JP5234915B2 - Reclining device - Google Patents

Description

  The present invention relates to a reclining device used in a vehicle or the like, and more particularly to a taumel-type reclining device that adjusts an inclination angle of a seat back steplessly.

  A so-called taumel-type reclining device, as disclosed in Patent Document 1, is provided with an external gear on one and the other of the pivot portions of a lower arm fixed to a seat cushion and an upper arm fixed to a seat back, and an external gear of the external gear. Either an external gear or an internal gear is fixed by an internal gear having internal teeth with more teeth than the teeth, and a rotary shaft that is coaxially and rotatably fitted to the external gear or the internal gear. By changing the meshing position of the external teeth and the internal teeth while eccentrically moving one of them around the other axis, it is possible to adjust the stepless angle of the seat back.

More specifically, a circular hole is formed in one of the shaft portions of the external gear and the internal gear, and a cylindrical portion having an outer surface smaller in diameter than the circular hole is provided in the other shaft portion. In the state where the external gear and the internal gear mesh with each other, the center of the cylindrical portion is positioned eccentric to the center of the circular hole. A pair of wedge-shaped members are inserted into the eccentric space between the circular hole and the cylindrical portion. The pair of wedge-shaped members are biased in a direction in which the wedge is driven between the circular hole and the cylindrical portion, and the relative movement between the external gear and the internal gear is normally prohibited. On the other hand, when the wedge-shaped member is moved in the direction of pulling out the wedge against the urging force by rotating the wedge releasing member with the center of the cylindrical portion as the rotation axis, relative movement between the external gear and the internal gear is allowed. The angle of the upper arm relative to the lower arm can be changed.
JP 2006-204891 A

  In the reclining device as described above, if the wedge-shaped member is not smoothly slid when adjusting the angle of the seat back, abnormal noise is generated during operation, operability is impaired, or part of the sliding surface is unevenly worn, etc. In order to be in an unpreferable state, measures have been taken such as coating the sliding surface of the wedge-shaped member to improve the sliding performance and applying grease as a lubricant. An object of the present invention is to provide a reclining device that is more excellent in sliding smoothness of the wedge-shaped member than before.

The present invention provides an external gear fixed to one of a seat cushion and a seat back so as to be positioned at the center of tilting of the seat back, and the number of teeth than the external teeth meshing with the external teeth of the external gear. Internal gears that have a large number of internal teeth and are fixed to the other of the seat cushion and the seat back, and large-diameter circular holes that are provided around the respective axes of one of the external gears and the internal gear. And a cylindrical portion having a smaller diameter than the circular hole, and an outer cylindrical surface and an inner cylindrical surface, which are inserted into an eccentric space between the inner surface of the circular hole and the outer surface of the cylindrical portion, and have different central axis positions, A pair of wedge-shaped members whose thickness in the width direction connecting the inner cylindrical surfaces changes in a wedge shape, and an urging means for urging the pair of wedge-shaped members in a wedge driving direction that restricts the relative movement of the external gear and the internal gear And a pair of wedge-shaped members as urging means. A wedge release member that changes the meshing position of the external teeth and the internal teeth while rotating one of the external gears and the internal gears eccentrically with respect to the other by rotating in a loosening direction opposite to the wedge driving direction. In the reclining device, the positions of the pair of wedge-shaped members that are pressed by the respective wedge release members are shifted in the direction along the rotation axis of the wedge release member, and the internal gear and the external gear side a normal thickness portion of the outer tube surface and the inner circumferential surface and both side surfaces, and the wedge releasing member having an abutment surface which abuts a sliding surface of, defined by an extension virtual surface of the outer cylinder surface and the inner circumferential surface It is characterized by forming a lubricant inflow portion thinner than the wall thickness to be formed. According to this configuration, the lubricant can easily flow into the inner cylindrical surface and the outer cylindrical surface, which are the sliding surfaces of the wedge-shaped member, and the sliding smoothness can be improved. Further, the lubrication performance can be further improved by preventing the lubricant from leaking to the region other than the portion where the normal thick portion requires lubrication. Moreover, since the applied force portion by the wedge releasing member is a wide normal thick portion, it is advantageous in terms of strength.

The present invention is also the end on the side which is pressed into the wedge releasing member of the pair of wedge members provided in the reclining device described above, at different positions in the direction along the rotation axis of the wedge releasing member, the wedge release A contact surface on which the member contacts and a lubricant inflow portion, and the lubricant inflow portion is formed as a portion thinner than a wall thickness defined by an outer virtual surface of the wedge-shaped member and an extended virtual surface of the inner cylindrical surface. The abutting surface is an end surface facing a notch portion in which a part of the wedge-shaped member is cut out, and has a width corresponding to the thickness connecting the outer cylindrical surface and the inner cylindrical surface of the wedge-shaped member. It is said. According to this configuration, the wedge-shaped member can be easily molded while improving the smoothness of sliding by the lubricant inflow portion.

