JP3383809B2 - Planetary roller type power transmission - Google Patents
Planetary roller type power transmissionInfo
- Publication number
- JP3383809B2 JP3383809B2 JP32396092A JP32396092A JP3383809B2 JP 3383809 B2 JP3383809 B2 JP 3383809B2 JP 32396092 A JP32396092 A JP 32396092A JP 32396092 A JP32396092 A JP 32396092A JP 3383809 B2 JP3383809 B2 JP 3383809B2
- Authority
- JP
- Japan
- Prior art keywords
- planetary
- shaft
- roller
- power transmission
- planetary roller
- 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 - Fee Related
Links
Landscapes
- Friction Gearing (AREA)
Description
【発明の詳細な説明】
【０００１】
【産業上の利用分野】本発明は、遊星ローラ式動力伝達
装置に係り、詳しくは、遊星ローラをキャリアにニード
ルローラ軸受を介して回転自在に軸支する遊星軸の構造
に関する。
【０００２】
【従来の技術】一般に、遊星ローラ式動力伝達装置は、
図４に示すように、ハウジング２１に固定の外輪２２
と、この外輪２２の内側に同心に配置された太陽軸２３
と、太陽軸２３と外輪２２との間に圧接状に介装された
複数の遊星ローラ２４，…と、遊星ローラ２４の公転に
より回転するキャリア２５とを備えたものである。増減
速が一段の装置では、太陽軸２３が高速の入出力軸とな
り、キャリア２５には低速の入出力軸２６が直結され
る。
【０００３】そして、従来の装置では、各遊星ローラ２
４が、キャリア２５に突設された遊星軸２７にニードル
ローラ軸受２８などの軸受を介して回転自在に取り付け
られる。この例のニードルローラ軸受２８は、遊星軸２
７を内輪とし、遊星ローラ２４を外輪とするものであ
り、複数のニードルローラおよび保持器からなる。
【０００４】
【発明が解決しようとする課題】ところで、この種の動
力伝達装置では、外輪２２と太陽軸２３との間に遊星ロ
ーラ２４を圧入するので、遊星ローラ２４は、両者の間
で微量ではあるが圧縮されて楕円形に変形し、遊星ロー
ラ２４と遊星軸２７との間には、公転方向の前後に遊び
ができる。
【０００５】このように遊星ローラ２４と遊星軸２７と
の間にできる遊びは、歯車機構のバックラッシュに相当
するものであり、回転変動の発生原因になる。
【０００６】これに対して、従来、例えば、特公平４−
３２２５６号公報に示すように、遊星軸外周の軸受の内
径側に楔部材を圧入することで、遊星ローラと遊星軸と
の間にできる遊びを減少させるようにしたものがある
が、この構造では、組立に手数がかかるばかりでなく、
楔部材の脱落を防止する構造が新たに必要となり、実際
の製作には問題がある。
【０００７】本発明は、上記のような従来の問題点に鑑
み、簡単な構造により、遊星ローラと遊星軸との間の遊
びをできるだけ小さくして回転変動を抑制することを課
題としている。
【０００８】
【課題を解決するための手段】本発明は、上記課題を達
成するために、ハウジングに固定の外輪と、この外輪の
内側に同心に配置された太陽軸と、太陽軸と外輪との間
に圧接状に介装された複数の遊星ローラと、遊星ローラ
の公転により回転するキャリアとを備え、各遊星ローラ
がキャリアに突設された遊星軸に保持器に保持されたニ
ードルローラ軸受を介して回転自在に支持されている遊
星ローラ式動力伝達装置において、遊星軸の外径が、ニ
ードルローラ軸受の内接円径に対して大きく設定される
とともに、遊星軸のニードルローラ軸受が装着される外
周各部のうち、公転経路と同心の円弧に外径側および内
径側の両部分が切除され、公転経路方向に関し遊星ロー
ラ、ニードルローラ軸受けおよび遊星軸間に、実質的に
隙間がないようにしている構成とした。
【０００９】
【作用】上記の構成において、遊星ローラが外輪と太陽
軸との間で圧縮されて楕円形に変形するのに対して、遊
星軸は、その外周２個所の削除部により予め、遊星ロー
ラの変形形状と概ね同じような断面形状で、かつ公転経
路方向にはニードルローラ軸受の内側に隙間なく嵌まる
大きさになっているから、遊星ローラは実質的に遊びの
ない状態で遊星軸に軸支されることになる。
【００１０】
