JP2006334284A - Reclining device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reclining device preventing the skipping of a wedge-shaped member. <P>SOLUTION: A rubber (a braking member) 40 decelerating the moving speed of a forehead wedge-shaped member by abutting on the forehead wedge-shaped member out of a wedge-shaped member (a first wedge-shaped member) 35 and a wedge-shaped member (a second wedge-shaped member) 36 moved by being pushed by a flange part (cam) 33c of a rotating shaft 33 is disposed between the internal circumferential face of a bush 34 and the outer circumferential face of a cylindrical part 31f of an externally toothed gear 31 and in a space between the side end face 35c of the wedge-shaped member (the first wedge-shaped member) 35 and the side end face 36c of the wedge-shaped member (the second wedge-shaped member) 36. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  In the present invention, external teeth are formed on the outer peripheral surface, and the external gear provided on one member of the seat cushion side member and the seat back side member is engaged with the external teeth of the external gear. The internal teeth having a larger number of teeth than the external teeth are engraved, and the internal gear provided on the other member of the seat cushion side member and the seat back side member, the internal gear, A cylindrical portion formed at the center of one gear of the external gear and extending toward the other; a through hole formed at the center of the other gear of the internal gear and the external gear and through which the cylindrical portion is inserted; A space between the outer peripheral surface of the cylindrical portion and the first wedge-shaped member provided in a space between the inner peripheral surface of the through-hole and the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through-hole. And external teeth of the external gear in cooperation with the first wedge-shaped member. The second wedge-shaped member that holds the meshing of the internal teeth of the internal gear, the first wedge-shaped member, and the second wedge-shaped member are engaged, and the internal teeth of the internal gear and the external gear An urging member for urging the first wedge-shaped member and the second wedge-shaped member in a direction in which the external teeth mesh with each other, and one wedge-shaped member among the first wedge-shaped member and the second wedge-shaped member. Pushing against the urging force of the urging means to move the first wedge-shaped member and the second wedge-shaped member, the meshing position of the external teeth of the external gear and the internal teeth of the internal gear is determined. The present invention relates to a reclining device having a striker for changing.

  As an example of a conventional reclining device, a reclining device shown in FIGS. 12 to 14 will be described. 12 is an exploded perspective view of the main part of the reclining device, FIG. 13 is an axial sectional view of the rotating shaft of FIG. 12, and FIG. 14 is a left side view of FIG.

The lower arm 1010 is fixed to a frame (not shown) of the seat cushion with a bolt or the like.
The upper arm 1020 is fixed to a seat back frame (not shown) by bolts or the like. The lower arm 1010 itself may be a seat cushion frame, and the upper arm 1020 itself may be a seat back frame.

  The gear mechanism 1030 is mounted between the lower arm 1010 and the upper arm 1020 and adjusts the inclination angle of the upper arm 1020. The lower arm 1010 is fitted to the external gear 1031 and the internal gear 1032 in the gear mechanism 1030. A plurality of cylindrical protrusions 1031a and 1032a are provided to be fitted into the holes and the fitting holes of the upper arm 1020.

The external gear 1031 has a substantially disk shape, an external tooth 1031b is formed on the outer peripheral surface, and a cylindrical portion 1031f is formed in the center.
The internal gear 1032 also has a substantially disk shape. The internal gear 1032 is engraved with internal teeth 1032b that are inscribed in the external teeth 1031b and are formed with at least one more tooth than the external teeth 1031b of the external gear 1031. A circular through hole 1032f is formed in the center of the internal gear 1032.

  A cylindrical portion 1033a of a cylindrical rotary shaft 1033 with a flange is rotatably fitted in the cylindrical portion 1031f of the external gear 1031. An arcuate cutout portion 1033c is formed in the flange portion 1033b of the rotary shaft 1033. The rotating shaft 1033 is rotationally driven when adjusting the inclination angle of the seat back, and in order to receive this rotational force, a serration for connection is cut on the inner peripheral surface of the cylindrical portion 1033a.

  Further, a cylindrical bush 1034 having excellent wear resistance is fitted and fixed in the through hole 1032f of the internal gear 1032. Furthermore, a pair of wedge-shaped members 1035 and 1036 are inserted between the inner peripheral surface of the bush 1034 and the outer peripheral surface of the cylindrical portion 1031f of the external gear 1031 so as to be in contact with both.

