JPS61282650A - Planetary gear mechanism - Google Patents
Planetary gear mechanismInfo
- Publication number
- JPS61282650A JPS61282650A JP60125697A JP12569785A JPS61282650A JP S61282650 A JPS61282650 A JP S61282650A JP 60125697 A JP60125697 A JP 60125697A JP 12569785 A JP12569785 A JP 12569785A JP S61282650 A JPS61282650 A JP S61282650A
- Authority
- JP
- Japan
- Prior art keywords
- internal gear
- planetary
- gear
- planetary gear
- brake
- 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.)
- Pending
Links
Landscapes
- Structure Of Transmissions (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は多段変速機や変速クラッチとして使用可能な遊
星歯車機構に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a planetary gear mechanism that can be used as a multi-stage transmission or a variable speed clutch.
遊星歯車機構の内歯車を回転自在に浮動させ、その内歯
車の外周に内歯車を制動するブレーキを設けたものがあ
る。この機構は、内歯車をブレーキによって制動したり
、制動解除したりすることにより、一方の回転軸から他
方の回転軸へ動力を変速伝達する変速機や変速クラッチ
として利用可能になる。There is a planetary gear mechanism in which the internal gear is made to float rotatably and a brake is provided around the outer circumference of the internal gear to brake the internal gear. This mechanism can be used as a transmission or a speed change clutch that transmits power from one rotating shaft to the other rotating shaft at variable speeds by braking or releasing the brake on the internal gear.
ところが、上述した浮動状態の内歯車を制動する場合、
内歯車の中心が太陽歯車の中心から瞬間的に若干のずれ
を発生することがあり、このずれによって内歯車と遊星
歯車の間のバックラッシュが０になる所謂二歯面噛合が
発生し、騒音発生や、最悪の場合には歯車の破損を招（
恐れがあった。従来、上記遊星歯車機構が極めて便利で
あるにもかかわらず実用化が遅れているのは、このよう
な事実に起因することが大きかった。However, when braking the floating internal gear mentioned above,
The center of the internal gear may momentarily deviate slightly from the center of the sun gear, and this deviation causes so-called two-tooth meshing in which the backlash between the internal gear and the planetary gear becomes 0, resulting in noise. or, in the worst case, damage to the gears (
There was fear. Conventionally, this fact has been largely responsible for the delay in practical application of the planetary gear mechanism, although it is extremely convenient.
本発明の目的は、上述のような内歯車を浮動状態にし、
その内歯車をブレーキで制動可能にした遊星歯車機構に
おいて、簡単でコンバクな機構にしなから二歯面噛合の
発生を防止できるようにした遊星歯車機構を提供するこ
とにある。The purpose of the present invention is to make the internal gear as described above floating,
To provide a planetary gear mechanism whose internal gear can be braked by a brake, which is a simple and compact mechanism and can prevent the occurrence of two-tooth surface meshing.
上記目的を達成する本発明は、太陽歯車に少なくとも３
個の遊星歯車を噛合させ、これらの遊星歯車に噛合する
内歯車を回転自在に浮動させ、この内歯車の外周に内歯
車を制動するブレーキを設けた遊星歯車機構において、
前記遊星歯車を支持する遊星軸に、前記内歯車の内周に
僅少の間隙を介して近接する円盤状のガイド板を回転自
在に支持したことを特徴とするものである。To achieve the above object, the present invention provides a sun gear with at least three
In a planetary gear mechanism, a number of planetary gears are meshed, an internal gear that meshes with these planetary gears is made to float rotatably, and a brake is provided on the outer periphery of the internal gear to brake the internal gear.
The planetary gear is characterized in that a disk-shaped guide plate is rotatably supported on the planetary shaft that supports the planetary gear, and is adjacent to the inner periphery of the internal gear with a slight gap therebetween.
以下、本発明を図に示す実施例により説明する。 The present invention will be explained below with reference to embodiments shown in the drawings.
第１〜３図は本発明の実施例による遊星歯車機構を示し
、１，２はそれぞれ一方が入力軸となり、他方が出力軸
となる回転軸であり、回転中心を同軸にして配置されて
いる。回転軸１には太陽歯車３が一体に設けられ、この
太陽歯車３に少なくとも３個の遊星歯車４，４．４が噛
合している。また、回転軸２にはキャリヤ６゜６を介し
て遊星軸５，５．５が固定され、各遊星軸５にベアリン
グ７を介して上記遊星歯車４がそれぞれ回転自在に支持
されている。Figures 1 to 3 show a planetary gear mechanism according to an embodiment of the present invention, and 1 and 2 are rotating shafts, one of which is an input shaft and the other is an output shaft, and they are arranged with their rotation centers coaxial. . A sun gear 3 is integrally provided on the rotating shaft 1, and at least three planetary gears 4, 4.4 mesh with the sun gear 3. Further, planetary shafts 5, 5.5 are fixed to the rotating shaft 2 via carriers 6.6, and the planetary gears 4 are rotatably supported on each planetary shaft 5 via bearings 7, respectively.
