JPH0633802B2 - Multi-stage transmission - Google Patents

Multi-stage transmission

Info

Publication number
JPH0633802B2
JPH0633802B2 JP59195345A JP19534584A JPH0633802B2 JP H0633802 B2 JPH0633802 B2 JP H0633802B2 JP 59195345 A JP59195345 A JP 59195345A JP 19534584 A JP19534584 A JP 19534584A JP H0633802 B2 JPH0633802 B2 JP H0633802B2
Authority
JP
Japan
Prior art keywords
sun
ring
planetary
sun wheel
outer ring
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
Application number
JP59195345A
Other languages
Japanese (ja)
Other versions
JPS6174952A (en
Inventor
章 近森
浩一 上田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koyo Seiko Co Ltd
Original Assignee
Koyo Seiko Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Koyo Seiko Co Ltd filed Critical Koyo Seiko Co Ltd
Priority to JP59195345A priority Critical patent/JPH0633802B2/en
Publication of JPS6174952A publication Critical patent/JPS6174952A/en
Publication of JPH0633802B2 publication Critical patent/JPH0633802B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Description

【発明の詳細な説明】 産業上の利用分野 本発明は、自動車、機械等に用いられる多段式変速機に
関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-stage transmission used in automobiles, machines and the like.

従来技術 従来の遊星ローラを具えた多段変速機は、例えば第５図
に記載のように、同軸的に配列された入力軸1 及び出力
軸と、入力軸1 に設けられた第１太陽ローラ2 と、ハウ
ジング24内に嵌合固定される一対の外輪3 、12と、第１
太陽ローラ2 の外周と一方の外輪3 の内周間に転動可能
に配置された複数個の第１遊星ローラ4 と、第１遊星ロ
ーラ4 を円周方向等間隔にピン7 により回転可能に軸支
する第１環状ローラキャリア8 と、該第１環状ローラキ
ャリア8 と同体的に形成されかつ第１太陽ローラ2 と出
力軸17の対峙する両端面間に介装された第２太陽ローラ
11と、該第２太陽ローラ11の外周と他方の外輪12の内周
間に転動可能に配置されかつ出力軸17の端部にもうけた
第２環状ローラキャリア15により回転可能にもうけた第
２環状ローラキャリア15により回転可能に軸支された第
２遊星ローラ13とを具え、出力軸17をハウジング19内に
所定の軸方向間隔をもって嵌合された一対のころがり軸
受により回転可能に支持した構造（例えば、実開昭56-1
71457 号公報第１図に記載のもの）である。そして、こ
の従来公知の多段変速機は、入力軸1 の動力を第１太陽
ローラ2 、第１遊星ローラ4 、及び外輪3 から成る第１
減速機構10により減速し、減速された動力をピン7 によ
り第１環状ローラキャリア8 、第２遊星ローラ及び外輪
12とから成る第２減速機構20に伝達してさらに減速し、
ピン15により出力軸17に伝達する。2. Description of the Related Art A conventional multi-stage transmission including a planetary roller is, for example, as shown in FIG. 5, an input shaft 1 and an output shaft arranged coaxially, and a first sun roller 2 provided on the input shaft 1. And a pair of outer rings 3 and 12 fitted and fixed in the housing 24, and the first
A plurality of first planetary rollers 4 rotatably arranged between the outer periphery of the sun roller 2 and the inner periphery of one outer ring 3, and the first planetary roller 4 can be rotated by a pin 7 at equal intervals in the circumferential direction. A first annular roller carrier 8 which is axially supported, and a second sun roller which is formed integrally with the first annular roller carrier 8 and is interposed between opposite end surfaces of the first sun roller 2 and the output shaft 17.
11 and a second annular roller carrier 15 disposed rotatably between the outer circumference of the second sun roller 11 and the inner circumference of the other outer ring 12 and rotatably provided by the second annular roller carrier 15 provided at the end of the output shaft 17. A second planetary roller 13 rotatably supported by two annular roller carriers 15, and an output shaft 17 is rotatably supported by a pair of rolling bearings fitted in a housing 19 with a predetermined axial gap. Structure (for example, actual development 56-1
No. 71457, disclosed in FIG. 1). In this conventionally known multi-stage transmission, the power of the input shaft 1 is divided into the first sun roller 2, the first planetary roller 4, and the outer ring 3 to form the first power.
The speed reduced by the speed reduction mechanism 10 is used to reduce the power reduced by the pin 7 to the first annular roller carrier 8, the second planetary roller and the outer ring.
It is transmitted to the second reduction mechanism 20 composed of 12 to further reduce the speed,
It is transmitted to the output shaft 17 by the pin 15.

