JPH07310805A - Transmission - Google Patents
TransmissionInfo
- Publication number
- JPH07310805A JPH07310805A JP6126784A JP12678494A JPH07310805A JP H07310805 A JPH07310805 A JP H07310805A JP 6126784 A JP6126784 A JP 6126784A JP 12678494 A JP12678494 A JP 12678494A JP H07310805 A JPH07310805 A JP H07310805A
- Authority
- JP
- Japan
- Prior art keywords
- spur gear
- input
- shaft
- planetary
- output
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は変速機に関する。FIELD OF THE INVENTION The present invention relates to a transmission.
【０００２】[0002]
【従来の技術】工作機械、産業機械、建設機械、農業機
械、車両機械等に用いられる変速機としては、従来、イ
ンバーターやサーボモーター等の電気制御による変速機
等が知られている。2. Description of the Related Art As a transmission used for a machine tool, an industrial machine, a construction machine, an agricultural machine, a vehicle machine or the like, a transmission which is electrically controlled by an inverter or a servomotor has been known.
【０００３】[0003]
【発明が解決しようとする課題】しかし、上記変速機で
は、低速域においては、低トルクで出力不足であり、効
率が悪いという問題がある。However, in the above-mentioned transmission, there is a problem that the efficiency is poor because of low torque and insufficient output in the low speed range.
【０００４】また、電力を使用しない自動車等に用いら
れる変速機では、制御に難があり、構造が複雑化する問
題がある。Further, in a transmission used in an automobile or the like which does not use electric power, there is a problem that control is difficult and the structure becomes complicated.
【０００５】そこで本発明は、構造が簡単で、かつ、取
扱い及び製作が容易で、広範囲の変速域で高効率である
と共に動的バランスが良好な変速機を提供することを目
的とする。SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a transmission which has a simple structure, is easy to handle and manufacture, has a high efficiency in a wide range of speed change range, and has a good dynamic balance.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するため
に、回転自在な入力軸と、該入力軸の入力回転軸心と同
軸で回転自在な出力軸と、該入力軸に上記入力回転軸心
と平行な軸心を中心として回転自在に枢着されて該入力
回転軸心廻りに公転自在な入力遊星第一外平歯車と、該
入力軸に上記入力回転軸心と平行な軸心を中心として回
転自在に枢着されて該入力回転軸心廻りに公転自在であ
ると共に入力遊星第一外平歯車と噛合する入力遊星第二
外平歯車と、上記出力軸に上記入力回転軸心と平行な軸
心を中心として回転自在に枢着されて該入力回転軸心廻
りに公転自在な出力遊星第一外平歯車と、該出力軸に上
記入力回転軸心と平行な軸心を中心として回転自在に枢
着されて該入力回転軸心廻りに公転自在であると共に出
力遊星第一外平歯車と噛合する出力遊星第二外平歯車
と、上記入力遊星第一外平歯車と出力遊星第一外平歯車
に夫々噛合すると共に上記入力回転軸心を中心として回
転自在な中間外平歯車と、上記入力回転軸心と同軸にて
上記入力軸と相対回転自在な回転体と、該回転体と同軸
にて一体回転すると共に上記入力遊星第二外平歯車と噛
合する変速第一内平歯車と、該回転体と同軸にて一体回
転すると共に上記出力遊星第二外平歯車と噛合する変速
第二内平歯車と、上記回転体の回転速度を変化させる変
速手段と、を備え、上記変速第一内平歯車と変速第二内
平歯車の歯数及び基準ピッチ円を僅かに相違させたもの
である。In order to achieve the above-mentioned object, a rotatable input shaft, an output shaft rotatable coaxially with the input rotary shaft center of the input shaft, and the input rotary shaft at the input shaft. An input planetary first external spur gear that is rotatably pivoted about an axis parallel to the center and is free to revolve around the input axis of rotation, and an axis parallel to the input axis of rotation on the input axis. An input planetary second external spur gear that is rotatably pivoted as a center and is free to revolve around the input rotational shaft center and meshes with the input planetary first external spur gear; and the output shaft has the input rotational shaft center. An output planetary first spur gear that is rotatably pivoted about a parallel shaft center and can revolve around the input rotation shaft center; and an output shaft centered on a shaft center parallel to the input rotation shaft center. The output planetary first outer spur tooth is rotatably pivotally mounted and can be revolved around the input rotation axis. An output planetary second external spur gear that meshes with the input planetary first external spur gear and an intermediate external spur gear that meshes with the input planetary first external spur gear and the output planetary first external spur gear, respectively, and is rotatable about the input rotation axis. A rotating body coaxial with the input rotating shaft and rotatable relative to the input shaft; and a first variable speed internal spur gear that rotates integrally with the rotating shaft and meshes with the input planetary second outer spur gear. A gear shift second internal spur gear that rotates integrally with the rotary body coaxially and meshes with the output planetary second outer spur gear; and a shift means that changes the rotational speed of the rotary body. The number of teeth and the reference pitch circle of the first internal spur gear and the variable speed second internal spur gear are slightly different.
【０００７】また、回転自在な入力軸と、該入力軸の入
力回転軸心と同軸で回転自在な出力軸と、該入力軸に上
記入力回転軸心と平行な軸心を中心として回転自在に枢
着されて該入力回転軸心廻りに公転自在な入力遊星第一
外平歯車と、該入力軸に上記入力回転軸心と平行な軸心
を中心として回転自在に枢着されて該入力回転軸心廻り
に公転自在であると共に入力遊星第一外平歯車と噛合す
る入力遊星第二外平歯車と、上記出力軸に上記入力回転
軸心と平行な軸心を中心として回転自在に枢着されて該
入力回転軸心廻りに公転自在な出力遊星第一外平歯車
と、該出力軸に上記入力回転軸心と平行な軸心を中心と
して回転自在に枢着されて該入力回転軸心廻りに公転自
在であると共に出力遊星第一外平歯車と噛合する出力遊
星第二外平歯車と、上記入力遊星第一外平歯車と噛合す
ると共に上記入力回転軸心を中心として回転自在な中間
第一外平歯車と、上記出力遊星第一外平歯車と噛合する
と共に上記入力回転軸心を中心として回転自在な中間第
二外平歯車と、上記入力回転軸心と同軸にて上記入力軸
と相対回転自在な回転体と、該回転体と同軸にて一体回
転すると共に上記入力遊星第二外平歯車と出力遊星第二
外平歯車に夫々噛合する変速内平歯車と、上記回転体の
回転速度を変化させる変速手段と、を備え、中間第一外
平歯車と中間第二外平歯車の歯数及び基準ピッチ円を僅
かに相違させたものである。Further, a rotatable input shaft, an output shaft rotatable coaxially with the input rotary shaft of the input shaft, and a rotary shaft centered on the input shaft parallel to the input rotary shaft. An input planetary first external spur gear that is pivotally attached and can revolve around the input rotation axis, and the input rotation that is rotatably attached to the input shaft about an axis parallel to the input rotation axis. An input planetary second external spur gear that is revolvable around the axis and meshes with the input planetary first external spur gear, and is rotatably pivoted on the output shaft about an axis parallel to the input rotation axis. And an output planetary first spur gear revolvable around the input rotation shaft center, and the input rotation shaft center rotatably attached to the output shaft about an axis parallel to the input rotation shaft center. An output planetary second external spur gear that is revolvable around and meshes with the output planetary first external spur gear, An intermediate first external spur gear that meshes with the input planetary first external spur gear and is rotatable about the input rotational shaft center, and meshes with the output planetary first external spur gear and the input rotational shaft center. A second intermediate external spur gear that is rotatable, a rotary body that is rotatable relative to the input shaft coaxially with the input rotary axis, and that rotates integrally with the rotary body coaxially with the input rotary shaft. A spur gear and an output planetary second outer spur gear, each of which meshes with the variable speed inner spur gear, and a speed changer that changes the rotational speed of the rotating body. The number of teeth and the reference pitch circle are slightly different.
