JP2010148629A - Seat reclining device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a seat reclining device, obtained at a low cost, and having excellent stability and strength in the locked state. <P>SOLUTION: The seat reclining device includes: a base plate and a gear plate, which are fixed to one and the other of the seat cushion side and the seat back side, respectively, to be rotated relative to each other; a rotary cam supported to be rotatable around the center of rotation substantially aligned with the center of the relative rotation; at least one movable locking member capable of moving in the radial direction of rotation of the rotary cam and having an externally toothed gear provided at the outer peripheral part to mesh with an internally toothed gear formed on the gear plate; and at least two wedge members abutting on the movable locking member at two different positions in the peripheral direction and respectively pressed by the rotary cam to press the movable locking member to the gear meshing position. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a seat reclining device that makes it possible to adjust the angle of a seat back of a seat.

Various types of reclining devices of this type have been put to practical use, and a type called a reclining device is known as a device that is particularly suitable for a vehicle seat and is reduced in size and weight. As seen in Patent Document 1, the basic structure includes a base plate having a substantially circular space on one and the other of the seat cushion frame side and the seat back frame side, and an internal gear (an inner peripheral gear) facing the circular space. And a gear mechanism having a locking mechanism between the two plates. The lock mechanism has a movable lock member (hereinafter referred to as a pole) supported so as to be movable in the radial direction in the circular space of the base plate, and the outer edge of the pole is connected to the internal gear of the gear plate. A meshable external gear is formed. When the pole and the gear plate are engaged with each other, the relative rotation between the base plate and the gear plate is restricted, and the seat back angle is fixed. When the pawl is disengaged from the gear plate, relative rotation between the base plate and the gear plate is permitted, and the angle of the seat back can be adjusted. The pole is position-controlled by a rotating cam that can be operated via an external operating means, and is switched between a locked state that engages with the gear plate and an unlocked state that releases engagement.
JP 2006-38230 A

  In the round reclining device as described above, a guide surface for moving and guiding the pole in the radial direction (the meshing direction with the gear plate and the meshing release direction) is formed on the pace plate, and the pole pressed by the rotating cam is provided. It was moved along the guide surface. When forming this guide surface, high processing accuracy is required to prevent the pole from falling or rattling, which causes malfunction of the locking mechanism. Especially, the guide surface is mirror-finished to make the pole operate smoothly. As a result, the manufacturing cost was high.

  Moreover, in the conventional round reclining device, the cam member presses the substantially central position in the circumferential direction with respect to the pole having a predetermined length in the circumferential direction, and meshes with the gear plate. In this configuration, the pole is inclined at the time of gear engagement due to the clearance existing between the members, and the effective meshing portion of the pole with respect to the gear plate is specified in a region that is deviated in the front-rear direction, and uneven wear is likely to occur. There was a problem. Also, in terms of meshing stability and strength, it is desirable to prevent the pole from tilting and mesh with the gear plate in the widest possible range in the circumferential direction (to ensure a large effective meshing area).

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a seat reclining device that is obtained at low cost and is excellent in stability and strength in a locked state.

  The seat reclining device of the present invention includes a base plate and a gear plate that are fixed to one and the other of the seat cushion side and the seat back side, and a rotation center that substantially matches the relative rotation center of the base plate and the gear plate. A rotary cam that is rotatably supported, at least one movable lock member that has an outer gear that is movable in the radial direction of the rotary cam and that can mesh with an internal gear formed on the gear plate, It is characterized by comprising at least two wedge members that abut against the movable lock member at two different positions in the circumferential direction and are pressed by the rotating cam to press the movable lock member to the gear meshing position.

  The rotating cam is in a locked state in which the external gear of the movable lock member and the internal gear of the gear plate are engaged with each other, and faces the inner peripheral portion of the movable lock member with a predetermined clearance between the contact positions of the two wedge members. It is preferable to have a pressing surface that comes into contact with the inner peripheral portion of the movable lock member when the pole is displaced in the direction opposite to the pressing direction by the wedge member.

  In the present invention, the number and arrangement of the movable lock member and the wedge member can be arbitrarily set. For example, the plurality of movable lock members and the plurality of wedge members can be alternately arranged without any gap over the entire circumference of the rotating cam in the rotation direction. Alternatively, a plurality of movable lock members and a plurality of wedge guide portions fixedly formed on the base plate are alternately provided in the rotational direction of the rotary cam, and the plurality of wedge members are respectively disposed between the movable lock member and the wedge guide portions. An inserted configuration can also be adopted.