18a 、18b 、は軸受、19はケース、21は回転軸心であ
る。18a and 18b are bearings, 19 is a case, and 21 is a rotation axis.

発明が解決しようとする問題点 前記の従来構造の減速機は、次の問題点をもっている。
すなわち、第１減速機構10で減速されトルクの増大され
た動力が第２減速機構20に伝達されるため、第２減速機
構20の第２太陽ローラ11、第２遊星ローラ13、外輪12等
の直径及び幅寸法を、強度面から、第１減速機構10のそ
れらよりも大きくしなければならない。このため、減速
機の全長A 及び外径B が必然的に大きくなり、減速機が
大型になる。また、外輪3 、12に対する各遊星ローラ4
、13の軸方向移動を制限する手段が設けられていな
い。このため、減速機の運転中、各遊星ローラ4 、13が
スキューを起こして過大なスラスト荷重を発生し、転動
面で焼付を生じたり、振動及び騒音を生じる。Problems to be Solved by the Invention The speed reducer having the conventional structure has the following problems.
That is, since the power reduced in the first reduction mechanism 10 and increased in torque is transmitted to the second reduction mechanism 20, the second sun roller 11, the second planetary roller 13, the outer ring 12, etc. of the second reduction mechanism 20 are transmitted. The diameter and width dimensions must be larger than those of the first reduction mechanism 10 in terms of strength. Therefore, the overall length A and outer diameter B of the reducer are necessarily large, and the reducer becomes large. Also, each planetary roller 4 for the outer ring 3, 12
, 13 are not provided with means for limiting the axial movement. Therefore, during operation of the speed reducer, the planetary rollers 4 and 13 are skewed to generate an excessive thrust load, causing seizure on the rolling surfaces, vibration and noise.

また、出力軸17が、減速機構以外のケース19内に設けた
軸受18a 、18b で支持され、しかもモーメント荷重の影
響を少なくするために一対の軸受の間隔を適度に大きく
してあるため、減速機の全長A がますます大きくなる。
さらに、外径を異にする２個の外輪3 、12を嵌合するた
めのハウジング24の二つの軸受座の加工が、両軸受座の
同心度を高精度に保証せねばならないため、複雑となり
高価なものとなる。In addition, the output shaft 17 is supported by bearings 18a, 18b provided inside the case 19 other than the reduction mechanism, and the space between the pair of bearings is appropriately increased to reduce the influence of moment load. The total length A of the machine becomes larger.
Further, the processing of the two bearing seats of the housing 24 for fitting the two outer rings 3 and 12 having different outer diameters is complicated because the concentricity of both bearing seats must be guaranteed with high accuracy. It will be expensive.

問題点を解決するための手段 本発明は、同軸的に配列された一対の回転軸間に多段の
遊星摩擦機構部を配置した多段式変速機において、一方
の回転軸に設けられた第１太陽輪と、ハウジングに嵌合
固定される第１の外輪と、第１太陽輪の外周と第１の外
輪の内周間に転動可能に配置された複数個の第１遊星ロ
ーラと、該第１遊星ローラを円周方向等間隔に回転可能
に軸支する第１環状ローラキャリアと、該第１環状ロー
ラキャリアから他方の回転軸の内端部を覆うよう軸方向
に延設されかつ一対の回転軸のうち少なくとも他方の回
転軸の内端部に回転可能に支持された円筒状の第２太陽
輪と、ハウジングに嵌合固定される第２の外輪と、該第
２太陽輪の外周と第２の外輪の内周間に転動可能に配置
された複数個の第２遊星ローラと、該第２遊星ローラを
円周方向等間隔に回転可能に軸支しかつ前記他方の回転
軸に動力伝達可能に設けられた第２環状ローラキャリア
とを有する構成とした。Means for Solving the Problems The present invention relates to a multi-stage transmission in which a multi-stage planetary friction mechanism section is arranged between a pair of coaxially arranged rotary shafts, and a first sun provided on one rotary shaft. A ring, a first outer ring fitted and fixed to the housing, a plurality of first planetary rollers rotatably arranged between the outer periphery of the first sun ring and the inner periphery of the first outer ring, and A first annular roller carrier that rotatably supports the first planetary roller rotatably at equal intervals in a circumferential direction, and a pair of axially extending from the first annular roller carrier so as to cover the inner end portion of the other rotating shaft. A cylindrical second sun ring rotatably supported on the inner end of at least the other of the rotary shafts, a second outer ring fitted and fixed to the housing, and an outer periphery of the second sun ring. A plurality of second planetary rollers rotatably arranged between the inner periphery of the second outer ring and the second planetary rollers; The star roller is rotatably supported at equal intervals in the circumferential direction, and a second annular roller carrier is provided on the other rotating shaft so as to be capable of transmitting power.

