JP2005231414A - Angle adjusting mechanism - Google Patents

Angle adjusting mechanism Download PDF

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JP2005231414A
JP2005231414A JP2004040359A JP2004040359A JP2005231414A JP 2005231414 A JP2005231414 A JP 2005231414A JP 2004040359 A JP2004040359 A JP 2004040359A JP 2004040359 A JP2004040359 A JP 2004040359A JP 2005231414 A JP2005231414 A JP 2005231414A
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internal gear
tooth
trochoid
gear portion
seat
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JP4107249B2 (en
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Sadao Ito
定夫 伊東
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Aisin Corp
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Aisin Seiki Co Ltd
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Priority to JP2004040359A priority Critical patent/JP4107249B2/en
Priority to TW093123244A priority patent/TWI249482B/en
Priority to EP04773148A priority patent/EP1663702B1/en
Priority to PCT/JP2004/013489 priority patent/WO2005025930A2/en
Priority to US10/571,259 priority patent/US7611436B2/en
Priority to KR1020067004993A priority patent/KR100852966B1/en
Priority to DE602004023862T priority patent/DE602004023862D1/en
Priority to EP09169250A priority patent/EP2116413B1/en
Publication of JP2005231414A publication Critical patent/JP2005231414A/en
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Publication of JP4107249B2 publication Critical patent/JP4107249B2/en
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  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an angle adjusting mechanism for a seat position adjusting device having a small size and excellent strength by combining gears having tooth profiles securing the strength. <P>SOLUTION: A tooth profile of an external gear part 54 is shaped into a circle, and a tooth profile of a first internal gear part 57 is shaped into a trochoid or cycloid shape. A tooth profile of a second internal gear part 65 is formed into a trochoid or cycloid shape formed on the basis of a stationary circle 23 whose diameter is larger than a stationary circle 24 of the first internal gear part 57 at a base point P in the same position as the first internal gear 57. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、シートの着座者の姿勢に合わせて、シートの形態を変更可能とする位置調整装置に適用される角度調整機構に関する。   The present invention relates to an angle adjusting mechanism applied to a position adjusting device that can change the form of a seat in accordance with the posture of a seat occupant.

従来、着座者が操作することによって、シートの形態を調整可能にするこの種の角度調整機構を適用した角度調整機構として、シートバーチカル装置又はシートリクライニング装置等がある。例えば、このようなシートバーチカル装置の角度調整機構は、第１内歯歯車部を備える可動部と、可動部を回転自在に支持し第１内歯歯車部と同中心軸上に配置され、第１内歯歯車部より歯数が少なくとも1つ異なる第２内歯歯車部を備える固定部とを備えて、これら第１と第２内歯歯車部に共通して噛合う外歯歯車部を有するピニオンを配置している。そして、操作によってピニオンの中心を第１と第２内歯歯車部の中心軸に周りに公転させることによって固定部に対して可動部を回転させる角度調整機構である。この機構ではピニオンの公転数に対して、可動部が大きく減速されて回転するものとなっている。そして、可動部に連結されたシートクッションの高さが軽い操作力で調整可能となっている。従来の角度調整機構では同軸に配置され、しかも歯数の異なる第１内歯歯車部と第２内歯歯車部が同じ外歯歯車部と円滑に噛合い作動することを可能にするために、外歯歯車部及び第１内歯歯車部と第２内歯歯車部はそれぞれ異なる転位で形成された転位歯形が利用されている(例えば、特許文献１参照。)。
特開２００３−２３７４３３公報 2. Description of the Related Art Conventionally, as an angle adjustment mechanism to which this type of angle adjustment mechanism that makes it possible to adjust the form of a seat when operated by a seated person, there is a seat vertical device or a seat reclining device. For example, the angle adjustment mechanism of such a seat vertical device includes a movable part having a first internal gear part, a movable part rotatably supported on the same central axis as the first internal gear part, A fixed portion having a second internal gear portion having at least one different number of teeth from one internal gear portion, and having an external gear portion that meshes in common with the first and second internal gear portions. A pinion is placed. And it is an angle adjustment mechanism which rotates a movable part with respect to a fixed part by revolving the center of a pinion around the central axis of a 1st and 2nd internal gear part by operation. In this mechanism, the movable portion is greatly decelerated and rotated with respect to the revolution number of the pinion. The height of the seat cushion connected to the movable part can be adjusted with a light operating force. In order to allow the first internal gear portion and the second internal gear portion, which are arranged coaxially in the conventional angle adjusting mechanism and have different numbers of teeth, to smoothly mesh and operate with the same external gear portion, The external gear portion, the first internal gear portion, and the second internal gear portion use dislocation tooth forms formed by different dislocations (see, for example, Patent Document 1).
JP 2003-237433 A

