JP2013086603A - Reduction gear mechanism - Google Patents

Reduction gear mechanism Download PDF

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JP2013086603A
JP2013086603A JP2011227574A JP2011227574A JP2013086603A JP 2013086603 A JP2013086603 A JP 2013086603A JP 2011227574 A JP2011227574 A JP 2011227574A JP 2011227574 A JP2011227574 A JP 2011227574A JP 2013086603 A JP2013086603 A JP 2013086603A
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cam
cam member
gear
internal gear
circular hole
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JP5781890B2 (en
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Toshiharu Ito
敏治 伊藤
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Shiroki Corp
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Shiroki Corp
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  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
  • Gear Transmission (AREA)
  • Pivots And Pivotal Connections (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a reduction gear mechanism having superior operation feeling, in which a time lug of actual lock release from lock release operation is reduced.SOLUTION: The reduction gear mechanism includes: a vertical wall section (circle hole) 61e with its rotary shaft as a center, which is provided in an internal gear 61; a vertical wall section (cylinder) 63c with its rotary shaft as a center, which is provided in an external gear 63, and which is inserted into the vertical wall section 61e; first and second cam members 71 and 73 for forming a cam hole together, which are provided in a space between the inner surface of the vertical seciton 61e and the outer face of the vertical seciton 63c, and stacked in a radial direction; a spring 77 which is locked to the cam hole, and which biases the second cam member 73 to the inner surface of the vertical wall section 61e, and the first cam member 71 to the outer face of the vertical wall section 63c, in a pressing direciton; and a lock release member 79 which changes a cam hole shape by moving the second cam member 73, and which reduces pressing force to the outer face of the vertical wall section 63c and the inner surface of the vertical wall section 61e, of the first cam member 71 and the second cam member 73.

Description

本発明は、固定部材側、回転部材側のうちのいずれか一方の側に設けられた内歯歯車と、前記固定部材側、前記回転部材側のうちの他方の側に設けられ、歯数が前記内歯歯車よりも少なく、前記内歯歯車に噛合する外歯歯車と、前記内歯歯車、前記外歯歯車のうちのいずれか一方を他方の歯車の回転軸を中心に偏心運動させながら前記内歯歯車、前記外歯歯車の噛合位置を変化させることにより、前記回転部材の前記固定部材に対する傾動角を変える減速歯車機構に関する。   The present invention provides an internal gear provided on one side of the fixed member side and the rotating member side, and is provided on the other side of the fixed member side and the rotating member side. Less than the internal gear, the external gear meshing with the internal gear, the internal gear, the external gear while eccentrically moving one of the external gear around the rotation axis of the other gear The present invention relates to a reduction gear mechanism that changes the tilt angle of the rotating member with respect to the fixed member by changing the meshing position of the internal gear and the external gear.

減速歯車機構の一例として、シートクッション（固定部材）に対してシートバック（回転部材）の傾動角度を変えるタウメル式のリクライニング装置がある。   As an example of a reduction gear mechanism, there is a taumel type reclining device that changes a tilt angle of a seat back (rotating member) with respect to a seat cushion (fixing member).

このリクライニング装置は、シートクッション側、シートバック側のうちのいずれか一方の側に内歯歯車を設け、シートクッション側、シートバック側のうちの他方の側に、歯数が内歯歯車よりも少なく、内歯歯車に噛合する外歯歯車を設け、内歯歯車、外歯歯車のうちのいずれか一方を他方の歯車の回転軸を中心に偏心運動させながら内歯歯車、外歯歯車の噛合位置を変化させることにより、シートバックのシートクッションに対する傾動角を変えるものである。   This reclining device is provided with an internal gear on one of the seat cushion side and the seat back side, and the number of teeth on the other side of the seat cushion side and the seat back side is larger than that of the internal gear. There are few external gears that mesh with the internal gears, and the internal gears and the external gears mesh while either one of the internal gears or the external gears moves eccentrically around the rotation axis of the other gear. By changing the position, the tilt angle of the seat back relative to the seat cushion is changed.

そして、図７に示すように、円形穴１の内面と円筒３の外面との間の偏心環状空間には一対の楔状部材５、７が配置されている。この一対の楔状部材５、７は、偏心環状空間に楔を打ち込む方向（矢印Ａ方向、矢印Ｂ方向）にスプリング９により付勢されている。   As shown in FIG. 7, a pair of wedge-shaped members 5 and 7 are disposed in the eccentric annular space between the inner surface of the circular hole 1 and the outer surface of the cylinder 3. The pair of wedge members 5 and 7 are urged by a spring 9 in a direction (arrow A direction and arrow B direction) in which the wedge is driven into the eccentric annular space.

楔状部材５、７は、それぞれ円形穴１の内面と円筒３の外面とを押圧することにより、内歯歯車と外歯歯車とが両者の回転軸間の偏心量を増やす方向に付勢され、内歯歯車と外歯歯車の噛合部位では、内歯と外歯とが圧接し、外歯歯車と内歯歯車の相対運動が禁止され、シートバックの傾動が禁止される（ロック状態）。   The wedge-shaped members 5 and 7 are urged in the direction in which the internal gear and the external gear increase the amount of eccentricity between the rotation shafts by pressing the inner surface of the circular hole 1 and the outer surface of the cylinder 3 respectively. At the meshing portion of the internal gear and the external gear, the internal teeth and the external teeth are pressed against each other, the relative movement of the external gear and the internal gear is prohibited, and the tilt of the seat back is prohibited (locked state).

ロック解除カム１１は、その当接面１１ａがスプリング９の付勢力に抗して楔状部材５、７の楔先端側の端面５ａまたは端面７ａを押して、楔状部材５または楔状部材７を偏心環状空間から引き抜く方向（矢印Ａまたは矢印Ｂ方向と逆方向）に押すようになっている。楔状部材５または楔状部材７がロック解除カム１１によって押されて移動すると、楔状部材５または楔状部材７の円形穴１の内面、円筒３の外面への押接力が減り、噛合部位での内歯と外歯との圧接状態が低減され、シートバックの傾動が可能となる（ロック解除状態）。   The abutment surface 11a of the lock releasing cam 11 pushes the end surface 5a or the end surface 7a of the wedge-shaped members 5 and 7 against the urging force of the spring 9 to push the wedge-shaped member 5 or the wedge-shaped member 7 into the eccentric annular space. It pushes in the direction (the direction opposite to the direction of arrow A or arrow B) to be pulled out from. When the wedge-shaped member 5 or the wedge-shaped member 7 is pushed and moved by the lock release cam 11, the pressing force against the inner surface of the circular hole 1 of the wedge-shaped member 5 or the wedge-shaped member 7 and the outer surface of the cylinder 3 is reduced, and the internal teeth at the meshing portion are reduced. And the pressure contact state between the external teeth are reduced, and the seat back can be tilted (unlocked state).