作 用 本発明の前記構成において、一方の回転軸30の動力は、
外輪35、第１太陽輪33、第１遊星ローラ38及び第１環状
ローラキャリア39から成る第１減速機構により周知の方
法で減速され、この減速された動力を第１環状ローラキ
ャリア39と同体的に形成された第２太陽輪44に伝達さ
れ、前記外輪35、第２太陽輪44、第２遊星ローラ47及び
第２環状ローラキャリア49から成る第２減速機構により
周知の方法で更に減速されて他方の回転軸31に伝達され
る。Operation In the above-mentioned configuration of the present invention, the power of the one rotating shaft 30 is
It is decelerated by a known method by a first reduction mechanism composed of an outer ring 35, a first sun wheel 33, a first planetary roller 38, and a first annular roller carrier 39, and this decelerated power is integrated with the first annular roller carrier 39. Is transmitted to the second sun wheel 44 formed on the second sun wheel 44, and further decelerated by a known method by a second speed reducing mechanism including the outer wheel 35, the second sun wheel 44, the second planetary roller 47 and the second annular roller carrier 49. It is transmitted to the other rotating shaft 31.

前記外輪35の内周面37と第１太陽輪33の外周面36間に転
動可能に圧接状態で配置された第１遊星ローラ38と、前
記外輪35の内周面37と第２太陽輪44の外周面45間に転動
可能に圧接状態で配置された第２遊星ローラ47とは、第
１遊星ローラ38と第２遊星ローラ47の間に外輪35に対し
浮動的に又は圧入嵌合して設けられたスペーサリング50
と、一つの外輪35の両端部に設けたスラストリング51、
52、止め輪53とにより一つの外輪35に対して減速機の運
転中、軸方向に移動を制限されて位置決めされて転動す
る。A first planetary roller 38 rotatably arranged between the inner peripheral surface 37 of the outer ring 35 and the outer peripheral surface 36 of the first sun ring 33, and the inner peripheral surface 37 of the outer ring 35 and the second sun ring. The second planetary roller 47, which is rollably arranged between the outer peripheral surfaces 45 of the shaft 44 in a press contact state, is floatingly or press-fitted to the outer ring 35 between the first planetary roller 38 and the second planetary roller 47. Spacer ring 50
And thrust rings 51 provided at both ends of one outer ring 35,
52 and stop ring 53, one outer ring 35 is positioned and rolled while the movement of the speed reducer is restricted in the axial direction during operation.

従って、第１太陽輪33は第１遊星ローラ38を介して外輪
35に対し軸方向に移動を制限され、第２太陽輪44は第２
遊星ローラ47を介して前記外輪35に対し軸方向に移動を
制限され、さらに第２環状ローラキャリア49が止め輪66
により軸方向に移動を制限されてそれぞれ回転する。Therefore, the first sun wheel 33 is connected to the outer ring via the first planetary roller 38.
The axial movement of the second sun wheel 44 is restricted with respect to 35
The movement of the outer ring 35 is restricted in the axial direction via the planetary rollers 47, and the second annular roller carrier 49 further includes a retaining ring 66.
The movement is restricted in the axial direction by the so that they rotate respectively.

また、前記第１太陽輪33の嵌合固着される回転軸30を出
力軸とし、前記第２環状ローラキャリア49の嵌合固着さ
れる回転軸31を入力軸として多段式増速機を構成する場
合は、前記の多段減速機における第２減速機構が第１増
速機構として機能し、同じく第１減速機構が第２増速機
構として機能することになる。Further, the rotary shaft 30 to which the first sun wheel 33 is fitted and fixed is used as an output shaft, and the rotary shaft 31 to which the second annular roller carrier 49 is fitted and fixed is used as an input shaft to form a multi-stage gearbox. In this case, the second speed reducing mechanism in the multi-stage speed reducer functions as the first speed increasing mechanism, and the first speed reducing mechanism also functions as the second speed increasing mechanism.