さらに遊星歯車４．４．４の外側には、浮動状態の内歯
車８が回転自在に噛合し、その外側にブレーキバンド９
が設けられている。ブレーキバンド９は、その締付は操
作により内歯車８を制動し、また緩めることにより制動
を解除するようになっている。Further, a floating internal gear 8 is rotatably engaged with the outer side of the planetary gear 4.4.4, and a brake band 9 is attached to the outer side of the internal gear 8.
is provided. The brake band 9 is tightened to brake the internal gear 8, and loosened to release the brake.
各遊星軸５には遊星歯車４を間に挟んで円盤状のガイド
板１０．１０が回転自在に支持されている。このガイド
板１０の外周が対面する内歯車８の内周にはガイド面８
ａが形成され、このガイド面８ａに上記ガイド板１０の
外周が僅少の間隙ｔを介して近接状態になっている。A disk-shaped guide plate 10.10 is rotatably supported on each planetary shaft 5 with the planetary gear 4 interposed therebetween. A guide surface 8 is provided on the inner periphery of the internal gear 8, which the outer periphery of the guide plate 10 faces.
a is formed, and the outer periphery of the guide plate 10 is in close proximity to this guide surface 8a with a slight gap t interposed therebetween.
上述した遊星歯車機構において、例えば回転軸１を入力
軸とし、回転軸２を出力軸にするとき、ブレーキバンド
９によって内歯車８を制動したときは、入力軸１の動力
は遊星歯車４．キャリヤ６を介して出力軸２に減速伝達
され、制動を解除すると内歯車８が空転し、動力が出力
軸２へ伝達されなくなる。また、逆に回転軸２を入力軸
にし、回転軸１を出力軸にするときは、同様に内歯車８
を制動状態にしたとき、出力軸１に動力が増速伝達され
、制動を解除したとき伝達されなくなる。In the planetary gear mechanism described above, for example, when the rotating shaft 1 is used as the input shaft and the rotating shaft 2 is used as the output shaft, and when the internal gear 8 is braked by the brake band 9, the power of the input shaft 1 is transferred to the planetary gear 4. The deceleration is transmitted to the output shaft 2 via the carrier 6, and when the brake is released, the internal gear 8 idles and the power is no longer transmitted to the output shaft 2. Conversely, when the rotating shaft 2 is used as the input shaft and the rotating shaft 1 is used as the output shaft, the internal gear 8
When the motor is put into a braking state, power is transmitted to the output shaft 1 at an increased speed, and when the braking is released, power is no longer transmitted.
上述のような動力伝達において、非制動状態のときの内
歯車８は、太陽歯車３の軸心を回転中心として回転する
が、ブレーキバンド９の締付けによって内歯車８を制動
するとき、その制動の瞬間に中心位置のずれが発生しよ
うとする。In the above-described power transmission, the internal gear 8 in the non-braking state rotates around the axis of the sun gear 3, but when the internal gear 8 is braked by tightening the brake band 9, the braking is The center position is about to shift at an instant.
しかし、上記装置では、中心位置のずれが発生した瞬間
、ガイド板１０が内歯車８のガイド面８ａに接触し、内
歯車８と遊星歯車４の間のバックラッシュがＯになる状
態、すなわち二歯面噛合が起こらないようにすることが
できる。また、ガイド板１０は遊星軸５を中心に回転自
在となっているので、ガイド板１０の内歯車８との接触
を転がり接触にすることができ、それによって摩耗など
のない円滑な二歯面噛合防止が達成される。However, in the above device, the moment the center position shift occurs, the guide plate 10 comes into contact with the guide surface 8a of the internal gear 8, and the backlash between the internal gear 8 and the planetary gear 4 becomes O, that is, the It is possible to prevent tooth surface meshing from occurring. Further, since the guide plate 10 is rotatable around the planetary shaft 5, the contact between the guide plate 10 and the internal gear 8 can be made into rolling contact, thereby creating a smooth two-tooth surface without wear. Anti-meshing is achieved.
なお、上述のような作用を行うガイド板１０は、上述の
ように左右２枚設けると左右幅を広げることができるた
め、内歯車８を安定な状態で支持ガイドする上で好まし
いが、１枚だけであっても二歯面噛合防止は可能である
ので差支えない。ガイド板１０を１枚だけにするときは
、ガイド面８ａに対向する部分の板厚を大きくすること
が望ましい。It should be noted that it is preferable to provide the guide plates 10 that perform the above-mentioned functions in order to support and guide the internal gear 8 in a stable state, since the width can be increased by providing two guide plates on the left and right sides as described above. There is no problem even if it is only that, since it is possible to prevent the two tooth surfaces from meshing. When using only one guide plate 10, it is desirable to increase the thickness of the portion facing the guide surface 8a.
