JP2007198480A - Planetary gear type continuously variable transmission - Google Patents

Planetary gear type continuously variable transmission Download PDF

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JP2007198480A
JP2007198480A JP2006017006A JP2006017006A JP2007198480A JP 2007198480 A JP2007198480 A JP 2007198480A JP 2006017006 A JP2006017006 A JP 2006017006A JP 2006017006 A JP2006017006 A JP 2006017006A JP 2007198480 A JP2007198480 A JP 2007198480A
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gear
planetary gear
continuously variable
planetary
rotation axis
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JP4868861B2 (en
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Eiji Imaoka
英治 今岡
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission which continuously engages gears without a slippage. <P>SOLUTION: The continuously variable transmission is equipped with: an input shaft 1 and an output shaft 3 each rotatably arranged on a rotary axis o; a sun gear 2 for input fixed to the input shaft 1; a carrier member 4 fixed to the output shaft 3; turning shafts 5, 5 arranged movably in the axial direction of the carrier member 4 and apart by 180°; two input planetary gears 6A, 6A fixed to the turning shafts 5, 5, respectively, and engaging with the sun gear 2; and output planetary gears 6B, 6B engaging with an internal gear 8 formed within the range of 180°. The transmission is provided with a shift control device 10 having cam plates 9A, 9B arranged tiltably around a tilting axis Oh orthogonal to the rotary axis o for reciprocating each of the planetary gears 6A, 6B once in the axial direction in response to one turn of the planetary gears 6A, 6B with the rotary axis o as the center, and changing the gear ratio by tilting the cam plates 9A, 9B. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、はすば歯車を利用して動力を確実に伝達することができる遊星歯車式無段変速装置に関する。   The present invention relates to a planetary gear type continuously variable transmission that can transmit power reliably using a helical gear.

従来の無段変速機は、たとえば互いに平行な軸に、対称に配置された円錐ローラをそれぞれ設け、これら円錐ローラ間に伝動ベルトを巻張したベルト式や、入力軸に略円錐湾曲型の入力デスクを設けるとともに、出力軸に入力デスクに対向して略円錐湾曲型の出力ディスクを設け、入力デスクと出力ディスク間に、接線周りに傾動可能な伝動ローラを回転自在に配置したトロイダル式（特許文献１）であり、両方とも滑り摩擦を利用したものである。
特開２０００−１９３０７７ Conventional continuously variable transmissions, for example, are provided with conical rollers arranged symmetrically on mutually parallel axes, and a belt type in which a transmission belt is wound between these conical rollers, or a substantially conical curved input on the input shaft. A toroidal type with a desk, a substantially conical curved output disk on the output shaft facing the input desk, and a rotatable transmission roller that can tilt around the tangent between the input desk and the output disk (patented) Reference 1), both of which utilize sliding friction.
JP2000-193077

従来の無段変速機は、滑り摩擦式であるため、滑りなどによる損失があり、伝達トルクが大きくなると、滑りが生じやすくなる傾向がある。
本発明は、変速比の変更時であっても、歯車を連続的に噛み合わせることで、回転トルクの大きさに関係なく動力を確実に伝達することができ、滑りのない遊星歯車式無段変速装置を提供することを目的とする。 Since the conventional continuously variable transmission is a sliding friction type, there is a loss due to slipping or the like, and when the transmission torque increases, slipping tends to occur easily.
Even when the gear ratio is changed, the present invention can transmit the power reliably regardless of the magnitude of the rotational torque by continuously meshing the gears, and is a planetary gear type continuously variable without slipping. An object is to provide a transmission.

請求項１記載の発明は、回転軸心上に設けられた太陽歯車と、当該太陽歯車の外周部に一定間隔をあけて固定された内歯車と、回転軸心に周りに回転自在に支持されたキャリア部材に設けられて太陽歯車および内歯車にそれぞれ噛み合う遊星ギヤとを具備した遊星歯車式無段変速装置であって、太陽歯車、遊星歯車および内歯車をそれぞれ所定のねじれ角を有するはすば歯車により構成し、キャリア部材に、複数の旋回軸を軸心方向にスライド自在に設けるとともに、前記各旋回軸に軸心方向の移動が規制された遊星歯車をそれぞれ設け、内歯車を回転軸心周りに１８０°の範囲にのみ設け、前記旋回軸は、前記各遊星歯車の少なくとも１個が前記内歯車に噛み合う位置に配置され、回転軸心に直交しかつ内歯車の二等分線に平行な傾動軸周りに傾動自在なカム板と、当該カム板を傾動可能な直線駆動機構とを有し、前記カム板の傾斜姿勢で回転軸心を中心とする遊星歯車の１回の旋回に対して前記旋回軸を介して遊星歯車をそれぞれ軸心方向に１往復移動させる変速調整手段を設けたものである。   The invention according to claim 1 is supported by a sun gear provided on the rotation axis, an internal gear fixed to the outer peripheral portion of the sun gear at a predetermined interval, and a rotation axis around the rotation gear. A planetary gear type continuously variable transmission provided on the carrier member and meshing with the sun gear and the internal gear, respectively, wherein the sun gear, the planetary gear, and the internal gear each have a predetermined twist angle. The carrier member is provided with a plurality of swiveling shafts slidably in the axial direction, and each swiveling shaft is provided with a planetary gear whose movement in the axial direction is restricted, and the internal gear is a rotating shaft. Provided only in the range of 180 ° around the center, the swivel shaft is disposed at a position where at least one of the planetary gears meshes with the internal gear, and is perpendicular to the rotational axis and is bisected by the internal gear. Parallel tilt axis circumference And a linear drive mechanism capable of tilting the cam plate, and the swivel shaft with respect to one turn of the planetary gear centering on the rotation axis in the tilted posture of the cam plate. Is provided with shift adjusting means for moving the planetary gears one reciprocally in the axial direction.

