JP2008188117A - Seat device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve the problem that in a seat device employing a taumel knuckle 35 for adjusting turning angle of a seat back, when the ratio of the number of teeth of an internally toothed gear 41 on the side of a seat cushion to the number of teeth of an externally toothed gear 42 on the side of a seat back is reduced and the seat back is turned backward from a raised position, revolution movement of the externally toothed gear 42 about an axis O of the internally toothed gear 41 is performed at several times, so that the seat cushion is prevented from smoothly tilting in association with the turning of the seat back. <P>SOLUTION: The ratio of the number of teeth of the internally toothed gear 41 to the number of teeth of the externally toothed gear 42 is set to be 4/3 or more. Therefore, when the seat back is turned backward from a raised state, the axis of the externally toothed gear 42 moves forward about the axis O of the internally toothed gear 41 so as not to be returned during turning. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

    The present invention relates to a seat device in which a predetermined portion of a seat cushion is moved in accordance with forward or backward tilt of a seat back.

With respect to a vehicle seat, a so-called interlocking tilt is known in which the front end of the seat cushion is moved forward and obliquely upward in accordance with the rearward tilt of the seat back, thereby changing the tilt of the seat cushion seat surface. (See Patent Documents 1 and 2). In this interlocking tilt, the arm rotating around the swing center of the seat back and the tilt mechanism of the seat cushion are connected by a link mechanism. Also known is a seat device in which the rear end of the seat back rises as the seat back tilts, and the seat back and the seat cushion are flush with each other when the seat back is tilted to a horizontal position. (See Patent Document 3). It is also known to use a taumel mechanism that combines an internal gear and an external gear with a reclining knuckle of an automobile seat to make it easier to maintain a seat back tilting posture (see Patent Document 4). .
Japanese Patent Laid-Open No. 06-245837 JP-A-62-192114 Japanese Utility Model Publication No. 05-1337 Japanese Patent Laid-Open No. 06-62852

    In the case of a knuckle using the above Taumel mechanism, as shown in FIG. 16, for example, an internal gear A can be provided on the seat cushion frame B and an external gear C can be provided on the seat back frame D. In such a configuration, when the external gear C meshes with the internal gear A and rotates clockwise, the axis of the external gear C rotates around the axis O of the internal gear A (revolves) a. → b → c, and the seat back is rotated rearward. In the figure, for the sake of clarity, the gear ratio of the internal gear A to the external gear C is 9/8, and the axis of the external gear C is around the axis O of the internal gear A. Is revolved once, the seat back tilts about 45 degrees backward. The fact that the axis of the external gear C revolves around the axis O of the internal gear A means that the seat back does not have a fixed center of swing and the lower end of the seat back changes when the seat back rotates. That's what it means. In this case, the lower end of the seat back moves back and forth by a distance corresponding to the diameter of the revolution track.

    Normally, the gear ratio is made smaller than 9/8 in order to reduce the seat back rotation operation force. For example, while the seat back is tilted 45 degrees rearward, the axis of the external gear C is The revolving around the axis O of the internal gear A is performed several times.

    Therefore, in the interlocking tilt in which the arm is provided at the lower end of the seat back and the tilt mechanism of the seat cushion is connected by the link mechanism, the tilt of the seat cushion is caused by the forward and backward movement of the lower end of the seat back due to the revolution. The movement is jerky. That is, the tip of the arm cannot move in a circular motion with a constant trajectory, and moves while repeating a reverse movement due to the revolution. By repeating this return, the seat cushion also moves, for example, repeating tilt → stop → tilt → stop, resulting in a sense of discomfort or discomfort to the passenger.

    Therefore, the present invention provides a seat device having a knuckle that utilizes a taumel mechanism so that the movement of the seat cushion side is made smooth when a part or the whole of the seat cushion is interlocked with the rotation of the seat back. The problem is to prevent it.

    In order to solve such problems, the present invention increases the ratio of the number of teeth of the internal gear to the external gear of the Taumel mechanism so that the seat cushion operates smoothly according to the rotation of the seat back. I made it.

That is, the invention according to claim 1 is an angle adjustment unit that rotates and holds the seat back from the reference standing position to at least one of the front and rear, and
A cushion actuation mechanism for moving a predetermined part of the seat cushion up and down or back and forth;
In a seat device including an interlocking mechanism that links a predetermined portion of the seat back and the cushion operating mechanism so that a predetermined portion of the seat cushion moves up and down or back and forth according to the rotation of the seat back,
The angle adjuster includes an external gear provided on one of the seat cushion and the seat back, and an external tooth that is engaged with the internal gear provided on the other and rolls on the inner peripheral side of the internal gear. And a gear ratio of the internal gear to the external gear is set to 4/3 or more.

    Therefore, when the seat back rotates, the movement is transmitted to the cushion operating mechanism by the interlocking mechanism, and the predetermined portion of the seat cushion moves up and down or back and forth. In this case, when the external gear of the angle adjusting portion is provided on the seat back side, the axis of the external gear revolves around the axis of the internal gear on the seat cushion side (circulation), and When the internal gear is provided on the seat back side, the axis of the internal gear revolves around the axis of the external gear on the seat cushion side.

    Therefore, when the seat back rotates, the revolution movement angle at which the axis of the seat back side gear revolves around the axis of the seat cushion side gear, and the external gear changes to the internal gear along with this revolution movement. The relationship between the angle of inclination relative to the angle, that is, the seat back rotation angle, is examined. When the gear ratio of the external gear to the external gear is 4/3, when the external gear makes 3/4 of the internal circumference of the internal gear, that is, when the revolution movement angle becomes 270 degrees, Of the teeth around the external gear, the tooth first meshed with the internal gear is again meshed with the internal gear. At this time, an angle at which the external gear is inclined relative to the internal gear (seat back rotation angle) is 90 degrees.

