JP2003222204A - Power transmission device - Google Patents
Power transmission deviceInfo
- Publication number
- JP2003222204A JP2003222204A JP2002023803A JP2002023803A JP2003222204A JP 2003222204 A JP2003222204 A JP 2003222204A JP 2002023803 A JP2002023803 A JP 2002023803A JP 2002023803 A JP2002023803 A JP 2002023803A JP 2003222204 A JP2003222204 A JP 2003222204A
- Authority
- JP
- Japan
- Prior art keywords
- rotating member
- input
- system rotating
- input system
- output system
- 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
- Retarders (AREA)
- Friction Gearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は動力伝達装置に関
し、詳しくは、一方の回転部材からの回転入力を、例え
ば遊星歯車機構により所定の減速比でもって他方の回転
部材へ出力する動力伝達装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device, and more particularly to a power transmission device that outputs a rotation input from one rotating member to the other rotating member with a predetermined reduction ratio by a planetary gear mechanism, for example. .
【０００２】[0002]
【従来の技術】従来の動力伝達装置の一例として、例え
ば特開平１０−１５３２４２号公報などに開示された遊
星歯車機構を用いた減速装置がある。2. Description of the Related Art As an example of a conventional power transmission device, there is a speed reducer using a planetary gear mechanism disclosed in, for example, Japanese Patent Application Laid-Open No. 10-153242.
【０００３】この種の減速装置は、ハウジングに固定さ
れた内歯車と、その内側に内歯車と軸心を一致させて配
置された太陽歯車と、その太陽歯車と内歯車の間に形成
された空間に配置された複数個の遊星歯車と、それら遊
星歯車を円周方向に等間隔かつ回転自在に保持するキャ
リアとを備えている。太陽歯車には、ハウジングに対し
て回転自在に支持された入力回転軸が同軸的に設けら
れ、キャリアには、ハウジングに対して回転自在に支持
された出力回転軸が設けられている。太陽歯車と内歯車
との間に位置する複数個の遊星歯車は、太陽歯車と内歯
車にそれぞれ噛合した状態で配設されている。This type of speed reducer is formed between an internal gear fixed to a housing, a sun gear arranged inside the internal gear with its axis aligned with the internal gear, and between the sun gear and the internal gear. It is provided with a plurality of planetary gears arranged in a space and a carrier that holds the planetary gears rotatably at equal intervals in the circumferential direction. The sun gear is coaxially provided with an input rotary shaft rotatably supported by the housing, and the carrier is provided with an output rotary shaft rotatably supported by the housing. A plurality of planetary gears located between the sun gear and the internal gear are arranged so as to mesh with the sun gear and the internal gear, respectively.
【０００４】減速装置では、入力回転軸からの回転入力
に基づいて、その入力回転軸に設けられた太陽歯車が回
転し、キャリアに対して回転自在に支持された遊星歯車
が自転しつつ太陽歯車の回りを公転することにより、入
力回転軸の回転が所定の減速比でもって出力回転軸に伝
達される。In the reduction gear transmission, the sun gear provided on the input rotation shaft rotates based on the rotation input from the input rotation shaft, and the planetary gear rotatably supported by the carrier rotates while the sun gear rotates. By revolving around, the rotation of the input rotary shaft is transmitted to the output rotary shaft with a predetermined reduction ratio.
【０００５】[0005]
【発明が解決しようとする課題】ところで、前述したよ
うに遊星歯車機構を用いた従来の減速装置では、入力回
転軸の回転が１／Ｘ倍に減速されて出力回転軸に伝達さ
れるが、仮に、何等かの原因により出力回転軸からの回
転逆入力があった場合には、その出力回転軸の回転がＸ
倍に増速されて入力回転軸に伝達されることになる。こ
のように入力回転軸と出力回転軸間での回転比は必ず反
比例関係となり、入力方向の変更によってこの関係を変
更することはできない。By the way, in the conventional speed reducer using the planetary gear mechanism as described above, the rotation of the input rotary shaft is decelerated by 1 / X and transmitted to the output rotary shaft. If there is a reverse rotation input from the output rotary shaft for some reason, the rotation of the output rotary shaft is X.