  The wedge-shaped member includes a biasing force receiving surface that receives a biasing force from the biasing member at an end opposite to the side where the lubricant inflow portion is formed, and the abutting surface of the biasing force receiving surface and the wedge releasing member Are preferably located on the same plane perpendicular to the rotational axis of the wedge release member. Thereby, when the wedge-shaped member moves, a moment that tends to cause an inclination is hardly generated, and the wedge-shaped member can be operated smoothly.

  The outer cylindrical surfaces of the pair of wedge-shaped members are cylindrical surfaces having substantially the same curvature as the outer cylindrical guide surface on the circular hole side where the outer cylindrical surfaces are slidably in contact, and the inner cylindrical surfaces of the pair of wedge-shaped members are The cylindrical surface is preferably a cylindrical surface having substantially the same curvature as the cylindrical guide surface on the cylindrical portion side that is slidably in contact with the cylindrical surface. Thereby, the contact surface pressure per unit area in the outer cylinder surface and inner cylinder surface side of a wedge-shaped member can be lowered | hung, and it can contribute to the improvement of sliding smoothness.

  According to the reclining device of the present invention described above, providing the lubricant inflow portion makes it easier to guide the lubricant to the sliding surface portion of the wedge-shaped member, and the smoothness of sliding of the wedge-shaped member can be improved. And in the aspect which provided the normal thick part and the lubricant inflow part in the edge part of the wedge-shaped member, smoothness of sliding can be improved more by preventing leakage of a lubricant by the normal thick part. In the aspect in which the lubricant inflow portion and the notch portion are provided at the end of the wedge-shaped member, the wedge-shaped member can be easily formed while improving the smoothness of sliding. In addition, the contact surface of the wedge release member and the biasing force receiving surface of the biasing member in the wedge-shaped member are in a positional relationship in which a moment in the falling direction is unlikely to occur, or the contact between the outer cylindrical surface and the inner cylindrical surface of the wedge-shaped member The smoothness of sliding is also improved by reducing the surface pressure.

  First, a schematic configuration of a Taumel type both reclining device as an object of the present invention will be described. 1 is fixed to a frame (not shown) of a seat cushion by a bolt or the like. In the lower arm 10, there are six fitting holes 11 (two of which appear in FIG. 1) around the position of the seat back tilt center (the portion intersecting the seat back tilt center axis). It is drilled to be located on the same circumference.

  The upper arm 20 is fixed to a seat back frame (not shown) by bolts or the like. In the upper arm 20, there are six fitting holes 21 (two of which appear in FIG. 1) around the seat back tilt center position (a portion intersecting the seat back tilt center axis). It is drilled so as to be located on the same circumference.

  The gear mechanism 30 is mounted between the lower arm 10 and the upper arm 20 and adjusts the inclination angle of the upper arm 20. The lower arm 10 is fitted to the external gear 31 and the internal gear 32 in the gear mechanism 30. A plurality of fixing protrusions 31 a and 32 a that are fitted into the hole 11 and the fitting hole 21 of the upper arm 20 are provided.

  As shown in FIG. 4, the external gear 31 has a substantially disk shape, and an external tooth 31 b is formed on the outer peripheral surface, and a cylindrical portion 31 c is formed in the center. An annular recess 31d is formed around the cylindrical portion 31c. The external gear 31 is positioned by fitting six fixing protrusions 31 a formed on the side surface into the fitting hole 11 of the lower arm 10, and is welded to the lower 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 (circular hole) 32 c is formed in the center of the internal gear 32. The through hole 32c is formed inside the cylindrical rib-shaped portion 32f, and an annular recess 32d is formed in a region between the cylindrical rib-shaped portion 32f and the internal teeth 32b. The internal gear 32 is positioned by fitting the six fixed protrusions 32 a on the side surface into the fitting holes 21 of the upper arm 20, and is welded to the upper arm 20 after this positioning.

  A cylindrical shaft portion 33a of a rotating shaft (wedge release member) 33 shown in FIG. 3 is rotatably fitted in the cylindrical portion 31c of the external gear 31. The rotation shaft 33 is rotated forward and backward with the center of the inner cylindrical surface of the cylindrical portion 31c as a rotation axis. The rotating shaft 33 has a disk-like flange portion 33b at the tip of the cylindrical shaft portion 33a, and has a sector shape protruding from the flange portion 33b in the outer diameter direction centering on the rotating shaft (axis line of the cylindrical shaft portion 33a). It has a striker portion 33c. A connecting serration 33d is cut in the inner cylindrical surface of the cylindrical shaft portion 33a.

  A cylindrical bush 34 having excellent wear resistance is fitted into and fixed to the through hole 32c of the internal gear 32. Further, between the inner cylinder guide surface S1 constituted by the outer cylinder surface of the cylindrical portion 31c of the external gear 31 and the outer cylinder guide surface S2 constituted by the inner cylinder surface of the bush 34, both guide surfaces S1 are provided. A pair of wedge-shaped members 35 and 36 are inserted so as to be slidably in contact with S2.

