JP2005230116A - Angular position adjustment mechanism - Google Patents

Angular position adjustment mechanism Download PDF

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Publication number
JP2005230116A
JP2005230116A JP2004040358A JP2004040358A JP2005230116A JP 2005230116 A JP2005230116 A JP 2005230116A JP 2004040358 A JP2004040358 A JP 2004040358A JP 2004040358 A JP2004040358 A JP 2004040358A JP 2005230116 A JP2005230116 A JP 2005230116A
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tooth
gear
internal gear
external gear
angular position
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JP2004040358A
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JP4029847B2 (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 JP2004040358A priority Critical patent/JP4029847B2/en
Priority to TW093123244A priority patent/TWI249482B/en
Priority to US10/571,259 priority patent/US7611436B2/en
Priority to PCT/JP2004/013489 priority patent/WO2005025930A2/en
Priority to KR1020067004993A priority patent/KR100852966B1/en
Priority to EP09169250A priority patent/EP2116413B1/en
Priority to EP04773148A priority patent/EP1663702B1/en
Priority to DE602004023862T priority patent/DE602004023862D1/en
Publication of JP2005230116A publication Critical patent/JP2005230116A/en
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Publication of JP4029847B2 publication Critical patent/JP4029847B2/en
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Abstract

<P>PROBLEM TO BE SOLVED: To obtain an angular position adjustment mechanism using an internal tooth gear having a tooth shape capable of securing a meshing strength and an external tooth gear. <P>SOLUTION: The shapes of the tools of the internal tooth gear 31 and the external tooth gear 21 are formed on the basis of the loop shapes 74a and 84a of prescribed trochoid curves 74 and 84. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、車両用シートのシートバック角度位置または、シートクッションの高さ位置を無段階に調整する機構等に採用され、特にその角度位置の保持状態で強度を必要とする角度位置調整機構に関する。   The present invention is employed in a mechanism for steplessly adjusting a seat back angular position of a vehicle seat or a height position of a seat cushion, and particularly relates to an angular position adjusting mechanism that requires strength in a state where the angular position is held. .

このような無段階に位置を調整可能とする角度位置調整機構は、図７に示されるように、１方のブラケットに内歯歯車２３１を形成し、また別のブラケットには外歯歯車２２１を形成して、内歯歯車２３１と外歯歯車２２１を噛合わせ、且つ相互に回転可能に組み合わせることによってブラケット間の角度位置を調整可能とし、またその位置を強固に保持できるように構成されている。   As shown in FIG. 7, the angular position adjusting mechanism that can adjust the position steplessly includes an internal gear 231 formed in one bracket and an external gear 221 formed in another bracket. By forming and meshing the internal gear 231 and the external gear 221 and combining them so that they can rotate with each other, the angular position between the brackets can be adjusted, and the position can be firmly held. .

これらの歯車に採用されている歯形は、図３に示されるように、例えば固定円７１と、固定円７１に内接して転がる回転円８０を設定して、回転円８０の円周上の基点２７１が描く軌跡であるサイクロイド曲線２７４に基づいて形成されている。即ち、外歯歯車２２１の形状を図７に示される基点２７１の位置を中心とする円弧形状歯形にして、また内歯歯車２３１の歯形を所定のサイクロイド曲線２７４からの等距離ａの位置に形成される歯面２７５を備えるように形成している。(例えば、特許文献１参照。)。   As shown in FIG. 3, the tooth profile adopted for these gears is, for example, a fixed circle 71 and a rotation circle 80 which is inscribed in the fixed circle 71 and set to rotate, and a base point on the circumference of the rotation circle 80. It is formed based on a cycloid curve 274 that is a trajectory drawn by 271. That is, the shape of the external gear 221 is an arc-shaped tooth profile centered on the position of the base point 271 shown in FIG. 7, and the tooth profile of the internal gear 231 is formed at a position a equidistant from the predetermined cycloid curve 274. The tooth surface 275 is formed. (For example, see Patent Document 1).

尚、後述するように、上記と同様に固定円７１と回転円８０の関係で、基点を回転円８０の円周上以外に設定した場合に、基点の描く軌跡はトロコイド曲線と呼ばれ、上記のサイクロイド曲線と区別される。
特開昭５５−６８３２８号公報 As will be described later, when the base point is set to a position other than the circumference of the rotation circle 80 in the relationship between the fixed circle 71 and the rotation circle 80 as described above, the locus drawn by the base point is called a trochoid curve. It is distinguished from the cycloid curve.
JP-A-55-68328

上記した従来技術のように、円弧形状歯形の外歯歯車２２１と、サイクロイド曲線に基づいて形成された歯形を有する内歯歯車２３１との噛合いでは、多くの噛合い点Ｍで内歯と外歯は当接し、大きな噛合い率が得られる。しかし、各歯が当接する噛合い点Ｍで外歯歯車の回転方向に直角な面ｅ（図７）に対して歯面ｆの傾きｄ（図７）が、大きくなり、歯に大きな荷重が作用し易くなる。このために噛合い強度を確保する上では不利となっている。   As in the prior art described above, when the external gear 221 having an arcuate tooth profile and the internal gear 231 having a tooth profile formed based on a cycloid curve are engaged, the internal teeth and the external gears are engaged at many mesh points M. The teeth abut and a large meshing rate is obtained. However, the inclination d (FIG. 7) of the tooth surface f becomes large with respect to the surface e (FIG. 7) perpendicular to the rotation direction of the external gear at the meshing point M where each tooth contacts, and a large load is applied to the teeth. It becomes easy to act. For this reason, it is disadvantageous in securing the meshing strength.