上記した転位歯形を有する歯車の組合わせを利用した角度調整機構では、減速比の大きな歯車機構を用いて乗員の体重が掛かったシートの姿勢を軽い操作力で調整可能にしている。しかし、従来のこのような角度調整機構では、転位歯車として通常インボリュート歯形が採用されていて、図１２及び図１３に示されるように、プラス方向に転位して（歯の切削工具を標準位置から歯車中心外側方向に移動）成形された外歯では、先端部が細くなり、この先端部分が欠け易くなる。更に、インボリュート歯形の組合せでは、第１と第２内歯歯車１５７、１６５とピニオンギヤ１５４が当接する噛合い点を結ぶ噛合い線は直線となる（図１２と図１３）。このために一回転の間で平均した噛合い点の数（噛合い率）は小さく、特に車両の衝突時など歯車に過大な荷重が作用するシートの位置調整装置に適用した場合は、角度調整機構を大型にして強度を確保する必要がある。   In the angle adjusting mechanism using a combination of gears having a shift tooth profile as described above, the posture of the seat on which the weight of the occupant is applied can be adjusted with a light operating force by using a gear mechanism having a large reduction ratio. However, in such a conventional angle adjusting mechanism, an involute tooth profile is normally adopted as the shift gear, and as shown in FIGS. 12 and 13, the shift is performed in the plus direction (the tooth cutting tool is moved from the standard position). In the external teeth molded (moving outward in the center of the gear), the tip portion becomes thin and the tip portion is easily chipped. Further, in the combination of involute tooth shapes, the mesh line connecting the mesh points where the first and second internal gears 157 and 165 and the pinion gear 154 come into contact with each other is a straight line (FIGS. 12 and 13). For this reason, the number of meshing points (meshing rate) averaged during one rotation is small, especially when applied to a seat position adjustment device in which an excessive load is applied to the gear, such as during a vehicle collision. It is necessary to secure the strength by increasing the size of the mechanism.

このために、本発明の課題は、強度の確保ができる歯形を有する歯車の組合せによって、強度に優れ、小型に構成できるシートの位置調整装置のための角度調整機構を実現することである。   Therefore, an object of the present invention is to realize an angle adjusting mechanism for a sheet position adjusting device that is excellent in strength and can be made compact by a combination of gears having tooth shapes that can ensure strength.

上記した技術的課題を解決するために講じた第１の技術的手段は、車両用シートの乗員の着座姿勢を調整可能とするためにシートの可動側に固定され、第１内歯歯車部を備える可動部と、前記可動部を回転自在に支持し第１内歯歯車部と同中心に配置され第１内歯歯車部とは少なくとも歯数が1つ異なる第２内歯歯車部を備える固定部と、前記第１内歯歯車部と前記第２内歯歯車部に噛合う外歯歯車部を有するピニオンを備える角度調整機構において、
前記外歯歯車部の歯形を円形状歯形とし、前記第１内歯歯車部の歯形をトロコイドまたはサイクロイド歯形で、前記第２内歯歯車部の歯形を前記第１内歯歯車部とは同位置の基点で且つ前記第１内歯歯車部の固定円より径を大とする固定円を基に形成されたトロコイドまたはサイクロイド歯形としたことである。 The first technical means taken in order to solve the above technical problem is fixed to the movable side of the seat so that the seating posture of the occupant of the vehicle seat can be adjusted, and the first internal gear portion is A fixed portion provided with a movable portion provided, and a second internal gear portion that is rotatably supported by the movable portion and is disposed at the same center as the first internal gear portion and having a number of teeth different from that of at least one tooth An angle adjustment mechanism comprising a pinion having an external gear portion meshing with a portion, and the first internal gear portion and the second internal gear portion,
The tooth form of the external gear part is a circular tooth form, the tooth form of the first internal gear part is a trochoid or cycloid tooth form, and the tooth form of the second internal gear part is the same position as the first internal gear part. And a trochoidal or cycloid tooth profile formed on the basis of a fixed circle having a diameter larger than that of the fixed circle of the first internal gear portion.

また、本発明で講じた第２の技術的手段は第１の手段に加えて、各前記トロコイドまたはサイクロイド歯形は、少なくとも前記円形状歯形と噛合いする範囲において、各前記トロコイドまたはサイクロイド歯形を形成するために定められる所定のトロコイドまたはサイクロイド曲線より一定間隔離れて歯面が形成されているようにしたことである。   In addition to the first means, the second technical means provided in the present invention is that each trochoid or cycloid tooth form forms each of the trochoid or cycloid tooth forms at least within the range of meshing with the circular tooth form. In other words, the tooth surface is formed at a predetermined distance from a predetermined trochoid or cycloid curve.

更に、また、本発明で講じた第３の技術的手段は第１の手段に加えて、前記外歯歯車部の歯先部と少なくとも前記第１内歯歯車部及び前記第２内歯歯車部のいずれか一方の歯底部分との間には間隙が設けたことをである。   Furthermore, in addition to the first means, the third technical means taken in the present invention is a tooth tip portion of the external gear portion, at least the first internal gear portion, and the second internal gear portion. That is, a gap is provided between any one of the tooth bottom portions.