  According to the seat reclining device of the present invention described above, the movable lock member is held through the two wedge members that come into contact with each other at different positions in the circumferential direction. Therefore, the guide surface for accurately guiding the movable lock member is provided. It can be configured without being provided on the base plate, and the manufacturing cost can be reduced. In addition, since the movable lock member is held by the two wedge members from both sides, the movable lock member is unlikely to fall when engaged with the gear plate, and stability and strength in the locked state can be improved.

  The vehicle seat 10 shown in FIG. 1 has a seat back 12 supported on the rear portion of the seat cushion 11 via a reclining device 13 with respect to a seat cushion 11 supported on the floor surface side via a seat rail. It is connected so that it can tilt. As shown in FIG. 2, the reclining device 13 includes six poles (movable lock members) 16, six wedge members 17, one rotating cam 18, and 1 between the base plate 14 and the gear plate 15. The base plate 14 and the gear plate 15 are combined by the pressing ring 20 so as to be relatively rotatable. The base plate 14 is a fixing member to the seat cushion frame constituting the seat cushion 11, and the gear plate 15 is a fixing member to the seat back frame constituting the seat back 12. It should be noted that the present invention is established even if the arrangement relationship between the base plate 14 and the gear plate 15 is reversed. In the following, the reclining device 13 on one side of the seat 10 will be described, but it is also possible to provide similar reclining devices on both sides of the seat and to interlock these by a known interlocking mechanism.

  The base plate 14 is formed with a substantially circular lock mechanism accommodation recess 14a on the side facing the gear plate 15, and a shaft insertion hole 14b is formed through substantially the center of the lock mechanism accommodation recess 14a. The gear plate 15 has an annular flange portion 15a that is rotatably supported on the inner peripheral portion of the lock mechanism housing recess 14a, and an internal gear 15b is formed on the inner peripheral portion of the annular flange portion 15a. Yes. The inner side of the internal gear 15 b in the gear plate 15 is a circular recess 15 c that faces the base plate 14. The holding ring 20 sandwiches the annular flange portion 15a of the gear plate 15 and the outer edge portion of the base plate 14 so that the base plate 14 and the gear plate 15 are not separated in the direction along the center of rotation while allowing relative rotation. Combined. A center shaft 21 is inserted into the shaft insertion hole 14 b of the base plate 14, and the center shaft 21 is supported so as to be rotatable about an axis substantially coincident with the relative rotation center of the base plate 14 and the gear plate 15. The center shaft 21 can be rotated by a lock release handle 22 (FIG. 1) provided on the side portion of the seat 10. In the following description, “circumferential direction” and “radial direction (inner diameter direction, outer diameter direction)” mean directions around the center shaft 21.

  Between the lock mechanism housing recess 14a and the circular recess 15c, a lock mechanism for controlling restriction and allowance of relative rotation of the pace plate 14 and the gear plate 15 is disposed. As shown in FIG. 3, this locking mechanism has an all-around structure in which six poles 16 and six wedge members 17 are alternately arranged over the entire circumferential direction. A rotating cam 18 is located on the inner diameter side of the member 17.

  All six poles 16 have the same shape. As shown in FIG. 5, each pole 16 is a fan-shaped member having an outer peripheral portion facing the internal gear 15b of the gear plate 15 and an inner peripheral portion facing the rotary cam 18 side. The external gear 16a that can mesh with the internal gear 15b is formed, and the inner peripheral portion is formed with an inner diameter convex portion 16b that protrudes in the inner diameter direction. The inner diameter convex portion 16b has a top portion 16c that is a protruding end in the inner diameter direction, and a tapered surface 16d and a rotation restricting surface 16e that are located across the top portion 16c. Located in the approximate center of the direction. The tapered surface 16d is a surface having an inclination that gradually advances in the outer diameter direction (approaching the external gear 16a) as the distance from the top portion 16c increases, and the rotation restricting surface 16e extends substantially linearly in the radial direction. It is the surface that was made. A cam relief surface 16f located on the outer diameter side of the inner diameter convex portion 16b is formed on the inner peripheral portion of the pole 16 following the rotation restricting surface 16e. The cam relief surface 16 f is an arc-shaped surface that is substantially centered on the axis of the center shaft 21. The pole 16 also includes a pair of circumferential end surfaces 16g and 16h that connect the outer peripheral portion having the external gear 16a and the inner peripheral portion having the inner convex portion 16b, and between the one circumferential end surface 16g and the cam relief surface 16f. Is formed with a wedge contact convex portion 16i, and a wedge contact convex portion 16j is formed between the other circumferential end surface 16h and the tapered surface 16d. A guide protrusion 16k protrudes from one side of the pole 16 at a substantially central position in the circumferential direction, and a pair of rotation restricting protrusions 16m (see FIGS. 2 and 5) protrude from the other side. . The rotation restricting protrusion 16m engages with a rotation restricting groove (not shown in the figure) formed on the base plate 14, so that the pole 16 moves relative to the base plate 14 in the rotation direction around the axis of the center shaft 21. Movement is restricted. On the other hand, the pole 16 is allowed to move in the radial direction around the axis of the center shaft 21 with respect to the base plate 14.