請求項２記載の発明は、請求項１記載の構成において、旋回軸の両端部に当接部をそれぞれ形成し、前記当接部がそれぞれ当接するカム板を、旋回軸の両側に配置し、前記両カム板を平行リンク機構を介して連結連動し傾動するように構成したものである。   According to a second aspect of the present invention, in the configuration according to the first aspect, contact portions are formed at both ends of the pivot shaft, and cam plates with which the contact portions abut are disposed on both sides of the pivot shaft, The cam plates are configured to be linked and interlocked via a parallel link mechanism and tilted.

請求項３記載の発明は、請求項１または２記載の構成において、遊星歯車は、太陽歯車に噛み合う入力遊星歯車と、内歯車に噛み合う出力遊星歯車とで構成されたものである。   According to a third aspect of the present invention, in the configuration of the first or second aspect, the planetary gear includes an input planetary gear that meshes with the sun gear and an output planetary gear that meshes with the internal gear.

請求項１記載の発明によれば、カム板が回転軸心に対して傾斜した状態で、太陽歯車に対する遊星歯車の噛み合い位置を回転軸心方向に往復移動させる。これにより、カム板が回転軸心に垂直な中立姿勢における遊星歯車の回転数に対して、はすば歯車のねじれ角による噛み合い位置のずれ分だけ回転速度を変化させることができる。そして１８０°の範囲にのみ設けられた内歯車により、遊星歯車の回転力を１８０°ごとに交互にキャリア部材に伝達することで、遊星歯車の旋回を連続してキャリア部材に伝達し回転することができる。したがって、変速調整装置で直線駆動機構によりカム板を傾動させることにより、遊星歯車と太陽歯車、内歯車とが噛み合った状態で、遊星歯車を軸心方向にスライドさせて、軸心方向の移動量を変化させ、これにより変速比を変更することができる。したがって、歯車を連続的に噛み合わせた状態で無段変速操作が可能となり、入力軸からの十分に大きい回転トルクを出力軸に確実に伝達することができて滑りが生じることがない。また、変速比を変更するときであっても、回転トルクの大きさに関係なく動力を確実に伝達することができ、滑りのない遊星歯車式無段変速装置を提供することができる。   According to the first aspect of the present invention, the meshing position of the planetary gear with respect to the sun gear is reciprocated in the direction of the rotational axis while the cam plate is inclined with respect to the rotational axis. As a result, the rotational speed of the planetary gear can be changed by the shift amount of the meshing position due to the helical angle of the helical gear with respect to the rotational speed of the planetary gear when the cam plate is in a neutral posture perpendicular to the rotational axis. Then, the rotation of the planetary gear is alternately transmitted to the carrier member every 180 ° by the internal gear provided only in the range of 180 °, so that the rotation of the planetary gear is continuously transmitted to the carrier member and rotated. Can do. Therefore, by tilting the cam plate by the linear drive mechanism in the speed change adjusting device, the planetary gear is slid in the axial direction in a state where the planetary gear, the sun gear, and the internal gear are engaged with each other. Thus, the gear ratio can be changed. Therefore, a continuously variable transmission operation can be performed with the gears continuously meshed, and a sufficiently large rotational torque from the input shaft can be reliably transmitted to the output shaft, so that no slip occurs. Moreover, even when changing the gear ratio, power can be reliably transmitted regardless of the magnitude of the rotational torque, and a planetary gear type continuously variable transmission without slipping can be provided.

請求項２記載の発明によれば、旋回軸の両端側にそれぞれカム板を配置して平行リンク機構により連結連動したので、旋回軸をカム板に付勢する拘束部材が不要となり、カム板を容易に傾動できる。   According to the second aspect of the present invention, since the cam plates are arranged on both ends of the pivot shaft and connected and interlocked by the parallel link mechanism, a restraining member for urging the pivot shaft to the cam plate becomes unnecessary, and the cam plate is Can tilt easily.

請求項３記載の発明によれば、遊星歯車を入力遊星歯車と出力遊星歯車とで構成したので、出力遊星歯車や内歯車のピッチ円の直径や設置位置を、太陽歯車に拘束されることなく設定することができ、設計の自由度を向上させることができる。   According to the invention of claim 3, since the planetary gear is composed of the input planetary gear and the output planetary gear, the diameter and the installation position of the pitch circle of the output planetary gear and the internal gear are not restricted by the sun gear. The degree of freedom of design can be improved.

以下、本発明の実施の形態を図面に基づいて説明する。
（基本原理）
この無段変速装置の基本原理を図１に基づいて説明する。ピッチ円直径Ｄ、ねじれ角θで同一歯数のはすば歯車Ａ，Ｂとを噛み合わせ、はすば歯車Ｂを回転させると同時に、はすば歯車Ｂをａ→ｂまで回転軸心方向に距離：Ｌをスライドさせると、はすば歯車Ｂの回転量に対してはすば歯車Ａの回転が、±δ（ずれ量）となり、このずれ量：δは、Ｌ・tanθで表される。この無段変速装置は、このように、互いに噛み合う一方のはすば歯車を回転軸心方向にスライドさせた時のはすば歯車の回転量の変化を利用したものである。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(Basic principle)
The basic principle of this continuously variable transmission will be described with reference to FIG. The helical gears A and B having the same number of teeth with the pitch circle diameter D and the torsion angle θ mesh with each other to rotate the helical gear B, and at the same time, rotate the helical gear B from a to b in the direction of the rotation axis. When the distance L is slid, the rotation of the helical gear A becomes ± δ (deviation amount) with respect to the rotation amount of the helical gear B, and this deviation amount: δ is expressed by L · tanθ. The In this way, this continuously variable transmission utilizes the change in the amount of rotation of the helical gear when one of the helical gears that mesh with each other is slid in the direction of the rotational axis.