請求項１に記載の発明によれば、先端が細くならずに形成された歯形状を有する外歯歯車と、トロコイドまたはサイクロイド歯形による内歯歯車によって大きな噛合い率を達成でき、強度の向上が図られる。   According to the first aspect of the present invention, a large meshing rate can be achieved by the external gear having a tooth shape formed without the tip being narrowed and the internal gear having a trochoid or cycloid tooth profile, thereby improving the strength. Figured.

また、請求項２に記載の発明によれば、円形状歯形を備える外歯歯車はトロコイドまたはサイクロイド歯車となっている第１及び第２内歯歯車部と隙間が非常に少ない噛合いが可能となり、ガタの少ない角度調整機構が実現できる。   According to the second aspect of the present invention, the external gear having a circular tooth profile can be meshed with the first and second internal gear portions which are trochoid or cycloid gears with very little clearance. An angle adjustment mechanism with little backlash can be realized.

更に、請求項３に記載の発明によれば、間隙は、噛合い作動のための潤滑用グリースが溜まるスペースとして機能し、角度調整機構の円滑な作動と、耐久性の向上をもたらす。   Further, according to the third aspect of the present invention, the gap functions as a space in which lubricating grease for meshing operation accumulates, and provides smooth operation of the angle adjusting mechanism and improved durability.

本発明に係る角度調整機構５の実施の形態について、以下に図１から図１１に基づいて説明する。   An embodiment of the angle adjusting mechanism 5 according to the present invention will be described below with reference to FIGS.

図１に示されるように、シート１０には位置調整装置としてシートクッション２の前端部分に装着されシートクッション２の上下方向位置を調整可能とするシートバーチカル装置４、シート１０の前後方向位置を調整可能とするシートスライド装置８、更にシートバック１の傾斜角度を調整可能とするリクライニング装置３を備える。本発明に係わる角度調整機構５はシート１０のリクライニング装置３とシートバーチカル装置４に適用可される。   As shown in FIG. 1, a seat vertical device 4 that is attached to the front end portion of the seat cushion 2 as a position adjusting device on the seat 10 and that allows the vertical position of the seat cushion 2 to be adjusted, and the front-back direction position of the seat 10 are adjusted. A seat slide device 8 that can be used, and a reclining device 3 that can adjust the inclination angle of the seat back 1 are provided. The angle adjusting mechanism 5 according to the present invention is applicable to the reclining device 3 and the seat vertical device 4 of the seat 10.

本発明に係わる角度調整機構５の基本構成及びその作動原理は、シートバーチカル装置４と、リクライニング装置３に適用されるものとは同じであるために、以下ではシートバーチカル装置４を例にして説明する。   Since the basic configuration of the angle adjusting mechanism 5 and the operation principle thereof according to the present invention are the same as those applied to the seat vertical device 4 and the reclining device 3, the following description will be given by taking the seat vertical device 4 as an example. To do.

図１に示されるように、シートバーチカル装置４はシートスライド８上に固定され、シートクッション２の強度を担う基板部３１を有する。基板部３１は縦壁部を有して、また左右の基板部３１の前端部を連結するようにクッションフレーム４１が配置されている。クッションフレーム４１は基板部３１の縦壁部に枢軸４３で上下方向に揺動回転ができるように取付けられている。   As shown in FIG. 1, the seat vertical device 4 is fixed on a seat slide 8 and has a substrate portion 31 that bears the strength of the seat cushion 2. The board part 31 has a vertical wall part, and a cushion frame 41 is arranged so as to connect the front end parts of the left and right board parts 31. The cushion frame 41 is attached to the vertical wall portion of the base plate portion 31 so as to be able to swing and rotate about the pivot 43 in the vertical direction.

左右の基板部３１の一方側前端部には前後方向に延びるアーム４６が、ピン４７によって、その後端で回転自在に結合されている。また、左右の基板部３１の他方側前端部には、駆動アーム５１を備える角度調整機構５が取付けられている。   An arm 46 extending in the front-rear direction is coupled to the front end portion on one side of the left and right substrate portions 31 by pins 47 so as to be rotatable at the rear ends. An angle adjusting mechanism 5 having a drive arm 51 is attached to the other front end of the left and right substrate portions 31.

図１と図３に示すように、駆動アーム５１は角度調整機構５の作動で基板部３１に対して回転可能になっている。駆動アーム５１とアーム４６の各先端には連結シャフト４２が溶接され、互いに連結されている。また、連結シャフト４２の左右端には、ピン４４がシート１０の幅方向の外側に向けて取付けられ、クッションフレーム４１の側壁部に形成され前後方向延びて形成された長穴４５に嵌っている。   As shown in FIGS. 1 and 3, the drive arm 51 is rotatable with respect to the substrate portion 31 by the operation of the angle adjustment mechanism 5. Connection shafts 42 are welded to the distal ends of the drive arm 51 and the arm 46 and are connected to each other. Further, pins 44 are attached to the left and right ends of the connecting shaft 42 toward the outer side in the width direction of the seat 10 and are fitted in elongated holes 45 formed on the side wall portions of the cushion frame 41 and extending in the front-rear direction. .

