JP2016174889A - Seat reclining device and seat - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce generation of abnormal sound due to the play between components.SOLUTION: A rolling member 80 is arranged in the opposing faces of lock plates 60A-60D that radially operate between guide walls 23a-23d and of guide grooves 23f-23i of a guide bracket 20. During the locking in which the external teeth of the lock plates 60A-60D mesh with the internal teeth of the internal gear 30, if a force is imparted making the guide bracket 20 and the internal gear 30 relatively rotated, the rolling member 80 functions as a wedge. With the lock plates 60A-60D pressurized in the direction abutting on the side of the guide walls 23a-23d, operation clearance between them is reduced, suppressing the play in the circumferential direction of the lock plates. Also, the respective opposing faces of the guide grooves 23f-23i and the lock plates 60A-60D are relatively pressurized in-between, suppressing the operation clearance in the lamination direction of the lock plate 20 and the guide bracket 30, so that the play is controlled.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a seat reclining device that is attached to a seat of a vehicle or the like and appropriately adjusts an inclination angle of a seat back with respect to a seat cushion, and a seat incorporating such a seat reclining device.

  In Patent Documents 1 and 2, a guide bracket is fixed to one of the seat cushion and the seat back, and an internal gear is fixed to the other, and a lock plate having external teeth meshing with internal teeth of the internal gear is disposed between the two. A reclining device is disclosed in which the seat back is maintained at an appropriate inclination angle by engaging both, and the seat back can be rotated back and forth by releasing the engagement between both. A mounting ring is fixed to the outer peripheral surface of the guide bracket or the internal gear. The mounting ring is formed in a ring shape having a bottom surface portion and a peripheral surface portion having a substantially L-shaped cross section, and is inserted from one of the guide bracket or the internal gear, and the peripheral surface portion is located on the back side in the insertion direction. It fixes to the outer peripheral surface of a null gear by welding etc., and the internal gear or guide bracket located in the meantime is supported so that it can rotate between bottom surfaces. Since it can be locked by meshing the lock plate housed inside and the internal teeth of the internal gear, it is suitable for thinning.

JP 2009-247392 A JP 2005-230300 A

  In Patent Documents 1 and 2, a cam urged by a spiral spring is arranged at the center, and a plurality of guide grooves are provided between adjacent guide walls provided in the guide bracket at a predetermined interval in the circumferential direction. The lock plate is arranged, and the lock plate is slid radially outward by the rotation of the cam by the elastic force of the spiral spring, and the external teeth of the lock plate are engaged with the internal teeth of the internal gear. Thereby, the inclination angle of the seat cushion of the seat back is maintained at a predetermined angle. On the other hand, when the operating lever is operated to rotate the cam in the reverse direction against the spiral spring elastic force, the cam engages with the lock plate and slides the lock plate radially inward to release the lock. The seat back can be tilted.

  The lock plate is slid in the radial direction along the guide groove between the adjacent guide walls provided on the guide bracket as described above, but there is a slight operation between the guide wall and the lock plate. Clearance is provided. This operating clearance is indispensable for smooth movement of the lock plate, but even when it is slightly locked, the lock plate moves in the circumferential direction by an amount corresponding to this operating clearance, and is loose. An abnormal noise may occur due to contact with the side surface of the guide wall. In addition, the operating clearance is not always as designed due to manufacturing errors of each component in the press process and heat treatment process during manufacturing, and there are variations, and this is also a factor that causes rattling and abnormal noise of the lock plate It has become.

  In Patent Document 2, one of the guide wall portions of the guide bracket is provided so as to be swingable, and a radius is provided between the movable guide wall portion and a fixed guide wall portion provided at a predetermined interval in the same manner as the lock plate. A plate-shaped wedge that can move in the direction is provided. Further, the movable guide wall portion and the plate-like wedge are provided so that the inclined side surfaces inclined by a predetermined angle with respect to the radial direction come into contact with each other. Therefore, when the plate-shaped wedge slides in the radial direction, the movable guide wall portion is pressed in the circumferential direction and swings, and is pressed against the side surface of the lock plate disposed adjacent to the movable guide wall portion. Thereby, at the time of locking, the operation clearance between the two is eliminated, and rattling of the lock plate is suppressed.

  However, in the case of Patent Document 2, one of the guide wall portions of the guide bracket must be provided so as to be swingable, and processed into a predetermined shape between the swingable movable guide wall portion and the fixed guide wall portion. The plate-shaped wedge must be disposed, and the structure is complicated, which increases the manufacturing cost. Further, although the play in the circumferential direction between the lock plate and the guide wall portion can be eliminated, the stack direction (axial direction) between the members arranged in layers such as the lock plate and the guide bracket or the internal gear. It is not possible to eliminate the operating clearance. In addition, not only the lock plate but also the plate-like wedge is moved in the radial direction by the elastic force of the spiral spring, and the movable guide wall is pressed toward the lock plate by the plate-like wedge, so the smooth movement of the lock plate in the radial direction is impaired. There is a possibility. Furthermore, since the lock plate is pressed only in the same direction along the circumference by the plate-shaped wedge and the movable guide wall, the engagement between the external teeth and the internal teeth of the internal gear is not smooth and is insufficient. There is also a possibility of a so-called pseudo lock (half lock).

  The present invention has been made in view of the above, and has a simple structure, not only the circumferential play between the lock plate and the guide wall of the guide bracket, but also the stacking direction of the guide bracket or the internal gear. The seat reclining device and the seat can improve the smoothness of the sliding of the lock plate in the radial direction and suppress the occurrence of pseudo-lock (half lock) between the outer teeth and the inner teeth. It is an object to provide a seat in which a reclining device is incorporated.

A guide bracket having a plurality of guide wall portions attached to one of the seat cushion and the seat back and spaced apart in the circumferential direction, and an interface attached to the other of the seat cushion and the seat back A null gear, and a mounting ring having a peripheral surface portion fixed to one outer peripheral surface of the guide bracket or the internal gear, and the guide bracket and the internal gear are relatively rotated, whereby the seat back is A seat reclining device that supports the seat cushion so as to be reclining,
A lock plate that is disposed in a guide groove between adjacent guide walls provided in the guide bracket so as to be operable in the radial direction, and has outer teeth that engage with the internal teeth of the internal gear on the outer peripheral surface. A locking mechanism having
At the time of locking in which the outer teeth of the lock plate and the inner teeth of the internal gear are meshed with each other, provided at least at one place between the respective members including the guide bracket, the internal gear and the lock plate. In the direction in which the operation clearance between the lock plate and the guide wall portion is reduced by the force of rotating the guide bracket and the internal gear relative to each other, and the operation clearance in the stacking direction of the respective members disposed in a stacked manner. And a rolling member forcing in both directions of the direction of reduction.

It is preferable that the rolling member is disposed at least at one place between the opposing surfaces of the guide groove portion of the guide bracket and the lock plate.
An arrangement position of the rolling member is a line connecting an outer end edge of one guide wall portion and an inner end edge of the other guide wall portion sandwiching the guide groove portion, and an inner side of the one guide wall portion. It is preferable that the outer peripheral side of the intersection of the line connecting the end edge and the outer end edge of the other guide wall portion.
A holding groove is formed on each of the facing surfaces of the guide groove portion of the guide bracket and the lock plate at least at one place where the rolling member is disposed,
When the rolling member is held by the holding grooves, and a force for rotating the guide bracket and the internal gear is applied at the time of locking, the rolling member is pressed against any part of the holding grooves and moves. It is preferable that the configuration is regulated.

  One of the holding grooves formed on each of the opposed surfaces has a diameter of the rolling member in both the radial direction and the circumferential direction so as to allow displacement in the radial direction and the circumferential direction of the rolling member. It is preferable to have a length exceeding.