上述のような遊星歯車機構を多段変速機に適用するとき
は、第４図あるいは第５図のように多段に設ければよい
。（ただし、第４図、第５図ではガイド板を省略して示
しである。）第４図の多段変速機は、回転軸１に２個の
太陽歯車３．３を設け、それぞれの太陽歯車３ごとに上
記遊星歯車機構を２段に構成するようにしたものである
。２段の遊星歯車機構におけるブレーキバンド９．９の
いずれか一方を選択的に締付は操作することにより、異
なる変速比の動力伝達が行えるようになっている。勿論
、遊星歯車機構を３段以上にすることもできる。When the planetary gear mechanism as described above is applied to a multi-stage transmission, it may be provided in multiple stages as shown in FIG. 4 or 5. (However, the guide plate is omitted in FIGS. 4 and 5.) The multi-stage transmission shown in FIG. The planetary gear mechanism is constructed in two stages every three stages. By selectively tightening one of the brake bands 9.9 in the two-stage planetary gear mechanism, power transmission at different gear ratios can be performed. Of course, the planetary gear mechanism can also have three or more stages.
上記第４図の多段変速機は、第１〜３図の実施例の遊星
歯車機構と同様に、遊星歯車４が遊星軸５に対しベアリ
ング７を介して回転自在に支持されているが、これを第
５図の多段変速機のように、遊星歯車４を遊星軸５に固
定状態にし、その遊星軸５をキャリヤ６に対しベアリン
グ７゛を介して回転自在に支持するようにしたものであ
ってもよい。この第５図の場合は、太陽歯車３が１個だ
けですむようになるので、機構を軽量簡素化する上で有
利である。この第５図の多段変速機にも、上記本発明に
よるガイド板１０は全く同様に使用することができる。In the multi-stage transmission shown in FIG. 4, the planetary gear 4 is rotatably supported by the planetary shaft 5 via a bearing 7, similar to the planetary gear mechanism of the embodiment shown in FIGS. 1 to 3. As in the multi-stage transmission shown in Fig. 5, the planetary gear 4 is fixed to the planetary shaft 5, and the planetary shaft 5 is rotatably supported by the carrier 6 via a bearing 7'. You can. In the case shown in FIG. 5, only one sun gear 3 is required, which is advantageous in making the mechanism lightweight and simple. The guide plate 10 according to the present invention described above can be used in the same manner in the multi-stage transmission shown in FIG.
上述したように本発明は、内歯車を浮動状態にし、その
内歯車を外周から制動するブレーキを設けた遊星歯車機
構において、遊星軸に対し円盤状のガイド板を支持し、
このガイド板の外周を前記内歯車の内周に僅少の間隙を
介して近接させる構成にしたので、ブレーキによって内
歯車を制動するとき、上記ガイド板が内歯車の内周に接
触することによって、内歯車と遊星歯車の間の二歯面噛
合の発生を防止することができる。また、上記円盤状の
ガイド板を遊星軸を中心として回転自在にしたので、上
記接触が転がり接触になり、摩耗の少ない円滑な機構に
なる。As described above, the present invention provides a planetary gear mechanism in which an internal gear is placed in a floating state and is provided with a brake that brakes the internal gear from the outer periphery.
Since the outer periphery of this guide plate is arranged to be close to the inner periphery of the internal gear with a small gap, when the internal gear is braked by the brake, the guide plate comes into contact with the inner periphery of the internal gear. It is possible to prevent the occurrence of two-tooth mesh between the internal gear and the planetary gear. Furthermore, since the disc-shaped guide plate is made rotatable around the planetary shaft, the contact is a rolling contact, resulting in a smooth mechanism with little wear.
また、上述のようにガイド板を設けるだけの簡単な構成
であるので、これによって多段変速機などをコンパクト
で、かつ廉価に製作することが可能になる。Further, since the structure is simple, just providing the guide plate as described above, it becomes possible to manufacture a multi-stage transmission etc. compactly and at low cost.
第１図は本発明の実施例からなる遊星歯車機構の要部を
示す縦断面図、第２図は同要部の正面図、第３図は同機
構の全体を示す正面図、第４図および第５図は、それぞ
れ遊星歯車機構からなる多段変速機の概略図である。
１．２・−・回転軸、 ３・−太陽歯車、 ４・−・遊
星歯車、 ５・−・遊星軸、 ６−・キャリヤ、 ８
・・・・内歯車、 ８ａ−・ガイド面、 ９・・・
−・ブレーキバンド、 １０−ガイド板、 を−・
・僅少の間隙。FIG. 1 is a longitudinal sectional view showing the main parts of a planetary gear mechanism according to an embodiment of the present invention, FIG. 2 is a front view of the main parts, FIG. 3 is a front view showing the entire mechanism, and FIG. and FIG. 5 are schematic diagrams of multi-stage transmissions each comprising a planetary gear mechanism. 1.2--rotating shaft, 3--sun gear, 4--planetary gear, 5--planetary shaft, 6--carrier, 8
...Internal gear, 8a--Guide surface, 9...