図２に示されるように、角度調整機構５は、基板部３１の前端側面部上に、３つのピン５５で固定して取付けられる固定ギヤメンバ５６有する。固定ギヤメンバ５６は平板状で、駆動アーム５１が側面で固定ギヤメンバ５６に対して当接し回転可能に係合する。更に図２と図３に示されるように、固定ギヤメンバ５６の側面部には回転軸受けとなる円形の凹部５８が形成され、対向する駆動アーム５１の側面部には回転部６８となる円形の突起が形成され、凹部５８と回転部６８は互いにガタが少なく且つ滑らかに回転が可能となる。   As shown in FIG. 2, the angle adjustment mechanism 5 has a fixed gear member 56 that is fixedly attached to the front side surface portion of the substrate portion 31 with three pins 55. The fixed gear member 56 has a flat plate shape, and the drive arm 51 abuts against the fixed gear member 56 on the side surface and is rotatably engaged. Further, as shown in FIGS. 2 and 3, a circular recess 58 serving as a rotation bearing is formed on the side surface of the fixed gear member 56, and a circular protrusion serving as the rotation unit 68 is formed on the side surface of the opposing drive arm 51. The concave portion 58 and the rotating portion 68 have little backlash and can be rotated smoothly.

固定ギヤメンバ５６の側面部には凹部５８と同心の窪み部が形成され、窪み部の内周面に第１内歯歯車５７が形成されている。一方、駆動アーム５１の側面部にも同様に窪み部が形成され、その窪み部の内周面には第２内歯歯車６５が形成されている。第１内歯歯車５７は第２内歯歯車６５より少なくとも一つ歯数が少ない。各第１と第２内歯歯車５７、６５の中心に形成されている軸穴５９、６６が、シャフト５２の第１軸部５２ｂで回転可能に嵌って同心軸上に配置されている。シャフト５２には第１軸部５２ｂの中間部分に第１軸部５２ｂより大きい径の第２軸部５２ａが形成されている。第２軸部５２ａの中心軸は、第１軸部５２ｂの中心軸に対して所定の間隔離れ且つ第１軸部５２ｂと並行に設定されている、即ち偏心したものとなっている。そして、第２軸部５２ａは、固定ギヤメンバ５６と駆動アーム５１が対向して組合わされた状態で、両方の窪みで形成される空間内に位置されている。第２軸部５２ａの外径は固定ギヤメンバ５６側が大きく駆動アーム５１に近づくほど小さくなるように、テーパ形状に形成されている。   A concave portion concentric with the concave portion 58 is formed on the side surface portion of the fixed gear member 56, and a first internal gear 57 is formed on the inner peripheral surface of the concave portion. On the other hand, a concave portion is similarly formed in the side surface portion of the drive arm 51, and a second internal gear 65 is formed on the inner peripheral surface of the concave portion. The first internal gear 57 has at least one fewer teeth than the second internal gear 65. Shaft holes 59 and 66 formed at the centers of the first and second internal gears 57 and 65 are fitted on the first shaft portion 52b of the shaft 52 so as to be rotatable and arranged on the concentric shaft. The shaft 52 is formed with a second shaft portion 52a having a diameter larger than that of the first shaft portion 52b at an intermediate portion of the first shaft portion 52b. The central axis of the second shaft portion 52a is set apart from the central axis of the first shaft portion 52b by a predetermined distance and in parallel with the first shaft portion 52b, that is, decentered. And the 2nd axial part 52a is located in the space formed with both hollows in the state which the fixed gear member 56 and the drive arm 51 combined in opposition. The outer diameter of the second shaft portion 52a is formed in a tapered shape so that the fixed gear member 56 side is larger and closer to the drive arm 51.

図２と図３に示すように、第２軸部５２ａ上にはピニオン５４が回転可能に取付けられている。ピニオン５４の外周に内歯歯車５７、６５の両方と噛合う外歯歯車５４ｂが形成されている。また、ピニオン５４の中心に設けられる回転穴５４ａは内径面がテーパ形状になっている。   As shown in FIGS. 2 and 3, a pinion 54 is rotatably mounted on the second shaft portion 52a. An external gear 54 b that meshes with both the internal gears 57 and 65 is formed on the outer periphery of the pinion 54. The rotation hole 54a provided at the center of the pinion 54 has a tapered inner diameter surface.

