JP2013082276A - Vehicle seat - Google Patents

Abstract

PROBLEM TO BE SOLVED: To adjust an urging force of a spring for raising a seat structure not to excessively develop momentum of a rasing speed.SOLUTION: A vehicle seat 1 has a seat back 2 (seat structure) hinge-connected to a seat cushion 3 in the state of being rotatable to be raised. A link mechanism 6 connected between the seat back 2 and the seat cushion 3 includes a four link mechanism which includes a first link member 6A integrally provided in the seat back 2, a second link member 6B rotatably and axially connected to the seat cushion 3, a third link member 6C axially connected to each of the first link member 6A and second link member 6B, and a fourth link member 6D comprising the seat cushion 3. A spiral spring 7 for urging the link mechanism 6 to perform link movement in the raising rotation direction of the seat back 2 is set in a part (joint part) for connecting the second link member 6B and the fourth link member 6D together.

Description

  The present invention relates to a vehicle seat. More specifically, the present invention relates to a vehicle seat in which a seat structure is hinged to be raised and rotated with respect to a base member provided on a floor.

  2. Description of the Related Art Conventionally, a vehicular seat is known in which a seat back is connected to a seat cushion so as to be reclined, and a spring biasing force in a forward rotation direction is always applied to the seat back (Patent Document 1). . The spring is hooked on a connecting portion between the seat back and the seat cushion, and the seat back can be raised by a spring biasing force.

JP 2004-305549 A

  However, in the conventional technique described in Patent Document 1, the urging force by the spring may be overwhelmed as the seat back raises up to the standing position, and the raising speed may be excessively boosted. The present invention was devised as a solution to the above-mentioned problem, and the problem to be solved by the present invention is that the urging force of the spring that raises the seat structure is not excessively raised in the raising speed. There is to be able to adjust so that.

In order to solve the above problems, the vehicle seat of the present invention takes the following means.
A first invention is a vehicle seat in which a seat structure is hinged to a base member provided on a floor so as to be raised and rotated. The base member is provided with a link mechanism that is connected to the seat structure and performs a link motion in conjunction with the raising rotation of the seat structure. The link mechanism includes a first link member provided integrally with the seat structure, a second link member rotatably provided to the base member, a first link member, and a second link member. Each of the four link mechanisms includes a third link member that is axially connected and a fourth link member that includes a base member. A spring that biases the link mechanism so as to perform a link motion in the direction in which the seat structure is raised up is set at either the joint portion of the second link member or the third link member.

  According to the first aspect of the present invention, by setting the spring at the joint portion of either the second link member or the third link member, the transition accompanying the raising of the seat structure of the urging torque exerted by the spring is achieved. The curve can be appropriately changed by selecting a joint to be set or changing the link ratio of the link mechanism. Therefore, the transition curve of the bias torque of the spring accompanying the raising of the seat structure is adjusted so as to be close to the transition curve of the self-weight action of the seat structure, so that the raising speed of the seat structure is not overly elastic. Can be adjusted.

  According to a second invention, in the first invention described above, the spring is set at a joint portion in which the second link member and the fourth link member are axially connected.

  According to the second aspect of the invention, the spring is set at the joint portion between the base member serving as the fixed link (fourth link member) and the second link member, so that the spring can be positioned even when the seat structure rotates. Can be set at a fixed position. Therefore, the link mechanism can have a compact configuration with a small operating space.

  According to a third invention, in the first or second invention described above, the relative rotation between the link members is stopped at the joint portion where the second link member and the fourth link member are axially connected, and the back of the seatback is stopped. A reclining device for fixing the tilt angle is provided.

  According to the third aspect of the invention, the reclining device is set at the joint portion between the base member serving as the fixed link (fourth link member) and the second link member, so that the seat structure rotates the reclining device. Even if the position does not change, it can be set to a fixed position. Accordingly, various related parts such as an operation member for operating the reclining device can be set at a fixed position with respect to the base member, and a compact configuration with a small operating space and stable operability can be obtained. Can be configured.

1 is an exploded perspective view showing a skeletal structure of a vehicle seat of Example 1. FIG. It is a side view of a vehicle seat. It is a disassembled perspective view of a reclining apparatus. It is the IV-IV sectional view taken on the line of FIG. It is the side view which showed the motion of the link mechanism interlocked with tilting rotation of a seat back. It is the model which showed the relationship between the rotation angle of a link mechanism, and the rotation angle of a seat back. It is the schematic diagram which showed the relationship of the rotation angle at the time of changing the link ratio of a link mechanism. It is the schematic diagram which showed the relationship of the rotation angle at the time of changing the link ratio of a link mechanism. It is the graph which compared the change curve of the self-weight action of a seat back, and spring energizing torque. It is a front view of the side flip-up type vehicle seat shown as another Example. It is a side view of the front raising type vehicle seat shown as other examples.

  EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is demonstrated using drawing.

  First, the configuration of the vehicle seat 1 according to the first embodiment will be described with reference to FIGS. As shown in FIG. 1, the vehicle seat 1 of this embodiment includes a seat back 2 that serves as a backrest for a seated occupant, a seat cushion 3 that serves as a seating portion, and a headrest 4 that serves as a receiving portion for the head. It is configured. Here, the seat back 2 corresponds to the “seat structure” of the present invention, and the seat cushion 3 corresponds to the “base member” of the present invention. The seat cushion 3 is connected to a vehicle floor via a pair of left and right slide devices 8 described later. The headrest 4 is provided attached to the upper part of the seat back 2.

  The seat back 2 is provided such that the lower end portion thereof is axially connected to the rear end portion of the seat cushion 3 described above by a connecting shaft 6P1, and is tiltable and rotatable in the front-rear direction of the seat. In addition, a link mechanism 6 is provided between the seat back 2 and the seat cushion 3 so as to be linked with the tilting rotation of the seat back 2. This link mechanism 6 is constituted by a four-joint link mechanism having a degree of freedom of 1, and the link movement is stopped by the configuration of the reclining device 5 provided with a rotation stopping structure provided at one joint portion of the link mechanism. And can be switched to be allowed. By switching so that the link motion of the link mechanism 6 is stopped or allowed, the backrest angle of the seat back 2 can be switched or fixed.

