JP2011225017A - Seat for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a seat for a vehicle in which a seat body can be lifted toward a movable frame of a sliding rail and torque can be transmitted with a simple configuration between a motor supported by either the seat body or the movable rail and a driven mechanism supported by the another of them.SOLUTION: In the seat for a vehicle, the motor 60 is supported on a seat cushion side, and a rail drive mechanism 133 is supported on upper rails 126, 128 of the sliding rail 120. One side of a link member 129 constituting a torque transmission mechanism 135 is turnably coupled to the seat cushion side, and the another side of the link member 129 is turnably coupled to the upper rail 128 side. A speed-increasing gear train is attached to the link member 129, and the torque of the motor 60 is transmitted to the rail drive mechanism 133 via the speed-increasing gear train.

Description

  The present invention relates to a vehicle seat, and in particular, includes a lifter mechanism that raises and lowers a seat cushion with respect to a movable rail of a slide rail, and either one by a motor supported by either the seat cushion or the movable rail. The present invention relates to a vehicle seat that drives a driven mechanism supported by the vehicle.

  In the power seat driving device shown in Patent Document 1 below, a front end vertical adjustment rotary shaft, a rear end vertical adjustment rotary shaft, between a pair of seat adjusters constituted by a fixed rail, a movable rail, a mechanism frame, and the like, A reclining adjustment rotary shaft and a slide adjustment rotary shaft are spanned. A movement motor is arranged at the center of these rotation shafts, and the drive motor is moved to a position where each rotation shaft can be rotated by this movement motor. As a result, the number of types of seat adjustment more than the number of motors is adjusted with a small number of motors.

Japanese Patent Laid-Open No. 11-42137

  By the way, in the vehicle seat provided with the lifter mechanism that raises and lowers the mechanism part frame (the frame of the seat body) with respect to the movable rail, the distance between the seat body and the movable rail changes. When the power seat driving device shown in Patent Document 1 is applied to such a vehicle seat, a motor (driving motor and moving motor) supported by one of the seat body and the movable rail; Since the distance between the rotating shaft supported by either one changes, it is considered that it is difficult to transmit the rotational force from the motor to the rotating shaft (driven mechanism) supported by the other.

  In consideration of the above-described facts, the present invention can move the seat body up and down relative to the movable frame of the slide rail, and supports the motor supported on either the seat body or the movable rail and on the other. An object of the present invention is to obtain a vehicle seat capable of transmitting a rotational force with a simple configuration to the driven mechanism.

  According to a first aspect of the present invention, there is provided a vehicle seat including: a slide rail that is slidably connected to a fixed rail that is fixed to a vehicle body floor, and a movable rail that is connected to a seat body; A lifter mechanism that moves up and down with respect to the movable rail, a motor supported on one of the seat body and the movable rail, and a driven that is supported on the other of the seat body and the movable rail A mechanism and a link having one side pivotally connected to the seat body side and the other side pivotally connected to the movable rail side and pivoting relative to both when the seat body is raised and lowered relative to the movable rail And a rotational force transmission mechanism that transmits the rotational force of the motor to the driven mechanism via a rotational member that is rotatably attached to the link member. To have.

  In the vehicle seat according to the first aspect, the motor is supported on one of the seat main body and the movable rail, and the driven mechanism is supported on the other. Further, one side of a link member constituting the rotational force transmission mechanism is rotatably connected to the seat body side, and the other side of the link member is rotatably connected to the movable rail side. A rotating member is attached to the link member, and the rotational force of the motor is transmitted to the driven mechanism through the rotating member.

  Here, the above-described link member rotates with respect to the seat body and the movable rail when the lifter mechanism raises and lowers the seat body with respect to the movable rail. That is, since the link member rotates to follow the change in the distance between the seat main body and the movable rail, an extendable mechanism or the like is unnecessary. Moreover, even if the link member rotates, the distance between the rotation center of the link member and the rotation member relative to the seat body, and the distance between the rotation center of the link member and the rotation member relative to the movable rail are both maintained constant. Is done. As a result, the structure for transmitting the rotational force from the motor supported on one of the seat main body and the movable frame to the rotating member, and the rotational force transmitted from the rotating member to the driven mechanism supported on the other one are transmitted. Therefore, it is possible to simplify the configuration for this. That is, for example, when a mechanism that can extend and contract and transmit a rotational force is employed, the configuration becomes complicated, but the present invention does not require such a complicated mechanism. Therefore, it is possible to transmit the rotational force with a simple configuration between the motor supported by one of the seat body and the movable rail and the driven mechanism supported by either one.

  A vehicle seat according to a second aspect of the present invention is the vehicle seat according to the first aspect, wherein the rotational force transmission mechanism has a plurality of gears as the rotating member.

  In the vehicle seat according to the second aspect, the rotational force of the motor is transmitted to the driven mechanism through a plurality of gears attached to the link member. Here, for example, if the gear train is constituted by a plurality of gears, the rotation of the motor can be increased or decreased as necessary. This is preferable because a dedicated configuration for increasing or decreasing the rotation of the motor can be omitted or simplified.

  A vehicle seat according to a third aspect of the present invention is the vehicle seat according to the second aspect, wherein the plurality of gears are arranged coaxially with a rotation axis of the link member with respect to the movable rail. The rail side gear is included.

  In the vehicle seat according to the third aspect, the plurality of gears attached to the link member include rail-side gears. Since the rail side gear is arranged coaxially with the rotation axis of the link member with respect to the movable rail, the positional relationship between the rail side gear and the movable rail is maintained even when the link member rotates with respect to the movable rail. Can be kept constant. Thereby, the configuration of the rotational force transmission mechanism can be further simplified.

  A vehicle seat according to a fourth aspect of the present invention is the vehicle seat according to the second or third aspect, wherein the plurality of gears are coaxial with a rotation axis of the link member with respect to the seat body. It is characterized in that a cushion-side gear arranged in is included.

  In the vehicle seat according to the fourth aspect, the plurality of gears attached to the link member include cushion side gears. Since the cushion side gear is arranged coaxially with the rotation axis of the link member with respect to the seat body, even if the link member rotates with respect to the seat body, the positional relationship between the cushion side gear and the seat body is maintained. Can be kept constant. Thereby, the configuration of the rotational force transmission mechanism can be further simplified.

  A vehicle seat according to a fifth aspect of the present invention is the vehicle seat according to any one of the first to fourth aspects, wherein the motor is supported by the seat body, and the driven mechanism is A rail drive mechanism is provided that slides the movable rail relative to the fixed rail by being supported by the movable rail and transmitting the rotational force of the motor.

  In the vehicle seat according to the fifth aspect, the rotational force can be transmitted with a simple configuration between the motor supported on the seat body side and the rail drive mechanism supported by the movable rail. In addition, since the motor is supported on the seat body side, it is suitable when other seat drive mechanisms (front tilt mechanism, recliner mechanism, etc.) driven by the motor are provided on the seat body side.

  A vehicle seat according to a sixth aspect of the present invention is the vehicle seat according to any one of the first to fifth aspects, wherein the driven mechanism is supported by the movable rail, and the motor is The motor is unitized together with a clutch mechanism having an output gear that rotates when the rotational force of the motor is transmitted, and is supported by the seat body, and one side of the link member is relatively rotatable about the axis of the output gear. It is connected to the clutch mechanism.

  7. The vehicle seat according to claim 6, wherein one side of the link member is united with a motor and connected to a clutch mechanism supported by the seat body, and an output gear that rotates by transmission of the rotational force of the motor. The relative rotation is possible around the axis line. As described above, since the link member is directly connected to the clutch mechanism without going through the seat body, the positioning work between the clutch mechanism (output gear) and the link member at the time of manufacturing the vehicle seat is facilitated. Can do.

  A vehicle seat according to a seventh aspect of the present invention is the vehicle seat according to any one of the first to sixth aspects, wherein the link member is a lifter link constituting the lifter mechanism. It is characterized by having.

  In the vehicle seat according to the seventh aspect, the lifter link constituting the lifter mechanism is shared as a link member constituting the rotational force transmission member. Thereby, the number of parts can be reduced, and the vehicle seat can be reduced in weight.

  As described above, in the vehicle seat according to the present invention, the seat body can be moved up and down with respect to the movable frame of the slide rail, and the motor supported on one of the seat body and the movable rail; Rotational force can be transmitted to the driven mechanism supported by either one with a simple configuration.