故に、本発明は、このような問題を解決し、より噛合い強度を確保することが出来る歯形状を備える内歯歯車と外歯歯車を用いた角度位置調整機構を得ることを、その技術的課題とする。   Therefore, the technical point of the present invention is to solve such a problem and to obtain an angular position adjusting mechanism using an internal gear and an external gear having a tooth shape capable of ensuring a higher meshing strength. Let it be an issue.

上記した課題を解決するために、本発明で講じた技術的な第１の手段は、車両シートの一方側の部材に固定される固定ブラケットと、前記シートの他方側の部材に固定される回転ブラケットと、前記固定ブラケットに回転支持されるシャフトと、前記固定ブラケットに形成された内歯歯車と、前記回転ブラケットに前記内歯歯車より少なくとも１つ以上歯数の少ない外歯歯車を形成して、前記シャフトの回転によって前記外歯歯車の中心を前記内歯歯車の中心周りに公転させて、前記シートの一方側の部材と前記他方側の部材の角度位置を調整可能とする角度位置調整機構において、
前記内歯歯車及び前記外歯歯車の歯の形状を所定のトロコイド曲線のループ形状に基づき形成したことである。 In order to solve the above-described problem, the first technical means taken in the present invention includes a fixing bracket fixed to a member on one side of a vehicle seat and a rotation fixed to a member on the other side of the seat. A bracket, a shaft rotatably supported by the fixed bracket, an internal gear formed on the fixed bracket, and an external gear having at least one or fewer teeth than the internal gear formed on the rotary bracket; An angular position adjusting mechanism that adjusts the angular position of the one side member and the other side member of the seat by revolving the center of the external gear around the center of the internal gear by the rotation of the shaft. In
The tooth shapes of the internal gear and the external gear are formed based on a loop shape of a predetermined trochoid curve.

また、本発明で講じた技術的な第２の手段は、第１の手段において前記内歯歯車及び前記外歯歯車の歯の形状は前記所定のトロコイド曲線のループ形状から一定距離離れて歯面が形成したことである。   Further, the second technical means taken in the present invention is that, in the first means, the tooth shapes of the internal gear and the external gear are separated from the loop shape of the predetermined trochoid curve by a certain distance. Is formed.

また、本発明で講じた技術的な第３の手段は、第１の手段において前記内歯歯車及び前記外歯歯車の歯の形状は前記所定のトロコイド曲線のループ形状から一定角度回転方向に離れて歯面が形成したことである。   Further, the third technical means taken in the present invention is that, in the first means, the tooth shapes of the internal gear and the external gear are separated from the loop shape of the predetermined trochoid curve in a rotation direction at a constant angle. The tooth surface was formed.

更に、本発明で講じた技術的な第４の手段は、第１又は第２の手段において前記内歯歯車及び前記外歯歯車の歯の噛合い状態で、前記内歯歯車の歯底と前記外歯歯車の歯先間に間隙を形成するために、少なくとも前記内歯歯車及び前記外歯歯車のいずれかの歯面に前記トロコイド曲線に基づかないで形成された逃がし歯面部を有するようにしたことである。   Further, a fourth technical means taken in the present invention is the first or second means in the meshing state of the teeth of the internal gear and the external gear, and the tooth bottom of the internal gear and the In order to form a gap between the tooth tips of the external gear, at least one tooth surface of the internal gear and the external gear has a relief tooth surface portion that is formed based on the trochoid curve. That is.

請求項１に記載の発明によれば、トロコイド曲線に基く歯形であるために内歯歯車と外歯歯車の噛合い範囲において大きい噛合い率が得られると共に、特にループ形状を用いているために各歯の当接する噛合い点での歯面の傾きが、外歯歯車の回転方向に直角な面に対して小さくすることができ、歯の強度を高くする効果が得られる。   According to the first aspect of the present invention, since the tooth profile is based on the trochoidal curve, a large meshing ratio is obtained in the meshing range of the internal gear and the external gear, and in particular, the loop shape is used. The inclination of the tooth surface at the meshing point where each tooth abuts can be reduced with respect to the surface perpendicular to the rotation direction of the external gear, and the effect of increasing the tooth strength can be obtained.