  The reclining device 5 described above is normally held in a state where the link motion of the link mechanism 6 is stopped (locked state) by a spring force action of a spiral spring 60 described later in FIG. The locked state of the reclining device 5 is released by a lifting operation of a release lever 5C provided on the side of the seat cushion 3 shown in FIG. Here, the release lever 5C is integrally coupled to the operation shaft member 5A inserted through the shaft center portion of the reclining device 5, and the operation shaft member 5A is pivoted integrally with the lifting operation. The reclining device 5 is switched from the locked state to the unlocked state. By this switching operation, the link mechanism 6 is switched to a state in which the link motion can be performed, and the backrest angle of the seat back 2 can be freely adjusted. In the unlocked state of the reclining device 5, when the lifting operation of the release lever 5C is stopped, the release lever 5C is returned to the original position together with the operation shaft member 5A and returned to the locked state. . As a result, the seat back 2 is fixed at the adjusted backrest angle position.

  Here, at the connecting portion between the link mechanism 6 and the seat cushion 3, two spiral springs 7 that apply a rotational urging force to the link mechanism 6 in the direction in which the seat back 2 is always rotated forward of the seat. Is hung. Here, the spiral spring 7 corresponds to the “spring” of the present invention. The structure for attaching these spiral springs 7 will be described later. By the biasing force of these spiral springs 7, the seat back 2 is released from the fixed state of the backrest angle, so that the seat back 2 reaches the position where it hits the back of the seated occupant. The backrest angle position is adjusted following the movement of the back of the seated occupant being tilted back and forth.

  Here, when the seat back 2 is in an angle region in which the backrest angle is tilted to the rear side of the seat from the position where the seat back is erected straight upward, the lifting operation of the release lever 5C is stopped, and the above-described operation is performed. Thus, the backrest angle is returned to a fixed state (locked state). However, when the backrest angle is within an angle region where the seatback angle is tilted forward from the standing position, the backrest angle is not fixed even if the lifting operation of the release lever 5C is stopped, and the seatback 2 can tilt. It is designed to be kept as it is.

  The angle region in which the former backrest angle is returned to the fixed state is formed by the rotation region of the lock zone set in the reclining device 5 to be described later, and the angle region in which the latter backrest angle is not returned to the fixed state is It is formed by a free zone rotation region set in a reclining device 5 to be described later. By setting the free zone, the front of the seat back 2 exceeding the standing position by the urging force of the spiral spring 7 when the release lever 5C is pulled up in a state where no person is sitting on the vehicle seat 1 If the seat back is lowered to the position, even if the operation of the release lever 5C is stopped, the seat back 2 is moved forward until it reaches a position in which the seat back 2 is in a forward leaning position to be locked with a stopper 3Fd provided on a seat cushion frame 3F described later. It has come to be defeated.

  Next, the structure of each part of the vehicle seat 1 described above will be described in detail. The seat back 2 is composed of a seat back frame 2F constituting the skeleton, a pad material 2P serving as a cushion portion constituting the outer shape of the seat back 2, and a cloth skin material 2C serving as an outer cover. The seat back frame 2F is formed by bending a steel pipe material (round pipe) in a reverse U shape so that the skeleton width between the frames on both sides approaches the center of the seat back 2 in the width direction. It is formed in a compact frame shape in the width direction. Between the frames on the both sides of the seat back frame 2F, horizontally long mounting plates 2F1 are bridged and integrally coupled to the front and lower two positions.

  In addition, at the lower part between the frames on both sides of the seat back frame 2F, a “U” -shaped U-shaped plate 2F2 projecting to the front side of the seat is integrally coupled across the frames on both sides. It is provided in a state. The U-shaped plate 2F2 has a plate-shaped plate 3F3 provided in a protruding state at a rear end portion of a seat cushion frame 3F, which will be described later. It is made into the state where the shaft was rotatably inserted and inserted into the shaft. As a result, the seat back frame 2F is axially coupled to the seat cushion frame 3F so as to be able to tilt and rotate in the seat front-rear direction.

  In addition, a plate-like lower end bracket 2F3 is integrally formed between the lower ends of both side frames projecting further downward from the mounting position of the U-shaped plate 2F2 of the seat back frame 2F. It is provided in a state where it is spanned and connected. A rear end portion of a third link member 6C constituting a link mechanism 6 described later is axially coupled to the lower end bracket 2F3 so as to be rotatable by a coupling shaft 6P4.

  The pad material 2P described above is made of urethane foam, and a steel wire 2P1 and two horizontally long mounting plates 2P2 are respectively inserted and integrally molded during foam molding. And buried. The wire 2P1 is circulated in an annular shape along the outer peripheral edge shape of the pad material 2P, and fulfills the function of maintaining the basic shape of the pad material 2P by its rigidity. The mounting plate 2P2 is bridged and integrally coupled to two positions above and below between the embedded wires 2P1. These mounting plates 2P2 are in a state in which two bolts 2B are integrally joined in advance, and each bolt 2B is provided so as to protrude from the shape of the pad material 2P to the seat rear side. .

  The pad material 2P is assembled and fixed to the seat back frame 2F as follows. That is, the pad material 2P has the two bolts 2B attached to each mounting plate 2P2 described above in the two holes 2Fa formed in each mounting plate 2F1 of the seat back frame 2F. Each is inserted and set from the front side of the seat, and is fixed integrally to the seat back frame 2F by screwing and fastening the nut 2N from the rear side to each of the inserted bolts 2B. It is assembled.

  The pad material 2P described above is formed in an upwardly spread shape in which the upper portion is wide in the width direction and the lower portion is narrow in the width direction. Specifically, the upper shape of the pad material 2P is formed in a shape having a shape that is wide in the lateral width direction so that the back of the seated occupant can be widely supported up to both shoulders of the seated occupant. The spreading shape of the upper part of the pad material 2P is formed so as to be gradually narrowed to the lower side toward the intermediate part of the pad material 2P. And the shape from the intermediate part of this pad material 2P to the lower part is formed in the slender shape which has the narrow width | variety of the grade which can support the seat passenger | crew's waist | hip | lumbar part. The skin material 2C is applied to the pad material 2P described above from the front surface side, and the peripheral edge portion thereof is turned to the rear side from each of the upper, lower, left and right peripheral edge portions of the pad material 2P and is attached to the rear surface portion of the pad material 2P. By being hooked, the entire surface of the pad material 2P is covered and stretched.