    That is, if the above-mentioned gear ratio is 4/3, the revolution movement angle when the seat back rotation angle is 90 degrees is 270 degrees. Further, if the seatback rotation angle is 60 degrees, the revolution movement angle is 180 degrees.

    Here, the shaft center of the seat back side gear revolves around the shaft center of the seat cushion side gear, and begins to return to the original position when the revolution movement angle exceeds 180 degrees. When the revolution movement angle reaches 180 degrees, the rotation angle of the seat back becomes 60 degrees. In other words, the shaft center does not return until the rotation angle reaches 60 degrees. Become.

    That is, in the present invention, since the above-mentioned tooth number ratio is set to 4/3 or more, the seat back is in a state close to the horizontal (horizontal) from the reference standing position (for example, a state inclined backward by about 5 to 20 ° with respect to the vertical). Even if it is rotated rearward until it becomes, the shaft center of the seat back side gear does not return backward. Therefore, when the predetermined portion of the seat cushion moves up and down or back and forth with the rotation of the seat back, the movement of the predetermined portion does not stop or reverse, and the passenger feels uncomfortable or uncomfortable. Is prevented.

    The tooth ratio is preferably 3/2 or more. As a result, the revolving movement angle when the rotation angle of the seat back is 90 degrees becomes 180 degrees or less, and the seat back is turned even if the seat back is rotated backward (horizontal) from the vertical standing state. The shaft center of the back side gear does not return backward. In addition, the distance deviated to the side by revolution when the shaft center of the seat back side gear moves is also reduced. That is, when the revolution movement angle is 180 degrees, the shaft center of the seat back side gear deviates to the side by a distance corresponding to the revolution radius before going from the initial position to the opposite position, but the revolution movement angle is small. Then, the amount of deviation becomes small, which is advantageous for the smooth operation of the seat cushion.

The invention according to claim 2 is the invention according to claim 1,
An operation force input unit for rotating the seat back;
The angle adjusting unit is characterized in that an operating force is input from the operating force input unit to rotate the seat back.

    That is, the angle adjusting unit is configured to push the seat back with the back against the bias of the spring in the hinge portion between the seat back and the seat cushion after the occupant releases the positioning lock of the seat back rotation. The operation force is input from the operation input unit (electric motor or manual operation force input knob (dial)), and the seat back is rotated to hold the position. The seat back tilting operability is improved.

The invention according to claim 3 is the invention according to claim 1 or claim 2,
The interlock mechanism includes a link that swings in the front-rear direction of the seat for operating the cushion operating mechanism, and the link is connected to a predetermined portion of the seat back.

    Therefore, the rotation of the seat back can be transmitted to the cushion operating mechanism with a simple configuration.

The invention according to claim 4 is the invention according to claim 1,
The angle adjustment unit is provided to rotate the seat back backward from the reference standing position,
The internal gear and the external gear of the angle adjustment unit are configured such that when the seat back rotates rearward from a reference standing position to a predetermined maximum backward tilt position, the seat among the internal gear and the external gear. The shaft center of the gear provided on the back side is combined so as to move forward around the shaft center of the gear provided on the seat cushion side,
The predetermined portion of the seat back is provided so as to be positioned below the shaft center of the gear provided on the seat back side when the seat back is in the reference standing position.

    Therefore, when the seat back rotates backward, the predetermined portion of the seat back for operating the seat cushion not only moves forward by the rotation itself associated with the rotation of the seat back, but also the seat back side gear. The revolving movement of the shaft center also moves forward. Therefore, the amount of forward movement of the predetermined portion when the seat back is tilted rearward is increased, and the predetermined portion of the seat cushion is easily moved.

    As described above, according to the present invention, the predetermined portion of the seat back and the cushion operating mechanism are linked by the interlocking mechanism so that the predetermined portion of the seat cushion moves up and down or back and forth according to the rotation of the seat back. In the seat apparatus, since the taumel mechanism is employed in the angle adjustment portion of the seat back and the gear ratio of the internal gear to the external gear of the taumel mechanism is set to 4/3 or more, the seat when the seat back rotates This is advantageous in making the predetermined portion of the seat cushion move smoothly so that the back side gear shaft is prevented from returning backward and not causing the passenger to feel uncomfortable or uncomfortable.

    Hereinafter, embodiments of the present invention will be described with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

<Embodiment 1>
(Overall configuration of sheet device)
FIG. 1 shows an embodiment in which a seat device according to the present invention is applied to a reclining type seat 1 installed in an automobile (in the following description, front and rear and right and left of an automobile are simply referred to as front and rear and right and left). A seat cushion 2 on which an occupant sits is attached to a vehicle body floor via a base frame 3 (see FIG. 2), and an ottoman 4 (footrest) is disposed in the lower part of the front end of the seat cushion 2 so as to be retractable. On the other hand, a seat back 5 is disposed so as to extend upward from the vicinity of the rear end of the seat cushion 2, and a headrest 6 is attached to the upper end of the seat back 5.

    In FIG. 2, the cushion structure of the seat cushion 2 is omitted and its frame structure is shown. Side frames 20 and 20 which are press-formed products of steel plates, for example, are provided on the left and right sides of the seat cushion 2, The front end portion and the rear end portion are connected by pipe members 21 and 22, respectively, and springs 23 and 23 made of a wire are bridged to the left and right at an intermediate portion in the front-rear direction. Further, a plate member 25 which is a frame of the ottoman 4 is attached to the pipe member 21 at the front end portion through arms 24 and 24 so as to be swingable.

    Side frames 30 and 30 of the base frame 3 are arranged in close proximity to the lower outer sides of the left and right cushion side frames 20 and 20, respectively. The base side frames 30 and 30 are also press-molded products, and they are connected to each other by front and rear connecting plates 31 and 31 and a pipe member 32.