実施例 本発明の一実施例を図において説明する。第１図及び第
２図において、本発明の変速機は、同軸的に配列された
一対の回転軸30、31と、一方の回転軸30にスプライン32
嵌合して設けられた第１太陽輪33と、ハウジング34に嵌
合固定される一つの外輪35と、第１太陽輪33の外周面36
と外輪35の内周面37間に転動可能にかつ半径方向に圧接
された状態で配置された複数個の第１遊星ローラ38と、
該第１遊星ローラ38を円周方向等間隔に回転可能に軸支
する第１環状ローラキャリア39と、該第１環状ローラキ
ャリア39と同体的に形成されかつ一対の回転軸30、31の
対峙する両内端部40、41にまたがってそれぞれニードル
ローラ42、43を介して回転可能に嵌合された第２太陽輪
44と、該第２太陽輪44の外周面45と前記外輪35の内周面
37間に転動可能にかつ半径方向に圧接された状態で配置
された複数個の第２遊星ローラ47と、該第２遊星ローラ
47を円周方向等間隔に回転可能に軸支しかつ他方の回転
軸31に動力伝達可能にスプライン48嵌合して固定された
第２環状ローラキャリア49と、一つの外輪35と一対の回
転軸30、31との間で回転する第１太陽輪33、第１遊星ロ
ーラ38、第１環状ローラキャリア39、第２太陽輪44、第
２遊星ローラ47、第２環状ローラキャリア49の軸方向移
動を外輪35に対し制限する手段46、50、51、52、53、6
3、64、65、66とを具えている。Embodiment An embodiment of the present invention will be described with reference to the drawings. 1 and 2, the transmission of the present invention includes a pair of coaxially arranged rotary shafts 30, 31 and a spline 32 on one rotary shaft 30.
The first sun ring 33 fitted and provided, one outer ring 35 fitted and fixed to the housing 34, and the outer peripheral surface 36 of the first sun ring 33.
And a plurality of first planetary rollers 38 which are arranged between the inner peripheral surface 37 of the outer ring 35 and the outer ring 35 so as to be rollable and in pressure contact with each other in the radial direction,
A first annular roller carrier 39 that rotatably supports the first planetary roller 38 at equal intervals in the circumferential direction, and a pair of rotating shafts 30 and 31 that are formed integrally with the first annular roller carrier 39 and face each other. A second sun wheel rotatably fitted over both inner ends 40, 41 via needle rollers 42, 43, respectively.
44, the outer peripheral surface 45 of the second sun wheel 44 and the inner peripheral surface of the outer wheel 35
A plurality of second planet rollers 47 arranged between 37 so as to be rollable and pressed in the radial direction; and the second planet rollers 47.
A second annular roller carrier 49, which is rotatably supported at equal intervals in the circumferential direction and fixed to the other rotary shaft 31 by spline 48 fitting and fixed, and one outer ring 35 and a pair of rotations. The axial direction of the first sun wheel 33, the first planetary roller 38, the first annular roller carrier 39, the second sun wheel 44, the second planetary roller 47, and the second annular roller carrier 49 that rotate between the shafts 30 and 31. Means 46, 50, 51, 52, 53, 6 for restricting movement to the outer ring 35
It has 3, 64, 65 and 66.

前記外輪35の内周面37は、第１遊星ローラ38と第２遊星
ローラ47に対する同一直径の軌道面を形成し、前記外輪
35の内周面37と第１太陽輪33の外周面36間に転動可能に
圧接状態で配置された第１遊星ローラ38と、前記外輪35
の内周面37と第２太陽輪44の外周面45間に転動可能に圧
接状態で配置された第２遊星ローラ47とは、第１遊星ロ
ーラ38と第２遊星ローラ47の間に外輪35に対し浮動的に
又は圧入嵌合して設けられたスペーサリング50と、一つ
の外輪35の両端部に設けたスラストリング51、52、止め
輪53とにより一つの外輪35に対して減速機の運転中、軸
方向に移動を制限されて位置決めされて転動する。The inner peripheral surface 37 of the outer ring 35 forms a raceway surface having the same diameter with respect to the first planetary roller 38 and the second planetary roller 47.
A first planetary roller 38 rotatably disposed between the inner peripheral surface 37 of 35 and the outer peripheral surface 36 of the first sun ring 33, and the outer ring 35.
The second planetary roller 47, which is rotatably disposed between the inner peripheral surface 37 and the outer peripheral surface 45 of the second sun wheel 44, is the outer ring between the first planetary roller 38 and the second planetary roller 47. A spacer ring 50 provided in a floating or press fit manner with respect to 35, thrust rings 51, 52 and retaining rings 53 provided at both ends of one outer ring 35, and a reduction gear for one outer ring 35. During operation, it is positioned in the axial direction and rolls while being positioned.