（基本構造）
この無段変速装置の基本構造は、図２に示すように、はすば歯車の回転軸心Ｏ方向の往復移動を連続的に行うために遊星歯車式としている。すなわち、回転軸心Ｏ上の入力軸１に歯幅の広い太陽歯車２が固定され、前記入力軸１の端部に軸受を介して出力軸３が同一の回転軸心Ｏ上に回転自在に配置されている。またこの出力軸３にはキャリア部材４が固定されており、このキャリア部材４に、回転軸心Ｏを中心として１８０°隔てて２本の旋回軸５，５が回転軸心Ｏに平行に配置され、これら旋回軸５，５はそれぞれ回転軸心Ｏ方向にスライド自在に支持されている。これら旋回軸５，５には、太陽歯車２に噛み合いその周囲を旋回する遊星歯車６，６が回転軸心Ｏ方向の移動を規制されて取り付けられている。そしてこれら遊星歯車６，６に外嵌されるリング体７には、遊星歯車６，６が噛み合う内歯車８が、回転軸心Ｏを中心とする１８０°の範囲に形成されている。 (Basic structure)
As shown in FIG. 2, the basic structure of the continuously variable transmission is a planetary gear type for continuously reciprocating the helical gear in the direction of the rotation axis O. That is, a sun gear 2 having a wide tooth width is fixed to the input shaft 1 on the rotation axis O, and the output shaft 3 is rotatable on the same rotation axis O via a bearing at the end of the input shaft 1. Has been placed. Further, a carrier member 4 is fixed to the output shaft 3, and two swivel shafts 5, 5 are arranged in parallel with the rotation axis O at 180 ° with respect to the rotation axis O as a center. The pivot shafts 5 and 5 are supported so as to be slidable in the direction of the rotation axis O, respectively. Planetary gears 6 and 6 that mesh with the sun gear 2 and turn around the sun gear 2 are attached to the swivel shafts 5 and 5 so that the movement in the direction of the rotation axis O is restricted. The ring body 7 that is externally fitted to the planetary gears 6 and 6 is formed with an internal gear 8 that meshes with the planetary gears 6 and 6 in a range of 180 ° with the rotational axis O as the center.

また旋回軸５，５の一端側に配置されたカム板９は、回転軸心Ｏに直交しかつ内歯車８の２等分線と平行な傾動軸心Ｏｈ周りに傾動自在に支持されている。このカム板９のカム面９ａには、ばねなどのカム面９ａ側に付勢する拘束部材（図示せず）により旋回軸５，５の端部がそれぞれ当接されている。前記各歯車２，６，８は、それぞれ同一ピッチで同一のねじり角θのはすば歯車により構成されている。   The cam plate 9 disposed on one end side of the pivot shafts 5 and 5 is supported so as to be tiltable around a tilt axis Oh that is orthogonal to the rotation axis O and parallel to the bisector of the internal gear 8. . The ends of the pivot shafts 5 and 5 are in contact with the cam surface 9a of the cam plate 9 by a restraining member (not shown) that urges the cam surface 9a such as a spring. The gears 2, 6, and 8 are helical gears having the same pitch and the same torsion angle θ.

上記構成において、図２（ａ）に一点鎖線で示すように、カム板９が回転軸心Ｏに対して９０°となる中立姿勢とし、入力軸１を介して太陽歯車２を、図３に示す反時計方向に回転させると、両遊星歯車６，６がそれぞれ時計方向に回転され、内歯車８に噛み合う一方の遊星歯車６，６により旋回軸５，５およびキャリア部材４を介して出力軸３が反時計方向に回転される。そして、入力側の太陽歯車２の歯数：ｃ、出力側の内歯車８の歯数（１周分）：ｄとすると、変速比が（ｃ＋ｄ）／ｃとなり、入力軸１に対して出力軸３が減速される。   2A, the cam plate 9 is in a neutral posture at 90 ° with respect to the rotational axis O, and the sun gear 2 is connected to the sun gear 2 via the input shaft 1 as shown in FIG. When the planetary gears 6 and 6 are rotated in the counterclockwise direction shown in the figure, the planetary gears 6 and 6 are respectively rotated in the clockwise direction. 3 is rotated counterclockwise. When the number of teeth of the input side sun gear 2 is c and the number of teeth of the output side internal gear 8 (one turn) is d, the transmission ratio is (c + d) / c, and the output is output to the input shaft 1. The shaft 3 is decelerated.

次に、図２（ａ）に実線で示すように、カム板９をα°傾斜させると、旋回軸５が１８０°旋回される間に、遊星歯車６が内歯車８のＰ１からＰ２まで回転軸心Ｏ方向に距離Ｌだけ移動される。これにより、太陽歯車２の回転量は、カム板９の中立姿勢の時に対して、周方向にずれ量：δ＝Ｌ・tanθだけずれることになる。そして遊星歯車６の１回の旋回ではその２倍だけずれる。したがって、先の変速比に対してずれ量：δ分により出力軸３が増速または減速される。そして、旋回軸５，５が１８０°旋回される毎に、Ｐ１からＰ２まで同一の回転軸心Ｏ方向に移動される遊星歯車６が内歯車８に順次噛み合い、増速状態または減速状態が継続される。   Next, as shown by a solid line in FIG. 2A, when the cam plate 9 is inclined by α °, the planetary gear 6 rotates from P1 to P2 of the internal gear 8 while the turning shaft 5 is turned 180 °. It is moved by a distance L in the direction of the axis O. As a result, the rotation amount of the sun gear 2 is shifted by a shift amount: δ = L · tan θ in the circumferential direction with respect to the neutral posture of the cam plate 9. Then, the planetary gear 6 is shifted twice by one turn. Therefore, the output shaft 3 is accelerated or decelerated by a deviation amount: δ from the previous gear ratio. Each time the turning shafts 5 and 5 are turned by 180 °, the planetary gear 6 moved in the same direction of the rotation axis O from P1 to P2 is sequentially meshed with the internal gear 8, and the speed increasing state or the speed reducing state is continued. Is done.

