JPH0260904B2 - - Google Patents
Info
- Publication number
- JPH0260904B2 JPH0260904B2 JP57053249A JP5324982A JPH0260904B2 JP H0260904 B2 JPH0260904 B2 JP H0260904B2 JP 57053249 A JP57053249 A JP 57053249A JP 5324982 A JP5324982 A JP 5324982A JP H0260904 B2 JPH0260904 B2 JP H0260904B2
- Authority
- JP
- Japan
- Prior art keywords
- cylindrical body
- outer cylindrical
- input shaft
- rolling mechanism
- inner cylindrical
- 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.)
- Expired - Lifetime
Links
- 238000005096 rolling process Methods 0.000 claims description 15
- 239000000463 material Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H49/00—Other gearings
- F16H49/001—Wave gearings, e.g. harmonic drive transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H49/00—Other gearings
- F16H2049/006—Wave generators producing a non-elliptical shape of flexsplines, i.e. with a qualified different shape than elliptical
Description
【発明の詳細な説明】
この発明は、車輪用ワイパーモータやサーボモ
ータ等の小型モータに使用される減速装置に関す
るものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a speed reduction device used in a small motor such as a wheel wiper motor or a servo motor.
従来、減速装置には、歯車減速機、ウオーム減
速機、遊星歯車減速機等、主に歯車の組み合わせ
を利用したもの、ハーモニツクドライブ装置のよ
うに弾性体歯車を利用した減速装置、あるいは油
圧等を利用した液圧減速装置等が知られている。 Conventionally, reduction gears include gear reduction gears, worm reduction gears, planetary gear reduction gears, etc. that mainly use a combination of gears, harmonic drive devices that use elastic gears, or hydraulic reduction devices. Hydraulic pressure reduction devices and the like are known.
しかしながら、歯車減速機は、高減速する場合
に歯車段数が多くなり大型になるとともにコスト
高になる等の欠点がある。 However, gear reduction gears have drawbacks such as increasing the number of gear stages for high speed reduction, resulting in large size and high cost.
また、高速回転ではバツクラツシユによる騒音
が大きくなり、しかも歯車列による多段減速では
機械効率が低下するという難点がある。殊にウオ
ーム減速機では高速回転による音は静かである
が、機械効率が極めて低く50％以下である。 In addition, high-speed rotation increases noise due to backlash, and multi-stage reduction using a gear train reduces mechanical efficiency. In particular, worm reducers are quiet due to high-speed rotation, but their mechanical efficiency is extremely low, below 50%.
また、ハーモニツクドライブ装置では、高減速
を要する場合は２段〜３段に増す必要があり、機
構が複雑となりコスト高になる欠点がある。 Further, in the harmonic drive device, when high deceleration is required, it is necessary to increase the number of stages to two to three stages, which has the drawback of making the mechanism complicated and increasing costs.
さらに、液圧減速機では、全効率が極めて低
く、パワー損失が大きいという欠点をもつてい
る。 Additionally, hydraulic speed reducers have the disadvantage of extremely low overall efficiency and large power losses.
この発明は、上述した問題を解決するためにな
されたものであつて、歯車や液圧等を使用せず、
外側円筒体と、該外側円筒体の内側に配置され外
側円筒体の内径より小なる外径を有し、かつ半径
方向に撓み変形し得るように薄肉剛性材料で成形
された内側筒体と該内側筒体の内周に設けられ、
前記内側筒体を少なくとも１箇所で外側円筒体に
強制摩擦内接させた状態で、その内接点を移動回
転させる弾性体からなる転がり機構と、該転がり
機構を駆動するための入力軸と、前記転がり機構
における前記内接点の位置決めを行ない前記入力
軸を取り囲んで該入力軸と一体に回転する持受体
とで構成することにより、高速回転でも騒音の発
生が少なく高減速が得られるようにしたものであ
る。 This invention was made to solve the above-mentioned problems, and does not use gears or hydraulic pressure, etc.
an outer cylindrical body, an inner cylindrical body disposed inside the outer cylindrical body, having an outer diameter smaller than the inner diameter of the outer cylindrical body, and formed of a thin rigid material so as to be deformable in the radial direction; Provided on the inner periphery of the inner cylinder,
a rolling mechanism made of an elastic body that moves and rotates the inner cylindrical body in a state in which the inner cylindrical body is forcedly frictionally inscribed with the outer cylindrical body at at least one point; an input shaft for driving the rolling mechanism; By positioning the internal contact point in the rolling mechanism and configuring it with a supporting body that surrounds the input shaft and rotates integrally with the input shaft, high deceleration can be obtained with little noise even during high speed rotation. It is something.