楔状部材５または楔状部材７の移動始めは、他方の楔状部材７または楔状部材５は円形穴１の内面、円筒３の外面との摩擦により、静止している。よって、一方の楔状部材が偏心環状空間から引き抜かれる方向に移動していくと、スプリング９の弾性反発力により他方の楔状部材が急に偏心環状空間に楔を打ち込む方向に移動する（以下、このスプリング９の弾性反発力により他方の楔状部材が押されて移動することを「スキップ」という。）この動作を繰り返しながら、内歯歯車と外歯歯車との偏心状態を保持し、シートバックは傾動する（例えば、特許文献１参照）。   At the beginning of the movement of the wedge-shaped member 5 or the wedge-shaped member 7, the other wedge-shaped member 7 or the wedge-shaped member 5 is stationary due to friction between the inner surface of the circular hole 1 and the outer surface of the cylinder 3. Therefore, when one wedge-shaped member moves in the direction in which it is pulled out from the eccentric annular space, the other wedge-shaped member suddenly moves in the direction in which the wedge is driven into the eccentric annular space by the elastic repulsive force of the spring 9 (hereinafter referred to as this). The movement of the other wedge-shaped member pushed by the elastic repulsive force of the spring 9 is called “skip”.) While repeating this operation, the eccentric state of the internal gear and the external gear is maintained, and the seat back tilts. (For example, refer to Patent Document 1).

特願2009-165647号Japanese Patent Application No. 2009-165647

図７に示す構成のリクライニング装置のロック状態は、楔状部材５、楔状部材７が円形穴１の内面に沿って移動することにより、楔状部材５、楔状部材７が円形穴１の内面と円筒３の外面とを押圧し、内歯歯車と外歯歯車との回転軸間の偏心量を変化させることにより得られる。このため、楔状部材５、楔状部材７の部品精度により、内歯歯車と外歯歯車との回転軸間の偏心量のばらつきが大きいという問題点がある。従って、楔状部材５、７の楔先端側の端面５ａ、７ａの位置がばらつき、楔状部材５、７の楔先端側の端面５ａ、７ａと、ロック解除カム１１との間には大きな隙間が必要である。このため、ロック解除カム１１を操作して、楔状部材５または楔状部材７を押しシートバックの傾動が可能となるまで、即ちロック解除されるまでに大きなタイムラグが発生する問題点がある。特に、シートを前傾にさせた直後に後傾させる場合は、あるいはシートを後傾させた直後に前傾させる場合は、ロック解除カムと楔状部材との隙間が更に大きくなっているので、タイムラグも更に大きくなる。   The locked state of the reclining device shown in FIG. 7 is that the wedge-shaped member 5 and the wedge-shaped member 7 move along the inner surface of the circular hole 1, so that the wedge-shaped member 5 and the wedge-shaped member 7 are aligned with the inner surface of the circular hole 1 and the cylinder 3. And the amount of eccentricity between the rotation shafts of the internal gear and the external gear is changed. For this reason, there exists a problem that the dispersion | variation in the eccentric amount between the rotating shafts of an internal gear and an external gear is large by the component precision of the wedge-shaped member 5 and the wedge-shaped member 7. Therefore, the positions of the end surfaces 5a and 7a on the wedge tip side of the wedge members 5 and 7 vary, and a large gap is required between the end surfaces 5a and 7a on the wedge tip side of the wedge members 5 and 7 and the unlocking cam 11. It is. For this reason, there is a problem that a large time lag occurs until the seatback can be tilted by operating the lock release cam 11 and pushing the wedge-shaped member 5 or the wedge-shaped member 7, that is, before the lock is released. In particular, when the seat is tilted backward immediately after being tilted forward, or when the seat is tilted forward immediately after being tilted backward, the gap between the unlocking cam and the wedge-shaped member is further increased. Is even larger.

次に、図７に示す構成のリクライニング装置では、一方の楔状部材が偏心環状空間から引き抜かれる方向に移動していくと、スプリング９の弾性反発力により他方の楔状部材が急に偏心環状空間に楔を打ち込む方向にスキップするので、操作フィーリングが悪い問題点がある。   Next, in the reclining device having the configuration shown in FIG. 7, when one wedge-shaped member moves in a direction in which it is pulled out from the eccentric annular space, the other wedge-shaped member suddenly enters the eccentric annular space due to the elastic repulsive force of the spring 9. Since the skip is performed in the direction of driving the wedge, there is a problem that the operation feeling is bad.

本発明は、上記問題点に鑑みてなされたもので、その課題は、ロック解除の操作と、実際にロック解除されるタイムラグが小さく、操作フィーリングがよい減速歯車機構を提供することにある。   The present invention has been made in view of the above problems, and an object thereof is to provide a reduction gear mechanism that has a small operation time and a small time lag that is actually unlocked and has a good operation feeling.

請求項１に係る発明は、固定部材側、回転部材側のうちのいずれか一方の側に設けられた内歯歯車と、前記固定部材側、前記回転部材側のうちの他方の側に設けられ、歯数が前記内歯歯車よりも少なく、前記内歯歯車に噛合する外歯歯車と、前記内歯歯車、前記外歯歯車のうちのいずれか一方を他方の歯車の回転軸を中心に偏心運動させながら前記内歯歯車、前記外歯歯車の噛合位置を変化させることにより、前記回転部材の前記固定部材に対する傾動角を変える減速歯車機構であって、前記外歯歯車、前記内歯歯車のうちの一方の歯車に設けられ、その回転軸を中心とした円形穴と、前記外歯歯車、前記内歯歯車のうちの他方の歯車に設けられ、その回転軸を中心とし、前記円形穴に挿入される円筒と、前記円形穴の内面と円筒の外面との間の空間に設けられ、径方向に積層され、協同してカム穴を形成する少なくとも２つのカム部材と、前記カム穴に係合し、少なくとも１つの前記カム部材を前記円形穴の内面に、少なくとも１つの前記カム部材を前記円筒の外面に押接する方向に付勢する付勢部材と、前記カム部材のうちの１つのカム部材を移動させて前記カム穴形状を変化させ、前記カム部材の前記円形穴の内面，前記円筒の外面への押接力を減らすロック解除部材と、を有することを特徴とする減速歯車機構である。   The invention according to claim 1 is provided on an internal gear provided on one of the fixed member side and the rotating member side, and on the other side of the fixed member side and the rotating member side. The number of teeth is smaller than that of the internal gear, and one of the external gear meshing with the internal gear and the internal gear or the external gear is eccentric about the rotation axis of the other gear. A reduction gear mechanism that changes a tilt angle of the rotating member with respect to the fixed member by changing a meshing position of the internal gear and the external gear while moving, wherein the external gear and the internal gear Provided in one of the gears and provided in a circular hole centered on the rotation shaft, and the other gear of the external gear and the internal gear, and centered on the rotation shaft and formed in the circular hole. A cylinder to be inserted, and an inner surface of the circular hole and an outer surface of the cylinder. At least two cam members that are stacked in the radial direction and cooperate to form a cam hole, and engage with the cam hole, and at least one of the cam members is disposed on the inner surface of the circular hole. A biasing member that biases one of the cam members in a direction of pressing against the outer surface of the cylinder; and one cam member of the cam members is moved to change the shape of the cam hole; A speed reduction gear mechanism comprising: an inner surface of a circular hole; and a lock release member that reduces a pressing force against the outer surface of the cylinder.