図1、図２及び図３に示されるように、シャフト５２の一方は、固定ギヤメンバ５６を貫通してシート１０の幅方向外側に延び、その先端に操作ハンドル７が固定して取付けられる。また、他方は駆動アーム５１を貫通して、シート１０の幅方向内側に延び、端部にワッシャ６１が取付けられる。ワッシャ６１と駆動アーム５１との間にスプリング６２が配置され、シャフト５２をシート１０の幅方向内側に付勢している。この付勢力によって、ピニオン５４の回転穴５４ａの内面を第２軸部５２ａ外径のテーパ面によって噛合い位置の方向に押し、噛合いのバックラッシュを無くする構成となっている。   As shown in FIGS. 1, 2, and 3, one of the shafts 52 extends through the fixed gear member 56 to the outside in the width direction of the seat 10, and the operation handle 7 is fixedly attached to the tip of the shaft 52. Further, the other passes through the drive arm 51 and extends inward in the width direction of the seat 10, and a washer 61 is attached to the end. A spring 62 is disposed between the washer 61 and the drive arm 51 and urges the shaft 52 inward in the width direction of the seat 10. With this urging force, the inner surface of the rotation hole 54a of the pinion 54 is pushed in the direction of the meshing position by the tapered surface of the second shaft portion 52a and the meshing backlash is eliminated.

次に本発明の主眼とする、上記した第１及び第２内歯歯車５７、６５、と外歯歯車５４ｂの歯形形状の形成方法について説明する。このために、先ず図７と図８を用いて、各歯車の歯形を決める基となるトロコイド曲線とサイクロイド曲線について述べる。   Next, a method for forming the tooth profile of the first and second internal gears 57 and 65 and the external gear 54b, which is the main point of the present invention, will be described. For this purpose, first, a trochoid curve and a cycloid curve, which are the basis for determining the tooth profile of each gear, will be described with reference to FIGS.

図７に示される３種類の曲線１２６、１２７，１２８は外側の固定円１２４に対して、内接して転がる回転円１２５を定義したとき、この回転円１２５と一体となっている点Ｐ１、Ｐ２，Ｐ３が描く軌跡を示し、トロコイド曲線と呼ばれる。各点Ｐ１、Ｐ２，Ｐ３が、夫々の曲線上で最も固定円１２４の中心から最も離れた図示されている位置を、各トロコイド曲線の基点と定義する。ここで、基点Ｐ１は回転円１２５の内側に、基点Ｐ２は回転円１２５の外側に位置し、基点Ｐ３は回転円１２５上に位置している。曲線１２８のようにＰ３が回転円１２５上ある場合は、トロコイド曲線の特別な場合としてサイクロイド曲線と呼ばれる。基点Ｐ１のように回転円１２５の内側にある場合は、ループ１２６ａが描かれる。   The three kinds of curves 126, 127, and 128 shown in FIG. 7 define points P1, P2 that are integral with the rotation circle 125 when a rotation circle 125 that is inscribed and rolled with respect to the outer fixed circle 124 is defined. , P3 indicate the trajectory drawn and is called a trochoid curve. The illustrated position where each point P1, P2, P3 is farthest from the center of the fixed circle 124 on each curve is defined as the base point of each trochoid curve. Here, the base point P1 is located inside the rotation circle 125, the base point P2 is located outside the rotation circle 125, and the base point P3 is located on the rotation circle 125. When P3 is on the rotation circle 125 like the curve 128, it is called a cycloid curve as a special case of the trochoid curve. When it is inside the rotation circle 125 like the base point P1, a loop 126a is drawn.

次に、本発明に係わる角度調整機構５の第１及び第２内歯歯車５７、６５の基となるトロコイド曲線は、上記の基点Ｐ１とＰ２に相当する基点を、図８に示される同位置の基点Ｐとなるように設定された固定円と回転円とによって求められる。即ち、第１内歯歯車５７に対する第１トロコイド曲線２７を描く固定円２４と回転円２５、第２内歯歯車６５に対する第２トロコイド曲線２６を描く固定円２２と回転円２３の２組となる。ここで、固定円２２は固定円２３より大きい径になり、また各固定円２２、２４は一致して中心Ｏ１に、また各回転円２３、２５の中心も一致してＯ２に位置する。そして、Ｏ１とＯ２は所定の距離離れて設定されている。Ｏ１とＯ２間の距離は、シャフト５２の第１軸部５２ｂと第２軸部５２ａの中心軸の偏心量と一致したものとなっている。このように描かれる第２トロコイド曲線２６は基点Ｐを頂点とするループ２６を有し、またトロコイド曲線２７は基点Ｐが頂点となる、尖った形状を有する軌跡となる。   Next, the trochoid curve that is the basis of the first and second internal gears 57 and 65 of the angle adjusting mechanism 5 according to the present invention is based on the base points corresponding to the base points P1 and P2 shown in FIG. It is calculated | required by the fixed circle and rotation circle set so that it might become the base point P of. That is, there are two sets of a fixed circle 24 and a rotation circle 25 that draw the first trochoid curve 27 for the first internal gear 57, and a fixed circle 22 and a rotation circle 23 that draw the second trochoid curve 26 for the second internal gear 65. . Here, the fixed circle 22 has a larger diameter than the fixed circle 23, and the fixed circles 22 and 24 coincide with each other at the center O1, and the centers of the respective rotation circles 23 and 25 coincide with each other and are positioned at O2. O1 and O2 are set a predetermined distance apart. The distance between O1 and O2 matches the amount of eccentricity of the central axis of the first shaft portion 52b and the second shaft portion 52a of the shaft 52. The second trochoid curve 26 drawn in this way has a loop 26 having the base point P as an apex, and the trochoid curve 27 becomes a locus having a sharp shape with the base point P being an apex.