又、請求項１に記載の発明に加えて請求項２又は請求項３に記載の発明によれば、内歯歯車および外歯歯車のトロコイド曲線を適用した歯形は、これらを形成するプレス加工型は、数値制御工作機械を用いることで高精度の形状に仕上げることができ、その結果各歯車の歯形状を精度良く形成できる。また歯形の設計で必要強度の確保が容易である。   According to the invention of claim 2 or claim 3 in addition to the invention of claim 1, the tooth profile to which the trochoidal curves of the internal gear and the external gear are applied is a press working mold that forms them. Can be finished into a highly accurate shape by using a numerically controlled machine tool, and as a result, the tooth shape of each gear can be accurately formed. In addition, it is easy to ensure the required strength by designing the tooth profile.

更に、請求項２又は請求項３に加えて、請求項４の記載の発明によれば、外歯歯車の歯先と内歯歯車の歯底には、間隙が形成され潤滑グリースが溜まる空間となり、歯車の耐久性が確保し易くなる。   Furthermore, according to the invention of claim 4 in addition to claim 2 or claim 3, a gap is formed between the tooth tip of the external gear and the tooth bottom of the internal gear to form a space in which lubricating grease accumulates. This makes it easy to ensure the durability of the gear.

以下、図１〜図４及び図６を用いて、本発明に関る第１の実施例の角度位置調整機構５について説明する。   Hereinafter, the angular position adjusting mechanism 5 according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 4 and 6.

先ず、図６に示すように、角度位置調整機構５は、例えばシート１０のシートバック１１の背凭れ角度を調整するリクライニング装置５０、またはシートクッション１２の高さ調整を行うバーチカル装置６０等に適応できるものである。即ち、リクライニング装置５０では、角度位置調整機構５をシートバック１１のフレーム１１aとシートクッション１２のフレーム１２a間に取り付け、操作ハンドル４７を回転することによって、シートバック１１の傾斜角度を任意に調整できる構成となる。また、操作ハンドル４７を操作していないときはシートバック１１の位置を保持するため規定の強度を確保して、乗員を支持することができる。同様に、バーチカル装置６０の場合、角度位置調整機構５はシートクッション１２のフレーム１２ａの前方端部に取り付けられ、リンク機構９を介してシートスライド１４に連結される。そして、操作ハンドル４７を回転することによって、フレーム１２ａの後端部とシートスライド１４を連結するピボット軸１５の周りにシートクッション１２を回転させて、シートクッション１２の高さを任意に調整できる構成となる。この場合も、操作ハンドル４７を操作してないときは乗員の体重を支え、高さを保持する。このように角度位置調整機構５は、位置の調整機能とともに、強固に位置を保持できる機能を備えるものである。   First, as shown in FIG. 6, the angular position adjustment mechanism 5 is adapted to, for example, a reclining device 50 that adjusts the backrest angle of the seat back 11 of the seat 10, or a vertical device 60 that adjusts the height of the seat cushion 12. It can be done. That is, in the reclining device 50, the angle position adjusting mechanism 5 is attached between the frame 11a of the seat back 11 and the frame 12a of the seat cushion 12, and the operation handle 47 is rotated, whereby the inclination angle of the seat back 11 can be arbitrarily adjusted. It becomes composition. Further, when the operation handle 47 is not operated, the position of the seat back 11 is maintained, so that a prescribed strength can be secured and the occupant can be supported. Similarly, in the case of the vertical device 60, the angular position adjusting mechanism 5 is attached to the front end portion of the frame 12 a of the seat cushion 12 and is connected to the seat slide 14 via the link mechanism 9. Then, by rotating the operation handle 47, the seat cushion 12 is rotated around the pivot shaft 15 that connects the rear end portion of the frame 12a and the seat slide 14, and the height of the seat cushion 12 can be arbitrarily adjusted. It becomes. Also in this case, when the operation handle 47 is not operated, the weight of the passenger is supported and the height is maintained. As described above, the angular position adjusting mechanism 5 has a function of holding the position firmly together with a function of adjusting the position.

次に、角度位置調整機構５の構成を、図１と図２に基づいて説明する。   Next, the configuration of the angular position adjusting mechanism 5 will be described with reference to FIGS.

本発明に関する角度位置調整機構５の基本構成は、互いに偏心する内歯歯車と外歯歯車を組み合わせて構成された公知の調整機構と同様のものである。即ち、角度位置調整機構５は、上記したシートリクライニング装置５０への適用例では、シートクッション１２のフレーム１２ａに固定して取り付けられる固定ブラケット３と、この固定ブラケット３に対して回転可能に支持され、シートバック１１のレーム１１ａに固定して取り付けられる回転ブラケット２を備えている。固定ブラケット３には内歯歯車３１が形成され、回転ブラケット２には外歯歯車２１が形成されている。内歯歯車３１に対して外歯歯車２１はその歯数が少なくとも１つ少なく設定され、互いに噛合い係合している。ちなみに、図１に示される実施例では、内歯歯車３１の歯数は３４で外歯歯車２１の歯数は３３に設定されている。   The basic configuration of the angular position adjusting mechanism 5 according to the present invention is the same as a known adjusting mechanism configured by combining an internal gear and an external gear that are eccentric to each other. That is, in the application example to the seat reclining device 50 described above, the angular position adjusting mechanism 5 is supported by the fixed bracket 3 fixedly attached to the frame 12a of the seat cushion 12 and the fixed bracket 3 so as to be rotatable. The rotary bracket 2 is fixedly attached to the frame 11 a of the seat back 11. An internal gear 31 is formed on the fixed bracket 3, and an external gear 21 is formed on the rotary bracket 2. The number of teeth of the external gear 21 is set to be at least one smaller than that of the internal gear 31, and meshingly engage with each other. Incidentally, in the embodiment shown in FIG. 1, the number of teeth of the internal gear 31 is set to 34 and the number of teeth of the external gear 21 is set to 33.