It is preferable that an inclined surface is formed on the bottom surface of one holding groove having a length exceeding the diameter of the rolling member in both the radial direction and the circumferential direction.
A groove having a substantially V-shaped cross section serving as an initial placement position of the rolling member on the bottom surface of one holding groove having a length exceeding the diameter of the rolling member in both the radial direction and the circumferential direction Is preferably formed.
The groove width along the radial direction of the other holding groove facing the one holding groove having a length exceeding the diameter of the rolling member in both the radial direction and the circumferential direction is from the vicinity of the center in the circumferential direction. Also, it is preferable that each end side is formed narrow.

It is preferable that a plurality of the lock plates are provided, and the rolling members are respectively disposed between opposing surfaces of one or more of the lock plates and the corresponding guide groove portions.
Between the opposing surfaces of the pair of lock plates provided at positions opposed to each other across the rotation center where the guide bracket and the internal gear rotate relative to each other and the corresponding guide groove portions, respectively, It is preferable that a rolling member is provided.
The mounting ring includes a ring-shaped bottom surface portion having an inner circumferential circle facing the guide bracket or the internal gear, and the ring-shaped bottom surface portion is bent inward from the circumferential surface portion side. It has an inwardly bent portion, and an inner peripheral end surface of the inwardly bent portion is opposed to the opposed inclined surface of the guide bracket or the internal gear in an oblique direction, and the opposed inclined surface is more than other portions. It is preferable that it is the structure which has a part which adjoins or contact | abuts partially.
The mounting ring includes a ring-shaped bottom surface portion having an inner circumferential circle facing the guide bracket or the internal gear, and the ring-shaped bottom surface portion is bent inward from the circumferential surface portion side. It is preferable that an inner bent portion is provided, and an inner peripheral end surface of the inner bent portion is the guide bracket.
A predetermined clearance is provided between the inwardly bent portion of the ring-shaped bottom surface portion and the guide bracket or the radially opposing surface of the internal gear that is radially opposed to the inwardly bent portion, and the guide It is preferable that the bracket or the internal gear is not fixed in the radial direction with respect to the mounting ring.
The mounting ring includes a ring-shaped bottom surface portion having an inner circumferential circle facing the guide bracket or the internal gear, and the ring-shaped bottom surface portion is bent inward from the circumferential surface portion side. It has an inwardly bent portion, and an inner peripheral end surface of the inwardly bent portion is opposed to the opposed inclined surface of the guide bracket or the internal gear in an oblique direction, and the opposed inclined surface is more than other portions. Partially has a close or abutting part, and
It is preferable that an inner peripheral end surface of the inwardly bent portion partially has a portion that abuts at a substantially right angle with a surface of the outer peripheral edge portion of the guide bracket or the internal gear.
The mounting ring has a ring-shaped bottom surface portion provided with an inner circumferential circle facing the guide bracket or the internal gear, and the means for reducing the frictional resistance includes the ring-shaped bottom surface portion, the guide bracket or the It is preferable that it is a sliding ring provided between internal gears.
The mounting ring has a ring-shaped bottom surface portion provided with an inner circumferential circle facing the guide bracket or the internal gear, and the means for reducing the frictional resistance includes the ring-shaped bottom surface portion, the guide bracket or the It is preferable that ball members disposed at a plurality of locations at substantially equal intervals in the circumferential direction are provided between the internal gear and the internal gear.

  The seat of the present invention is a seat comprising a seat cushion and a seat back, wherein any one of the seat reclining devices is disposed between the seat cushion and the seat back. To do.

  According to the present invention, the rolling member is disposed between the opposing surfaces of the lock plate that operates in the radial direction between the guide wall portions and the guide groove portion of the guide bracket. For this reason, when a force that causes the guide bracket and the internal gear to rotate relative to each other is applied at the time of locking in which the external teeth of the lock plate and the internal teeth of the internal gear mesh, Direction). However, since only a very small operating clearance is provided between the members, the rolling member functions as a wedge at the displacement limit position after being displaced very slightly. As a result, the lock plate is pressed in the direction in which the lock plate abuts against the side surface of the guide wall portion, the operation clearance between the two is reduced, the play of the lock plate in the circumferential direction is suppressed, and the guide groove portion and the lock plate are By relatively pressing between the opposing surfaces, the operation clearance in the stacking direction between the lock plate and the guide bracket and the operation clearance in the stacking direction between the lock plate and the internal gear are also reduced. In other words, not only the circumferential direction but also the play in the stacking direction of the lock plates is suppressed. On the other hand, since it has a rolling member, when the lock plate slides outward in the guide groove, friction is small due to the rolling of the rolling member, and the sliding of the lock plate in the radial direction is smooth. Can increase the sex. Further, when the external teeth of the lock plate mesh with the internal teeth of the internal gear, the lock plate slightly swings in any direction that is easily meshed by the rolling of the rolling member. The certainty of the meshing action can be improved and the occurrence of pseudo lock (half lock) can also be suppressed.

FIG. 1A is a plan view of a seat reclining device according to an embodiment of the present invention as viewed from the guide bracket side, and FIG. 1B is a side view of FIG. FIG. 1C is a rear view of FIG. FIG. 2 is an exploded perspective view of the seat reclining device according to the embodiment of the present invention. 3A is a seat reclining device according to an embodiment of the present invention, which is a cross-sectional view taken along the line AA of FIG. 3B, and FIG. FIG. 3C is a cross-sectional view taken along the line BB of FIG. 3B, and FIG. 3D is a cross-sectional view of FIG. FIG. FIG. 4A is a plan view of the guide bracket used in the seat reclining device according to the embodiment of the present invention as viewed from the side facing the internal gear, and FIG. FIG. 4A is a cross-sectional view taken along a line DD in FIG. 4A, and FIG. 4C is a cross-sectional view taken along a line EE in FIG. FIGS. 5A to 5C are diagrams showing the arrangement relationship between the lock plate having the plate-side holding groove and the rolling member according to one example, and among these, FIG. (B) is a side view of the lock plate, and (c) is a perspective view. FIGS. 5D to 5F are views showing the arrangement relationship between the lock plate having the plate-side holding groove and the rolling member according to another example, and among these, FIG. (E) is a side view of the lock plate, and (f) is a perspective view. 6A and 6B are views for explaining the operation of the seat reclining device according to the embodiment of the present invention. FIG. 6A is a cross-sectional view, and FIG. 6B is an internal gear. It is the top view shown abbreviate | omitting. FIG. 7 is a view for explaining a preferable arrangement position of the rolling members. FIG. 8 is an exploded perspective view of a seat reclining device according to another embodiment of the present invention. FIG. 9A is a seat reclining device according to another embodiment of the present invention, which is a cross-sectional view taken along the line AA in FIG. 9B, and FIG. FIG. 9C is a cross-sectional view taken along line BB in FIG. 9B, and FIG. 9D is a cross-sectional view taken along line C-B in FIG. 9B. FIG. FIG. 10 is a cross-sectional view for explaining the operation of the seat reclining device according to another embodiment of the present invention. Fig.11 (a) is a top view for demonstrating the effect | action of the lock plate and rolling member of the reclining apparatus for seats concerning other embodiment of this invention, FIG.11 (b) is a rolling member. It is the figure which showed the state located on the DD line | wire of Fig.11 (a), FIG.11 (c) is a state in which the rolling member is located on the EE line | wire of Fig.11 (a). FIG. FIG. 12 is an exploded perspective view of a seat reclining device according to still another embodiment of the present invention. FIG. 13A is a plan view of a seat reclining device according to still another embodiment of the present invention, and FIG. 13B is a cross-sectional view taken along line AA in FIG. 13 (c) is a cross-sectional view taken along line BB in FIG. 13 (a). FIG. 14A is a plan view of a guide bracket used in a seat reclining device according to still another embodiment of the present invention as viewed from the side facing the internal gear, and FIG. 14A is a cross-sectional view taken along the line CC of FIG. 14A, and FIG. 14C is a cross-sectional view taken along the line DD of FIG. 14A. FIG. 15 is a diagram for explaining a method of measuring load-displacement characteristics of Test Example 1, Test Example 2, and Comparative Example 1. FIG. 16 is a diagram showing measurement results of load-displacement characteristics of Test Example 1 and Comparative Example 1. FIG. 17 is a diagram showing measurement results of load-displacement characteristics of Test Example 1 and Test Example 2. FIG. 18 is a diagram showing the measurement results of the bending moments of Test Example 1 and Test Example 2. FIG. 19 is a perspective view of a seat reclining device according to still another embodiment of the present invention. 20A is a side view of the seat reclining device shown in FIG. 19, and FIG. 20B is a plan view seen from the guide bracket side. 21A is a cross-sectional view taken along the line BB in FIG. 20B, FIG. 21B is a cross-sectional view taken along the line FF in FIG. 20B, and FIG. FIG. 21A is an enlarged view of a portion A in FIG. 21A, and FIG. 21D is a diagram showing a portion where the inner peripheral end face is in partial contact. FIG. 22 is a plan view seen from the internal gear side of a seat reclining device according to still another embodiment of the present invention. FIG. 23A is a plan view seen from the guide bracket side of the seat reclining device shown in FIG. 22, and FIG. 23B is a cross-sectional view taken along the line DD in FIG. 24A is a cross-sectional view taken along the line AA in FIG. 22, FIG. 24B is a cross-sectional view taken along the line BB in FIG. 22, and FIG. FIG. 23 is a cross-sectional view taken along the line CC of FIG.