【０００８】さらに、複数の入力遊星第一外平歯車と入
力遊星第二外平歯車を、入力回転軸心を中心とする円周
上に於て周方向等ピッチで配設すると共に、複数の出力
遊星第一外平歯車及び出力遊星第二外平歯車を、入力回
転軸心を中心とする円周上に於て周方向等ピッチで配設
する。Further, a plurality of input planetary first external spur gears and a plurality of input planetary second external spur gears are arranged at equal pitches in the circumferential direction on the circumference centered on the input rotation axis, and a plurality of The output planetary first external spur gear and the output planetary second external spur gear are arranged at equal pitches in the circumferential direction on the circumference around the input rotation axis.
【０００９】また、回転自在な入力軸と、該入力軸の入
力回転軸心と同軸で回転自在な出力軸と、上記入力軸に
形成された偏心軸部にその偏心軸心を中心として回転自
在に枢着されて上記入力回転軸心廻りに偏心回転する入
力外平歯車と、該入力外平歯車と同軸にて一体回転して
上記入力回転軸心廻りに偏心回転する入力内平歯車と、
上記出力軸に形成された偏心軸部にその偏心軸心を中心
として回転自在に枢着されて上記入力回転軸心廻りに偏
心回転する出力外平歯車と、該出力外平歯車と同軸にて
一体回転して上記入力回転軸心廻りに偏心回転する出力
内平歯車と、上記入力内平歯車と出力内平歯車に夫々噛
合すると共に上記入力回転軸心を中心として回転自在な
中間外平歯車と、上記入力回転軸心と同軸にて上記入力
軸と相対回転自在な回転体と、該回転体と同軸にて一体
回転すると共に上記入力外平歯車と噛合する変速第一内
平歯車と、該回転体と同軸にて一体回転すると共に上記
出力外平歯車と噛合する変速第二内平歯車と、上記回転
体の回転速度を変化させる変速手段と、を備え、上記変
速第一内平歯車と変速第二内平歯車の歯数及び基準ピッ
チ円を僅かに相違させたものである。Further, a rotatable input shaft, an output shaft rotatable coaxially with the input rotation shaft center of the input shaft, and an eccentric shaft portion formed on the input shaft are rotatable around the eccentric shaft center. An input external spur gear that is pivotally attached to and rotates eccentrically around the input rotation shaft, and an input internal spur gear that rotates integrally with the input outer spur gear coaxially and rotates eccentrically around the input rotation shaft center,
An output external spur gear that is rotatably attached to an eccentric shaft portion formed on the output shaft about the eccentric shaft center and rotates eccentrically around the input rotation shaft center, and coaxial with the output external spur gear. An output inner spur gear that integrally rotates and eccentrically rotates around the input rotation shaft, and an intermediate outer spur gear that meshes with the input inner spur gear and the output inner spur gear and is rotatable about the input rotation shaft center. A rotary body that is rotatable relative to the input shaft coaxially with the input rotary shaft, and a transmission first internal spur gear that rotates integrally with the rotary body and that meshes with the input external spur gear. The speed-changing first internal spur gear, comprising: a speed-changing second internal spur gear that rotates integrally with the rotating body and meshes with the output outer spur gear; and speed-changing means that changes the rotational speed of the rotating body. And the number of teeth of the second internal spur gear and the standard pitch circle are slightly different It is those that were.
【００１０】[0010]
【作用】原動機等により入力軸が回転している状態で、
変速手段にて、回転体と入力軸を同一の回転方向及び回
転速度にすれば、入力軸から出力軸まで回転トルクを伝
動する歯車全部がロック状態となって、出力軸は入力軸
と同一回転数となる。そして、入力軸よりも回転体の回
転速度を遅らせていくと、その回転速度差によって、上
記歯車の内で自転可能な歯車が自転を始め、これによ
り、上記回転速度差の大小に応じて、出力軸の回転が遅
くなる。[Operation] With the input shaft rotating by the prime mover,
If the rotating body and the input shaft are made to have the same rotation direction and the same rotation speed by the speed changing means, all the gears that transmit the rotation torque from the input shaft to the output shaft are locked, and the output shaft rotates at the same speed as the input shaft Becomes a number. Then, when the rotation speed of the rotating body is delayed from the input shaft, the rotation speed difference causes the rotatable gear to start rotating in the gears, whereby, depending on the magnitude of the rotation speed difference, The output shaft rotates slowly.
【００１１】[0011]
【実施例】以下、実施例を示す図面に基づいて本発明を
詳説する。The present invention will be described in detail below with reference to the drawings illustrating the embodiments.
【００１２】図１は、本発明に係る変速機の一実施例を
示し、この変速機は、回転自在な入力軸１と、入力軸１
の入力回転軸心Ａと同軸で回転自在な出力軸２と、入力
回転軸心Ａと平行な軸心Ｂを中心として回転自在な入力
遊星第一外平歯車３と、入力回転軸心Ａと平行な軸心Ｃ
を中心として回転自在な入力遊星第二外平歯車４と、入
力回転軸心Ａと平行な軸心Ｅを中心として回転自在な出
力遊星第一外平歯車５と、入力回転軸心Ａと平行な軸心
Ｇを中心として回転自在な出力遊星第二外平歯車６と、
入力回転軸心Ａを中心として回転自在な中間外平歯車７
と、入力回転軸心Ａと同軸にて入力軸１と相対回転自在
な回転体８と、回転体８と同軸Ａにて一体回転する変速
第一内平歯車９と、回転体８と同軸Ａにて一体回転する
変速第二内平歯車10と、回転体８の回転速度を変化させ
る変速手段11と、を備えている。FIG. 1 shows an embodiment of a transmission according to the present invention. This transmission has a rotatable input shaft 1 and an input shaft 1.
An output shaft 2 which is rotatable coaxially with the input rotation axis A, an input planetary first spur gear 3 which is rotatable around an axis B parallel to the input rotation axis A, and an input rotation axis A Parallel axis C
The input planetary external second spur gear 4 rotatable around the center, the output planetary first external spur gear 5 rotatable about an axis E parallel to the input rotational axis A, and the input rotational axis A parallel to An output planetary second spur gear 6 which is rotatable about a central axis G,
Intermediate external spur gear 7 rotatable about the input rotation axis A
A rotary body 8 which is rotatable relative to the input shaft 1 coaxially with the input rotary axis A; a variable speed first internal spur gear 9 which rotates integrally with the rotary body 8 coaxially with the rotary body 8; The second internal spur gear 10 that rotates integrally with each other and the speed changing means 11 that changes the rotation speed of the rotating body 8 are provided.
【００１３】具体的には、入力軸１と出力軸２は、軸受
12…等を介してケーシング等に、入力回転軸心Ａを中心
に回転自在に枢支される。また、出力軸２の基端部に、
入力軸１の先端部が相対回転自在に枢支される。入力軸
１の基端側は、図示省略の原動機に接続されて回転駆動
され、出力軸２の先端側は、変速駆動される機械等に接
続される。なお、同図に於て左側が先端側、右側が基端
側である。Specifically, the input shaft 1 and the output shaft 2 are bearings.
It is rotatably supported by a casing or the like via 12 ... Also, at the base end of the output shaft 2,
The tip of the input shaft 1 is pivotally supported so as to be relatively rotatable. The base end side of the input shaft 1 is connected to a prime mover (not shown) to be rotationally driven, and the tip end side of the output shaft 2 is connected to a machine that is driven at variable speeds. In the figure, the left side is the tip side and the right side is the base side.