請求項２に係る発明は、前記カム部材は、前記円形穴の内面側に設けられた第１カム部材と、該第１カム部材より前記円筒の外面側に設けられた第２カム部材とからなり、前記第１カム部材の前記第２カム部材との対向面に、二つの傾斜面からなり、半径方向にへこんだ第１凹部が形成され、第２カム部材の前記第１カム部材との対向面に、二つの傾斜面からなり、半径方向にへこみ、前記第１凹部と協同して前記カム穴を形成する第２凹部が形成されたことを特徴とする請求項１記載の減速歯車機構である。   According to a second aspect of the present invention, the cam member includes: a first cam member provided on the inner surface side of the circular hole; and a second cam member provided on the outer surface side of the cylinder from the first cam member. The first cam member is formed with two inclined surfaces on the surface of the first cam member facing the second cam member, and a first recess recessed in the radial direction is formed, and the second cam member is connected to the first cam member. 2. The reduction gear mechanism according to claim 1, wherein the opposing surface is formed with two inclined surfaces and is recessed in the radial direction to form a second recess that cooperates with the first recess to form the cam hole. It is.

請求項３に係る発明は、前記付勢手段は、前記第１カム部材の第１凹部の二つの傾斜面を押して、前記第１カム部材を前記円形穴の内面に押接させ、前記第２カム部材の第２凹部の二つの傾斜面を押して、前記第２カム部材を前記円筒の外面に押接させること特徴とする請求項２記載の減速歯車機構である。   According to a third aspect of the present invention, the urging means pushes the two inclined surfaces of the first recess of the first cam member to press the first cam member against the inner surface of the circular hole, and the second 3. The reduction gear mechanism according to claim 2, wherein the two inclined surfaces of the second concave portion of the cam member are pressed so that the second cam member is pressed against the outer surface of the cylinder.

請求項４に係る発明は、前記ロック解除部材は、前記空間に配置され、前記第１カム部材の周方向の端部を押すカム押圧部を有することを特徴とする請求項２記載の減速歯車機構である。   The invention according to claim 4 is characterized in that the unlocking member has a cam pressing portion that is disposed in the space and presses an end portion in the circumferential direction of the first cam member. Mechanism.

請求項１−請求項４に係る発明によれば、前記円形穴の内面と円筒の外面との間の空間に設けられ、径方向に積層され、協同してカム穴を形成する少なくとも２つのカム部材と、前記カム穴に係合し、少なくとも１つの前記カム部材を前記円形穴の内面に、少なくとも１つの前記カム部材を前記円筒の外面に押接する方向に付勢する付勢部材と、前記カム部材のうちの１つのカム部材を移動させて前記カム穴形状を変化させ、前記カム部材の前記円形穴の内面，前記円筒の外面への押接力を減らすロック解除部材と、を有することにより、カム部材は半径方向に移動する。よって、カム部材の移動量は少なく、カム部材の位置のばらつきが小さくなる。そして、カム部材とロック解除部材との隙間を小さくでき、ロック解除の操作と、実際にロック解除されるタイムラグが小さくなる。   According to the first to fourth aspects of the invention, at least two cams that are provided in a space between the inner surface of the circular hole and the outer surface of the cylinder, are stacked in a radial direction, and cooperatively form a cam hole. A biasing member that engages with the cam hole and biases at least one of the cam members against the inner surface of the circular hole and at least one of the cam members against the outer surface of the cylinder; A lock release member that moves one of the cam members to change the shape of the cam hole and reduces the pressing force of the cam member against the inner surface of the circular hole and the outer surface of the cylinder; The cam member moves in the radial direction. Therefore, the amount of movement of the cam member is small, and variations in the position of the cam member are reduced. And the clearance gap between a cam member and a lock release member can be made small, and the unlocking operation and the time lag actually unlocked become small.

また、カム部材のうち少なくとも１つのカム部材は前記円形穴の内面に押接し、少なくとも１つの前記カム部材は前記円筒の外面に押接し、前記内歯歯車と前記外歯歯車との偏心状態を保持している。よって、回転部材の傾動時に、背景技術の欄で説明した楔状部材（カム部材）のスキップがなく、操作フィーリングがよい。   Further, at least one of the cam members is pressed against the inner surface of the circular hole, and at least one of the cam members is pressed against the outer surface of the cylinder, and the eccentric state between the internal gear and the external gear is determined. keeping. Therefore, when the rotating member is tilted, the wedge-like member (cam member) described in the background art section is not skipped, and the operation feeling is good.

実施形態のリクライニング装置の分解斜視図である。It is a disassembled perspective view of the reclining apparatus of embodiment. 図１に示すリクライニング装置が組み付けられたシートの要部側面図である。It is a principal part side view of the sheet | seat with which the reclining apparatus shown in FIG. 1 was assembled | attached. 図２の切断線III-IIIでの切断面を示す端面図である。It is an end elevation which shows the cut surface in the cutting line III-III of FIG. 図１に示すリクライニング装置のロック状態を説明する図である。It is a figure explaining the locked state of the reclining apparatus shown in FIG. 図１に示すリクライニング装置のロック解除状態を説明する図である。It is a figure explaining the lock release state of the reclining apparatus shown in FIG. 従来のリクライニング装置の問題点を説明する図である。It is a figure explaining the problem of the conventional reclining apparatus.