内歯歯車３１の中心部分には、円筒形状のカラー部３ａが、内歯歯車３１の中心軸３１ａの軸方向に沿って突起して形成されている。また、カラー部３ａの内径にシャフト４３が貫通して配置され、シャフト４３にはシート１０の反対側面に装着される、角度調整機構（図示せず）と連動させるための連動部材４６が連結される。   A cylindrical collar portion 3 a is formed at the central portion of the internal gear 31 so as to protrude along the axial direction of the central shaft 31 a of the internal gear 31. In addition, a shaft 43 is disposed through the inner diameter of the collar portion 3a, and an interlocking member 46 is connected to the shaft 43 to be interlocked with an angle adjusting mechanism (not shown) mounted on the opposite side surface of the seat 10. The

回転ブラケット２に形成された外歯歯車２１の中心部分には、穴２aが形成されている。穴２aの内径には内径面部２ｂを備える軸受け部材が圧入して取り付けられている。内径面部２ｂは外歯歯車２１の中心２１ａと同心で、その径はカラー部３ａの外径より大きく設定されている。   A hole 2 a is formed in the center portion of the external gear 21 formed in the rotating bracket 2. A bearing member having an inner diameter surface portion 2b is press-fitted and attached to the inner diameter of the hole 2a. The inner diameter surface portion 2b is concentric with the center 21a of the external gear 21, and its diameter is set larger than the outer diameter of the collar portion 3a.

次に、内歯歯車３１と外歯歯車２１との間に配置されるバックラッシュ調整機構４について説明する。   Next, the backlash adjusting mechanism 4 disposed between the internal gear 31 and the external gear 21 will be described.

バックラッシュ調整機構４は、内径面部２ｂとカラー部３ａの外径との間の隙間に配置された１対のくさび部材４１を備えている。くさび部材４１は、図１に示される状態の位置で、上方部分の厚みが下方部分の厚みより厚く、また厚みが上方から下方に行くに従い減少する形状となっている。１対のくさび部材４１同士は、図１に示されるように上端と下端の部分で、互いに間隔を持つようにしてカラー部３ａの外径上に配置されている。そして、ばね部材４２がくさび部材４１の上端間の間隔を広げる方向に作用力を及ぼすように取り付けられている。更に図１に示されるように、ばね部材４２の作用力が作用することで、くさび部材４１は、カラー部３ａの下側に回り込み、カラー部３ａに対して、内径面部２ｂを図１の上方に持ち上げるように作用する構成になっている。このように、内径面部２ｂが上方に持ち上げられる結果、外歯歯車２１の中心２１ａは、内歯歯車３１の中心３１ａに対して、より偏心量を大きくする。そして、外歯歯車２１の歯と内歯歯車３１の歯との間に隙間、即ちバックラッシュを無くなるように互いに押し付けられる構成となっている。   The backlash adjusting mechanism 4 includes a pair of wedge members 41 disposed in a gap between the inner diameter surface portion 2b and the outer diameter of the collar portion 3a. In the position shown in FIG. 1, the wedge member 41 has a shape in which the thickness of the upper portion is thicker than the thickness of the lower portion, and the thickness decreases from the upper side to the lower side. As shown in FIG. 1, the pair of wedge members 41 are arranged on the outer diameter of the collar portion 3a so as to be spaced apart from each other at the upper end portion and the lower end portion. The spring member 42 is attached so as to exert an acting force in a direction that widens the interval between the upper ends of the wedge members 41. Further, as shown in FIG. 1, when the acting force of the spring member 42 acts, the wedge member 41 wraps around to the lower side of the collar portion 3a, and the inner diameter surface portion 2b is set to the upper portion of FIG. It is the structure which acts so that it may lift. As described above, as a result of the inner diameter surface portion 2 b being lifted upward, the center 21 a of the external gear 21 is more eccentric than the center 31 a of the internal gear 31. And it is the structure mutually pressed so that a clearance gap, ie, a backlash, may be eliminated between the teeth of the external gear 21 and the teeth of the internal gear 31.