It is a perspective view which shows the structure of the principal part of the vehicle seat which concerns on 1st Embodiment of this invention. It is a perspective view of the state which omitted the cushion front frame in FIG. FIG. 3 is a perspective view showing the vehicle seat shown in FIG. 2 as seen from an angle different from that in FIG. 2. It is a perspective view which shows 1 motor power unit and a support bracket which are the structural members of the vehicle seat which concerns on 1st Embodiment of this invention. FIG. 5 is a perspective view showing the one motor power unit and the support bracket shown in FIG. 4 as viewed from an angle different from that in FIG. 4. FIG. 6 is a perspective view of a clutch mechanism that is a constituent member of one motor power unit shown in FIGS. 4 and 5. It is a disassembled perspective view which shows the partial structure of the clutch mechanism which is a structural member of 1 motor power unit shown by FIG.4 and FIG.5. It is a figure for demonstrating the operation method of the switch unit provided in the vehicle seat which concerns on 1st Embodiment of this invention, (A) is slide operation, (B) is front tilt operation, (C) is a lift. (D) corresponds to the recliner operation, and (E) corresponds to the lumbar operation. It is a perspective view which shows the structure of the sliding drive force transmission mechanism provided in the vehicle seat which concerns on 1st Embodiment of this invention. FIG. 10 is a perspective view showing a link member and a speed increasing gear train of a rotational force transmission mechanism constituting the sliding drive force transmission mechanism shown in FIG. 9. 9 shows a configuration of an outer side gear box that is a constituent member of the sliding drive force transmission mechanism shown in FIG. 9, (A) is a perspective view seen from the left side of the seat, and (B) is a perspective view seen from the right side of the seat. It is. 9A and 9B show a configuration of an inner side gear box that is a constituent member of the sliding drive force transmission mechanism shown in FIG. 9, wherein FIG. 9A is a perspective view seen from the right side of the seat, and FIG. It is. FIG. 3 is a perspective view illustrating a configuration of a front tilt driving force transmission mechanism provided in the vehicle seat according to the first embodiment of the present invention. (A) It is a perspective view which shows the structure of the gear box for front tilt which is a structural member of the driving force transmission mechanism for front tilt shown in FIG. 13, (B) is the gear box for front tilt shown in (A). It is a perspective view which shows the structure of the screw gearwheel which is a structural member, and a screw. It is a perspective view which shows the structure of the peripheral member containing the lifter mechanism provided in the vehicle seat which concerns on 1st Embodiment of this invention. It is a perspective view which shows the structure of the drive force transmission mechanism for lifters provided in the vehicle seat which concerns on 1st Embodiment of this invention. (A) It is a perspective view which shows the structure of the gear box for lifters which is a structural member of the drive force transmission mechanism for lifters shown by FIG. 16, (B) is a structural member of the gear box for lifters shown by (A). It is a perspective view which shows the structure of a certain screw gear and a screw. 1 is a perspective view showing a configuration of a lumbar driving force transmission mechanism provided in a vehicle seat according to a first embodiment of the present invention. It is a perspective view which shows the structure of the principal part of the driving force transmission mechanism for lumbars shown by FIG. It is a perspective view which shows the structure of the recliner driving force transmission mechanism provided in the vehicle seat which concerns on 1st Embodiment of this invention. It is a disassembled perspective view which shows the structure of the front side gearbox which is a structural member of the drive force transmission mechanism for recliners shown by FIG. FIG. 21 is an exploded perspective view showing a configuration of peripheral members including a rear gear box and a speed increasing gear train, which are components of the recliner driving force transmission mechanism shown in FIG. It is a perspective view which shows the structure of the sliding drive force transmission mechanism provided in the vehicle seat which concerns on 2nd Embodiment of this invention. FIG. 24 is a perspective view showing a link member and a speed increasing gear train of a rotational force transmission mechanism that constitutes the sliding drive force transmission mechanism shown in FIG. 23.

<First Embodiment>
Hereinafter, with reference to FIGS. 1-24, the vehicle seat 10 which concerns on 1st Embodiment of this invention is demonstrated. In each figure, the arrow FR indicates the front direction of the seat, the arrow UP indicates the upper direction of the seat, the arrow LH indicates the left direction of the seat, and the arrow RH indicates the right direction of the seat. Further, in the vehicle seat 10, the seat width direction and the seat left-right direction coincide with each other.

  In the following description, a title is assigned for each large configuration of the present embodiment. However, a main part of the present embodiment is assigned to a portion labeled (configuration of the sliding drive force transmission mechanism 50). It is described.

  As shown in FIGS. 1 to 3, the vehicle seat 10 includes a seat cushion 12 and a seat back 16 that constitute a seat body. The seat cushion 12 has a cushion frame 14 that is a skeleton member, and the seat back 16 has a back frame 18 that is a skeleton member.

  The cushion frame 14 includes a pair of left and right side frames 20, 22 extending in the front-rear direction of the seat, a front frame 24 (see FIGS. 2 and 3) that connects the front portions of the pair of side frames 20, 22, and a pair of side frames. A rear frame 26 that connects the rear portions of the side frames 20 and 22, and an auxiliary frame 27 that is disposed on the seat rear side of the front frame 24 and connects the front and rear intermediate portions of the pair of side frames 20 and 22. It consists of

  The front frame 24, the rear frame 26, and the auxiliary frame 27 are all formed of a pipe material made of a metal material or the like, and are arranged in a state where the axial direction is along the sheet width direction. The auxiliary frame 27 is formed with a smaller diameter than the front frame 24, and is disposed below the front frame 24 on the front side of the seat with respect to the center portion in the front-rear direction of the cushion frame 14.

  On the other hand, the back frame 18 includes a pair of left and right side frames 28 and 30 extending in the vertical direction of the seat, a lower frame 32 connecting lower portions of the pair of side frames 28 and 30, and upper portions of the pair of side frames 28 and 30. And an upper frame 34 for connecting the two.

  A cushion spring 35 is attached to the cushion frame 14, and a seat cushion pad (not shown) covered with an outer skin is attached to the upper side of the cushion spring 35. A back spring 37 is attached to the back frame 18, and a seat back pad (not shown) covered with a skin is attached to the front side of the back spring 37.

  The vehicle seat 10 is provided with a slide mechanism 36, a front tilt mechanism 38, a lifter mechanism 40, a lumbar mechanism 42, and a recliner mechanism 46 (all seat drive mechanisms). These seat driving mechanisms are configured to be driven by one motor power unit 48 shown in FIGS. 4 and 5, and a sliding driving force is transmitted between the one motor power unit 48 and each of the sheet driving mechanisms. Mechanism 50 (see FIG. 9), front tilt driving force transmission mechanism 52 (see FIG. 13), lifter driving force transmission mechanism 54 (see FIG. 16), lumbar driving force transmission mechanism 56 (see FIG. 18), and recliner A driving force transmission mechanism 58 (see FIG. 20) is disposed. First, the 1 motor power unit 48 will be described.

(Configuration of one motor power unit 48)
As shown in FIGS. 4 and 5, the one motor power unit 48 is a unit in which a single motor 60 having a reduction gear 59 and a clutch mechanism 62 are unitized. The clutch mechanism 62 is formed in a columnar shape as a whole, and is arranged in a state where the axial direction is along the sheet width direction. Further, the motor 60 is arranged on one end side (left side of the seat) in the axial direction of the clutch mechanism 62, and an output shaft (not shown) provided in the speed reducer 59 is arranged coaxially with the clutch mechanism 62.

  The one motor power unit 48 described above is supported by the front frame 24 and the auxiliary frame 27 (see FIGS. 2 and 3) of the cushion frame 14 via the support bracket 64. The support bracket 64 includes a plurality of plates 65A, 65B, 65C, 65D, 65E, 65F, and 65G formed of a sheet metal material or the like. These plates 65 </ b> A to 65 </ b> G are arranged side by side in the sheet width direction with the plate thickness direction of the main portion being along the sheet width direction, and are connected in the sheet width direction by long nuts 67, screws 69, and the like. Each of the plates 65A to 65G has a circular through hole coaxially formed, and the clutch mechanism 62 is assembled to the plates 65A to 65G in a state of passing through the through holes.

  The two plates 65F and 65G arranged on the left end side of the plates 65A to 65G are fastened with the front side and the front-rear direction intermediate part partially overlapped in the plate thickness direction. Further, the plate 65G disposed at the leftmost end is bent in a crank shape at the rear side and is separated from the plate 65F. A plate 65H formed of a sheet metal material or the like is fastened to the upper part of the front portion of the second plate 65F from the left. The plate 65H protrudes toward the left side of the seat.

