JP2007111128A - Seat reclining device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a manual seat reclining device which can minutely adjust the reclining angle of a seat back and can strongly resist an external force by the seat back. <P>SOLUTION: The seat reclining device is provided with a first gearwheel body 2 fixed on a seat cushion side and is equipped with a first internally-toothed section 2a, a second gear wheel body 3 fixed on the seat back and is equipped with a second internally-toothed section 3a with teeth smaller in radius and in number than the first internally-toothed section 2a, and planet gear wheels 6 equipped with first toothed sections 6a and second toothed sections 6b which intermesh with the first and the second internally-toothed sections 2a, 3a, respectively. The first toothed section 6a and the second toothed section 6b of each planet gear wheel 6 have the same number of teeth and each tooth of the first toothed section 6a and the second toothed section 6b conforms to each counterpart in the circumference direction and an intermeshing position P1 where the first internally-toothed section 2a and the first toothed section 6a are intermeshed with each other and an intermeshing position P2 where the second internally-toothed section 3a and the second toothed section 6b are intermeshed with each other are out of alignment in the radius direction. A shaft center is provided with a planet gear wheel locking/unlocking means 7A which transforms the rotation of each planet gear wheel 6 between a lock position which prevents each planet gear wheel 6 from rotating and a lock releasing position which allows each planet gear wheel 6 to rotate. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a manual seat reclining device that adjusts an inclination angle of a seat back without using power.

  Conventional manual seat reclining devices are disclosed in Patent Document 1 and Patent Document 2. As shown in FIG. 13, the seat reclining device 100 of the first conventional example shown in Patent Document 1 includes a shaft 101 disposed on the center of rotation of a seat cushion (not shown) and a seat back (not shown), An operation lever 102 that rotates the shaft 101, a gear plate 104 that is passed through the shaft 101 and fixed to a seat back (not shown) via an arm plate 103, and a shaft 101 that passes through the base plate 105. And a housing 106 fixed to a seat cushion (not shown), a lock gear 108 and a cam plate 109 which are disposed in an internal space 107 of the housing 106 and the gear plate 104 and supported by the shaft 101.

  Inner teeth 104a and outer teeth 108a that mesh with each other are formed at the opposing positions of the gear plate 104 and the lock gear 108, respectively. The lock gear 108 is movable in the axial direction of the shaft 101, but the lock gear 108 and the housing 106 are fitted in a non-rotatable state at any position. Further, the lock gear 108 is urged by a spring 110 in a meshing release direction (a arrow direction). The cam plate 109 is provided so as to rotate integrally with the shaft 101, and the position of the lock gear 108 in the axial direction can be regulated by the rotational position.

  In the above-described configuration, when the operation lever 102 is not operated, it is located at a lock position (position in FIG. 13) where the inner tooth portion 104a of the gear plate 104 and the outer tooth portion 108a of the lock gear 108 mesh. In this locked position, the rotational force acting on the seat back (not shown) acts on the meshing position of the inner tooth portion 104a of the gear plate 104 and the outer tooth portion 108a of the lock gear 108. Since the rotation is prevented by the housing 106, the seat back (not shown) does not swing. That is, even when a rotational force acts on the seat back (not shown) in the locked position, the seat back (not shown) maintains the inclination angle.

  When the operation lever 102 is operated, the cam plate 109 is rotated together with the shaft 101, and the position restriction of the lock gear 108 is released. Then, the lock gear 108 is displaced in the direction of the arrow a by the spring force of the spring 110, and the meshing between the inner tooth portion 104a and the outer tooth portion 108a is separated and shifted to the unlocking position. When the rotational force acts on the seat back (not shown) in this unlocked position, the seat back (not shown) freely rotates because the gear plate 104 is in a freely rotating state. That is, the inclination angle of the seat back (not shown) can be varied by a manual operation in which the user applies a rotational force to the seat back (not shown). After the seat back (not shown) is adjusted to a desired inclination angle, when the operation lever 102 is returned to the original position, the lock gear 108 is shifted in the direction of the arrow a by the cam plate 109, and the internal teeth of the gear plate 104. The portion 104a and the external gear portion 108a of the lock gear 108 mesh with each other at the meshing position facing each other, and the seat back (not shown) is locked at this inclination angle.

  As shown in FIG. 14, the seat reclining device 120 of the second conventional example shown in Patent Document 2 is fixed to the seat cushion side, fixed to the seat back side, and rotatably supported by the bracket 121. The outer ring 122, the inner cam 123 fixed to the bracket 121 and accommodated in the circular groove of the outer ring 122, the compression springs 124 and the pair accommodated in a plurality of spaces on the circumference between the outer ring 122 and the inner cam 123, respectively. Steel balls 125, 125, a pair of release plates 126, 127 each having a locking projection 126a, 127a that regulates the distance between the pair of steel balls 125, 125, and the pair of release plates 126, 127 relative to each other. And an operating lever 128 to be operated.