-・Brake band, 10-guide plate, -・
・Small gap.
Claims (1)
らの遊星歯車に噛合する内歯車を回転自在に浮動させ、
この内歯車の外周に内歯車を制動するブレーキを設けた
遊星歯車機構において、前記遊星歯車を支持する遊星軸
に、前記内歯車の内周に僅少の間隙を介して近接する円
盤状のガイド板を回転自在に支持したことを特徴とする
遊星歯車機構。At least three planetary gears are meshed with the sun gear, and an internal gear that meshes with these planetary gears is rotatably floating;
In this planetary gear mechanism in which a brake for braking the internal gear is provided on the outer periphery of the internal gear, a disk-shaped guide plate is provided near the inner periphery of the internal gear with a small gap between the planetary shafts that support the planetary gears. A planetary gear mechanism characterized by rotatably supported.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60125697A JPS61282650A (en) | 1985-06-10 | 1985-06-10 | Planetary gear mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60125697A JPS61282650A (en) | 1985-06-10 | 1985-06-10 | Planetary gear mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61282650A true JPS61282650A (en) | 1986-12-12 |
Family
ID=14916470
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60125697A Pending JPS61282650A (en) | 1985-06-10 | 1985-06-10 | Planetary gear mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61282650A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03121335A (en) * | 1989-10-02 | 1991-05-23 | Matetsukusu Kk | Timing drive unit for epicycle gear |
| EP2011999A2 (en) | 2007-07-05 | 2009-01-07 | Denso Corporation | Speed reduction type starter for engines |
| EP2048356A2 (en) | 2007-10-11 | 2009-04-15 | Denso Corporation | Speed reduction type starter for engines |
| EP2067984A2 (en) | 2007-12-05 | 2009-06-10 | Denso Corporation | Starter having two planetary speed reducers with different speed reduction ratios |
| JP2015515590A (en) * | 2013-03-08 | 2015-05-28 | リ、ジャンリＬＩ， Ｊｉａｎｌｉ | Floating gear reducer |
| JP2016180510A (en) * | 2016-05-12 | 2016-10-13 | リ、ジャンリＬＩ， Ｊｉａｎｌｉ | Floating gear speed reducer |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS53104068A (en) * | 1977-02-21 | 1978-09-09 | Hitachi Ltd | Planetary change gear |
-
1985
- 1985-06-10 JP JP60125697A patent/JPS61282650A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS53104068A (en) * | 1977-02-21 | 1978-09-09 | Hitachi Ltd | Planetary change gear |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03121335A (en) * | 1989-10-02 | 1991-05-23 | Matetsukusu Kk | Timing drive unit for epicycle gear |
| EP2011999A2 (en) | 2007-07-05 | 2009-01-07 | Denso Corporation | Speed reduction type starter for engines |
| JP2009013886A (en) * | 2007-07-05 | 2009-01-22 | Denso Corp | Starter |
| EP2011999A3 (en) * | 2007-07-05 | 2010-05-19 | Denso Corporation | Speed reduction type starter for engines |
| US8091443B2 (en) | 2007-07-05 | 2012-01-10 | Denso Corporation | Speed reduction type starter for engines |
| EP2048356A2 (en) | 2007-10-11 | 2009-04-15 | Denso Corporation | Speed reduction type starter for engines |
| EP2048356A3 (en) * | 2007-10-11 | 2010-05-19 | Denso Corporation | Speed reduction type starter for engines |
| EP2067984A2 (en) | 2007-12-05 | 2009-06-10 | Denso Corporation | Starter having two planetary speed reducers with different speed reduction ratios |
| EP2067984A3 (en) * | 2007-12-05 | 2010-05-19 | Denso Corporation | Starter having two planetary speed reducers with different speed reduction ratios |
| JP2015515590A (en) * | 2013-03-08 | 2015-05-28 | リ、ジャンリＬＩ， Ｊｉａｎｌｉ | Floating gear reducer |
| US9447846B2 (en) | 2013-03-08 | 2016-09-20 | Jianli LI | Suspended wheel reducer |
| JP2016180510A (en) * | 2016-05-12 | 2016-10-13 | リ、ジャンリＬＩ， Ｊｉａｎｌｉ | Floating gear speed reducer |
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