【００１４】図１と図２に示すように、入力遊星第一外
平歯車３と入力遊星第二外平歯車４は、入力軸１の一部
に形成された軸心方向の枢軸13，14に夫々枢着され、入
力回転軸心Ａ廻りに公転自在とされると共に軸心Ｂ，Ｃ
を中心として夫々自転自在とされる。As shown in FIGS. 1 and 2, the input planetary first external spur gear 3 and the input planetary second external spur gear 4 are axial pivots 13, 14 formed in a part of the input shaft 1 in the axial direction. Are pivotally connected to each other and can be revolved around the input rotation axis A and the axes B and C.
It is said that each of them can rotate freely.
【００１５】入力遊星第一外平歯車３は、中間外平歯車
７と入力遊星第二外平歯車４に夫々噛合し、入力遊星第
二外平歯車４は、変速第一内平歯車９と噛合する。この
入力遊星第一外平歯車３と入力遊星第二外平歯車４を対
でもって、入力回転軸心Ａを中心とする円周上に於て周
方向等ピッチで配設する。The input planetary first outer spur gear 3 meshes with the intermediate outer spur gear 7 and the input planetary second outer spur gear 4, respectively, and the input planetary second outer spur gear 4 and the variable speed first inner spur gear 9 respectively. Mesh. The input planetary first external spur gear 3 and the input planetary second external spur gear 4 are arranged in pairs on the circumference centered on the input rotation axis A at equal pitches in the circumferential direction.
【００１６】出力遊星第一外平歯車５と出力遊星第二外
平歯車６、出力軸２の一部に形成された軸心方向の枢軸
15，16に夫々枢着され、入力回転軸心Ａ廻りに公転自在
とされると共に軸心Ｅ，Ｇを中心として夫々自転自在と
される。The output planetary first external spur gear 5, the output planetary second external spur gear 6, and a pivot shaft formed in a part of the output shaft 2 in the axial direction.
They are pivotally attached to 15 and 16, respectively, so as to be revolvable around the input rotation axis A and to be rotatable about axis E and G respectively.
【００１７】出力遊星第一外平歯車５は、中間外平歯車
７と出力遊星第二外平歯車６に夫々噛合し、出力遊星第
二外平歯車６は、変速第二内平歯車10と噛合する。この
出力遊星第一外平歯車５と出力遊星第二外平歯車６を対
でもって、入力回転軸心Ａを中心とする円周上に於て周
方向等ピッチで配設する。The output planetary first outer spur gear 5 meshes with the intermediate outer spur gear 7 and the output planetary second outer spur gear 6, respectively, and the output planetary second outer spur gear 6 and the variable speed second inner spur gear 10 respectively. Mesh. The output planetary first external spur gear 5 and the output planetary second external spur gear 6 are arranged in pairs on the circumference centering on the input rotation axis A at equal circumferential pitches.
【００１８】中間外平歯車７は、入力軸１に回転自在に
枢着される。回転体８は、中空状であって、全歯車を包
囲状として入力軸１及び出力軸２に外嵌状に設けられ
る。この回転体８に、変速第一内平歯車９と変速第二内
平歯車10が、軸心方向に並ぶように一体形成される。The intermediate spur gear 7 is rotatably attached to the input shaft 1. The rotating body 8 is hollow and is provided on the input shaft 1 and the output shaft 2 so as to be fitted around the entire gears. A first variable speed internal spur gear 9 and a second variable speed internal spur gear 10 are integrally formed on the rotor 8 so as to be aligned in the axial direction.
【００１９】さらに、変速第一内平歯車９の歯数及び基
準ピッチ円を、変速第二内平歯車10の歯数及び基準ピッ
チ円に対して、僅かに相違させる。また、各歯車の転位
量はゼロである。Further, the number of teeth and the reference pitch circle of the first variable speed internal spur gear 9 are slightly different from the number of teeth and the standard pitch circle of the second variable speed internal spur gear 10. Further, the dislocation amount of each gear is zero.
【００２０】回転体８の基端部には、プーリー17が、滑
りキー18を介して外嵌状に取付けられる。プーリー17
は、一対のプーリー半体19ａ，19ｂからなり、一方のプ
ーリー半体19ａは回転体８に固定される。他方のプーリ
ー半体19ｂは、回転体８に対して、一体回転可能かつ軸
心Ａ方向にスライド自在となっており、図示省略のバネ
等によりプーリー半体19ａに接近する方向に弾発付勢さ
れる。A pulley 17 is attached to the base end of the rotating body 8 via a slide key 18 in an externally fitted shape. Pulley 17
Is composed of a pair of pulley halves 19a and 19b, and one pulley half 19a is fixed to the rotating body 8. The other pulley half body 19b is integrally rotatable with respect to the rotating body 8 and is slidable in the direction of the axis A, and is elastically biased toward the pulley half body 19a by a spring (not shown) or the like. To be done.
【００２１】プーリー17と、図示省略の電動機等の回転
軸に取付けられたプーリーには、Ｖベルト20が巻き掛け
られ、該回転軸の回転により、プーリー17及び回転体８
が一体に回転する。また、プーリー半体19ａに対してプ
ーリー半体19ｂを接近・離間させることにより、Ｖベル
ト20を、プーリー17の径方向にスライドさせ、プーリー
17及び回転体８の回転速度（即ち、変速第一内平歯車９
と変速第二内平歯車10の回転速度）を変化させることが
できる。A V-belt 20 is wound around the pulley 17 and a pulley attached to a rotating shaft of an electric motor (not shown), and the pulley 17 and the rotating body 8 are rotated by the rotation of the rotating shaft.
Rotate together. Further, the V belt 20 is slid in the radial direction of the pulley 17 by moving the pulley half body 19b toward and away from the pulley half body 19a, and
17 and the rotational speed of the rotating body 8 (that is, the variable speed first internal spur gear 9
And the rotation speed of the second internal spur gear 10) can be changed.
【００２２】このプーリー17やＶベルト20等により変速
手段11が構成される。なお、これ以外に、摩擦車や油圧
等を用いて変速手段17を構成するも自由であり、さら
に、回転体８を正転・逆転自在に制御できる変速手段11
を用いるも自由である。The pulley 17 and the V-belt 20 constitute the speed changing means 11. In addition to this, the speed change means 17 can be freely constructed by using a friction wheel, hydraulic pressure, etc., and further, the speed change means 11 capable of controlling the rotating body 8 to rotate normally and reversely.
You are free to use.
【００２３】しかして、上述の如く構成された変速機に
於て、入力軸１を所定速度で回転させた状態として、回
転体８を、入力軸１と同一の方向及び回転速度で回転さ
せれば、入力遊星第一外平歯車３、入力遊星第二外平歯
車４、出力遊星第一外平歯車５、出力遊星第二外平歯車
６、中間外平歯車７、変速第一内平歯車９、変速第二内
平歯車10が全てロック状態となって、入力遊星第一外平
歯車３、入力遊星第二外平歯車４、出力遊星第一外平歯
車５、出力遊星第二外平歯車６は自転を起こさずに、入
力回転軸心Ａ廻りに一体に（入力軸１と同一回転方向
へ）回転（公転）する。従って、出力軸２は入力軸１と
同一回転数となる。Therefore, in the transmission constructed as described above, the rotating body 8 can be rotated in the same direction and rotational speed as the input shaft 1 with the input shaft 1 being rotated at a predetermined speed. For example, input planetary first outer spur gear 3, input planetary second outer spur gear 4, output planetary first outer spur gear 5, output planetary second outer spur gear 6, intermediate outer spur gear 7, variable speed first inner spur gear. 9, the transmission second internal spur gear 10 is all locked, the input planetary first outer spur gear 3, the input planetary second outer spur gear 4, the output planetary first outer spur gear 5, the output planetary second outer spur gear The gear 6 rotates (revolves) integrally (in the same rotation direction as the input shaft 1) around the input rotation axis A without causing rotation. Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.