    Further, a rising portion 30a that is curved and extends upward is formed at the rear end portion of the base side frame 30, and the lower end portion of the frame of the seat back 5 rotates through a knuckle 35 (angle adjusting portion). It is attached as possible.

    The seat device is provided with a tilt mechanism that changes the inclination of the seat surface of the seat cushion 2 in conjunction with the rotation of the seat back 5. This point will be described in detail later.

(Knuckle (angle adjustment part))
As shown in FIGS. 3 and 4, the knuckle 35 includes an internal gear 41 formed at the rear end rising portion 30 a of the seat cushion side frame, and an external gear 42 formed at the frame lower end portion 51 of the seat back. A Taumel mechanism is used. The ratio of the number of teeth of the internal gear 41 to the external gear 42 is 4/3 or more (in the example shown, about 4/3). This will be specifically described below.

    As shown in FIG. 4, an internal gear 41 and a bearing cylinder 43 on the inner side are formed concentrically at the rising portion 30 a on the seat cushion side, and the seat width is between the internal gear 41 and the bearing cylinder 43. Open outward in the direction. A rotation shaft 44 extending in the seat width direction is fitted to the bearing cylinder 43 of the left and right rising portions 30a of the seat and is rotatably supported.

    An annular external gear 42 is provided at the lower end 51 of the seat back frame so as to protrude toward the center in the seat width direction. The annular external gear 42 is inserted between the internal gear 41 of the rising portion 30a and the bearing cylinder 43 from the outside in the seat width direction. A cover 45 is fixed to the rotating shaft 44 outside the lower end 51 of the seat back frame, and the cover 45 covers the inside of the annular external gear 42. A support cylinder 46 is formed in the center of the cover 45, and the support cylinder 46 is fitted on the outer peripheral side of the bearing cylinder 43 so as to be rotatable from the outside in the seat width direction.

    As shown in FIG. 3, since the external gear 42 has a smaller number of teeth than the internal gear 41, it is eccentric with respect to the internal gear 41 by partially meshing with the internal gear 41. A space between the inner peripheral surface of the external gear 42 and the support tube 46 is referred to as an eccentric region. A pair of arc-shaped wedges 47 and 47 and an arc-shaped operating body 48 are inserted in the eccentric region. The wedges 47, 47 are urged away from each other by a spring 49, and due to the urging, the space between the inner peripheral surface of the external gear 42 and the support cylinder 46 in the eccentric region is narrowed. It is pushed in and is in a state of biting into the inner peripheral surface of the external gear 42 and the outer peripheral surface of the support cylinder 46. As a result, the external gear 42 has a large amount of eccentricity and is strongly pressed by the meshing portion with the internal gear 41, so that the external gear 42 is in a non-rotatable locked state. That is, the seat back 5 is held so as not to rotate with respect to the seat cushion 2.

    The operating body 48 is integrally provided on the outer peripheral surface side of the support tube 46 of the cover 45 and is disposed on the opposite side of the wedges 47 and 47 in the eccentric region, and both end surfaces are relative to the end surfaces of the wedges 47 and 47. is doing. When the rotating shaft 44 is rotated in one direction, the operating body 48 rotates in the same direction together with the rotating shaft 44 and hits one wedge 47, whereby the one wedge 47 rotates in the same direction and the above biting is released. (The above lock is released). Along with this, the external gear 42 rotates while changing the meshing position with the internal gear 41. By this rotation, the lock of the other wedge 47 is also released. The same applies when the rotation shaft 44 is rotated in the other direction.

    By rotating the rotating shaft 44 in this manner, the seat back 5 is unlocked with respect to the seat cushion 2 and is rotated forward or backward by the rotation of the external gear 42. At that time, the external gear 42 on the seat back side is eccentric with respect to the axis of the rotating shaft 44 (the axis of the internal gear 41), and revolves around the axis. The revolution movement angle of the external gear 42 when the seat back 5 rotates 60 degrees is 180 degrees.

    Further, in the present embodiment, when the seat back 5 is in the reference standing position (a state in which the seat back 5 is tilted backward by a predetermined angle between 5 and 20 degrees), as shown in FIG. The taumel mechanism is configured such that the shaft center of the seatback side external gear 42 is located at a position A that is most eccentric to the seat rear side with respect to the axis O of the tooth gear 41. Therefore, when the seatback 5 rotates rearward from the reference standing position, the axis of the external gear 42 moves forward around the axis of the internal gear 41 (A → A ′). In the present embodiment, the axial center of the external gear 42 is the B position that is most eccentric to the front side of the seat when the seat back 5 is at the maximum rearward tilted position (a state where the seatback 5 is tilted about 80 degrees rearward relative to the vertical). To.

    Accordingly, the axis of the external gear 42 moves only forward around the axis of the internal gear 41 when the seat back 5 rotates backward from the reference standing position to the maximum backward tilt position, and the maximum rear When returning from the tilted position to the reference standing position, it moves only backward around the axis of the internal gear 41.

(Operating force of the angle adjuster)
As shown in FIG. 4, one end of the rotating shaft 44 projects outward from the cover 45, and a worm gear 61 is fixed to the projecting portion. As shown in FIG. 6, the worm gear 61 that is rotationally driven by the output shaft (operation force input unit) of the electric motor 62 is engaged with the worm gear 61. Accordingly, an operating force is input to the knuckle 35 by the operation of the electric motor 62, whereby the rotating shaft 44 rotates and the seat back 5 rotates. The electric motor 62 is supported by the rear end rising portion 30a of the seat cushion side frame, and is operated by an occupant by an operation switch (not shown) provided in the seat 1 or in the room. The electric motor 62 may be installed on a vehicle body structure such as a vehicle body panel.