The speed is doubled and transmitted to the input rotary shaft. In this way, the rotation ratio between the input rotary shaft and the output rotary shaft always has an inverse proportional relationship, and this relationship cannot be changed by changing the input direction.
【０００６】通常、入力回転軸の回転が１／Ｘ倍に減速
されて出力回転軸に伝達される減速装置において、仮
に、何等かの原因に基づいて出力回転軸からの回転逆入
力があると、入力回転軸の回転数が増大してしまうこと
になる。その結果、入力回転軸の駆動源における許容回
転数が低い場合に、出力回転軸から入力回転軸への逆入
力により、その駆動源の許容回転数を超えることがあ
り、駆動源に悪影響を与える等の問題が生じる可能性が
あった。Normally, in a reduction gear transmission in which the rotation of the input rotary shaft is decelerated by 1 / X and transmitted to the output rotary shaft, if there is a reverse rotation input from the output rotary shaft for some reason. Therefore, the number of rotations of the input rotary shaft will increase. As a result, when the allowable rotation speed of the drive source of the input rotary shaft is low, the reverse rotation of the output rotary shaft to the input rotary shaft may exceed the allowable rotation speed of the drive source, which adversely affects the drive source. Such problems may occur.
【０００７】そこで、本発明は前記問題点に鑑みて提案
されたもので、その目的とするところは、出力回転軸か
ら入力回転軸への逆入力があっても、入力回転軸の駆動
源における許容回転数を超えないようにした減速装置と
し得る動力伝達装置を提供することにある。Therefore, the present invention has been proposed in view of the above problems, and an object of the present invention is to provide a drive source for an input rotary shaft even if there is a reverse input from the output rotary shaft to the input rotary shaft. It is an object of the present invention to provide a power transmission device that can serve as a reduction gear device that does not exceed an allowable rotation speed.
【０００８】[0008]
【課題を解決するための手段】前記目的を達成するため
の技術的手段として、本発明に係る動力伝達装置は、駆
動源により回転駆動される入力系回転部材と、その入力
系回転部材から伝達された回転トルクを外部へ取り出す
ための出力系回転部材と、前記入力系回転部材と出力系
回転部材との間に、入力系回転部材からの回転を減速す
る遊星機構を介して設けられ、入力系回転部材から出力
系回転部材への回転入力をトルク伝達部材の係合により
伝達し、出力系回転部材から入力系回転部材への回転逆
入力を前記トルク伝達部材の離脱により遮断する第一の
ワンウェイクラッチと、前記入力系回転部材と出力系回
転部材との間に設けられ、入力系回転部材から出力系回
転部材への回転入力をトルク伝達部材の離脱により遮断
し、出力系回転部材から入力系回転部材への回転逆入力
を前記トルク伝達部材の係合により伝達する第二のワン
ウェイクラッチとを具備したことを特徴とする。As a technical means for achieving the above object, a power transmission device according to the present invention is an input system rotating member which is rotationally driven by a drive source and a transmission from the input system rotating member. An output system rotating member for extracting the generated rotational torque to the outside, and a planetary mechanism that reduces the rotation from the input system rotating member between the input system rotating member and the output system rotating member, A first input for transmitting rotation input from the system rotation member to the output system rotation member by engagement of the torque transmission member, and blocking a reverse rotation input from the output system rotation member to the input system rotation member by separation of the torque transmission member. A one-way clutch is provided between the input system rotating member and the output system rotating member, and cuts the rotation input from the input system rotating member to the output system rotating member by detaching the torque transmitting member, and the output system rotating unit. Characterized in that the rotary reverse input to input system rotating member; and a second one-way clutch for transmitting the engagement of the torque transmitting member from.
