor;
Around the axis extending in one direction, is pivotally connected to the housing, extends above the seat, has a slide guide projection at the tip, and is connected to the clutch mechanism corresponding to the slide mechanism as it rotates A slide operation handle to
A tilt operation handle and a lifter operation handle that are rotatably connected to the housing around an axis extending in parallel with the one direction, and that bring the clutch mechanism corresponding to the tilt mechanism and the lifter mechanism into a connected state with the rotation. When,
A tilt relay lever and a lifter relay that are pivotally connected to the tilt operation handle and the lifter operation handle around an axis extending in parallel with the one direction, and extend upward in front of and behind the slide operation handle, respectively. Lever,
The tip ends of the tilt relay lever and the lifter relay lever are supported so as to be rotatable around an axis extending in parallel with the one direction, and the slide guide protrusions extend in the circumferential direction around each of the two tip portions. A seat driving device comprising: a moving operation knob formed with a slide guide concave portion that is inserted so as to be relatively movable and immovable in the front-rear direction of the seat. The sheet driving apparatus according to claim 1,
The tilt relay lever and the lifter relay lever each have a tilt guide protrusion and a lifter guide protrusion at the tip,
The tilt guide protrusion is fixed to the housing, and the tilt guide protrusion is movably inserted in a circumferential direction around the lifter guide protrusion and in the front-rear direction of the seat, and the lifter guide protrusion is the tilt guide protrusion. A sheet driving apparatus comprising a guide plate having a lifter guide recess inserted movably in a circumferential direction centering on the section and in a front-rear direction of the sheet. The sheet driving apparatus according to claim 2, wherein
The seat driving device, wherein the guide plate is formed with a slide front / rear guide recess for allowing the slide guide protrusion to move in the front / rear direction of the sheet and restricting the movement in the vertical direction.

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