次に図面を用いて本発明の実施の形態を説明する。   Next, embodiments of the present invention will be described with reference to the drawings.

最初に、図２を用いて、実施形態のリクライニング装置が設けられたシートの説明を行う。図２は実施形態のリクライニング装置が組み付けられたシートの要部側面図である。   First, the seat provided with the reclining device of the embodiment will be described with reference to FIG. FIG. 2 is a side view of a main part of the seat in which the reclining device according to the embodiment is assembled.

図に示すように、リクライニング装置５１は、シートクッション側の部材であるロアアーム（回転部材）５３と、シートバック側の部材であるシートバックフレーム（固定部材）５５との間に設けられる。   As shown in the figure, the reclining device 51 is provided between a lower arm (rotating member) 53 that is a member on the seat cushion side and a seat back frame (fixing member) 55 that is a member on the seat back side.

次に、図１、図３、図４を用いてリクライニング装置５１の説明を行う。図１は実施形態のリクライニング装置の分解斜視図、図３は図２の切断線III-IIIでの切断面を示す端面図、図４は図１に示すリクライニング装置のロック状態を説明する図である。   Next, the reclining device 51 will be described with reference to FIGS. 1, 3, and 4. FIG. 1 is an exploded perspective view of the reclining device of the embodiment, FIG. 3 is an end view showing a cut surface taken along a cutting line III-III in FIG. 2, and FIG. 4 is a diagram for explaining a locked state of the reclining device shown in FIG. is there.

図１において、内歯歯車６１は、円形の底部６１ａと底部６１ａの周部に沿って形成された円筒状の立壁部６１ｂとからなり、一方の面が開放面となった略有底円筒状となっている。立壁部６１ｂの内周面には、周方向全域にわたって内歯６１ｃが形成されている。また、内歯歯車６１の底部６１ａの中央には、貫通した穴６１ｄが形成されている。穴６１ｄの内周面に沿って、前記開放面方向に突出する円筒状の立壁部６１ｅが形成されている。この円筒状の立壁部６１ｅの内部には円形穴が形成されている。内歯歯車６１の底部６１ａの外面には、３つの円弧状の凸部６１ｆが形成されている。また、図３、図４に示すように、ロアアーム５３には、３つの円弧状の穴５３ａが形成されている。そして、これらの穴５３ａに内歯歯車６１の凸部６１ｆが嵌合し、嵌合部分が溶接やかしめ等の手法により固着され、内歯歯車６１はロアアーム５３に取り付けられている。   In FIG. 1, an internal gear 61 is composed of a circular bottom 61a and a cylindrical standing wall 61b formed along the periphery of the bottom 61a, and has a substantially bottomed cylindrical shape with one surface being an open surface. It has become. Internal teeth 61c are formed on the inner peripheral surface of the standing wall portion 61b over the entire circumferential direction. A through hole 61d is formed at the center of the bottom 61a of the internal gear 61. A cylindrical standing wall portion 61e protruding in the open surface direction is formed along the inner peripheral surface of the hole 61d. A circular hole is formed in the cylindrical standing wall portion 61e. Three arc-shaped convex portions 61 f are formed on the outer surface of the bottom portion 61 a of the internal gear 61. As shown in FIGS. 3 and 4, the lower arm 53 is formed with three arc-shaped holes 53a. And the convex part 61f of the internal gear 61 fits into these holes 53a, the fitting part adheres by methods, such as welding and caulking, and the internal gear 61 is attached to the lower arm 53.

再び、図１に戻って、有底円筒状の内歯歯車６１の内部には、外歯歯車６３が配置される。外歯歯車６３の外面には、周方向全域にわたって外歯６３ａが形成されている。そして、外歯歯車６３の外歯６３ａは内歯歯車６１の内歯６１ｃに噛合可能となっている。更に、外歯歯車６３の外歯６３ａの歯数は、内歯歯車６１の内歯６１ｃの歯数より小さく設定されている。また、外歯歯車６３の中央部には、貫通した穴６３ｂが形成されている。外歯歯車６３の内歯歯車６１と対向する面側には、穴６３ｂの開口の縁部に沿って、内歯歯車６１方向に突出する円筒状の立壁部６３ｃが形成されている。この円筒状の立壁部６３ｃの外径は、内歯歯車６１の円筒状の立壁部６１ｅの内径より小さく設定され、外歯歯車６３の円筒状の立壁部６３ｃは、円形穴である内歯歯車６１の円筒状の立壁部６１ｅ内に挿入される円筒として機能する。   Returning again to FIG. 1, the external gear 63 is disposed inside the bottomed cylindrical internal gear 61. External teeth 63 a are formed on the outer surface of the external gear 63 over the entire circumferential direction. The external teeth 63 a of the external gear 63 can mesh with the internal teeth 61 c of the internal gear 61. Further, the number of external teeth 63 a of the external gear 63 is set smaller than the number of internal teeth 61 c of the internal gear 61. Further, a through hole 63 b is formed in the central portion of the external gear 63. On the surface side of the external gear 63 facing the internal gear 61, a cylindrical standing wall 63c that protrudes in the direction of the internal gear 61 is formed along the edge of the opening of the hole 63b. The outer diameter of the cylindrical standing wall 63c is set smaller than the inner diameter of the cylindrical standing wall 61e of the internal gear 61, and the cylindrical standing wall 63c of the external gear 63 is an internal gear that is a circular hole. It functions as a cylinder inserted into the 61 cylindrical standing wall 61e.

そして、図４に示すように、内歯歯車６１の内歯６１ｃに外歯歯車６３の外歯６３ａが噛合している状態では、内歯歯車６１の回転軸（円筒状の立壁部６１ｅ（円形穴）の中心）Ｏ１と、外歯歯車６３の回転軸（立壁部６３ｃの中心）Ｏ２とは異なり、偏心している。よって、内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）の内面と、外歯歯車６３の円筒状の立壁部６３ｃ（円筒）の外面との間には、偏心環状空間Ｋが形成されている。   As shown in FIG. 4, when the external teeth 63a of the external gear 63 are engaged with the internal teeth 61c of the internal gear 61, the rotation shaft (cylindrical upright wall portion 61e (circular Unlike the center) O1 of the hole) and the rotation axis (center of the standing wall 63c) O2 of the external gear 63, they are eccentric. Therefore, an eccentric annular space K is formed between the inner surface of the cylindrical standing wall 61e (circular hole) of the internal gear 61 and the outer surface of the cylindrical standing wall 63c (cylindrical) of the external gear 63. ing.