  The wedge-shaped members 1035 and 1036 have a plane-symmetric shape, and the wedge-shaped member 1035, the inner peripheral surface 1035a of the wedge-shaped member 1036, and the inner peripheral surface 1036a have an inner diameter that is substantially the same as the outer diameter of the cylindrical portion 1031f of the external gear 1031. The wedge-shaped member 1035, the outer peripheral surface 1035b of the wedge-shaped member 1036, and the outer peripheral surface 1036b have an outer diameter substantially the same as the inner diameter of the bush 1034. The wedge-shaped member 1035, the inner peripheral surface 1035a of the wedge-shaped member 1036, the inner peripheral surface 1036a and the outer peripheral surface 1035b, and the outer peripheral surface 1036b are changed in a wedge shape because their center axes do not coincide with each other.

  When the rotating shaft 1033 rotates counterclockwise in FIG. 14, the side wall 1033g of the notch 1033c of the rotating shaft 1033 contacts the side end surface 1035g of the wedge-shaped member 1035, and conversely, the rotating shaft 1033 in FIG. When rotated in the clockwise direction, the side end face 1033h of the rotary shaft 1033 comes into contact with the side end face 1036g of the wedge-shaped member 1036 on the opposite side.

  The wedge-shaped members 1035 and 1036 are disposed between the inner peripheral surface of the bush 1034 and the outer peripheral surface of the cylindrical portion 1031f of the external gear 1031 so that the thick-wall side faces each other. The center teeth 1032 are eccentric and the outer teeth 1031b are engaged with the inner teeth 1032b. As described later, the wedge-shaped members 1035 and 1036 cause the rotary shaft 1033 to mesh the internal teeth 1032b and the external teeth 1031b, so that either the external gear 1031 or the internal gear 1032 is centered on the other gear axis. It can be revolved. The wedge-shaped members 1035 and 1036 are separated from the spring 1037, in other words, the force in the direction in which the wedges are driven into the both wedge-shaped members 1035 and 1036. In other words, the internal teeth 1032b of the internal gear 1032 and the external gears. The urging force in the direction in which the external teeth 1031b of the 1031 mesh is received.

  The spring 1037 includes a one-turn annular portion 1037a and end portions 1037b and 1037c rising from the annular portion 1037a. The annular portion 1037a is an annular space continuously provided inside the recess 1031c of the external gear 1031. It is stored inside. Further, the end portion 1037b is engaged with a groove portion 1035d formed on the thick side end surface of the wedge-shaped member 1035, and the end portion 1037c is engaged with a groove portion 1036d formed on the thick side end surface of the wedge-shaped member 1036. It is locked.

  The cylindrical pressing member 1038 is fitted to the outer peripheral surface of the internal gear 1032, and both ends of the cylindrical pressing member 1038 protrude toward the central axis, and sandwich the external gear 1031 and the internal gear 1032. Thereby, it can control that the external gear 1031 and the internal gear 1032 leave | separate in an axial direction. An annular groove 1033d is cut at the tip of the rotary shaft 1033, and a retaining ring 1039 is locked there.

  Next, the operation of the above embodiment will be described. In a state where no rotational operation force is applied to the rotary shaft 1033 from the outside, the spring 1037 biases the wedge-shaped members 1035 and 1036 away from each other and applies a force in a direction in which the wedges are driven into the wedge-shaped members 1035 and 1036. . For this reason, relative movement between the internal gear 1032 and the rotating shaft 1033 is prohibited, the gear mechanism 1030 is in a locked state, and the seat back is locked in that position.

  When the rotating shaft 1033 is rotated clockwise in FIG. 14 in this locked state, the side end face 1033h of the rotating shaft 1033 presses the side end face 1036g of the wedge-shaped member 1036. Then, a force in the direction of pulling out the wedge-shaped member 1036 from the gap acts on the wedge-shaped member 1036, and the rotary shaft 1033 and the wedge-shaped member 1036 rotate in the clockwise direction with respect to the internal gear 1032. As a result, a gap is generated between the wedge-shaped member 1036 and the peripheral member, and the internal gear 1032 can move. Then, the wedge-shaped member 1035 receiving the urging force of the spring 1037 rotates in the clockwise direction so as to fill this gap.