  Further, a motor 60 is disposed on the side opposite to the clutch mechanism 62 via a plate 65G disposed at the leftmost end. The motor 60 is fastened to the plates 65F and 65G by screws 71 and 73 (see FIG. 5) penetrating through the overlapping portions of the plates 65F and 65G being screwed into the housing of the speed reducer 59.

  The above-described support bracket 64 has hook portions provided on the upper end side of the front end portions of the plates 65A to 65G and the left end side of the plate 65H hooked on the front frame 24 of the cushion frame 14, and the rear portions of the plates 65A to 65G. A locking portion provided on the end side is locked to the auxiliary frame 27. Thus, the one motor power unit 48 is supported in a suspended state by the front frame 24 and the auxiliary frame 27 via the support bracket 64.

  Next, the clutch mechanism 62 will be described in detail. As shown in FIG. 6, the clutch mechanism 62 is formed in a columnar shape as a whole, and is arranged in a state where the axial direction is along the sheet width direction, and a plurality (three in this case) arranged side by side in the sheet width direction. ) Clutch units 66, 68, and 70, and a movable shaft 72 (see FIG. 7, not shown in FIG. 6). The movable shaft 72 is disposed at the axial center of the clutch mechanism 62 in a state where the axial direction is along the seat width direction, and is urged to the right side of the seat (the cam 116 side described later) by the spring 73. The movable shaft 72 is provided with three reduced-diameter portions 72A, 72B, 72C obtained by reducing the outer diameter of the movable shaft 72. These reduced diameter portions 72A, 72B, 72C are arranged at substantially equal intervals in the axial direction of the movable shaft 72.

  On the other hand, the clutch units 66, 68 and 70 have basically the same configuration, but here, the clutch unit 68 disposed at the center will be described first. As shown in FIG. 7, the clutch unit 68 includes a pair of input shafts 74 and 76 that are arranged side by side in the sheet width direction with the axial direction being along the sheet width direction. These input shafts 74 and 76 are formed in a substantially cylindrical shape, and are rotatably supported by the plates 65C and 65D of the support bracket 64 described above. Inside the input shafts 74 and 76, the above-described movable shaft 72 penetrates so as to be relatively movable along the axial direction.

  Between the input shafts 74 and 76, a pair of annular brackets 78 and 80 and a plurality (three in this case) of pins 82 are arranged. The annular brackets 78 and 80 are formed in a substantially disk shape, and are disposed so as to be back-to-back with each other in a state where the axial direction is along the sheet width direction. Each of the annular brackets 78 and 80 has a circular through hole formed in the axial center thereof, and the movable shaft 72 passes through these through holes concentrically.

  Further, the three pins 82 are arranged at equal intervals in the circumferential direction of the movable shaft 72 with the axial direction along the seat width direction, and the central portions in the axial direction are formed in the annular brackets 78 and 80. It is fitted in the through hole. One end in the axial direction of the three pins 82 is fitted into a circular hole (not shown) formed in the end face of one input shaft 74, and the other end in the axial direction of the three pins 82 is the other input shaft 76. Is fitted in a circular hole (not shown) formed on the end face of the. Thereby, the input shafts 74 and 76 are connected through the three pins 82 so as not to be relatively rotatable, and the annular brackets 78 and 80 are supported by the input shafts 74 and 76 through the three pins 82.

  Further, a lifter drive gear 84 is attached to one input shaft 74. The lifter drive gear 84 is formed in a cylindrical shape, and is arranged in a state where the axial direction is along the sheet width direction, and a part of the input shaft 74 is fitted inside the one axial side. Thereby, the lifter drive gear 84 is rotatably supported by the input shaft 74. External teeth are formed on the outer peripheral portion on one side in the axial direction of the lifter drive gear 84, and internal teeth are formed on the inner peripheral portion on the other side in the axial direction of the lifter drive gear 84.

  A front tilt drive gear 86 is attached to the other input shaft 76. The front tilt drive gear 86 is formed in a cylindrical shape similar to the lifter drive gear 84, and is disposed in a state where the axial direction is along the sheet width direction. However, the front tilt drive gear 86 is arranged in a direction opposite to the lifter drive gear 84 (in a back-to-back state). A part of the input shaft 76 is fitted on the inner side of the front tilt drive gear 86 in the axial direction, whereby the front tilt drive gear 86 is rotatably supported by the input shaft 76. External teeth are formed on the outer peripheral portion on one side in the axial direction of the front tilt drive gear 86, and internal teeth are formed on the inner peripheral portion on the other side in the axial direction of the front tilt drive gear 86.

  A pair of pawls 88 are disposed inside the lifter drive gear 84. These pawls 88 are rotatably attached to one end side in the axial direction of two pins 82 among the three pins 82 described above. A pair of pawls 90 are arranged inside the front tilt drive gear 86. These pawls 90 are rotatably attached to the other axial end of the two pins 82 described above. These pawls 88 and 90 are urged to one side around the axis of the pin 82 by a torsion coil spring 92, and one end part thereof is in contact with the outer peripheral part of the movable shaft 72 by the contact urging force.

  Here, when the movable shaft 72 is moved in the axial direction so that one end portion of the pawl 88 faces the reduced diameter portion 72B of the movable shaft 72, the pawl 88 rotates around the pin 82 by the biasing force of the torsion coil spring 92. The other end side of the pawl 88 is engaged with the inner teeth of the lifter drive gear 84. When the input shaft 74 rotates in this state, the rotational force of the input shaft 74 is transmitted to the lifter drive gear 84 via the pin 82 and the pawl 88.

  Further, when the movable shaft 72 moves in the axial direction so that one end portion of the pawl 90 faces the reduced diameter portion 72B of the movable shaft 72, the pawl 90 rotates around the pin 82 by the biasing force of the torsion coil spring 92, The other end of the pawl 90 meshes with the inner teeth of the front tilt drive gear 86. When the input shaft 76 rotates in this state, the rotational force of the input shaft 76 is transmitted to the front tilt drive gear 86 via the pin 82 and the pawl 90.

  The clutch unit 68 configured as described above is disposed between the clutch units 66 and 70 as shown in FIG. The clutch unit 66 arranged on the right side of the clutch unit 68 has basically the same configuration as the clutch unit 68, but includes a slide drive gear 94 (output gear) instead of the lifter drive gear 84. A recliner drive gear 96 is provided instead of the front tilt drive gear 86.

  On the other hand, the clutch unit 70 disposed on the left side of the clutch unit 68 has basically the same configuration as the clutch unit 68, but includes a lumbar drive gear 98 instead of the lifter drive gear 84, and has a front tilt. A cover 100 is attached instead of the drive gear 86 (one gear is omitted). A gear similar to the front tilt drive gear 86 can be added in place of the cover 100. In the first embodiment, the slide drive gear 94, the recliner drive gear 96, the lifter drive gear 84, the front tilt drive gear 86, and the lumbar drive gear 98 are coaxially arranged in the seat width direction. .

  In the clutch units 66, 68, 70, input shafts (input shafts basically configured in the same manner as the input shafts 74, 76) arranged inside the drive gears are connected to each other so as not to rotate relative to each other. The motor 60 is connected to the output shaft of the motor 60 via a cylindrical motor connecting member 102. Accordingly, the rotational force of the motor 60 is transmitted to the input shafts, and the transmission path of the rotational force between the drive gears and the motor 60 is switched by the movement of the movable shaft 72 in the axial direction. Yes.

  Specifically, when the movable shaft 72 is moved in the axial direction and the reduced diameter portion 72B corresponding to the clutch unit 68 is opposed to the pawl 88 disposed inside the lifter drive gear 84, the contact pawl 88 is lifted. The drive gear 84 meshes with the inner teeth, and the rotational force of the motor 60 is transmitted to the lifter drive gear 84. When the reduced diameter portion 72B faces the pawl 90 disposed inside the front tilt drive gear 86, the contact pawl 90 is engaged with the inner teeth of the front tilt drive gear 86, and the rotational force of the motor 60 is increased by the front tilt. It is transmitted to the drive gear 86.

  Similarly, when the reduced diameter portion 72A corresponding to the clutch unit 66 faces a pawl (not shown) disposed inside the slide drive gear 94, the contact pawl is engaged with an internal tooth (not shown) of the slide drive gear 94, and the motor 60 Is transmitted to the slide drive gear 94. When the reduced diameter portion 72A faces a pawl (not shown) arranged inside the recliner drive gear 96, the contact pawl is engaged with an internal tooth (not shown) of the recliner drive gear 96, and the rotational force of the motor 60 is driven by the recliner drive. It is transmitted to the gear 96. Further, when the reduced diameter portion 72C of the movable shaft 72 corresponding to the clutch unit 70 faces a pawl (not shown) disposed inside the lumbar drive gear 98, the contact pawl is engaged with the inner teeth of the lumbar drive gear 98, and the motor The rotational force of 60 is transmitted to the lumbar drive gear 98.