【００２４】この状態から、回転体８の回転を変速手段
11にて入力軸１の回転よりも遅らせていくと、両者８，
１の回転速度差により、入力遊星第一外平歯車３、入力
遊星第二外平歯車４が自転を始めると共に、中間外平歯
車７を介して、出力遊星第一外平歯車５、出力遊星第二
外平歯車６が自転して、出力遊星第一外平歯車５、出力
遊星第二外平歯車６の公転（即ち出力軸２の回転）が入
力軸１よりも遅くなり、ついには出力軸２の回転が停止
する（以下ゼロ回転という）。From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 11, both 8 and
The rotation speed difference of 1 causes the input planetary first external spur gear 3 and the input planetary second external spur gear 4 to start rotating, and via the intermediate external spur gear 7, the output planetary first external spur gear 5 and the output planetary gear. The second outer spur gear 6 rotates, and the revolution of the output planetary first outer spur gear 5 and the output planetary second outer spur gear 6 (that is, the rotation of the output shaft 2) becomes slower than that of the input shaft 1, and finally the output. The rotation of the shaft 2 stops (hereinafter referred to as zero rotation).
【００２５】このようにして、変速手段11にて回転体８
の回転速度を変化させるだけで、全域定出力で出力軸２
の無段変速が行える。しかも、出力軸２のゼロ回転は、
入力軸１を回転させる原動機の回転数に関係なく得られ
て、原動機の回転力により保障され、閉ループである。In this way, the rotating body 8 is moved by the transmission means 11.
Simply by changing the rotation speed of the
Can be continuously variable. Moreover, the zero rotation of the output shaft 2 is
It is obtained regardless of the number of revolutions of the prime mover that rotates the input shaft 1, is guaranteed by the rotational force of the prime mover, and is a closed loop.
【００２６】この図１の実施例では、変速第一内平歯車
９と変速第二内平歯車10の基準ピッチ円を僅かに相違さ
せることにより、その周速度、角速度及び通過する歯数
に違いがでてくるという事を利用し、かつ、変速第一内
平歯車９と変速第二内平歯車10の歯数を僅かに相違させ
ることにより、その干渉する力を利用して、トルクを発
生させ、変速力を取り出すことができる。In the embodiment of FIG. 1, the peripheral pitch, the angular velocity and the number of passing teeth are made different by slightly differentiating the reference pitch circles of the variable speed first internal spur gear 9 and the variable speed second internal spur gear 10. Is generated, and the number of teeth of the speed-changing first internal spur gear 9 and the speed-changing second internal spur gear 10 are slightly different, and torque is generated by using the interfering force. It is possible to take out the shift force.
【００２７】なお、変速第一内平歯車９と変速第二内平
歯車10の歯数を同一とすると、出力軸２と入力軸１の回
転速度が常に同一となって、変速しなくなる。また、変
速第一内平歯車９の歯数を変速第二内平歯車10の歯数の
１／２にすると、いわゆる「すべり」が発生して出力軸
２が常に回転しなくなる。If the number of teeth of the speed-changing first internal spur gear 9 and that of the speed-changing second internal spur gear 10 are the same, the output shaft 2 and the input shaft 1 will always have the same rotational speed, and no speed change will occur. When the number of teeth of the first variable speed internal spur gear 9 is set to 1/2 of the number of teeth of the second variable speed internal spur gear 10, so-called "slip" occurs and the output shaft 2 does not always rotate.
【００２８】次に、図３は他の実施例で、図１の実施例
における（変速第一内平歯車９、変速第二内平歯車10側
ではなくて）中間外平歯車７側の歯数及び基準ピッチ円
が相違するように構成したものである。Next, FIG. 3 shows another embodiment, in which the teeth on the side of the intermediate outer spur gear 7 (instead of on the side of the first variable speed internal spur gear 9 and the second variable speed internal spur gear 10) in the embodiment of FIG. The number and the reference pitch circle are different.
【００２９】即ち、図３の変速機では、図１と同様構成
の入力軸１、出力軸２、入力遊星第一外平歯車３、入力
遊星第二外平歯車４、出力遊星第一外平歯車５、出力遊
星第二外平歯車６及び変速手段11の他に、入力遊星第一
外平歯車３と噛合すると共に入力回転軸心Ａを中心とし
て回転自在な中間第一外平歯車21と、出力遊星第一外平
歯車５と噛合すると共に入力回転軸心Ａを中心として回
転自在な中間第二外平歯車22と、回転体８と同軸Ａにて
一体回転すると共に入力遊星第二外平歯車４と出力遊星
第二外平歯車６に夫々噛合する変速内平歯車23と、を備
え、中間第一外平歯車21の歯数及び基準ピッチ円を、中
間第二外平歯車22の歯数及び基準ピッチ円に対して僅か
に相違させている。この場合も各歯車の転位量はゼロで
ある。That is, in the transmission of FIG. 3, the input shaft 1, the output shaft 2, the input planetary first outer spur gear 3, the input planetary second outer spur gear 4, and the output planetary first outer spur of the same construction as in FIG. In addition to the gear 5, the output planetary second external spur gear 6 and the speed changing means 11, an intermediate first external spur gear 21 which meshes with the input planetary first external spur gear 3 and is rotatable about the input rotation axis A. , An intermediate second outer spur gear 22 that meshes with the output planetary first outer spur gear 5 and is rotatable about the input rotation axis A, and rotates integrally with the rotating body 8 coaxially with the rotating body 8 and simultaneously with the input planetary second outer spur gear. The spur gear 4 and the variable speed internal spur gear 23 that mesh with the output planetary second outer spur gear 6, respectively, are provided, and the number of teeth and the reference pitch circle of the intermediate first outer spur gear 21 are The number of teeth and the reference pitch circle are slightly different. In this case as well, the shift amount of each gear is zero.
【００３０】具体的には、変速内平歯車23は回転体８に
一体形成される。中間第一外平歯車21と中間第二外平歯
車22は、軸心方向に並ぶように一体形成され、入力軸１
と出力軸２に回転自在に枢支される。なお、入力軸１を
図１のように構成して、該入力軸１に、中間第一外平歯
車21と中間第二外平歯車22を、枢着するも自由である。Specifically, the variable speed spur gear 23 is formed integrally with the rotating body 8. The intermediate first external spur gear 21 and the intermediate second external spur gear 22 are integrally formed so as to be aligned in the axial direction, and the input shaft 1
And the output shaft 2 is rotatably supported. The input shaft 1 may be configured as shown in FIG. 1 and the intermediate first external spur gear 21 and the intermediate second external spur gear 22 may be pivotally attached to the input shaft 1.
【００３１】また、入力遊星第一外平歯車３と入力遊星
第二外平歯車４を対でもって、入力回転軸心Ａを中心と
する円周上に於て周方向等ピッチで配設すると共に、出
力遊星第一外平歯車５と出力遊星第二外平歯車６を対で
もって、入力回転軸心Ａを中心とする円周上に於て周方
向等ピッチで配設する。Further, the input planetary first external spur gear 3 and the input planetary second external spur gear 4 are arranged in pairs on the circumference centered on the input rotation axis A at equal pitches in the circumferential direction. At the same time, the output planetary first external spur gear 5 and the output planetary second external spur gear 6 are arranged in pairs on the circumference centered on the input rotation axis A at equal circumferential pitches.