  The wedge-shaped members 35 and 36 have a plane-symmetric shape, and the detailed structure of the wedge-shaped member 35 will be described with reference to FIGS. The wedge-shaped member 35 includes an inner cylindrical surface 35a having a cylindrical surface whose diameter size and curvature are substantially the same as those of the inner cylinder guide surface S1, and an outer surface having a cylindrical surface having substantially the same diameter size and curvature as those of the outer cylinder guide surface S2. And a cylindrical surface 35b. The inner cylinder surface 35a and the outer cylinder surface 35b of the wedge-shaped member 35 do not have the same center axis, and the thickness of the wedge-shaped member 35 is changed to a wedge shape. In the following description, in the wedge-shaped member 35, the end in the circumferential direction on the side where the thickness in the width direction connecting the inner cylindrical surface 35a and the outer cylindrical surface 35b is increased is referred to as the thick end, and the thickness in the width direction is referred to. The end in the circumferential direction on the side where is small is referred to as a thin end.

  The wedge-shaped member 35 is inclined at one side of the thin-walled end portion so as to be closer to the center in the width direction than the virtual surface obtained by extending the inner cylinder surface 35a following the inner cylinder surface 35a (inner cylinder A non-sliding surface 35c (concave with respect to the extended virtual surface of the surface 35a) is formed, and the outer cylindrical surface 35b is extended on the other side of the thin end portion following the outer cylindrical surface 35b. A non-sliding surface 35d that is inclined so as to be closer to the center in the width direction than the virtual surface (recessed with respect to the extended virtual surface of the inner cylindrical surface 35a) is formed. The non-sliding surfaces 35c and 35d are non-parallel planes that gradually narrow each other as the wedge-shaped member 35 progresses from the thick end portion side to the thin end portion side. The portion sandwiched between the non-sliding surfaces 35c and 35d is a lubricant inflow portion 35f that is thinner than the wall thickness defined by the extended virtual surface of the inner cylinder surface 35a and the outer cylinder surface 35b.

  When the direction along the rotation axis of the rotating shaft 33 is defined as the height direction of the wedge-shaped member 35, the lubricant inflow portion 35f is not formed in the entire region in the height direction, but is formed at the thin end portion of the wedge-shaped member 35. There is also a region where the inner cylinder surface 35a and the outer cylinder surface 35b are formed without interruption up to the tip. That is, the thin end portion of the wedge-shaped member 35 has a normal thick portion 35e whose both sides in the width direction (thickness direction) are defined by the inner cylindrical surface 35a and the outer cylindrical surface 35b, and the width direction (thickness direction). The above-described lubricant inflow portion 35f, whose both side portions are defined by the non-sliding surfaces 35c and 35d, is formed at different positions in the height direction. The circumferential end surfaces of the normal thick portion 35e and the lubricant inflow portion 35f are substantially flush with each other, and the end surface of the normal thick portion 35e is a striker contact surface that is substantially parallel to the rotation axis of the rotary shaft 33 ( The contact surface of the wedge releasing member) is 35 g. The normal thick part 35e and the lubricant inflow part 35f are connected by a tapered surface that gradually increases in width from the lubricant inflow part 35f side to the normal thick part 35e side.

  In the wedge-shaped member 35, spring holding projections 35h and 35i are formed on the thick end opposite to the thin end where the normal thick portion 35e and the lubricant inflow portion 35f are formed. As shown in FIG. 9, the spring holding projections 35h and 35i form a partially cylindrical spring end insertion space 35j that is partially opened. The spring holding convex portion 35 h formed on the inner diameter side following the inner cylindrical surface 35 a has a substantially uniform cross-sectional shape toward the height direction of the wedge-shaped member 35. On the other hand, the spring holding convex portion 35i formed on the outer diameter side following the outer cylindrical surface 35b has a partial region in the height direction removed, and the spring engagement convex portion 35i is removed from the region where the guide convex portion 35i is removed. A mating surface (biasing force receiving surface) 35k is formed. As shown in FIG. 11, the spring engagement surface 35k is formed at substantially the same position as the striker contact surface 35g on the thin end portion side in the height direction of the wedge-shaped member 35. In other words, the striker contact surface 35g and the spring engagement surface 35k are located on the same plane orthogonal to the rotation axis of the rotation shaft 33.