  Hereinafter, the present invention will be described in more detail based on the embodiments shown in the drawings. 1 to 6 show a seat reclining device 10 according to an embodiment of the present invention. The seat reclining device 10 is attached between the side frame of the seat cushion frame and the side frame of the seat back frame. As shown in FIGS. 1 to 6, the seat reclining device 10 includes a guide bracket 20 and an internal gear 30. For example, the guide bracket 20 is fixed near the rear portion of the side frame of the seat cushion frame. The internal gear 30 is fixed near the lower part of the side frame of the seat back frame.

  The guide bracket 20 is formed in a disk shape, and the connection protrusions 21 and 21 protruding outward on the outer surface are formed at positions facing each other by 180 degrees across the rotation center of the guide bracket 20 and the internal gear 30. The connection protrusions 21 and 21 are connected to a side frame of a seat cushion frame, for example. An arrangement hole 22 having a predetermined diameter for arranging the spiral spring 40 is formed through the center. An engagement groove 22a is provided in at least one place on the inner peripheral surface of the arrangement hole 22, and the outer end 41 of the spiral spring 40 is engaged with any one of the engagement grooves 22a.

  As shown in FIGS. 2 to 4 and the like, the guide bracket 20 has four guide wall portions 23a to 23d protruding on the inner surface (the surface facing the internal gear 30) at equal intervals in the circumferential direction. Lock plates 60A to 60D, which will be described later, are arranged in the four guide groove portions 23f to 23i between the adjacent guide wall portions 23a and 23b, 23b and 23c, 23c and 23d, and 23d and 23a. Then, it slides in the radial direction along the guide groove portions 23f to 23i.

  As shown in FIGS. 2 and 3, the internal gear 30 is formed in a circular shape in plan view and is formed in a substantially concave shape in cross section, and an internal tooth 32 is formed on the inner peripheral surface of the concave portion 31, and the concave shape is formed. The portion 31 is disposed so as to face the inner surface of the guide bracket 20. A circular large-diameter protrusion 33 protruding outward is provided on the outer surface of the internal gear 30, and a plurality of connecting protrusions 34 protruding further outward from the outer surface of the circular large-diameter protrusion 33 are provided in the circumferential direction. Is formed. For example, it is connected to the side frame of the seat back frame via the connection protrusion 34.

  The guide bracket 20 and the internal gear 30 are configured such that the inner surface of the guide bracket 20 and the concave portion 31 of the internal gear 30 face each other, the end surface of the peripheral wall 31 a of the concave portion 31 is brought into contact with the inner surface of the guide bracket 20, and Positioned. The attachment ring 70 is formed in a circular ring shape in plan view, and has a ring-shaped bottom surface portion 71 and a peripheral surface portion 72 that rises from the outer peripheral edge of the ring-shaped bottom surface portion 71.

  The mounting ring 70 is configured such that the inner surface of the guide bracket 20 and the concave portion 31 of the internal gear 30 face each other, and the lock mechanism including the spiral spring 40, the cam 50, and the lock plates 60A to 60D is accommodated in the inner space. In the embodiment, the peripheral surface portion 72 is mounted on the outer peripheral surfaces of the internal gear 30 and the guide bracket 20 from the outer surface side of the internal gear 30 (see FIGS. 1 and 2). At this time, the inner diameter of the inner circumferential circle 71a of the ring-shaped bottom portion 71 is almost the same as the outer diameter of the circular large-diameter protrusion 33 of the internal gear 30, and is large enough to allow the circular large-diameter protrusion 33 to be inserted. Therefore, when assembled in this manner, the circular large-diameter protrusion 33 is exposed to the outside of the inner peripheral edge 71a. After mounting the mounting ring 70 in this way, the peripheral surface portion 72 is welded and fixed to the outer peripheral surface of the guide bracket 20. Therefore, in a state where the connecting projection 21 of the guide bracket 20 is fixedly connected to the side frame of the seat cushion, for example, and the connecting protrusion 34 of the internal gear 30 is fixedly connected to the side frame of the seat back, for example, the seat back is connected to the seat cushion. The guide bracket 20 and the internal gear 30 rotate relatively. At this time, the radial movement of the internal gear 30 is restricted by the peripheral surface portion 72 of the mounting ring 70, and the axial movement of the internal gear 30 is restricted by the ring-shaped bottom surface portion 71, so that a smooth rotational motion is made. .

  The ring-shaped bottom surface portion 71 is provided with protrusions 71b projecting toward the internal gear 30 at predetermined intervals in the circumferential direction (see FIG. 6A). As a result, the outer peripheral edge 30a of the internal gear 30 does not come into surface contact with the ring-shaped bottom surface portion 71 but comes into contact with the protrusion 71b, so that the rotational movement of the internal gear 30 with respect to the mounting ring 70 is smooth. Become.

  As shown in FIGS. 2 and 3, the cam 50 corresponds to the lock plates 60 </ b> A to 60 </ b> D arranged in four in the present embodiment, at equal intervals in the circumferential direction, as shown in FIG. Four engaging protrusions 51, 51 extending diagonally counterclockwise and extending substantially in a circular arc shape are provided. Further, the main body 52 of the cam 50 excluding the engaging protrusions 51 and 51 has a large outer diameter at a position spaced a predetermined angle in the counterclockwise direction in FIG. The step portions 52b and 52b that bulge out are formed at four locations. A flat center hole 52a through which the shaft portion of the operation member for the reclining operation is inserted is formed at the center of the cam 50. When the operation member is rotated forward or backward, the cam 50 follows this. Rotate in the same direction.