更に、バックラッシュ調整機構４は、シャフト４３の回転中心から離間してシャフト４３と１体的に形成された爪部４４を備えている。爪部４４の先端はシャフト４３の回転中心軸と平行に伸び、１対のくさび部材４１の下端間に挿入される。シャフト４３は、更にその一端部が角度位置調整機構５の側方側に突出するように伸び、その先端に操作ハンドル４７が固定して取り付けられている。   Further, the backlash adjusting mechanism 4 includes a claw portion 44 that is separated from the rotation center of the shaft 43 and formed integrally with the shaft 43. The tip of the claw portion 44 extends in parallel with the rotation center axis of the shaft 43 and is inserted between the lower ends of the pair of wedge members 41. The shaft 43 further extends so that one end thereof protrudes to the side of the angular position adjusting mechanism 5, and an operation handle 47 is fixedly attached to the tip of the shaft 43.

操作ハンドル４７を回転させるように操作することによって、爪部４４をくさび部材４１の一方側の下端部に当接させ、くさび部材４１をばね部材４２の作用力に抗して持ち上げると、外歯歯車２１の中心２１ａと内歯歯車３１の中心３１ａの距離が少なくなる。この結果、両歯車の噛合いが緩みバックラッシュは大きくなる。バックラッシュは大きくなることによって、両歯車は少ない噛合い抵抗で回転が可能となる。   When the operation handle 47 is operated to rotate, the claw portion 44 is brought into contact with the lower end portion on one side of the wedge member 41, and the wedge member 41 is lifted against the acting force of the spring member 42. The distance between the center 21a of the gear 21 and the center 31a of the internal gear 31 is reduced. As a result, the meshing of both gears is loosened and the backlash is increased. By increasing the backlash, both gears can rotate with little meshing resistance.

更に、操作ハンドル４７の回転操作を続けると、外歯歯車２１の中心２１ａは内歯歯車３１の中心３１ａの周りを公転し、一対のくさび部材４１の位置は図１の位置から回転し、これにともなって外歯歯車２１と内歯歯車３１の噛合い位置も順に回転する。操作ハンドル４７が１回転することで、歯車の１ピッチの角度に相当する角度、固定ブラケット３に対して回転ブラケット２の位置が回転する。これによって、固定ブラケット３と回転ブラケット２の角度位置を調整できる構成となっている。   When the operation handle 47 continues to rotate, the center 21a of the external gear 21 revolves around the center 31a of the internal gear 31, and the position of the pair of wedge members 41 rotates from the position shown in FIG. Accordingly, the meshing position of the external gear 21 and the internal gear 31 also rotates in order. By rotating the operation handle 47 once, the position of the rotary bracket 2 rotates with respect to the fixed bracket 3 by an angle corresponding to the angle of one pitch of the gear. Thus, the angular position of the fixed bracket 3 and the rotating bracket 2 can be adjusted.

次に、上記角度調整機構５に備えられ、トロコイド曲線を用いて形成された内歯歯車３１と外歯歯車２１の歯の形状について図３及び図４を用いて説明する。   Next, the shapes of the teeth of the internal gear 31 and the external gear 21 that are provided in the angle adjusting mechanism 5 and are formed using the trochoidal curve will be described with reference to FIGS. 3 and 4.

先ず、図３に示すように、第１の固定円７１に対して、転がるように内接する回転円８０を設定し、回転円８０の内部に基点７０を設定したとき、基点７０の描く軌跡は第１のトロコイド曲線７４となる。そして、第１のトロコイド曲線７４は、ループ形状７４ａを有する。更に、第１の固定円７１の内側に接するように設定された第２の固定円８１に対して、回転円８０を内接して転がしたときは基点７０はトロコイド曲線８４を描き、このトロコイド曲線８４は同様にループ形状８４ａを有する。   First, as shown in FIG. 3, when a rotation circle 80 that is inscribed so as to roll is set for the first fixed circle 71 and a base point 70 is set inside the rotation circle 80, the locus drawn by the base point 70 is The first trochoid curve 74 is obtained. The first trochoid curve 74 has a loop shape 74a. Further, when the second fixed circle 81 set to be in contact with the inside of the first fixed circle 71 is rolled while inscribed in the rotation circle 80, the base point 70 draws a trochoid curve 84, and this trochoid curve Similarly, 84 has a loop shape 84a.

