JPS6138242A - Accelerating/decelerating device of planetary gear - Google Patents
Accelerating/decelerating device of planetary gearInfo
- Publication number
- JPS6138242A JPS6138242A JP15856884A JP15856884A JPS6138242A JP S6138242 A JPS6138242 A JP S6138242A JP 15856884 A JP15856884 A JP 15856884A JP 15856884 A JP15856884 A JP 15856884A JP S6138242 A JPS6138242 A JP S6138242A
- Authority
- JP
- Japan
- Prior art keywords
- input shaft
- output shaft
- hole
- drive
- spline
- 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
Links
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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/322—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising at least one universal joint, e.g. a Cardan joint
Landscapes
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明は内歯歯車がピン又はピンとローラの組合わせよ
りなり、外歯歯車がトロコイド歯形等からなる遊星歯車
装置の改良に係り、更に詳しくはユニバーサルジヨイン
ト結合部を有する遊星歯車装置の改良に関する。Detailed Description of the Invention (Field of Industrial Application) The present invention relates to an improvement of a planetary gear device in which an internal gear is made of a pin or a combination of a pin and a roller, and an external gear is made of a trochoid tooth profile. relates to an improvement in a planetary gear train having a universal joint connection.
(従来の技術)
第3図及び第4図を参照して、従来の遊星歯車減速機に
ついて説明する。(Prior Art) A conventional planetary gear reducer will be described with reference to FIGS. 3 and 4.
遊星歯車減速機は、この公知のものでは入力軸1から入
力される回転を減速して出力軸2へ与えるものとなって
いる。In this known planetary gear reducer, rotation input from an input shaft 1 is reduced in speed and applied to an output shaft 2.
この減速する機構は次のとおりである。The mechanism for this deceleration is as follows.
入力軸1には所定位相差(この例では180°)をもっ
て偏心体33.3□が設けられている。夫々の偏心体3
8.32はコロ4を介して外歯歯車51.5.と接して
いる。外歯歯lL5い52には内ローラ孔6が複数個設
けられ、内ピン7及び内ローラ8が嵌入されている。前
記外歯歯車51.5□の外周にはトロコイドや円弧など
の外歯9が設けられ、内歯歯車10に設けられた外ピン
11と前記外歯9とが噛み合っている。An eccentric body 33.3□ is provided on the input shaft 1 with a predetermined phase difference (180° in this example). each eccentric body 3
8.32 is connected to the external gear 51.5 through the roller 4. It is in contact with A plurality of inner roller holes 6 are provided in the outer tooth lL5 52, into which the inner pin 7 and the inner roller 8 are fitted. External teeth 9 such as a trochoid or an arc are provided on the outer periphery of the external gear 51.5□, and the external pins 11 provided on the internal gear 10 mesh with the external teeth 9.
前記内ビン7は出力軸2の7ランノ部12に固着又は嵌
入されている。The inner bottle 7 is fixed or fitted into the 7-run section 12 of the output shaft 2.
この公知例では、入力軸1の1回転が偏心体38.32
の1回転となるが、外歯歯車51.52は内ローラ孔6
と内ビン7とにより自転を拘束されており揺動回転させ
られるから、外歯歯車51.52の歯数と外ピン11の
本数(歯数)の差が1個の場合、入力軸1の1回転によ
り外歯歯車51.52の外歯9と内歯歯車10の内歯で
ある外ビン11とが1歯だけ噛み合い変位する(ずれる
)。このため、入力軸1の1回転は外歯歯車53.52
の1/歯数に減速され、その回転を内ピン7を介して出
力軸2へ伝達される。In this known example, one revolution of the input shaft 1 corresponds to 38.32 degrees of the eccentric body.
However, the external gears 51 and 52 rotate through the inner roller hole 6.
Since the rotation is restrained by the inner pin 7 and the rotation is oscillated, if the difference between the number of teeth of the external gears 51 and 52 and the number of outer pins 11 (the number of teeth) is 1, the input shaft 1 One rotation causes the external teeth 9 of the external gears 51, 52 and the external pin 11, which is the internal tooth of the internal gear 10, to engage and displace (shift) by one tooth. Therefore, one rotation of the input shaft 1 is made by the external gear 53.52
The rotation is reduced to 1/the number of teeth, and the rotation is transmitted to the output shaft 2 via the inner pin 7.