以下、この発明を、その実施例を示した添付図
面に基づいて詳細に説明する。 Hereinafter, the present invention will be described in detail based on the accompanying drawings showing embodiments thereof.
第１図ないし第２図は、この発明の一実施例に
よる原理構成図であつて、入力軸１は回転軸中心
ｏよりｅだけ偏心したクランク軸１ａをもつてい
る。 FIGS. 1 and 2 are diagrams showing the basic structure of an embodiment of the present invention, in which an input shaft 1 has a crankshaft 1a eccentric from the center o of the rotating shaft by an amount e.
前記入力軸１のクランク軸１ａには転がり機構
の機能を有する加圧ローラ２が回転自在に嵌装さ
れ、薄肉内側筒体３の内周面に所定の加圧力で内
接している。 A pressure roller 2 having a function of a rolling mechanism is rotatably fitted to the crankshaft 1a of the input shaft 1, and is inscribed in the inner peripheral surface of the thin inner cylinder 3 with a predetermined pressure.
前記加圧ローラ２は、薄肉内側筒体３の内周面
に所定の摩擦圧力を保持するために弾性体で成形
され、弾性限界内で応力を生させた状態で組付け
られ、薄肉内側筒体３は加圧ローラ２によつて弾
性限界内で歪みを生じても破損しない適当な肉厚
に成形されている。 The pressure roller 2 is formed of an elastic body in order to maintain a predetermined friction pressure on the inner peripheral surface of the thin inner cylinder 3, and is assembled in a state where stress is generated within the elastic limit. The body 3 is formed to have an appropriate thickness so that it will not break even if it is distorted by the pressure roller 2 within its elastic limit.
また、前記内側筒体３には回転軸中心上に出力
軸４が一体に固着され、内側筒体３の外側には、
内側筒体３の外径よりも僅かに大きい内径を有す
る外側円筒体５が、内側筒体３の出力軸４と同心
に配設され、その内面に内側筒体３がその撓み部
分で内接されている。 Further, an output shaft 4 is integrally fixed to the inner cylinder 3 on the center of the rotation axis, and on the outside of the inner cylinder 3,
An outer cylindrical body 5 having an inner diameter slightly larger than the outer diameter of the inner cylindrical body 3 is disposed concentrically with the output shaft 4 of the inner cylindrical body 3, and the inner cylindrical body 3 is inscribed in its inner surface with its flexible portion. has been done.
ここで、前記入力軸１を回転させると、この入
力軸１に偏心して取付けられた加圧ローラ２が外
側円筒体５の内周面に内側筒体３を所定の摩擦圧
力で押し付けながら自転および公転する。このと
き、内側筒体３の外径と外側円筒体５の内径との
径差に円周率を乗じた値だけ回転ずれが生じるの
で、これを連続回転させると内側筒体３と外側円
筒体５との間に回転差が生じる。つまり、上述し
た構成において、内側筒体３の外径をR1、外側
円筒体５の内径をR2とし、仮に入力軸１を固定
として外側円筒体５を１回転させると、内側筒体
３はR2／R1回同方向に回転する。また、加圧ロ
ーラ２が１回転公転すると内側筒体３はR2−
R1／R1回反対方向に回転する。 Here, when the input shaft 1 is rotated, the pressure roller 2 eccentrically attached to the input shaft 1 rotates and presses the inner cylinder 3 against the inner peripheral surface of the outer cylinder 5 with a predetermined friction pressure. revolve. At this time, a rotational deviation occurs by the value obtained by multiplying the diameter difference between the outer diameter of the inner cylinder 3 and the inner diameter of the outer cylinder 5 by pi, so if this is continuously rotated, the inner cylinder 3 and the outer cylinder There is a difference in rotation between 5 and 5. That is, in the above-mentioned configuration, if the outer diameter of the inner cylinder 3 is R 1 and the inner diameter of the outer cylinder 5 is R 2 , and if the input shaft 1 is fixed and the outer cylinder 5 is rotated once, then the inner cylinder 3 rotates R 2 /R once in the same direction. Moreover, when the pressure roller 2 revolves once, the inner cylinder 3 becomes R 2 −
R 1 /R Rotate once in the opposite direction.