ここで、カム板９の傾斜角αを変化させることにより、距離Ｌが変化して歯車２，６，８が噛み合った状態で変速比を連続的に変化させることができる。
［実施の形態１］
本発明に係る減速装置の実施の形態１を図３〜図７に基づいて説明する。なお、先の説明の同一部材には同一符号を付して説明する。 Here, by changing the inclination angle α of the cam plate 9, the gear ratio can be continuously changed in a state where the distance L is changed and the gears 2, 6 and 8 are engaged.
[Embodiment 1]
A first embodiment of a speed reducer according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected and demonstrated to the same member of the previous description.

基部フレーム１１には前後一対の前端板１２および後端板１３が垂設され、前端板１２に入力軸１が回転軸心Ｏ上に軸受を介して回転自在に支持され、後端板１３に出力軸３が回転軸心Ｏ上に軸受を介して回転自在に支持されている。前端板１２と後端板１３の間の基部フレーム１１には、一対の板材からなり回転軸心Ｏに垂直なリング支持体１４が立設固定され、このリング支持体１４には、内歯車８が形成されたリング体７が固定され、前記内歯車８は回転軸心Ｏを中心に１８０度の範囲に形成されるとともに、上部と下部が出入口となるように配置されている。   A pair of front and rear front end plates 12 and a rear end plate 13 are suspended from the base frame 11, and the input shaft 1 is rotatably supported by the front end plate 12 on a rotation axis O via a bearing. The output shaft 3 is rotatably supported on the rotation axis O via a bearing. On the base frame 11 between the front end plate 12 and the rear end plate 13, a ring support 14 made of a pair of plates and perpendicular to the rotation axis O is erected and fixed. The internal gear 8 is formed in a range of 180 degrees around the rotation axis O, and the upper and lower parts are arranged as an entrance / exit.

前記入力軸１には、リング体７と前端板１２の間に太陽歯車２が固定されている。また出力軸３には、リング体７の両側にそれぞれキャリア部材４Ａ，４Ｂが固定されている。そしてキャリア部材４Ａ，４Ｂに回転軸心Ｏ周りに１８０°隔てて形成されたスライド穴４ａ，４ｂに、回転軸心Ｏに平行な２本の旋回軸５，５がそれぞれ回転軸心Ｏ方向にスライド自在に支持されている。これら旋回軸５，５には太陽歯車２に噛み合う入力遊星歯車６Ａ，６Ａと、内歯車８に噛み合う出力遊星歯車６Ｂ，６Ｂとがそれぞれ固定され互いに連結連動されている。   A sun gear 2 is fixed to the input shaft 1 between the ring body 7 and the front end plate 12. Carrier members 4A and 4B are fixed to the output shaft 3 on both sides of the ring body 7, respectively. Then, in the slide holes 4a and 4b formed in the carrier members 4A and 4B at a distance of 180 ° around the rotation axis O, the two pivot shafts 5 and 5 parallel to the rotation axis O are respectively in the direction of the rotation axis O. It is slidably supported. The planetary gears 6A and 6A meshing with the sun gear 2 and the output planetary gears 6B and 6B meshing with the internal gear 8 are fixed to the swivel shafts 5 and 5, respectively, and are connected to each other.

旋回軸５，５の前後側には、各旋回軸５，５の両端の受動部５ａ，５ａが摺接する前後一対のカム板９Ａ，９Ｂと、カム板９Ａ，９Ｂを傾動させるためのアクチュエータまたはシリンダなどの直線駆動機構（図示せず）とを具備した変速調整装置（変速調整手段）１０が配置されている。これらカム板９Ａ，９Ｂは入力軸１および出力軸３がそれぞれ遊嵌する開口部９ａ，９ｂが形成され、前後端板１２，１３を連結する左右の側部フレーム１５，１５に、回転軸心Ｏに直交しかつ内歯車８の二等分線に平行な傾動軸心Ｏｈ上の傾動ピン１６Ａ，１６Ｂを介して前後に傾動自在に支持されている。ここで、カム板９Ａ，９Ｂのカム面９Ｃ，９Ｃは傾動軸心Ｏｈ上にある。   On the front and rear sides of the pivot shafts 5 and 5, a pair of front and rear cam plates 9A and 9B in which the passive portions 5a and 5a at both ends of the respective pivot shafts 5 and 5 are in sliding contact with an actuator for tilting the cam plates 9A and 9B or A shift adjustment device (shift adjustment means) 10 including a linear drive mechanism (not shown) such as a cylinder is disposed. These cam plates 9A and 9B are formed with openings 9a and 9b in which the input shaft 1 and the output shaft 3 are loosely fitted, respectively, and the left and right side frames 15 and 15 connecting the front and rear end plates 12 and 13 are connected to the rotation axis. It is tiltably supported back and forth via tilt pins 16A and 16B on a tilt axis Oh that is orthogonal to O and parallel to the bisector of the internal gear 8. Here, the cam surfaces 9C and 9C of the cam plates 9A and 9B are on the tilt axis Oh.