  The wedge-shaped member 36 that is symmetrical to the wedge-shaped member 35 has the same structure. That is, the inner cylindrical surface 36a and the outer cylindrical surface 36b of the wedge-shaped member 36 are substantially the same as the inner cylindrical guide surface S1 on the external gear 31 side and the outer cylindrical guide surface S2 on the bush 34 (internal gear 32 side), respectively. It has a diameter size and a curvature, and the central axes thereof do not coincide with each other, and the thickness of the wedge-shaped member 36 is changed to a wedge shape. The thin end portion which is one end portion in the circumferential direction of the wedge-shaped member 36 has a thin lubricant inflow portion 36f whose side portions in the width direction (thickness direction) are defined by the non-sliding surfaces 36c and 36d, The inner cylindrical surface 36a and the outer cylindrical surface 36b form a normal thick portion 36e whose side in the width direction (thickness direction) is defined, and the circumferential end surface of the normal thick portion 36e is the rotating shaft 33. The striker contact surface (contact surface of the wedge release member) 36g is substantially parallel to the rotation axis of this. Further, on the thick end portion which is the other end portion in the circumferential direction of the wedge-shaped member 36, a spring holding convex portion 36h formed in the whole area in the height direction and a spring holding convex portion 36i formed up to a middle position in the height direction. And a spring end insertion space 36j surrounded by the spring holding projections 36h and 36i is formed. A spring engagement surface (biasing force receiving surface) is provided at a position substantially the same as the striker contact surface 36g (a position on the same plane orthogonal to the rotation axis of the rotation shaft 33) at the portion where the guide convex portion 36i is cut out. 36k is formed.

  The wedge-shaped members 35, 36 are arranged between the inner cylinder guide surface S1 on the external gear 31 side and the outer cylinder guide surface S2 on the bush 34 side (internal gear 32 side) so that the thick end portions thereof face each other. Inserted into. In this inserted state, the inner cylindrical surfaces 35a and 36a of the wedge-shaped members 35 and 36 are slidably in contact with the inner cylindrical guide surface S1, and the outer cylindrical surfaces 35b and 36b of the wedge-shaped members 35 and 36 are respectively outer cylinders. The guide surface S2 is slidably contacted. At this time, the non-sliding surfaces 35c, 36c of the wedge-shaped members 35, 36 are separated from the inner cylinder guide surface S1, and a grease reservoir space G1 is formed between the wedge-shaped members 35, 36 and the inner cylinder guide surface S1. Similarly, the non-sliding surfaces 35d, 36d of the wedge-shaped members 35, 36 are separated from the outer cylinder guide surface S2, and a grease pool space G2 is formed between the outer cylinder guide surface S2. Between the inner cylinder surfaces 35a and 36a and the outer cylinder surfaces 35b and 36b of the wedge-shaped members 35 and 36, and the inner cylinder guide surface S1 and the outer cylinder guide surface S2, the sliding surface is prevented from being worn and the sliding is smooth. Grease for increasing the viscosity is applied. Moreover, the coating which reduces sliding resistance is given on these sliding surfaces.

  The wedge-shaped members 35 and 36 receive a biasing force in a direction away from a spring (biasing means) 37 as an elastic member. The spring 37 rises in the axial direction of the annular portion 37a from the annular portion 37a of one turn, radial bent portions 37b and 37b bent from the annular portion 37a in the inner diameter direction, and radial bent portions 37b and 37c. The annular portion 37a is supported in an annular step portion formed by the cylindrical rib-like portion 32f of the internal gear 32. The axial end portions 37d and 37e protrude from the radial bent portions 37b and 37b in a direction approaching the lower arm 10 (right direction in FIG. 1), and the axial end portion 37d is a spring of the wedge-shaped member 35. The axial end 37e is inserted into the spring end insertion space 36j surrounded by the spring holding projections 36h and 36i of the wedge-shaped member 36, and is inserted into the spring end insertion space 35j surrounded by the holding projections 35h and 35i. . At this time, the radially bent portions 37b and 37c of the spring 37 abut on the spring engaging surfaces 35k and 36k of the wedge-shaped members 35 and 36, and the wedge-shaped members 35 and 36 are separated from each other (the direction in which the thin-walled end portions are approached). ). In other words, in the wedge-shaped members 35 and 36, the spring engaging surfaces 35 k and 36 k are areas where the urging force of the spring 37 is applied.

  The wedge-shaped members 35 and 36 described above are configured to decenter the internal gear 32 with respect to the external gear 31 and to mesh the internal teeth 32b with the external teeth 31b. In the wedge-shaped members 35 and 36, the center axes of the inner cylindrical surfaces 35a and 36a and the outer cylindrical surfaces 35b and 36b do not coincide with each other, so that the external gear 31 on the side having the inner cylindrical guide surface S1 The internal gear 32 on the side having the tube guide surface S2 is eccentrically positioned, and the internal teeth 32b are engaged with the external teeth 31b in the eccentric state. Through the wedge-shaped members 35 and 36, the rotary shaft 33 changes the meshing position of the external teeth 31b and the internal teeth 32b while eccentrically moving the through hole 32c (bush 34) with respect to the cylindrical portion 31c. The external gear 31 and the internal gear 32 can be moved relative to each other.