  The cam 50 is provided with a first shaft portion 53 that protrudes from the periphery of the flat center hole 52a toward the guide bracket 20 on the surface facing the guide bracket 20 (see FIGS. 1A and 3B). . The first shaft portion 53 is formed with an outer diameter smaller than the inner diameter of the spiral spring 40, and the first shaft portion 53 is formed with an engagement groove 53a cut out from the outer peripheral surface toward the center. Yes. The spiral spring 40 is disposed on the outer periphery of the first shaft portion 53, and an inner end portion 42 of the spiral spring 40 is engaged with the engagement groove 53 a of the first shaft portion 53, and the arrangement hole 22 of the guide bracket 20 together with the first shaft portion 53. Placed inside. The spiral spring 40 is engaged with the engaging groove 22a formed on the inner peripheral surface of the arrangement hole 22 of the guide bracket 20 at the outer end 41 as described above. For this reason, when the inner end 42 is engaged with the engagement groove 53a, the cam 50 is urged clockwise in FIG.

  At the center of the internal gear 30, a second shaft portion 35 protruding toward the cam 50 is provided. The second shaft portion 35 is inserted into a bearing hole 54 formed in the cam 50, and the cam 50 is It is rotatably supported (see FIG. 2).

  In the present embodiment, four lock plates 60A to 60D are used. The four lock plates 60 </ b> A to 60 </ b> D correspond to the four angular engagement protrusions 51, 51 formed on the cam 50, and the width is between the adjacent guide wall portions 23 a, 23 b, between 23 b and 23 c, respectively. , 23c and 23d, and between 23d and 23a with as little operating clearance as possible, guided by the adjacent side surfaces of the guide wall portions 23a to 23d, respectively, and on the guide groove portions 23f to 23i along the radial direction of the guide bracket 20 Is slidable.

  The lock plates 60 </ b> A to 60 </ b> D and the cam 50 are urged radially outward by rotation of the cam 50 in one direction (clockwise in FIG. 6B) by the elasticity of the spiral spring 40. Any shape that satisfies the fact that the lock plates 60A to 60D can be displaced in the central direction by rotating the cam 50 in the reverse direction (counterclockwise in FIG. 6B) by the operation member may be used. In the present embodiment, the lock plates 60A to 60D are formed in a substantially rectangular shape in plan view, while the cam 50 is formed with the angular engagement protrusions 51 and 51. Engaged grooves 61, 61 are provided that are notched in a substantially arc shape counterclockwise in FIG. 6B from the inner peripheral surface. When the cam 50 rotates counterclockwise in FIG. 6B, the engaging protrusions 51 and 51 engage with the engaged grooves 61 and 61, respectively, and draw the lock plates 60A to 60D toward the center. When the cam 50 is urged by the spiral spring 40 and rotates clockwise in FIG. 6B, the engagement protrusions 51 and 51 and the step portions 52b and 52b press the lock plates 60A to 60D outward in the radial direction. To do. Outer teeth 63, 63 are formed on the outer peripheral surfaces of the lock plates 60A to 60D. When pressed outward in the radial direction, they engage with the inner teeth 32 of the internal gear 30, and the guide bracket 20 and the internal gear are engaged. And 30 are locked so that they cannot rotate relative to each other.

  Here, of the four lock plates 60A to 60D, in the present embodiment, one opposing surface of the two lock plates 60A and 60C facing each other at 180 degrees across the rotation centers of the guide bracket 20 and the internal gear 30 (this book In the embodiment, holding grooves (plate-side holding grooves) 60A1 and 60C1 are formed on the guide bracket 20 on the surface facing the guide groove portions 23f and 23h (see FIGS. 3A, 3C, and 5). ). In the guide groove portions 23f and 23h of the guide bracket 20, holding grooves (bracket side holding grooves) 23f1 and 23h1 are formed at positions facing the plate side holding grooves 60A1 and 60C1 (see FIGS. 2 to 4).

  A rolling member 80 is disposed between the plate side holding grooves 60A1 and 60C1 and the bracket side holding grooves 23f1 and 23h1. The rolling member 80 only needs to be able to roll in the radial direction and the circumferential direction, but preferably a metal sphere (metal sphere) that easily rolls in either direction is used. Further, either one of the holding grooves, in this embodiment, the bracket side holding grooves 23f1 and 23h1 is formed larger than the diameter of the rolling member 80 in both the radial direction and the circumferential direction, and the bracket side holding grooves 23f1 and 23h1 are formed in the bracket side holding grooves 23f1 and 23h1. It can be displaced in an appropriate direction. In addition, inclined surfaces 23f2 and 23h2 are formed on the bottom surfaces of the bracket-side holding grooves 23f1 and 23h1 so as to rise from the substantially central portion in the circumferential direction of the bracket-side holding grooves 23f1 and 23h1 toward one end side. . The inclined surfaces 23f2 and 23h2 are arranged in such a direction that the rolling member 80 does not press the inclined surfaces 23f2 and 23h2 when a load is applied rearward to the seat back during assembly, that is, the bracket-side holding groove 23f1. , 23h1 is preferably formed so as to be inclined from the substantially central portion in the circumferential direction toward the front end side of the seat back in the rotational direction. Although it is possible to form the seat back so as to incline toward the rear end side in the rotational direction, in that case, rolling to the inclined surfaces 23f2 and 23h2 due to repeated loads on the seat back when the occupant is seated The indentation of the member 80 is likely to occur, and the wedge effect may be deteriorated early.

  On the other hand, the plate-side holding grooves 60A1 and 60C1 are formed in such a shape that a part of the rolling member 80 protrudes outward and can roll on the groove bottom surfaces of the bracket-side holding grooves 23f1 and 23h1. For example, as shown in FIGS. 5A to 5C, the length along the circumferential direction is longer than the diameter of the rolling member 80, and the radial groove width D <b> 1 is less than the diameter of the rolling member 80. A shape that allows the rolling member 80 to roll while making point contact with the peripheral portions of the plate-side holding grooves 60A1 and 60C1, or as shown in FIGS. 5 (d) to 5 (f) It is formed in a circular shape having a smaller diameter than the member 80, and the rolling member 80 is formed into a shape that can be rolled while making line contact with the peripheral edge portions of the plate-side holding groove portions 60A1 and 60C1.

  When the relative position of the rolling member 80 in the bracket-side holding grooves 23f1 and 23h1 is a position corresponding to the inclined surfaces 23f2 and 23h2, the seat reclining device 1 is the stacking direction of the lock plates 60A and 60C and the guide bracket 20. A force is applied in the axial direction, and is sandwiched between the two.

  According to the present embodiment, at the time of locking, as described above, the cam 50 is urged by the spiral spring 40 and rotates clockwise in FIG. 3B, and the lock plates 60 </ b> A to 60 </ b> D are adjacent to each other. Guided by the walls 23a to 23d and pressed radially outward on the guide grooves 23f to 23i, the outer teeth 63 and 63 of the lock plates 60A to 60D mesh with the inner teeth 32 of the internal gear 30. Since the rolling member 80 is disposed between the opposing surfaces of the lock plates 60A, 60C and the guide groove portions 23f, 23h, when the outer teeth 63, 63 mesh with the inner teeth 32, the rolling member 80 Thus, the lock plates 60A and 60C are swung in a direction in which they can be easily engaged with each other, and so-called pseudo lock (half lock) can be suppressed. If the outer teeth 63, 63 of the two lock plates 60A, 60C are securely engaged with the inner teeth 32, the other two lock plates 60B, 60D arranged at a predetermined interval in the circumferential direction will be described. The external teeth 63 and 63 also mesh with the internal teeth 32 without causing a false lock.