  Similar to the pole 16, the six wedge members 17 all have the same shape. As shown in FIG. 6, the wedge member 17 has an outer diameter protruding portion 17a inserted between the circumferential end faces 16g and 16h of two adjacent poles 16, and is closer to the inner diameter side than the outer diameter protruding portion 17a. A pole pressing surface 17b that can contact the wedge contact convex portion 16j of the pole 16 and a pole pressing surface 17c that can contact the wedge contact convex portion 16i of the pole 16 are formed on both side portions. . The pole pressing surface 17b and the pole pressing surface 17c are tapered surfaces that are opposite to each other in the inclination direction so that the interval between the pole pressing surface 17b and the pole pressing surface 17c increases toward the inner diameter side away from the outer diameter protruding portion 17a. Further, a mountain-shaped cam contact convex portion 17d is formed on the innermost diameter side of the wedge member 17, and a cam contact tapered surface 17e is formed from the cam contact convex portion 17d toward the pole pressing surface 17b. Yes. Contrary to the pole pressing surface 17b, the cam contact taper surface 17e is an inclined surface that gradually approaches the pole pressing surface 17c as it advances toward the inner diameter side. A guide protrusion 17f protrudes from one side surface of the wedge member 17, and a rotation restricting protrusion 17g (see FIGS. 2 and 6) located substantially coaxially with the guide protrusion 17f protrudes from the other side surface. Yes. When the rotation restricting protrusion 17g engages with a rotation restricting groove (not shown in the figure) formed in the base plate 14, the wedge member 17 moves relative to the base plate 14 in the rotation direction about the axis of the center shaft 21. Movement is regulated. On the other hand, the wedge member 17 is allowed to move in the radial direction around the axis of the center shaft 21 with respect to the base plate 14.

  The rotary cam 18 is formed with a non-circular (oval-type) shaft fitting hole 18a at the center, and includes six wedge operation arms 18b that project radially toward the outer diameter direction. Each wedge operating arm 18b has a common shape. One side surface of the wedge operation arm 18b is a rotation restricting surface 18c extending substantially in the radial direction. The wedge operation arm 18b is further provided with a first tapered surface having a different inclination angle following the rotation restricting surface 18c. 18d and the 2nd taper surface 18e are formed. The first tapered surface 18d constitutes the outer diameter direction end of the wedge operating arm 18b, and is inclined so as to advance in the inner diameter direction (on the shaft fitting hole 18a side) as the distance from the rotation restricting surface 18c increases. The second tapered surface 18e is also an inclined surface in the same direction as the first tapered surface 18d, but the inclination angle of the rotating cam 18 with respect to the rotational direction is larger than that of the first tapered surface 18d. In other words, the second taper surface 18e is larger in the radial movement amount given to the contact object at the unit rotation angle of the rotary cam 18 than the first taper surface 18d. In addition, a total of six pole pressing surfaces 18f are formed on the outer peripheral portion of the rotating cam 18 in a region following the second tapered surface 18e of each wedge operating arm 18b. The pole pressing surface 18 f is an arcuate surface with the axis of the center shaft 21 as the center. In addition, a total of six pole escape recesses 18g are formed between the rotation restricting surface 18c of each wedge operating arm 18b and each pole pressing surface 18f, which are cut in the inner diameter direction from the pole pressing surface 18f. The six wedge operating arms 18b, the six pole pressing surfaces 18f, and the six pole escape recesses 18g are arranged at substantially equal intervals in the circumferential direction.