【００３２】そして、入力軸１を所定速度で回転させた
状態として、回転体８を、入力軸１と同一の方向及び回
転速度で回転させれば、変速内平歯車23、入力遊星第一
外平歯車３、入力遊星第二外平歯車４、出力遊星第一外
平歯車５、出力遊星第二外平歯車６、中間第一外平歯車
21、中間第二外平歯車22が全てロック状態となって、入
力遊星第一外平歯車３、入力遊星第二外平歯車４、出力
遊星第一外平歯車５、出力遊星第二外平歯車６は自転を
起こさずに、入力回転軸心Ａ廻りに一体に（入力軸１と
同一回転方向へ）回転（公転）する。従って、出力軸２
は入力軸１と同一回転数となる。When the input shaft 1 is rotated at a predetermined speed and the rotating body 8 is rotated in the same direction and at the same rotation speed as the input shaft 1, the internal spur gear 23 of the variable speed transmission and the first planetary outside of the input planetary gear are rotated. Spur gear 3, input planet second outer spur gear 4, output planet first outer spur gear 5, output planet second outer spur gear 6, intermediate first outer spur gear
21 and the intermediate second external spur gear 22 are all locked, and the input planetary first external spur gear 3, the input planetary second external spur gear 4, the output planetary first external spur gear 5, the output planetary second external spur gear The gear 6 rotates (revolves) integrally (in the same rotation direction as the input shaft 1) around the input rotation axis A without causing rotation. Therefore, output shaft 2
Is the same as the input shaft 1.
【００３３】この状態から、回転体８の回転を変速手段
11にて入力軸１の回転よりも遅らせていくと、両者８，
１の回転速度差により、入力遊星第一外平歯車３、入力
遊星第二外平歯車４が自転を始めると共に、中間第一外
平歯車21、中間第二外平歯車22を介して、出力遊星第一
外平歯車５、出力遊星第二外平歯車６が自転して、出力
遊星第一外平歯車５、出力遊星第二外平歯車６の公転
（即ち出力軸２の回転）が入力軸１よりも遅くなり、つ
いには出力軸２の回転が停止する。From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 11, both 8 and
Due to the rotational speed difference of 1, the input planetary first outer spur gear 3 and the input planetary second outer spur gear 4 start to rotate, and output through the intermediate first outer spur gear 21 and the intermediate second outer spur gear 22. The planetary first outer spur gear 5 and the output planetary second outer spur gear 6 rotate, and the revolutions of the output planetary first outer spur gear 5 and the output planetary second outer spur gear 6 (that is, the rotation of the output shaft 2) are input. It becomes slower than the shaft 1, and finally the output shaft 2 stops rotating.
【００３４】このようにして、変速手段11にて回転体８
の回転速度を変化させるだけで、全域定出力で出力軸２
の無段変速が行える。しかも、出力軸２のゼロ回転は、
入力軸１を回転させる原動機の回転数に関係なく得られ
て、原動機の回転力により保障され、閉ループである。In this way, the rotating body 8 is moved by the transmission means 11.
Simply by changing the rotation speed of the
Can be continuously variable. Moreover, the zero rotation of the output shaft 2 is
It is obtained regardless of the number of revolutions of the prime mover that rotates the input shaft 1, is guaranteed by the rotational force of the prime mover, and is a closed loop.
【００３５】この図３の実施例では、中間第一外平歯車
21と中間第二外平歯車22の基準ピッチ円を僅かに相違さ
せることにより、その周速度、角速度及び通過する歯数
に違いがでてくるという事を利用し、かつ、中間第一外
平歯車21と中間第二外平歯車22の歯数を僅かに相違させ
ることにより、その干渉する力を利用して、トルクを発
生させ、変速力を取り出すことができる。In the embodiment of FIG. 3, the intermediate first external spur gear is used.
21 and the intermediate second external spur gear 22 are slightly different from each other in the reference pitch circle, so that the peripheral speed, the angular speed, and the number of passing teeth are different, and the intermediate first external spur gear is used. By slightly differentiating the number of teeth of the gear 21 and the intermediate second external spur gear 22, torque can be generated by utilizing the interfering force, and the transmission force can be taken out.
【００３６】なお、中間第一外平歯車21と中間第二外平
歯車22の歯数を同一とすると、出力軸２と入力軸１の回
転速度が常に同一となって、変速しなくなる。また、中
間第一外平歯車21の歯数を中間第二外平歯車22の歯数の
１／２にすると、いわゆる「すべり」が発生して出力軸
２が常に回転しなくなる。If the intermediate first external spur gear 21 and the intermediate second external spur gear 22 have the same number of teeth, the rotational speeds of the output shaft 2 and the input shaft 1 are always the same, and gear shifting is not possible. Further, when the number of teeth of the intermediate first external spur gear 21 is set to 1/2 of the number of teeth of the intermediate second external spur gear 22, so-called "slip" occurs and the output shaft 2 does not always rotate.
【００３７】次に、図４と図５は別の実施例で、図１の
実施例における入力遊星第一外平歯車３、入力遊星第二
外平歯車４、出力遊星第一外平歯車５、出力遊星第二外
平歯車６等を、他の歯車で置き換えて構成したものであ
る。Next, FIG. 4 and FIG. 5 show another embodiment, which is the input planetary first external spur gear 3, the input planetary second external spur gear 4, and the output planetary first external spur gear 5 in the embodiment of FIG. The output planetary second outer spur gear 6 and the like are replaced with other gears.
【００３８】即ち、図４の変速機では、図１と同様構成
の中間外平歯車７及び変速手段11の他に、入力軸１に形
成された偏心軸部24にその偏心軸心Ｈを中心として回転
（自転）自在に枢着される入力外平歯車25と、入力外平
歯車25と同軸Ｈにて一体回転すると共に中間外平歯車７
と噛合する入力内平歯車26と、出力軸２に形成された偏
心軸部27にその偏心軸心Ｉを中心として回転（自転）自
在に枢着される出力外平歯車28と、出力外平歯車28と同
軸Ｉにて一体回転すると共に中間外平歯車７と噛合する
出力内平歯車29と、回転体８と同軸Ａにて一体回転する
と共に入力外平歯車25と噛合する変速第一内平歯車30
と、回転体８と同軸Ａにて一体回転すると共に出力外平
歯車28と噛合する変速第二内平歯車31と、を備え、変速
第一内平歯車30の歯数及び基準ピッチ円を、変速第二内
平歯車31の歯数及び基準ピッチ円に対して、僅かに相違
させている。この場合も各歯車の転位量はゼロである。That is, in the transmission shown in FIG. 4, in addition to the intermediate external spur gear 7 and the transmission means 11 having the same construction as in FIG. 1, the eccentric shaft center H is centered on the eccentric shaft portion 24 formed on the input shaft 1. The external spur gear 25, which is rotatably (rotatably) pivoted as a unit, rotates integrally with the external spur gear 25 coaxially with the external spur gear 25, and the intermediate external spur gear 7
An input inner spur gear 26, an output outer spur gear 28 pivotally attached to an eccentric shaft portion 27 formed on the output shaft 2 so as to rotate (rotate) about the eccentric shaft center I, and an output outer spur gear. An output inner spur gear 29 that rotates integrally with the gear 28 on the same axis I and meshes with the intermediate outer spur gear 7; Spur gear 30
And a speed-changing second internal spur gear 31 that rotates integrally with the rotor 8 coaxially with the output outer spur gear 28 and that has the number of teeth of the speed-changing first internal spur gear 30 and a reference pitch circle. The number of teeth of the variable speed second internal spur gear 31 and the reference pitch circle are slightly different. In this case as well, the shift amount of each gear is zero.