前記第２遊星ローラ47は、第１遊星ローラ38より伝達ト
ルクが大きく、また第２太陽輪44の厚みを比較的大きく
して強度を保つため、第１遊星ローラ38の外周直径d と
幅寸法w ′よりも小さい外周直径d ′と大きい幅寸法w
に形成されている。The second planetary roller 47 has a larger transmission torque than the first planetary roller 38, and the second sun wheel 44 has a relatively large thickness to maintain strength, so that the outer diameter d and the width dimension of the first planetary roller 38 are increased. Outer diameter d ′ smaller than w ′ and large width w
Is formed in.

また前記第２太陽輪44は、外周に第２遊星ローラ47が転
動する軌道溝46を形成し、一対の回転軸30、31の両内端
部40、41にそれぞれニードルローラ42、43を介して回転
可能に嵌合されている。Further, the second sun wheel 44 has an orbital groove 46 on the outer periphery thereof on which the second planetary roller 47 rolls, and needle rollers 42 and 43 are respectively provided on both inner end portions 40 and 41 of the pair of rotary shafts 30 and 31. It is rotatably fitted through.

また、第１環状ローラキャリア39及び第２太陽輪44は、
第２太陽輪44の外周に設けた軌道溝46上を第２遊星ロー
ラ47が転動しているから、前記軌道溝46により軸方向移
動が制限される。55は第１遊星ローラ38を回転可能に軸
支するピンで、第１環状ローラキャリア39に円周等間隔
に設けた孔56に一端を圧入嵌合され他端を第１遊星ロー
ラ38の軸孔57にニードルローラ58を介して挿入されてい
る。59は第２遊星ローラ47を回転可能に軸支するピン
で、第２環状ローラキャリア49に円周等間隔に設けた孔
60に一端を圧入嵌合され他端を第２遊星ローラ47の軸孔
61にブッシュ62介して挿入されている。63、64は、第１
太陽輪33の両端に設けられ第１遊星ローラ38を介して外
輪35に対し第１太陽輪33の軸方向移動を制限するスラス
トリングであり、65は第１太陽輪33とスラストリング6
3、64を回転軸30上に軸方向に固定する止め輪である。6
6は第２環状ローラキャリア49を回転軸31上に軸方向に
固定する止め輪であり、第２環状ローラキャリア49は止
め輪66によって係止されて軸方向に移動を制限されてい
る。67は回転軸31が嵌合されるハウジングである。68は
回転軸31を支承するころがり軸受、69は一対の回転軸3
0、31の回転軸心である。Further, the first annular roller carrier 39 and the second sun wheel 44 are
Since the second planetary roller 47 is rolling on the raceway groove 46 provided on the outer periphery of the second sun wheel 44, the movement in the axial direction is restricted by the raceway groove 46. Reference numeral 55 is a pin that rotatably supports the first planetary roller 38. One end of the pin 55 is press-fitted into holes 56 provided in the first annular roller carrier 39 at equal intervals around the circumference, and the other end is the shaft of the first planetary roller 38. It is inserted into the hole 57 via a needle roller 58. Reference numeral 59 is a pin that rotatably supports the second planetary roller 47, and holes formed in the second annular roller carrier 49 at equal intervals around the circumference.
One end is press-fitted into 60 and the other end is the shaft hole of the second planetary roller 47.
It is inserted into 61 via bush 62. 63 and 64 are the first
Thrust rings are provided at both ends of the sun ring 33 to restrict the axial movement of the first sun ring 33 with respect to the outer ring 35 via the first planetary rollers 38, and 65 is the first sun ring 33 and the thrust ring 6
It is a retaining ring that fixes 3, 64 on the rotating shaft 30 in the axial direction. 6
Reference numeral 6 denotes a retaining ring that fixes the second annular roller carrier 49 on the rotating shaft 31 in the axial direction, and the second annular roller carrier 49 is locked by the retaining ring 66 and is restricted from moving in the axial direction. 67 is a housing into which the rotary shaft 31 is fitted. 68 is a rolling bearing that supports the rotating shaft 31, 69 is a pair of rotating shafts 3
The axis of rotation is 0 and 31.

前記の構成において、一方の回転軸30の動力は、外輪3
5、第１太陽輪33、第１遊星ローラ38及び第１環状ロー
ラキャリア39から成る第１減速機構により周知の方法で
減速される。すなわち、第１減速機構の減速比ｉ1 は、
下記式のようになる。In the above structure, the power of one rotating shaft 30 is the outer ring 3
5, the first sun wheel 33, the first planetary roller 38 and the first annular roller carrier 39 reduce the speed in a known manner by the first speed reducing mechanism. That is, the reduction ratio i1 of the first reduction mechanism is
It becomes like the following formula.