上記各トロコイド曲線を基にして、図１０と図１１に示されるように、第１内歯歯車５７は、トロコイド曲線２７に対して、一定の距離Ｒを保って形成された歯面を有するように、また第２内歯歯車６５は、トロコイド曲線２６に対して、一定の距離Ｒを保って形成された歯面を有するように形成される。   Based on the above trochoid curves, as shown in FIGS. 10 and 11, the first internal gear 57 has a tooth surface formed with a constant distance R with respect to the trochoid curve 27. In addition, the second internal gear 65 is formed so as to have a tooth surface formed with a constant distance R with respect to the trochoid curve 26.

一方、上記のように成形された第１内歯歯車５７と第２内歯歯車６５とに噛合う外歯歯車５４ｂの歯形は、図９に示されるように第１及び第２内歯歯車５７、６５の基点Ｐと一致する位置に設定された基点Ｑを中心とし、半径Ｒで成形された円形状歯形となっている。   On the other hand, the tooth profile of the external gear 54b meshed with the first internal gear 57 and the second internal gear 65 formed as described above is the first and second internal gear 57 as shown in FIG. , 65 is a circular tooth profile formed with a radius R, with the base point Q set at a position coincident with the base point P of 65 as the center.

このように形成された外歯歯車５４ｂと第１及び第２内歯歯車５７、６５との噛合いは、各トロコイド曲線２６、２７を点Ｑが辿るように移動するので、理論的にも精度の良い噛合いが実現できる歯形となっている。このために、角度調整機構５によって車両用シート１０の位置調整装置ように、走行中の振動に曝される場合でもガタ付きとか騒音の発生の少ない装置が可能となる。   The meshing between the external gear 54b formed in this way and the first and second internal gears 57 and 65 moves so that the point Q follows the trochoidal curves 26 and 27, so that the accuracy is theoretically accurate. It is a tooth profile that can achieve good meshing. For this reason, an apparatus with little play or noise generation is possible even when exposed to vibration during traveling, such as a position adjustment device for the vehicle seat 10 by the angle adjustment mechanism 5.

図４、図５及び図６に本発明の第１及び第２内歯歯車５７、６５と外歯歯車５４ｂの噛合いの状態を示す。特に図５と図６に示されるように、第１内歯歯車５７と外歯歯車５４ｂの接触点を結ぶ噛合い線５７aと、第２内歯歯車６５と外歯歯車５４ｂの接触点を結ぶ噛合い線６５ａは円弧となる。インボリュート歯形の噛合い線１５８、１５９（図１２、図１３）は直線となるのに比べ、トロコイド歯車の方がより多くの当接点が得られ、強度向上が図りやすい構成となる。また円形状歯形となる外歯歯車５４ｂは、欠け易くなるように先端部で歯幅が狭くなることがなく、この点でもインボリュート歯形よりは、強度的に有利に構成できる。   4, 5 and 6 show the meshing state of the first and second internal gears 57, 65 and the external gear 54b of the present invention. In particular, as shown in FIGS. 5 and 6, the mesh line 57a connecting the contact points of the first internal gear 57 and the external gear 54b and the contact points of the second internal gear 65 and the external gear 54b are connected. The mesh line 65a is an arc. Compared to the involute teeth meshing lines 158 and 159 (FIGS. 12 and 13) being straight, the trochoidal gear has more contact points, and the strength can be easily improved. Further, the external gear 54b having a circular tooth profile does not have a narrowed tooth width at the tip so as to be easily chipped, and in this respect as well, the external gear 54b can be configured more advantageously than the involute tooth profile.

図９に示されるように、外歯歯車５４ｂの歯先部分を距離d削除して少なくとも第１及び第２内歯歯車５７、６５の一方と最も深く噛合う位置でも、外歯歯車５４ｂとの間に間隙５４aが生じるように構成している。間隙５４aは、噛合い作動のための潤滑用グリースが溜まるスペースとして機能し、角度調整機構５の円滑な作動と、耐久性の向上をもたらす。尚、図９のように外歯歯車５４ｂの歯先部分を削除する方法によらずに、第１または第２内歯歯車５７、６５の歯底を削除する方法で間隙を確保しても良いことは自明である。   As shown in FIG. 9, the tooth tip portion of the external gear 54b is deleted by the distance d, and at least the position where the external gear 54b meshes most with one of the first and second internal gears 57 and 65, A gap 54a is formed between them. The gap 54a functions as a space in which lubricating grease for meshing operation accumulates, and provides smooth operation of the angle adjusting mechanism 5 and improved durability. Note that the gap may be secured by a method of deleting the tooth bottom of the first or second internal gear 57, 65, instead of the method of deleting the tooth tip portion of the external gear 54b as shown in FIG. That is obvious.