【００３９】具体的には、変速第一内平歯車30と変速第
二内平歯車31は回転体８に一体形成される。入力外平歯
車25と入力内平歯車26は、軸心方向に並ぶように一体形
成され、入力回転軸心Ａ廻りに偏心回転自在とされる。
出力外平歯車28と出力内平歯車29も、軸心方向に並ぶよ
うに一体形成され、入力回転軸心Ａ廻りに偏心回転自在
とされる。偏心軸心Ｉ，Ｈは、入力回転軸心Ａと平行と
される。Specifically, the first variable speed internal spur gear 30 and the second variable speed internal spur gear 31 are formed integrally with the rotor 8. The input outer spur gear 25 and the input inner spur gear 26 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A.
The output outer spur gear 28 and the output inner spur gear 29 are integrally formed so as to be aligned in the axial direction, and are eccentrically rotatable about the input rotation axis A. The eccentric shaft centers I and H are parallel to the input rotation shaft center A.
【００４０】そして、入力軸１を所定速度で回転させた
状態として、回転体８を、入力軸１と同一の方向及び回
転速度で回転させれば、変速第一内平歯車30、入力外平
歯車25、入力内平歯車26、中間外平歯車７、出力内平歯
車29、出力外平歯車28、変速第二内平歯車31が全てロッ
ク状態となって、入力外平歯車25、入力内平歯車26、出
力内平歯車29、出力外平歯車28は自転を起こさずに、入
力回転軸心Ａ廻りに一体に（入力軸１と同一回転方向
へ）回転する。従って、出力軸２は入力軸１と同一回転
数となる。When the input shaft 1 is rotated at a predetermined speed and the rotating body 8 is rotated in the same direction and at the same rotation speed as the input shaft 1, the variable speed first internal spur gear 30 and the input external spur gear 30 are rotated. The gear 25, the input inner spur gear 26, the intermediate outer spur gear 7, the output inner spur gear 29, the output outer spur gear 28, and the second speed change inner spur gear 31 are all in the locked state, and the input outer spur gear 25 and the inner input spur gear The spur gear 26, the output inner spur gear 29, and the output outer spur gear 28 rotate integrally around the input rotation axis A (in the same rotation direction as the input shaft 1) without causing rotation. Therefore, the output shaft 2 has the same rotation speed as the input shaft 1.
【００４１】この状態から、回転体８の回転を変速手段
11にて入力軸１の回転よりも遅らせていくと、両者８，
１の回転速度差により、入力外平歯車25、入力内平歯車
26が自転を始めると共に、中間外平歯車７を介して、出
力内平歯車29、出力外平歯車28が自転して、出力内平歯
車29、出力外平歯車28の偏心回転（即ち出力軸２の回
転）が入力軸１よりも遅くなり、ついには出力軸２の回
転が停止する。From this state, the rotation of the rotating body 8 is changed by the speed changing means.
When it is delayed from the rotation of the input shaft 1 at 11, both 8 and
Input external spur gear 25, input internal spur gear
When 26 starts to rotate, the output inner spur gear 29 and the output outer spur gear 28 rotate by way of the intermediate outer spur gear 7, and the eccentric rotation of the output inner spur gear 29 and the output outer spur gear 28 (that is, the output shaft). 2 rotation) becomes slower than that of the input shaft 1, and finally the rotation of the output shaft 2 stops.
【００４２】このようにして、変速手段11にて回転体８
の回転速度を変化させるだけで、全域定出力で出力軸２
の無段変速が行える。しかも、出力軸２のゼロ回転は、
入力軸１を回転させる原動機の回転数に関係なく得られ
て、原動機の回転力により保障され、閉ループである。In this way, the transmission 8 is rotated by the transmission means 11.
Simply by changing the rotation speed of the
Can be continuously variable. Moreover, the zero rotation of the output shaft 2 is
It is obtained regardless of the number of revolutions of the prime mover that rotates the input shaft 1, is guaranteed by the rotational force of the prime mover, and is a closed loop.
【００４３】この図４の実施例では、変速第一内平歯車
30と変速第二内平歯車31の基準ピッチ円を僅かに相違さ
せることにより、その周速度、角速度及び通過する歯数
に違いがでてくるという事を利用し、かつ、変速第一内
平歯車30と変速第二内平歯車31の歯数を僅かに相違させ
ることにより、その干渉する力を利用して、トルクを発
生させ、変速力を取り出すことができる。In the embodiment of FIG. 4, the variable speed first internal spur gear is used.
By utilizing the fact that the reference pitch circles of 30 and the second internal spur gear 31 are slightly different, the peripheral speed, angular velocity, and the number of passing teeth are different. By slightly differentiating the number of teeth of the gear 30 and the speed-changing second internal spur gear 31, it is possible to generate torque by utilizing the interfering force and to extract the speed-changing force.
【００４４】なお、変速第一内平歯車30と変速第二内平
歯車31の歯数を同一とすると、出力軸２と入力軸１の回
転速度が常に同一となって、変速しなくなる。また、変
速第一内平歯車30の歯数を変速第二内平歯車31の歯数の
１／２にすると、いわゆる「すべり」が発生して出力軸
２が常に回転しなくなる。If the number of teeth of the first variable speed internal spur gear 30 is the same as the number of teeth of the second variable speed internal spur gear 31, the rotational speeds of the output shaft 2 and the input shaft 1 will always be the same, and no speed change will occur. When the number of teeth of the first variable speed internal spur gear 30 is set to 1/2 of the number of teeth of the second variable speed internal spur gear 31, so-called "slip" occurs and the output shaft 2 does not always rotate.
【００４５】本発明は上述の実施例に限定されず本発明
の要旨を逸脱しない範囲で設計変更自由である。例え
ば、入力遊星第一外平歯車３、入力遊星第二外平歯車
４、出力遊星第一外平歯車５、出力遊星第二外平歯車６
の個数の増減は自由である。さらに、各歯車の歯数の増
減も自由である。The present invention is not limited to the above-described embodiments, and design changes can be freely made without departing from the gist of the present invention. For example, the input planetary first external spur gear 3, the input planetary second external spur gear 4, the output planetary first external spur gear 5, the output planetary second external spur gear 6
The number of can be increased or decreased freely. Furthermore, the number of teeth of each gear can be freely increased or decreased.
【００４６】また、図１に於て、回転体８に変速第一内
平歯車９と変速第二内平歯車10を一体形成せずに、別体
の部品を相互に固着して一体化してもよい。同様に、図
３に於て、中間第一外平歯車21と中間第二外平歯車22、
回転体８と変速内平歯車23を、夫々一体形成せずに、別
体の部品を相互に固着して一体化してもよい。さらに、
図４に於て、変速第一内平歯車30と回転体８、変速第二
内平歯車31と回転体８、入力外平歯車25と入力内平歯車
26、出力外平歯車28と出力内平歯車29を、夫々一体形成
せずに、別体の部品を相互に固着して一体化してもよ
い。Further, in FIG. 1, the speed-changing first internal spur gear 9 and the speed-changing second internal spur gear 10 are not integrally formed on the rotating body 8, but separate components are fixed to each other and integrated. Good. Similarly, in FIG. 3, the intermediate first external spur gear 21 and the intermediate second external spur gear 22,
The rotating body 8 and the variable speed internal spur gear 23 may not be integrally formed, but separate parts may be fixed to each other and integrated. further,
In FIG. 4, the transmission first internal spur gear 30 and the rotating body 8, the transmission second inner spur gear 31 and the rotating body 8, the input outer spur gear 25 and the input inner spur gear.
26, the output outer spur gear 28 and the output inner spur gear 29 may not be integrally formed, but separate components may be fixed to each other and integrated.