  In the above configuration, when the operation lever 128 is not operated, the pair of steel balls 125, 125 are fitted between the outer ring 122 and the inner cam 123 by the spring force of each compression spring 124 (the position in FIG. 14). Located in. In this locked position, the rotational force acting on the seat back (not shown) acts between the outer ring 122 and the steel balls 125, 125, or between the steel balls 125, 125 and the inner cam 123. Since the rotation is prevented by the frictional force between these members, the seat back (not shown) does not swing. That is, even when a rotational force acts on the seat back (not shown) in the locked position, the seat back (not shown) maintains the inclination angle.

When the operation lever 128 is operated, the pair of release plates 126 and 127 are rotationally displaced, and both the locking projections 126a and 127a reduce the distance between the pair of steel balls 125 and 125, that is, unlocking for releasing the fitting. Displace to position. When the rotational force acts on the seat back (not shown) in the unlocked position, the seat back (not shown) freely rotates because the outer ring 122 is in a freely rotating state. That is, the inclination angle of the seat back (not shown) can be varied by a manual operation in which the user applies a rotational force to the seat back (not shown). After the seat back (not shown) is adjusted to a desired inclination angle, when the operation lever 128 is returned to the original position, the pair of steel balls 125 and 125 are returned to the fitted position again by the spring force of the compression spring 124, A seat back (not shown) is locked at this tilt angle.
JP-A-8-317829 JP 2001-137061 A

  In the first conventional example, in the locked position, the rotational force from the seat back (not shown) is received by the meshing of the inner tooth portion 104a of the gear plate 104 and the outer tooth portion 108a of the lock gear 108. Strong. However, since the seat back (not shown) can be locked only at the position where the inner tooth portion 104a of the gear plate 104 and the outer tooth portion 108a of the lock gear 108 mesh with each other, the inclination angle of the seat back (not shown) can be continuously adjusted. Cannot adjust. In addition, since the pitch of the teeth is an interval that can be directly adjusted, the interval that can be adjusted is increased when the teeth are enlarged to increase the strength.

  On the other hand, in the second conventional example, in the unlocked position, the pair of steel balls 125 and 125 and the compression spring 124 rotate together with the inner cam 123 to be fitted at any position of the outer ring 122. Therefore, the inclination angle of the seat back (not shown) can be adjusted steplessly. However, in the locked position, the rotational force from the seat back (not shown) is received by the frictional force between the outer ring 122 and the inner cam 123 and the steel balls 125, 125, so that the strength is weak.

  Therefore, the present invention has been made to solve the above-described problems, and is a manual type, in which the inclination angle of the seat back can be adjusted steplessly or at a small interval, and the external force from the seat back can be adjusted. An object of the present invention is to provide a seat reclining device that is strong in strength.

  The invention according to claim 1 is a first gear body that has a first internal gear portion that is fixed to one side of a seat cushion and a seat back and has a rotation center between the seat cushion and the seat back as an axis. It is fixed to the other side of the seat cushion and the seat back, has a rotation center between the seat cushion and the seat back as an axis, and has a second internal tooth portion having a smaller number of teeth than the first internal tooth portion. A first gear portion and a second tooth portion that mesh with the second gear body, the first inner tooth portion, and the second inner tooth portion, respectively, and have the same center and are integrally rotatable; A plurality of planetary gears supported so as to be able to revolve around the core, and the plurality of planetary gears revolve around the shaft core while changing the meshing position with the first internal gear portion and the second internal gear portion. And the first internal tooth portion and the second internal tooth portion A seat reclining device in which a tilt angle of the seat back is varied by changing a relative rotation angle between the first gear body and the second gear body due to a difference in number, wherein each planetary gear includes The first tooth portion and the second tooth portion have the same number of teeth, the teeth of the first tooth portion and the teeth of the second tooth portion are arranged at the same position in the circumferential direction, and the first inner tooth portion and the first tooth The meshing position with the part and the meshing position of the second tooth part and the second tooth part are configured to be shifted in the radial direction, and the shaft core has a lock position for preventing rotation of the planetary gear, and Planetary gear locking / unlocking means for shifting between the unlocking position allowing rotation of the planetary gear is provided.

  The invention according to claim 2 is the seat reclining device according to claim 1, wherein the planetary gear locking / unlocking means is disposed on the shaft core of the first gear body and the second gear body, A shaft that is moved in the axial direction between the lock position and the unlock position by the operation of the operation unit, and a tapered body that is provided on the outer periphery of the shaft and abuts on each gear shaft of each planetary gear, The taper body is frictionally engaged with the gear shaft at the lock position of the shaft.

  A third aspect of the invention is the seat reclining device according to the second aspect, wherein the planetary gears are arranged in a radial direction at positions where the planetary gears mesh with the first internal gear portion and the second internal gear portion deeper than a predetermined meshing position. The taper body presses the gear shaft radially outward at the shaft lock position, and the planetary gears are in deep engagement with the first internal gear portion and the second internal gear portion. Features.