したがつて、入力軸１と内側筒体３の出力軸４
との減速比は１：R2−R1／R1となり、加圧ローラ２
を高速で公転させると、外側円筒体５を固定した
場合、内側筒体３が出力側となり、また、内側筒
体３を固定した場合は、外側円筒体５が出力側と
なつて回転し、そこで外側円筒体５の内径と内側
筒体３の外径との差R2−R1が小さくなることに
より、減速比は極めて大きくなり、高減速が可能
となる。 Therefore, the input shaft 1 and the output shaft 4 of the inner cylinder 3
The reduction ratio is 1:R 2 −R 1 /R 1 , and when the pressure roller 2 is revolved at high speed, when the outer cylinder 5 is fixed, the inner cylinder 3 becomes the output side, and the inner cylinder When the body 3 is fixed, the outer cylindrical body 5 becomes the output side and rotates, and the difference R 2 - R 1 between the inner diameter of the outer cylindrical body 5 and the outer diameter of the inner cylindrical body 3 becomes smaller. The reduction ratio becomes extremely large, allowing for high speed reduction.
第３図ないし第４図は、この発明の他の実施例
による原理構成図を示したものであつて、入力軸
１０に回転自在に装着した持受体１１に例えば３
つの突軸１２が120度の中心角をもつて突設され、
各突軸１２に弾性体からなり、転がり機構の機能
を有する遊星輪１３が入力軸１０に圧接し、かつ
内側筒体１４に内接して自転しながら公転するよ
うに嵌装支持されている。 FIGS. 3 and 4 show the principle configuration diagrams according to other embodiments of the present invention, in which, for example, three
Two protruding shafts 12 are protruded with a central angle of 120 degrees,
A planetary wheel 13, which is made of an elastic body and has the function of a rolling mechanism, is in pressure contact with the input shaft 10 and inscribed in the inner cylindrical body 14, and is fitted and supported on each of the protruding shafts 12 so as to rotate and revolve.
前記内側筒体１４の外側には、その外径より僅
かに大きな外径を有する外側円筒体１５が同心に
配設され、前記内側筒体１４は３個の遊星輪１３
により、３点で外側円筒体１５に内接されてい
る。 An outer cylindrical body 15 having an outer diameter slightly larger than the outer diameter of the inner cylindrical body 14 is disposed concentrically on the outside of the inner cylindrical body 14 .
Therefore, it is inscribed in the outer cylindrical body 15 at three points.
ここで前記入力軸１０を回転させると、この入
力軸１０に圧接した３個の遊星輪１３は、それぞ
れ自転しながら内側筒体１４を弾性限界内で撓ま
せて外側円筒体１５に内接させ、その内接点を移
動させながら公転し、その運動において、外側円
筒体１５の内径と内側筒体１４の外径の径差に円
周率を乗じ、さらに遊星輪１３差動比を乗じた値
だけ回転ずれを生じる。これを連続的に回転し、
例えば外側円筒体１５を固定した場合、内側筒体
１４が出力軸となり、また内側筒体１４を固定し
た場合、外側円筒体１５が出力軸となる。 When the input shaft 10 is rotated, the three planetary wheels 13 pressed against the input shaft 10 bend the inner cylindrical body 14 within its elastic limit while rotating, and are inscribed in the outer cylindrical body 15. , revolves while moving its inner contact point, and during that movement, the value obtained by multiplying the diameter difference between the inner diameter of the outer cylindrical body 15 and the outer diameter of the inner cylindrical body 14 by pi, and further by the differential ratio of the planetary wheels 13. rotational deviation occurs. Rotate this continuously,
For example, when the outer cylindrical body 15 is fixed, the inner cylindrical body 14 becomes the output shaft, and when the inner cylindrical body 14 is fixed, the outer cylindrical body 15 becomes the output shaft.