但し、r1は第１太陽輪33の外径、r2は外輪35の内径であ
る。 However, r1 is the outer diameter of the first sun ring 33, and r2 is the inner diameter of the outer ring 35.

この減速された動力は、ピン55により第１環状ローラキ
ャリア39と同体的に形成された第２太陽輪44に伝達さ
れ、前記外輪35、第２太陽輪44、第２遊星ローラ47及び
第２環状ローラキャリア49から成る第２減速機構により
周知の方法で更に減速されて他方の回転軸31に伝達され
る。すなわち第２減速機の減速比ｉ2 は、下記式のよ
うになる。This decelerated power is transmitted by the pin 55 to the second sun wheel 44 formed integrally with the first annular roller carrier 39, and the outer wheel 35, the second sun wheel 44, the second planetary roller 47 and the second sun roller 44 are formed. It is further decelerated by a second deceleration mechanism including an annular roller carrier 49 by a known method and transmitted to the other rotating shaft 31. That is, the reduction ratio i2 of the second reduction gear is expressed by the following equation.

但し、R1は第２太陽輪44の外径、r2は外輪35の内径であ
る。 However, R1 is the outer diameter of the second sun ring 44, and r2 is the inner diameter of the outer ring 35.

従って、回転軸31はｉ＝ｉ1 ×ｉ2 の減速比で減速され
た回転数で回転軸30と同一方向に回転される。Therefore, the rotating shaft 31 is rotated in the same direction as the rotating shaft 30 at a rotation speed reduced at a reduction ratio of i = i1 × i2.

第３図は、本発明の他の実施例であって、第１太陽輪33
が回転軸30の端部に同体的に形成され、円筒状の第２太
陽輪４４が他方の回転軸３１の内端部４１にニードルロ
ーラ43を介して回転可能に嵌合され、第２環状ローラキ
ャリア49が前記他方の回転軸31にフランジとして同体的
に形成されている。第２環状ローラキャリア49は、回転
軸31を支承する図示しない軸受により軸方向の移動を制
限されている。その他の構成は第１図と同様である。FIG. 3 shows another embodiment of the present invention, in which the first sun wheel 33
Is integrally formed at the end of the rotary shaft 30, and the cylindrical second sun wheel 44 is rotatably fitted to the inner end 41 of the other rotary shaft 31 via the needle roller 43, and the second annular ring A roller carrier 49 is integrally formed as a flange on the other rotating shaft 31. The second annular roller carrier 49 is restricted from moving in the axial direction by a bearing (not shown) that supports the rotating shaft 31. Other configurations are the same as in FIG.

第４図は、本発明のさらに他の実施例であって、第２遊
星ローラ47を第１遊星ローラ38の外径ｄと同一の外径
ｄ′とし、幅ｗを第１遊星ローラ38の幅ｗ′より大きく
形成して伝達トルクに適した強度を付与したものであ
る。さらにまた、第４図に示すように、前記各実施例の
第２太陽輪44の外周に形成する軌道溝46を、第２太陽輪
44の外周端部に設けたスラストワッシャ70と該スラスト
ワッシャ70を軸方向に固定する止め輪71で形成したもの
で、止め輪71は周溝72に嵌着されている。FIG. 4 shows still another embodiment of the present invention, in which the second planetary roller 47 has the same outer diameter d'as the outer diameter d of the first planetary roller 38 and the width w of the first planetary roller 38. It is formed to have a width larger than the width w'and has a strength suitable for the transmission torque. Furthermore, as shown in FIG. 4, an orbital groove 46 formed on the outer circumference of the second sun ring 44 of each of the above-mentioned embodiments is provided with a second sun ring.
It is formed by a thrust washer 70 provided at the outer peripheral end of 44 and a retaining ring 71 for axially fixing the thrust washer 70, and the retaining ring 71 is fitted in the circumferential groove 72.

また、本発明は、第１太陽輪33の設けられる回転軸30を
入力軸とし、前記第２環状ローラキャリア49の設けられ
る回転軸31を出力軸として多段式減速機を構成すること
も、前記第１太陽輪33の設けられる回転軸30を出力軸と
し、前記第２環状ローラキャリア49の設けられる回転軸
31を入力軸として多段式増速機を構成することもでき
る。The present invention may also be configured as a multi-stage speed reducer using the rotary shaft 30 provided with the first sun wheel 33 as an input shaft and the rotary shaft 31 provided with the second annular roller carrier 49 as an output shaft. The output shaft is the rotary shaft 30 provided with the first sun wheel 33, and the rotary shaft provided with the second annular roller carrier 49.
It is also possible to configure a multi-stage gearbox with 31 as an input shaft.