  A fourth aspect of the invention is the seat reclining device according to the second or third aspect, wherein the planetary gears are engaged with the first internal gear portion and the second internal gear portion deeper than a predetermined meshing position. It is provided so as to be movable in a radial direction between a position and a shallow meshing position, and in the lock position of the shaft, the tapered body presses the gear shaft radially outward, and the planetary gears and the first internal gear portion The planetary gear moves to a position where it engages with the first internal gear and the second internal gear shallower than a predetermined meshing position at a position where the shaft is unlocked. In addition, the tooth of the first tooth portion meshing with the first internal tooth portion and the tooth of the second tooth portion meshing with the second internal tooth portion are adjacent to each other in the circumferential direction. To do.

  The invention according to claim 5 is the seat reclining device according to claim 1, wherein the planetary gear locking / unlocking means is disposed on the shaft core of the first gear body and the second gear body, A shaft that is moved in the axial direction between a locked position and an unlocked position by operation of the operating portion, and a sun gear that is provided on the outer periphery of the shaft and meshes with each planetary gear, or a shaft portion, In the lock position of the shaft, the sun gear or the shaft portion is engaged between the tooth portions of the first tooth portion or the second tooth portion of each planetary gear.

  A sixth aspect of the invention is the seat reclining device according to the fifth aspect, wherein the second internal tooth portion and the second tooth portion are formed in a tapered shape, and the teeth of the sun gear meshing with the second tooth portion. The portion is formed in a taper shape, and the sun gear meshes with the second tooth portion at the shaft lock position, and the planet gears do not mesh with the second tooth portion at the shaft unlock position. It is characterized by allowing rotation.

  A seventh aspect of the present invention is the seat reclining device according to the fifth or sixth aspect, wherein the planetary gears are engaged with the first internal gear portion and the second internal gear portion deeper than a predetermined meshing position. In the locked position of the shaft, the sun gear or shaft portion presses the planetary gears radially outward, and the planetary gears are connected to the first internal gear and the shaft. It is characterized by deeply meshing with the second internal tooth portion.

  As described above, according to the first aspect of the present invention, the rotational force acting between the seat cushion and the seat back is input to each planetary gear as a meshing input, but the first internal gear portion of the first gear body. And the first meshing point between the first tooth portions of each planetary gear and the second meshing point between the second internal tooth portion of the second gear body and the second tooth portion of each planetary gear are shifted in the radial direction. Therefore, a rotational moment based on the resultant force of both meshing inputs acts on each planetary gear. Here, when the planetary gear locking / unlocking means is in the locked position, the planetary gears do not rotate due to the rotation preventing force of the planetary gear locking / unlocking means acting. Therefore, the seat back maintains the inclination angle. When the planetary gear locking / unlocking means is in the unlocked position, each planetary gear is rotated by a rotational moment based on the resultant force of both meshing inputs. Therefore, the inclination angle of the seat back can be varied. As described above, the inclination angle of the seat back can be adjusted manually. Since the relative rotational angle of both the first internal gear portion of the first gear body and the second internal gear portion of the second gear body meshes with the planetary gear can be varied, the inclination angle of the seat back can be adjusted steplessly. Or can be adjusted at small intervals.

  Further, in the locked position, the seat back receives rotational force acting on the seat back by meshing the first internal gear portion of the first gear body and the second internal gear portion of the second gear body with each planetary gear. Strong in strength against external force from the back.

  According to the invention of claim 2, since the rotation of each planetary gear is prevented by the frictional resistance force between the gear shaft of each planetary gear and the tapered body, the inclination angle of the seat back can be adjusted steplessly.

  According to the invention of claim 3, in the locked position, the tapered body urges each planetary gear in a direction of deeply meshing with each of the first and second gear bodies, and thus each planetary gear and the first and second gear bodies. There is no backlash between the two. Therefore, the backlash of the seat back due to the backlash between each planetary gear and the first and second gear bodies can be prevented.

  According to the invention of claim 4, since each planetary gear meshes deeply with the first and second internal teeth at the locked position, it is possible to prevent backlash between each planetary gear and the first and second internal teeth. In the unlocked position, each planetary gear meshes shallowly with the first and second internal teeth, so that the teeth of the first teeth meshing with the first internal teeth and the second internal teeth are meshed with each other. The teeth of the two tooth portions can be made different in the circumferential direction, whereby the rotational moment based on the resultant force of both meshing inputs can be increased, so that each planetary gear easily rotates.

  According to the invention of claim 5, in order to prevent rotation of each planetary gear by engaging the sun gear or the shaft portion between the first tooth portion or the second tooth portion of each planetary gear, The inclination angle of the seat back can be adjusted at small intervals.

  According to the invention of claim 6, in the locked position, the sun gear is urged in the direction of deeply meshing with the second tooth portion of each planetary gear, so that there is a backlash between each planetary gear and the sun gear. Does not occur. Therefore, the backlash of the seat back due to the backlash between each planetary gear and the sun gear can be prevented.