  Specifically, in a state where the cylindrical shaft portion 33a of the rotating shaft 33 is rotatably supported by the cylindrical portion 31c of the external gear 31, the striker portion 33c of the rotating shaft 33 is a striker of the wedge-shaped member 35 and the wedge-shaped member 36. The pressing surface 33c1, which is located at the circumferential position between the contact surfaces 35g, 36g, is the one circumferential end surface of the striker portion 33c, faces the striker contact surface 35g, and is the other circumferential end surface. 33c2 faces the striker contact surface 36g. When the rotating shaft 33 rotates counterclockwise in FIG. 6, the pressing surface 33 c 1 of the striker portion 33 c comes into contact with the striker contact surface 35 g of the opposing wedge-shaped member 35, and resists the biasing force of the spring 37, so that the wedge-shaped member 35 can be pressed in the approaching direction with the thick end of the wedge-shaped member 36. Conversely, when the rotating shaft 33 rotates clockwise in FIG. 6, the pressing surface 33 c 2 of the striker portion 33 c comes into contact with the striker contact surface 35 g of the wedge-shaped member 36 on the opposite side and resists the biasing force of the spring 37. The wedge-shaped member 36 can be pressed in the approaching direction with the thick end portion of the wedge-shaped member 35.

  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 (see FIG. 1). Thereby, it can control that the external gear 31 and the internal gear 32 leave | separate in an axial direction. An annular groove 33e is cut at the tip of the rotary shaft 33, and a retaining ring 39 is locked there.

  In the above reclining device, a pair is symmetrically arranged on both sides of each seat, and the left and right rotary shafts 33 are connected via a connecting shaft 13 (FIG. 1) inserted and fixed between serrations 33d of the cylindrical shaft portion 33a. It is connected. The connecting shaft 13 and the rotating shaft 33 are rotationally driven when adjusting the inclination angle of the seat back.

  In the above reclining device, the spring 37 biases the wedge-shaped members 35 and 36 away from each other in a state in which no rotational operation force is applied to the connecting shaft 13 (the rotating shaft 33) from the outside, and both the wedge-shaped members 35 and 36 are urged. Is given the force in the direction of driving the wedge. Therefore, relative movement between the internal gear 32 and the rotary shaft 33 is prohibited, the gear mechanism 30 is in a locked state, and the seat back is locked at that position.

  In this locked state, when the rotating shaft 33 is rotated, for example, counterclockwise in FIGS. 2 and 6, the pressing surface 33c1 of the rotating shaft 33 abuts against the striker contact surface 35g of the wedge-shaped member 35, and the wedge-shaped member 35 is separated from the gap. Accordingly, the rotation shaft 33 and the wedge-shaped member 35 rotate counterclockwise with respect to the internal gear 32. As a result, a gap is generated between the wedge-shaped member 35 and the peripheral member, and the internal gear 32 can be moved. Then, the wedge-shaped member 36 receiving the urging force of the spring 37 rotates counterclockwise so as to fill this gap.

  By this interlocking operation, the wedge-shaped members 35 and 36 rotate counterclockwise together with the rotating shaft 33. Similarly, with respect to the clockwise rotation, the pressing surface 33c2 of the rotating shaft 33 abuts against the striker contact surface 36g of the wedge-shaped member 36, and a force in the direction of pulling out the wedge-shaped member 36 from the gap is applied. , 35 are rotated clockwise together with the rotary shaft 33. 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 33, the gear mechanism 30 changes from the locked state to the unlocked state, and the external gear 31b and the internal teeth 32b move while the internal gear 32 moves eccentrically with respect to the external gear 31. Change the meshing position. As a result, the upper arm 20 can be tilted with respect to the lower arm 10, and the tilt angle of the seat back can be adjusted.

  In the gear mechanism 30, stopper protrusions 31 e and 32 e are provided on the external gear 31 and the internal gear 32 in order to regulate the maximum tilt angle of the upper arm 20 with respect to the lower arm 10. The stopper projection 31e of the external gear 31 protrudes into the recess 31d from the inner peripheral portion of the external gear 31b toward the cylindrical portion 31c, and the stopper projection 32e of the internal gear 32 is a cylindrical rib-shaped portion 32f. It protrudes in the recessed part 32d toward the internal tooth 32b side from the outer peripheral part. When a predetermined amount of relative rotation occurs between the external gear 31 and the internal gear 32, the side surfaces of the stopper protrusions 31e and 32e come into contact with each other to restrict the rotational operation and limit the further angle change of the seat back. Is done.