図１、図４に示すように、この偏心環状空間Ｋには、径方向に積層された少なくとも２つのカム部材が設けられる。本実施形態のカム部材は、内歯歯車６１の立壁部（円形穴）６１ｅの内面側に設けられた円弧状の第１カム部材７１と、第１カム部材７１より外歯歯車６３の立壁部（円筒）６３ｃの外面側に設けられた円弧状の第２カム部７３とからなっている。   As shown in FIGS. 1 and 4, the eccentric annular space K is provided with at least two cam members stacked in the radial direction. The cam member of the present embodiment includes an arc-shaped first cam member 71 provided on the inner surface side of the standing wall portion (circular hole) 61e of the internal gear 61, and the standing wall portion of the external gear 63 from the first cam member 71. (Cylinder) It consists of the arc-shaped 2nd cam part 73 provided in the outer surface side of 63c.

第１カム部材７１の第２カム部材７３との対向面には、二つの傾斜面、即ち、傾斜面７１ｄと、傾斜面７１ｄと逆斜面の関係にある傾斜面７１ｅとからなり、半径方向にへこんだ第１凹部７１ａが形成されている。   The opposing surface of the first cam member 71 to the second cam member 73 is composed of two inclined surfaces, that is, an inclined surface 71d and an inclined surface 71e having a reverse inclined surface relationship with the inclined surface 71d. A recessed first recess 71a is formed.

第２カム部材７３の第１部材７１との対向面にも、二つの傾斜面、即ち、傾斜面７３ｄと、傾斜面７３ｄと逆斜面の関係にある傾斜面７３ｅからなり、半径方向にへこんだ第２凹部７３ａが形成されている。尚、傾斜面７３ｄ，傾斜面７３ｅの傾斜角は、傾斜面７１ｄ，傾斜面７１ｅの傾斜角より大きく設定されている。   The surface of the second cam member 73 facing the first member 71 is also composed of two inclined surfaces, that is, an inclined surface 73d, and an inclined surface 73e that is in an inversely inclined relationship with the inclined surface 73d, and is recessed in the radial direction. A second recess 73a is formed. The inclination angles of the inclined surface 73d and the inclined surface 73e are set larger than the inclination angles of the inclined surface 71d and the inclined surface 71e.

そして、第１凹部７１ａと第２凹部７３ａとによって、カム穴７５が形成されている。   A cam hole 75 is formed by the first recess 71a and the second recess 73a.

このカム穴７５には、縮径方向に弾性変形したスプリング（付勢部材）７７の端部７７ｂ、端部７７ｃが係合している。   The cam hole 75 is engaged with end portions 77b and 77c of a spring (biasing member) 77 that is elastically deformed in the direction of diameter reduction.

よって、拡径方向に弾性復帰しようとするスプリング７７の端部７７ｂ、端部７７ｃが、第１カム部材７１の第１凹部７１ａの二つの傾斜面を７１ｄ、７１ｅを押し、第１カム部材７１は内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）内面に押接している。また、拡径方向に弾性復帰しようとするスプリング７７の端部７７ｂ、端部７７ｃが、第２カム部材７３の第２凹部７３ａの二つの傾斜面を７３ｄ、７３ｅを押し、第２カム部材７３は外歯歯車６３の立壁部６３ｃの外面に押接している。   Therefore, the end 77b and the end 77c of the spring 77 that is about to return elastically in the diameter expanding direction push the two inclined surfaces of the first recess 71a of the first cam member 71 against the first cam member 71. Is in pressure contact with the inner surface of the cylindrical standing wall 61e (circular hole) of the internal gear 61. In addition, the end 77b and the end 77c of the spring 77 which is about to return elastically in the diameter expansion direction push the two inclined surfaces 73d and 73e of the second recess 73a of the second cam member 73, and the second cam member 73. Is in press contact with the outer surface of the standing wall 63c of the external gear 63.

そして、図４に示すように、第１カム部材７１と第２カム部材７３の円弧角は、第１カム部材７１の方が第２カム部材７３より若干大きく設定されている。   As shown in FIG. 4, the arc angles of the first cam member 71 and the second cam member 73 are set slightly larger in the first cam member 71 than in the second cam member 73.

再び、図１、図４に戻って、ロック解除部材７９は、本体部７９ｄと、本体部７９ｄと連接され、外歯歯車６３の立壁部６３ｃの内部に嵌合する円筒部７９ｅと、円筒部７９ｅの外面と隙間を介して設けられ、偏心環状空間Ｋに配置されるカム部７９ａとからなっている。   1 and 4 again, the unlocking member 79 includes a main body portion 79d, a cylindrical portion 79e that is connected to the main body portion 79d, and fits inside the standing wall portion 63c of the external gear 63, and a cylindrical portion. The cam portion 79a is provided in the eccentric annular space K and is provided through an outer surface of the 79e and a gap.

ロック解除部材７９には、回転軸Ｏ２と同軸の穴７９ｆを有している。尚、本実施形態では、穴７９ｆの内面には、セレーションが施され、図示しない駆動軸が嵌合し、駆動軸とロック解除部材７９とは一体となって回転するようになっている。   The unlocking member 79 has a hole 79f coaxial with the rotation axis O2. In this embodiment, serrations are applied to the inner surface of the hole 79f, a drive shaft (not shown) is fitted, and the drive shaft and the unlocking member 79 rotate together.

カム部７９ａは、第１カム部材７１、第２カム部材７３の周方向の一方の端面である第１端面７１ｂ、第１端面７３ｂと対向する第１カム押圧部７９ｂを有している。また、カム部７９ａは、第１カム部材７１、第２カム部材７３の周方向の他方の端面である第２端面７１ｃ、第２端面７３ｃと対向する第２カム押圧部７９ｃを有している。   The cam portion 79 a includes a first cam member 71, a first end surface 71 b that is one end surface in the circumferential direction of the second cam member 73, and a first cam pressing portion 79 b that faces the first end surface 73 b. The cam portion 79a has a first cam member 71, a second end surface 71c that is the other circumferential end surface of the second cam member 73, and a second cam pressing portion 79c that faces the second end surface 73c. .

図１に示すように、内歯歯車６１、外歯歯車６３とは、連結リング８１で軸方向に相対移動できないように挟まれている。   As shown in FIG. 1, the internal gear 61 and the external gear 63 are sandwiched by a connecting ring 81 so that they cannot move relative to each other in the axial direction.