  As described above, the seat back 2 described above has a configuration in which the space 2P3 is formed on both side portions of the lower portion of the pad material 2P because the width shape of the lower portion of the pad material 2P is narrow and the shape is widened upward. It has become. As shown in FIG. 2, the space 2 </ b> P <b> 3 can be used as a leg opening space where a passenger in the rear seat can throw out both legs forward. As a result, even in a vehicle in which the distance between the front seat and the rear seat is narrow, it is possible to sufficiently ensure the comfortability of the passenger sitting on the rear seat.

  As shown in FIG. 1, the seat cushion 3 includes a seat cushion frame 3 </ b> F that forms a skeleton thereof, a pad material 3 </ b> P that becomes a cushion portion that forms an outer shape of the seat cushion 3, a cloth skin material 3 </ b> C that becomes an outer cover, It is composed of The seat cushion frame 3F is formed by bending a steel pipe material (round pipe) into a square frame shape. Between the frames on both sides of the seat cushion frame 3F, two horizontally long mounting plates 3F1 are bridged and integrally coupled at two upper and lower upper surface positions. Further, a base plate 3F2 having an L-shaped cross section that is long in the front-rear direction is bridged between the front and rear frames of the seat cushion frame 3F and is integrally coupled. The L-shaped plate has a horizontally oriented surface portion that is integrally welded to the lower surface portions of the front and rear frames of the seat cushion frame 3F, and the other surface portion is fixed to the seat cushion frame. It is provided in a state of hanging downward from 3F.

  Further, a “U” -shaped U-shaped plate 3F3 projecting to the rear side of the seat is provided in an integrally coupled state at the center of the rear frame of the seat cushion frame 3F. The U-shaped plate 3F3 is connected to the above-described U-shaped plate 2F2 coupled to the lower portion of the seat back frame 2F so as to be rotatable by a connecting shaft 6P1 in a state in which both protruding plate portions overlap each other. It is said that it was in the state. The seat cushion frame 3F is installed and fixed on the upper rails 8B of the pair of left and right sliding devices 8 installed on the lower floor by leg frames 3F4 coupled to the four corners thereof. Yes. The configuration of each slide device 8 will be described in detail later.

  The pad material 3P is made of foamed urethane, and a wire 3P1 made of steel wire and two horizontally long mounting plates 3P2 are respectively inserted and integrally molded during foam molding inside the pad material 3P. And buried. The wire 3P1 is circulated in an annular shape along the outer peripheral edge shape of the pad material 3P, and fulfills the function of maintaining the basic shape of the pad material 3P by its rigidity. The mounting plate 3P2 is provided in a state in which it is bridged and integrally coupled to two positions in the front and rear, straddling between the embedded wires 3P1. These mounting plates 3P2 are in a state in which two bolts 3B are integrally joined in advance, and each bolt 3B is provided to protrude from the shape of the pad material 3P to the seat lower side. .

  The pad material 3P is assembled and fixed to the seat cushion frame 3F as follows. That is, the pad material 3P has two bolts 3B each attached to each mounting plate 3P2 described above in each two holes 3Fa formed in each mounting plate 3F1 of the seat cushion frame 3F. Each of the bolts 3B is inserted and set from the upper side, and the nut 3N is screwed and fastened to the inserted bolt 3B from the lower side to be integrally fixed to the seat cushion frame 3F. It is assembled.

  The skin material 3C is applied to the above-described pad material 3P from the upper surface side, and the peripheral edge portion thereof is turned downward from the front, rear, left and right peripheral edge portions of the pad material 3P to the lower surface portion of the pad material 3P. By being hooked, the entire surface of the pad material 3P is covered and stretched. In addition, a skin material 3C having the same configuration is also applied to the lower part of the pad material 3P so as to surround the space raised by the lower leg frame 3F4 from the outer side of the seat cushion frame 3F. It is provided.

  The headrest 4 has a configuration in which a cloth skin material 4C is put on a pad material 4P made of urethane foam. The headrest 4 is set by being fitted into the bent portion at the top of the seat back frame 2F described above from above. It is in a state.

  Each slide device 8 is composed of a lower rail 8A fixed on the floor, an upper rail 8B assembled to the lower rail 8A so as to be slidable back and forth, and a slide lock mechanism (not shown) provided between the rails. ing. Each lower rail 8A is provided in a state of being fixed at a position raised from the floor by a pair of front and rear leg frames 8A1. The upper rail 8B has a structure in which the lower end portion of the leg frame 3F4 coupled to the four corners of the seat cushion frame 3F described above is coupled to the upper surface portion thereof, and is integrally coupled to the seat cushion frame 3F. The slide device 8 is normally held in a state where the slide of each upper rail 8B is locked by the above-described slide lock mechanism (not shown), and by releasing the slide lock state by operating a lever (not shown), Each of the upper rails 8B is slidable so that the seating position in the front-rear direction of the seat cushion 3 can be adjusted.

  As shown in FIG. 2, the link mechanism 6 includes a first link member 6A constituted by the seat back frame 2F itself, and a second link member 6B rotatably connected to the base plate 3F2 of the seat cushion frame 3F. The first link member 6A and the second link member 6B have a third link member 6C in which each end portion is rotatably connected to the lower end portion of the second link member 6B, and a seat cushion frame 3F itself. The four-link member 6D is configured as a four-joint link mechanism. Specifically, the first link member 6A is rotatably connected to the fourth link member 6D (base plate 3F2) by the connecting shaft 6P1 described above. The upper end of the second link member 6B is rotatably connected to the fourth link member 6D (base plate 3F2) by a connecting shaft 6P2 configured by a reclining device 5 described later. The front end portion of the third link member 6C is rotatably connected to the lower end portion of the second link member 6B by a connecting shaft 6P3, and the rear end portion is connected to the first link member 6A by a connecting shaft 6P4. A shaft is rotatably connected to the (lower end side bracket 2F3 integrally coupled to the seat back frame 2F).