つまり、入力軸１０の半径r1、内側筒体１４の
半径R1、外側円筒体１５の半径R2とし、入力軸
１０が一回転すると、内側筒体１４は
r1／R2−r1／R1／１＋r1／R2＝（R1−R2）／（R2＋r1）
・r1／R1
回反転するので、外側円筒体１５の内径R2と内
側筒体１４の半径R1との差R2−R1が小さければ
減速比は極めて大きくなり、高減速が可能とな
る。 In other words, if the radius r 1 of the input shaft 10, the radius R 1 of the inner cylindrical body 14, and the radius R 2 of the outer cylindrical body 15, when the input shaft 10 rotates once, the inner cylindrical body 14 becomes r 1 /R 2 - r 1 /R 1 /1 + r 1 /R 2 = (R 1 - R 2 ) / (R 2 + r 1 )
・Since r 1 /R is reversed once , if the difference R 2 - R 1 between the inner diameter R 2 of the outer cylindrical body 15 and the radius R 1 of the inner cylindrical body 14 is small, the reduction ratio becomes extremely large and high deceleration is possible. becomes.
なお、遊星輪１３は球体でも良いものである。 Note that the planet wheels 13 may be spherical.
第５図ないし第６図は、この発明による原理を
用いてワイパーモータ等に適用した場合を示した
ものであり、２０はモータ、２１はその回転軸、
２２は減速装置のケース本体である。前記ケース
本体２２には外側円筒体２３が固着されており、
この外側円筒体２３の内側に位置づけされた内側
筒体２４には、出力軸２５が一体に固着され、ケ
ース本体２２に軸受２６等を介して回転自在に装
置されている。また、前記内側筒体２４の内周面
にはモータ２０の回転軸２１の周囲に配設され、
回転軸２１にて回転させられる３個の遊星輪２７
がそれぞれ圧接しており、前記遊星輪２７の関係
位置は持受体２８により保持されて、回転軸２１
を中心に回転自在に装着されている。 5 and 6 show a case where the principle according to the present invention is applied to a wiper motor, etc., where 20 is the motor, 21 is its rotating shaft,
22 is a case body of the speed reduction device. An outer cylindrical body 23 is fixed to the case body 22,
An output shaft 25 is integrally fixed to the inner cylindrical body 24 positioned inside the outer cylindrical body 23, and is rotatably mounted on the case body 22 via a bearing 26 or the like. Further, on the inner peripheral surface of the inner cylindrical body 24, disposed around the rotating shaft 21 of the motor 20,
Three planetary wheels 27 rotated by the rotating shaft 21
are in pressure contact with each other, and the relative position of the planetary ring 27 is held by a supporter 28, and the rotation shaft 21
It is attached so that it can rotate freely around the center.
したがつて、モータ２０が回転すると、回転軸
２１により各遊星輪２７が内側筒体２４に圧接し
て自転しながら公転し、外側円筒体２３の内径と
内側筒体２４との径差による回転ずれを生じ、内
側筒体２４の出力軸２５に高減速された回転が伝
達されるようになつている。 Therefore, when the motor 20 rotates, each planetary ring 27 comes into pressure contact with the inner cylinder 24 by the rotating shaft 21 and revolves around its own axis, causing rotation due to the difference in diameter between the inner diameter of the outer cylinder 23 and the inner cylinder 24. A shift occurs, and highly decelerated rotation is transmitted to the output shaft 25 of the inner cylindrical body 24.