【０００９】本発明の動力伝達装置では、第一のワンウ
ェイクラッチのトルク伝達部材の係合方向と第二のワン
ウェイクラッチのトルク伝達部材の係合方向とを逆向き
としている。その結果、入力系回転部材からの回転入力
は、第一のワンウェイクラッチのトルク伝達部材の係合
により伝達し得るため、遊星機構により所定の減速比で
もって減速した上で第一のワンウェイクラッチを介して
出力系回転部材に伝達される。このとき、第二のワンウ
ェイクラッチは、そのトルク伝達部材の係合方向が第一
のワンウェイクラッチと逆向きであるために空転可能な
状態にあり、入力系回転部材と出力系回転部材との間
は、第二のワンウェイクラッチを介して離脱した状態に
ある。In the power transmission device of the present invention, the engagement direction of the torque transmission member of the first one-way clutch is opposite to the engagement direction of the torque transmission member of the second one-way clutch. As a result, the rotational input from the input system rotating member can be transmitted by the engagement of the torque transmitting member of the first one-way clutch, so the planetary mechanism reduces the speed with a predetermined reduction ratio and then the first one-way clutch is engaged. It is transmitted to the output system rotating member via the. At this time, the second one-way clutch is in the idling state because the engagement direction of the torque transmission member is opposite to that of the first one-way clutch, and the second one-way clutch is between the input system rotating member and the output system rotating member. Is disengaged via the second one-way clutch.
【００１０】一方、出力系回転部材からの回転逆入力
は、第二のワンウェイクラッチのトルク伝達部材の係合
により伝達し得るため、その第二のワンウェイクラッチ
を介して入力系回転部材に伝達される。このとき、第一
のワンウェイクラッチは、そのトルク伝達部材の係合方
向が第二のワンウェイクラッチと逆向きであるために空
転可能な状態にあり、入力系回転部材と出力系回転部材
との間は、第一のワンウェイクラッチを介して離脱した
状態にあることから、出力系回転部材からの回転逆入力
は、遊星機構を介さないので入力系回転部材の回転は増
速されることなく、第二のワンウェイクラッチを介して
１：１で入力系回転部材に伝達される。On the other hand, the reverse rotation input from the output system rotating member can be transmitted by the engagement of the torque transmitting member of the second one-way clutch, and therefore is transmitted to the input system rotating member via the second one-way clutch. It At this time, the first one-way clutch is in the idling state because the engagement direction of the torque transmission member is opposite to that of the second one-way clutch, so that the first system one-way clutch is not locked between the input system rotary member and the output system rotary member. Is disengaged via the first one-way clutch, the reverse rotation input from the output system rotary member does not go through the planetary mechanism, so the rotation of the input system rotary member is not accelerated, and It is transmitted to the input system rotating member at a ratio of 1: 1 through the second one-way clutch.
【００１１】なお、入力系回転部材からの回転を減速す
る遊星機構の一つとしては、静止系部材に設けられた内
歯車と、その内側に前記入力系回転部材と同軸上に配設
された太陽歯車と、この太陽歯車と前記内歯車との間に
それら両者と噛合するように介装された複数の遊星歯車
と、これら遊星歯車を円周方向等間隔に回転自在に保持
するキャリアとで構成された遊星歯車機構が実現可能で
ある。As one of planetary mechanisms for reducing the speed of rotation from the input system rotating member, an internal gear provided on the stationary system member and the inner gear arranged coaxially with the input system rotating member. A sun gear, a plurality of planet gears interposed between the sun gear and the internal gear so as to mesh with them, and a carrier that rotatably holds these planet gears at equal circumferential intervals. A configured planetary gear mechanism is feasible.