【実施例】以下、本発明の詳細を図１ないし図３に示す
一実施例に基づいて説明する。図１は、本発明の一実施
例に係る遊星ローラ式動力伝達装置の断面図、図２はそ
の要部である遊星ローラの拡大正面図、図３は、遊星軸
の削除個所を示す正面図である。
【００１１】図１に示すように、この実施例の動力伝達
装置が、ハウジング１に固定の外輪２と、この外輪２の
内側に同心に配置された太陽軸３と、太陽軸３と外輪２
との間に圧接状に介装された複数の遊星ローラ４，…
と、遊星ローラ４の公転により回転するキャリア５とを
備えている点は、従来の装置と同じである。また、太陽
軸３が高速の入出力軸になるとともに、キャリア５に低
速の入出力軸６が取り付けられており、各遊星ローラ４
が、キャリア５に突設された遊星軸７にニードルローラ
軸受８のような軸受を介して回転自在に軸支される点
も、前記した従来の装置と同じである。
【００１２】この実施例の遊星ローラ式動力伝達装置
は、前記の遊星軸７の寸法、形状に特徴があり、図２に
示すように、遊星軸７には、遊星ローラ４の内側に設け
られるニードルローラ軸受８の内接円径に対して大きい
外径Ｄのものが使用され、かつ、遊星軸７の外周各部の
うち、公転経路の外径側および内径側の両部分が削除さ
れて、一対の削除部７ａ，７ｂが形成されている。
【００１３】遊星軸７の外径寸法Ｄは、遊星ローラ４を
外輪２と太陽軸３との間に圧入することにより、遊星ロ
ーラ４とニードルローラ軸受８とが楕円形に変形するの
を考慮して設定したもので、楕円形に変形したときのニ
ードルローラ軸受８の内接楕円の長軸方向の内径に相当
する。
【００１４】また、遊星軸７に形成される削除部７ａ，
７ｂは、各遊星軸７をキャリア５に取り付けた後に、各
遊星軸７の外周部を、公転経路と同心に設定された削除
線Ｃ1，Ｃ2に沿って研削して形成されるものである。こ
の研削を行うには、図３に示すように、キャリア５にす
べての遊星軸７を取り付けた後、これら遊星軸７を公転
経路Ｅの中心の周りで旋回させながら、遊星軸７の外周
部に回転砥石を作用させる。なお、各削除部７ａ，７ｂ
の削除深さは、具体的には、外径１０ｍｍの遊星軸で、
１０μｍ程度である。
【００１５】上記の構成において、組立に当たって、外
輪２と太陽軸３との間に遊星ローラ４を圧入すると、遊
星ローラ４とその内側のニードルローラ軸受８は、圧縮
されて楕円形に変形するが、遊星軸７は、遊星ローラ４
の変形形状と同じく、ほぼ長円の断面形状になってお
り、しかも、変形したニードルローラ軸受８の内側に隙
間なく嵌まる大きさになっているから、遊星ローラ４と
遊星軸７との間には実質的に遊びがなくなる。
【００１６】ところで、遊星ローラ式動力伝達装置を高
精度の位置決め装置の減速機として利用する場合では、
特に遊星軸７それぞれの中心を結ぶＰＣＤの円弧をキャ
リア５の回転中心からの円弧と一致させるように、キャ
リア５に対する遊星軸７の取付精度を高精度に行う必要
があり、組立工程の負担が大きくなる。しかし、本実施
例のように、遊星軸７の外周部に対する研削により削除
部７ａ，７ｂを形成するようにしていれば、キャリア５
への遊星軸７の取付位置に若干のずれがあっても、遊星
軸７の外周部のうち、ずれにより正規位置からはみ出る
部分が削り取られるから、遊星軸７それぞれの外接円軌
跡がキャリア５の回転中心からの円弧と一致することに
なり、これによって、遊星軸７のＰＣＤのばらつきが補
正されることになる。したがって、キャリア５への遊星
軸７の取付は、特に高い精度で行う必要がなくなり、組
立工程の負担が軽減されるようになる。
【００１７】
【００１８】
【発明の効果】以上述べたように、本発明によれば、遊
星軸の断面が圧入により変形した遊星ローラの内径側に
合致する形状、大きさになっているから、遊星ローラは
遊星軸に実質的には遊びがない状態で軸支されることに
なり、回転変動を激減できて高精度な位置決め装置とし
て利用できるようになる。
【００１９】しかも、楔部材を用いる従来技術のように
新たに部材を付加するものではないから、容易に実施し
うる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary roller type power transmission device, and more particularly, to a planetary roller rotatably supported on a carrier via a needle roller bearing. Related to the structure of the planetary shaft. [0002] Generally, a planetary roller type power transmission device is
As shown in FIG.