【００４７】[0047]
【発明の効果】本発明は上述の如く構成されているの
で、次に記載するような著大な効果を奏する。Since the present invention is constructed as described above, it has the following great effects.
【００４８】本発明の変速機は、歯車等の簡単な形状・
構造の部品により構成されているので、取扱い操作及び
製作が容易である。さらに、変速手段11にて回転体８の
回転速度を変化させるだけで、出力軸２を無段階かつ全
域定出力で、所望回転数に変速することができる。しか
も、閉ループのため、歯車に反力が作用せず、噛合した
歯車を軽く回すことができる。また、各歯車を転移させ
る必要がないため、強度不足とならず、耐久性が良い。The transmission of the present invention has a simple shape such as a gear.
Since it is composed of structural parts, it is easy to handle and manufacture. Further, by simply changing the rotation speed of the rotating body 8 by the speed changing means 11, the output shaft 2 can be speed-changed to a desired rotation speed in a stepless and constant output range. Moreover, because of the closed loop, the reaction force does not act on the gear, and the meshed gear can be turned lightly. Further, since it is not necessary to transfer each gear, strength is not insufficient and durability is good.
【００４９】また、請求項３記載の変速機では、入力遊
星第一外平歯車３及び入力遊星第二外平歯車４と、出力
遊星第一外平歯車５及び出力遊星第二外平歯車６と、に
対して、夫々、ウエイトバランス（錘）等によるバラン
シングが不要となって、変速機全体の動的バランスが良
くなり、回転時の振動を抑えることができる。In the transmission according to the third aspect, the input planetary first external spur gear 3 and the input planetary second external spur gear 4, the output planetary first external spur gear 5, and the output planetary second external spur gear 6 are provided. On the other hand, balancing by weight balance (weight) or the like becomes unnecessary, the dynamic balance of the entire transmission is improved, and vibration during rotation can be suppressed.
【図１】本発明の一実施例を示す断面側面図である。FIG. 1 is a sectional side view showing an embodiment of the present invention.
【図２】歯車の位置関係を示す簡略正面図である。FIG. 2 is a simplified front view showing the positional relationship of gears.
【図３】他の実施例を示す断面側面図である。FIG. 3 is a sectional side view showing another embodiment.
【図４】別の実施例を示す断面側面図である。FIG. 4 is a sectional side view showing another embodiment.
【図５】歯車の位置関係を示す簡略正面図である。FIG. 5 is a simplified front view showing the positional relationship of gears.
１ 入力軸 ２ 出力軸 ３ 入力遊星第一外平歯車 ４ 入力遊星第二外平歯車 ５ 出力遊星第一外平歯車 ６ 出力遊星第二外平歯車 ７ 中間外平歯車 ８ 回転体 ９ 変速第一内平歯車 10 変速第二内平歯車 11 変速手段 21 中間第一外平歯車 22 中間第二外平歯車 23 変速内平歯車 24 偏心軸部 25 入力外平歯車 26 入力内平歯車 27 偏心軸部 28 出力外平歯車 29 出力内平歯車 30 変速第一内平歯車 31 変速第二内平歯車 Ａ 入力回転軸心 Ｂ 軸心 Ｃ 軸心 Ｅ 軸心 Ｇ 軸心 Ｉ 偏心軸心 Ｈ 偏心軸心 1 Input Shaft 2 Output Shaft 3 Input Planet 1st Outer Spur Gear 4 Input Planet 2nd Outer Spur Gear 5 Output Planet 1st Outer Spur Gear 6 Output Planet 2nd Outer Spur Gear 7 Intermediate Outer Spur Gear 8 Rotating Body 9 Speed 1st Inner spur gear 10 Speed change second inner spur gear 11 Speed change means 21 Middle first outer spur gear 22 Middle second outer spur gear 23 Speed change inner spur gear 24 Eccentric shaft 25 Input outer spur gear 26 Input inner spur gear 27 Eccentric shaft 28 Output outer spur gear 29 Output inner spur gear 30 Speed change first inner spur gear 31 Speed change second inner spur gear A Input rotation shaft center B shaft center C shaft center E shaft center G shaft center I Eccentric shaft center H Eccentric shaft center
Claims (4)
力回転軸心Ａと同軸で回転自在な出力軸２と、該入力軸
１に上記入力回転軸心Ａと平行な軸心Ｂを中心として回
転自在に枢着されて該入力回転軸心Ａ廻りに公転自在な
入力遊星第一外平歯車３と、該入力軸１に上記入力回転
軸心Ａと平行な軸心Ｃを中心として回転自在に枢着され
て該入力回転軸心Ａ廻りに公転自在であると共に入力遊
星第一外平歯車３と噛合する入力遊星第二外平歯車４
と、上記出力軸２に上記入力回転軸心Ａと平行な軸心Ｅ
を中心として回転自在に枢着されて該入力回転軸心Ａ廻
りに公転自在な出力遊星第一外平歯車５と、該出力軸２
に上記入力回転軸心Ａと平行な軸心Ｇを中心として回転
自在に枢着されて該入力回転軸心Ａ廻りに公転自在であ
ると共に上記出力遊星第一外平歯車５と噛合する出力遊
星第二外平歯車６と、上記入力遊星第一外平歯車３と出
力遊星第一外平歯車５に夫々噛合すると共に上記入力回
転軸心Ａを中心として回転自在な中間外平歯車７と、上
記入力回転軸心Ａと同軸にて上記入力軸１と相対回転自
在な回転体８と、該回転体８と同軸Ａにて一体回転する
と共に上記入力遊星第二外平歯車４と噛合する変速第一
内平歯車９と、該回転体８と同軸Ａにて一体回転すると
共に上記出力遊星第二外平歯車６と噛合する変速第二内
平歯車10と、上記回転体８の回転速度を変化させる変速
手段11と、を備え、上記変速第一内平歯車９と変速第二
内平歯車10の歯数及び基準ピッチ円を僅かに相違させた
ことを特徴とする変速機。1. An input shaft 1 which is rotatable, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, and an axis parallel to the input rotation axis A on the input shaft 1. An input planetary first external spur gear 3 which is rotatably pivoted about B and is revolvable around the input rotation axis A, and an axis C parallel to the input rotation axis A on the input shaft 1. An input planetary second external spur gear 4 which is rotatably pivoted as a center, is revolvable around the input rotation axis A, and meshes with the input planetary first external spur gear 3.
And the output shaft 2 has an axis E parallel to the input rotation axis A.
An output planetary first external spur gear 5 that is rotatably pivoted about the input rotation axis A and is revolvable around the input rotation axis A, and the output shaft 2
An output planet which is rotatably pivoted about an axis G parallel to the input rotation axis A, is revolvable around the input rotation axis A, and meshes with the output planetary first spur gear 5. A second outer spur gear 6, an intermediate outer spur gear 7 that meshes with the input planetary first outer spur gear 3 and the output planetary first outer spur gear 5, respectively, and is rotatable about the input rotation axis A; A rotating body 8 which is rotatable relative to the input shaft 1 coaxially with the input rotating shaft A, and a gear shift which rotates integrally with the rotating body 8 coaxially with the rotating body 8 and meshes with the input planetary second external spur gear 4. The rotation speed of the first internal spur gear 9, the variable speed second internal spur gear 10 that rotates integrally with the rotating body 8 coaxially A and meshes with the output planetary second outer spur gear 6, and the rotating speed of the rotating body 8 are described below. And a speed change means (11) for changing the number of teeth of the speed change first internal spur gear (9) and the speed change second internal spur gear (10). Transmission, wherein a reference pitch circle were slightly different.