そしてカム板９Ａ，９Ｂから上方に突出されたアーム１８Ａ，１８Ｂの先端部間に平行リンクアーム１８Ｃが連結ピン１８ａ，１８ｂを介して回動自在に連結され、前記傾動ピン１６Ａ，１６Ｂと連結ピン１８ａ，１８ｂとが連結点となる平行リンク機構が構成されている。そして平行リンクアーム１８Ｃの前端部には、カム板９Ａ，９Ｂを傾動させるためのアクチュエータまたはシリンダなどの直線駆動機構（図示せず）からなる変速調整装置（変速調整手段）１０の出力ロッド１０ａが連結されている。   A parallel link arm 18C is rotatably connected between the tip portions of the arms 18A and 18B protruding upward from the cam plates 9A and 9B via connection pins 18a and 18b, and the tilt pins 16A and 16B are connected to the connection pins. A parallel link mechanism in which 18a and 18b are connection points is configured. At the front end of the parallel link arm 18C, an output rod 10a of a speed change adjusting device (speed change adjusting means) 10 comprising a linear drive mechanism (not shown) such as an actuator or a cylinder for tilting the cam plates 9A, 9B is provided. It is connected.

上記構成において、図１に示すように、変速調整装置１０により、カム板９Ａ，９Ｂが回転軸心Ｏに垂直な中立姿勢では、入力軸１により遊星歯車２が、図４，図５に矢印で示す反時計方向に回転されると、２つの入力遊星歯車６Ａ，６Ａは時計方向に回転される。そして入力遊星歯車６Ａ，６Ａにより旋回軸５，５を介して回転される２つの出力遊星歯車６Ｂ，６Ｂのうち、内歯車８に噛み合う一方の出力遊星歯車６Ｂによりキャリア部材４が反時計方向に旋回移動され、これにより出力軸３が回転される。この時の変速比は、入力側の太陽歯車２の歯数：ｃ、出力側の内歯車８の歯数（１周分）：ｄとすると、変速比は（ｃ＋ｄ）／ｃとなり、入力軸１に対して出力軸３が減速される。   In the above configuration, as shown in FIG. 1, the planetary gear 2 is moved by the input shaft 1 to the planetary gear 2 in the neutral posture in which the cam plates 9 </ b> A and 9 </ b> B are perpendicular to the rotation axis O by the transmission adjusting device 10. Are rotated counterclockwise, the two input planetary gears 6A, 6A are rotated clockwise. Of the two output planetary gears 6B, 6B rotated by the input planetary gears 6A, 6A via the pivot shafts 5, 5, the carrier member 4 is counterclockwise by the one output planetary gear 6B meshing with the internal gear 8. As a result, the output shaft 3 is rotated. If the gear ratio at this time is the number of teeth of the sun gear 2 on the input side: c, and the number of teeth of the internal gear 8 on the output side (one turn): d, the gear ratio is (c + d) / c, and the input shaft 1, the output shaft 3 is decelerated.

ついで、図７に実線で示すように、変速調整装置１０によりカム板９Ａ，９Ｂがα°で傾斜される変速姿勢とすると、カム板９Ａ，９Ｂのカム面９Ｃ，９Ｃの傾斜に従って旋回軸６Ａ，６Ｂが回転軸心Ｏ方向に相対して出退され、入力遊星歯車６Ａ，６Ａは太陽歯車２の外周面を楕円方向に沿って転動する。またそれに連動して出力遊星歯車６Ｂ，６Ｂもそれぞれ回転軸心Ｏ方向に相対移動され、半円状の内歯車８に噛み合う一方の出力遊星歯車６Ｂも楕円方向に沿って順次転動し、出力遊星歯車６Ｂ，６Ｂはそれぞれ往復移動する半分、たとえば往路側だけキャリア部材４を旋回駆動して旋回力を順次出力軸３に伝達し回転駆動する。この時、中立位置と比較して、遊星歯車６Ａ，６Ｂの１回の旋回におけるずれ量δがＬ・tanθ×２となる。またカム板９Ａ，９Ｂを、図３の仮想線で示すように、逆に方向に傾斜角−α°とした場合には、−δとなる。そしてカム板９Ａ，９Ｂの傾斜角α°を変化させることにより、１回転における移動量：Ｌが変化してずれ量：δが連続的に変化するが、この時に太陽歯車２、遊星歯車６および内歯車８は互いに噛み合った状態で、無段階に変速させることができる。   Next, as shown by the solid line in FIG. 7, when the shift adjustment device 10 is used to shift the cam plates 9A and 9B at an angle of α °, the pivot shaft 6A is moved according to the inclination of the cam surfaces 9C and 9C of the cam plates 9A and 9B. , 6B are retracted relative to the direction of the rotation axis O, and the input planetary gears 6A, 6A roll on the outer peripheral surface of the sun gear 2 along the elliptical direction. In conjunction with this, the output planetary gears 6B and 6B are also moved relative to each other in the direction of the rotation axis O, and one of the output planetary gears 6B meshing with the semicircular inner gear 8 also rolls sequentially along the elliptical direction, and outputs. Each of the planetary gears 6B and 6B reciprocates, for example, the carrier member 4 is swiveled only on the forward path side, and the swiveling force is sequentially transmitted to the output shaft 3 to be rotationally driven. At this time, as compared with the neutral position, the deviation δ in one turn of the planetary gears 6A and 6B is L · tan θ × 2. On the other hand, when the cam plates 9A and 9B are inclined in the direction of -α ° as shown by phantom lines in FIG. Then, by changing the inclination angle α ° of the cam plates 9A and 9B, the movement amount in one rotation: L changes and the deviation amount: δ changes continuously. At this time, the sun gear 2, the planetary gear 6 and The internal gear 8 can be shifted steplessly while being engaged with each other.