(Tilt mechanism)
As shown in FIG. 6, a tilt mechanism 7 that tilts (swings) the seat cushion 2 adjacent to the inside (right side) of the left side frame 20 of the seat cushion 2, and this tilt is rotated by the seat back 5. When the seat back 5 is rotated from the reference standing position shown in FIG. 6 to a reclining position (see FIG. 7) inclined backward by a predetermined angle, the interlocking mechanism 8 that is linked to the movement is integrally provided. The front part of the seat cushion 2 is raised along with the inclination so that the inclination toward the rear side of the seating surface is strengthened. The predetermined angle can be set in advance as, for example, an inclination angle of the seat back 5 (for example, an angle inclined about 40 degrees with respect to the vertical) suitable for an occupant sitting on the seat 1 to take a nap.

    First, the tilt mechanism 7 will be described. As shown in FIG. 6, a downward projecting portion 20 a is formed at the front portion of the cushion side frame 20, and the projecting portion 20 a is interposed via a link 70 and a swing lever 71. The base side frame 30 is connected to the front portion so that the height can be adjusted. In addition, a downward projecting portion 20 b is formed at the rear end portion of the cushion side frame 20, and the projecting portion 20 b rotates around a support pin (a horizontal axis) 37 attached to the base side frame 30. Supported as possible.

    Thus, the cushion side frame 20 rotates around the support pin 37 that supports the lower projecting portion 20b on the rear side, so that the front portion of the seat cushion 2 swings up and down (tilt). Even if the front part of the seat cushion 2 swings, the rear end thereof hardly moves (in this example, it moves slightly back and forth due to the swing of the downward projecting part 20b), and the front part of the seat cushion 2 also moves up and down. The amount of movement before and after the amount of movement is small.

    More specifically, the lower projecting portion 20 a on the front side of the cushion side frame 20 is rotatably connected to the upper end portion of the link 70 via a pin 72, and the lower end portion of the link 70 is rocked via a pin 73. The movable lever 71 is pivotally connected to one end of the movable lever 71. This rocking lever 71 is a “<”-shaped flat plate member, and a rocking shaft 74 is fixed in a bent state at a bent portion. As shown in FIG. 2, the swing shaft 74 extends in the left-right direction, and both end portions thereof are rotatably supported by the base side frames 30 and 30, respectively.

    One side of the rocking lever 71 extends substantially forward from the rocking shaft 74 and rocks up and down. A link 70 connected to the end of the rocking lever 71 is located forward of the rocking shaft 74. The point of action of the force from the swing lever 71 to the cushion side frame 20 is positioned forward. This means that the point of application of the force to the front portion of the seat cushion 2 is far from the rear shaft support portion (support pin 37), and thereby the seat cushion can be operated with a relatively small force. The front part of 2 can be moved up and down.

    As described above, one side (hereinafter also referred to as an output side) of the swing lever 71 that operates the cushion side frame 20 via the link 70 is separated from the swing shaft 74 when the seat back 5 is in the reference standing position. It extends diagonally forward and downward. Therefore, the front part of the cushion side frame 20 connected to the end part on the output side via the link 70 is positioned relatively downward, and at this time, the seating surface of the seat cushion 2 is the seating posture of the occupant It is in the appropriate inclination state set beforehand corresponding to. Hereinafter, it is said that the seat cushion 2 is at the reference position at this time.

    Further, in this embodiment, a coil spring 75 is disposed between the cushion side frame 20 and the base side frame 30 behind the link 70 and the swing lever 71 so as to extend vertically, The front part of the cushion side frame 20 is always urged downward. This urging force acts downward on the output side of the swing lever 71 via the link 70, and always urges the swing lever 71 to rotate counterclockwise in FIG.

    On the other hand, although not shown, a stopper portion is provided on the inner side of the base side frame 30 so as to engage with the cushion side frame 20 when the seat cushion 2 is at the reference position and to prevent downward movement thereof. ing. For this reason, even if it is urged downward by the tensile force of the coil spring 75 as described above, the front part of the cushion side frame 20 cannot move below the position corresponding to the reference position of the seat cushion 2. . That is, the front portion of the seat cushion 2 is at the lowest position at the reference position.

    As described above, the other side of the swing lever 71 having a “<” shape extends substantially upward from the swing shaft 74 in this embodiment. The front end portion of the second interlocking link 81 of the interlocking mechanism 8 is rotatably connected, and the rotational displacement of the drive part 66 of the seat back 5 is transmitted via the interlocking mechanism 8 ( Hereinafter, the other side of the swing lever 71 is also referred to as an input side). As will be described in detail later, when the seat back 5 tilts backward from the reference standing position to the reclining position, the input lever is pulled backward via the second interlocking link 81, so that the swing lever 71 is a coil spring. It rotates in the clockwise direction in the figure against the rotational biasing force of 75.

    When the swing lever 71 rotates in this manner, the output side thereof moves upward and pushes up the front portion of the cushion side frame 20 via the link 70. FIG. 7 shows a state in which the seat back 5 is tilted rearward to the reclining position. At this time, the front portion of the seat cushion 2 is at the highest position (uppermost position), and its seating surface tilts relatively rearward. Thus, it is possible to appropriately hold the buttocks of the occupant whose upper body is entrusted to the seatback 5 tilted backward, and to prevent the forward displacement thereof. The position of the seat cushion 2 at this time is hereinafter referred to as a tilt position.

    As described above, in the tilt mechanism 7 of this embodiment, the movement of the second interlocking link 81 in the front-rear direction accompanying the rotation of the seat back 5 is efficiently moved up and down by the “<”-shaped swing lever 71. In other words, the front part of the seat cushion 2 is moved up and down by converting into movement in the direction, and the amount of vertical movement of the front part of the seat cushion 2 can be sufficiently increased with a compact configuration.