  By this interlocking operation, the wedge-shaped members 1036 and 1035 rotate in the clockwise direction together with the rotating shaft 1033. The same applies to the counterclockwise rotation. Therefore, the internal gear 1032 is supported by the rotary shaft 1033 at an eccentric position where the internal teeth 1032b mesh with the external teeth 1031b, and the external gear 1031, the internal gear 1032 and the rotary shaft 1033 constitute a gear mechanism. Will be.

Thus, by rotating the rotary shaft 1033, the upper arm 1020 can be tilted with respect to the lower arm 1010, and the inclination angle of the seat back can be adjusted (see, for example, cited document 1).
JP 2002-112848 A (3rd page, 4th page, FIG. 1, FIG. 2, FIG. 4)

When an occupant is seated on the seat and the back of the occupant presses the seat back, a load in the direction of arrow F acts on the climbing device as shown in FIG.
FIG. 15 shows a case where the reclining device operates in a state where such a load in the F direction is applied. FIG. 15A shows the reclining device in the locked state. In this state, a load in the direction of arrow F acts on the wedge-shaped member 1035 via the bush 1034.

  (A) When the rotary shaft 1033 is turned from the locked state shown in the figure (clockwise in this figure), the wedge-shaped members 1035 and 1036 are rotated together with the rotary shaft 1033 as shown in FIGS. Rotate in the direction.

Here, in the state shown in FIG. 5B, a load in the direction of arrow F acts on the wedge-shaped member 1035 via the bush 1034, and therefore a large frictional resistance force acts on the wedge-shaped member 1035.
However, when the wedge-shaped member 1035 moves to the state shown in FIG. 5C, the counterpart to which the frictional resistance force due to the load F acts becomes the wedge-shaped member 1036 from the wedge-shaped member 1035. Then, the wedge-shaped member 1035 in which a large frictional resistance force is no longer applied moves greatly at a stroke as shown in FIG. 4D due to the urging force of the spring 1037 (this phenomenon is hereinafter referred to as skipping of the wedge-shaped member).

  When the wedge-shaped member skips, the reclining speed changes abruptly, giving the seated person discomfort. When the reclining device is driven by a motor, there is a problem in that the load on the motor changes abruptly and a motor noise is generated.

  The present invention has been made in view of the above problems, and an object thereof is to provide a reclining device that does not cause skipping of a wedge-shaped member.

  The invention according to claim 1, which solves the above problem, has external teeth formed on the outer peripheral surface, and an external gear provided on one of the seat cushion side member and the seat back side member, Internal teeth that mesh with the external teeth of the external gear and have internal teeth with a larger number of teeth than the external teeth, and are provided on the other member of the seat cushion side member and the seat back side member Formed at the center of one gear of the gear, the internal gear and the external gear and extending toward the other; and formed at the center of the other gear of the internal gear and the external gear; A first wedge-shaped member movably provided in a space between the through hole through which the cylindrical portion is inserted, the outer peripheral surface of the cylindrical portion, and the inner peripheral surface of the through hole; the outer peripheral surface of the cylindrical portion; The first wedge-shaped member is movably provided in a space between the inner peripheral surfaces of the holes. The second wedge-shaped member that holds the engagement between the external teeth of the external gear and the internal teeth of the internal gear in cooperation, the first wedge-shaped member, and the second wedge-shaped member are engaged, A biasing member that biases the first wedge-shaped member, the second wedge-shaped member in a direction in which the internal teeth of the toothed gear and the external teeth of the external gear mesh with each other, the first wedge-shaped member, the second One of the wedge-shaped members is pushed against the urging force of the urging means to move the first wedge-shaped member and the second wedge-shaped member, and the external teeth of the external gear and the In a reclining device having a striker that changes a meshing position with an internal tooth of an internal gear, the first wedge-shaped member that is moved by being pushed by the striker, and the leading wedge-shaped member among the second wedge-shaped members are applied. A braking member is provided to reduce the moving speed of the leading wedge member in contact therewith. It is reclining apparatus according to claim.

The braking member abuts on the leading wedge member of the first wedge member and the second wedge member that is moved by being pushed by the striker, and decelerates the moving speed of the leading wedge member.
The invention according to claim 2 is characterized in that the braking member is disposed in a space between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole, and the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole. The reclining device according to claim 1, wherein the reclining device is an elastic body that is pressed against each other.