  At the time of locking, as described above, the spiral spring 40 causes the lock plates 60A and 60C to have the radial force P1 that engages the external teeth 63 and 63 with the internal teeth 32, and the guide walls 23b and 23d. A force P2 pressed against the side surface acts (see FIG. 3B). The rolling member 80 is pressed against the inclined surfaces 23f2 and 23h2 by this force P2 and exhibits a wedge effect. That is, the component force in the direction substantially perpendicular to the inclined surfaces 23f2 and 23h2 (the component direction in the stacking direction of the lock plates 60A and 60C and the guide bracket 20 (the axial direction of the seat reclining device 1)) and the reverse direction of the acting direction of the force P2 Reaction force P3 acts in the direction of the resultant force with the component force (see FIG. 6A). Due to the reaction force P3, the lock plates 60A and 60C are circumferentially shifted to the respective side surfaces of the guide wall portions 23a and 23c located in the backward direction of the seat back, and b at the 180 degree symmetrical position in FIG. The abutting at two points of the part-b part eliminates the operating clearance between the lock plates 60A, 60C and the guide wall parts 23a, 23c. In addition, since the lock plates 60A and 60C are shifted toward the internal gear 30 by the reaction force P3, each of the stacked layers including the operation clearance between the lock plates 60A to 60D and the internal gear 30 is provided. There is no working clearance between members. As a result, the play is eliminated in both the circumferential direction and the stacking direction. When the seat back tries to move forward, the rolling member 80 bites in a wedge shape again in an attempt to displace in the direction of the inclined surfaces 23f2 and 23h2. Thereby, the forward displacement is also suppressed. That is, according to the present embodiment, backlash is suppressed in any of the front and rear rotational directions, and the backlash in the stacking direction of the members disposed in a stacked manner including the lock plates 60A to 60D, the guide bracket 20, and the internal gear 30 is prevented. Are also suppressed, and the generation of abnormal noise caused by them is suppressed.

  On the other hand, when unlocking, the operating member is operated to rotate the cam 50 in the opposite direction (counterclockwise in FIG. 6B). As a result, the engagement protrusions 51 and 51 of the cam 50 are engaged with the engaged grooves 61 and 61 of the lock plates 60A to 60D, respectively, and the lock plates 60A to 60D are pulled toward the center, and the external teeth 63 and 63 and the internal tooth 32 do not mesh, and the lock is released. In this embodiment, since the rolling member 80 is disposed on the two lock plates 60A and 60C, the two lock plates 60A and 60C are displaced while receiving the rolling resistance instead of the sliding resistance. . As a result, the resistance at the time of displacement of the two lock plates 60A and 60C is compared with the conventional structure in which all the lock plates are displaced while receiving sliding resistance without disposing the rolling member 80 at all. Accordingly, the total resistance of the four lock plates 60A to 60D is reduced, and the movement is smooth. For this reason, the resistance when the operating member is operated is reduced and the operational feeling is improved. In addition, it is also possible to provide the rolling member 80 corresponding to all of the four lock plates 60A to 60D and further reduce the resistance during operation.

  Further, in order to make the displacement of the lock plates 60A and 60C while receiving the rolling resistance of the rolling member 80 at the time of unlocking smoother, the arrangement position of the rolling member 80 is a guide as shown in FIG. A line connecting the outer end edges 23a2 and 23c2 of one of the guide wall portions 23a and 23c adjacent to each other across the groove portions 23f and 23h and the inner end edges 23b1 and 23d1 of the other guide wall portions 23b and 23d, and one guide wall It is preferable that both the intersections Q1 and Q2 of the lines connecting the inner end edges 23a1 and 23c1 of the portions 23a and 23c and the outer end edges 23b2 and 23d2 of the other guide wall portions 23b and 23d are on the outer peripheral side. In other words, the plate-side holding grooves 60A1 and 60C1 of the lock plates 60A and 60C and the bracket-side holding grooves 23f1 and 23h1 of the guide bracket 20 position the rolling member 80 on the outer peripheral side from the intersections Q1 and Q2. It is preferable to be formed at each position where

  At the time of unlocking, the lock plates 60A and 60C are attracted by the engaging protrusions 51 and 51 of the cam 50 acting on the engaged grooves 61 and 61 located closer to the inner periphery thereof. Therefore, the rolling member 80 serving as a fulcrum for the rolling motion is disposed at a position further away from the contact point with the engaged grooves 61 and 61 that are the action points of the engaging protrusions 51 and 51. The movement of the lock plates 60A and 60C toward the center is more stable. As a result, the resistance at the time of unlocking is further reduced, and unlocking with a smaller force is possible, which contributes to further improvement of the operational feeling.

  The guide bracket 20 is preferably not subjected to a surface hardening process such as a heat treatment. When a load due to rolling of the rolling member 80 is applied, it can be received by the elastic action of the guide bracket 20 which is bent in the axial direction and is not surface-hardened, and attenuates high-frequency vibrations input to the seat back. Can contribute.

  8-11 is a figure for demonstrating other embodiment of this invention. In the present embodiment, the bracket side holding grooves 23f1 and 23h1 are the same as the above embodiment in that both the radial direction and the circumferential direction are formed to be larger than the diameter of the rolling member 80. An inclined surface is not provided, but a flat surface is formed. As shown in FIG. 11, the plate-side holding grooves 60A1 and 60C1 have a groove width D1 along the radial direction in the vicinity of the center in the circumferential direction that is less than the diameter of the rolling member 80 and in the vicinity of the circumferential end. The groove width D2 is formed in a shape that is narrower than D1. Therefore, the rolling member 80 is supported by point contact with the peripheral portions of the plate-side holding groove portions 60A1 and 60C1 instead of being entirely located in the groove with respect to the plate-side holding groove portions 60A1 and 60C1. It will be. And since the groove width is narrowed from D1 to D2 as the relative position of the rolling member 80 in the plate-side holding groove portions 60A1 and 60C1 is closer to the end in the circumferential direction than in the vicinity of the center in the circumferential direction, the peripheral portion The point contact point gradually becomes shallower, and the rolling member 80 is relatively pushed in the direction of pressing the bottom surfaces of the bracket-side holding grooves 23f1 and 23h1, that is, the stacking direction of the lock plates 60A and 60C and the guide bracket 20 In order to be displaced in the axial direction of the seat reclining device 1, the wedge is sandwiched between the two.

  According to the present embodiment, at the time of locking, the radial force P1 that engages the external teeth 63, 63 and the internal teeth 32 on the lock plates 60A, 60C by the spiral spring 40, as in the above embodiment. Then, a force P2 pressed against the side surfaces of the guide wall portions 23b and 23d acts (see FIG. 9B). For this reason, the rolling member 80 is positioned relative to the lock plates 60A and 60C at the center position of the rolling member 80 as shown in FIG. 11, from the position of the DD line in FIG. Since it changes in the direction of the arrow c to the position of the −E line, as shown in FIGS. 11B and 11C, the rolling member 80 is held on the plate side in the stacking direction (axial direction). It is slightly displaced in the direction of the arrow d in FIG. 10 detaching from the grooves 60A1 and 60C1. Thereby, the lock plates 60A and 60C are offset in the circumferential direction, and the operating clearance with the guide wall portions 23a and 23c is reduced. At the same time, the distance between the center of the rolling member 80 and the lock plates 60A and 60C increases from L1 (for example, 0.87 mm) to L2 (for example, 0.91 mm). Since the wedges are sandwiched between the guide groove portions 23f and 23h of the guide bracket 20, the lock plates 60A and 60C are shifted toward the internal gear 30 in FIG. The operating clearance in the axial direction is also reduced. Therefore, in the configuration of the present embodiment, as in the above-described embodiment, there is no backlash in the circumferential direction or the stacking direction, and the generation of abnormal noise is suppressed. However, in the case of this embodiment, processing is easy in that it is not necessary to form an inclined surface in the bracket side holding grooves 23f1 and 23h1.