  The above-described movable shaft 72 is configured to be moved in the axial direction by the switch unit 104 (see FIGS. 1 to 3) attached to the side frame 22 on the right side (outer side) of the cushion frame 14. The switch unit 104 includes a switch knob 106 attached to the side frame 22. The switch knob 106 includes a rotation knob 108 that is rotatable about an axis along the sheet width direction.

  The rotation of the rotary knob 108 is transmitted to the cam 116 via the gear train 112, and the cam 116 is rotated about the axis along the sheet width direction. The cam 116 is provided with an inclined surface (not shown) on the left side of the seat (1 motor power unit 48 side), and a small diameter portion 72D provided coaxially on one end side in the axial direction of the movable shaft 72 on the inclined surface. (See FIGS. 4, 5, and 7). Therefore, when the cam 116 is rotated around the axis, the inclined surface is brought into sliding contact with the tip of the small diameter portion 72D, so that the movable shaft 72 is moved in the axial direction. As a result, the seated occupant can manually move the rotary knob 108 to move the movable shaft 72 in the axial direction by the operation force, so that the seat 60 can move between the drive gears of the clutch mechanism 62 and the motor 60. The transmission path of the rotational force can be selectively switched.

  Specifically, in a state where the rotation knob 108 is disposed at the position shown in FIG. 8A, it becomes possible to transmit the rotational force between the slide drive gear 94 and the motor 60, and FIG. In the state where the rotary knob 108 is disposed at the position shown in FIG. 8, the rotational force can be transmitted between the front tilt drive gear 86 and the motor 60, and the rotary knob 108 is placed at the position shown in FIG. In the disposed state, the rotational force can be transmitted between the lifter drive gear 84 and the motor 60, and in the state where the rotation knob 108 is disposed at the position shown in FIG. 8D, the recliner drive gear 96 is provided. Rotational force can be transmitted between the lumbar drive gear 98 and the motor 60 and the rotational knob 108 is disposed at the position shown in FIG. Communication is possible.

  Further, as shown in FIGS. 1 and 2, a translation knob 110 is slidably attached to the rotary knob 108 described above. The translation knob 110 is connected to a switch (not shown), and the switch is electrically connected to the motor 60. Thus, when the translation knob 110 is slid to one side with respect to the rotation knob 108, the motor 60 rotates in the forward direction, and when the translation knob 110 is slid to the other side with respect to the rotation knob 108, the motor 60 is reversed. It has become.

  Next, the slide driving force transmission mechanism 50 that transmits the driving force from the above-described one motor power unit 48 to the slide mechanism 36 will be described.

(Configuration of slide driving force transmission mechanism 50)
As shown in FIG. 9, the slide mechanism 36 to which the slide driving force transmission mechanism 50 transmits the driving force includes a slide rail 120. The slide rail 120 is slidably attached to the pair of left and right lower frames 122 and 124 (fixed frames) fixed to the vehicle body floor portion, and the lower frames 122 and 124, and the side frame 20 of the cushion frame 14. 22 (not shown in FIG. 9), a pair of left and right upper frames 126 and 128 (movable frames) are provided, and the vehicle seat 10 can be slid in the longitudinal direction of the seat with respect to the vehicle body floor. .

  The sliding drive force transmission mechanism 50 according to the first embodiment includes the rail drive mechanism 133 that slides the above-described upper frames 126 and 128 with respect to the lower rails 122 and 124 when a rotational force is input. And a rotational force transmission mechanism 135 that transmits the rotational force of the slide drive gear 94 to the rail drive mechanism 133.

  The rotational force transmission mechanism 135 includes a link member 129 disposed between the right upper frame 128 and the clutch mechanism 62. The front end side (lower end side) of the link member 129 is rotatably connected to an outer side gear box 144 constituting the rail drive mechanism 133. The outer side gear box 144 is fixed to the upper surface of the front end portion of the upper frame 128, and the front end side of the link member 129 is rotatably connected to the front end portion of the upper frame 128 via the outer side gear box 144. Yes.

  On the other hand, a circular hole 131 is formed on the rear end side (upper end side) of the link member 129 as shown in FIG. 10. The circular hole 131 has an axial end portion ( A cylindrical connecting portion 62A (see FIG. 9) provided at the right end portion is fitted. Thus, the rear end side of the link member 129 and the clutch mechanism 62 are coupled so as to be rotatable about the axis of the clutch mechanism 62 (around the axis along the sheet width direction). That is, the rear end side of the link member 129 is rotatably connected to the cushion frame 14 via the clutch mechanism 62. In the first embodiment, the axes of the clutch mechanism 62 are the axes of the slide drive gear 94, the recliner drive gear 96, the lifter drive gear 84, the front tilt drive gear 86, and the lumbar drive gear 98 shown in FIG. Match.

  A shaft 130 is attached to the rear end side of the link member 129 on the front end side of the circular hole 131. The shaft 130 is arranged in a state where the axial direction is along the sheet width direction, and protrudes inward in the sheet width direction from the link member 129. One end of the shaft 130 in the axial direction is supported so as to be rotatable with respect to the link member 129, and a gear 132 is fixed to the other end of the shaft 130 in the axial direction. The gear 132 is meshed with the external teeth of the slide drive gear 94 described above. For this reason, when the slide drive gear 94 rotates, the gear 132 rotates integrally with the shaft 130 around the axis.

  One end in the axial direction of the shaft 130 protrudes to the opposite side of the clutch mechanism 62 via the link member 129, and the gear 136 constituting the speed increasing gear train 134 as shown in FIG. (Rotating member) is fixed coaxially and integrally. The gear 136 is covered with a cover 140 attached to the link member 129 and meshed with another gear 137 (rotating member) disposed between the cover 140 and the link member 129. A gear 139 (rotating member) larger in diameter than the gear 137 is provided coaxially and integrally on the right side (the cover 140 side) of the gear 137. These gears 137 and 139 are arranged on the front end side of the link member 129 with respect to the gear 136, and are supported by the link member 129 and the cover 140 so as to be rotatable around an axis along the sheet width direction. .

  The gear 139 described above is meshed with another gear 141 (rotating member) disposed between the cover 140 and the link member 129. A gear 143 (rotating member) having a diameter larger than that of the gear 141 is coaxially and integrally provided on the right side of the gear 141 (on the cover 140 side). These gears 141 and 143 are arranged on the front end side of the link member 129 with respect to the gears 137 and 139, and are supported by the link member 129 and the cover 140 so as to be rotatable around an axis along the sheet width direction. ing.

  Further, the gear 143 described above is meshed with a rail-side gear 138 (rotating member) disposed at the front end portion of the link member 129 between the cover 140 and the link member 129. The rail-side gear 138 is formed to have a smaller diameter than the gear 143, and is supported so as to be rotatable about an axis along the seat width direction with respect to the link member 129 and the cover 140.

  Here, in the first embodiment, the rotational force transmission mechanism 135 is configured by the link member 129, the cover 140, the shaft 130, the gear 132, and the speed increasing gear train 134, and the speed increasing gear train 134 is The rotation of the gear 136 is increased and transmitted to the rail side gear 138. The rail side gear 138 corresponds to the rail drive mechanism 133.

  The rail drive mechanism 133 has a transmission gear train 142 (see FIG. 11) housed in the outer gear box 144 described above. The transmission gear train 142 includes a gear 146 that is coaxially and integrally connected to the rail-side gear 138 of the speed increasing gear train 134. The rotation of the gear 146 is transmitted to a gear 148 that is provided at the upper end portion of the outer side gear box 144 and forms the transmission gear train 142. A screw gear 150 (see FIG. 11B) is coaxially arranged on the outer side of the gear 148 in the sheet width direction, and the gear 148 and the screw gear 150 rotate integrally.

  Another screw gear 152 meshed with the screw gear 150 is arranged below the screw gear 150. The screw gear 152 is fixed to the front end portion of the outer screw 154. The outer-side screw 154 is a long rod-like member having a male screw formed on the outer peripheral portion, and is arranged on the upper side of the upper frame 128 with the axial direction along the seat longitudinal direction as shown in FIG. The front end portion of the outer side screw 154 is rotatably supported by the outer side gear box 144, and the rear end portion of the outer side screw 154 is rotatable by a support member 156 attached to the rear end portion of the upper frame 128. It is supported by. Further, an outer side nut 158 formed in a substantially block shape is screwed into an intermediate portion of the outer side screw 154, and the outer side nut 158 is fixed to the lower frame 124 via a bracket 160.