【００１２】また、他の遊星機構としては、静止系部材
に設けられた固定輪と、その内側に入力系回転部材と同
軸上に配設された太陽ローラと、この太陽ローラと前記
固定輪との間にそれら両者と圧接する状態で介装された
複数の遊星ローラと、これら遊星ローラを円周方向等間
隔に回転自在に保持するキャリアとで構成された遊星ロ
ーラ機構が実現可能である。As another planetary mechanism, a fixed ring provided on a stationary system member, a sun roller provided inside the stationary ring coaxially with the input system rotating member, the sun roller and the fixed ring are provided. It is possible to realize a planetary roller mechanism including a plurality of planetary rollers interposed between the two in pressure contact with each other, and a carrier that rotatably holds these planetary rollers at equal intervals in the circumferential direction.
【００１３】さらに、前記ワンウェイクラッチのトルク
伝達部材としては、スプラグ、ローラあるいはラチェッ
トのうちから選択されるいずれかを使用することが可能
である。Further, as the torque transmission member of the one-way clutch, it is possible to use any one selected from a sprag, a roller and a ratchet.
【００１４】[0014]
【発明の実施の形態】図１乃至図７は本発明に係る動力
伝達装置の実施形態を示す。図１および図２は遊星機構
を利用した減速装置の概略構成、図３は図１の減速装置
に組み込まれた遊星機構の一例として遊星歯車機構を示
し、図４は遊星機構の他例として遊星ローラ機構を示
す。図５乃至図７は図１の減速装置に組み込まれたワン
ウェイクラッチで、図５はスプラグタイプ、図６はロー
ラタイプ、図７はラチェットタイプをそれぞれ示す。1 to 7 show an embodiment of a power transmission device according to the present invention. 1 and 2 show a schematic structure of a speed reducer using a planetary mechanism, FIG. 3 shows a planetary gear mechanism as an example of a planetary mechanism incorporated in the speed reducer of FIG. 1, and FIG. 4 shows a planetary gear as another example of the planetary mechanism. The roller mechanism is shown. 5 to 7 show a one-way clutch incorporated in the speed reducer of FIG. 1, FIG. 5 shows a sprag type, FIG. 6 shows a roller type, and FIG. 7 shows a ratchet type.
【００１５】この実施形態の減速装置は、図１および図
２に示すように駆動源（図示せず）により回転駆動され
る入力系回転部材１と、その入力系回転部材１から伝達
された回転トルクを外部へ取り出すための出力系回転部
材２と、入力系回転部材１と出力系回転部材２との間
に、入力系回転部材１からの回転を減速する遊星機構３
を介して設けられ、入力系回転部材１から出力系回転部
材２への回転入力をトルク伝達部材（後述）の係合によ
り伝達し、出力系回転部材２から入力系回転部材１への
回転逆入力をトルク伝達部材の離脱により遮断する第一
のワンウェイクラッチ４と、入力系回転部材１と出力系
回転部材２との間に設けられ、入力系回転部材１から出
力系回転部材２への回転入力をトルク伝達部材の離脱に
より遮断し、出力系回転部材２から入力系回転部材１へ
の回転逆入力をトルク伝達部材の係合により伝達する第
二のワンウェイクラッチ５とを主要部として構成されて
いる。The speed reducer of this embodiment, as shown in FIGS. 1 and 2, has an input system rotary member 1 which is rotationally driven by a drive source (not shown), and a rotation transmitted from the input system rotary member 1. A planetary mechanism 3 for decelerating the rotation from the input system rotating member 1 between the output system rotating member 2 for extracting the torque to the outside and the input system rotating member 1 and the output system rotating member 2.
The rotation input from the input system rotating member 1 to the output system rotating member 2 is transmitted by the engagement of the torque transmitting member (described later), and the rotation reverse from the output system rotating member 2 to the input system rotating member 1 is performed. Rotation from the input system rotating member 1 to the output system rotating member 2 is provided between the input system rotating member 1 and the output system rotating member 2 and the first one-way clutch 4 that disconnects the input by separating the torque transmitting member. A second one-way clutch 5 is provided as a main part for interrupting an input by disengagement of the torque transmission member and transmitting a rotational reverse input from the output system rotation member 2 to the input system rotation member 1 by engagement of the torque transmission member. ing.