And a sun shaft 23 concentrically arranged inside the outer ring 22.
, A plurality of planetary rollers 24,... Disposed between the sun shaft 23 and the outer ring 22 in a press-contact manner, and a carrier 25 that rotates by the revolution of the planetary rollers 24. In a device with one stage of acceleration / deceleration, the sun shaft 23 is a high-speed input / output shaft, and the low-speed input / output shaft 26 is directly connected to the carrier 25. In the conventional apparatus, each planetary roller 2
4 is rotatably mounted on a planet shaft 27 protruding from the carrier 25 via a bearing such as a needle roller bearing 28. The needle roller bearing 28 of this example is a planetary shaft 2
7 is an inner ring, and the planetary roller 24 is an outer ring, and includes a plurality of needle rollers and a retainer. In this type of power transmission device, since the planetary roller 24 is press-fitted between the outer ring 22 and the sun shaft 23, the amount of the planetary roller 24 is small between the two. However, it is compressed and deformed into an elliptical shape, and there is play between the planetary roller 24 and the planetary shaft 27 before and after in the revolving direction. The play created between the planetary roller 24 and the planetary shaft 27 in this manner corresponds to backlash of the gear mechanism, and causes rotation fluctuation. On the other hand, conventionally, for example,
As disclosed in Japanese Patent No. 32256, there is a structure in which a wedge member is press-fitted on the inner diameter side of a bearing on the outer periphery of a planetary shaft to reduce play created between the planetary roller and the planetary shaft. , Not only takes time to assemble,
A new structure for preventing the wedge member from falling off is required, and there is a problem in actual production. The present invention has been made in view of the above-described conventional problems, and has as its object to reduce the play between the planetary roller and the planetary shaft as much as possible with a simple structure to suppress rotation fluctuation. In order to achieve the above object, the present invention provides an outer ring fixed to a housing, a sun shaft arranged concentrically inside the outer ring, a sun shaft and the outer ring. A plurality of planetary rollers interposed in a press-contact manner therebetween, and a carrier that rotates by the revolution of the planetary rollers, and each of the planetary rollers is held by a retainer on a planetary shaft protruding from the carrier and a needle roller bearing. In the planetary roller type power transmission device which is rotatably supported via the shaft, the outer diameter of the planetary shaft is set to be larger than the inscribed circle diameter of the needle roller bearing, and the needle roller bearing of the planetary shaft is mounted. of outer <br/> circumference each section to be, both parts of the outer diameter side and inner diameter side is excised an arc of revolution path concentric with the planetary rollers relates revolution path direction, between the needle roller bearing and the planetary axes, substantially To Between is a structure that is so not. In the above construction, the planetary roller is compressed between the outer ring and the sun shaft to be deformed into an elliptical shape, whereas the planetary shaft is preliminarily formed by removing the two outer peripheral portions thereof. Since the cross-sectional shape is almost the same as the deformed shape of the roller, and it is large enough to fit inside the needle roller bearing in the direction of the revolving path without any gap, the planetary roller has substantially no play in the planetary shaft. Will be pivotally supported. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the present invention will be described below with reference to one embodiment shown in FIGS. FIG. 1 is a sectional view of a planetary roller type power transmission device according to one embodiment of the present invention, FIG. 2 is an enlarged front view of a planetary roller which is a main part thereof, and FIG. 3 is a front view showing a deleted portion of a planetary shaft. It is. As shown in FIG. 1, the power transmission device of this embodiment includes an outer ring 2 fixed to a housing 1, a sun shaft 3 disposed concentrically inside the outer ring 2, a sun shaft 3 and the outer ring 2
And a plurality of planetary rollers 4, which are interposed in a press-contact state between them.