次に、上記のように構成されたバーチカル装置の実施例においての本発明に関わる角度調整機構５の作動を説明する。   Next, the operation of the angle adjusting mechanism 5 according to the present invention in the embodiment of the vertical apparatus configured as described above will be described.

操作ハンドル７を回転操作することによって、シャフト５２の第２軸部５２ａの中心軸は第１軸部５２ｂの周りを公転する。そして第２軸部５２ａ上に取付けられたピニオン５４は各第１と第２内歯歯車５７、６５と噛合いながら第２軸部５２ａ上で回転しつつ、第１軸部５２ｂの周りを公転する。これによって、操作ハンドル７を一回転させることで駆動アーム５１は固定ギヤメンバ５６に対して内歯歯車５７、６５の歯数差分、回転する。そして、駆動アーム５１および駆動アーム５１に連結シャフト４２によって連結されたアーム４６の各前端を軽い操作ハンドル７の操作力で上下に移動させることができる。ピン４４を介して係合されるシートクッション２の前端に荷重が作用している場合でも、シートクッション２の前端部は軽いハンドル７の操作力で上下移動ができるように作動する。   By rotating the operation handle 7, the central axis of the second shaft portion 52a of the shaft 52 revolves around the first shaft portion 52b. The pinion 54 mounted on the second shaft portion 52a revolves around the first shaft portion 52b while rotating on the second shaft portion 52a while meshing with the first and second internal gears 57 and 65. To do. Accordingly, by rotating the operation handle 7 once, the drive arm 51 rotates with respect to the fixed gear member 56 by the difference in the number of teeth of the internal gears 57 and 65. The front end of the arm 46 connected to the drive arm 51 and the drive arm 51 by the connection shaft 42 can be moved up and down by the operation force of the light operation handle 7. Even when a load is applied to the front end of the seat cushion 2 engaged via the pin 44, the front end portion of the seat cushion 2 operates so as to be able to move up and down by the operating force of the light handle 7.

本発明に関わる角度調整機構が適用されるシートバーチカル装置とリクライニング装置を備えるシートの斜視図である。It is a perspective view of a seat provided with a seat vertical device and a reclining device to which an angle adjustment mechanism concerning the present invention is applied. シートバーチカル装置の角度調整機構の分解斜視図である。It is a disassembled perspective view of the angle adjustment mechanism of a sheet vertical apparatus. 図１におけるＡ−Ａ断面図である。It is AA sectional drawing in FIG. 本発明に関わる角度調整機構のピニオンと第１及び第２内歯歯車の噛合い状態を示す平面図である。尚、噛合い状態が分かるように実線のみで示す。It is a top view which shows the meshing state of the pinion of the angle adjustment mechanism in connection with this invention, and a 1st and 2nd internal gear. In addition, it shows only with a continuous line so that a meshing state can be understood. 本発明に関わる角度調整機構のピニオンと第１内歯歯車の噛合い状態を示す平面図である。It is a top view which shows the meshing state of the pinion and 1st internal gear of the angle adjustment mechanism concerning this invention. 本発明に関わる角度調整機構のピニオンと第２内歯歯車の噛合い状態を示す平面図である。It is a top view which shows the meshing state of the pinion of the angle adjustment mechanism in connection with this invention, and a 2nd internal gear. トロコイド及びサイクロイド曲線の作図法の説明図である。It is explanatory drawing of the construction method of a trochoid and a cycloid curve. 本発明に採用した第１及び第２内歯歯車の歯形の基になるトロコイド曲線と、その固定円及び回転円の説明図である。It is explanatory drawing of the trochoid curve used as the basis of the tooth profile of the 1st and 2nd internal gear employ | adopted for this invention, its fixed circle, and a rotation circle. 本発明の構成のピニオンに採用した円形状歯形を示す平面図である。It is a top view which shows the circular tooth profile employ | adopted as the pinion of the structure of this invention. 本発明の構成の第１内歯歯車に採用したトロコイド歯形を示す平面図である。It is a top view which shows the trochoid tooth profile employ | adopted as the 1st internal gear of the structure of this invention. 本発明の構成の第２内歯歯車に採用したトロコイド歯形を示す平面図である。It is a top view which shows the trochoid tooth profile employ | adopted as the 2nd internal gear of the structure of this invention. 従来の角度調整機構に採用されたインボリュート歯形のピニオンと第１内歯歯車の噛合い状態を示す平面図である。It is a top view which shows the meshing state of the pinion of the involute tooth profile employ | adopted as the conventional angle adjustment mechanism, and the 1st internal gear. 従来の角度調整機構に採用されたインボリュート歯形のピニオンと第２内歯歯車の噛合い状態を示す平面図である。It is a top view which shows the meshing state of the pinion of the involute tooth shape employ | adopted as the conventional angle adjustment mechanism, and the 2nd internal gear.