    Further, the end of the swing lever 71 on the input side is positioned above the swing shaft 74 and is pulled rearward by the second interlocking link 81 as the seat back 5 rotates backward. As a result, the input side of the swing lever 71 is displaced rearward, that is, away from the swing shaft 74, so that it is easy to prevent the interference between them, and this also constitutes the tilt mechanism 7 compactly. This is preferable.

(Interlocking mechanism)
Next, the interlocking mechanism 8 will be described. The interlocking mechanism 8 of this embodiment includes a first and a second connecting the drive unit (predetermined portion of the seat back) 66 provided at the frame lower end 51 of the seat back 5 to the swing lever 71 of the tilt mechanism 7. The two interlocking links 80 and 81. One end portion (end portion on the seat back side) of the first interlocking link 80 is rotatably connected to the driving portion 66 via a pin 82, while the other end portion (tilt mechanism) of the first interlocking link 80 is provided. Side end) is rotatably connected to a rear end portion of the second interlocking link 81 via a pin 83. The front end portion of the second interlocking link 81 is rotatably connected to the input side end portion of the swing lever 71 of the tilt mechanism 7 via the pin 76 as described above.

    The drive portion 66 of the seat back 5 is provided so as to be positioned below the axis of the external gear 42 when the seat back 5 is in the reference standing position. Therefore, when the seat back 5 rotates backward from the reference standing position, the drive unit 66 moves forward.

-Long hole of the first interlocking link-
In this embodiment, the first interlocking link 80 is formed with a long hole 80a that is long in the longitudinal direction, and the long hole 80a can rotate with the support pin 38 attached to the base side frame 30 and slide. Engagement possible. For this reason, the first interlocking link 80 has an end portion (pin 82) between the elongated hole 80 a and the support pin 38 when the seatback 5 rotates around the rotation support shaft 52. The operation is restricted so that the engaged state is maintained, and as a result, the first interlocking link 80 is either rotated around the support pin 38 or slid along the support pin 38. The operation mode is switched so as to become the subject.

    For example, when the seat back 5 rotates between the reference standing position (FIG. 6) and the reclining position (FIG. 7), the moving direction of the one end portion (pin 82) of the first interlocking link 80 (in FIG. 6, the arrow a1). 1) is significantly different from the direction in which the elongated hole 80a extends, the first interlocking link 80 mainly operates to rotate around the support pin 38, and is connected to the other end. The rear end portion of the interlocking link 81 moves substantially in the front-rear direction as indicated by an arrow a2 in FIG. As a result, the entire second interlocking link 81 moves in the front-rear direction.

    On the other hand, when the seat back 5 is further tilted backward beyond the reclining position in FIG. 7, the movement direction of one end (pin 82) of the first interlocking link 80 is the long hole 80a as shown by an arrow a3 in FIG. Therefore, the first interlocking link 80 moves in the vertical direction by sliding the elongated hole 80a with respect to the support pin 38. As shown in FIG. 8, the support pin 38 is positioned at the lowermost end of the long hole 80 a of the first interlocking link 80 in the full flat position where the seat back 5 is substantially laid down.

    Then, when the seat back 5 rotates between the reclining position (FIG. 7) and the full flat position (FIG. 8), the other end portion (pin 83) of the first interlocking link 80 is shown by an arrow in FIG. As shown by a4, the second interlocking link 81 connected to the rear end portion of the second interlocking link 81 is rotated around the pin 76 at the front end portion, but is almost in the front and rear direction. Do not move.

    In other words, when the seat back 5 is tilted backward from the reference standing position, the first interlocking link 80 operates as a pivoting body as the seat back 5 tilts backward until the reclining position, whereby the second interlocking link is operated. The tilt mechanism 7 is operated via 81, and the inclination of the seat surface of the seat cushion 2 changes. On the other hand, when the seat back 5 is tilted backward beyond the reclining position, the first interlocking link 80 mainly operates by sliding up and down, and the tilt mechanism 7 does not operate, so that the seat cushion 2 is in the tilt position. Maintained.

-Long hole of the second interlocking link-
In this embodiment, a long hole 81a is also formed in the front end portion of the second interlocking link 81 connected to the output side of the swing lever 71 as described above, and a connecting pin 76 rotates in the long hole 81a. It is inserted so as to be slidable. As shown in FIG. 6 and the like, the long hole 81a extends long in the front-rear direction, so that the front end portion of the second interlocking link 81 can turn to the input-side end portion of the swing lever 71 and is substantially in the front-rear direction. It is slidably connected to.

    Due to the presence of the long hole 81a, even if the second interlocking link 81 moves back and forth as the seat back 5 rotates as described above, it is not transmitted to the swing lever 71 and the tilt mechanism 7 operates. There are things that do not. That is, when the seat back 5 is in the reference standing position, as shown in FIG. 6, the pin 76 is located at the front end of the long hole 81a of the second interlocking link 81, from which the second interlocking link 81 moves forward. Even if it moves, the pin 76 only slides relatively rearward in the long hole 81a formed therein, and the pin 76 is not pushed forward from the second interlocking link 81.

    Further, when the seat cushion 2 is in the reference position, the seat cushion 2 is prevented from moving downward by the stopper portion via the cushion side frame 20, and thus the swing lever 71 is in a state opposite to that shown in FIG. Clockwise rotation is prevented. Therefore, when the seatback 5 rotates between the reference standing position (FIG. 6) and the position tilted forward (FIG. 9), the first interlocking link 80 rotates accordingly, and the second interlocking is performed. Even if the link 81 moves back and forth, the operation is not transmitted to the swing lever 71, and the seat cushion 2 remains maintained at the reference position.