(発明が解決しようとする問題点) 以上の如き遊星歯車機構では次のような不具合がある。(Problem that the invention attempts to solve) The planetary gear mechanism described above has the following problems.
内ローラ孔6、内ピン7及び内口−28による動力伝達
機構は出力軸2にラジアル方向の荷重を与える。このた
め、出力軸2の変形を防止する頑丈な7ランノ部12を
設けなければならず、出力軸2の近傍は径方向にコンパ
クト化できない。又、内ローラ孔6、内ビン7及び内ロ
ーラ8による動力伝達機構は高精度の加工を必要とし、
かつ僅な変形でも悪影響を及ぼすので、適当な剛性も必
要となる。A power transmission mechanism including the inner roller hole 6, the inner pin 7, and the inner port 28 applies a load to the output shaft 2 in the radial direction. For this reason, it is necessary to provide a sturdy seven-run section 12 to prevent deformation of the output shaft 2, and the vicinity of the output shaft 2 cannot be made compact in the radial direction. In addition, the power transmission mechanism using the inner roller hole 6, inner bottle 7, and inner roller 8 requires high-precision machining.
In addition, since even a slight deformation has an adverse effect, appropriate rigidity is also required.
内ローラ孔6の存在は外歯歯車51.5□において大き
いスペースを占めるため、外歯歯車51.52の小型化
に障害となり、結局機器全体の小型化の難点となってい
る。The presence of the inner roller hole 6 occupies a large space in the external gear 51.5□, which becomes an obstacle to miniaturization of the external gear 51.52, and ultimately becomes a difficulty in miniaturizing the entire device.
一方、内歯歯車にキャリヤを取付け、このキャリヤと出
力軸とを中間ドライブギヤで連結し、出力軸にラジアル
方向の荷重が作用しないようにした機構も公知であるが
、この装置では入力軸が片持ち状態となるので、入力軸
の負荷を受ける軸受の荷重が大きく、このため入力側ケ
ーシングをコンパクトに出来ない。On the other hand, there is also a known mechanism in which a carrier is attached to the internal gear and the carrier and the output shaft are connected by an intermediate drive gear so that no load is applied to the output shaft in the radial direction. Since it is in a cantilevered state, the load on the bearing that receives the load of the input shaft is large, and therefore the input side casing cannot be made compact.
本発明の目的は上記欠点を改善し、簡単な機構で入力軸
側の簡素化、小型化を達成するとともに、軸方向にも短
かくかつ出力軸側をも簡素化、小型化した遊星歯車増減
速成を提供するものである。The purpose of the present invention is to improve the above-mentioned drawbacks, to achieve simplification and miniaturization of the input shaft side with a simple mechanism, and to provide a planetary gear that is short in the axial direction and simplified and miniaturized of the output shaft side. It provides quick preparation.
(問題点を解決するための手段)
本発明の特徴とするところは、入力軸に偏心体を介して
装着された外歯歯車と、該外歯歯車と噛合する出力軸と
同心の内歯歯車とを有する遊星歯車装置においで、前記
出力軸に凹所な設け、該凹所内に該出力軸と同心にスプ
ライン穴又はスプラインを設け、前記外歯歯車にキャリ
ヤを設け、該キャリヤに外歯歯車と同心にスプライン穴
又はスプラインを設け、前記出力軸のスプライン穴又は
スプラインと前記外歯歯車のスプライン穴又はスプライ
ンとを両端にスプライン又はスプライン穴が設けられた
ドライブにより連結し、該ドライブは内部に貫通口を有
する筒状となっており、前記入力軸が前記ドライブの貫
通口を挿通して前記出力軸の凹所内で軸受けしたところ
にある。(Means for Solving Problems) The present invention is characterized by an external gear mounted on an input shaft via an eccentric body, and an internal gear concentric with the output shaft that meshes with the external gear. a planetary gear device comprising: a recess provided in the output shaft; a spline hole or spline provided in the recess concentrically with the output shaft; a carrier provided in the external gear; A spline hole or spline is provided concentrically with the output shaft, and the spline hole or spline of the output shaft and the spline hole or spline of the external gear are connected by a drive having splines or spline holes at both ends, and the drive is connected to the spline hole or spline inside. It has a cylindrical shape with a through hole, and the input shaft is inserted through the through hole of the drive and is supported within the recess of the output shaft.