符号の説明Explanation of symbols

１０ シート
２２、２４ 固定円
２３、２５ 回転円
５１ 可動部（駆動アーム）
５４ ピニオン
５４ｂ 外歯歯車部
５６ 固定部（固定ギヤメンバ）
５７ 第１内歯歯車部
６５ 第２内歯歯車部
10 Sheet 22, 24 Fixed circle 23, 25 Rotating circle 51 Movable part (drive arm)
54 pinion 54b external gear 56 fixed part (fixed gear member)
57 1st internal gear part 65 2nd internal gear part

Claims (3)

車両用シートの乗員の着座姿勢を調整可能とするためにシートの可動側に固定され、第１内歯歯車部を備える可動部と、
前記可動部を回転自在に支持し第１内歯歯車部と同中心に配置され第１内歯歯車部とは少なくとも歯数が1つ異なる第２内歯歯車部を備える固定部と、
前記第１内歯歯車部と前記第２内歯歯車部に噛合う外歯歯車部を有するピニオンを備える角度調整機構において、
前記外歯歯車部の歯形を円形状歯形とし、前記第１内歯歯車部の歯形をトロコイドまたはサイクロイド歯形で、前記第２内歯歯車部の歯形を前記第１内歯歯車部とは同位置の基点で且つ前記第１内歯歯車部の固定円より径を大とする固定円を基に形成されたトロコイドまたはサイクロイド歯形としたことを特徴とする角度調整機構。 A movable part that is fixed to the movable side of the seat to enable adjustment of the seating posture of the occupant of the vehicle seat and includes a first internal gear part;
A fixed portion including a second internal gear portion that rotatably supports the movable portion and is arranged at the same center as the first internal gear portion and has a number of teeth different from that of the first internal gear portion;
In the angle adjustment mechanism including a pinion having an external gear portion meshing with the first internal gear portion and the second internal gear portion,
The tooth form of the external gear part is a circular tooth form, the tooth form of the first internal gear part is a trochoid or cycloid tooth form, and the tooth form of the second internal gear part is the same position as the first internal gear part. An angle adjustment mechanism characterized by a trochoid or cycloid tooth profile formed on the basis of a fixed circle having a diameter larger than the fixed circle of the first internal gear portion. 前記第１と前記第２内歯歯車部の前記トロコイドまたはサイクロイド歯形は、少なくとも前記円形状歯形と噛合いする範囲において、各前記トロコイドまたはサイクロイド歯形を形成するために定められる所定のトロコイドまたはサイクロイド曲線より一定間隔離れて歯面が形成されていることを特徴とする請求項１に記載の角度調整機構。 The trochoid or cycloid tooth profile of the first and second internal gear portions is a predetermined trochoid or cycloid curve defined to form each trochoid or cycloid tooth profile at least in the range of meshing with the circular tooth profile. 2. The angle adjusting mechanism according to claim 1, wherein the tooth surfaces are formed at a predetermined distance apart. 前記外歯歯車部の歯先部と少なくとも前記第１内歯歯車部及び前記第２内歯歯車部のいずれか一方の歯底部分との間には間隙が設けたことを特徴とする請求項１に記載の角度調整機構。 2. A gap is provided between a tooth tip portion of the external gear portion and at least one tooth bottom portion of the first internal gear portion and the second internal gear portion. The angle adjustment mechanism according to 1.
JP2004040359A 2003-09-10 2004-02-17 Angle adjustment mechanism Expired - Fee Related JP4107249B2 (en)

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JP2004040359A JP4107249B2 (en) 2004-02-17 2004-02-17 Angle adjustment mechanism
TW093123244A TWI249482B (en) 2003-09-10 2004-08-03 Angular position adjusting mechanism
PCT/JP2004/013489 WO2005025930A2 (en) 2003-09-10 2004-09-09 Angular position adjusting mechanism
US10/571,259 US7611436B2 (en) 2003-09-10 2004-09-09 Angular position adjusting mechanism
EP04773148A EP1663702B1 (en) 2003-09-10 2004-09-09 Angular position adjusting mechanism
KR1020067004993A KR100852966B1 (en) 2003-09-10 2004-09-09 Angular position adjusting mechanism
DE602004023862T DE602004023862D1 (en) 2003-09-10 2004-09-09 WINKELPOSITIONSEINSTELLMECHANISMUS
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Publication number Priority date Publication date Assignee Title
CN110811197A (en) * 2019-11-20 2020-02-21 重庆延锋安道拓汽车部件***有限公司 Office chair inclination angle adjusting mechanism
CN110811197B (en) * 2019-11-20 2024-04-19 安道拓(重庆)汽车部件有限公司 Office chair inclination angle adjusting mechanism

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