  According to the first aspect of the present invention, the leading wedge-shaped member of the first wedge-shaped member and the second wedge-shaped member that are moved by being pushed by the striker comes into contact with each other, and the leading wedge-shaped member By providing the braking member that decelerates the moving speed, the skip of the first wedge-shaped member pushed by the striker and the leading wedge-shaped member of the second wedge-shaped member does not occur.

  According to the second aspect of the present invention, the braking member is disposed in a space between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole, thereby saving space. Further, since the elastic body is pressed against the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole, an optimum braking force can be obtained by changing the material, size, etc. of the elastic body.

  Embodiments of the present invention will be described below with reference to the drawings. 1 to 5, the lower arm 20 is a member on the seat cushion side, and as shown in FIG. 5, a seat back tilt center position (a portion intersecting with the seat back tilt center axis) in the lower arm 20. Around the periphery, a plurality (six) of fitting holes 21 are formed so as to be positioned on the same circumference.

  The upper arm 10 is a member on the seat back side, and as shown in FIG. 5, there are a plurality (6) of the upper arm 10 around the center position of the seat back tilt (the portion intersecting the tilt center axis of the seat back). ) Fitting holes 11 are formed so as to be located on the same circumference.

  As shown particularly in FIG. 1, the gear mechanism 30 is mounted between the upper arm 10 and the lower arm 20 and adjusts the inclination angle of the upper arm 10. The external gear 31 and the internal gear in the gear mechanism 30. A plurality of columnar protrusions 31 a and 32 a that are fitted into the fitting hole 11 of the upper arm 10 and the fitting hole 21 of the lower arm 20 are provided on the upper arm 32.

  As shown in FIG. 6, the external gear 31 has a substantially disk shape, an outer tooth 31 b is formed on the outer peripheral surface, and a cylindrical portion 31 f extending in the direction of the internal gear 32 is formed at the center. Yes. The external gear 31 is positioned by fitting a plurality (six) of protrusions 31 a formed on the side surface into the fitting hole 11 of the upper arm 10, and is welded to the upper arm 10 after this positioning.

  The internal gear 32 is also substantially disk-shaped as shown in FIG. The internal gear 32 is engraved with internal teeth 32b that are inscribed with the external teeth 31b and that have at least one more tooth than the external teeth 31b of the external gear 31. A circular through hole 32 f is formed in the center of the internal gear 32. The cylindrical portion 31f of the external gear 31 is inserted through the through hole 32f. The internal gear 32 is positioned by fitting a plurality (six) of cylindrical protrusions 32 a on the side surface into the fitting hole 21 of the lower arm 20, and is welded to the lower arm 20 after this positioning.

  Of the opposing surfaces of the external gear 31 and the internal gear 32, a concave portion 31c is formed on the opposing surface of the external gear 31 so that a substantially arc-shaped space is formed, and on the opposing surface of the internal gear 32, A protruding portion 32c protruding into the recessed portion 31c is formed. Since the internal gear 32 in the gear mechanism 30 adjusts the inclination angle of the seat back, the internal gear 32 naturally rotates with respect to the external gear 31, but it is necessary to limit the rotation range within a certain range. There is also. The concave portion 31c and the convex portion 32c function as the rotation regulating stopper, and the convex portion 32c is brought into contact with the side wall 31d of the concave portion 31c so that the rotation of the external gear 31 is within a certain range. It is regulated.

  A neck portion 33 a of a rotating shaft 33 with a flange as shown in FIG. 8 is rotatably fitted in the cylindrical portion 31 f of the external gear 31. The rotating shaft 33 is rotated by a flange portion (striker) 33b, a neck portion 33a, an annular groove 33d formed in the neck portion 33a, a first serration portion 33i to which the gear 100 shown in FIG. 1 is attached, and a rotating shaft of the reclining device on the other side. The 2nd serration part 33j to which the connection rod (not shown) which transmits is attached is formed. An arcuate cutout 33c is formed in the flange 33b. The rotary shaft 33 is rotationally driven when adjusting the inclination angle of the seat back.

  A cylindrical bush 34 having excellent wear resistance is fitted into and fixed to the through hole 32f of the internal gear 32. Further, a pair of wedge-shaped members (first wedge-shaped member) 35 and a wedge-shaped member (first wedge-shaped member) are provided between the inner peripheral surface of the bush 34 and the outer peripheral surface of the cylindrical portion 31f of the external gear 31 so as to be in contact with both. 2 wedge-shaped member) 36 is inserted.