  According to the invention of claim 7, the sun gear or the shaft portion urges each planetary gear in a direction in which the planetary gear is deeply engaged with the first and second gear bodies. There is no backlash between the two. Therefore, the backlash of the seat back due to the backlash between each planetary gear and the first and second gear bodies can be prevented.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  1 to 6 show a first embodiment of the present invention, FIG. 1 is an exploded perspective view of a seat reclining device 1A, FIG. 2 is a sectional view of the seat reclining device 1A, and FIG. 3 is an enlarged view of a portion A in FIG. 4 is a cross-sectional view taken along line BB in FIG. 2, FIG. 5 is a diagram for explaining the rotational moment and frictional resistance acting on the planetary gear 6 when the planetary gear 6 is in a predetermined meshing position, and FIG. It is a figure explaining the rotational moment and frictional resistance which act on the planetary gear 6 when the planetary gear 6 exists in a meshing position shallower than FIG.

  1 to 3, a seat reclining device 1A includes a first gear body 2 fixed on a seat cushion (not shown) side, and a second gear body 3 fixed on a seat back (not shown) side. , A pair of carrier plates 4, 5 disposed on both outer sides of the first and second gear bodies 2, 3, and four planetary gears 6 accommodated in an internal space surrounded by the pair of carrier plates 4, 5. Planetary gear locking / unlocking means 7A for allowing or preventing the rotation of each planetary gear 6 by the rotational force input from the first gear body 2 and the second gear body 3, and this planetary gear locking An operation button 8A which is an operation unit for operating the unlocking means 7A is provided.

  The first gear body 2 has a first internal tooth portion 2a having a rotation center between a seat cushion (not shown) and a seat back (not shown) as an axis O1. The second gear body 3 includes a second internal tooth portion 3a having a rotation center between a seat cushion (not shown) and a seat back (not shown) as an axis O1. The second internal tooth portion 3a is smaller in diameter than the first internal tooth portion 2a, and has a smaller number of teeth by an integral multiple of the number of planetary gears 6 (in this first embodiment, only 4 teeth). Is set.

  The pair of carrier plates 4 and 5 are connected to each other by four carrier shafts 10. As a result, the pair of carrier plates 4 and 5 are integrally rotated with respect to the first and second gear bodies 2 and 3. The pair of carrier plates 4 and 5 are respectively formed with elongated holes 11 extending in the radial direction about the axis O1 at four positions facing each other. A gear shaft 12 is inserted between the long holes 11 facing each other. Each planetary gear 6 is supported on each gear shaft 12 so as to be integrally rotatable. Each planetary gear 6 may be rotatably supported on each gear shaft 12. Accordingly, each planetary gear 6 can be slightly shifted together with the gear shaft 12 in the radial direction around the axis O1, as indicated by an arrow in FIG.

  Each planetary gear 6 is integrally formed on the outer periphery with a first tooth portion 6a meshing with the first internal tooth portion 2a and a second tooth portion 6b meshing with the second internal tooth portion 3a. The first tooth portion 6a and the second tooth portion 6b have the same number of teeth, and each tooth of the first tooth portion 6a is arranged at the same position in the circumferential direction as each tooth of the second tooth portion 6b. Moreover, the 2nd tooth | gear part 6b is formed in the small diameter with respect to the 1st tooth | gear part 6a. Each planetary gear 6 can rotate about the rotation center O2 by the gear shaft 12, and can revolve around the axis O1 by the carrier plates 4 and 5, so that the first inner tooth portion 2a and the second inner gear 2 It revolves around the axis O1 while changing the meshing position with the tooth 3a. When each planetary gear 6 revolves, the relative rotation angle between the first gear body 2 and the second gear body 3 changes due to the difference in the number of teeth of the first internal gear portion 2a and the second internal gear portion 3a. The inclination angle of the seat back (not shown) is variable.

  The planetary gear locking / unlocking means 7A includes a shaft 13 disposed around the axis O1 of the first gear body 2 and the second gear body 3 and supported so as to be movable in the axial direction, and a shaft portion of the shaft 13 The taper body 14 is provided integrally with the outer periphery, and is in contact with the large diameter portion 12a of each gear shaft 12 of each planetary gear 6. The shaft 13 is supported so as to be movable in the axial direction between a lock position and a lock release position. A spring force of a compression spring 15 is applied to the shaft 13 in the lock position direction a.

  The tapered body 14 includes a minimum diameter surface 14a having a minimum distance from the axis O1, an inclined surface 14b in which the distance from the axis O1 gradually increases, and a maximum diameter surface 14c having a maximum distance from the axis O1. It is composed of In the locked position of the shaft 13, as shown in FIG. 2 and FIG. 3, each gear shaft 12 is positioned on the inclined surface 14b and the inclined surface 14b abuts on the large-diameter portion 12a. The planetary gears 6 are pressed outward in the radial direction and are positioned at positions where the planetary gears 6 are deeply engaged with the first and second gear bodies 2 and 3. In the unlocked position of the shaft 13, the large-diameter portion 12 a of each gear shaft 12 is positioned away from the inclined surface 14 b, and each planetary gear 6 is positioned at a position where the planetary gear 6 is shallowly engaged with the first and second gear bodies 2 and 3. .