次に、上記構成の作動を説明する。図１、図４、図５を用いて、説明する。図５は図１に示すリクライニング装置のロック解除状態を説明する図である。   Next, the operation of the above configuration will be described. A description will be given with reference to FIGS. 1, 4, and 5. FIG. 5 is a view for explaining the unlocked state of the reclining device shown in FIG.

（ロック時）
図４に示すように、拡径方向に弾性復帰しようとするスプリング７７の端部７７ｂ、端部７７ｃは、カム穴７５の第１カム部材７１の第１凹部７１ａの斜面と、第２カム部材７３の第２凹部７３ａの斜面とに押圧している。 (When locked)
As shown in FIG. 4, the end 77b and the end 77c of the spring 77 to be elastically restored in the diameter increasing direction are the slope of the first recess 71a of the first cam member 71 of the cam hole 75 and the second cam member. 73 is pressed against the slope of the second recess 73a.

第１カム部材７１の第１凹部７１ａの斜面が押圧されることにより、第１カム部材７１は半径方向に移動し、外歯歯車６３の立壁部６３ｃの外面に押接している。また、第２カム部材７３の第２凹部７３ａの斜面が押圧されることにより、第２カム部材７３は半径方向に移動し、内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）内面に押接している。即ち、内歯歯車６１と外歯歯車６３とが両者の回転軸間の偏心量を増やす方向に付勢され、内歯歯車６１と外歯歯車６３の噛合部位では、内歯６１ｃと外歯６３ａとが圧接し、外歯歯車６３と内歯歯車６１の相対運動が禁止され、シートバックの傾動が禁止されるロック状態となっている。   When the inclined surface of the first recess 71 a of the first cam member 71 is pressed, the first cam member 71 moves in the radial direction and presses against the outer surface of the standing wall portion 63 c of the external gear 63. Further, when the inclined surface of the second recess 73a of the second cam member 73 is pressed, the second cam member 73 moves in the radial direction, and on the inner surface of the cylindrical standing wall portion 61e (circular hole) of the internal gear 61. It is pressed against. That is, the internal gear 61 and the external gear 63 are urged in a direction to increase the amount of eccentricity between the rotary shafts, and the internal teeth 61c and the external teeth 63a are engaged at the meshing portion of the internal gear 61 and the external gear 63. Are in a locked state in which the relative movement of the external gear 63 and the internal gear 61 is prohibited, and the tilt of the seat back is prohibited.

（ロック解除状態）
ロック状態において、操作ボタン、または操作ハンドルを操作して、図示しない駆動軸を右方向または左方向に回転駆動すると、ロック解除部材７９が右方向または左方向に回転する。一例として、図１において矢印Ｃ方向から見たとき、ロック解除部材７９が反時計方向に回転したとき、カム部７９ａの第１カム押圧部７９ｂが第１カム部材７１の第１端面７１ｂを最初に押し、第１カム部材７１のみが反時計方向に回転する。第１カム部材７１のみが回転移動することで、図５に示すようにカム穴７５の形状が変化する。このカム穴７５の形状変化により、スプリング７７の端部７７ｂ、端部７７ｃは矢印Ｄ方向にずれ、第１カム部材７１の第１凹部７１ａの斜面との当接位置が変わる。よって、第１カム部材７１の外歯歯車６３の立壁部６３ｃの外面を押接する力と、第２カム部材７３の内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）内面を押接する力とが減少し、内歯歯車６１と外歯歯車６３とが両者の回転軸間の偏心量が減る。 (Unlocked state)
When the operation button or the operation handle is operated in the locked state to drive the drive shaft (not shown) to the right or left, the lock release member 79 rotates to the right or left. As an example, when viewed from the direction of arrow C in FIG. 1, when the unlocking member 79 rotates counterclockwise, the first cam pressing portion 79 b of the cam portion 79 a first touches the first end surface 71 b of the first cam member 71. Only the first cam member 71 rotates counterclockwise. As only the first cam member 71 rotates, the shape of the cam hole 75 changes as shown in FIG. Due to the shape change of the cam hole 75, the end 77b and the end 77c of the spring 77 are displaced in the direction of arrow D, and the contact position of the first cam member 71 with the inclined surface of the first recess 71a changes. Therefore, the force that presses the outer surface of the standing wall portion 63c of the external gear 63 of the first cam member 71 and the force that presses the inner surface of the cylindrical standing wall portion 61e (circular hole) of the internal gear 61 of the second cam member 73. As a result, the amount of eccentricity between the rotating shafts of the internal gear 61 and the external gear 63 decreases.

よって、内歯歯車６１と外歯歯車６３の噛合部位での内歯６１ｃと外歯６３ａとの圧接が低減され、外歯歯車６３と内歯歯車６１の相対運動が可能となる。   Accordingly, the pressure contact between the internal teeth 61c and the external teeth 63a at the meshing portion of the internal gear 61 and the external gear 63 is reduced, and the external gear 63 and the internal gear 61 can be moved relative to each other.

更に、ロック解除部材７９が反時計方向に回転すると、カム部７９ａの第１カム押圧部７９ｂが第２カム部材７３の第１端面７３ｂと、第１カム部材７１の第１端面７１ｂとを押すようになり、外歯歯車６３は、内歯歯車６１の回転軸Ｏ１を中心に偏心運動しながら内歯歯車６１、外歯歯車６３の噛合位置が変化し、シートバックのシートクッションに対する傾動角が変わる。   Further, when the unlocking member 79 rotates counterclockwise, the first cam pressing portion 79b of the cam portion 79a presses the first end surface 73b of the second cam member 73 and the first end surface 71b of the first cam member 71. Thus, the external gear 63 changes the meshing position of the internal gear 61 and the external gear 63 while eccentrically moving around the rotation axis O1 of the internal gear 61, and the tilt angle of the seat back with respect to the seat cushion is changed. change.

このような構成によれば、以下のような効果がある。   Such a configuration has the following effects.

(1)スプリング７７の付勢力により第１カム部材７１、第２カム部材７３は半径方向に移動する。よって、第１カム部材７１、第２カム部材７３の移動量は少なく、カム部材の位置のばらつきが小さくなる。よって、第１カム部材７１、第２カム部材７３とロック解除部材７９のカム部７９ａとの隙間を小さくでき、ロック解除の操作と、実際にロック解除されるタイムラグが小さくなる。  (1) The first cam member 71 and the second cam member 73 move in the radial direction by the biasing force of the spring 77. Therefore, the movement amount of the first cam member 71 and the second cam member 73 is small, and the variation in the position of the cam member is small. Therefore, the clearance between the first cam member 71 and the second cam member 73 and the cam portion 79a of the unlocking member 79 can be reduced, and the unlocking operation and the time lag that is actually unlocked are reduced.