(実施例) 以下、図によって詳細に説明する。(Example) This will be explained in detail below with reference to the drawings.
第1.2図は本発明の一実施例を示すものであり、入力
軸21には偏心量Cを有する偏心体22が形成され、該
偏心体22に軸受23を介して外歯歯車24が装着され
ている。従って外歯歯車24の軸心02は入力軸21(
内歯歯車26)の軸心01に対してeだけ偏心して装着
されている。この外歯歯車24の外歯25はトロコイド
歯形や円弧歯形など適宜の歯形からなっており、内歯歯
車26の外ピン27からなる内歯と噛み合っている。外
歯歯車24にはキャリア部28が一体に設けられており
、キャリア部28には外歯歯車24と同心の内スプライ
ン穴29が設けられている。FIG. 1.2 shows an embodiment of the present invention, in which an eccentric body 22 having an eccentricity C is formed on the input shaft 21, and an external gear 24 is connected to the eccentric body 22 via a bearing 23. It is installed. Therefore, the axis 02 of the external gear 24 is located at the input shaft 21 (
It is mounted eccentrically by e with respect to the axis 01 of the internal gear 26). The external teeth 25 of the external gear 24 have an appropriate tooth profile such as a trochoidal tooth profile or an arc tooth profile, and mesh with the internal teeth of the external pin 27 of the internal gear 26 . The external gear 24 is integrally provided with a carrier portion 28, and the carrier portion 28 is provided with an internal spline hole 29 concentric with the external gear 24.
一方、出力軸30には凹所31が設けられており、該凹
所31には入力軸21と同心の内スプライン穴32が設
けられており、前記各内スプライン穴29.32との間
に浮動支持された外スプライン33.34を有するドラ
イブ35が設けられている。On the other hand, the output shaft 30 is provided with a recess 31, and the recess 31 is provided with an inner spline hole 32 concentric with the input shaft 21, and between each of the inner spline holes 29 and 32. A drive 35 is provided having floatingly supported external splines 33,34.
ドライブ35は筒状となっており、内部に貫通孔36を
有している。入力軸21はドライブ35の貫通孔36を
挿通しており、出力軸30の凹所31内で軸受37によ
り支承されている。The drive 35 has a cylindrical shape and has a through hole 36 inside. The input shaft 21 is inserted through the through hole 36 of the drive 35 and is supported by a bearing 37 within the recess 31 of the output shaft 30 .
このため、入力軸21は外歯歯車24の両側で軸受37
及び軸受38によって両持支持されている。Therefore, the input shaft 21 has bearings 37 on both sides of the external gear 24.
and are supported on both sides by bearings 38.
内歯歯車26は筒長状となって出力軸ケーシングと一体
となっており、入力軸ケーシング39にポル)40によ
り固着されている。出力軸30は軸受41により内歯歯
車26の筒長部分で支承されている。The internal gear 26 has an elongated cylindrical shape and is integrated with the output shaft casing, and is fixed to the input shaft casing 39 by a pin 40. The output shaft 30 is supported by a bearing 41 on the cylindrical length of the internal gear 26 .
以上の如く構成された本発明の遊星歯車載速成の作用に
ついて述べる。The operation of the planetary gear-mounted speed generator of the present invention constructed as described above will be described.