  As shown in FIG. 2, the center shaft 21 has a rotation transmitting portion 21a having a non-circular (oval) cross section that fits into the shaft fitting hole 18a, and the rotary cam 18 and the center shaft 21 are integrally rotated. The

  A pair of cylindrical bosses 18 h provided on the rotating cam 18 are fitted in the boss holes 19 a of the guide plate 19 (see FIGS. 3 and 4), and the rotating cam 18 rotates together with the guide plate 19. In the guide plate 19, six pole guide grooves 19b and wedge guide grooves 19c are alternately formed in the circumferential direction, and guide protrusions 16k provided on the pole 16 are inserted into the respective pole guide grooves 19b. A guide projection 17f provided on the wedge member 17 is inserted into each wedge guide groove 19c (see FIGS. 3 and 4). The pole 16 has a radial movement trajectory determined by sliding the guide protrusion 16k with respect to the pole guide groove 19b, and the wedge member 17 has a radial movement trajectory due to sliding of the guide protrusion 17f with respect to the wedge guide groove 19c. Determined.

  The combined body of the rotary cam 18, the guide plate 19 and the center shaft 21 is given a rotational biasing force in the direction indicated by the arrow F in FIGS. 2 to 4 and FIGS. Yes. This urging means is provided in an internal space formed by the lock mechanism housing concave portion 14a and the circular concave portion 15c and is engaged with the rotary cam 18, and is provided outside the internal space and is engaged with the center shaft 21. An arbitrary configuration such as an external spring can be used.

  The operation of the reclining device 13 having the above configuration will be described. In the locked state shown in FIG. 8, the six wedge members 17 have their cam contact projections 17d located on the most inner diameter side in contact with the first tapered surface 18d of the wedge operation arm 18b and are pressed in the outer diameter direction. It has been. Each of the six poles 16 is in a position where the external gear 16a meshes with the internal gear 15b of the gear plate 15, and each pole 16 is sandwiched from both sides by a pair of wedge members 17 located on both sides in the circumferential direction. Is retained. More specifically, the pole pressing surface 17b of the first wedge member 17 adjacent to the wedge abutting convex portion 16i located at one circumferential end of the inner peripheral portion of each pole 16 abuts the other. The pole pressing surface 17c of the second wedge member 17 adjacent thereto is in contact with the wedge contact convex portion 16j located at the circumferential end. That is, two wedge members 17 adjacent to each other in the circumferential direction are set, and the pole 16 positioned therebetween is directed from the both end positions of the inner peripheral portion (wedge abutting convex portions 16i, 16j) toward the outer diameter direction. Pressed. Then, the external gear 16a of the pole 16 whose movement in the rotation direction with respect to the base plate 14 is engaged with the internal gear 15b of the gear plate 15, whereby the relative rotation between the base plate 14 and the gear plate 15 is restricted. The seat back 12 is fixed at a certain angular position. This locked state is maintained by the urging means for urging the rotation cam 18 in the direction of arrow F.

  In the locked state of FIG. 8, the six pole pressing surfaces 18 f of the rotating cam 18 are opposed to the top 16 c of the inner diameter convex portion 16 b of the pole 16. When no special external force is applied to the locking mechanism, a clearance is secured between the pole pressing surface 18f and the top portion 16c, and each pole 16 is formed by a pair of wedge members 17 positioned at both ends in the circumferential direction. It is in a point support state. When a force that moves the pole 16 in the inner diameter direction against the pressing of the wedge member 17 is input, the top portion 16c comes into contact with the pole pressing surface 18f and becomes a third support location for the pole 16. . As described above, when the external force is applied, in addition to the holding by the pair of wedge members 17 on both sides, the rotation cam 18 directly supports the pole 18 at the intermediate position in the circumferential direction. The strength can be increased and the locked state can be reliably maintained.