以上、詳細に説明したように、この発明による
減速装置は、外側円筒体と、該外側円筒体の内側
に配設され、外側円筒体の内径より小なる外径を
有し、かつ半径方向に撓み変形し得るように薄肉
剛性材料で成形された内側筒体と、該内側筒体の
円周に設けられ、前記内側筒体を少なくとも１箇
所で外側円筒体に強制摩擦内接させた状態で、そ
の内接点を移動回転させる加圧ローラ等の転がり
機構と、該転がり機構を駆動するための入力軸
と、前記転がり機構における前記内接点の位置決
めを行ない前記入力軸を取り囲んで該入力軸と一
体に回転する持受体とからなり、前記転がり機構
の回転により、内側筒体および外側円筒体のいず
れか一方を固定した場合に他方が回転し出力軸と
され、しかも内側筒体と外側円筒体との間に、両
筒体の径差による回転ずれを生じるよう構成され
ているので、入力軸の回転により、内側筒体また
は外側円筒体に高減速が得られ、歯車を全く使用
しない高効率な高減速機である。 As described above in detail, the speed reduction device according to the present invention includes an outer cylindrical body, is disposed inside the outer cylindrical body, has an outer diameter smaller than the inner diameter of the outer cylindrical body, and has a radial direction. an inner cylindrical body formed of a thin rigid material so as to be able to bend and deform; and a state in which the inner cylindrical body is provided on the circumference of the inner cylindrical body, and the inner cylindrical body is forcedly frictionally inscribed with the outer cylindrical body at at least one location. , a rolling mechanism such as a pressure roller that moves and rotates the inner contact point, an input shaft for driving the rolling mechanism, and a roller that positions the inner contact point in the rolling mechanism and surrounds the input shaft and connects the input shaft with the input shaft. The rotation of the rolling mechanism causes the other to rotate and serve as an output shaft when either the inner cylinder or the outer cylinder is fixed. Since the structure is configured so that a rotational misalignment occurs between the two cylinders due to the difference in diameter between the two cylinders, rotation of the input shaft provides high deceleration to the inner cylinder or outer cylinder. It is an efficient high reduction gear.
また、この発明による減速装置は、減速部分の
運転が転がり摩擦接触で、かつ一段減速により高
減速が得られるため、非常に高い機械効率があ
り、また転がり接触であるから、高速回転でも騒
音の発生が少なく、歯車機構のように背隙がない
ため、正転、逆転時の機械的遊びが皆無となる。 In addition, the reduction gear according to the present invention has a very high mechanical efficiency because the operation of the reduction part is rolling friction contact and high deceleration can be obtained by one-step reduction.Also, since it is rolling contact, it produces no noise even at high speed rotation. Since there are fewer occurrences and there is no back gap like in a gear mechanism, there is no mechanical play during forward or reverse rotation.
したがつて、この発明による減速装置は、小型
モータの減速機等に最適であり、特にワイパーモ
ータの減速に使用した場合、モータ回転数の大巾
な減少ができるとともに、反転音や回転音を低減
することができる。また、サーボモータ等に使用
した場合にもモータ出力が小さくできるとともに
正転、逆転によるヒスチリシスも皆無となり、高
性能な減速が得られる等の効果がある。 Therefore, the reduction gear according to the present invention is most suitable for reduction gears for small motors, etc., and especially when used to reduce the speed of wiper motors, it can significantly reduce the motor rotation speed and reduce reversal noise and rotation noise. can be reduced. Furthermore, when used in a servo motor or the like, the motor output can be reduced, there is no hysteresis due to forward or reverse rotation, and high-performance deceleration can be achieved.
第１図は、この発明の一実施例による基本原理
を示す減速機構の断面図、第２図は正面図、第３
図は他の実施例による基本原理を示す減速機構の
正面図、第４図は断面図、第５図はこの発明をワ
イパーモータに実施例した場合の減速装置の縦断
側面図、第６図は要部の断面図である。
１……入力軸、１ａ……クランタ軸、２……加
圧ローラ、３……内側筒体、４……出力軸、５…
…外側円筒体、２０……モータ、２１……回転
軸、２２……ケース本体、２３……外側円筒体、
２４……内側筒体、２５……出力軸、２６……軸
受、２７……遊星輪、２８……持受体。
FIG. 1 is a sectional view of a speed reduction mechanism showing the basic principle according to an embodiment of the present invention, FIG. 2 is a front view, and FIG.