そして、図４に示されるように、内歯歯車３１と外歯歯車２１の歯形は、夫々ループ形状７４ａ、８４ａを基に形成される。即ち、内歯歯車３１の歯面はループ形状７４ａに対して一定距離ａ離れて、また外歯歯車２１の歯面もループ形状８４ａに対して一定距離ａ離れて設定されている。このように形成される内歯歯車３１と外歯歯車２１の歯面は、図４に示されるように複数の噛合い点Ｍで互いに当接して噛合う。また、各噛合い点Ｍを結ぶ噛合い線Ｌは内歯歯車３１の内周及び外歯歯車２１の外周方向に概略沿うように湾曲して伸びる。その結果、例えばインボリュート曲線によって形成される一般的な内歯と外歯歯車では噛合い線が直線となるのに対して、より多くの噛合い点Ｍが得られ、１回転で生じる噛合い点の数を平均した噛合い率は大きくなる。この結果、強度の高い噛合いが実現できる。   As shown in FIG. 4, the tooth shapes of the internal gear 31 and the external gear 21 are formed based on the loop shapes 74a and 84a, respectively. That is, the tooth surface of the internal gear 31 is set a certain distance a away from the loop shape 74a, and the tooth surface of the external gear 21 is also set a certain distance a away from the loop shape 84a. The tooth surfaces of the internal gear 31 and the external gear 21 formed in this manner are in contact with each other at a plurality of meshing points M as shown in FIG. The mesh line L connecting the mesh points M is curved and extends so as to be substantially along the inner circumference of the internal gear 31 and the outer circumference direction of the external gear 21. As a result, for example, in a general internal gear and an external gear formed by an involute curve, the meshing line becomes a straight line, whereas more meshing points M are obtained and meshing points generated in one rotation. The meshing rate, which is the average of the numbers, increases. As a result, high-strength engagement can be realized.

更に外歯歯車２１では、先端部分をループ形状８４ａに対して一定距離ａの位置から距離ｂを削除し平坦となる歯先部２２を設けている。この形状によって、内歯歯車３１に対して外歯歯車２１が最も深く噛合う上死点位置Ｄ（図４の右側に示される位置）においても、外歯歯車２１の歯先部２２と内歯歯車３１の間には間隙が維持され、潤滑となるグリースが溜まり、円滑な作動と耐久性が確保される構成となっている。   Further, the external gear 21 is provided with a tooth tip portion 22 which is flattened by removing the distance b from the position of the constant distance a with respect to the loop shape 84a. With this shape, even at the top dead center position D (the position shown on the right side of FIG. 4) where the external gear 21 is most deeply engaged with the internal gear 31, the tooth tip 22 and the internal teeth of the external gear 21. A gap is maintained between the gears 31, grease to be lubricated is collected, and smooth operation and durability are ensured.

図4に更に示されるように、外歯歯車２１は、夫々所定の歯の高さに設定され、歯先部２２と歯の側面２３の境界となる角部には曲面Ｒ１、歯底部にはＲ３の曲面が施されている。一方、内歯歯車３１は、その歯先部３２の角部には曲面Ｒ２が施されて、外歯歯車２１との噛合い回転で歯が互いに干渉を生じさせない形状にしている。これら歯形の各曲面Ｒ１，Ｒ２および歯先部２２のようにトロコイド曲線には基づかずに、歯の当接に関与する側面２３、３３から当接しない側に逃げるようにした形成された歯面部分（逃がし歯面部）を備えることによって、噛合いの上死点の位置Ｄ（図４）で外歯歯車２１は噛合いの当接は生じないように設定されている。そして、噛合い点Ｍはこの上死点位置Ｄの左右側に分散して配置されるようになる。このような構成に形成された歯車では、各歯型に形状の誤差が生じていても、上死点位置Ｄの位置の歯に荷重が集中することなく複数の噛合い点Ｍで多くの歯に荷重は分散される。   As further shown in FIG. 4, the external gear 21 is set to a predetermined tooth height, and a curved surface R1 is provided at a corner portion which is a boundary between the tooth tip portion 22 and the tooth side surface 23, and a tooth bottom portion is provided. The curved surface of R3 is given. On the other hand, the internal gear 31 has a curved surface R <b> 2 at the corner of the tooth tip 32, so that the teeth do not interfere with each other by meshing rotation with the external gear 21. The tooth surfaces formed so as to escape from the side surfaces 23 and 33 involved in the tooth contact to the non-contact side without being based on the trochoid curve like the curved surfaces R1 and R2 and the tooth tip portion 22 of these tooth shapes. By providing the portion (the relief tooth surface portion), the external gear 21 is set so that the meshing contact does not occur at the top dead center position D (FIG. 4). The meshing points M are distributed and arranged on the left and right sides of the top dead center position D. In the gear formed in such a configuration, even if a shape error has occurred in each tooth type, a large number of teeth at a plurality of meshing points M without load concentration on the teeth at the top dead center position D. The load is dispersed.

更にループ形状７４ａ、８４ａに基づいて形成された各歯は、外歯歯車２１では歯底に近づく程、又内歯歯車３１では歯先に行く程、外歯の側面２３と内歯の側面３３は径方向に向くように湾曲している。このため、図４の左側位置に示されるように、上死点の位置Ｄから離れた位置では、外歯歯車２１と内歯歯車３１は噛合い点Ｍでの歯車の歯面ｆが、外歯歯車の回転方向に直角な面ｅに対し傾きｄは小さくなる。このために回転方向の荷重に対する強度をより確保しやすくできる構成となっている。   Further, the teeth formed on the basis of the loop shapes 74a and 84a, the outer tooth side surface 23 and the inner tooth side surface 33, the closer to the tooth bottom in the external gear 21, and the closer to the tooth tip in the internal gear 31. Is curved to face in the radial direction. For this reason, as shown in the left side position of FIG. 4, at a position away from the top dead center position D, the external gear 21 and the internal gear 31 have the gear tooth surface f at the meshing point M, The inclination d becomes smaller with respect to the surface e perpendicular to the rotation direction of the toothed gear. For this reason, it becomes the structure which can ensure the intensity | strength with respect to the load of a rotation direction more easily.