(2) 第１カム部材７１は、内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）内面に押接し、第２カム部材７３は、外歯歯車６３の立壁部６３ｃの外面に押接し、内歯歯車６１と外歯歯車６３との偏心状態を保持している。よって、シートバックの傾動時に、背景技術の欄で説明した楔状部材（カム部材）のスキップがなく、操作フィーリングがよい。  (2) The first cam member 71 is pressed against the inner surface of the cylindrical standing wall 61e (circular hole) of the internal gear 61, and the second cam member 73 is pressed against the outer surface of the standing wall 63c of the external gear 63. The eccentric state of the internal gear 61 and the external gear 63 is maintained. Therefore, when the seat back is tilted, the wedge-like member (cam member) described in the background art section is not skipped, and the operation feeling is good.

(3) 本実施形態では、外側の第１カム部材７１の円弧角を大きくして、ロック解除時にロック解除部材７９は最初に第１カム部材７１を押すようにしたことにより、スプリング７７の端部７７ｂ、端部７７ｃは矢印Ｄ方向にずれ、第１カム部材７１の外歯歯車６３の立壁部６３ｃの外面を押接する力と、第２カム部材７３の内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）内面を押接する力とが減少すると共に、内歯歯車６１と外歯歯車６３とが両者の回転軸間の偏心量が減り、ロック解除が容易に得られる。  (3) In this embodiment, the arc angle of the outer first cam member 71 is increased, and the unlocking member 79 first pushes the first cam member 71 when unlocking, so that the end of the spring 77 is The portion 77b and the end portion 77c are displaced in the direction of arrow D, and the force that presses the outer surface of the standing wall 63c of the external gear 63 of the first cam member 71 and the cylindrical standing wall of the internal gear 61 of the second cam member 73 The force that presses the inner surface of the portion 61e (circular hole) is reduced, and the amount of eccentricity between the rotating shafts of the internal gear 61 and the external gear 63 is reduced, so that unlocking can be easily obtained.

一方、内側の第２カム部材７３の円弧角を大きくして、ロック解除時にロック解除部材７９は最初に第２カム部材７３を押すようにした場合、スプリング７７の端部７７ｃは矢印Ｅ方向にずれるが、スプリング７７の端部７７ｂは傾斜角の大きな第２カム部材７３の斜面７３ｄで押されるので、矢印Ｆ方向（スプリング押し込み方向）に押され、ずれにくい。よって、第１カム部材７１の外歯歯車６３の立壁部６３ｃの外面を押接する力と、第２カム部材７３の内歯歯車６１の円筒状の立壁部６１ｅ（円形穴）内面を押接する力とが減少しにくく、内歯歯車６１と外歯歯車６３とが両者の回転軸間の偏心量も減りにくく、ロック解除しづらい。   On the other hand, when the arc angle of the second inner cam member 73 is increased so that the unlocking member 79 first pushes the second cam member 73 when unlocking, the end 77c of the spring 77 extends in the direction of arrow E. However, since the end 77b of the spring 77 is pushed by the slope 73d of the second cam member 73 having a large inclination angle, it is pushed in the arrow F direction (spring push-in direction) and is not easily displaced. Therefore, the force that presses the outer surface of the standing wall portion 63c of the external gear 63 of the first cam member 71 and the force that presses the inner surface of the cylindrical standing wall portion 61e (circular hole) of the internal gear 61 of the second cam member 73. And the internal gear 61 and the external gear 63 are less likely to reduce the amount of eccentricity between the rotating shafts of each other, and are difficult to unlock.

尚、本発明は上記実施形態に限定するものではない。上記実施形態ではリクライニング装置に適用した例で説明したが、他に、リンク機構を用いてシートクッションを昇降させるシートリフタ機構やチルト機構のリンクを回転させる部分に適用可能である。   In addition, this invention is not limited to the said embodiment. In the above-described embodiment, an example in which the present invention is applied to a reclining device has been described. However, the present invention can be applied to a part that rotates a link of a seat lifter mechanism or a tilt mechanism that lifts and lowers a seat cushion using a link mechanism.

また、パワーウインド、パワーシート、パワースライドドア、パワーバックドア、パワーラッゲージ等に用いられるモータと減速機とが一体となったギヤードモータの減速機部分にも適用可能である。   Further, the present invention can also be applied to a reduction gear portion of a geared motor in which a motor and a reduction gear used in a power window, a power seat, a power slide door, a power back door, a power luggage and the like are integrated.

更に、上記実施形態では、第１カム７１と第２カム７３との対向面に、半径方向にへこんだ第１凹部７１ａ、第２凹部７３ａを形成し、縮径方向に弾性変形したスプリング７７の弾性復帰力により、第１カム７１と第２カム７３とをロック方向に付勢したが、これに限定するものではない。例えば、第１カムの第２カムとの対向面に、第１傾斜面と、第１傾斜面と逆斜面の関係にある第２傾斜面とからなり、半径方向に突出した第１凸部を形成し、第２カムの第１カムとの対向面に、第３傾斜面と、第３傾斜面と逆斜面の関係にある第４傾斜面とからなり、半径方向に突出し、第１凸部と協同してカム穴を形成する第２凸部を形成し、拡径方向に弾性変形したスプリングの一方の端部を第１凸部の第１傾斜面、第２凸部の第３傾斜面に係合させ、他方の端部を第１凸部の第２傾斜面、第２凸部の第４傾斜面に係合させるようにしてもよい。   Furthermore, in the above-described embodiment, the first recess 71a and the second recess 73a that are recessed in the radial direction are formed on the opposing surfaces of the first cam 71 and the second cam 73, and the spring 77 elastically deformed in the diameter reducing direction is formed. Although the first cam 71 and the second cam 73 are urged in the locking direction by the elastic restoring force, the present invention is not limited to this. For example, a first convex portion that protrudes in the radial direction is formed of a first inclined surface and a second inclined surface having a reverse inclined surface relationship with the first inclined surface on a surface of the first cam facing the second cam. The first convex portion is formed and includes a third inclined surface on a surface facing the first cam of the second cam, and a fourth inclined surface having a relationship of a reverse slope with the third inclined surface, and protrudes in the radial direction. The second convex part which forms a cam hole in cooperation with the one end of the spring which is elastically deformed in the diameter increasing direction is the first inclined surface of the first convex part and the third inclined surface of the second convex part The other end may be engaged with the second inclined surface of the first convex portion and the fourth inclined surface of the second convex portion.