【００１６】前記入力系回転部材１には、遊星機構３の
一部を構成する太陽歯車６が同軸的に設けられている。
また、入力系回転部材１と同軸上に配置された出力系回
転部材２は、その中心軸部２ａから軸方向に延在した小
拡径部２ｂと、その小拡径部２ｂから軸方向に延在した
大拡径部２ｃを有し、小拡径部２ｂと入力系回転部材１
とを第二のワンウェイクラッチ５で連結し、大拡径部２
ｃと遊星機構３の一部を構成するキャリア１１とを第一
のワンウェイクラッチ４で連結した構造を具備する。The input system rotating member 1 is coaxially provided with a sun gear 6 which constitutes a part of the planetary gear mechanism 3.
Further, the output system rotating member 2 arranged coaxially with the input system rotating member 1 has a small expanded diameter portion 2b extending axially from the central shaft portion 2a and an axial direction extending from the small expanded diameter portion 2b. It has a large expanded diameter portion 2c extending, and a small expanded diameter portion 2b and an input system rotary member 1
Is connected with the second one-way clutch 5, and the large diameter expanded portion 2
It has a structure in which c and a carrier 11 forming a part of the planetary gear mechanism 3 are connected by a first one-way clutch 4.
【００１７】入力系回転部材１と出力系回転部材２との
間に設けられた遊星機構の一例として遊星歯車機構３を
図３に例示する。この遊星歯車機構３は、静止系部材で
あるハウジング７に固定された内歯車８と、その内側に
入力系回転部材１と同軸上に配設された太陽歯車６と、
この太陽歯車６と内歯車８との間にそれら両者と噛合す
るように介装された複数の遊星歯車９と、これら遊星歯
車９を円周方向等間隔に支持軸１０により回転自在に保
持するキャリア１１とで構成されている。A planetary gear mechanism 3 is shown in FIG. 3 as an example of a planetary mechanism provided between the input system rotary member 1 and the output system rotary member 2. The planetary gear mechanism 3 includes an internal gear 8 fixed to a housing 7 that is a stationary system member, and a sun gear 6 disposed inside the internal gear 8 coaxially with the input system rotating member 1.
A plurality of planetary gears 9 interposed between the sun gear 6 and the internal gear 8 so as to mesh with them, and these planetary gears 9 are rotatably held by a support shaft 10 at equal intervals in the circumferential direction. It is composed of a carrier 11.
【００１８】なお、本発明における遊星機構としては、
前述した遊星歯車機構３以外にも、図４に示す遊星ロー
ラ機構３’でも可能である。この遊星ローラ機構３’
は、ハウジング７に設けられた固定輪８’と、その内側
に入力系回転部材１と同軸上に配設された太陽ローラ
６’と、この太陽ローラ６’と固定輪８’との間にそれ
ら両者と圧接する状態で介装された複数の遊星ローラ
９’と、これら遊星ローラ９’を円周方向等間隔に支持
軸１０により回転自在に保持するキャリア１１とで構成
されている。As the planetary mechanism in the present invention,
Other than the planetary gear mechanism 3 described above, the planetary roller mechanism 3 ′ shown in FIG. 4 is also possible. This planetary roller mechanism 3 '
Is a fixed ring 8'provided in the housing 7, a sun roller 6'arranged inside the fixed ring 8 ', coaxially with the input system rotating member 1, and between the sun roller 6'and the fixed ring 8'. It is composed of a plurality of planetary rollers 9'which are interposed in pressure contact with both of them, and a carrier 11 which rotatably holds these planetary rollers 9'at equal intervals in the circumferential direction by a support shaft 10.