  The operation button 8 </ b> A is fixed to one end of the shaft 13 protruding from the carrier plate 5. By pressing the operation button 8A in the direction b against the spring force of the compression spring 15, the shaft 13 can be changed from the locked position to the unlocked position.

  In the above configuration, when the operation button 8A is not operated, the shaft 13 is positioned at the lock position by the spring force of the compression spring 15 as shown in FIGS. In this locked position, the large-diameter portion 12a of each gear shaft 12 abuts on the inclined surface 14b of the tapered body 14, so that each planetary gear 6 is in contact with the first and second internal gear portions 2a, 3a as shown in FIG. Bite deeply. In this deeply engaged lock state, the rotational force acting between the seat back (not shown) and the seat cushion (not shown) is the first internal gear portion of the first gear body 2 as shown in FIG. 2a and the first meshing point P1 between the first tooth portion 6a of the planetary gear 6 and the second meshing point P2 between the second internal tooth portion 3a of the second gear body 3 and the second tooth portion 6b of the planetary gear 6. Works. Then, the resultant force F3 of the both meshing inputs F1 and F2 acts on the planetary gear 6. Here, since the first meshing point P1 and the second meshing point P2 are displaced in the radial direction, the resultant force F3 acts in a direction displaced from the rotation center O2 of the planetary gear 6, and the resultant force F3 causes the planet. A rotational moment M1 that attempts to rotate the gear 6 acts.

  The resultant force F3 acts on the tapered body 14 via the gear shaft 12 of the planetary gear 6, and the direction thereof is substantially the radial direction of the tapered body 14, that is, the shaft 13. Therefore, the planetary gear 6 generates a frictional resistance N1 (vertical component force of F3 × friction coefficient) caused by the resultant force F3 between the large diameter portion 12a of the gear shaft 12 of the planetary gear 6 and the tapered body 14. . That is, in the locked position, the rotation of each planetary gear 6 can be prevented by increasing the frictional resistance N1 between each planetary gear 6 and the tapered body 14 from the rotational moment M1 acting on each planetary gear 6. Therefore, the seat back (not shown) maintains the inclination angle.

  When the operation button 8A is pressed, the shaft 13 moves in the direction of the arrow b and changes to the unlock position. In this unlocked position, the inclined portion 14b of the tapered body 14 is disengaged from the large diameter portion of each gear shaft 12, so that no frictional resistance N1 is generated, and each planetary gear 6 can be rotated by the rotational moment M1. Further, in this unlocked state, each planetary gear 6 is shallowly engaged with the first and second inner teeth 2a, 3a, so that a seat back (not shown) and a seat cushion (not shown) are provided. ) Between the first meshing point P1 between the first internal gear portion 2a of the first gear body 2 and the first gear portion 6a of the planetary gear 6, as shown in FIG. It acts on the second meshing point P2 between the second internal tooth portion 3a of the body 3 and the second tooth portion 6b of the planetary gear 6. The resultant force F3 of the meshing inputs F1 and F2 acts on the planetary gear 6. Here, in the unlocking position, each planetary gear 6 meshes shallowly with the first and second internal teeth 2a, 3a, so that the first internal teeth 2a and the first teeth 6a of the planetary gear 6 are in contact with each other. Since the first meshing point P1 has moved to the adjacent tooth, this resultant force F3 acts in a direction passing through a position away from the rotation center O2 of the planetary gear 6 compared to the case shown in FIG. The rotational moment M2 acting on the planetary gear 6 by F3 becomes a large value, and each planetary gear 6 becomes easy to rotate.

  Further, when the planetary gear 6 rotates, the gear shaft 12 of the planetary gear 6 and the tapered body 14 are not in contact with each other, so that no frictional resistance force is generated, and each planetary gear 6 is rotated by the rotational moment M2. That is, since each planetary gear 6 is easy to rotate at the unlocking position where the meshing is shallow, the rotational force (operation force) necessary to adjust the inclination of the seat back can be reduced. When each planetary gear 6 revolves while meshing with the first and second internal teeth 2a, 3a, the relative rotational angle between the first gear body 2 and the second gear body 3 changes, and the seat back (not shown) The angle of inclination is variable. From the above, the inclination angle of the seat back (not shown) can be adjusted by a manual method in which a rotational force is applied to the seat back (not shown).

  Since the first internal gear portion 2a of the first gear body 2 and the second internal gear portion 3a of the second gear body 3 are engaged with the planetary gear 6, the relative rotation angle of both can be varied. (Not shown) can be adjusted steplessly. Further, when the shaft 13 is in the locked position, the rotational force acting on the seat back (not shown) is applied to the first internal gear portion 2 a of the first gear body 2 and the second internal gear portion 3 a of the second gear body 3. Since each planetary gear 6 is received by meshing, it is strong in strength against an external force from a seat back (not shown).