入力軸21の回転により偏心体22を回転させ、軸受2
3を介して外歯歯車24へ伝達される。この時、入力軸
21の軸心O3と外歯歯車24の回転軸02とはeだけ
偏心しており、かつ、外歯歯車24はキャリア部28を
介して浮動支持されたドライブ35に連結されているの
で、外歯歯車24の入力軸21の軸心01まわりの公転
運動はドライブ35の揺動運動により吸収され、入力軸
21の回転のみが外歯歯車24と外ビン27との噛合に
より 1/外歯25の歯数 に減速されて取出され、こ
の外歯歯車24の回転はキャリア部28を介してドライ
ブ35へ伝えられ、ドライブ25から出力軸30へ伝達
される。The eccentric body 22 is rotated by the rotation of the input shaft 21, and the bearing 2
3 to the external gear 24. At this time, the axis O3 of the input shaft 21 and the rotation axis 02 of the external gear 24 are eccentric by e, and the external gear 24 is connected to the drive 35 which is floatingly supported via the carrier part 28. Therefore, the revolution movement of the input shaft 21 of the external gear 24 around the axis 01 is absorbed by the swinging movement of the drive 35, and only the rotation of the input shaft 21 is caused by the meshing of the external gear 24 and the external pin 27. The rotation of the external gear 24 is transmitted to the drive 35 via the carrier portion 28, and from the drive 25 to the output shaft 30.
入力軸26に作用する荷重は外歯歯車24を介して入力
軸26にかかるが、入力軸26の両側に軸受37.38
が設けられて両持となっているので、それぞれの軸受3
7.38に作用する荷重が軽くなり、軸受37.38を
小型化しうるものとなる。The load acting on the input shaft 26 is applied to the input shaft 26 via the external gear 24, but there are bearings 37 and 38 on both sides of the input shaft 26.
are provided and are supported on both sides, so each bearing 3
The load acting on 7.38 becomes lighter, and the bearing 37.38 can be made smaller.
なお、上記は減速機について説明しているが、本発明は
増速槻としても適用しうるものである。Although the above description has been made regarding a speed reducer, the present invention can also be applied to a speed increaser.
以上の如く構成され、作用する本発明の効果を挙げる次
のとおりである。The effects of the present invention, which is constructed and operated as described above, are listed below.
入力軸が両持支持であるので、入力軸を支承する軸受を
小型化でき、入力軸及び入力軸ケーシングな小型化、簡
素化できるものとなる。Since the input shaft is supported on both sides, the bearing supporting the input shaft can be downsized, and the input shaft and input shaft casing can be downsized and simplified.
ドライブが筒状であるから、軽量化できる。Since the drive is cylindrical, it can be lightweight.
ドライブがキャリアおよび出力軸に対して浮動している
ので、加工誤差が吸収され、加工精度をそれ程必要とし
なくなる。Since the drive is floating relative to the carrier and output shaft, machining errors are absorbed and machining accuracy is not required as much.
又、内ローラ穴を必要としないので、外歯歯車の半径方
向スペースが節約され、減速機の小型化が得られる。Further, since no inner roller hole is required, the space in the radial direction of the external gear is saved, and the reduction gear can be made smaller.
出力軸にはトルクのみが伝達され、ラジアル荷重が作用
しないので、変形に基づ(角度バックラッシュが低減さ
れる。Since only torque is transmitted to the output shaft and no radial load acts, angular backlash is reduced based on deformation.
外歯歯車を筒長として出力軸ケーシングと一体としたも
のでは、出力側を小型化、簡素化しうるものとなる」二
、ボルト結合がないので、大きいトルクの伝達が可能と
なる。If the external gear is made into a cylinder and is integrated with the output shaft casing, the output side can be downsized and simplified. 2. Since there is no bolt connection, large torque can be transmitted.
第1図は本発明の一実施例を示す断面図、第2図は第1
図のB−B断面図、第3図は従来装置の一例を示す断面
図、第4図は第3図のA−A断面図である。
21:入力軸、 22:偏心体、 23:軸受、
24:外歯歯車、 26:内歯歯車、 28:キャ
リア部、 30:出力軸、 35ニドライブ、
36:貫通孔 37.38:軸受復代理人 弁理士 辻
三部FIG. 1 is a sectional view showing one embodiment of the present invention, and FIG.