なお、この変速範囲を、出力軸３の出力側に増速用歯車装置を介在させることにより、大きい変速範囲を得ることもできる。
上記実施の形態１によれば、変速調整装置１０によりカム板９Ａ，９Ｂを傾斜させることで、遊星歯車６Ａ，６Ｂと太陽歯車２、内歯車８とが噛み合った状態で遊星歯車６Ａ，６Ｂを回転軸心Ｏ方向にスライドさせて変速比を変更することができる。これにより無段変速操作が可能となり、変速比の変更時でも入力軸１から出力軸３に十分に大きい回転トルクを伝達することができる。したがって、伝達トルクの大きさに関係なく動力を確実に伝達することができ、滑りのない遊星歯車式無段変速装置を提供することができる。 It should be noted that this speed change range can be obtained by interposing a speed increasing gear device on the output side of the output shaft 3.
According to the first embodiment, the planetary gears 6A, 6B are engaged with the planetary gears 6A, 6B, the sun gear 2, and the internal gear 8 by inclining the cam plates 9A, 9B by the transmission adjusting device 10. The gear ratio can be changed by sliding in the direction of the rotation axis O. As a result, a continuously variable transmission operation is possible, and a sufficiently large rotational torque can be transmitted from the input shaft 1 to the output shaft 3 even when the gear ratio is changed. Therefore, it is possible to provide a planetary gear type continuously variable transmission that can reliably transmit power regardless of the magnitude of the transmission torque and that does not slip.

なお、変速調整装置１０を手動レバーなどにより駆動する形式であってもよい。
［実施の形態２］
図８は、カム面を傾斜させた場合の太陽歯車２の歯面の展開面上における遊星歯車６Ａの転動軌跡を示すグラフで、遊星歯車６Ａが内歯８に噛み合う１８０°の範囲を示している。実施の形態１では、太陽歯車２が等速回転した場合、図８に一点鎖線で示すように、遊星歯車６Ａ（受動部５ａ）が一定速度で回転軸心Ｏ方向に移動される直線の基準線Ｓに沿うことが望ましい。しかし、カム面９Ｃが平坦であるため、図８に実線で示すように、回転軸Ｏの回転に従って所定の変動距離：γで増減を繰り返す曲線上の変動軌跡Ｔとなり、これにより出力軸３の回転速度が変動する。 The shift adjustment device 10 may be driven by a manual lever or the like.
[Embodiment 2]
FIG. 8 is a graph showing the rolling trajectory of the planetary gear 6A on the development surface of the tooth surface of the sun gear 2 when the cam surface is inclined, and shows a range of 180 ° where the planetary gear 6A meshes with the internal teeth 8. ing. In the first embodiment, when the sun gear 2 rotates at a constant speed, a reference of a straight line in which the planetary gear 6A (passive part 5a) is moved in the direction of the rotation axis O at a constant speed, as shown by a one-dot chain line in FIG. It is desirable to follow the line S. However, since the cam surface 9C is flat, as shown by a solid line in FIG. 8, a change locus T on the curve that repeatedly increases and decreases with a predetermined change distance: γ according to the rotation of the rotation axis O is obtained. The rotation speed fluctuates.

ところで、図９に示すように、受動部５ａは先尖り形に形成されてカム板９Ａ，９Ｂのカム面９Ｃにそれぞれ摺接されるが、回転軸心Ｏに対してカム板９Ａ，９Ｂの傾斜角が０°の姿勢では、受動部５ａの摺接点は一点鎖線で示すように真円軌跡ＳＬに沿って移動し、またカム板９Ａ，９Ｂが傾動軸心Ｏｈを中心に傾動されると、受動部５ａの摺接点が実線で示すように上下に長い楕円軌跡ＥＬとなる。したがって、カム板９Ａ，９Ｂを傾動させると、旋回軸５，５の受動部５ａがカム面９Ｃ上で、真円軌跡ＳＬと楕円形軌跡ＥＬの範囲で移動することになる。   By the way, as shown in FIG. 9, the passive portion 5a is formed in a pointed shape and is slidably contacted with the cam surfaces 9C of the cam plates 9A and 9B, but the cam plates 9A and 9B are in contact with the rotation axis O. When the tilt angle is 0 °, the sliding contact of the passive portion 5a moves along the perfect circle locus SL as shown by the alternate long and short dash line, and the cam plates 9A and 9B are tilted about the tilt axis Oh. As shown by the solid line, the sliding contact of the passive portion 5a becomes an elliptical locus EL that is long in the vertical direction. Therefore, when the cam plates 9A and 9B are tilted, the passive portion 5a of the pivot shafts 5 and 5 moves on the cam surface 9C within the range of the perfect circular locus SL and the elliptical locus EL.

この実施の形態２では、上記回転速度の変動を解決するために、カム板９Ａ，９Ｂ上で旋回軸５，５の受動部５ａ，５ａが当接する部位を、内歯車８の回転角度位置に対応して、旋回軸５，５が一定速度で回転軸心Ｏ方向に移動するように形成したものである。すなわち、カム面９Ｃの真円軌跡ＳＬと楕円形軌跡ＥＬの範囲で回転軸心Ｏ方向の変動距離：γを補正して補正距離が−γとなるようにカム面９Ｃの起伏を形成している。これにより、受動部５ａを基準線Ｓに沿って移動させることにより、出力軸３の回転がほぼ一定になるように回転速度を伝達することができる。   In the second embodiment, in order to solve the fluctuations in the rotational speed, the portion where the passive portions 5a and 5a of the turning shafts 5 and 5 abut on the cam plates 9A and 9B is set to the rotational angle position of the internal gear 8. Correspondingly, the turning shafts 5 and 5 are formed to move in the direction of the rotation axis O at a constant speed. That is, the undulation of the cam surface 9C is formed so that the variation distance: γ in the direction of the rotation axis O in the range of the perfect circle locus SL and the elliptical locus EL of the cam surface 9C is corrected and the correction distance becomes −γ. Yes. Thereby, by moving the passive part 5a along the reference line S, the rotation speed can be transmitted so that the rotation of the output shaft 3 becomes substantially constant.