  When the seated person tries to adjust the angle of the seat back 12, the unlocking handle 22 is operated to rotate in the unlocking direction G (shown in FIGS. 8 to 12) opposite to the biasing direction F of the biasing means. The combined body of the cam 18, the guide plate 19 and the center shaft 21 is rotated. 9 to 12 show the unlocking operation by the rotation operation in the unlocking direction G step by step. The reclining device 13 is provided with a play so that the locked state is maintained even if the rotational cam 18 is slightly changed in the unlocking direction from the position shown in FIG. The end position of the corner is shown. In FIG. 9, with the change in the angle of the rotary cam 18 in the unlocking direction G, the contact position of the wedge operating arm 18b with respect to each wedge member 17 changes, and the boundary between the first tapered surface 18d and the second tapered surface 18e. The vicinity comes off the cam contact convex portion 17d and comes into contact with the cam contact taper surface 17e. However, in the state of FIG. 9, the radial position of each wedge member 17 is hardly changed from the locked state of FIG. 8, and the pole 16 is held at a position where the external gear 16a meshes with the internal gear 15b. ing.

  When the rotating cam 18 and the guide plate 19 are rotated in the unlocking direction G beyond the end of the play angle, the contact position of the wedge operating arm 18b with respect to each wedge member 17 changes as shown in FIG. The vicinity of the boundary between the first taper surface 18d and the second taper surface 18e gradually moves away from the cam contact convex portion 17d while maintaining contact with the cam contact taper surface 17e. Each of the six wedge members 17 is moved in the inner diameter direction by the contact position change with respect to the rotating cam 18 and the guide of the wedge guide groove 19 c of the guide plate 19 that rotates together with the rotating cam 18. When the wedge member 17 moves to the inner diameter side, movement of the poles 16 held by the pair of wedge members 17 at both circumferential positions is allowed in the inner diameter direction. Each pole 16 is guided by the pole guide groove 19b of the guide plate 19 and starts moving in the inner diameter direction. That is, the meshing release of the external gear 16a and the internal gear 15b starts.

  When the rotating cam 18 and the guide plate 19 are further rotated in the unlocking direction G from the start of meshing release in FIG. 10, as shown in FIG. 11, the end of the cam contact taper surface 17e (on the side closer to the pole pressing surface 17b). The positional relationship between the wedge operating arm 18b and the wedge member 17 changes so that the vicinity of the end portion is supported by the second tapered surface 18e. In other words, each of the six wedge operating arms 18b of the rotary cam 18 is displaced in a direction away from the corresponding wedge member 17. Each wedge member 17 is further moved in the inner diameter direction by the change of the contact position with respect to the rotating cam 18 and the guide of the wedge guide groove 19c of the guide plate 19. As a result, the pressure applied to each pole 16 by each wedge member 17 in the outer diameter direction is also released, the pole 16 moves in the inner diameter direction while being guided by the pole guide groove 19b, and the external gear 16a moves inside the gear plate 15. The meshing with the tooth gear 15b is released. At this time, the part of the rotating cam 18 that faces the top 16c of the pole 16 has changed from the pole holding surface 18f in the locked state to the pole relief recess 18g, and the inner diameter projection 16b enters the pole relief recess 18g. By doing so, the movement of the pole 16 in the inner diameter direction is not hindered. Further, since the wedge operating arm 18b enters the concave space where the cam relief surface 16f faces the pole 16, there is no interference between the wedge operating arm 18b and the pole 16.

  When the rotating cam 18 and the guide plate 19 are rotated in the unlocking direction G until the fully open state of FIG. 12, the six poles 16 and the six wedge members 17 are guided to the pole guide groove 19b and the wedge guide groove 19c, respectively. Then, it further moves in the inner diameter direction, and the meshing of the external gear 16a and the internal gear 15b is completely released. Then, the rotation restricting surface 18c of each wedge operating arm 18b comes into contact with the rotation restricting surface 16e of the pole 16, so that the rotation of the rotating cam 18 in the unlocking direction G is restricted. In this fully open state, the inner diameter convex portion 16b of the pole 16 enters the pole relief recess 18g, and the wedge operating arm 18b is located at a position where the first taper surface 18d is close to the cam relief surface 16f with respect to the pole 16. It is settled. Each wedge member 17 is held in a state in which the cam contact convex portion 17 d is in contact with the pole pressing surface 18 f of the rotating cam 18.

  In this fully open state, relative rotation of the base plate 14 and the gear plate 15 is allowed, and the seat back 12 can be adjusted to an arbitrary angular position. After the angle adjustment is completed, the unlocking operation on the unlocking handle 22 is released. Then, the combined body of the rotary cam 18, the guide plate 19 and the center shaft 21 is rotated in the biasing direction F by the biasing force of the biasing means, and the six wedge operating arms 18b provided on the rotary cam 18 are six wedge members. 17 is pressed in the outer diameter direction, and the pole 16 is pushed into the meshing position with the internal gear 15b of the gear plate 15 via each wedge member 17 to return to the locked state of FIG.