3 is a sectional view showing an example of a conventional device, and FIG. 4 is a sectional view taken along A-A in FIG. 3. 21: Input shaft, 22: Eccentric body, 23: Bearing,
24: External gear, 26: Internal gear, 28: Carrier section, 30: Output shaft, 35 Nidrive,
36: Through hole 37. 38: Bearing sub-agent Patent attorney Sanbe Tsuji
Claims (1)
歯車と噛合する出力軸と同心の内歯歯車とを有する遊星
歯車装置において、前記出力軸に凹所を設け、該凹所内
に該出力軸と同心にスプライン穴又はスプラインを設け
、前記外歯歯車にキャリヤを設け、該キャリヤに外歯歯
車と同心にスプライン穴又はスプラインを設け、前記出
力軸のスプライン穴又はスプラインと前記外歯歯車のス
プライン穴又はスプラインとを両端にスプライン又はス
プライン穴が設けられたドライブにより連結し、該ドラ
イブは内部に貫通口を有する筒状となっており、前記入
力軸が前記ドライブの貫通口を挿通して前記出力軸の凹
所内で軸受けされていることを特徴とする遊星歯車装置
。In a planetary gear device having an external gear mounted on an input shaft via an eccentric, and an internal gear concentric with an output shaft that meshes with the external gear, a recess is provided in the output shaft, and the recess A spline hole or spline is provided in the output shaft concentrically with the output shaft, a carrier is provided in the external gear, a spline hole or spline is provided in the carrier concentrically with the external gear, and the spline hole or spline of the output shaft and the The spline holes or splines of the external gear are connected by a drive having splines or spline holes at both ends, and the drive has a cylindrical shape with a through hole inside, and the input shaft connects to the through hole of the drive. A planetary gear device, characterized in that the output shaft is supported in a recess through which the output shaft is inserted.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15856884A JPS6138242A (en) | 1984-07-31 | 1984-07-31 | Accelerating/decelerating device of planetary gear |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15856884A JPS6138242A (en) | 1984-07-31 | 1984-07-31 | Accelerating/decelerating device of planetary gear |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6138242A true JPS6138242A (en) | 1986-02-24 |
JPH0556417B2 JPH0556417B2 (en) | 1993-08-19 |
Family
ID=15674533
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15856884A Granted JPS6138242A (en) | 1984-07-31 | 1984-07-31 | Accelerating/decelerating device of planetary gear |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6138242A (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4770062A (en) * | 1986-02-19 | 1988-09-13 | Sumitomo Heavy Industries Ltd. | Planetary gear apparatus |
JPH01316144A (en) * | 1988-03-05 | 1989-12-21 | Teijin Seiki Co Ltd | Driving device for automatic tool exchange device |
JPH02110449U (en) * | 1989-02-21 | 1990-09-04 | ||
JPH02245545A (en) * | 1989-10-07 | 1990-10-01 | Sumitomo Heavy Ind Ltd | Planet gear speed change gear |
JPH09168936A (en) * | 1988-03-05 | 1997-06-30 | Teijin Seiki Co Ltd | Driving device for automatic tool changer |
-
1984
- 1984-07-31 JP JP15856884A patent/JPS6138242A/en active Granted
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4770062A (en) * | 1986-02-19 | 1988-09-13 | Sumitomo Heavy Industries Ltd. | Planetary gear apparatus |
JPH01316144A (en) * | 1988-03-05 | 1989-12-21 | Teijin Seiki Co Ltd | Driving device for automatic tool exchange device |
JPH09168936A (en) * | 1988-03-05 | 1997-06-30 | Teijin Seiki Co Ltd | Driving device for automatic tool changer |
JPH02110449U (en) * | 1989-02-21 | 1990-09-04 | ||
JPH02245545A (en) * | 1989-10-07 | 1990-10-01 | Sumitomo Heavy Ind Ltd | Planet gear speed change gear |
Also Published As
Publication number | Publication date |
---|---|
JPH0556417B2 (en) | 1993-08-19 |
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