  As a result, as shown in FIG. 5, the link mechanism 6 is configured such that the second link member 6B and the first link member 6A move in conjunction with the movement of the seat back 2 tilting and rotating around the connecting shaft 6P1. The fourth link member 6D (base plate 3F2) is used as a fixed link, and the link movement is performed in a manner of swinging and rotating in the front-rear direction. The reclining device 5 constituting the connecting shaft 6P2 of the second link member 6B and the fourth link member 6D (base plate 3F2) described above will be described in detail later, but the second link member 6B is connected to the fourth link member 6D. In addition to the function as a rotating shaft device that is rotatably supported, the second link member 6B is normally provided with a function as a rotation lock device that can hold the second link member 6B in a state in which the rotation is stopped.

  With the configuration of the reclining device 5, the seat back 2 is normally held in a state in which the backrest angle is fixed via the configuration in which the link mechanism 6 described above is held in a rotationally stopped state. It has become. The seat back 2 can be tilted and rotated in the front-rear direction while being accompanied by the link motion of the link mechanism 6 by releasing the rotation stop state of the reclining device 5 described above by the lifting operation of the release lever 5C described above. It can be switched to a ready state.

  Here, between the second link member 6B provided with the reclining device 5 interposed therebetween and the base plate 3F2, a rotational biasing force in the counterclockwise direction shown in the drawing is always applied to the second link member 6B. Thus, two spiral springs 7 are applied to the seat back 2 so as to always apply a rotational biasing force in the direction of forward rotation. As shown in FIG. 4, these spiral springs 7 have their inner end portions hooked on a spring hook plate 3Fb formed by cutting and raising the base plate 3F2, and their outer end portions are the first end portions. The spring hooking plate 6B2 having an L-shaped cross section coupled to the two link members 6B is hooked on the protruding surface portion and is provided in the same direction in a side-by-side manner.

  By the way, as shown in FIG. 6, the link mechanism 6 mentioned above is the parallel link whose link ratio is 1: 1 in which the link length L1 of the first link member 6A and the link length M1 of the second link member 6B are the same. It becomes the composition of. Accordingly, the change angle θ1 of the backrest angle of the seatback 2 (first link member 6A) and the change angle γ1 of the second link member 6B change at the same rate. Here, the reclining device 5 that functions as the rotation lock device described above has a structure that locks rotation by meshing teeth, as will be described later, and the meshing pitch between the teeth is set at an interval of 2 degrees. Thus, the rotation can be locked at intervals of 2 degrees. Therefore, the adjustment pitch of the backrest angle of the seat back 2 is also the same as the meshing pitch of the reclining device 5 because the link ratio of the link mechanism 6 is 1: 1 as described above. The backrest angle can be adjusted with this adjustment pitch.

  The adjustment pitch of the backrest angle of the seat back 2 is adjusted to be smaller or larger than the meshing pitch (2 degrees) of the reclining device 5 by changing the link ratio of the link mechanism 6 described above. Can be adjusted. Specifically, as shown in FIG. 7, the second link ratio is set so that the link length L2 of the first link member 6A is longer than the link length M2 of the second link member 6B. The change angle θ2 of the first link member 6A (seat back 2) with respect to the change angle γ2 of the link member 6B can be adjusted to be small. Thereby, the adjustment pitch of the backrest angle of the seat back 2 is set to be smaller (finer) than 2 degrees which is the meshing pitch of the reclining device 5. Further, as shown in FIG. 8, the second link member 6B is set by setting the link ratio between the two so that the link length L3 of the first link member 6A is shorter than the link length M3 of the second link member 6B. The change angle θ3 of the first link member 6A (seat back 2) with respect to the change angle γ3 can be adjusted to be large. Thereby, the adjustment pitch of the backrest angle of the seat back 2 is set to be larger than 2 degrees which is the meshing pitch of the reclining device 5.

  Further, a spiral spring 7 for urging the seat back 2 in the forward rotation direction is connected to the connecting portion between the second link member 6B and the fourth link member 6D of the link mechanism 6 (four-link mechanism). By setting two, the urging torque exerted by these spiral springs 7 changes as shown by a transition curve P1 shown by a solid line in FIG. 9 as the seat back 2 is raised and rotated. Become. Here, in the graph of FIG. 9, the horizontal axis represents the rotation angle of the seat back 2, and the vertical axis represents the urging torque exerted by the spiral spring 7 or the magnitude of the self-weight moment of the seat back 2. In the drawing, a transition curve P2 that changes to a U-shape indicated by a broken line is a curve that shows a change in the self-weight moment of the seat back 2 acting around the rotation center (the connecting shaft 6P1) of the seat back 2. The lowest point position located substantially at the center of the transition curve P2 indicates the angular position at which the seat back 2 stands up, and each transition in which the self-weight moment increases toward the right side or the left side from there is the seat back. It is shown that the self-weight moment increases as 2 tilts backward or forward.

  In addition, the transition curve P3 indicated by the phantom line in FIG. 5 indicates that the spiral spring (7A) is the center of rotation of the seat back 2 (the connecting portion between the first link member 6A and the fourth link member 6D). This shows the change in the biasing torque exerted by the spiral spring (7A) when it is set to. In this way, when the spiral spring (7A) is set at the center of rotation of the seat back 2, the urging torque exerted by the torsional angle increases as the rotation angle of the seat back 2 advances in the backward tilt direction. Increases, and changes so as to increase linearly ascending to the right. Therefore, by increasing or decreasing the set number of the spiral spring (7A) on the transition curve P3 of the energizing torque of the spiral spring (7A) that increases linearly in such a way as to rise rightward, the weight of the seat back 2 is increased. It is very difficult to adjust the moment transition curve P2 so as to be close to the moment transition curve P2.

  That is, the above-described spiral spring 7A always keeps the seat back until the transition curve P3 of the urging torque that is exerted raises the seat back 2 from the rearward tilt position to the front position beyond the upright position. The spring force must be adjusted so as to shift a value higher than the self-weight moment of 2 (transition curve P2). In that case, if the adjustment of the spring force described above is performed by changing the set number of the spiral springs 7A, the urging torque to be exerted becomes too large or too small. Difficult to adjust. If the urging torque described above becomes too large, the urging torque (transition curve P3) exerted by the spiral spring 7A at the position (maximum angle position) where the seat back 2 is greatly tilted rearward, and the seat The difference from the self-weight moment of the back 2 (transition curve P2) becomes particularly significant, and the raising speed of the seat back 2 is excessively boosted.