  On the other hand, when the seat back 5 is between the reference standing position (FIG. 6) and the reclining position (FIG. 7), the seat cushion 2 is also between the reference position and the tilt position. The tensile force of the acting coil spring 75 acts on the swing lever 71 via the link 70, and this is urged to rotate counterclockwise in FIG. For this reason, when the seat back 5 returns from the reclining position to the reference standing position, the pin 76 moves forward so as not to leave the front end of the elongated hole 81a as the second interlocking link 81 moves forward. Accordingly, the swing lever 71 rotates.

    On the other hand, when the seat back 5 tilts rearward toward the reclining position, the second interlocking link 81 moves rearward while pulling the pin 76 engaged with the elongated hole 81a at the front end portion thereof, and thus the swinging movement is performed. The moving lever 71 turns clockwise in FIG. 6 or the like against the turning biasing force caused by the tensile force of the coil spring 75.

    In other words, in this embodiment, when the seat back 5 is tilted forward from the reference standing position, the second displacement link 81 is connected to the connecting portion on the tilt mechanism 7 side so that the rotational displacement is not transmitted to the tilt mechanism 7. The long hole 81a is provided, and when the seat back 5 returns to the reference standing position from the reclining position, the rotational displacement is difficult to be transmitted. It is configured such that it always returns downward to the reference position by being urged downward by a tensile force of 75. As a result, the rotational displacement of the seat back 5 returning from the reclining position is transmitted to the tilt mechanism 7. Will be.

(Sheet operation)
Next, the operation of the seat 1 according to this embodiment will be described. First, when the seat back 5 is tilted backward from the reference standing position shown in FIG. 6, the rotating shaft 44 is rotated by the rotating worm gear 61 by operating the electric motor 62 by a switch operation. Due to the rotation of the rotating shaft 44, the operating body 48 rotates around the bearing cylinder 43 and the wedges 47, 47 are removed. Thereby, the external gear 42 on the seat back side rotates to change the meshing position with the internal gear 41 on the seat cushion side. That is, the seat back 5 rotates backward.

    Although the external gear 42 on the seat back side is eccentric with respect to the internal gear 41 on the seat cushion side, the gear ratio of the external gear 42 to the internal gear 41 is set to 4/3 or more. Even if the seat back 5 is rotated backward from the reference standing position to the reclining position, the axis of the external gear 42 only moves forward around the axis of the internal gear 41 and does not return backward. . Accordingly, the drive unit 66 on the seat back side moves forward around the rotation shaft 44 as the seat back 5 rotates rearward.

    As the drive unit 66 moves forward, the first interlocking link 80 smoothly rotates counterclockwise without being slightly swung back and forth around the support pin 38. Accordingly, the second interlocking link 81 moves rearward and pulls the input side of the swing lever 71 rearward. As a result, the swing lever 71 is rotated clockwise as shown in FIG. 6 and the like, and the front portion of the cushion side frame 20 is pushed up via the link 70, thereby resisting the tensile force of the coil spring 75. The front rises. Thus, when the front part of the seat cushion 2 rises, the rise does not stop or reverse, preventing the passenger from feeling uncomfortable or uncomfortable.

    In this way, the front part of the seat cushion 2 rises as the seat back 5 tilts backward, and the rear tilt of the seat surface gradually increases, so that the butt of the occupant is appropriately adjusted according to the degree of rear tilt of the seat back 5 Will be able to hold. Then, as shown in FIG. 7, when the seat back 5 is in the reclining position and the occupant tilts the upper body in the seat back 5 so that it is easy to take a nap, the seat cushion 2 is compared at the tilt position. It will be in the state where it inclined tightly, and it can prevent front shift of a crew member's buttocks.

    Thus, even when the front portion of the seat cushion 2 is raised to the uppermost position so that the seat surface is inclined relatively tightly, the rear end of the seat cushion 2 is hardly moved (in this example, Rather, since there is no large gap between the lower end of the reclining seat back 5 as described above, the occupant's bottom is sandwiched in such a gap, and the comfortability is impaired. There is no fear.

    When the seat back 5 further tilts backward, the first interlocking link 80 now slides in the elongated hole 80a with respect to the support pin 38 and moves generally upward, whereby the second interlocking link 81 is moved. It rotates around its front end (pin 76) counterclockwise (upward) in the figure, and hardly moves back and forth. Thus, the swing lever 71 does not swing until the seat back 5 reaches the full flat position (FIG. 8), and the seat cushion 2 is maintained in the tilt position.

    Thus, when the seat back 5 tilts backward beyond the reclining position, the rotational displacement is not transmitted to the tilt mechanism 7 and the seat cushion 2 is maintained at the tilt position. The tilt of the seat surface does not become too tight even if the vehicle is tilted backward, so that the occupant's comfortability does not deteriorate and the operation of the reclining lever and the like does not become difficult.

    When the seatback 5 tilted backward beyond the reclining position returns to the reference standing position as described above, even if the seatback 5 is rotated to the reclining position in the same manner as described above, the second interlocking link 81 is moved to its front end. The swing lever 71 does not swing only by rotating around the portion (pin 76). On the other hand, from the reclining position to the reference standing position, when the first interlocking link 80 rotates around the support pin 38 clockwise as the seat back 5 rotates, the second interlocking link 81 is thereby rotated. Is moved forward, and the swing lever 71 is rotated counterclockwise in the figure by the rotation biasing force generated by the tensile force of the coil spring 75.

    Therefore, as the seat back 5 gradually rises from the reclining position toward the reference standing position, the front portion of the seat cushion 2 is gradually moved downward by the tensile force of the coil spring 75, and the inclination of the seat surface gradually increases. To become loose. As a result, the seat surface of the seat cushion 2 is in an appropriate inclined state corresponding to the degree of rearward inclination of the seatback 5 as in the case of the rearward inclination.