  As described above, in the reclining device 13 of the present embodiment, the rotating cam 18 presses a plurality of (six) wedge members 17 in the outer diameter direction, and the plurality of wedge members 17 form a pair. Further, different positions (both end positions) in the circumferential direction of the inner peripheral portion of the pole 16 are pressed while being sandwiched and held at the meshing position with the gear plate 15. With this configuration, it is not necessary to provide the base plate 14 with a guide surface for precisely controlling the position of the pole 16, and it is more expensive and time-consuming than the conventional apparatus that has been expensive to manufacture (especially mirror finishing). As a result, the effects of cost reduction and productivity improvement can be obtained.

  In addition, the configuration in which the circumferential ends of the pole 16 are held by the two wedge members 17 has an effect of suppressing the inclination of the pole 16 in the meshed state with the gear plate 15. When the pawl 16 is engaged with the gear plate 15, unlike the present embodiment, the center of the pawl 16 in the circumferential direction can be pressed by the rotating cam 18 in the outer diameter direction. In this case, since it is difficult to precisely mesh the entire area of the internal gear 15b and the external gear 16a due to the clearance between the members, the pole 16 pressed at the center portion is inclined and the effective gear is effective. The meshing region tends to concentrate near one end in the circumferential direction, causing uneven wear of the gear. On the other hand, in the configuration in which the pole 16 is uniformly pressed from both ends in the circumferential direction by the two wedge members 17 as in the present embodiment, the inclination of the pole 16 hardly occurs, and the external gear 16a is effective against the internal gear 15b. The meshing area can be widened (the gear can be used effectively). As a result, the stability and support strength of the pole 16 in the locked state are improved, and it is possible to obtain excellent operation accuracy by preventing uneven wear of the gear.

  In addition, as described above, when an external force is applied to displace the pole 16 in the inner diameter direction in the locked state, in addition to the wedge members 17 on both sides, the pole pressing surface 18f of the rotating cam 18 causes the circumferential direction. The top portion 16c of the inner diameter convex portion 16b located at the center is in contact with and supported. A small clearance is provided between the pole pressing surface 18f and the top portion 16c by design so that the abutting support by the pole pressing surface 18f does not occur in a normal locked state. It is difficult to always support each pole 16 at three points in consideration of variations in individual component accuracy. Therefore, in a normal locked state with a small load, the structure is reinforced with support by the pole pressing surface 18f only in a state where a load is applied, based on the two-point holding by the two wedge members 17. Thus, the lock mechanism is easy to manage the accuracy of the holding portion of the pole 16 and excellent in durability.

  In the reclining device 13 described above, the six poles 16 and the six wedge members 17 are alternately arranged over the entire region in the circumferential direction. It is also possible to use a type that is not arranged all around. In the second embodiment shown in FIGS. 13 and 14, the number of poles 16 is three, and three wedge guide portions 25 are fixedly formed as a part of the base plate 14 between the three poles 16. Has been. Each wedge guide portion 25 is configured as a fan-like convex portion similar to the pole 16 except that it does not have the external gear 16a and the inner diameter convex portion 16b, and faces the circumferential end faces 16g and 16h of the pole 16. A pair of circumferential end faces 25a and 25b is provided, and a pair of wedge abutment protrusions 25c and 25d are provided on the inner diameter side of the circumferential end faces 25a and 25b. The wedge abutment protrusions 25c and 25d abut the pole pressing surfaces 17b and 17c of the two adjacent wedge members 17 in the locked state, and stably hold the respective wedge members 17 between the poles 16. It has a function to make it. 13 and 14, the configuration excluding these three wedge guide portions 25 is the same as that of the previous embodiment, and each of the three poles 16 is held by two wedge members 17 at both ends in the circumferential direction. Yes.

  As mentioned above, although demonstrated based on illustration embodiment, this invention is not limited to this embodiment, It is possible to set it as a different structure unless it deviates from the main point of invention. For example, in consideration of stability and strength at the time of locking, it is preferable to provide three or more poles with different circumferential positions as in the previous embodiments, but the lock constituting the reclining device of the present invention The mechanism is formed by at least one pole (movable lock member) and two wedge members, and the arrangement and number thereof are not limited to those shown in the illustrated embodiment.