  However, as in this embodiment, the spiral spring 7 is set at the connecting portion (joint portion) between the second link member 6B and the fourth link member 6D of the link mechanism 6 (four-bar link mechanism). The urging torque exerted by the spiral spring 7 can be changed so as to be a downward-sloping curve as indicated by a transition curve P1 indicated by a solid line in FIG. The shape of the transition curve P1 changes the link ratio between the first link member 6A and the second link member 6B described above, or sets the spiral spring 7 between the second link member 6B and the third link member 6C. Various changes can be made by changing the connecting portion (joint portion) or the connecting portion (joint portion) between the third link member 6C and the first link member 6A. That is, as in the present embodiment, the spiral spring 7 is set at the joint portion via the link mechanism 6 that is linked to the movement of the seat back 2, so that the number of the spiral springs 7 is not increased. By changing the setting location and the link ratio of the link mechanism 6, the shape of the transition curve P1 of the urging torque exerted can be changed to a shape suitable for the shape of the transition curve P2 of the self-weight moment of the seat back 2. Can be adjusted to take.

  Further, in the present embodiment, the spiral spring 7 is set at the joint portion between the fourth link member 6D (seat cushion frame 3F) and the second link member 6B serving as a fixed link, whereby the spiral spring 7 is seated back 2. It can be set to a fixed position where the position does not change even if is rotated. Similarly, since the reclining device 5 is set at the joint portion between the fourth link member 6D (seat cushion frame 3F) serving as a fixed link and the second link member 6B, the seat back 2 rotates the reclining device 5. Even if the position does not change, it can be set to a fixed position. Therefore, by setting the position of the reclining device 5 and the spiral spring 7, the link mechanism 6 can have a compact configuration with a small operating space.

  Next, the specific configuration of the reclining device 5 described above will be described in detail with reference to FIGS. As shown in FIG. 3, the reclining device 5 includes a disk-shaped ratchet 10 and guide 20, two poles 30, a slide cam 40, a hinge cam 50, a spiral spring 60, and an outer peripheral ring 70. However, these are assembled together in the axial direction.

  In the ratchet 10 described above, a cylindrical portion 12 is formed on the outer peripheral portion of the disk portion 11 so as to protrude in a cylindrical shape in a plate thickness direction (axial direction) that is an assembling direction to the guide 20. The cylindrical portion 12 is formed by being extruded by half-cutting the outer peripheral portion of the disc portion 11 in the plate thickness direction. The inner circumferential surface of the cylindrical portion 12 has an inner circumferential tooth surface 12a having inner teeth that can mesh with outer circumferential tooth surfaces 30a of the respective poles 30 described later, and a smooth arc surface with no inner teeth. The protruding riding surface 12b is formed side by side in the circumferential direction. The tooth pitch of the inner peripheral tooth surface 12a is set to 2 degrees. Moreover, the said raising surface 12b is formed in the position of one place of the circumferential direction on the internal peripheral surface of the cylindrical part 12, The internal peripheral surface is radial direction rather than the tooth tip of the internal peripheral tooth surface 12a. An arc surface protruding inward is formed.

  As shown in FIG. 4, the ratchet 10 has a disk surface on the outer side of the disk portion 11 joined to the plate surface of the second link member 6 </ b> B of the link mechanism 6 described above. Here, a round hole 14 penetrating in the axial direction is formed at the center of the disk portion 11 of the ratchet 10. The second link member 6B is also formed with a round hole 6B1 penetrating in the axial direction at a position coaxial with the round hole 14. In these round holes 14 and 6B1, the operation shaft member 5A for performing the switching operation of locking / unlocking of the reclining device 5 is penetrated in the axial direction.

  Next, the configuration of the guide 20 will be described with reference to FIG. The guide 20 is formed in a disk shape having an outer diameter slightly larger than that of the ratchet 10 described above, and a plate thickness direction (axial direction) that is an assembling direction to the ratchet 10 is formed on the outer peripheral portion of the disk portion 21. A cylindrical portion 22 protruding in a cylindrical shape is formed. The cylindrical portion 22 is formed by being extruded by half-cutting the outer peripheral portion of the disc portion 21 in the plate thickness direction. The cylindrical portion 22 has an inner diameter slightly larger than the outer diameter of the cylindrical portion 12 of the ratchet 10, and as shown in FIG. 4, the cylindrical portion 12 of the ratchet 10 is fitted in the cylinder in the axial direction. As a result, the cylindrical portions 12 and 22 are loosely fitted in and out of each other, and the ratchet 10 and the guide 20 are assembled in a state of supporting each other in a relatively rotatable manner. It is like that.

  As shown in FIG. 3, guide walls 21a, 21b, 21c, and 21d projecting in the plate thickness direction, which is the assembling direction to the ratchet 10, are provided at four positions on the disk portion 21 of the guide 20 in the circumferential direction. (Hereinafter referred to as guide walls 21a to 21d). These guide walls 21a to 21d are formed by being extruded by partially punching part of the disk portion 21 in the plate thickness direction. The guide walls 21a to 21d support two poles 30 described later set on the disk part 21 in the circumferential direction so as to be movable only inward and outward in the radial direction, and also the disk part. The slide cam 40 set at the center portion on 21 is supported in the circumferential direction so as to be movable only in a radial direction perpendicular to the slide direction of each pole 30.

  As shown in FIG. 4, the outer surface of the disk portion 21 of the guide 20 is joined to the plate surface of the base plate 3 </ b> F <b> 2 integrally joined to the seat cushion frame 3 </ b> F described above. Has been. Here, a round hole 25 penetrating in the axial direction is formed at the center of the disk portion 21 of the guide 20 described above. Further, the base plate 3F2 is formed by cutting and raising the spring hook plate 3Fb for hooking the inner ends of the spiral springs 7 described above, so that a hole is formed in the cut and raised portion. 3Fc is formed. An operation shaft member 5A that performs the switching operation of the reclining device 5 described above is inserted through the round hole 25 and the hole 3Fc in the axial direction. As shown in FIG. 3, two spring hooks 24c protruding in a pin shape are formed on the outer surface of the guide 20 described above. The outer end 62 of the spiral spring 60 is hooked on one of the spring hooks 24c.