  In the reclining device configured as described above, as described above, the lubricant inflow having the concave side portions that do not contact the inner cylinder guide surface S1 and the outer cylinder guide surface S2 at the thin end portion of the wedge-shaped member 35. A portion 35f is formed, a grease pool space G1 is formed between the non-sliding surface 35c and the inner cylinder guide surface S1, and a grease pool space G2 is formed between the non-sliding surface 35d and the outer cylinder guide surface S2. Is formed. Similarly, in the wedge-shaped member 36, a lubricant inflow portion 36f having a concave side portion that does not contact the inner cylinder guide surface S1 and the outer cylinder guide surface S2 is formed at the thin end portion. A grease reservoir space G1 is formed between the surface 36c and the inner cylinder guide surface S1, and a grease reservoir space G2 is formed between the non-sliding surface 36d and the outer cylinder guide surface S2. When the wedge-shaped members 35 and 36 are moved in the circumferential direction during the tilting operation of the seat back, these grease reservoir spaces G1 and G2 function as an introduction portion for the grease for lubrication, and the inner cylinder that is a sliding contact surface on the inner diameter side Grease easily enters between the surfaces 35a, 36a and the inner cylinder guide surface S1, and between the outer cylinder surfaces 35b, 36b, which are sliding surfaces on the outer diameter side, and the outer cylinder guide surface S2. Therefore, the lubricating performance is improved and the wedge-shaped members 35 and 36 can be operated smoothly as compared with the case where the grease reservoir spaces G1 and G2 are not provided, and abnormal noise during operation and uneven wear of the sliding surface are prevented. Can be prevented.

  Further, at the thin-walled ends of the wedge-shaped members 35, 36, the positions of the lubricant inflow portions 35f, 36f are different from each other in the height direction, and the normal thick portions 35e, which are wider than the lubricant inflow portions 35f, 36f, By providing 36e, it becomes difficult for grease to flow out in the height direction from the grease reservoir spaces G1, G2, and between the inner cylinder surfaces 35a, 36a, which are sliding surfaces, and the inner cylinder guide surface S1, the outer cylinder surface 35b, It is possible to efficiently send grease between 36b and the outer cylinder guide surface S2.

  Further, the inner cylindrical surfaces 35a, 36a of the wedge-shaped members 35, 36 are formed as cylindrical surfaces having substantially the same curvature as the inner cylindrical guide surface S1 on the external gear 31 side, and these contact surface pressures (per unit area) Surface pressure) is kept low. Similarly, the outer cylindrical surfaces 35b and 36b of the wedge-shaped members 35 and 36 are formed as cylindrical surfaces having substantially the same curvature as the outer cylindrical guide surface S2 on the bush 34 (internal gear 32) side. (Surface pressure per unit area) is kept low. In this way, by making the curvatures of the sliding contact surfaces the same and reducing the contact surface pressure, coupled with the provision of the grease reservoir spaces G1 and G2, a smoother operation of the wedge-shaped members 35 and 36 is achieved. ing.

  Further, as can be seen from FIG. 11, in the wedge-shaped member 35, the engagement area between the radial bent portion 37 b, which is the biasing force applying portion by the spring 37, and the spring engaging surface 35 k, and the wedge releasing force applying force by the rotating shaft 33. The engagement area between the pressing surface 33c1 and the striker contact surface 35g, which is a portion, overlaps in a plane direction (left-right direction in FIG. 11) orthogonal to the rotation axis of the rotation shaft 33. In other words, the spring 37 and the rotary shaft 33 are in a relationship of pressing the wedge-shaped member 35 at substantially the same position in the height direction (vertical direction in FIG. 11) along the rotation axis of the rotary shaft 33. Thus, when the striker contact surface 35g is pressed by the pressing surface 33c1, a moment that tends to tilt the wedge-shaped member 35 with respect to a plane orthogonal to the rotation axis of the rotating shaft 33 is less likely to occur. The same applies to the wedge-shaped member 36. The engagement region between the radial bent portion 37c and the spring engaging surface 36j, which is a biasing force applying portion of the spring 37, and the pressing surface 33c2 that is the wedge releasing force applying portion of the rotating shaft 33. When the striker contact surface 36g is pressed by the pressing surface 33c2, the engagement region between the contact surface 36g and the striker contact surface 36g presses the wedge-shaped member 36 at substantially the same position in the height direction along the rotation axis of the rotary shaft 33. In addition, a moment for tilting the wedge-shaped member 36 with respect to a plane orthogonal to the rotation axis of the rotation shaft 33 is unlikely to occur.

  Further, as can be seen from FIG. 6, the striker contact surface 35g with which the pressing surface 33c1 of the rotary shaft 33 contacts is substantially the width direction (thickness direction) connecting the inner cylindrical surface 35a and the outer cylindrical surface 35b of the wedge-shaped member 35. It is formed at the center. Therefore, when the striker contact surface 35g is pressed by the pressing surface 33c1 to perform the wedge releasing operation, a moment of falling toward the inner diameter side or the outer diameter side is unlikely to occur. Similarly, the wedge-shaped member 36 has a striker contact surface 36g formed at a substantially central portion in the width direction (thickness direction) connecting the inner cylindrical surface 36a and the outer cylindrical surface 36b. When the striker contact surface 36g is pressed to perform the wedge releasing operation, a moment of falling toward the inner diameter side or the outer diameter side is unlikely to occur. Thus, the structure in which the moment of tilting or tilting hardly occurs during the wedge releasing operation also improves the smoothness of the operation of the wedge-shaped members 35 and 36.