  On the other hand, one end of the torque cable 164 shown in FIG. 9 is connected to the gear 146 of the transmission gear train 142 described above. The torque cable 164 is arranged with the axial direction along the seat width direction, and the other axial end is inserted into an inner gear box 166 attached to the front end of the inner upper frame 126. Yes. A transmission gear train 168 is disposed in the inner gear box 166 as shown in FIG. 12A, and the gear 170 constituting the transmission gear train 168 is disposed at one end in the axial direction of the torque cable 164. It is connected. Thereby, the rotation of the gear 146 is transmitted to the gear 170 via the torque cable 164. The rotation of the gear 170 is transmitted to a gear 172 provided at the upper end of the inner gear box 166. A screw gear 174 is coaxially arranged on the outer side of the gear 172 in the sheet width direction, and the gear 172 and the screw gear 174 rotate integrally.

  Another screw gear 176 meshed with the screw gear 174 is disposed below the screw gear 174. The screw gear 176 is fixed to the front end portion of the inner side screw 178. The inner side screw 178 is a member similar to the outer side screw 154, a front end portion is rotatably supported by the inner side gear box 166, and a rear end portion is a support member 180 attached to the rear end portion of the upper frame 126. Is rotatably supported. Further, an inner side nut 182 formed in a substantially block shape is screwed into an intermediate portion of the outer side screw 154, and the inner side nut 182 is fixed to the lower frame 122 via a bracket 184. The rail drive mechanism 133 configured as described above constitutes the slide drive force transmission mechanism 50 together with the rotational force transmission mechanism 135 as described above.

  Here, when the translation knob 110 is slid in a state where the rotation knob 108 is disposed at the position shown in FIG. 8A, the rotational force of the motor 60 is transmitted to the slide drive gear 94, and slide drive is performed. The gear 94 rotates. The rotation of the slide drive gear 94 is transmitted to the outer screw 154 via the gear 132, the shaft 130, the speed increasing gear train 134, the transmission gear train 142, and the screw gears 150 and 152, and the torque cable 164 is transmitted. It is transmitted to the inner screw 178 via the gear train 168 and screw gears 174 and 176. Thus, when the outer side screw 154 and the inner side screw 178 rotate about the axis, the outer side nut 158 moves relative to the outer side screw 154 in the axial direction, and the inner side nut 182 moves relative to the inner side screw 178. Move relative to the axis. As a result, the upper rail 128 is slid with respect to the lower rail 124 to which the outer side nut 158 is fixed, and the upper rail 126 is slid with respect to the lower rail 122 to which the inner side nut 182 is fixed. Slide back and forth with respect to the part.

  In this case, when the translation knob 110 is operated in the arrow FORWARD direction of FIG. 8A, the vehicle seat 10 is slid to the vehicle front side, and the translation knob 110 is operated in the arrow BACK direction of FIG. Then, the vehicle seat 10 is slid to the vehicle rear side.

  Next, the front tilt driving force transmission mechanism 52 that transmits the driving force from the one motor power unit 48 to the front tilt mechanism 38 will be described.

(Configuration of Front Tilt Driving Force Transmission Mechanism 52)
As shown in FIG. 13, the front tilt mechanism 38 to which the front tilt driving force transmission mechanism 52 transmits the driving force is a plate-like cushion front frame 186 (between the front portions of the side frames 20, 22). 1). Connecting members 188 and 190 are fixed to the left and right sides of the rear end side of the cushion front frame 186, and these connecting members 188 and 190 are rotatably connected to the side frames 20 and 22 via pins 192. Has been.

  A front tilt gear box 194 constituting the front tilt driving force transmission mechanism 52 is disposed below the cushion front frame 186 and on the front side of the clutch mechanism 62 in the seat. The front tilt gearbox 194 is sandwiched between the plates 65B and 65C shown in FIGS. 4 and 5 and fastened to both. As shown in FIG. 13, a pair of gears 196 and 198 arranged in the front-rear direction of the seat are disposed on the inner side in the seat width direction of the front tilt gear box 194 so as to mesh with each other. These gears 196 and 198 are rotatably supported by the front tilt gear box 194 in a state where the axial direction is along the sheet width direction.

  The rear gear 196 is engaged with the front tilt drive gear 86 described above, and the front gear 198 is connected to a screw gear 200 (see FIG. 14A) disposed in the front tilt gear box 194. Has been. The screw gear 200 is rotatably supported by the front tilt gear box 194, and another screw gear 202 is engaged with the screw gear 200. The screw gear 202 is formed in a cylindrical shape, and is supported so as not to move relative to the front tilt gear box 194 in the axial direction and to rotate about the axis. A female screw is formed inside the screw gear 202, and a screw 204 having a male screw formed on the outer peripheral portion is screwed to the female screw. A flat plate-like connecting portion 204A is provided on the upper end side of the screw 204, and the connecting portion 204A is connected to a front end portion of an outer side arm 206 (see FIG. 13) constituting the front tilt mechanism 38 via a pin. Are connected. The outer side arm 206 is paired with the inner side arm 208, and the rear end portions of the outer side arm 206 are attached to the front frame 24 of the cushion frame 14 so as to be rotatable about an axis along the seat width direction. ing. Each of the outer side arm 206 and the inner side arm 208 is connected in the seat width direction via the connecting rod 210, and each front end side is connected to the lower surface of the cushion front frame 186 via the brackets 212 and 214. Yes.

  Here, when the translation knob 110 is slid in a state where the rotation knob 108 is disposed at the position shown in FIG. 8B, the rotational force of the motor 60 is transmitted to the front tilt drive gear 86, and the front The tilt drive gear 86 rotates. The rotation of the front tilt drive gear 86 is transmitted to the screw gear 202 via the gears 196 and 198 and the screw gear 200, and the screw gear 202 rotates. When the screw gear 202 rotates, the screw 204 screwed inside the screw gear 202 is moved in the axial direction (substantially up and down direction) with respect to the screw gear 202. Accordingly, the front end sides of the outer side arm 206 and the inner side arm 208 are swung up and down around the front frame 24, and the cushion front frame 186 is swung up and down around the pin 192. Thereby, the inclination angle of the front side of the seat surface of the seat cushion 12 is adjusted.

  In this case, when the translation knob 110 is operated in the direction of the arrow UP in FIG. 8B, the inclination angle of the seat cushion 12 on the front side of the seating surface is increased, and the translation knob 110 is moved in the direction of the arrow DOWN in FIG. When operated in the direction, the inclination angle of the seat cushion 12 on the front side of the seating surface is reduced.

  Next, the front lifter driving force transmission mechanism 54 that transmits the driving force from the one motor power unit 48 to the lifter mechanism 40 will be described.

(Configuration of lifter driving force transmission mechanism 54)
As shown in FIG. 15, the lifter mechanism 40 to which the lifter driving force transmission mechanism 54 transmits the driving force includes a pair of left and right front links 216 and 218 and a pair of left and right rear links 220 and 222 (both are lifter links). It has. The front links 216 and 218 and the rear links 220 and 222 are connected at the front end side (lower end side) to the upper frames 126 and 128 of the slide rail 120 so as to be rotatable around an axis along the seat width direction. The end side (upper end side) is connected to the side frames 20 and 22 of the cushion frame 14 so as to be rotatable about an axis along the seat width direction.

  As shown in FIG. 16, a lifter gear box 224 constituting the lifter driving force transmission mechanism 54 is disposed between the right front link 218 and the clutch mechanism 62. The lifter gear box 224 is sandwiched between the plates 65A and 65B shown in FIGS. 4 and 5 and fastened to both. A shaft 226 protrudes inside the lifter gear box 224 in the seat width direction. The shaft 226 is rotatably supported by the lifter gear box 224 and the plate 65C described above in a state where the axial direction is along the seat width direction, and a gear 228 is fixed to the tip of the shaft 226.