    When the seat back 5 that has returned to the reference standing position further rotates forward, the first interlocking link 80 moves around the support pin 38 along with the rotation as in the case of returning from the reclining position as described above. As a result, the second interlocking link 81 moves forward. At this time, the seat cushion 2 is already in the reference position, and the front portion thereof cannot move any further downward. Does not rotate, and the input side pin 76 slides relatively rearward along the elongated hole 81a at the front end of the second interlocking link 81.

    That is, the rotational displacement of the seat back 5 is absorbed by the elongated hole 81 a of the second interlocking link 81 in the interlocking mechanism 8 and is not transmitted to the tilt mechanism 7. On the contrary, when the seat back 5 is rotated from the forward tilt position to the reference standing position, the rotational displacement is absorbed by the elongated hole 81a of the second interlocking link 81 in the same manner as described above, to the tilt mechanism 7. Is not transmitted.

<Embodiment 2>
This embodiment is shown in FIGS. A drive portion 66 is provided that protrudes downward from the frame lower end portion 51 of the seat back 5 when in the reference standing position. Further, the interlocking mechanism 8 is constituted by one interlocking link 85. The configuration of the tilt mechanism 7 is also changed. Other configurations are substantially the same as those of the first embodiment. Hereinafter, the same members are denoted by the same reference numerals, and description thereof is omitted.

    Referring to FIG. 10, in this example, the swing lever 77 of the tilt mechanism 7 is not shaped like “<” as in the above embodiment, and the swing shaft 74 is fixed to one end (the upper end in the figure) and the other end (The lower end in the figure) is constituted by a link serving as both an input side and an output side. Further, the link 70 connected to the swing lever 77 by the pin 73 has a longer axial length than that of the above embodiment. Furthermore, the front end portion of the interlocking link 85 is connected to the pin 73 that connects the two through a slot 85a so as to be rotatable and slidable.

    The interlocking link 85 is shaped like a letter “h” that is long in the front-rear direction so that the first and second interlocking links 80, 81 in the above embodiment are integrated, and the bent portion on the rear end side is the base side frame 30. The side of the upper projecting portion 30a extends upward, and a driving portion 66 on the seat back 5 side is rotatably connected to an upper end portion thereof via a pin 86. An elongated hole 66a is formed in the driving portion 66, and a pin 86 attached to the rear end portion of the interlocking link 85 is rotatably and slidably engaged with the elongated hole 66a. .

    Then, when the seat back 5 tilts backward (reclining) from the reference standing position shown in FIG. 10 to the reclining position shown in FIG. 11, the connecting portion (pin 86) with the drive unit 66 moves as the seat back 5 rotates. By rotating around the rotating shaft 44 in the clockwise direction in the figure, the interlocking link 85 moves forward, so that the lower end portion of the swing lever 77 rotates around the swing shaft 74 in the clockwise direction in the figure. At the same time, the front portion of the cushion side frame 20 is pushed up via the link 70, and the seat cushion 2 is positioned at the tilt position where the front portion is the uppermost position.

    Next, when the seat back 5 further tilts beyond the reclining position (FIG. 11), the pin 86 at the rear end portion of the interlocking link 85 slides along the elongated hole 66a of the driving portion 66, and the seat back 5, even if the drive unit 66 rotates around the rotation shaft 44, the interlocking link 85 only rotates around its front end (pin 73), and the swing lever 77 or The link 70 is not operated. Therefore, the seat cushion 2 is maintained in the tilt position until the seat back 5 reaches the full flat position shown in FIG.

    On the other hand, when the seat back 5 tilts forward from the reference standing position (FIG. 10), the drive unit 66 rotates around the rotation shaft 44 counterclockwise as the rotation proceeds, and the connecting portion with this. As the (pin 86) moves rearward and obliquely upward, the interlocking link 85 moves backward including its front end. However, in the long hole 85a at the front end portion of the interlocking link 85 that moves backward in this manner, the pin 73 slides relatively to the front side, and the pin 73 is not pulled to the rear side. Therefore, the swing lever 77 and the link 70 do not operate. For this reason, the seat cushion 2 is maintained at the reference position as shown in FIG.

    Thus, when the seat back 5 is further rotated forward from a state inclined forward by a predetermined angle, and the drive unit 66 further rotates around the rotation shaft 44, the rear end portion of the interlocking link 85 is moved by the pin 86. Further, the pin 73 is already lifted obliquely upward, but since the pin 73 is already positioned at the front end in the elongated hole 85a at the front end, the pin 73 is also moved obliquely upward and rearward. The swing lever 77 is lifted obliquely upward rearward, whereby the swing lever 77 rotates around the swing shaft 74 counterclockwise in the figure.

    By the rotation of the swing lever 77, the front portion of the cushion side frame 20 is pulled down via the link 70, and the seat surface of the seat cushion 2 sinks as shown in FIG. Therefore, the seat back 5 can be largely inclined forward until the back surface thereof becomes a substantially horizontal forward lying position without causing interference with the seat cushion 2.

    In this example, as described above, the interlocking link 85 is connected to the drive unit 66 on the seat back 5 side and the swing lever 77 on the tilt mechanism 7 side through the long holes 66a and 85a, respectively. Then, while the seat back 5 is rotated 90 ° or more (first set angle) from the reference standing position (FIG. 10) to the front prone position (FIG. 14), the seat cushion 2 is moved by the tilt mechanism 7. Only about 15 ° (second set angle) rotates. That is, since the downward tilt angle is smaller than the reference position of the seat cushion 2, it is not necessary to dispose the tilt angle greatly away from the vehicle body floor, and it can be said that the degree of freedom in layout is high.