And a carrier 5 rotating by the revolution of the planetary roller 4 are the same as the conventional apparatus. The sun shaft 3 is a high-speed input / output shaft, and the low-speed input / output shaft 6 is attached to the carrier 5.
However, it is the same as the above-described conventional device in that the planetary shaft 7 protruding from the carrier 5 is rotatably supported via a bearing such as a needle roller bearing 8. The planetary roller type power transmission of this embodiment is characterized by the size and shape of the planetary shaft 7, and is provided inside the planetary roller 4 on the planetary shaft 7, as shown in FIG. An outer diameter D having a larger outer diameter than the inscribed circle diameter of the needle roller bearing 8 is used, and both the outer diameter side and the inner diameter side of the orbital path of the outer circumference of the planetary shaft 7 are deleted. A pair of deletion parts 7a and 7b are formed. The outer diameter D of the planetary shaft 7 takes into account that the planetary roller 4 and the needle roller bearing 8 are deformed into an elliptical shape by press-fitting the planetary roller 4 between the outer ring 2 and the sun shaft 3. And corresponds to the inner diameter in the major axis direction of the inscribed ellipse of the needle roller bearing 8 when deformed into an elliptical shape. [0014] In addition, a deletion part 7a,
7b, after the attachment of each planet axle 7 to the carrier 5, the outer peripheral portion of each planetary shaft 7, along the revolving path and delete line C 1, which is set concentrically, C 2 intended to be formed by grinding is there. To perform this grinding, as shown in FIG. 3, after all the planetary shafts 7 are attached to the carrier 5, while rotating these planetary shafts 7 around the center of the revolving path E, the outer peripheral portion of the planetary shafts 7 is rotated. A rotating whetstone acts on Each of the deletion units 7a and 7b
Specifically, the removal depth of the planetary shaft with an outer diameter of 10 mm
It is about 10 μm. In the above configuration, when the planetary roller 4 is press-fitted between the outer ring 2 and the sun shaft 3 during assembly, the planetary roller 4 and the needle roller bearing 8 inside the planetary roller 4 are compressed and deformed into an elliptical shape. , The planetary shaft 7 is the planetary roller 4
As with the deformed shape of the above, the cross-sectional shape is substantially elliptical, and the size is such that it fits without any clearance inside the deformed needle roller bearing 8. Has virtually no play. In the case where the planetary roller type power transmission device is used as a speed reducer of a high-precision positioning device,
In particular, it is necessary to perform the mounting accuracy of the planetary shaft 7 to the carrier 5 with high accuracy so that the arc of the PCD connecting the centers of the respective planetary shafts 7 coincides with the circular arc from the rotation center of the carrier 5. growing. However, if the deleted portions 7a and 7b are formed by grinding the outer peripheral portion of the planetary shaft 7 as in this embodiment, the carrier 5
Even if there is a slight shift in the mounting position of the planetary shaft 7, the portion of the outer peripheral portion of the planetary shaft 7 that protrudes from the normal position is cut off, so that the circumscribed circular locus of each of the planetary shafts 7 This coincides with the arc from the center of rotation, thereby correcting the variation of the PCD of the planetary shaft 7. Therefore, it is not necessary to attach the planetary shaft 7 to the carrier 5 with particularly high precision, and the burden on the assembling process is reduced. As described above, according to the present invention, since the cross section of the planetary shaft has a shape and a size that match the inner diameter side of the planetary roller deformed by press-fitting, Since the planetary roller is supported by the planetary shaft with substantially no play, the rotation fluctuation can be greatly reduced, and the planetary roller can be used as a highly accurate positioning device. In addition, unlike the prior art using a wedge member, a new member is not added, so that it can be easily implemented.