  The gear 228 is meshed with the lifter drive gear 84 described above, and the shaft 226 is fixed to a screw gear 230 (see FIG. 17A) disposed in the lifter gear box 224. The lifter gear box 224 has the same configuration as the front tilt gear box 194 described above. When the screw gear 230 rotates, the screw gear 232 meshed with the screw gear 230 rotates and the screw 234 rotates. The screw gear 232 is moved in the axial direction (substantially the seat front-rear direction here). A flat plate-like connecting portion 234A is provided at the rear end portion of the screw 234, and the front end portion of the connecting pipe 236 is fixed to the connecting portion 234A. The rear end portion of the connection pipe 236 is rotatably connected to the upper end portion (rear end portion) of the right rear link 222 via a pin (not shown).

  Here, when the translation knob 110 is slid in a state where the rotary knob 108 is disposed at the position shown in FIG. 8C, the rotational force of the motor 60 is transmitted to the lifter drive gear 84, and the lifter drive is performed. The gear 84 rotates. The rotation of the lifter drive gear 84 is transmitted to the screw 234 via the gear 228, the shaft 226, and the screw gears 230 and 232, and the screw 234 is moved in the axial direction (substantially the seat front-rear direction) with respect to the screw gear 232. The As a result, the connecting pipe 236 is moved substantially in the front-rear direction of the seat, the rear link 222 is swung up and down about the front end side (lower end side), and the rear link 220 and the front link are interlocked with the rear link 222. The links 216 and 218 are swung up and down around each front end side. Thereby, the cushion frame 14 is moved up and down, and the seat surface height of the seat cushion 12 is adjusted in the up and down direction.

  In this case, when the translation knob 110 is operated in the arrow UP direction in FIG. 8C, the seat surface of the seat cushion 12 is raised, and the translation knob 110 is operated in the arrow DOWN direction in FIG. Then, the seat surface of the seat cushion 12 is lowered.

  Next, the lumbar driving force transmission mechanism 56 that transmits the driving force from the one motor power unit 48 to the lumbar mechanism 42 will be described.

(Configuration of lumbar driving force transmission mechanism 56)
As shown in FIG. 18, the lumbar mechanism 42 to which the lumbar driving force transmission mechanism 56 transmits the driving force includes a wire 238 whose one end is locked to the left side frame 28 of the back frame 18. An intermediate portion of the wire 238 is wound around the back side of the back spring 37 of the seat back 16 and is drawn out from between the right side frame 30 and the back spring 37 to the front side of the back frame 18. An intermediate portion of the wire 238 drawn to the front side of the back frame 18 is inserted inside a wire tube 242 whose one end is locked to the side frame 30. The other end of the wire tube 242 is disposed in the seat cushion 12 (not shown in FIG. 18), and the other end is locked to an extension 65E1 (see FIGS. 4 and 5) provided on the plate 65E. ing. The other end of the wire 238 is drawn from the other end of the wire tube 242. The other end of the wire 238 is locked to a screw 246 provided in the lumbar gear box 244.

  The lumbar gear box 244 is basically configured in the same manner as the front tilt gear box 194 and the lifter gear box 224 described above, and the gear meshed with the lumbar drive gear 98 as shown in FIG. The rotation of H.248 is transmitted to the screw 246 via a gear 250 disposed on the lower side of the gear 248 and a pair of screw gears (not shown), and the screw 246 is moved in the seat longitudinal direction. The rear end side of the screw 246 is connected to the extension portion 65E1 shown in FIGS. 4 and 5 via a link 252 that functions as a rotation stop of the screw 246, and a wire 238 is connected to the rear end portion of the screw 246. The other end is locked.

  Here, when the translation knob 110 is slid in a state where the rotation knob 108 described above is disposed at the position shown in FIG. 8E, the rotational force of the motor 60 is transmitted to the lumbar drive gear 98 to drive the lumbar. The gear 98 rotates. The rotation of the lumbar drive gear 98 is transmitted to the screw 246 via gears 248 and 250 and a screw gear (not shown), and the screw 246 is moved substantially in the front-rear direction of the seat. As a result, the wire 238 whose other end is locked to the rear end of the screw 246 is pushed and pulled, and the back spring 37 around which the intermediate portion of the wire 238 is wound back is swung in the front-rear direction of the seat back 16. Moved. As a result, the lower side of the seat back 16 is moved back and forth, and lumbar adjustment is performed.

  In this case, when the translation knob 110 is operated in the arrow FORWARD direction of FIG. 8E, the lower side of the backrest surface of the seat back 16 is pushed out to the front side of the seat back 16, and the translation knob 110 is moved to FIG. When operated in the direction of the arrow BACK in E), the lower side of the backrest surface of the seat back 16 is retracted to the rear side of the seat back 16.

  Next, the recliner driving force transmission mechanism 58 that transmits the driving force from the one motor power unit 48 to the recliner mechanism 46 will be described.

(Configuration of Recliner Driving Force Transmission Mechanism 58)
As shown in FIG. 20, the recliner driving force transmission mechanism 58 transmits the driving force, and the recliner mechanism 46 includes an outer side recliner unit 254 and an inner side recliner unit 256 (a pair of left and right recliner units). Yes. The outer side recliner unit 254 is disposed between the side frame 22 and the side frame 30 on the right side (outer side) of the vehicle seat 10, and the inner side recliner unit 256 is disposed on the left side (inner side) of the vehicle seat 10. The side frame 20 is disposed between the side frame 20 and the side frame 28. The recliner mechanism 46 includes a connecting shaft 258 that is spanned between the outer side recliner unit 254 and the inner side recliner unit 256.

  The recliner mechanism 46 described above is well known in the art, and is provided in the outer side recliner unit 254 and the inner side recliner unit 256 when the connecting shaft 258 is rotated around an axis along the seat width direction. The planetary gear mechanism that does not rotate rotates and the back frame 18 reclines with respect to the cushion frame 14.

  A recliner driving force transmission mechanism 58 is disposed between the outer side recliner unit 254 and the one motor power unit 48. The recliner driving force transmission mechanism 58 includes a front gear box 260 and a rear gear box 262 that are disposed on the outer side in the seat width direction with respect to the side frame 22 (see FIG. 1). The front gear box 260 is fixed to the front end side of the side frame 22 at the side of the clutch mechanism 62 by screws 261 (see FIG. 21), and the rear gear box 262 is a frame 264 of the outer side recliner unit 254 ( It is fixed to the front end side of FIG. The frame 264 is fixed to the rear end portion of the side frame 22.

  As shown in FIG. 21, the front side gear box 260 is formed in a box shape by fastening an outer side box 266 and an inner side box 268 with screws 270. Are arranged with an upper screw gear 272 and a lower screw gear 274 which are meshed with each other. The upper screw gear 272 is arranged in a state where the axial direction is along the sheet width direction, and is fixed to one end portion in the axial direction of the shaft 276 which is also arranged in a state where the axial direction is along the sheet width direction. The shaft 276 is rotatably supported by a bearing hole 278 formed in the outer side box 266 and a bearing hole (not shown) formed in the inner side box 268. The other axial end of the shaft 276 protrudes from the inner box 268 toward the inner side in the seat width direction (clutch mechanism 62 side), and a gear 280 is attached to the other axial end of the shaft 276. The gear 280 is meshed with the recliner drive gear 96 described above. Thereby, the rotational force of the recliner drive gear 96 is transmitted to the screw gear 272 via the gear 280 and the shaft 276.

  On the other hand, the lower screw gear 274 meshed with the screw gear 272 is arranged in a state where the axial direction is along the seat longitudinal direction, and is fixed to the front end portion (one axial end portion) of the spindle 282 which is a bar. ing. The spindle 282 is formed in a long cylindrical shape and is disposed on the outer side in the seat width direction with respect to the side frame 22 as shown in FIG. The spindle 282 is disposed in the seat cushion 12 with the axial direction along the front-rear direction of the seat, and is supported by the side frame 22 via the front gear box 260 and the rear gear box 262.

  A front end portion of the spindle 282 is rotatably supported by a pair of front and rear bearing portions 284 and 286 provided in the front gear box 260. The bearing portion 284 is formed by combining a semicircular concave portion 288 formed in the outer side box 266 and a semicircular concave portion 290 formed in the inner side box 268. The portion 286 is formed by combining a semicircular recess (not shown) formed in the outer box 266 and a semicircular recess 292 formed in the inner box 268. A ring-shaped cover 294 is attached to the front side of the bearing portion 284, and a similar cover 296 is attached to the rear side of the bearing portion 286.

  As shown in FIG. 22, the rear end portion of the spindle 282 is inserted into the rear gear box 262 and is rotatably supported by the rear gear box 262. The rear gear box 262 has basically the same configuration as the front gear box 260, and is disposed on the inner side in the seat width direction with respect to the frame 264 of the outer side recliner unit 254. In FIG. 22, in the rear gear box 262, the same reference numerals are given to the same configurations as those of the front gear box 260.