  Referring to FIG. 3, a guide groove 23 that is recessed in a “ten” shape in the plate thickness direction is formed on the inner disk surface of the disk portion 21 of the guide 20 described above. The guide groove 23 is formed by half-cutting the disk portion 21 into a “ten” shape in the plate thickness direction, and the four corners of a portion where the groove shape crosses, that is, a region between the grooves protruding in the radial direction. Each of the above-described guide walls 21a to 21d is formed in the portion so as to protrude in a vertical wall shape in the plate thickness direction. Of the groove portions recessed in the “ten” shape, the guide groove 23 described above has two groove portions extending from the center portion of the guide 20 to the upper side and the lower side in the drawing, respectively. It is formed as a pole groove 23a that can be accommodated inside so as to be movable inward and outward in the radial direction.

  Similarly, of the groove portions of the guide groove 23 recessed in the “ten” shape, the groove portion formed by communicating the center portion of the guide 20 and the two groove portions extending in the left-right direction in the drawing is provided with a slide cam 40 described later. It is formed as a cam groove 23b that can be accommodated inside so as to be movable in the horizontal direction (radial direction) shown in the figure. The guide walls 21a to 21d described above are respectively assigned to the side surfaces of the poles 30 accommodated in the pole grooves 23a and the side surfaces of the slide cams 40 accommodated in the cam grooves 23b. The pole 30 and the slide cam 40 are each guided so as to be movable only in a specific radial direction.

  Each pole 30 described above is set in each pole groove 23a formed in the above-described guide 20, so that it can move only inward and outward in the radial direction along the shape in each pole groove 23a. It is arrange | positioned as the state supported in the circumferential direction. The outer peripheral surfaces of these poles 30 are formed as outer peripheral tooth surfaces 30a having external teeth that can mesh with the inner peripheral tooth surfaces 12a of the cylindrical portion 12 of the ratchet 10 described above.

  Each of the poles 30 is pushed outward in the radial direction by a slide operation of a slide cam 40 described later, and the outer peripheral tooth surfaces 30a are engaged with the inner peripheral tooth surfaces 12a of the cylindrical portion 12 of the ratchet 10. Become. As a result, each pole 30 is integrally pressed in the rotational direction (circumferential direction) with respect to the ratchet 10 as being pressed against the inner peripheral tooth surface 12a of the ratchet 10 by the pressing force of the slide cam 40. It is held in a state.

  Each of the poles 30 can slide only inward and outward in the radial direction by the support in the circumferential direction by the guide walls 21a to 21d described above in relation to the guide 20. Accordingly, the ratchet 10 is in a state in which the respective poles 30 are engaged with each other, so that the ratchet 10 is integrated with the guide 20 through the poles 30 in the rotational direction, that is, the rotation with respect to the guide 20 is locked. Is held. As a result, the reclining device 5 is rotationally locked.

  The rotation lock state of the reclining device 5 is released when the slide cam 40 is slid in the opposite direction and each pole 30 is drawn inward in the radial direction to be released from the meshing state with the ratchet 10. It has become. Here, the operations of pushing the above-described poles 30 outward in the radial direction by the sliding motion of the slide cam 40 or pulling them inward in the radial direction are performed on the upper and lower peripheral edges of the slide cam 40 shown in FIG. Each shoulder 42 and hook 44 are formed.

  Specifically, each shoulder portion 42 is pushed out from the inside in the radial direction to the outside in such a manner that the both leg portions 32 of each pole 30 ride on each other as the slide cam 40 slides in one direction. Is meshed with the inner peripheral tooth surface 12 a of the ratchet 10. The hooks 44 are formed to bend from the upper and lower outer peripheral portions of the slide cam 40 so that the slide cam 40 slides in the other direction. Each pole 30 is pulled inward in the radial direction by being hooked on each hook portion 31 formed in the portion, and each pole 30 is removed from the meshed state with the inner peripheral tooth surface 12a of the ratchet 10. Yes. Here, the movement of the respective poles 30 inward in the radial direction is allowed by the structure in which the leg portions 32 enter into the respective groove portions 43 formed in the periphery of the upper and lower sides of the slide cam 40. It has become.

  The slide cam 40 normally presses each pole 30 from the inner side in the radial direction with the hinge cam 50 mounted in the through hole 41 in the center thereof being moved and urged in one slide direction. Thus, the ratchet 10 is held in a state of being pressed and meshed with the inner peripheral tooth surface 12a. Then, when the hinge cam 50 is rotated against the urging force, the slide cam 40 is pushed and moved in the other slide direction, and the respective pawls 30 are pulled inward in the radial direction to engage with the ratchet 10. It is supposed to be removed from the state.

  By the way, when each of the above-described poles 30 is in a state where the rotation position of the ratchet 10 with respect to the guide 20 is in a state where the riding surface 12b is located at the position to which any of the poles 30 is moved, the locking movement is performed. It is blocked by climbing onto the door and cannot be locked. Specifically, when any one of the above-mentioned poles 30 rides on the riding surface 12b, the movement of the slide cam 40 that applies a pressing force in the pushing direction to each pole 30 is stopped. Thereby, the locking operation of the other pole 30 is also stopped, and the reclining device 5 is kept in the unlocked state. Thus, in the rotation angle region where the above-described riding surface 12b interferes with any one of the poles 30, the locking operation of the reclining device 5 is prevented, and the reclining device 5 is kept in the unlocked state. This rotation angle region is set as the rotation angle region constituting the above-described free zone. Further, the reclining device 5 is returned to the locked state in the rotation angle region in which each of the poles 30 can mesh with the inner peripheral tooth surface 12a of the ratchet 10 without the ride surface 12b interfering with any of the poles 30. It is set as a lock zone.