  In the first embodiment, the planetary gear locking / unlocking means 7A is disposed on the axis O1 of the first gear body 2 and the second gear body 3, and the lock position and the unlock position are operated by operating the operation portion 8A. Between the shaft 13 and the tapered portion 14 provided on the outer periphery of the shaft portion of the shaft 13 and in contact with each gear shaft 12 of each planetary gear 6. When the body 14 is frictionally engaged with the large diameter portion 12a of the gear shaft 12, the rotation of each planetary gear 6 can be prevented. Therefore, since the rotation preventing force at the locked position can be obtained by the frictional resistance force between the gear shaft 12 and the tapered body 14 of each planetary gear 6, the planetary gear locking / unlocking means 7A can have a simple configuration. it can.

  When the shaft 13 is located at the lock position, the tapered body 14 urges each planetary gear 6 in a direction of deeply meshing with the first and second gear bodies 2, 3. There is no backlash between the first and second gear bodies 2 and 3. Therefore, the backlash of the seat back due to the backlash between each planetary gear 6 and the first and second gear bodies 2 and 3 can be prevented.

  In the first embodiment, the operation unit is configured by a push operation unit 8a fixed to the shaft 13, and when the push operation unit 8a is operated, the shaft 13 is configured to shift in the axial direction. The reclining operation can be performed by a push operation.

  In the first embodiment, the taper body 14 is frictionally engaged with the large-diameter portion 12a of the gear shaft 12 to prevent the rotation of each planetary gear 6. However, the shaft portion of the shaft 13 is connected to each planetary gear 6. The first tooth portion 6a or the second tooth portion 6b may be engaged between the tooth portions. In this case, the inclination angle of the seat back cannot be adjusted steplessly. However, since each planetary gear 6 acts as a speed reduction mechanism, the inclination angle can be adjusted with a small interval (pitch).

  7 to 9 show a second embodiment of the present invention, FIG. 7 is a sectional view of the seat reclining device 1B in a locked state, FIG. 8 is a sectional view of the seat reclining device 1B in an unlocked state, and FIG. It is CC sectional view taken on the line.

  As shown in FIGS. 7 to 9, the seat reclining device 1B according to the second embodiment is mainly composed of a planetary gear locking / unlocking means 7B and an operation unit as compared with the first embodiment. Is different.

  That is, the planetary gear locking / unlocking means 7B of the second embodiment is arranged around the axis O1 of the first gear body 2 and the second gear body 3, and is supported so as to be movable in the axial direction. And a sun gear 20 fixed to the shaft 13. The second internal gear portion 3a of the second gear body 3 and the second gear portion 6b of each planetary gear 6 meshing with the second internal gear portion 3a are formed in a tapered shape. (2) The meshing position between the inner tooth part 2a and the first tooth part 6a of each planetary gear 6 and the meshing position between the second inner tooth part 2a and the second tooth part 6b are shifted in the radial direction. . The tooth portion 20a of the sun gear 20 and the tooth portion 6b of each planetary gear 6 that meshes with the sun gear 20 are formed in a tapered shape. At the locked position of the shaft 13, the sun gear 20 meshes with each planetary gear 6, and each planetary gear 6 is urged outward by the taper shape of both teeth 20 a, 6 b, whereby each planetary gear 6 is It meshes deeply with the first and second gear bodies 2 and 3. At the unlocked position of the shaft 13, the sun gear 20 does not mesh with the planetary gears 6 and allows the planetary gears 6 to shift in the direction of the revolution center, thereby rotating the planetary gears 6.

  The operation unit is configured by an operation lever 8B that is swingably supported at the intermediate position with the support pin 21 as a fulcrum. One end side of the operation lever 8B is a push operation unit 8a by the user. The other end side of the operation lever 8B is engaged with the shaft 13. The shaft 13 is biased in the lock position direction a by the spring force of the disc spring 22. By pushing the push operation portion 8a, the shaft 13 is shifted to the unlocking position against the spring force of the disc spring 22.

  The carrier plates 4 and 5 are rotatably accommodated in the internal spaces of the first gear body 2 and the second gear body 3. The first gear body 2 and the second gear body 3 are assembled together by a holder ring 23 so as to be rotatable. Then, the side surfaces of the first gear body 2 and the second gear body 3 are fixed to the seat cushion side or the seat back side by welding or the like, respectively.

  Since other configurations are the same as those of the second embodiment, the same components in the drawings are denoted by the same reference numerals, and the description thereof is omitted.

  In the second embodiment, the rotational moment M1 acts on each planetary gear 6 in the locked position and unlocked position of the shaft 13 as in the first embodiment, and each planet by the rotational moment M1 is in the locked position. The rotation of the gear 6 is blocked by meshing with the sun gear 20, and no rotation blocking force acts at the unlocked position. As described above, the inclination angle of the seat back (not shown) can be adjusted manually as in the first embodiment.