  A screw gear 298 (first gear) is fixed to a rear end portion of the spindle 282 inserted inside the rear gear box 262, and the screw gear 298 is disposed below the screw gear 298. It is meshed with another screw gear 300 (second gear). The screw gear 300 is arranged in a state where the axial direction is along the sheet width direction, and is fixed to an intermediate portion in the axial direction of the shaft 302 which is also arranged in a state where the axial direction is along the sheet width direction. One end of the shaft 302 in the axial direction is rotatably supported by the inner side box 268 of the rear gear box 262, and the other end in the axial direction is rotatably supported by the outer side box 266 of the rear gear box 262. Has been. Further, the other axial end of the shaft 302 passes through the frame 264 of the outer recliner unit 254 and protrudes outward in the seat width direction of the frame 264.

  A reduction gear train 304 is disposed outside the frame 264 in the seat width direction, and a gear 306 constituting the reduction gear train 304 is fixed to the protruding portion of the shaft 302. The rotation of the gear 306 is transmitted to the final gear 312 of the reduction gear train 304 via the gears 308 and 310. The gear 312 is fixed to one end of the connecting shaft 258 in the axial direction. The gears 308 and 310 are arranged coaxially and are rotatably supported by a support shaft 314 provided on the frame 264. Further, the gears 306, 308, 310, and 312 of the reduction gear train 304 include a long plate-like holding plate 316 that is connected to the shaft 302, the support shaft 314, and the connecting shaft 258 by a locking tool 318 (for example, an E ring). By being locked, the shaft 302, the support shaft 314, and the connecting shaft 258 are held.

  Here, when the translation knob 110 is slid in a state where the rotation knob 108 is disposed at the position shown in FIG. 8D, the rotational force of the motor 60 is transmitted to the recliner drive gear 96, and the recliner drive is performed. The gear 96 rotates. The rotation of the recliner drive gear 96 is transmitted to the spindle 282 via the gear 280, the shaft 276, and the screw gears 272 and 274, and the spindle 282 is rotated around the axis along the seat front-rear direction. When the spindle 282 is rotated, the screw gear 298 fixed to the rear end portion of the spindle 282 rotates, and the screw gear 300 meshed with the screw gear 298 is integrated with the shaft 302 and the gear 306 of the reduction gear train 304. Rotate. The rotation of the gear 306 is decelerated by the reduction gear train 304 and transmitted to the final gear 312, and the gear 312 is rotated integrally with the connecting shaft 258. Accordingly, the outer side recliner unit 254 and the inner side recliner unit 256 are operated, and the back frame 18 is reclined with respect to the cushion frame 14.

  In this case, when the translation knob 110 is operated in the arrow FORWARD direction of FIG. 8D, the back frame 18 is tilted forward of the seat with respect to the cushion frame 14, and the translation knob 110 of FIG. When operated in the direction of the arrow BACK, the back frame 18 is tilted to the rear side of the seat with respect to the cushion frame 14.

  Next, the operation and effect of the first embodiment will be described.

(Operation and effect of the first embodiment)
In the vehicle seat 10 having the above-described configuration, the rotational force of the motor 60 disposed on the front side in the seat cushion 12 is input to the sliding drive force transmission mechanism 50 via the slide drive gear 94 of the clutch mechanism 62. . The sliding drive force transmission mechanism 50 is constituted by a rail drive mechanism 133 and a rotational force transmission mechanism 135. The rotational force transmission mechanism 135 has a link member 129 having a front end side rotatably connected to the upper rail 128 side and a rear end side rotatably connected to the seat cushion 12 side. The rotational force of the slide drive gear 94 is transmitted to the rail drive mechanism 133 via the attached speed increasing gear train 134. Thereby, the rail drive mechanism 133 slides the upper rails 128 and 126 with respect to the lower rails 122 and 124, and the seat cushion 12 and the seat back 16 (seat body) are slid back and forth with respect to the vehicle body floor.

  In the vehicle seat 10, the rotational force of the motor 60 is input to the lifter driving force transmission mechanism 54 via the lifter driving gear 84 of the clutch mechanism 62. Accordingly, the lifter driving force transmission mechanism 54 drives the lifter mechanism 40, and the seat cushion 12 and the seat back 16 (seat body) are moved up and down with respect to the upper rails 128 and 126 of the slide rail 120.

  Here, as described above, when the seat body is moved up and down with respect to the upper rails 128 and 126, the link member 129 described above rotates with respect to the seat cushion 12 and the upper rail 128. That is, since the link member 129 rotates to follow the change in the distance between the seat body and the upper rail 128, a mechanism that can be expanded and contracted is unnecessary. Moreover, even if the link member 129 rotates, the distance between the rotation center of the link member 129 with respect to the seat cushion 12 and the speed increasing gear train 134 (each gear constituting the speed increasing gear train 134), and the rotation center of the link member 129 with respect to the upper rail. And the speed-up gear train 134 (each gear constituting the gear train) 134 are all kept constant. Thereby, the structure (here, the shaft 130 and the gear 132) for transmitting the rotational force from the slide drive gear 94 supported by the seat cushion 12 to the speed increasing gear train 134, and the rail driving mechanism 133 from the speed increasing gear train 134. Any of the configurations for transmitting the rotational force (here, the gear 146 of the transmission gear train 142) can be simplified. That is, for example, when a mechanism that can extend and contract and transmit a rotational force is employed, the configuration is complicated, but in the present embodiment, such a complicated mechanism is unnecessary. Therefore, the rotational force can be transmitted between the motor 60 supported by the seat cushion 12 and the rail drive mechanism 133 supported by the upper rail 128 with a simple configuration.

  Moreover, in this vehicle seat 10, the rotational force of the motor 60 is accelerated by the speed increasing gear train 134 and transmitted to the rail drive mechanism 133. Therefore, the rotational speed of the clutch mechanism 62 during motor operation is set low. Can do. Thereby, since the silence of the clutch mechanism 62 can be improved, the comfort of the vehicle occupant can be improved. In addition, since it is not necessary to provide a dedicated speed increasing gear train or the like for increasing the rotation of the motor 60 on the rail driving mechanism 133 side, the rail driving mechanism 133 can be reduced in size.

  Further, in the vehicle seat 10, the rail-side gear 138 that is the final gear of the speed increasing gear train 134 is disposed coaxially with the rotation axis of the link member 129 with respect to the upper rail 128. For this reason, even if the link member 129 rotates with respect to the upper rail 128, the position of the rail side gear 138 with respect to the upper rail 128 is kept constant. As a result, the rail-side gear 138 can be coaxially and integrally connected to the gear 146 of the transmission gear train 142 supported on the upper rail 128 side, so that the speed-up gear train 134 rotates to the transmission gear train 142. The configuration for transmitting force can be made extremely simple.

  In the vehicle seat 10, the front tilt driving force transmission mechanism 52, the lifter driving force transmission mechanism 54, the lumbar driving force transmission mechanism 56, and the recliner driving force transmission mechanism 58 are provided on the seat body side. Since the motor 60 is supported, the configuration for transmitting the rotational force from the motor 60 to each of the driving force transmission mechanisms can be simplified.

  Further, in the vehicle seat 10, the rear end side of the link member 129 is connected to the clutch mechanism 62 supported by the seat cushion 12, and relative to the clutch mechanism 62 about the axis of the slide drive gear 94. It can be rotated. Thus, since the link member 129 is directly coupled to the clutch mechanism 62 without the seat cushion 14 or the like interposed therebetween, the positioning of the clutch mechanism 62 (slide drive gear 94) and the link member 129 at the time of manufacturing the vehicle seat 10 is performed. Work can be made easy. Further, when the link member 129 rotates with respect to the clutch mechanism 62 (seat cushion 12), the gear 132 attached to the link member 129 rotates around the axis of the slide drive gear 94 with high accuracy. Regardless of the rotational position of 129, the meshing state of the gear 132 and the slide drive gear 94 can be stabilized.

  Further, in this vehicle seat 10, a dedicated link member 129 that constitutes the rotational force transmission mechanism 135 is provided separately from the front links 216 and 218 and the rear links 220 and 222 that constitute the lifter mechanism 40. It is possible to prevent an excessive load from being applied to the speed increasing gear train 134 attached to the link member 129. Thereby, durability of the rotational force transmission mechanism 135 can be improved.