  The hinge cam 50 is inserted into a round hole 25 formed in the center portion of the guide 20 described above and is pivotally supported so as to protrude in the axial direction and the outer peripheral portion of the shaft portion. The formed operation protrusion 52 is set in a state of being fitted into a through hole 41 formed through the central portion of the slide cam 40. Specifically, the hinge cam 50 is set in a state in which the operation projection 52 is inserted into the operation hole 41 a that is formed in a part of the peripheral edge in the through hole 41 of the slide cam 40. An inner end 61 of a spiral spring 60 is hooked on a rectangular tubular spring hooking portion 51 protruding in the axial direction of the hinge cam 50. Thus, the hinge cam 50 is configured to be applied with a rotational urging force by the spiral spring 60 hooked between the hinge cam 50 and the guide 20.

  The hinge cam 50 is normally urged in one rotational direction with respect to the guide 20 by the urging force of the spiral spring 60, and is attached to the slide cam 40 via the operation projection 52 described above. A rotational biasing force in the same direction is applied. Here, on the hinge cam 50, the operation shaft member 5A is inserted into the axial center portion thereof in an axial direction so as to be integrally coupled in the rotation direction. As a result, as shown in FIG. 4, the hinge cam 50 is rotated in a direction against the urging force of the spiral spring 60 as the release lever 5C is pulled up, and the slide cam 40 is reclined. The device 5 is operated to release the lock.

  As shown in FIG. 3, the outer peripheral ring 70 is formed by punching a thin steel plate into a ring shape, and further punching out the punched disk portion into a step shape in the plate thickness direction (axial direction). A ring-shaped first seat surface portion 71 and a second seat surface portion 72 having a surface facing in the axial direction are formed in a cylindrical shape with a seat, which is formed side by side in a step shape in the axial direction. A cylindrical portion 73 protruding in a cylindrical shape in the axial direction is formed on the outer peripheral portion of the outer peripheral ring 70.

  The outer peripheral ring 70 has the ratchet 10 and the guide 20 assembled in order inside the cylinder, so that the cylindrical portion 12 of the ratchet 10 is assigned from the outside in the axial direction by the first seat surface portion 71 described above. The cylindrical portion 22 of the guide 20 is covered with the cylindrical portion 73 from the outer peripheral side, with the cylindrical portion 22 of the guide 20 being applied from the inner side in the axial direction by the two seating surface portions 72. Then, after this assembly, the tip of the cylindrical portion 73 (caulking portion 73a) of the outer peripheral ring 70 is bent inward in the radial direction, and the cylindrical portion 22 of the guide 20 is axially interposed between the second seating surface portion 72 and the second seating surface portion 72. By crimping so as to be sandwiched, the outer peripheral ring 70 is assembled in a state of being integrally coupled to the cylindrical portion 22 of the guide 20. By this assembly, the outer peripheral ring 70 is in a state in which the ratchet 10 and the guide 20 are assembled in the axial direction, with the first seat surface portion 71 holding the ratchet 10 so as not to be detached from the guide 20 in the axial direction. It comes to hold.

  The above is the basic structure of the reclining device 5. The reclining device 5 described above can rotate the second link member 6B with respect to the seat cushion 3 (base plate 3F2) by the structure in which the ratchet 10 and the guide 20 are assembled so as to be rotatably supported relative to each other. It is the structure which functions as a rotating shaft apparatus pivotally supported by. In addition, the reclining device 5 has an angular pitch at which the rotation can be stopped twice by the mutual meshing pitch set between the inner peripheral tooth surface 12a of the ratchet 10 and the outer peripheral tooth surface 30a of each pole 30 described above. Is set. Accordingly, the rotational movement of the second link member 6B with respect to the seat cushion frame 3F can be stopped at a pitch of 2 degrees.

  As described above, according to the configuration of the vehicle seat 1 of the present embodiment, the reclining device 5 that functions as a rotation shaft device capable of stopping rotation is disposed below the seat cushion 3 that moves in conjunction with the tilting rotation of the seat back 2. The reclining device 5 can be provided so as not to overhang the upper portion of the seat cushion 3 by adopting a configuration in which any joint portion (the connecting shaft 6P2) of the provided link mechanism 6 is set. Therefore, even if the seat width of the vehicle seat 1 is reduced, the reclining device 5 can be prevented from interfering with the seated occupant. In other words, the link mechanism 6 is connected to the lower part of the seat back 2 and the reclining device 5 is set to any joint part of the link mechanism 6, so that the central axis (linkage) of the tilting rotation of the seat back 2 is established. Even if the setting position of the shaft 6P1) is not lowered or the like, even if the setting position of the reclining device 5 is changed and the lateral width of the seat back 2 is reduced, the reclining device 5 does not interfere with the seated occupant. Can do.

  Further, the link mechanism 6 is constituted by a four-joint link mechanism in which the seat cushion frame 3F is a fixed link (fourth link member 6D), and the reclining device 5 is composed of the fixed link (fourth link member 6D) and the second link member. By adopting a configuration in which it is set at the joint with 6B (as the connecting shaft 6P2), the reclining device 5 can be set at a fixed position where the position does not change even if the seat back 2 tilts. Accordingly, various parts related to the release lever 5C for operating the reclining device 5 and the operation shaft member 5A can be set at fixed positions with respect to the seat cushion frame 3F, and the link mechanism 6 is compact with a small operating space. And a configuration capable of obtaining stable operability.

  In addition, since the link mechanism 6 is arranged at the central portion in the seat width direction, the seat width of the vehicle seat 1 can be more easily narrowed. Moreover, the link length of the 3rd link member 6C is set short by having set the connection position of 2nd link member 6B and 4th link member 6D (base board 3F2) in the location near the rear part of the seat cushion 3. FIG. It is possible to make the link mechanism 6 compact and to have a high structural strength.