  In the present invention, the rolling member 80 made of a metal ball is inserted and disposed. However, if there is play between the rolling member 80 and the guide bracket 20 and the internal gear 30 due to manufacturing errors or the like. The effect of eliminating rattling due to the wedge action is reduced. For this reason, the link-shaped bottom surface 71 of the mounting ring 70 and the guide bracket 20 are disposed so as to sandwich the rolling member 80, the lock plates 60A to 60D, the internal gear 30 and the like disposed therebetween as strongly as possible. It is desirable. On the other hand, in order to reduce the frictional resistance during rotation of the internal gear 30 with respect to the mounting ring 70 when strongly pinched, and to ensure smooth rotation, as shown in FIGS. It is preferable that a sliding ring 90 made of a material having a small frictional resistance is interposed between the outer peripheral edge 30a and the ring-shaped bottom surface portion 71 of the mounting ring 70. Examples of such a sliding ring 90 include an oil-free type ring-shaped member made of a composite material in which a resin and a metal are combined, a dry-coated washer, a stainless steel washer, and the like. Further, as a means for reducing the frictional resistance between them, in addition to such means for disposing the sliding ring 90, the outer surface of the internal gear 30 regardless of whether or not the sliding ring 90 is disposed. It is also possible to employ a means for applying a dry coating to the opposing sliding surfaces of the side peripheral edge 30a and the ring-shaped bottom surface portion 71 of the mounting ring 70.

  Further, when the rolling member 80 made of a metal ball is assembled, the rolling member 80 is positioned between the bracket side holding grooves 23f1 and 23h1 of the guide bracket 20 and the plate side holding grooves 60A1 and 60C1 of the lock plates 60A and 60C. Since the rolling member 80 rolls easily, there is a possibility that the assembling property may be impaired. Therefore, as shown in FIGS. 12 to 14, it is preferable to form shallow grooves (V-shaped grooves) 23f3 and 23h3 having a substantially V-shaped cross section on the bottom surfaces of the bracket-side holding grooves 23f1 and 23h1. At the time of assembling, the rolling member 80 is disposed in the V-shaped grooves 23f3 and 23h3 which are the initial disposing positions, so that the assembling can be easily performed.

(Load test)
Here, as shown in FIG. 15, the connecting projection 34 of the internal gear 30 is welded to a back-side rigid jig 1000 having a predetermined length corresponding to the seat back, and the connecting projection 21 of the guide bracket 20 is attached to the seat cushion. By welding to the assumed cushion-side rigid jig 1100, the seat reclining device 10 is disposed between them, and the upper part of the back-side rigid jig 1000 (the position of the load point in FIG. 15) is pressed back and forth. Load-displacement characteristics were measured. The amount of displacement was measured at a predetermined position in a substantially middle portion of the back side rigid jig 1000. FIG. 16 shows the measurement result, and the measurement result using the seat reclining device 10 of the present embodiment in which the rolling member 80 made of a metal sphere is disposed is “Test Example 1”, and for the seat of the present embodiment. The measurement result of the structure obtained by removing the rolling member 80 from the reclining device 10 is “Comparative Example 1”. From FIG. 16, in Comparative Example 1, there is a backlash in which the load value hardly changes from the displacement amount −0.2 mm to around +0.2 mm in the backward displacement direction, and the displacement amount +0.1 mm to −0 in the forward displacement direction. .There is a play where the load value hardly changes until around 1 mm. On the other hand, in Test Example 1, it can be seen that the region where the load value does not change is not in any direction, but has changed to a spring feeling, and there is no backlash. Therefore, it can be seen that the provision of the rolling member 80 as in the seat reclining device 10 of the present embodiment is highly effective in suppressing rattling.

  Next, the seat reclining device 10 according to the present embodiment is assembled, and the seat reclining device according to Test Example 2 in which convex portions protruding radially inward are formed on the peripheral surface portion 72 of the mounting ring 70 by dowel processing. Then, the same load-displacement characteristics as in FIG. 16 were measured. The results are shown in FIG. In such a dowel processing, in a conventional seat reclining device in which the rolling member 80 is not disposed, an internal gear or the like is punched from, for example, only the front surface of the peripheral surface 72 of the mounting ring 70. This is known as a measure against backlash. As is clear from FIG. 17, as in Test Example 2, when doweling is performed after disposing the rolling member 80, the displacement amount is near +0.2 mm to +0.4 mm in any displacement direction. There is a region in which the load value hardly changes. This is considered to be due to the fact that the backlash to be eliminated by disposing the rolling member 80 causes the arrangement balance of the rolling member 80 to collapse and the wedge effect to be reduced by performing doweling. Therefore, from the comparison with Test Example 1, when the rolling member 80 is provided, it is possible to further suppress the backlash by subjecting the peripheral surface portion 72 of the mounting ring 70 to the convex portion protruding radially inward. It turns out that it does not necessarily lead to an effect. However, rattling is also suppressed in Test Example 2 as compared with Comparative Example 1 in which no rolling member 80 is provided.

(Bending moment test)
The measurement was performed by applying a load to the load point of the back-side rigid jig 1000 provided with the seat reclining device 10 shown in FIG. 15 until the seat reclining device 10 was broken. The results are shown in FIG. In FIG. 18, the measurement result using the seat reclining device 10 of the present embodiment is “Test Example 1”, and the measurement result of the structure excluding the rolling member 80 from the seat reclining device 10 of the present embodiment is “ Comparative Example 1 ”.

  First, in the case of Test Example 1, since the play is small in both the circumferential direction and the stacking direction, when the guide bracket 20 and the internal gear 30 are rotated relative to each other by a load, the lock plates 60A to 60A- 60D presses the guide wall portions 23a to 23d along the rotation direction (shear direction), and the guide wall portions 23a to 23d receive force without escaping in the stacking direction. Therefore, in Test Example 1, a load exceeding 500 Nm can be received with an initial displacement of 10 mm or less, whereas in Comparative Example 1, the load value is about half that of the initial displacement. Thereafter, due to the deformation of the guide wall portions 23a to 23d, a force in the shearing direction and a bending stress that escapes in the stacking direction act. Thus, the relationship between the displacement amount and the load value in the process in which fracture progresses due to the resultant force of both is similar in both Test Example 1 and Comparative Example 1, but the displacement amount is in the range of about 40 to 50 mm and the range after 120 mm. , A change to be a spring constant value peculiar to Test Example 1 is observed. From these, the load resistance value of Test Example 1 is improved by about 500 Nm compared to Comparative Example 1, and the displacement amount is also extended by about 20 mm, which shows that the strength is improved.

  19 to 21 are views showing a seat reclining device 100 according to still another embodiment of the present invention. The structure of the guide bracket 20, internal gear 30, spiral spring 40, cam 50, lock plates 60 </ b> A to 60 </ b> D and rolling member 80 in the seat reclining device 100 is the same as that shown in FIGS. 12 to 14. However, the structure of the mounting ring 700 is different. 12 to 14, in order to reduce the frictional resistance during rotation of the internal gear 30 with respect to the mounting ring 70 and to ensure smooth rotation, the outer peripheral edge 30 a of the internal gear 30 and the ring shape of the mounting ring 70. A sliding ring 90 having a low frictional resistance is interposed between the bottom surface 71 and a metal ball instead of the sliding ring 90 as a means for reducing the frictional resistance between them. A ball member 95 is provided. Specifically, as shown in FIGS. 21A and 21B, the ring-shaped bottom surface portion 710 of the mounting ring 700 is inward from the peripheral surface portion 720 side to the outer peripheral side periphery of the internal gear 30. The ball member 95 is formed so as to be held between the ring-shaped bottom surface portion 71 and 30a. The number of the ball members 95 is not limited, but it is preferable to arrange the ball members 95 at a plurality of locations at approximately equal intervals in the circumferential direction (in this embodiment, at three locations at approximately equal intervals in the circumferential direction). Then, convex portions 710a and 710a projecting inward from the outer surface are formed by doweling on both sides of the ring-shaped bottom surface portion 710 in the circumferential direction with the ball members 95 interposed therebetween. The rolling range in the circumferential direction is regulated.