前記第１太陽輪33の設けられる回転軸30を出力軸とし、
前記第２環状ローラキャリア49の設けられる回転軸31を
入力軸として多段式増速機を構成する場合は、前記の多
段減速機における第２減速機構が第１増速機構として機
能し、同じく第１減速機構が第２増速機構として機能す
ることになる。The rotating shaft 30 provided with the first sun wheel 33 is used as an output shaft,
When the multi-stage speed increaser is configured with the rotary shaft 31 provided with the second annular roller carrier 49 as the input shaft, the second speed reducing mechanism in the multi-speed reducer functions as the first speed increasing mechanism, The first deceleration mechanism functions as the second speed increasing mechanism.

効 果 以上説明したように、本発明によれば、他方の回転軸の
内端部（遊星機構部の内方の端部）にそれを覆う円筒状
の第２太陽輪を回転自在に支持させるとともに、この第
２太陽輪の外周面と第２外輪との間に複数の第２遊星ロ
ーラを介装する構造としているから、他方の回転軸の内
端部の支持剛性をアップすることができて、結果的に、
他方の回転軸の内端部から外端部に適度に離れた位置を
一つの軸受で支持すれば事足りるようになる。したがっ
て、従来のように他方の回転軸を二つの軸受で支持させ
るためのスペースを確保する必要がなくなり、その分、
変速機の軸方向寸法を短くできるようになる。Effect As described above, according to the present invention, the inner end of the other rotary shaft (the inner end of the planetary mechanism) rotatably supports the cylindrical second sun wheel that covers it. At the same time, since a plurality of second planetary rollers are provided between the outer peripheral surface of the second sun wheel and the second outer wheel, it is possible to increase the support rigidity of the inner end of the other rotating shaft. And as a result,
It suffices if one bearing supports a position that is appropriately separated from the inner end portion to the outer end portion of the other rotating shaft. Therefore, it is not necessary to secure a space for supporting the other rotary shaft by the two bearings as in the conventional case, and accordingly,
The axial size of the transmission can be shortened.

【図面の簡単な説明】[Brief description of drawings]

第１図は、本発明の一実施例の縦断面図、第２図(イ) は
第１図のイ−イ線の断面図、第２図(ロ) は第１図のロ−
ロ線の断面図、第３図は本発明の他の実施例の縦断面
図、第４図は本発明のさらに他の実施例を示す縦断面
図、第５図は従来の多段変速機の縦断面図である。 30、31……回転軸、33……第１太陽輪、35……外輪、38
……第１遊星ローラ、39……第１環状ローラキャリア、
44……第２太陽輪、47……第２遊星ローラ、49……第２
環状ローラキャリア、46、50、51、52、53、63、64、6
5、66……軸方向移動を制限する手段1 is a vertical sectional view of an embodiment of the present invention, FIG. 2 (a) is a sectional view taken along the line EE in FIG. 1, and FIG. 2 (b) is a sectional view in FIG.
Fig. 3 is a vertical sectional view of another embodiment of the present invention, Fig. 4 is a vertical sectional view of yet another embodiment of the present invention, and Fig. 5 is a conventional multi-stage transmission. FIG. 30, 31 …… Rotary axis, 33 …… First sun wheel, 35 …… Outer wheel, 38
...... First planetary roller, 39 …… First annular roller carrier,
44 …… second sun wheel, 47 …… second planetary roller, 49 …… second
Annular roller carrier, 46, 50, 51, 52, 53, 63, 64, 6
5, 66 …… Means for limiting axial movement

フロントページの続き (56)参考文献 特開 昭50−22970（ＪＰ，Ａ) 実開 昭56−171457（ＪＰ，Ｕ) 実開 昭48−76375（ＪＰ，Ｕ)Continuation of the front page (56) References JP-A-50-22970 (JP, A) Actually open Sho-56-171457 (JP, U) Actual-open Sho-48-76375 (JP, U)

Claims (3)