The figure is a front view of a speed reduction mechanism showing the basic principle according to another embodiment, FIG. 4 is a cross-sectional view, FIG. FIG. 3 is a cross-sectional view of main parts. DESCRIPTION OF SYMBOLS 1...Input shaft, 1a...Clunter shaft, 2...Pressure roller, 3...Inner cylinder, 4...Output shaft, 5...
...Outer cylindrical body, 20...Motor, 21...Rotating shaft, 22...Case body, 23...Outer cylindrical body,
24... Inner cylindrical body, 25... Output shaft, 26... Bearing, 27... Planet wheel, 28... Holder.
Claims (1)
内径より少なる外径を有し、かつ半径方向に撓み
変形し得るように薄肉剛性材料で成形された内側
筒体と、 該内側筒体の内周に設けられ、前記内側筒体を
少なくとも１箇所で外側円筒体に強制摩擦内接さ
せた状態で、その内接点を移動回転させる弾性体
からなる転がり機構と、 該転がり機構を駆動するための入力軸と、 前記転がり機構における前記内接点の位置決め
を行ない前記入力軸を取り囲んで該入力軸と一体
に回転する持受体とからなり、 前記転がり機構の回転により、内側筒体および
外側円筒体のいずれか一方を固定した場合に他方
が回転し出力軸とされ、しかも前記内側筒体と外
側円筒体との間に両筒体の径差による回転ずれを
生じることを特徴とする減速装置。[Scope of Claims] 1. An outer cylindrical body; and a thin-walled rigid material disposed inside the outer cylindrical body, having an outer diameter smaller than the inner diameter of the outer cylindrical body, and capable of being flexibly deformed in the radial direction. an inner cylindrical body formed of; and an elastic member provided on the inner periphery of the inner cylindrical body, which moves and rotates the inward contact point while the inner cylindrical body is forcedly frictionally inscribed with the outer cylindrical body at least at one location. A rolling mechanism consisting of a body, an input shaft for driving the rolling mechanism, and a supporting body that positions the internal contact point in the rolling mechanism, surrounds the input shaft, and rotates together with the input shaft. , Due to the rotation of the rolling mechanism, when either the inner cylindrical body or the outer cylindrical body is fixed, the other rotates and becomes an output shaft, and furthermore, between the inner cylindrical body and the outer cylindrical body, both cylindrical bodies are A speed reduction device characterized by causing rotational deviation due to a diameter difference.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5324982A JPS58170960A (en) | 1982-03-31 | 1982-03-31 | Speed reduction gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5324982A JPS58170960A (en) | 1982-03-31 | 1982-03-31 | Speed reduction gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58170960A JPS58170960A (en) | 1983-10-07 |
| JPH0260904B2 true JPH0260904B2 (en) | 1990-12-18 |
Family
ID=12937514
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5324982A Granted JPS58170960A (en) | 1982-03-31 | 1982-03-31 | Speed reduction gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58170960A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006040020A1 (en) * | 2006-08-25 | 2008-03-20 | Vojacek, Herbert, Prof. Dr.-Ing. | Planetary friction gear with high gear ratio |
| DE112007002580B4 (en) * | 2006-08-25 | 2012-07-05 | Herbert Vojacek | Planetary friction gear with high gear ratio |
| FR3057328B1 (en) * | 2016-10-10 | 2018-10-26 | Peugeot Citroen Automobiles Sa | DEFORMATION WAVE GEAR COMPRISING ELASTIC MEANS AND HUB WITH EXTERNAL TOOTH |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1115459A (en) * | 1964-12-18 | 1968-05-29 | Gen Precision Systems Inc | Torque transmission device |
| JPS4872556A (en) * | 1971-12-29 | 1973-09-29 |
-
1982
- 1982-03-31 JP JP5324982A patent/JPS58170960A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1115459A (en) * | 1964-12-18 | 1968-05-29 | Gen Precision Systems Inc | Torque transmission device |
| JPS4872556A (en) * | 1971-12-29 | 1973-09-29 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58170960A (en) | 1983-10-07 |
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