  By disposing the ball member 95 as in the present embodiment, the frictional resistance during rotation between the internal gear 30 and the mounting ring 700 is reduced, and the lamination direction of each member is ensured while ensuring smooth rotation. It also fulfills the function of making the backlash smaller. The inwardly bent portion 711 of the ring-shaped bottom surface portion 710 processed so as to hold the ball member 95 has a bending angle of several tens of degrees (for example, 30 degrees to 60 degrees). Between the vicinity of the outer peripheral edge 30a and the outer side surface 30a2 of the outer protruding portion that protrudes outward from the position inside the inner peripheral end surface 711a, which is the front end surface of the inner bent portion 711. An inclined facing surface 30a1 having an inclined angle of several tens of degrees (for example, 30 degrees to 60 degrees) is formed. And the clearance (refer FIG.21 (c)) of the internal peripheral end surface 711a of the inward bending part 711 and the inclination opposing surface 30a1 of the internal gear 30 is set at about 0.3-0.5 mm in a normal location. On the other hand, in the circumferential direction of the inner peripheral end surface 711, it partially protrudes in the direction of the inclined facing surface 30a1, and the clearance is about 0.1 to 0.3 mm or substantially 0.1 m or less (including 0 mm). A portion having no clearance is provided (see FIG. 21D).

  The inner peripheral end surface 711a of the inwardly bent portion 711 and the inclined facing surface 30a1 are thus made to face each other at an angle of several tens of degrees (for example, 30 to 60 degrees), and the clearance can be partially narrowed and further contacted. Assuming that the clearance is substantially zero, the internal gear 30 has a function of suppressing rattling in two directions, ie, the thickness direction (member stacking direction) and the radial direction. That is, when a very narrow clearance of 0.1 to 0.3 mm is set, the backlash in two directions is suppressed to the narrow clearance range even at the maximum, and when it is substantially zero, the backlash is in two directions. There is almost no backlash. A narrow portion (including the case where the clearance is zero) between the inner peripheral end surface 711a of the inwardly bent portion 711 of the mounting ring 700 and the inclined facing surface 30a1 of the internal gear 30 is 2-3 in the circumferential direction. It is preferable to provide a portion, and when three ball members 95 are provided in the circumferential direction as described above, a portion having a narrow clearance is provided at a substantially middle portion between the adjacent ball members 95 and 95 in the circumferential direction. Is more preferable. Accordingly, the function of the ball member 95 and the function of the inner peripheral end surface 711a due to the narrow clearance portion are exhibited at a balanced position in the circumferential direction. That is, two types of backlash control functions act by the ball member 95 and the inner peripheral end surface 711a that also have a function of reducing the friction coefficient. In addition, since a metal ball made of iron can be used as the ball member 95, the ball member 95 is a rattling suppressing means that can be employed at a low cost.

  Moreover, it can replace with the attachment ring 700 shown in FIGS. 19-21, and the attachment ring 7000 shown in FIGS. 22-24 can also be used. Like the mounting ring 700 shown in FIGS. 19 to 21, the mounting ring 7000 includes convex portions 7110 and 7110 that protrude inward and are formed by doweling out of the ring-shaped bottom surface portion 7100. A ball member 95 is loaded between the convex portions 7110 and 7110.

  The ring-shaped bottom surface portion 7100 of the mounting ring 7000 is bent so as to hold the ball member 95 inward from the peripheral surface portion 7200 side. However, in the loading position of the ball member 95, FIG. 24 (a), the distance between the inner peripheral end surface 7111a of the inwardly bent portion 7111 of the ring-shaped bottom surface portion 7100 and the opposing inclined surface 30a1 in the vicinity of the outer peripheral edge 30a of the opposing internal gear 30 is 0. The shape has a normal clearance X of about 3 to 0.5 mm. At the loading position of the ball member 95, the inwardly bent portion 7111 of the ring-shaped bottom surface portion 7100 has a bending angle inclined by several tens of degrees until it comes into contact with the outer surface of the ball member 95 (see FIG. 24A). 24B and 24C, the inner peripheral end surface 7111a of the inwardly bent portion 7111 is in contact with the surface of the outer peripheral edge 30a at a substantially right angle except at the loading position of the ball member 95. Is bent. Among these, the inwardly bent portion 7111 other than the loading position of the ball member 95 is partially in the circumferential direction, and in the present embodiment, 3 is a substantially intermediate portion in the circumferential direction between the adjacent ball members 95 and 95. The inner peripheral end surface 7111a is in contact with the outer peripheral edge 30a (see FIG. 24B), and the other portions have a slight clearance Y.

  According to the present embodiment, in the ring-shaped bottom surface portion 7100, a part of the inner peripheral end surface 7111 a of the inward bent portion 7111 is in contact with the surface of the outer peripheral edge 30 a of the internal gear 30 at a substantially right angle. As a result, the internal gear 30 is pressed by the inwardly bent portion 7111 of the ring-shaped bottom surface portion 7100 in addition to the ball member 95, and the thickness direction of the internal gear 30 (the stacking direction of each member) ) Can be further reduced. Further, the internal gear 30 is not pressed in the thickness direction by a convex portion that protrudes from the ring-shaped bottom surface portion 7100 by, for example, doweling, but is adjusted by adjusting the bending angle of the inward bending portion 7111. Since the peripheral end surface 7111a is pressed against the outer peripheral side edge 30a of the internal gear 30 at a substantially right angle, the section coefficient of the portion performing the pressing function is compared with a convex portion or the like projected by dowel processing. It is high, and it is difficult for the pressing function to deteriorate due to the relative rotation of the internal gear 30. This point is also the same in the embodiment of FIGS. 19 to 21 in which the inner peripheral end surface 711a of the inward bent portion 711 is brought close to or in contact with the inclined facing surface 30a1.

  In the present embodiment, the inner bent portion 7111 has a predetermined clearance Z with respect to the outer surface of the outwardly protruding portion of the internal gear 30 (radially opposed surface that faces the inner bent portion 7111 in the radial direction) 30a2. It has composition which has. Due to the clearance Z and the clearance X at the loading position of the ball member 95, the internal gear 30 is not fixed to the mounting ring 7000 in the radial direction and has some play. In this respect, the inner peripheral end surface 711a of the inwardly bent portion 711 shown in FIGS. 19 to 21 approaches or comes into contact with the opposing inclined surface 30a1 at an inclination angle of 30 degrees to 60 degrees, and the thickness direction and the radial direction It differs from the structure which suppresses the backlash of two directions. If the internal gear 30 is fixed in the radial direction with respect to the mounting ring 7000 and there is substantially no play in the radial direction, the dimensional error of each member cannot be absorbed and smooth operation may be hindered. For this reason, the present embodiment shown in FIGS. 22 to 24 has a configuration in which some play is provided in the radial direction in consideration of this point. However, in the case where the dimensional accuracy of each member is equal to or higher than a predetermined value, there is no problem even with the configuration shown in FIGS.