上記構成によれば、旋回移動に従って旋回軸９Ａ，９Ｂを回転軸心Ｏ方向に移動させるカム板９Ａ，９Ｂのカム面９Ｃを、旋回軸９Ａ，９Ｂが一定速度で回転軸心Ｏ方向に移動するように形成したので、出力軸３の回転速度の変動をほとんど無くすことができる。   According to the above configuration, on the cam surfaces 9C of the cam plates 9A and 9B that move the turning shafts 9A and 9B in the direction of the rotation axis O according to the turning movement, the turning shafts 9A and 9B move in the direction of the rotation axis O at a constant speed. As a result, the fluctuation of the rotation speed of the output shaft 3 can be almost eliminated.

なお、本発明に係る遊星歯車式無段変速機を、図１０に示すように、上記基本構造に基づいて製造することもできる。上記基本構造および実施の形態１と同一部材には同一符号を付して説明を省略する。これによれば、遊星歯車の個数を減らすことができ、全体をコンパクトに構成できるほか、先の実施の形態と同様の作用効果を奏することができる。   The planetary gear type continuously variable transmission according to the present invention can also be manufactured based on the basic structure as shown in FIG. The same members as those in the basic structure and the first embodiment are denoted by the same reference numerals, and description thereof is omitted. According to this, the number of planetary gears can be reduced, the whole can be configured compactly, and the same operational effects as in the previous embodiment can be achieved.

またキャリア部材４Ａ，４Ｂに２本の旋回軸５，５を１８０°隔てて配置したが、内歯車８と出力側遊星歯車６Ｂの係合、離脱をスムーズに行うために、たとえば図１１（ａ）に示すように、互いに接近された２本の旋回軸５，５を二組１８０°隔てた対称位置に配置してもよく、また図１１（ｂ）に示すように、１２０°ごとに３本の旋回軸５をそれぞれ配置することもできる。もちろん、図示しないが、９０°ごとに３本の旋回軸を配置してもよい。   Further, although the two turning shafts 5 and 5 are arranged 180 degrees apart on the carrier members 4A and 4B, in order to smoothly engage and disengage the internal gear 8 and the output side planetary gear 6B, for example, FIG. As shown in FIG. 11 (b), two swiveling shafts 5 and 5 that are close to each other may be arranged at symmetrical positions separated by 180 °, and as shown in FIG. Each of the pivot shafts 5 can also be arranged. Of course, although not shown, three pivot axes may be arranged every 90 °.

さらに上記構成において、入力軸１を出力用として、出力軸３を入力用として使用することもできる。   Further, in the above configuration, the input shaft 1 can be used for output and the output shaft 3 can be used for input.

本発明に係る遊星歯車式無段減速装置の基本原理を示す説明図で、（ａ）ははすば歯車の噛み合い状態を示す側面図、（ｂ）ははすば歯車Ａの歯面の展開図である。BRIEF DESCRIPTION OF THE DRAWINGS It is explanatory drawing which shows the basic principle of the planetary gear type continuously variable reduction device which concerns on this invention, (a) is a side view which shows the meshing state of a helical gear, (b) is expansion | deployment of the tooth surface of the helical gear A FIG. 同遊星歯車式無段減速装置の基本構造を示す説明図で、（ａ）は遊星歯車の噛み合いを示す側面図、（ｂ）は（ａ）に示すＨ−Ｈ断面図である。It is explanatory drawing which shows the basic structure of the planetary gear type continuously variable reduction gear, (a) is a side view showing meshing of the planetary gear, and (b) is an HH sectional view shown in (a). 本発明に係る遊星歯車式無段減速装置の実施の形態１を示す縦断面図である。It is a longitudinal cross-sectional view which shows Embodiment 1 of the planetary gear type continuously variable reduction gear according to the present invention. 図３に示すＥ−Ｅ断面図である。It is EE sectional drawing shown in FIG. 図３に示すＦ−Ｆ断面図である。It is FF sectional drawing shown in FIG. 図３に示すＧ−Ｇ断面図である。It is GG sectional drawing shown in FIG. 同遊星歯車式無段変速機の変速動作を示す縦断面図である。It is a longitudinal cross-sectional view which shows speed change operation | movement of the planetary gear type continuously variable transmission. 本発明に係る遊星歯車式無段減速装置の実施の形態２を示し、太陽歯車の歯面展開図における遊星歯車の移動軌跡を示すグラフである。It is a graph which shows Embodiment 2 of the planetary gear type continuously variable reduction gear according to the present invention, and shows the movement locus of the planetary gear in the tooth surface development view of the sun gear. 同遊星歯車式無段変速機における旋回軸のカム板上の移動軌跡を示す説明図である。It is explanatory drawing which shows the movement locus | trajectory on the cam board of the rotating shaft in the planetary gear type continuously variable transmission. 同遊星歯車式無段変速機の基本構造による他の実施の形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows other embodiment by the basic structure of the planetary gear type continuously variable transmission. 同遊星歯車式無段変速機の旋回軸および遊星歯車の配置を示す説明図で、（ａ）は４本の旋回軸の配置、（ｂ）は３本の旋回軸の配置を示す。It is explanatory drawing which shows arrangement | positioning of the turning axis and planetary gear of the planetary gear type continuously variable transmission, (a) shows the arrangement of four turning axes, and (b) shows the arrangement of three turning axes.