  In the second embodiment, since the sun gear 20 meshes with the first tooth portion 6a or the second tooth portion 6b of each planetary gear 6, the inclination angle of the seat back cannot be adjusted steplessly. Since each planetary gear 6 acts as a speed reduction mechanism, the inclination angle can be adjusted with a small interval (pitch).

  In the second embodiment, the planetary gear locking / unlocking means 7B is disposed on the axis O1 of the first gear body 2 and the second gear body 3, and the lock position and the unlock position are operated by operating the operation portion 8B. And a sun gear 20 fixed to the shaft 13 and capable of meshing with each planetary gear 6, and the second internal tooth portion 3 a and the second tooth portion 6 b are tapered. The tooth portion of the sun gear meshing with the second tooth portion 6b is formed on the tapered surface, and the sun gear 20 meshes with each planetary gear 6 at the lock position of the shaft 13, and at the unlock position of the shaft 13. The sun gear 20 is configured to allow rotation of each planetary gear 6 without meshing with each planetary gear 6. With the above configuration, at the locked position of the shaft 13, each planetary gear 6 is deeper than the first and second gear bodies 2, 3 due to the tapered shape of the teeth 20 a, 6 b of both the sun gear 20 and each planetary gear 6. Since the gears are biased in the meshing direction, no backlash occurs between the planetary gears 6 and the first and second gear bodies 2 and 3. Therefore, the backlash of the seat back (not shown) due to the backlash between each planetary gear 6 and the first and second gear bodies 2 and 3 can be prevented.

  In the second embodiment, the operation unit is configured by an operation lever 8B that is swingably supported. One end of the operation lever 8B is configured as a push operation unit 8a, and when the push operation unit 8a is operated, Since the other end side of the lever 8B presses the shaft 13 in the axial direction to shift the shaft 13 in the axial direction, the reclining operation can be performed by a push operation.

  10 to 12 show a third embodiment of the present invention, FIG. 10 is a side view of the seat reclining device 1C, FIG. 11 is a sectional view of the seat reclining device 1C in a locked state, and FIG. 12 is a lock of the seat reclining device 1C. It is sectional drawing of a cancellation | release state.

  As shown in FIGS. 10 to 12, the seat reclining device 1 </ b> C according to the third embodiment is different from the second embodiment only in the configuration of the operation unit.

  That is, the operation unit of the third embodiment is configured by an operation lever 8C that is swingably supported around the support pin 21 at an intermediate position. One end side of the operation lever 8C is configured as a lever operation portion 8b by the user. The other end side of the operation lever 8 </ b> C is configured to interfere with the tapered surface 13 a at the end of the shaft 13. When the lever operating portion 8b is pulled against the spring force of the spring 24, the other end side of the operating lever 8C presses the tapered surface 13a of the shaft 13, and the shaft 13 is pressed in the axial direction. With this pressing force, the shaft 13 is shifted from the locked position to the unlocked position.

  Since the other configuration is the same as that of the second embodiment, the same components in the drawings are denoted by the same reference numerals and the description thereof is omitted.

  Also in the third embodiment, the seat back inclination angle can be adjusted manually by the same operation as in the first and second embodiments.

  In the third embodiment, the reclining operation can be performed by lever operation.

  In each embodiment, the number of planetary gears 6 is four.

  In each embodiment, the first gear body 2 is fixed to the seat cushion side, and the second gear body 3 is fixed to the seat back side. Conversely, the first gear body 2 is fixed to the seat back side. The second gear body 3 may be fixed and fixed to the seat cushion side.

1 is an exploded perspective view of a seat reclining device according to a first embodiment of the present invention. 1 is a cross-sectional view of a seat reclining device according to a first embodiment of the present invention. FIG. 3 shows the first embodiment of the present invention and is an enlarged view of a portion A in FIG. 2. FIG. 3 shows the first embodiment of the present invention and is a cross-sectional view taken along line BB in FIG. 2. It is a figure which shows 1st Embodiment of this invention and demonstrates the rotational moment and frictional resistance which act on a planetary gear when a planetary gear exists in a predetermined meshing position. FIG. 6 is a diagram illustrating a first embodiment of the present invention and explaining a rotational moment and a frictional resistance acting on the planetary gear when the planetary gear is in a meshing position shallower than the position of FIG. 5. It is sectional drawing of the locked state of the seat reclining apparatus which shows 2nd Embodiment of this invention. It is sectional drawing of the lock release state of the seat reclining apparatus which shows 2nd Embodiment of this invention. FIG. 8 shows a second embodiment of the present invention and is a cross-sectional view taken along the line CC of FIG. It is a side view of a seat reclining device, showing a third embodiment of the present invention. It is sectional drawing of the locked state of the seat reclining apparatus which shows 3rd Embodiment of this invention. It is sectional drawing of the lock release state of a seat reclining apparatus which shows 3rd Embodiment of this invention. It is sectional drawing of the seat reclining apparatus of a 1st prior art example. It is a front view of the seat reclining device of the 2nd conventional example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1A-1C Seat reclining apparatus 2 1st gear body 2a 1st internal tooth part 3 2nd gear body 3a 2nd internal tooth part 6 Planetary gear 6a 1st tooth part 6b 2nd tooth part 7A, 7B Planetary gear lock | unlock 8A Operation button (operation unit)
8B, 8C Operation lever (operation part)
8a Push operation part 8b Lever operation part 12 Gear shaft 13 Shaft 14 Tapered body 20 Sun gear O1 Shaft O2 Center of rotation