６１ 内歯歯車
６１ｅ 立壁部（円形穴）
６３ 外歯歯車
６３ｃ 立壁部（円筒）
７１ 第１カム部材
７３ 第２カム部材
７７ スプリング（付勢部材）
７９ ロック解除部材 61 Internal gear 61e Standing wall (circular hole)
63 External gear 63c Standing wall (cylindrical)
71 First cam member 73 Second cam member 77 Spring (biasing member)
79 Unlocking member

Claims (4)

固定部材側、回転部材側のうちのいずれか一方の側に設けられた内歯歯車と、
前記固定部材側、前記回転部材側のうちの他方の側に設けられ、歯数が前記内歯歯車よりも少なく、前記内歯歯車に噛合する外歯歯車と、
前記内歯歯車、前記外歯歯車のうちのいずれか一方を他方の歯車の回転軸を中心に偏心運動させながら前記内歯歯車、前記外歯歯車の噛合位置を変化させることにより、前記回転部材の前記固定部材に対する傾動角を変える減速歯車機構であって、
前記外歯歯車、前記内歯歯車のうちの一方の歯車に設けられ、その回転軸を中心とした円形穴と、
前記外歯歯車、前記内歯歯車のうちの他方の歯車に設けられ、その回転軸を中心とし、前記円形穴に挿入される円筒と、
前記円形穴の内面と円筒の外面との間の空間に設けられ、径方向に積層され、協同してカム穴を形成する少なくとも２つのカム部材と、
前記カム穴に係合し、少なくとも１つの前記カム部材を前記円形穴の内面に、少なくとも１つの前記カム部材を前記円筒の外面に押接する方向に付勢する付勢部材と、
前記カム部材のうちの１つのカム部材を移動させて前記カム穴形状を変化させ、前記カム部材の前記円形穴の内面，前記円筒の外面への押接力を減らすロック解除部材と、
を有することを特徴とする減速歯車機構。 An internal gear provided on either the fixed member side or the rotating member side;
An external gear that is provided on the other side of the fixed member side and the rotating member side, has fewer teeth than the internal gear, and meshes with the internal gear;
By changing the meshing position of the internal gear and the external gear while either one of the internal gear and the external gear is eccentrically moved around the rotation axis of the other gear, the rotating member is obtained. A reduction gear mechanism that changes the tilt angle of the fixed member with respect to the fixed member,
A circular hole provided on one of the external gear and the internal gear and having a rotation axis as a center;
A cylinder that is provided on the other gear of the external gear and the internal gear, and that is inserted into the circular hole around the rotation axis;
At least two cam members provided in a space between the inner surface of the circular hole and the outer surface of the cylinder, stacked in a radial direction, and cooperatively forming a cam hole;
An urging member that engages with the cam hole and urges at least one of the cam members on an inner surface of the circular hole and urges at least one of the cam members on an outer surface of the cylinder;
An unlocking member that moves one cam member of the cam members to change the shape of the cam hole, and reduces the pressing force to the inner surface of the circular hole of the cam member and the outer surface of the cylinder;
A reduction gear mechanism characterized by comprising: 前記カム部材は、
前記円形穴の内面側に設けられた第１カム部材と、
該第１カム部材より前記円筒の外面側に設けられた第２カム部材とからなり、
前記第１カム部材の前記第２カム部材との対向面に、二つの傾斜面からなり、半径方向にへこんだ第１凹部が形成され、
第２カム部材の前記第１カム部材との対向面に、二つの傾斜面からなり、半径方向にへこみ、前記第１凹部と協同して前記カム穴を形成する第２凹部が形成されたことを特徴とする請求項１記載の減速歯車機構。 The cam member is
A first cam member provided on the inner surface side of the circular hole;
A second cam member provided on the outer surface side of the cylinder from the first cam member;
A first concave portion formed of two inclined surfaces and recessed in the radial direction is formed on a surface of the first cam member facing the second cam member,
On the surface of the second cam member facing the first cam member, there are formed two inclined surfaces that are recessed in the radial direction and that form the cam hole in cooperation with the first recess. The reduction gear mechanism according to claim 1. 前記付勢手段は、
前記第１カム部材の第１凹部の二つの傾斜面を押して、前記第１カム部材を前記円形穴の内面に押接させ、
前記第２カム部材の第２凹部の二つの傾斜面を押して、前記第２カム部材を前記円筒の外面に押接させること特徴とする請求項２記載の減速歯車機構。 The biasing means is
Pressing the two inclined surfaces of the first recess of the first cam member to press the first cam member against the inner surface of the circular hole;
3. The reduction gear mechanism according to claim 2, wherein the second cam member is pressed against the outer surface of the cylinder by pressing two inclined surfaces of the second recess of the second cam member. 前記ロック解除部材は、
前記空間に配置され、前記第１カム部材の周方向の端部を押すカム押圧部を有することを特徴とする請求項２記載の減速歯車機構。 The unlocking member is
The speed reduction gear mechanism according to claim 2, further comprising a cam pressing portion that is disposed in the space and presses a circumferential end portion of the first cam member.
JP2011227574A 2011-10-17 2011-10-17 Reduction gear mechanism Expired - Fee Related JP5781890B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013215613A1 (en) * 2013-08-07 2015-02-12 Sitech Sitztechnik Gmbh Vehicle seat with integrated adjustment mechanism and method for connecting a fitting for a vehicle seat

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Publication number Priority date Publication date Assignee Title
JP2002058562A (en) * 2000-07-11 2002-02-26 Faurecia Autositze Gmbh & Co Kg Adjusting fitting for automobile seat, particularly inclination adjusting fitting for backrest part of automobile seat
US20080061616A1 (en) * 2006-09-12 2008-03-13 Lear Corporation Continuous recliner
JP2009055985A (en) * 2007-08-30 2009-03-19 Fuji Kiko Co Ltd Vehicle seat reclining device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002058562A (en) * 2000-07-11 2002-02-26 Faurecia Autositze Gmbh & Co Kg Adjusting fitting for automobile seat, particularly inclination adjusting fitting for backrest part of automobile seat
US20080061616A1 (en) * 2006-09-12 2008-03-13 Lear Corporation Continuous recliner
JP2009055985A (en) * 2007-08-30 2009-03-19 Fuji Kiko Co Ltd Vehicle seat reclining device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013215613A1 (en) * 2013-08-07 2015-02-12 Sitech Sitztechnik Gmbh Vehicle seat with integrated adjustment mechanism and method for connecting a fitting for a vehicle seat

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