    Further, as can be seen from FIGS. 11, 12, etc., since the interlocking link 85 has a “he” shape, the interlocking link 85 does not protrude upward even when the seat back 5 is largely inclined backward. The interference with the cushion body of the seat cushion 2 can be easily avoided.

    Thus, also in the case of the present embodiment, when the seat back 5 rotates rearward from the reference standing position, the axis of the external gear of the knuckle 35 only moves forward, so the seat cushion 2 is jerky. Tilt smoothly without tilting.

<Embodiment 3>
In this embodiment, the present invention is applied to an ottoman rotation mechanism and is shown in FIG. The drive part 66 for the ottoman turning mechanism 90 projects downward from the lower part 51 of the seat back frame when the seat back is in the reference standing position, as in the second embodiment. The ottoman 91 is provided with a footrest cushion 93 on one side of a substrate 92. The ottoman rotation mechanism 90 is configured such that one end of the substrate 92 of the ottoman 91 is rotatably connected to the front end of the base side frame 30 of the seat cushion 2 by a support pin 94 in the seat width direction.

    The interlocking mechanism 8 is configured by one link 87. That is, the link 87 extends in the front-rear direction, its front end is connected to the base plate 92 of the ottoman 91 by the connecting pin 88 in the sheet width direction, and its rear end is connected to the driving unit 66 by the connecting pin 89 in the sheet width direction. . The connecting pin 88 at the front end is provided movably in a long hole (a long hole extending from the base end side to the front end side) 92 a formed in the substrate 92. Further, the link 87 is provided with a long hole 87a in the link longitudinal direction at an intermediate portion thereof, and the long hole 87a is engaged with a regulation pin 30A provided in the base side frame 30 in the seat width direction so as to be relatively movable. .

    Therefore, when the seat back 5 is rotated backward, the link 87 is moved forward by the accompanying rotation of the drive unit 66, and accordingly, the ottoman 91 is rotated forward from the state where the ottoman 91 is suspended from the front end of the seat cushion 2. Then rise. Also in the case of this embodiment, when the seat back 5 rotates backward from the reference standing position, the axis of the external gear of the knuckle 35 only moves forward, so that the ottoman 91 can smoothly move without being jerky. Rotation rises.

<Other embodiments>
In the above embodiment, the internal gear 41 is provided on the seat cushion side and the external gear 42 is provided on the seat back side. Conversely, the internal gear 41 is provided on the seat back side, and the external gear 42 is provided on the seat cushion side. It may be provided.

1 is a perspective view illustrating an appearance of an automobile seat according to Embodiment 1. FIG. It is a perspective view which omits the cushion body of the same form and shows the frame structure of a seat cushion. It is sectional drawing which shows the structure of the knuckle of the same form. FIG. 4 is a sectional view taken along line AA in FIG. 3. It is explanatory drawing which shows that the shaft center of the external gear of the knuckle of the same form moves around the shaft center O of the internal gear. It is a side view which shows the relationship of each mechanism of the sheet | seat apparatus of the form. FIG. 7 is a view corresponding to FIG. 6 at the time of reclining. FIG. 7 is a view corresponding to FIG. 6 when fully flat. FIG. 7 is a view corresponding to FIG. 6 when the seat back is tilted forward. FIG. 7 is a view corresponding to FIG. 6 according to the second embodiment. FIG. 8 is a view corresponding to FIG. FIG. 9 is a view corresponding to FIG. FIG. 10 is a view corresponding to FIG. FIG. 11 is a view corresponding to FIG. 10 when the seat back is retracted. FIG. 7 is a view corresponding to FIG. 6 according to the third embodiment. It is explanatory drawing of the subject of this invention.

Explanation of symbols

1 sheet (sheet device)
2 Seat cushion 5 Seat back 7 Tilt mechanism (cushion operating mechanism)
8 interlocking mechanism 35 knuckle (angle adjustment part)
41 Internal gear 42 External gear 44 Rotating shaft 62 Electric motor (operation force input unit)
66 Driving part (predetermined part of seat back)
90 Ottoman rotation mechanism (cushion operating mechanism)
91 Ottoman (footrest)

Claims (4)

An angle adjuster for rotating and holding the seat back from the reference standing position to at least one of the front and rear, and
A cushion actuation mechanism for moving a predetermined part of the seat cushion up and down or back and forth;
In a seat device including an interlocking mechanism that links a predetermined portion of the seat back and the cushion operating mechanism so that a predetermined portion of the seat cushion moves up and down or back and forth according to the rotation of the seat back,
The angle adjuster includes an external gear provided on one of the seat cushion and the seat back, and an external tooth that is engaged with the internal gear provided on the other and rolls on the inner peripheral side of the internal gear. And a gear ratio of the internal gear to the external gear is set to 4/3 or more. In claim 1,
An operation force input unit for rotating the seat back;
The seat device according to claim 1, wherein the angle adjustment unit rotates the seat back when an operation force is input from the operation force input unit. In claim 1 or claim 2,
2. The seat device according to claim 1, wherein the interlocking mechanism includes a link that swings in the front-rear direction of the seat for operating the cushion operating mechanism, and the link is connected to a predetermined portion of the seat back. In claim 1,
The angle adjustment unit is provided to rotate the seat back backward from the reference standing position,
The internal gear and the external gear of the angle adjustment unit are configured such that when the seat back rotates rearward from a reference standing position to a predetermined maximum backward tilt position, the seat among the internal gear and the external gear. The shaft center of the gear provided on the back side is combined so as to move forward around the shaft center of the gear provided on the seat cushion side,
The seat device, wherein the predetermined portion of the seat back is provided so as to be positioned below the shaft center of the gear provided on the seat back side when the seat back is in a reference standing position. .

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