尚上記の実施例では、内歯歯車３１と外歯歯車２１の歯形をループ形状７４ａ、８４ａから一定距離ａ離れて歯面を設定されているとしたが、ループ形状７４ａ、８４ａに対して各歯車の回転方向に所定の角度を左右に回転させた位置に、歯面を設定しても良い。   In the above-described embodiment, the tooth shapes of the internal gear 31 and the external gear 21 are set apart from the loop shapes 74a and 84a by a fixed distance a, but the tooth surfaces are set for the loop shapes 74a and 84a. The tooth surface may be set at a position where a predetermined angle is rotated left and right in the rotation direction of the gear.

以上述べたように、上記した内歯歯車３１と外歯歯車２１は夫々回転ブラケット２固定ブラケット３にプレス形成による半抜き形成法などで成形されるが、厳密に理論式で定義されるトロコイド曲線を適用することによって、数値制御による工作機械を用いれば成形型を精度良く作製できる。またこのような理論式によって、用途に応じた歯の強度を的確、且つ容易に設定することができる。   As described above, the internal gear 31 and the external gear 21 described above are formed on the rotary bracket 2 fixed bracket 3 by a half punching method by press forming or the like, but a trochoid curve defined strictly by a theoretical formula. By using a machine tool with a numerical control, a molding die can be produced with high accuracy. In addition, with such a theoretical formula, the tooth strength according to the application can be set accurately and easily.

次に図５に、本発明に関わる角度位置調整機構５に採用可能な歯形状の第２実施例を示す。図５に示される例では、最も小さい径の円を固定円１８０にして、固定円１８０の外周で回転円１７１、１８１の内周と接するようにしている。そして基点１７０が夫々の回転円１７１、１８１が転がることで描かれるトロコイド曲線１７４，１８４を得る。この場合、第１実施例のループ形状７４ａ、８４ａとは固定円と回転円の径方向に対して反対の方向にループする。トロコイド曲線１７４、１８４に基き得られた歯形を備える外歯歯車１２１と内歯歯車１３１も第１の実施例と同様に角度位置調整機構５に適用すれば作動可能である。   Next, FIG. 5 shows a second embodiment of a tooth shape that can be employed in the angular position adjusting mechanism 5 according to the present invention. In the example shown in FIG. 5, the circle with the smallest diameter is the fixed circle 180, and the outer periphery of the fixed circle 180 is in contact with the inner periphery of the rotating circles 171 and 181. Then, trochoid curves 174 and 184 drawn by the rotation of the rotation points 171 and 181 at the base point 170 are obtained. In this case, the loop shapes 74a and 84a of the first embodiment loop in a direction opposite to the radial direction of the fixed circle and the rotating circle. The external gear 121 and the internal gear 131 having tooth shapes obtained based on the trochoid curves 174 and 184 can be operated if applied to the angular position adjusting mechanism 5 as in the first embodiment.

本発明に関わる角度位置調整機構の平面図である。It is a top view of the angle position adjustment mechanism in connection with this invention. 図１のＨ−Ｈでの断面図である。It is sectional drawing in HH of FIG. トロコイド曲線とサイクロイド曲線の説明図である。It is explanatory drawing of a trochoid curve and a cycloid curve. 本発明の角度位置調整機構の適用されるトロコイド曲線に基づいた歯形を示す拡大図である。It is an enlarged view which shows the tooth profile based on the trochoid curve to which the angular position adjustment mechanism of this invention is applied. 本発明の第２実施例となる角度位置調整機構の適用されるトロコイド曲線に基づいた歯形を示す平面図である。It is a top view which shows the tooth profile based on the trochoid curve to which the angular position adjustment mechanism used as 2nd Example of this invention is applied. 本発明に関わる角度位置調整機構をシートのシートバックの背凭れ角度を調整装とクッションの高さ調整装置等に適応した場合を示す側面図である。FIG. 5 is a side view showing a case where the angular position adjustment mechanism according to the present invention is applied to an adjustment device for adjusting the backrest angle of a seat back of a seat, a height adjustment device for a cushion, and the like. 従来技術による角度位置調整機構のサイクロイド曲線に基づいた歯形を示す。The tooth profile based on the cycloid curve of the angular position adjustment mechanism by a prior art is shown.