【００１９】第一のワンウェイクラッチ４および第二の
ワンウェイクラッチ５は、スプラグタイプ、ローラタイ
プあるいはラチェットタイプのいずれかの構造のものが
可能である。例えばスプラグタイプのワンウェイクラッ
チ構造は、図５に示すように入力系回転部材１の外周に
圧入された内輪１２と、出力系回転部材２の内周に圧入
された外輪１３との間に、内側保持器１４と外側保持器
１５とによって多数のスプラグ１６を保持し、その内外
側保持器１４，１５の間にリボンスプリング１７を嵌
め、そのリボンスプリング１７により各スプラグ１６に
実線矢印方向のモーメントを与えて、内輪１２の外周面
と外輪１３の内周面に各スプラグ１６を接触させている
（実開平５−８６０４４号公報参照）。The first one-way clutch 4 and the second one-way clutch 5 can have any structure of sprag type, roller type or ratchet type. For example, as shown in FIG. 5, the sprag type one-way clutch structure has an inner side between an inner ring 12 press-fitted to the outer periphery of the input system rotary member 1 and an outer ring 13 press-fitted to the inner periphery of the output system rotary member 2. A large number of sprags 16 are held by the retainer 14 and the outer retainer 15, and a ribbon spring 17 is fitted between the inner and outer retainers 14 and 15. The ribbon spring 17 applies a moment to each sprag 16 in the direction of the solid line arrow. Then, each sprag 16 is brought into contact with the outer peripheral surface of the inner ring 12 and the inner peripheral surface of the outer ring 13 (see Japanese Utility Model Laid-Open No. 5-86044).
【００２０】リボンスプリング１７は、リボン状の金属
薄板に一定のピッチのスプラグ挿入孔を形成し、そのス
プラグ挿入孔の一方の側辺に弾性舌片１８を設けてい
る。また、その弾性舌片１８とリボンスプリングの両側
辺には、それらに弾性力を与える彎曲部１９が形成さ
れ、この弾性舌片１８が各スプラグ１６の側面に接触し
て前述した方向にスプラグ１６を付勢している。In the ribbon spring 17, a sprag insertion hole with a constant pitch is formed in a ribbon-shaped thin metal plate, and an elastic tongue piece 18 is provided on one side of the sprag insertion hole. Further, the elastic tongue piece 18 and the ribbon spring are formed on both sides of the ribbon spring with a curved portion 19 which gives elastic force to the elastic tongue piece 18. The elastic tongue piece 18 comes into contact with the side surface of each sprag 16 in the direction described above. Is urged.
【００２１】このワンウェイクラッチでは、内輪１２と
外輪１３が係合方向に相対回転し、内側保持器１４と外
側保持器１５が相対回転すると、各スプラグ１６が図示
状態とは逆方向に傾き、内輪１２と外輪１３間に係合す
ることにより、入力系回転部材１からの回転が出力系回
転部材２へ伝達される。また、内輪１２と外輪１３が前
述とは逆方向に回転すると、内外側保持器１４，１５の
相対回転によってスプラグ１６が係合状態から外れ、ス
プラグ１６が内輪１２と外輪１３間で離脱し、入力系回
転部材１は空転し、入力系回転部材１からの回転が出力
系回転部材２へ伝達されない。In this one-way clutch, when the inner ring 12 and the outer ring 13 rotate relative to each other in the engaging direction and the inner cage 14 and the outer cage 15 rotate relative to each other, each sprag 16 tilts in the direction opposite to the illustrated state, and the inner ring By engaging between 12 and the outer ring 13, the rotation from the input system rotary member 1 is transmitted to the output system rotary member 2. When the inner ring 12 and the outer ring 13 rotate in the opposite direction to the above, the sprags 16 are disengaged from each other by the relative rotation of the inner and outer cages 14 and 15, and the sprags 16 are disengaged between the inner ring 12 and the outer ring 13. The input system rotary member 1 runs idle, and the rotation from the input system rotary member 1 is not transmitted to the output system rotary member 2.