  In the first embodiment, the rear end side of the link member 129 is connected to the clutch mechanism 62. However, the invention according to claims 1 to 6 is not limited thereto, and the rear end of the link member 129 is not limited thereto. The side may be connected to the side frame 22 of the seat cushion frame 14 or the like.

  In the first embodiment, the rail-side gear 138 is coaxially disposed with the rotation axis of the link member 129 with respect to the upper rail 128 and is coaxially and integrally connected to the gear 146 of the transmission gear train 142. However, the invention according to claims 1 and 2 is not limited thereto, and the gear attached to the link member 129 is engaged with the gear 146 of the transmission gear train 142 and the link member 129 is rotated. In some cases, the gear may be configured to rotate around the gear 142 while maintaining the meshed state with the gear 142. This also applies to the second embodiment of the present invention described below.

<Second Embodiment>
Next, a second embodiment of the present invention will be described. In addition, about the structure and effect | action similar to the said 1st Embodiment, the same code | symbol as the said 1st Embodiment is provided, and the description is abbreviate | omitted.

  FIG. 23 is a perspective view showing the configuration of a slide driving force transmission mechanism 320 that is a component of the vehicle seat according to the second embodiment of the present invention. The sliding drive force transmission mechanism 320 has basically the same configuration as the sliding drive force transmission mechanism 50 according to the first embodiment, but the configuration of the rotational force transmission mechanism 322 is the first embodiment. This is different from the rotational force transmission mechanism 135 according to FIG.

  In this rotational force transmission mechanism 322, the front link 218 (link for lifter; see FIGS. 15 and 16) constituting the lifter mechanism 40 is shared as a link member, and the link member 129 according to the first embodiment is used. Is omitted. The front end side (lower end side) of the front link 218 is rotatably connected to the front end side of the upper frame 128 via the outer side gear box 144, and rotates around the axis line along the seat width direction with respect to the upper frame 128. It is possible to rotate. Further, the rear end side (upper end side) of the front link 218 is connected to the side frame 22 of the cushion frame 14 so as to be rotatable about an axis along the seat width direction, similarly to the first embodiment. Yes.

  A shaft 324 is attached to the rear end side (upper end side) of the front link 218. The shaft 324 is disposed in a state where the axial direction is along the seat width direction, and projects from the front link 218 toward the inside in the seat width direction. One end of the shaft 324 in the axial direction is supported so as to be rotatable with respect to the front link 218, and a gear 326 is fixed to the other end of the shaft 324 in the axial direction. The gear 326 is engaged with another gear 328 supported by the support bracket 64 (see FIGS. 4 and 5). The gear 328 is engaged with the external teeth of the slide drive gear 94. For this reason, when the slide drive gear 94 rotates, the gear 328 rotates and the gear 326 rotates around the axis integrally with the shaft 324. The clutch mechanism 62 according to this embodiment has basically the same configuration as the clutch mechanism 62 according to the first embodiment. In this embodiment, the arrangement of the slide drive gear 94 and the lifter drive gear 84 is arranged. Have been replaced.

  One end of the shaft 324 in the axial direction protrudes to the opposite side of the clutch mechanism 62 via the front link 218, and a cushion that constitutes the speed increasing gear train 330 shown in FIG. The side gear 136 is fixed. The cushion side gear 136 is disposed coaxially with the rotational axis of the front link 218 with respect to the cushion frame 14. The rotation of the cushion side gear 136 is accelerated by gears 332, 334, 336, 338, 340, 342, 344 (all of which are rotating members) constituting the speed increasing gear train 330, and is arranged at the front end portion of the front link 218. Is transmitted to the rail-side gear 138. The gear 138 is coaxially and integrally connected to the gear 146 (see FIG. 11A) of the transmission gear train 142. In this embodiment, the torque cable 164 of the rail drive mechanism 133 is coaxially and integrally connected to a gear 162 (see FIG. 11A) constituting the transmission gear train 142.

  In this embodiment, the rotation of the slide drive gear 94 is transmitted to the rail drive mechanism 133 via the gears 328 and 326, the shaft 324, and the speed increasing gear train 330. As a result, the seat body is slid back and forth with respect to the vehicle body floor as in the first embodiment.

  Also in this embodiment, since the rotational force of the motor 60 is transmitted to the rail drive mechanism 133 via the speed increasing gear train 330 attached to the front link 218, the lifter mechanism 40 is established and the seat body side Rotational force can be transmitted between the motor 60 supported by the motor and the rail drive mechanism 133 supported on the upper frame 128 side with a simple configuration.

  In addition, in this embodiment, the cushion side gear 136 of the speed increasing gear train 330 is arranged coaxially with the rotational axis of the front link 218 relative to the seat cushion 12, so the front link 218 is relative to the seat cushion 12. Even if it rotates, the distance between the slide drive gear 94 and the cushion side gear 136 of the clutch mechanism 62 supported on the seat cushion 12 side can be kept constant. Thereby, the configuration (here, the shaft 324 and the gears 326 and 328) for transmitting the rotational force from the slide drive gear 94 supported on the seat cushion 12 side to the speed increasing gear train 330 can be simplified. .

  Further, in this embodiment, since the front link 218 constituting the lifter mechanism 40 is shared as a link member constituting the rotational force transmission mechanism 322, the number of parts can be reduced and the vehicle seat can be reduced in weight. Can be

  In each of the above embodiments, the case where the rail drive mechanism 133 constituting the slide drive force transmission mechanism 50, 320 is a driven mechanism has been described. However, the inventions according to claim 1 and claim 2 are based on this. Not limited to this, the present invention can be applied to a driven mechanism other than the rail driving mechanism 133.

  In each of the above embodiments, the rotational force transmission mechanisms 135 and 322 transmit the rotational force to the rail drive mechanism 133 via the speed increasing gear trains 134 and 330 (a plurality of gears). The invention is not limited to this, and a simple transmission gear train, a reduction gear train, or the like can be employed instead of the speed increasing gear trains 134 and 330. Moreover, in the invention which concerns on Claim 1, a rotation member is not limited to a gear, For example, a sprocket can also be employ | adopted as a rotation member. In this case, it becomes the structure which transmits a rotational force using the said sprocket and chain.

  In addition, the present invention can be implemented with various modifications without departing from the scope of the invention. Needless to say, the scope of rights of the present invention is not limited to the above embodiments.

10 Vehicle Seat 12 Seat Cushion (Seat Body)
16 Seat back (Seat body)
40 Lifter mechanism 60 Motor 62 Clutch mechanism 94 Slide drive gear (output gear)
120 Slide rail 122, 124 Lower rail (fixed rail)
126, 128 Upper rail (movable rail)
129 Link member 133 Rail drive mechanism (driven mechanism)
135 Rotational Force Transmission Mechanism 136 Cushion Side Gear (Rotating Member)
138 Rail side gear (Rotating member)
137, 139, 141, 143 Gear (Rotating member)

Claims (7)

A slide rail that is slidably connected to a fixed rail that is fixed to the vehicle body floor, and a movable rail connected to the seat body;
A lifter mechanism for raising and lowering the seat body with respect to the movable rail;
A motor supported on one of the seat body and the movable rail;
A driven mechanism supported on the other of the seat body and the movable rail;
One side is rotatably connected to the seat body side and the other side is rotatably connected to the movable rail side, and has a link member that rotates relative to the movable body when the seat body moves up and down relative to the movable rail. And a rotational force transmission mechanism that transmits the rotational force of the motor to the driven mechanism via a rotational member rotatably attached to the link member;
Vehicle seat equipped with   The vehicle seat according to claim 1, wherein the rotational force transmission mechanism includes a plurality of gears as the rotational member.   The vehicle seat according to claim 2, wherein the plurality of gears include rail-side gears arranged coaxially with a rotation axis of the link member with respect to the movable rail.   4. The vehicle according to claim 2, wherein the plurality of gears include a cushion side gear disposed coaxially with a rotation axis of the link member with respect to the seat body. 5. Sheet.   The motor is supported by the seat body, and the driven mechanism is supported by the movable rail, and the rotational force of the motor is transmitted to slide the movable rail with respect to the fixed rail. The vehicular seat according to any one of claims 1 to 4, wherein the vehicular seat is provided.   The driven mechanism is supported by the movable rail, and the motor is unitized together with a clutch mechanism having an output gear that is rotated by transmission of the rotational force of the motor, and is supported by the seat body, and the link member 6. The vehicle seat according to claim 1, wherein one side is connected to the clutch mechanism so as to be relatively rotatable about an axis of the output gear.   The vehicle seat according to any one of claims 1 to 6, wherein the link member is a lifter link that constitutes the lifter mechanism.

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