It is a side view of a vehicular seat provided with a seat reclining device to which the present invention is applied. It is a disassembled perspective view of a seat reclining device. FIG. 3 is a side view of the seat reclining device in a state where a gear plate and a guide plate are removed, as viewed from the direction of arrow A in FIG. 2. FIG. 3 is a side view of the seat reclining device with the gear plate removed, as viewed from the direction of arrow A in FIG. 2. It is the single-piece | unit top view of the pole seen from the arrow B direction of FIG. It is the single-piece | unit top view of the wedge member seen from the arrow B direction of FIG. FIG. 3 is a single plan view showing a part of a rotating cam viewed from the direction of arrow B in FIG. 2. FIG. 3 is a side view showing a main part of the seat reclining device in a locked state as seen from the direction of arrow B in FIG. 2. FIG. 9 is a side view showing a state in which the rotating cam and the guide plate are rotated in the unlocking direction from the locked state of FIG. 8 to the end of the play angle. FIG. 10 is a side view showing a state in which the rotation cam and the guide plate are further rotated in the unlocking direction from the state of FIG. 9 and the meshing release of the pole and the gear plate is started. FIG. 11 is a side view showing a state in which the rotation cam and the guide plate are further rotated in the unlocking direction from the state of FIG. 10 and the engagement between the pole and the gear plate is released. FIG. 12 is a side view showing a state in which the rotating cam and the guide plate are further rotated in the unlocking direction from the state of FIG. 11 to reach the full open position (lock releasing position). It is a side view of a reclining device showing a different embodiment of the present invention. It is the side view to which the principal part of the reclining apparatus of FIG. 13 was expanded.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Vehicle seat 11 Seat cushion 12 Seat back 13 Reclining device 14 Base plate 15 Gear plate 15b Internal gear 16 Pole (movable lock member)
16a External gear 16b Inner diameter convex portion 16c Inner diameter convex portion top portion 16e Rotation restricting surface 16f Cam relief surface 16g 16h Circumferential end surface 16i 16j Wedge abutting convex portion 16k Guide protrusion 16m Rotation restricting projection 17 Wedge member 17b 17c Pole pressing surface 17d Cam contact convex portion 17e Cam contact taper surface 17f Guide projection 17g Rotation restriction projection 18 Rotation cam 18b Wedge operation arm 18c Rotation restriction surface 18d First taper surface 18e Second taper surface 18f Pole holding surface 19 Guide plate 19b Pole guide groove 19c Wedge guide groove 20 Holding ring 21 Center shaft 22 Unlocking handle 25 Wedge guide portion 25a 25b Circumferential end face 25c 25d Wedge abutting convex portion F Energizing direction by the energizing means G Unlocking direction

Claims (4)

A base plate and a gear plate that are relatively rotatable and fixed to one and the other of the seat cushion side and the seat back side;
A rotating cam supported rotatably at a rotation center substantially coincident with a relative rotation center of the base plate and the gear plate;
At least one movable locking member having an outer gear on the outer peripheral portion, which is movable in a rotational radius direction of the rotating cam and meshable with an inner gear formed on the gear plate; and circumferential direction with respect to the movable locking member At least two wedge members that are in contact with each other at two different positions and are pressed by the rotating cam to press the movable lock member to the gear meshing position;
A seat reclining device comprising: 2. The seat reclining device according to claim 1, wherein the rotary cam is movable between the contact positions of the two wedge members in a locked state in which the external gear of the movable lock member meshes with the internal gear of the gear plate. It has a pressing surface that faces the inner peripheral portion of the lock member with a predetermined clearance and contacts the inner peripheral portion of the movable lock member when the movable lock member is displaced in a direction opposite to the pressing direction by the wedge member. Seat reclining device. 3. The seat reclining device according to claim 1, wherein the plurality of movable lock members and the plurality of wedge members are alternately arranged over the entire circumference in the rotation direction of the rotary cam. apparatus. 3. The seat reclining device according to claim 1, wherein a plurality of the movable lock members and a plurality of wedge guide portions fixedly formed on the base plate are alternately provided in a rotation direction of the rotating cam, A seat reclining device, wherein each wedge member is inserted between a movable lock member and a wedge guide portion.

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