Claims (7)

A first gear body having a first internal tooth portion fixed to one side of a seat cushion and a seat back and having a rotation center between the seat cushion and the seat back as an axis;
It is fixed to the other side of the seat cushion and the seat back, has a rotation center between the seat cushion and the seat back as an axis, and has a second internal tooth portion having a smaller number of teeth than the first internal tooth portion. A second gear body;
The first internal teeth and the second internal teeth are engaged with the first internal teeth and the first internal teeth, the first teeth and the second teeth have the same center and can be rotated together, and can revolve around the axis. A plurality of planetary gears supported by
The plurality of planetary gears revolve around an axis while changing the meshing position with the first internal gear portion and the second internal gear portion, and the number of teeth of the first internal gear portion and the second internal gear portion A seat reclining device in which an inclination angle of the seat back is varied by changing a relative rotation angle between the first gear body and the second gear body due to the difference in
In each of the planetary gears, the first tooth portion and the second tooth portion have the same number of teeth, the teeth of the first tooth portion and the teeth of the second tooth portion are arranged at the same position in the circumferential direction, and the first gear The meshing position of the internal tooth part and the first tooth part and the meshing position of the second tooth part and the second tooth part are configured to be shifted in the radial direction,
A planetary gear locking / unlocking means that is shifted between a lock position that prevents rotation of the planetary gear and a lock release position that allows rotation of the planetary gear is disposed on the shaft core. A seat reclining device. The seat reclining device according to claim 1,
The planetary gear lock / unlock means is disposed on the shaft cores of the first gear body and the second gear body, and is moved in the axial direction between a lock position and a lock release position by operation of an operation portion. And a taper body provided on the outer periphery of the shaft and abutting against each gear shaft of each planetary gear, and the taper body frictionally engages with the gear shaft at a lock position of the shaft. A seat reclining device. The seat reclining device according to claim 2,
The planetary gears are provided so as to be movable in a radial direction to positions where the planetary gears mesh with the first internal gear and the second internal gear deeper than a predetermined meshing position.
In the locked position of the shaft, the tapered body presses the gear shaft radially outward,
Each of the planetary gears is deeply engaged with the first internal gear and the second internal gear, and the seat reclining device is characterized in that The seat reclining device according to claim 2 or claim 3,
Each planetary gear is provided to be movable in a radial direction between a position engaging with the first internal gear and the second internal gear deeper than a predetermined meshing position and a position meshing shallowly.
In the locked position of the shaft, the tapered body presses the gear shaft radially outward, and the planetary gears move to positions where they are deeply engaged with the first internal gear and the second internal gear,
In the unlocked position of the shaft, the planetary gears move to a position where the planetary gear meshes with the first internal gear portion and the second internal gear portion shallower than a predetermined meshing position, and
The seat of the first tooth portion meshing with the first internal tooth portion and the tooth of the second tooth portion meshing with the second internal tooth portion are teeth adjacent in the circumferential direction. Reclining device. The seat reclining device according to claim 1,
The planetary gear locking / unlocking means is disposed on the shaft cores of the first gear body and the second gear body, and is moved in the axial direction between a lock position and a lock release position by operation of an operation portion. Shaft,
A sun gear or shaft portion provided on an outer periphery of the shaft and meshing with each planetary gear, and at the lock position of the shaft, the sun gear or shaft portion is a first tooth portion of each planetary gear, or A seat reclining device that engages between the tooth portions of the second tooth portion. The seat reclining device according to claim 5,
The second internal tooth portion and the second tooth portion are formed in a tapered shape, and the tooth portion portion of the sun gear meshing with the second tooth portion is formed in a tapered shape,
In the locked position of the shaft, the sun gear meshes with the second tooth portion,
The seat reclining device, wherein the planetary gear is allowed to rotate without meshing with the second tooth portion at the unlocked position of the shaft. The seat reclining device according to claim 5 or 6,
The planetary gears are provided so as to be movable in a radial direction to positions where the planetary gears mesh with the first internal gear and the second internal gear deeper than a predetermined meshing position.
In the locked position of the shaft, the sun gear or the shaft portion presses each planetary gear radially outward,
Each of the planetary gears is deeply engaged with the first internal gear and the second internal gear, and the seat reclining device is characterized in that

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