  The wedge-shaped members 35 and 36 have a plane-symmetric shape, and the shape of the wedge-shaped member 35 is shown in FIGS. The wedge-shaped member 35, the inner peripheral surface 35a of the wedge-shaped member 36, and the inner peripheral surface 36a have substantially the same inner diameter as the outer peripheral surface of the cylindrical portion 31f of the external gear 31, and the wedge-shaped member 35, the outer peripheral surface 35b of the wedge-shaped member 36, The outer peripheral surface 36 b has an outer diameter that is substantially the same as the inner diameter of the bush 34. The wedge-shaped member 35, the inner peripheral surface 35a of the wedge-shaped member 36, the inner peripheral surface 36a and the outer peripheral surface 35b, and the outer peripheral surface 36b are changed in a wedge shape because their center axes do not coincide with each other.

Further, the wedge-shaped member 35 and the wedge-shaped member 36 are formed with a fin portion 35e and a fin portion 36e that can come into contact with the distal end surface of the cylindrical portion 31f of the external gear 31.
In this embodiment, the wedge-shaped member 35, the inner peripheral surface 35a of the wedge-shaped member 36, the outer peripheral surface of the cylindrical portion 31f of the external gear 31 facing the inner peripheral surface 36a, the wedge-shaped member 35, and the wedge-shaped member 36 The outer peripheral surface 35 b and the outer peripheral surface of the bush 34 facing the outer peripheral surface 36 b (the inner peripheral surface of the through hole 32 f of the internal gear 32) are substantially at the same position in the axial direction of the rotary shaft 33.

  As shown in FIG. 2, a flange portion 33 b as a striker integrally formed with the rotary shaft 33 in the space between the thin side end surface 35 c of the wedge member 35 and the thin side end surface 36 c of the wedge member 36. Is overhanging. Therefore, when the rotating shaft 33 rotates counterclockwise in FIG. 2, the side wall 33g of the notch 33c of the rotating shaft 33 comes into contact with the side end surface 35c of the wedge-shaped member 35, and conversely, the rotating shaft 33 is in FIG. , The side wall 33h of the notch 33c of the rotary shaft 33 comes into contact with the side end surface 36c of the wedge-shaped member 36 on the opposite side.

  The wedge-shaped member 35 and the wedge-shaped member 36 are disposed between the inner peripheral surface of the bush 34 and the outer peripheral surface of the cylindrical portion 31f of the external gear 31 so that the thick side faces each other. The tooth gear 32 is eccentric, and the outer teeth 31b are engaged with the inner teeth 32b. As will be described later, the wedge-shaped member 35 and the wedge-shaped member 36 cause the rotary shaft 33 to mesh the internal teeth 32b and the external teeth 31b, and to set one of the external gear 31 and the internal gear 32 to the other gear shaft. Can revolve to the center. The wedge-shaped members 35 and 36 receive a biasing force in a direction away from a spring 37 as a biasing means as shown in FIG.

  The spring 37 includes an annular portion 37a having an intermediate portion of one turn and end portions 37b and 37c rising from the annular portion 37a. The annular portion 37a is a space between the internal gear 32 and the external gear 31. In other portions, in the present embodiment, the rotary shaft 33 is wound around the internal gear 32 and the lower arm 20. Further, the end portion 37b is engaged with a groove portion 35d formed on the side wall on the thick side of the wedge-shaped member 35, and the end portion 37c is formed on a groove portion 36d formed on the side end surface on the thick side of the wedge-shaped member 36. It is locked. Furthermore, the lower arm 20 is set in a shape that covers the internal gear 32.

  The cylindrical pressing member 38 is fitted to the outer peripheral surface of the internal gear 32, and both end portions thereof protrude toward the central axis, and sandwich the external gear 31 and the internal gear 32. Thereby, it can control that the external gear 31 and the internal gear 32 leave | separate in an axial direction. Note that a ring 39 for retaining is retained in the annular groove 33d of the rotating shaft 33.