【特許請求の範囲】[Claims] 【請求項１】同軸的に配列された一対の回転軸(30,31)
間に多段の遊星摩擦機構部を配置した多段式変速機にお
いて、 一方の回転軸(30)に設けられた第１太陽輪(33)と、 ハウジング(34)に嵌合固定される第１の外輪(35)と、 第１太陽輪(33)の外周と第１の外輪(35)の内周間に転動
可能に配置された複数個の第１遊星ローラ(38)と、 該第１遊星ローラ(38)を円周方向等間隔に回転可能に軸
支する第１環状ローラキャリア(39,55) と、 該第１環状ローラキャリア(39,55)から他方の回転軸(3
1)の内端部(41)を覆うよう軸方向に延設されかつ一対の
回転軸(30,31)のうち少なくとも他方の回転軸(31)の内
端部(41)に回転可能に支持された円筒状の第２太陽輪(4
4)と、 ハウジング(34)に嵌合固定される第２の外輪(35)と、 該第２太陽輪(44)の外周と第２の外輪(35)の内周間に転
動可能に配置された複数個の第２遊星ローラ(47)と、 該第２遊星ローラ(47)を円周方向等間隔に回転可能に軸
支しかつ前記他方の回転軸(31)に動力伝達可能に設けら
れた第２環状ローラキャリア(49,59)とを具えてなる多
段式変速機。1. A pair of coaxially arranged rotating shafts (30, 31)
In a multi-stage transmission in which a multi-stage planetary friction mechanism portion is arranged between the first sun wheel (33) provided on one rotating shaft (30) and the first sun wheel (33) fitted and fixed to the housing (34). An outer ring (35), a plurality of first planetary rollers (38) rotatably arranged between the outer periphery of the first sun ring (33) and the inner periphery of the first outer ring (35), A first annular roller carrier (39, 55) that rotatably supports the planetary roller (38) at equal intervals in the circumferential direction, and the other rotating shaft (3) from the first annular roller carrier (39, 55).
1) Extending in the axial direction so as to cover the inner end (41) of (1), and rotatably supported by the inner end (41) of at least the other rotating shaft (31) of the pair of rotating shafts (30, 31). Cylindrical second sun wheel (4
4), a second outer ring (35) fitted and fixed to the housing (34), and rollable between the outer periphery of the second sun ring (44) and the inner periphery of the second outer ring (35). A plurality of second planetary rollers (47) arranged, the second planetary rollers (47) being rotatably supported at equal intervals in the circumferential direction and capable of transmitting power to the other rotating shaft (31). A multi-stage transmission comprising a second annular roller carrier (49, 59) provided. 【請求項２】前記第２太陽輪(44)が、第２環状ローラキ
ャリア(49,59)の設けられる回転軸(31)の内端部(41)に
ニードルローラ(42,43)を介して回転可能に嵌合されて
いることを特徴とする特許請求の範囲第１項記載の多段
式変速機。2. The second sun wheel (44) is provided with a needle roller (42, 43) on an inner end (41) of a rotary shaft (31) provided with a second annular roller carrier (49, 59). The multi-stage transmission according to claim 1, wherein the multi-stage transmission is rotatably fitted. 【請求項３】前記第２太陽輪(44)が、一対の回転軸(30,
31)の両内端部(40,41)にそれぞれニードルローラ(42,4
3)を介して回転可能に嵌合されていることを特徴とする
特許請求の範囲第１項記載の多段式変速機。3. The second sun wheel (44) has a pair of rotating shafts (30,
31) on both inner ends (40, 41) of the needle rollers (42, 4) respectively.
The multi-stage transmission according to claim 1, wherein the multi-stage transmission is rotatably fitted through 3).
JP59195345A 1984-09-17 1984-09-17 Multi-stage transmission Expired - Lifetime JPH0633802B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP59195345A JPH0633802B2 (en) 1984-09-17 1984-09-17 Multi-stage transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP59195345A JPH0633802B2 (en) 1984-09-17 1984-09-17 Multi-stage transmission

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP4098022A Division JPH0792127B2 (en) 1992-04-17 1992-04-17 Multi-stage transmission

Publications (2)

Publication Number Publication Date
JPS6174952A JPS6174952A (en) 1986-04-17
JPH0633802B2 true JPH0633802B2 (en) 1994-05-02

Family

ID=16339622

Family Applications (1)

Application Number Title Priority Date Filing Date
JP59195345A Expired - Lifetime JPH0633802B2 (en) 1984-09-17 1984-09-17 Multi-stage transmission

Country Status (1)

Country Link
JP (1) JPH0633802B2 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6414949U (en) * 1987-07-17 1989-01-25
JPH0440036Y2 (en) * 1987-11-20 1992-09-18
JP2552797Y2 (en) * 1990-12-18 1997-10-29 光洋精工株式会社 Multi-stage transmission type planetary roller power transmission
JP5310667B2 (en) 2010-07-26 2013-10-09 株式会社豊田中央研究所 Traction drive mechanism

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5022970A (en) * 1973-07-04 1975-03-12
JPS56171457U (en) * 1980-05-21 1981-12-18

Also Published As

Publication number Publication date
JPS6174952A (en) 1986-04-17

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