  As mentioned above, although the embodiment of the present invention has been described using one example, the present invention can be implemented in various forms in addition to the above example. For example, as shown in FIG. 10, the configuration of the present invention can also be applied to a configuration in which the seat body 1 </ b> A is flipped up to the vehicle side via the link mechanism 6 to be in the retracted state. Specifically, the link mechanism 6 is provided integrally with the seat body 1A and is rotatably connected to the floor by a connecting shaft 6P1 and connected to the floor by a connecting shaft 6P2. The second link member 6B is axially connected, the third link member 6C is rotatably connected to the first link member 6A and the second link member 6B by connection shafts 6P3 and 6P4, respectively, and the floor itself. A fourth link member 6D serving as a fixed link. The seat body 1A is hinged to the floor so as to be rotatable around the connecting shaft 6P1, and is normally locked at a use position on the floor. A spiral spring 7 is applied to the connecting portion between the second link member 6B and the fourth link member 6D. The spiral spring 7 applies a biasing force to the link mechanism 6 in the rotational direction in which the seat body 1A is raised. As a result, the seat main body 1A is released from the locked state with respect to the floor, so that the seat main body 1A is raised from the floor by the urging force of the spiral spring 7 and is flipped up to the side of the vehicle and stored. It is like that.

  Further, as shown in FIG. 11, the configuration of the present invention can also be applied to a configuration in which the seat body 1 </ b> A is flipped up forward of the vehicle via the link mechanism 6 to be in the retracted state. Specifically, the link mechanism 6 is provided integrally with the seat body 1A and is rotatably connected to the floor by a connecting shaft 6P1 and connected to the floor by a connecting shaft 6P2. The second link member 6B is axially connected, the third link member 6C is rotatably connected to the first link member 6A and the second link member 6B by connection shafts 6P3 and 6P4, respectively, and the floor itself. A fourth link member 6D serving as a fixed link. The seat body 1A is hinged to the floor so as to be rotatable around the connecting shaft 6P1, and is normally locked at a use position on the floor. A spiral spring 7 is applied to the connecting portion between the second link member 6B and the fourth link member 6D. The spiral spring 7 applies a biasing force to the link mechanism 6 in the rotational direction in which the seat body 1A is raised. As a result, when the seat body 1A is unlocked from the floor, the seat body 1A is lifted from the floor by the urging force of the spiral spring 7 and is pushed up and stored in front of the vehicle. It has become.

  Moreover, in the said Example, although the reclining apparatus 5 illustrated the structure set as the joint part (as connection shaft 6P2) to which the 2nd link member 6B and 4th link member 6D of the link mechanism 6 were connected, It is set to the joint part where the second link member 6B and the third link member 6C are connected (as the connecting shaft 6P3), or the joint part where the third link member 6C and the first link member 6A are connected (connected) It may be configured to be set as the axis 6P4.

  Moreover, in the said Example, although the link mechanism 6 and the reclining apparatus 5 illustrated the structure provided in one center of the width direction in the vehicle seat 1, the structure which arranged these two or more side by side in the center is arranged. It is good also as a structure each arrange | positioned to both side parts. The same applies to the spiral spring (spring). Further, the link mechanism may employ another link mechanism having a degree of freedom of 1 other than the four-bar link mechanism. In addition, the spring that urges the link mechanism to link and move in the direction in which the seat structure is lifted up is a spring that exerts a spring urging force in the direction (rotation direction) to return torsion, such as a spiral spring. A spring that exerts a spring biasing force in a linear direction, such as a compression spring, can also be used.

DESCRIPTION OF SYMBOLS 1 Vehicle seat 1A Seat body 2 Seat back (seat structure)
2F Seat back frame 2F1 Mounting plate 2Fa hole 2F2 U-shaped plate 2F3 Lower end bracket 2P Pad material 2P1 Wire 2P2 Mounting plate 2P3 Space 2B Bolt 2N Nut 2C Skin material 3 Seat cushion (base member)
3F Seat cushion frame 3F1 Mounting plate 3Fa hole 3F2 Base plate 3Fb Spring hook plate 3Fb Air hole 3F3 U-shaped plate 3Fd Stopper 3F4 Leg frame 3P Pad material 3P1 Wire 3P2 Mounting plate 3B Bolt 3N Nut 3C Skin material 4 Head material 4 Material 5 Reclining device 5A Operation shaft member 5C Release lever 6 Link mechanism 6A First link member 6B Second link member 6B1 Round hole 6B2 Spring hook plate 6C Third link member 6D Fourth link member 6P1 to 6P4 Connection shaft 7 Spiral spring ( Spring)
7A Spiral spring 8 Slide device 8A Lower rail 8A1 Leg frame 8B Upper rail 10 Ratchet 11 Disk part 12 Cylindrical part 12a Inner peripheral tooth surface 12b Raised surface 14 Round hole 20 Guide 21 Disk part 21a-21d Guide wall 22 Cylindrical part 23 Guide groove 23a Pole groove 23b Cam groove 24c Spring hook portion 25 Round hole 30 Pole 30a Outer peripheral tooth surface 31 Hook portion 32 Leg portion 40 Slide cam 41 Through hole 41a Operation hole portion 42 Shoulder portion 43 Groove portion 44 Hook 50 Hinge cam 51 Spring hook portion 52 Operation protrusion 60 spiral spring 61 inner end 62 outer end 70 outer peripheral ring 71 first seat surface portion 72 second seat surface portion 73 cylindrical portion 73a caulking portion θ1 to θ3 change angle γ1 to γ3 change angle L1 to L3 link length M1 to M3 link length P1 P3 transition curve

Claims (3)

A seat for a vehicle in which a seat structure is hinged to be raised and rotated with respect to a base member provided on a floor,
The base member is provided with a link mechanism that is connected to the seat structure and performs a link motion in conjunction with the raising rotation of the seat structure.
The link mechanism includes a first link member provided integrally with the seat structure, a second link member rotatably connected to the base member, the first link member, and the first link member. A four-link mechanism comprising a third link member that is axially connected to each of the two link members, and a fourth link member constituted by the base member;
A spring for urging the link mechanism to link and move in the direction in which the seat structure is raised up is set at a joint portion of the second link member or the third link member. Vehicle seat. The vehicle seat according to claim 1,
The vehicle seat according to claim 1, wherein the spring is set at a joint portion where the second link member and the fourth link member are axially connected. The vehicle seat according to claim 1 or 2,
A reclining device that stops the relative rotation between the link members and fixes the backrest angle of the seat back is disposed at a joint portion where the second link member and the fourth link member are axially connected. A vehicle seat characterized by the above.

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