  In this embodiment, between the inner peripheral surface of the bush 34 and the outer peripheral surface of the cylindrical portion 31 f of the external gear 31, between the side end surface 35 c of the wedge-shaped member 35 and the side end surface 36 c of the wedge-shaped member 36. A rubber 40 as an elastic body is arranged in the space. The rubber 40 has a flat rectangular parallelepiped shape as shown in FIG. 4 in a natural state, and is elastically deformed in an arc shape between the inner peripheral surface of the bush 34 and the outer peripheral surface of the cylindrical portion 1031f of the external gear 31. Placed in the space. As shown in FIG. 11A, the rubber 40 is pressed against the outer peripheral surface of the cylindrical portion 31 f of the external gear 31 by the elastic repulsive force, as shown in FIG. The end portion side is pressed against the inner peripheral surface of the bush 34. For this reason, the rubber 40 functions as a braking member that abuts the side end surface of the leading wedge-shaped member of the moving wedge-shaped member 35 and the wedge-shaped member 36 and decelerates the moving speed of the leading wedge-shaped member.

  Next, the operation of the above embodiment will be described. In a state where no rotational operation force is applied to the rotary shaft 33 from the outside, the spring 37 biases the wedge-shaped members 35 and 36 away from each other, and applies a force in the direction of driving the wedges to the wedge-shaped members 35 and 36. . For this reason, the relative movement between the internal gear 32 and the rotary shaft 33 is prohibited, and the gear mechanism 30 is in a locked state in which the external teeth 31b of the external gear 31 and the internal teeth 32b of the internal gear 32 mesh with each other. The back is locked in that position.

  In this locked state, when the rotary shaft 33 is rotated in the clockwise direction in FIG. 2, for example, a force in the direction of pulling out the wedge-shaped member 36 from the side wall 33h of the rotary shaft 33 to the side end surface 36c of the wedge-shaped member 36 acts. The wedge-shaped member 36 rotates clockwise with respect to the internal gear 32. As a result, a gap is generated between the wedge-shaped member 36 and the peripheral member, and the internal gear 32 can be moved. Then, the wedge-shaped member 35 receiving the urging force of the spring 37 rotates in the clockwise direction so as to fill this gap.

  By this interlocking operation, the wedge-shaped members 36 and 35 rotate in the clockwise direction together with the rotating shaft 33. The same applies to the counterclockwise rotation. Therefore, the internal gear 32 is supported by the rotary shaft 33 at an eccentric position where the internal teeth 32b mesh with the external teeth 31b, and the external gear 31, the internal gear 32, and the rotary shaft 33 constitute a gear mechanism. Will be.

  Thus, by rotating the rotary shaft (flange portion 33 b) 33, the meshing position of the external teeth 31 b of the external gear 31 and the internal teeth 32 b of the internal gear 32 is changed, and the upper arm 10 is moved with respect to the lower arm 20. It can be tilted to adjust the tilt angle of the seat back.

  Here, the operation of the rubber 40 will be described with reference to FIG. FIGS. 11A to 11D are views for explaining the operation of the rubber 40 when the rotary shaft 33 is rotated in the clockwise direction. In addition, since the passenger | crew sits on the seat and the back part of the passenger presses the seat back, a load in the direction of arrow F acts on the climbing device.

(A) When the rotating shaft 33 is rotated clockwise from the locked state shown in the drawing, the wedge-shaped members 36 and 35 rotate together with the rotating shaft 33 in the clockwise direction as shown in FIGS.
Here, in the state shown in FIG. 5B, a load in the direction of arrow F acts on the wedge-shaped member 1035 via the bush 34, and therefore a large frictional resistance force acts on the wedge-shaped member 1035.

  However, when the wedge-shaped member 35 is moved to the state shown in FIG. Then, the wedge-shaped member 35 to which the large frictional resistance does not act tends to move greatly at once due to the urging force of the spring 37. However, the rubber 40 that presses against the outer peripheral surface of the cylindrical portion 31 f of the external gear 31 and the inner peripheral surface of the bush 34 is disposed in front of the moving direction of the wedge-shaped member 35. Therefore, when the wedge-shaped member 35 comes into contact with the rubber 40, the moving speed of the wedge-shaped member 35 is reduced, and the wedge-shaped member 35 and the wedge-shaped member 36 are synchronized with the rotation of the rotary shaft 33 as shown in FIG. Move.