【図面の簡単な説明】
【図１】本発明の一実施例に係る遊星ローラ式動力伝達
装置の断面図。
【図２】上記実施例の要部である遊星ローラの拡大正面
図。
【図３】上記実施例の遊星軸の削除個所を示す正面図。
【図４】従来の遊星ローラ式動力伝達装置の断面図。
【符号の説明】
１ ハウジング
２ 外輪
３ 太陽軸
４ 遊星ローラ
５ キャリア
７ 遊星軸
７ａ，７ｂ 削除部
８ ニードルローラ軸受BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of a planetary roller type power transmission device according to one embodiment of the present invention. FIG. 2 is an enlarged front view of a planetary roller which is a main part of the embodiment. FIG. 3 is a front view showing a portion where the planetary shaft is deleted in the embodiment. FIG. 4 is a sectional view of a conventional planetary roller type power transmission device. [Description of Signs] 1 Housing 2 Outer ring 3 Sun shaft 4 Planetary roller 5 Carrier 7 Planetary shafts 7a, 7b Deletion section 8 Needle roller bearing
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭56−18148（ＪＰ，Ａ) 特開 昭61−84455（ＪＰ，Ａ) 特開 昭63−231049（ＪＰ，Ａ) 実開 昭61−84259（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16H 13/08 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-56-18148 (JP, A) JP-A-61-84455 (JP, A) JP-A-63-231049 (JP, A) 84259 (JP, U) (58) Field surveyed (Int. Cl. 7 , DB name) F16H 13/08
Claims (1)
内側に同心に配置された太陽軸と、太陽軸と外輪との間
に圧接状に介装された複数の遊星ローラと、遊星ローラ
の公転により回転するキャリアとを備え、各遊星ローラ
がキャリアに突設された遊星軸に保持器に保持されたニ
ードルローラ軸受を介して回転自在に支持されている遊
星ローラ式動力伝達装置において、 遊星軸の外径が、ニードルローラ軸受の内接円径に対し
て大きく設定されるとともに、遊星軸のニードルローラ
軸受が装着される外周各部のうち、公転経路と同心の円
弧に外径側および内径側の両部分が切除され、公転経路
方向に関し遊星ローラ、ニードルローラ軸受けおよび遊
星軸間に、実質的に隙間がないようにしている、ことを
特徴とする遊星ローラ式動力伝達装置。(57) [Claims 1] An outer ring fixed to a housing, a sun shaft arranged concentrically inside the outer ring, and a press-fit interposed between the sun shaft and the outer ring. A plurality of planetary rollers and a carrier that rotates by the revolution of the planetary rollers are provided, and each planetary roller is rotatably supported by a planetary shaft protruding from the carrier via a needle roller bearing held by a holder. in the planetary roller type power transmission device, the outer diameter of the planetary shaft, while being largely set against the inscribed circle diameter of the needle roller bearings, needle roller of the planetary shaft
A circle concentric with the orbital path of each part of the outer circumference where the bearing is mounted
A planetary roller type characterized in that both the outer diameter side and the inner diameter side are cut off in the arc so that there is substantially no gap between the planetary roller, the needle roller bearing and the planetary shaft in the direction of the revolution path. Power transmission device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32396092A JP3383809B2 (en) | 1992-12-03 | 1992-12-03 | Planetary roller type power transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32396092A JP3383809B2 (en) | 1992-12-03 | 1992-12-03 | Planetary roller type power transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06174026A JPH06174026A (en) | 1994-06-21 |
| JP3383809B2 true JP3383809B2 (en) | 2003-03-10 |
Family
ID=18160557
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32396092A Expired - Fee Related JP3383809B2 (en) | 1992-12-03 | 1992-12-03 | Planetary roller type power transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3383809B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6300005B2 (en) * | 2013-12-12 | 2018-03-28 | 株式会社ジェイテクト | Planetary roller type transmission |
| JP6278235B2 (en) | 2013-12-27 | 2018-02-14 | 株式会社ジェイテクト | Planetary roller type transmission |
-
1992
- 1992-12-03 JP JP32396092A patent/JP3383809B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06174026A (en) | 1994-06-21 |
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