  In addition, in the wedge-shaped members 35 and 36, spring-engaging surfaces 35k and 36k are formed by spring-holding convex portions 35i and 36i in a form in which a part in the height direction is cut out. On the other hand, by adopting a configuration in which the radially bent portions 37b and 37c of the spring 37 are engaged, the height of the spring 37 in the direction of the rotation axis of the rotary shaft 33 can be kept low, and the gear mechanism 30 can be made thin. Has contributed.

FIG. 12 shows a different embodiment of the wedge-shaped member. The wedge-shaped member 35 (36) of the previous embodiment is formed such that the circumferential end surfaces of the normal thick portion 35e (36e) and the lubricant inflow portion 35f (36f) at the thin end portion are substantially flush. . On the other hand, in the thin end portion of the wedge-shaped member 135 in FIG. 12, a part in the height direction is the lubricant inflow portion 135f formed by the non-sliding surfaces 135c and 135d in common with the previous embodiment. However, the remaining portion in the height direction corresponding to the normal thick portion 35e of the previous embodiment is a notch portion 135e where there is no flesh, and the wedge portion is extended on the circumferential extension of the notch portion 135e. A striker contact surface 135g for receiving a pressing operation force in the release direction is formed. The striker contact surface 135g has a width corresponding to the thickness connecting the inner cylindrical surface 35a and the outer cylindrical surface 35b of the wedge-shaped member 135. The wedge-shaped member 135 of this form has an advantage that it is easy to mold during manufacture while improving the smoothness of sliding by the lubricant inflow portion 135f. In FIG. 12, only one wedge-shaped member 135 of the pair is shown, but the other wedge-shaped member forming a pair also has the same structure.

  As mentioned above, although demonstrated based on illustration embodiment, this invention is not limited to this embodiment, It is possible to set it as a different structure unless it deviates from the main point of invention. For example, in the wedge-shaped member of the illustrated embodiment, the non-sliding surfaces 35c, 35d, 36c, 36d, 135c, and 135d formed in the lubricant inflow portions 35f, 36f, and 135f are flat surfaces, but may be curved surfaces.

  In the illustrated embodiment, the grease pool spaces G1 and G2 are formed on the extension of both the outer cylinder surface and the inner cylinder surface of the wedge member. However, this is sufficient for suppressing abnormal noise during sliding. Can be obtained, the lubricant inflow portion may be formed so that the grease reservoir space is formed only on either the outer cylinder surface side or the inner cylinder surface side.

  In the illustrated embodiment, the inner cylindrical surface of the bush 34 is the outer cylindrical guide surface S2 in which the outer cylindrical surface of the wedge-shaped member is slidably contacted. However, the bush 34 is not interposed and the inner cylindrical surface of the internal gear 32 is not inserted. It is also possible to adopt a mode in which the outer cylindrical surface of the wedge-shaped member is in sliding contact with the cylindrical surface directly.

It is a longitudinal cross-sectional view which shows an example of the Taumel type reclining apparatus provided with the external gear and the internal gear by this invention. It is the left view which showed the reclining apparatus of FIG. 1 except the upper arm and the lower arm. It is a disassembled perspective view of the principal part of the reclining apparatus of FIG. It is a figure which shows an external gear, (a) is a front view, (b) is AA sectional drawing of (a). It is a figure which shows the internal gear of the state which fitted the bush in the center through-hole, (a) is a front view, (b) is BB sectional drawing of (a). It is the side view which expanded and showed the eccentric shaft part vicinity between the internal gear in FIG. 2, and an external gear. It is a single-piece | unit perspective view of a wedge-shaped member. FIG. 8 is a single perspective view of a wedge-shaped member viewed from a direction different from that in FIG. 7. It is a top view of a wedge-shaped member. FIG. 10 is a front view of the thin-walled end side of the wedge-shaped member as viewed from the direction of arrow A in FIG. 9. FIG. 10 is a side view of the wedge-shaped member viewed from the direction of arrow B in FIG. 9. It is a perspective view which shows different embodiment of a wedge-shaped member.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Lower arm 11 Fitting hole 13 Connecting shaft 20 Upper arm 21 Fitting hole 30 Gear mechanism 31 External gear 31b External tooth 31c Cylindrical part 32 Internal gear 32b Internal tooth 32c Through hole (circular hole)
32f Cylindrical rib portion 33 Rotating shaft (wedge release member)
33c Striker portion 33c1 33c2 Press surface 34 Bush 35 36 Wedge-like member 35a 36a Inner cylindrical surface 35b 36b Outer cylindrical surface 35c 35d 36c 36d Non-sliding surface 35e 36e Normal thick portion 35f 36f Lubricant inflow portion 35g 36g Strike contact surface ( Contact surface of wedge release member)
35h 35i 36h 36i Spring holding projection 35j 36j Spring end insertion space 35k 36k Spring engagement surface (biasing force receiving surface)
37 Spring (biasing means)
37a Annular portion 37b 37b Radially bent portion 37d 37e Axial end portion 38 Holding member 39 Retaining ring 135 Wedge-like member 135c 135d Non-sliding surface 135e Notch 135f Lubricant inflow portion 135g Striker contact surface G1 G2 Grease pool space S1 Inner cylinder guide surface S2 Outer cylinder guide surface