With such a configuration, the following effects can be obtained.
(1) The wedge-shaped member 35 that is pushed by the flange portion (striker) 33c of the rotating shaft 33 and the wedge-shaped member on the leading side of the wedge-shaped member 36 come into contact with each other to reduce the moving speed of the wedge-shaped member on the leading side. By providing the rubber 40, the skip of the wedge-shaped member on the leading side of the wedge-shaped member 35 and the wedge-shaped member 36 pushed by the striker does not occur.
(2) The rubber 40 is between the inner peripheral surface of the bush 34 and the outer peripheral surface of the cylindrical portion 31f of the external gear 31, and between the side end surface 35c of the wedge-shaped member 35 and the side end surface 36c of the wedge-shaped member 36. Space saving can be achieved by arranging in the space. Further, the rubber 40 is an elastic body that is pressed against the inner peripheral surface of the bush 34 and the outer peripheral surface of the cylindrical portion 31f of the external gear 31, so that the rubber 40 can be optimized by changing the material, size, etc. A braking force can be obtained.

  The present invention is not limited to the above embodiment. For example, in the embodiment described above, the external gear 31 is attached to the upper arm 10 and the internal gear 32 is attached to the lower arm 20, but the reverse may be possible.

  The striker is formed integrally with the rotating shaft 33, but may be a separate member.

It is a longitudinal cross-sectional view which shows the embodiment of this invention. FIG. 2 is a left side view (the upper arm and the lower arm are deleted) in the embodiment of FIG. 1. FIG. 2 is a right side view (the upper arm and the lower arm are deleted) in the embodiment of FIG. 1. It is a disassembled perspective view of the principal part in the embodiment of FIG. It is a figure for demonstrating the coupling | bonding with a gear mechanism part, an upper arm, and a lower arm. It is a figure which shows an external gear, (b) is AA sectional drawing of (a). It is a figure which shows an internal gear, (b) is BB sectional drawing of (a). It is a figure which shows a rotating shaft, (b) is CC sectional drawing of (a). It is an enlarged view which shows a wedge-shaped member, (a) is a top view, (b) is a front view, (c) is a perspective view. It is a figure which shows a spring, (a) is a top view, (b) is a front view. It is a figure explaining the action | operation of rubber | gum when rotating the rotating shaft of FIG. 1 clockwise. It is a disassembled perspective view of the conventional reclining apparatus. It is sectional drawing of the axial direction of the rotating shaft of FIG. FIG. 14 is a left side view of FIG. 13. It is a figure explaining the skip of the wedge-shaped member of a reclining apparatus.

Explanation of symbols

31 External gear 31f Cylindrical part 40 Bush 33 Rotating shaft 33c Flange part (cam)
35 Wedge-shaped member (first wedge-shaped member)
35c, 36c side end face 36 wedge-shaped member (second wedge-shaped member)

Claims (2)

External teeth are formed on the outer peripheral surface, and external gears provided on one member of the seat cushion side member and the seat back side member,
Internal teeth that mesh with the external teeth of the external gear and have internal teeth with a larger number of teeth than the external teeth, and are provided on the other member of the seat cushion side member and the seat back side member Gears,
A cylindrical portion formed at the center of one gear of the internal gear and the external gear and extending toward the other;
A through hole formed in the center of the other gear of the internal gear and the external gear, and through which the cylindrical portion is inserted;
A first wedge-shaped member movably provided in a space between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole;
The external teeth of the external gear and the internal teeth of the internal gear are provided in a space between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole in cooperation with the first wedge-shaped member. A second wedge-shaped member that holds the engagement of
The first wedge-shaped member and the second wedge-shaped member are engaged with the first wedge-shaped member and the second wedge-shaped member, and the internal teeth of the internal gear and the external teeth of the external gear mesh with each other. A biasing member that biases the member;
One of the first wedge-shaped member and the second wedge-shaped member is pushed against the urging force of the urging means to move the first wedge-shaped member and the second wedge-shaped member. A striker that changes the meshing position of the external teeth of the external gear and the internal teeth of the internal gear;
In a reclining device having
A braking member for reducing the moving speed of the leading wedge member by contacting the leading wedge member out of the first wedge member and the second wedge member that is pushed and moved by the striker is provided. A reclining device characterized by that.   The braking member is an elastic body that is disposed in a space between the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole and presses against the outer peripheral surface of the cylindrical portion and the inner peripheral surface of the through hole. The reclining device according to claim 1.

Images