符号の説明Explanation of symbols

Ｏ 回転軸心
Ｏｈ 傾動軸心
１ 入力軸
２ 太陽歯車
３ 出力軸
４Ａ，４Ｂ キャリア部材
５ 旋回軸
５ａ 受動部
６Ａ 入力遊星歯車
６Ｂ 出力遊星歯車
７ リング体
８ 内歯車
９Ａ，９Ｂ カム板
９Ｃ カム面
１０ 変速調整装置
１１ 基板フレーム
１２ 前端板
１３ 後端板
１４ リング支持体
１５ 側部フレーム
１６Ａ，１６Ｂ 傾動ピン
１８Ｃ 平行リンクアーム O rotational axis Oh tilt axis 1 input shaft 2 sun gear 3 output shaft 4A, 4B carrier member 5 swivel shaft 5a passive part 6A input planetary gear 6B output planetary gear 7 ring body 8 internal gear 9A, 9B cam plate 9C cam surface DESCRIPTION OF SYMBOLS 10 Shift adjustment apparatus 11 Board frame 12 Front end plate 13 Rear end plate 14 Ring support body 15 Side frame 16A, 16B Tilt pin 18C Parallel link arm

Claims (3)

回転軸心上に設けられた太陽歯車と、当該太陽歯車の外周部に一定間隔をあけて固定された内歯車と、回転軸心に周りに回転自在に支持されたキャリア部材に設けられて太陽歯車および内歯車にそれぞれ噛み合う遊星ギヤとを具備した遊星歯車式無段変速装置であって、
太陽歯車、遊星歯車および内歯車をそれぞれ所定のねじれ角を有するはすば歯車により構成し、
キャリア部材に、複数の旋回軸を軸心方向にスライド自在に設けるとともに、前記各旋回軸に軸心方向の移動が規制された遊星歯車をそれぞれ設け、
内歯車を回転軸心周りに１８０°の範囲にのみ設け、
前記旋回軸は、前記各遊星歯車の少なくとも１個が前記内歯車に噛み合う位置に配置され、
回転軸心に直交しかつ内歯車の二等分線に平行な傾動軸周りに傾動自在なカム板と、当該カム板を傾動可能な直線駆動機構とを有し、前記カム板の傾斜姿勢で回転軸心を中心とする遊星歯車の１回の旋回に対して前記旋回軸を介して遊星歯車をそれぞれ軸心方向に１往復移動させる変速調整手段を設けた
遊星歯車式無段変速装置。 A sun gear provided on a rotation axis, an internal gear fixed to the outer periphery of the sun gear at a predetermined interval, and a carrier member rotatably supported around the rotation axis. A planetary gear type continuously variable transmission comprising a planetary gear meshing with a gear and an internal gear,
Each of the sun gear, the planetary gear, and the internal gear is constituted by a helical gear having a predetermined twist angle,
The carrier member is provided with a plurality of pivot shafts slidably in the axial direction, and each of the pivot shafts is provided with a planetary gear whose movement in the axial direction is restricted,
The internal gear is provided only in the range of 180 ° around the rotation axis,
The pivot shaft is disposed at a position where at least one of the planetary gears meshes with the internal gear;
A cam plate that can be tilted around a tilting axis that is orthogonal to the rotation axis and parallel to the bisector of the internal gear, and a linear drive mechanism that can tilt the cam plate, A planetary gear type continuously variable transmission provided with shift adjusting means for reciprocating the planetary gears in the axial direction through the swivel shaft for one turn of the planetary gear centered on the rotation axis. 旋回軸の両端部に当接部をそれぞれ形成し、
前記当接部がそれぞれ当接するカム板を、旋回軸の両側に配置し、
前記両カム板を平行リンク機構を介して連結連動し傾動するように構成した
請求項１記載の遊星歯車式無段変速装置。 Abutment parts are formed on both ends of the pivot shaft,
The cam plates with which the abutment portions abut each other are arranged on both sides of the pivot shaft,
The planetary gear type continuously variable transmission according to claim 1, wherein both the cam plates are connected and interlocked via a parallel link mechanism. 遊星歯車は、太陽歯車に噛み合う入力遊星歯車と、内歯車に噛み合う出力遊星歯車とで構成された
請求項１または２記載の遊星歯車式無段変速装置。
The planetary gear type continuously variable transmission according to claim 1 or 2, wherein the planetary gear is configured by an input planetary gear meshing with a sun gear and an output planetary gear meshing with an internal gear.
JP2006017006A 2006-01-26 2006-01-26 Planetary gear type continuously variable transmission Expired - Fee Related JP4868861B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010007760A (en) * 2008-06-26 2010-01-14 Toyota Central R&D Labs Inc Transmission
CN113812476A (en) * 2021-09-18 2021-12-21 浙江理工大学 Planetary-driven variable-inclination-angle variable-speed manual-imitation water-sieve-type green rocking machine and green rocking method thereof

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49111074A (en) * 1973-02-24 1974-10-23
JPS5069463A (en) * 1973-10-22 1975-06-10
JPS50108451A (en) * 1974-02-05 1975-08-26

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49111074A (en) * 1973-02-24 1974-10-23
JPS5069463A (en) * 1973-10-22 1975-06-10
JPS50108451A (en) * 1974-02-05 1975-08-26

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010007760A (en) * 2008-06-26 2010-01-14 Toyota Central R&D Labs Inc Transmission
CN113812476A (en) * 2021-09-18 2021-12-21 浙江理工大学 Planetary-driven variable-inclination-angle variable-speed manual-imitation water-sieve-type green rocking machine and green rocking method thereof
CN113812476B (en) * 2021-09-18 2024-01-12 浙江理工大学 Planetary-driven inclination-angle-changing speed-changing imitation manual water screen type green rocking machine and green rocking method thereof

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