Claims (4)

An external gear fixed to one of the seat cushion and the seat back and positioned at the center of tilting of the seat back; and
An internal gear having more teeth than the external teeth meshing with the external teeth of the external gear is formed, and an internal gear fixed to the other of the seat cushion and the seat back;
A large-diameter circular hole provided on one and the other of the external gear and the internal gear with the respective axes as centers, and a cylindrical portion having a smaller diameter than the circular hole;
Thickness in the width direction, which is inserted into an eccentric space between the inner surface of the circular hole and the outer surface of the cylindrical portion, has an outer cylindrical surface and an inner cylindrical surface with different central axis positions and connects the outer cylindrical surface and the inner cylindrical surface. A pair of wedge-shaped members that change into a wedge shape;
Urging means for urging the pair of wedge-shaped members in a wedge driving direction for restricting relative movement between the external gear and the internal gear;
The external gear is rotatably supported by the inner cylindrical portion of the cylindrical portion, abutted against and pressed against the ends of the pair of wedge-shaped members, and rotated in a loosening direction opposite to the wedge driving direction by the biasing means. And a wedge releasing member that changes the meshing position of the external teeth and the internal teeth while eccentrically moving one of the internal gears with respect to the other,
The end portions of the pair of wedge-shaped members that are pressed by the wedge release members are made to have different positions in the direction along the rotation axis of the wedge release members,
A normal thick portion having a contact surface on which the outer cylinder surface and the inner cylinder surface are both side surfaces and the wedge release member contacts ;
A lubricant inflow portion thinner than a wall thickness defined by an extended virtual surface of the outer cylinder surface and the inner cylinder surface;
A reclining device characterized by forming An external gear fixed to one of the seat cushion and the seat back and positioned at the center of tilting of the seat back; and
An internal gear having more teeth than the external teeth meshing with the external teeth of the external gear is formed, and an internal gear fixed to the other of the seat cushion and the seat back;
A large-diameter circular hole provided on one and the other of the external gear and the internal gear with the respective axes as centers, and a cylindrical portion having a smaller diameter than the circular hole;
Thickness in the width direction, which is inserted into an eccentric space between the inner surface of the circular hole and the outer surface of the cylindrical portion, has an outer cylindrical surface and an inner cylindrical surface with different central axis positions and connects the outer cylindrical surface and the inner cylindrical surface. A pair of wedge-shaped members that change into a wedge shape;
Urging means for urging the pair of wedge-shaped members in a wedge driving direction for restricting relative movement between the external gear and the internal gear;
The external gear is rotatably supported by the inner cylindrical portion of the cylindrical portion, abutted against and pressed against the ends of the pair of wedge-shaped members, and rotated in a loosening direction opposite to the wedge driving direction by the biasing means. And a wedge releasing member that changes the meshing position of the external teeth and the internal teeth while eccentrically moving one of the internal gears relative to the other, a reclining device comprising:
The end on the side that is pressed into each of the wedge releasing member of the pair of wedge-shaped members, at different positions in a direction along the axis of rotation of the wedge releasing member, abutment surface which the wedge releasing member abuts and A lubricant inflow portion,
The lubricant inflow portion is formed as a portion thinner than a wall thickness defined by an extended virtual surface of the outer cylinder surface and the inner cylinder surface,
The contact surface is an end surface facing a notch part of the wedge-shaped member, and has a width corresponding to a thickness connecting the outer cylinder surface and the inner cylinder surface. Reclining device. 3. The reclining device according to claim 1, wherein the wedge-shaped member has a biasing force receiving surface that receives a biasing force from the biasing member at an end opposite to a side where the lubricant inflow portion is formed. reclining apparatus, and abutment surface該付force receiving surface and the wedge releasing member abuts, characterized in that they are positioned on the same plane perpendicular to the axis of rotation of the wedge releasing member. 4. The reclining device according to claim 1, wherein the outer cylindrical surfaces of the pair of wedge-shaped members have substantially the same curvature as the outer cylindrical guide surface on the circular hole side where the outer cylindrical surfaces are slidably in contact with each other. The inner cylindrical surfaces of the pair of wedge-shaped members are cylindrical surfaces having substantially the same curvature as the inner cylindrical guide surface on the cylindrical portion side where the inner cylindrical surfaces are slidably in contact with each other. Reclining device.

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