力回転軸心Ａと同軸で回転自在な出力軸２と、該入力軸
１に上記入力回転軸心Ａと平行な軸心Ｂを中心として回
転自在に枢着されて該入力回転軸心Ａ廻りに公転自在な
入力遊星第一外平歯車３と、該入力軸１に上記入力回転
軸心Ａと平行な軸心Ｃを中心として回転自在に枢着され
て該入力回転軸心Ａ廻りに公転自在であると共に上記入
力遊星第一外平歯車３と噛合する入力遊星第二外平歯車
４と、上記出力軸２に上記入力回転軸心Ａと平行な軸心
Ｅを中心として回転自在に枢着されて該入力回転軸心Ａ
廻りに公転自在な出力遊星第一外平歯車５と、該出力軸
２に上記入力回転軸心Ａと平行な軸心Ｇを中心として回
転自在に枢着されて該入力回転軸心Ａ廻りに公転自在で
あると共に上記出力遊星第一外平歯車５と噛合する出力
遊星第二外平歯車６と、上記入力遊星第一外平歯車３と
噛合すると共に上記入力回転軸心Ａを中心として回転自
在な中間第一外平歯車21と、上記出力遊星第一外平歯車
５と噛合すると共に上記入力回転軸心Ａを中心として回
転自在な中間第二外平歯車22と、上記入力回転軸心Ａと
同軸にて上記入力軸１と相対回転自在な回転体８と、該
回転体８と同軸Ａにて一体回転すると共に上記入力遊星
第二外平歯車４と出力遊星第二外平歯車６に夫々噛合す
る変速内平歯車23と、上記回転体８の回転速度を変化さ
せる変速手段11と、を備え、中間第一外平歯車21と中間
第二外平歯車22の歯数及び基準ピッチ円を僅かに相違さ
せたことを特徴とする変速機。2. An input shaft 1 which is rotatable, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, and an axis which is parallel to the input rotation axis A on the input shaft 1. An input planetary first external spur gear 3 which is rotatably pivoted about B and is revolvable around the input rotation axis A, and an axis C parallel to the input rotation axis A on the input shaft 1. An input planetary second external spur gear 4 which is rotatably pivoted as a center, is revolvable around the input rotation axis A, and meshes with the input planetary first external spur gear 3, and the output shaft 2 is The input rotation axis A is rotatably pivoted about an axis E parallel to the input rotation axis A.
An output planetary first external spur gear 5 that is freely revolvable around it, and is rotatably attached to the output shaft 2 about an axis G parallel to the input rotation axis A, and is rotated around the input rotation axis A. The output planetary second external spur gear 6 which is revolvable and meshes with the output planetary first outer spur gear 5, and the input planetary first outer spur gear 3 meshes and rotates about the input rotation axis A. A free intermediate first external spur gear 21, an intermediate second external spur gear 22 which meshes with the output planetary first external spur gear 5 and is rotatable around the input rotational axis A, and the input rotational axis A rotating body 8 which is rotatable relative to the input shaft 1 coaxially with A, rotates integrally with the rotating body 8 coaxially with the rotating body 8, and also has the input planetary second external spur gear 4 and the output planetary second external spur gear 6 An internal variable speed spur gear 23 meshing with each other, a speed change means 11 for changing the rotational speed of the rotating body 8, Provided, the transmission, characterized in that the number of teeth and the reference pitch circle of the intermediate first Hokahira gear 21 and the intermediate second Hokahira gear 22 is slightly different.
遊星第二外平歯車４…を、入力回転軸心Ａを中心とする
円周上に於て周方向等ピッチで配設すると共に、複数の
出力遊星第一外平歯車５…及び出力遊星第二外平歯車６
…を、入力回転軸心Ａを中心とする円周上に於て周方向
等ピッチで配設した請求項１又は２記載の変速機。3. A plurality of input planetary first external spur gears 3 ... and a plurality of input planetary second external spur gears 4 ... Are arranged on the circumference centered on the input rotation axis A at equal circumferential pitches. And a plurality of output planetary first external spur gears 5 ... and output planetary second external spur gears 6
3. The transmission according to claim 1 or 2, wherein ... are arranged at equal pitches in a circumferential direction on a circumference centered on the input rotation axis A.
力回転軸心Ａと同軸で回転自在な出力軸２と、上記入力
軸１に形成された偏心軸部24にその偏心軸心Ｈを中心と
して回転自在に枢着されて上記入力回転軸心Ａ廻りに偏
心回転する入力外平歯車25と、該入力外平歯車25と同軸
Ｈにて一体回転して上記入力回転軸心Ａ廻りに偏心回転
する入力内平歯車26と、上記出力軸２に形成された偏心
軸部27にその偏心軸心Ｉを中心として回転自在に枢着さ
れて上記入力回転軸心Ａ廻りに偏心回転する出力外平歯
車28と、該出力外平歯車28と同軸Ｉにて一体回転して上
記入力回転軸心Ａ廻りに偏心回転する出力内平歯車29
と、上記入力内平歯車26と出力内平歯車29に夫々噛合す
ると共に上記入力回転軸心Ａを中心として回転自在な中
間外平歯車７と、上記入力回転軸心Ａと同軸にて上記入
力軸１と相対回転自在な回転体８と、該回転体８と同軸
Ａにて一体回転すると共に上記入力外平歯車25と噛合す
る変速第一内平歯車30と、該回転体８と同軸Ａにて一体
回転すると共に上記出力外平歯車28と噛合する変速第二
内平歯車31と、上記回転体８の回転速度を変化させる変
速手段11と、を備え、上記変速第一内平歯車30と変速第
二内平歯車31の歯数及び基準ピッチ円を僅かに相違させ
たことを特徴とする変速機。4. An input shaft 1 which is rotatable, an output shaft 2 which is rotatable coaxially with an input rotation axis A of the input shaft 1, an eccentric shaft portion 24 formed on the input shaft 1, and an eccentric shaft thereof. An input external spur gear 25, which is rotatably pivoted about a center H and eccentrically rotates around the input rotation shaft center A, and the input outer spur gear 25 is integrally rotated coaxially with the input external spur gear 25 to integrally rotate the input rotation shaft center. An input internal spur gear 26 that rotates eccentrically around A, and an eccentric shaft portion 27 formed on the output shaft 2 are rotatably attached about the eccentric shaft center I and are eccentric around the input rotation shaft A. A rotating output spur gear 28 and an output spur gear 29 that rotates integrally with the output spur gear 28 coaxially with the output outer spur gear 28 and eccentrically rotates around the input rotation axis A.
An intermediate outer spur gear 7 that meshes with the input inner spur gear 26 and the output inner spur gear 29, respectively, and is rotatable about the input rotation axis A, and the input coaxial with the input rotation axis A. A rotating body 8 rotatable relative to the shaft 1, a first variable speed internal spur gear 30 that integrally rotates with the rotating body 8 at the same axis A and meshes with the input outer spur gear 25, and a coaxial body A with the rotating body 8. And a transmission means 11 for changing the rotation speed of the rotating body 8 and a transmission first internal spur gear 30. And a second transmission internal spur gear 31 having a slightly different number of teeth and a reference pitch circle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6126784A JP2798607B2 (en) | 1994-05-16 | 1994-05-16 | transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6126784A JP2798607B2 (en) | 1994-05-16 | 1994-05-16 | transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07310805A true JPH07310805A (en) | 1995-11-28 |
| JP2798607B2 JP2798607B2 (en) | 1998-09-17 |
Family
ID=14943859
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6126784A Expired - Lifetime JP2798607B2 (en) | 1994-05-16 | 1994-05-16 | transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2798607B2 (en) |
-
1994
- 1994-05-16 JP JP6126784A patent/JP2798607B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JP2798607B2 (en) | 1998-09-17 |
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| EXPY | Cancellation because of completion of term |