  Further, as the mounting ring, the inner peripheral end surface 711a of the inwardly bent portion 711 shown in FIGS. 19 to 21 is inclined at an angle of 30 to 60 degrees, and is narrowed by 0.3 mm or less on the opposing inclined surface 30a1. Both the structure facing or substantially abutting with a clearance and the structure where the inwardly bent portion 7111 shown in FIGS. 22 to 24 is brought into contact with the outer peripheral edge 30a of the internal gear 30 substantially at right angles. It can also be set as the structure provided with. In this case, the inwardly bent portion 711 facing the opposing inclined surface 30a1 at an angle of 30 to 60 degrees can suppress backlash in two directions, ie, the thickness direction and the radial direction, and is substantially perpendicular to the outer peripheral edge 30a. The inward bent portion 7111 that comes into contact can further suppress backlash in the thickness direction. By combining both, the backlash suppressing effect is further increased. Therefore, it is possible to adopt a configuration in which the ball member 95 used for suppressing play in the stacking direction is not provided.

10,100 Seat reclining device 20 Guide bracket 23a-23d Guide wall 23f-23i Guide groove 23f1, 23h1 Bracket side holding groove 23f2, 23h2 Inclined surface 30 Internal gear 32 Internal teeth 40 Spiral spring 50 Cam 60A-60D Lock plate 60A1, 60C1 Plate side holding groove 63 External teeth 70,700 Mounting ring 80 Rolling member 90 Sliding ring 95 Ball member

Claims (18)

A guide bracket having a plurality of guide wall portions attached to one of the seat cushion and the seat back and spaced apart in the circumferential direction, and an interface attached to the other of the seat cushion and the seat back A null gear, and a mounting ring having a peripheral surface portion fixed to one outer peripheral surface of the guide bracket or the internal gear, and the guide bracket and the internal gear are relatively rotated, whereby the seat back is A seat reclining device that supports the seat cushion so as to be reclining,
A lock plate that is disposed in a guide groove between adjacent guide walls provided in the guide bracket so as to be operable in the radial direction, and has outer teeth that engage with the internal teeth of the internal gear on the outer peripheral surface. A locking mechanism having
At the time of locking in which the outer teeth of the lock plate and the inner teeth of the internal gear are meshed with each other, provided at least at one place between the respective members including the guide bracket, the internal gear and the lock plate. In the direction in which the operation clearance between the lock plate and the guide wall portion is reduced by the force of rotating the guide bracket and the internal gear relative to each other, and the operation clearance in the stacking direction of the respective members disposed in a stacked manner. A reclining device for a seat, comprising: a rolling member forcing in both directions of the direction of reduction.   2. The seat reclining device according to claim 1, wherein the rolling member is disposed at at least one position between the opposing surfaces of the guide groove portion of the guide bracket and the lock plate.   An arrangement position of the rolling member is a line connecting an outer end edge of one guide wall portion and an inner end edge of the other guide wall portion sandwiching the guide groove portion, and an inner side of the one guide wall portion. The seat reclining device according to claim 1, wherein the seat reclining device is located on an outer peripheral side of an intersection of a line connecting the end edge and the outer end edge of the other guide wall portion. A holding groove is formed on each of the facing surfaces of the guide groove portion of the guide bracket and the lock plate at least at one place where the rolling member is disposed,
When the rolling member is held by the holding grooves, and a force for rotating the guide bracket and the internal gear is applied at the time of locking, the rolling member is pressed against any part of the holding grooves and moves. The reclining device for a seat according to claim 2 or 3 to be regulated.   One of the holding grooves formed on each of the opposed surfaces has a diameter of the rolling member in both the radial direction and the circumferential direction so as to allow displacement in the radial direction and the circumferential direction of the rolling member. The seat reclining device according to claim 4, wherein the seat reclining device has a length exceeding the length.   The seat reclining device according to claim 5, wherein an inclined surface is formed on a groove bottom surface of one holding groove having a length exceeding a diameter of the rolling member in both the radial direction and the circumferential direction.   A groove having a substantially V-shaped cross section serving as an initial placement position of the rolling member on the bottom surface of one holding groove having a length exceeding the diameter of the rolling member in both the radial direction and the circumferential direction The reclining device for seats according to claim 5 or 6 in which is formed.   The groove width along the radial direction of the other holding groove facing the one holding groove having a length exceeding the diameter of the rolling member in both the radial direction and the circumferential direction is from the vicinity of the center in the circumferential direction. The reclining device for a seat according to any one of claims 5 to 7, wherein each end portion side is also narrowly formed.   The said rolling member is provided in multiple numbers, The said rolling member is each arrange | positioned between each opposing surface of the one or more lock plates among them and each said guide groove part corresponding to it. The seat reclining device according to claim 1.   Between the opposing surfaces of the pair of lock plates provided at positions opposed to each other across the rotation center where the guide bracket and the internal gear rotate relative to each other and the corresponding guide groove portions, respectively, The seat reclining device according to claim 9, wherein a rolling member is disposed.   The mounting ring includes a ring-shaped bottom surface portion having an inner circumferential circle facing the guide bracket or the internal gear, and the ring-shaped bottom surface portion is bent inward from the circumferential surface portion side. It has an inwardly bent portion, and an inner peripheral end surface of the inwardly bent portion is opposed to the opposed inclined surface of the guide bracket or the internal gear in an oblique direction, and the opposed inclined surface is more than other portions. The seat reclining device according to any one of claims 1 to 10, wherein the seat reclining device is configured to partially include a portion that is close to or abuts.   The mounting ring includes a ring-shaped bottom surface portion having an inner circumferential circle facing the guide bracket or the internal gear, and the ring-shaped bottom surface portion is bent inward from the circumferential surface portion side. 11. It has an inward bending part, The inner peripheral end surface of this inward bending part partially has the site | part which contact | abuts substantially perpendicularly to the surface of the outer peripheral peripheral part of the said guide bracket or the said internal gear. The reclining device for seats according to any one of the above.   A predetermined clearance is provided between the inwardly bent portion of the ring-shaped bottom surface portion and the guide bracket or the radially opposing surface of the internal gear that is radially opposed to the inwardly bent portion, and the guide The seat reclining device according to claim 12, wherein the bracket or the internal gear is not fixed in a radial direction with respect to the mounting ring. The mounting ring includes a ring-shaped bottom surface portion having an inner circumferential circle facing the guide bracket or the internal gear, and the ring-shaped bottom surface portion is bent inward from the circumferential surface portion side. It has an inwardly bent portion, and an inner peripheral end surface of the inwardly bent portion is opposed to the opposed inclined surface of the guide bracket or the internal gear in an oblique direction, and the opposed inclined surface is more than other portions. Partially has a close or abutting part, and
The seat according to any one of claims 1 to 10, wherein an inner peripheral end surface of the inwardly bent portion partially has a portion that abuts substantially perpendicularly to a surface of an outer peripheral edge of the guide bracket or the internal gear. Reclining device.   15. A means for reducing a frictional resistance between the mounting ring and one of the guide bracket or the internal gear that rotates relative to the mounting ring is provided. The reclining device for seats according to any one of the above.   The mounting ring has a ring-shaped bottom surface portion provided with an inner circumferential circle facing the guide bracket or the internal gear, and the means for reducing the frictional resistance includes the ring-shaped bottom surface portion, the guide bracket or the The seat reclining device according to claim 15, which is a sliding ring provided between the internal gear and the internal gear.   The mounting ring has a ring-shaped bottom surface portion provided with an inner circumferential circle facing the guide bracket or the internal gear, and the means for reducing the frictional resistance includes the ring-shaped bottom surface portion, the guide bracket or the The seat reclining according to claim 15, further comprising ball members disposed at a plurality of positions at substantially equal intervals in the circumferential direction between the internal gear and the internal gear. In a seat with a seat cushion and a seat back,
The seat reclining device according to any one of claims 1 to 17, wherein the seat reclining device is disposed between the seat cushion and the seat back.