符号の説明Explanation of symbols

２ 固定ブラケット
３ 回転ブラケット
１０ シート
２１ 外歯歯車
３１ 内歯歯車
４３ シャフト
Ｒ１，Ｒ２、２２ 逃がし歯面部
７４ トロコイド曲線（第１のトロコイド曲線）
７４ａ ループ形状
８４ トロコイド曲線（第２のトロコイド曲線）
８４ａ ループ形状 2 Fixed bracket 3 Rotating bracket 10 Seat 21 External gear 31 Internal gear 43 Shafts R1, R2, 22 Relief tooth surface 74 Trochoid curve (first trochoid curve)
74a Loop shape 84 Trochoid curve (second trochoid curve)
84a Loop shape

Claims (4)

車両シートの一方側の部材に固定される固定ブラケットと、
前記シートの他方側の部材に固定される回転ブラケットと、
前記固定ブラケットに回転支持されるシャフトと、
前記固定ブラケットに形成された内歯歯車と、
前記回転ブラケットに前記内歯歯車より少なくとも１つ以上歯数の少ない外歯歯車を形成して、前記シャフトの回転によって前記外歯歯車の中心を前記内歯歯車の中心周りに公転させて、前記シートの一方側の部材と前記他方側の部材の角度位置を調整可能とする角度位置調整機構において、
前記内歯歯車及び前記外歯歯車の歯の形状を所定のトロコイド曲線のループ形状に基づき形成したことを特徴とする角度位置調整機構。 A fixing bracket fixed to a member on one side of the vehicle seat;
A rotating bracket fixed to a member on the other side of the seat;
A shaft rotatably supported by the fixed bracket;
An internal gear formed on the fixed bracket;
Forming an external gear having at least one tooth number smaller than that of the internal gear on the rotary bracket, revolving the center of the external gear around the center of the internal gear by rotation of the shaft, In the angular position adjustment mechanism that enables adjustment of the angular position of the member on one side of the sheet and the member on the other side,
An angular position adjusting mechanism characterized in that the tooth shapes of the internal gear and the external gear are formed based on a loop shape of a predetermined trochoid curve. 前記内歯歯車及び前記外歯歯車の歯の形状は前記所定の前記トロコイド曲線の前記ループ形状から一定距離離れて歯面が形成したことを特徴とする請求項１に記載の角度位置調整機構。 2. The angular position adjusting mechanism according to claim 1, wherein tooth shapes of the internal gear and the external gear are formed at a predetermined distance from the loop shape of the predetermined trochoid curve. 前記内歯歯車及び前記外歯歯車の歯の形状は前記所定の前記トロコイド曲線の前記ループ形状から一定角度回転方向に離れて歯面が形成したことを特徴とする請求項１に記載の角度位置調整機構。   2. The angular position according to claim 1, wherein tooth shapes of the internal gear and the external gear are formed so that tooth surfaces are separated from the loop shape of the predetermined trochoid curve in a rotation direction at a predetermined angle. Adjustment mechanism. 前記内歯歯車及び前記外歯歯車の歯の噛合い状態で、前記内歯歯車の歯底と前記外歯歯車の歯先間に間隙を形成するために、少なくとも前記内歯歯車及び前記外歯歯車のいずれかの歯面に前記トロコイド曲線に基づかないで形成された逃がし歯面部を有すること特徴とする請求項１又は請求項２に記載の角度位置調整機構。 In order to form a gap between the tooth bottom of the internal gear and the tooth tip of the external gear in the meshed state of the teeth of the internal gear and the external gear, at least the internal gear and the external gear The angular position adjusting mechanism according to claim 1 or 2, further comprising a relief tooth surface portion formed on any tooth surface of the gear without being based on the trochoidal curve.
JP2004040358A 2003-09-10 2004-02-17 Angular position adjustment mechanism Expired - Fee Related JP4029847B2 (en)

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JPWO2008015845A1 (en) * 2006-07-31 2009-12-17 トヨタ紡織株式会社 Gear and coupling device using the gear
US8016356B2 (en) 2006-07-31 2011-09-13 Toyota Boshoku Kabushiki Kaisha Gears and coupling apparatus using the gears
JP4992901B2 (en) * 2006-07-31 2012-08-08 トヨタ紡織株式会社 Connecting device
WO2008152829A1 (en) * 2007-06-11 2008-12-18 Toyota Boshoku Kabushiki Kaisha Turning mechanism
US8460145B2 (en) 2007-06-11 2013-06-11 Toyota Boshoku Kabushiki Kaisha Rotation mechanism
JP5223863B2 (en) * 2007-06-11 2013-06-26 トヨタ紡織株式会社 Rotating mechanism
CN101629616B (en) * 2008-07-15 2012-03-21 丰田纺织株式会社 Gear assembly and connecting device
JP2013502938A (en) * 2009-08-28 2013-01-31 カイペル ゲーエムベーハー アンド カンパニー カーゲー Vehicle seat fitting
KR101743427B1 (en) 2009-08-28 2017-06-05 존슨 컨트롤즈 컴포넌츠 게엠베하 운트 코. 카게 Fitting for a vehicle seat
JP2018083579A (en) * 2016-11-25 2018-05-31 トヨタ紡織株式会社 Reduction gear
JP2021116844A (en) * 2020-01-24 2021-08-10 株式会社アイシン Gear and gear mechanism
JP7419835B2 (en) 2020-01-24 2024-01-23 株式会社アイシン Gears and gear mechanisms

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