【００２２】このようにワンウェイクラッチにおけるス
プラグ１６の係合・離脱により入力系回転部材１と出力
系回転部材２との間での動力伝達を断接する。ここで、
第一のワンウェイクラッチ４のスプラグ１６の係合方向
と第二のワンウェイクラッチ５のスプラグ１６の係合方
向とは逆向きに設定されている。つまり、第一のワンウ
ェイクラッチ４のスプラグ１６の係合方向を白抜き矢印
Ａ方向とすると、第二のワンウェイクラッチ５のスプラ
グ１６の係合方向は白抜き矢印Ｂ方向になっている。In this way, the power transmission between the input system rotary member 1 and the output system rotary member 2 is connected and disconnected by the engagement / disengagement of the sprag 16 in the one-way clutch. here,
The engagement direction of the sprag 16 of the first one-way clutch 4 and the engagement direction of the sprag 16 of the second one-way clutch 5 are set to be opposite. That is, assuming that the engagement direction of the sprag 16 of the first one-way clutch 4 is the white arrow A direction, the engagement direction of the sprag 16 of the second one-way clutch 5 is the white arrow B direction.
【００２３】なお、本発明におけるワンウェイクラッチ
構造は、前述したスプラグタイプ以外にも、図６に示す
ローラタイプや図７に示すラチェットタイプのものでも
可能である。これらローラタイプおよびラチェットタイ
プのいずれも、前述したスプラグタイプのものと同様、
第一のワンウェイクラッチ４のローラおよびラチェット
の係合方向は、第二のワンウェイクラッチ５と逆向きに
設定されている。The one-way clutch structure according to the present invention may be of the roller type shown in FIG. 6 or the ratchet type shown in FIG. 7, in addition to the sprag type described above. Both of these roller type and ratchet type are similar to the sprag type mentioned above.
The engagement direction of the roller and ratchet of the first one-way clutch 4 is set to be opposite to that of the second one-way clutch 5.
【００２４】ローラタイプのワンウェイクラッチ構造
は、図６に示すように外輪２０の内周面に一定間隔をお
いてポケット２１を設け、そのポケット２１にローラ２
２を挿入し、ポケット２１の底面に回転の一方向に間隙
が狭くなる傾斜面２３を形成し、ローラ２２をその傾斜
の方向に付勢するばね２４を各ポケット２１に収納し、
外輪２０の内周に内輪２６を配置し、ポケット２１を楔
形空所に形成した構造を具備する（特開平９−８９０１
１号公報参照）。In the roller type one-way clutch structure, as shown in FIG. 6, pockets 21 are provided on the inner peripheral surface of the outer ring 20 at regular intervals, and the rollers 2 are placed in the pockets 21.
2 is inserted, an inclined surface 23 having a narrow gap in one direction of rotation is formed on the bottom surface of the pocket 21, and a spring 24 for biasing the roller 22 in the inclined direction is housed in each pocket 21.
The inner ring 26 is arranged on the inner circumference of the outer ring 20 and the pocket 21 is formed in a wedge-shaped space (Japanese Patent Laid-Open No. 9-8901).
(See Japanese Patent Publication No. 1).
【００２５】このワンウェイクラッチは、内輪２６の内
径側に入力系回転部材１を圧入し、外輪２０の外径側に
出力系回転部材２を圧入した状態で組み込まれる。通常
の状態でローラ２２は、ばね２４により、ポケット２１
の傾斜面２３と内輪２６の外径面との間で形成された楔
形空所の狭い方向に付勢され、その付勢方向に入力系回
転部材１が回転されると、外輪２０と内輪２６間でロー
ラ２２が係合して入力系回転部材１からの回転を外輪２
０およびこれと一体の出力系回転部材２に伝達する。入
力系回転部材１が逆回転すると、ローラ２２がばね２４
を圧縮しながら楔形空所の広い方に移動するため、外輪
２０と内輪２６間でローラ２２が離脱して入力系回転部
材１は空転し、入力系回転部材１からの回転が出力系回
転部材２へ伝達されない。This one-way clutch is assembled in a state in which the input system rotating member 1 is press-fitted on the inner diameter side of the inner ring 26 and the output system rotating member 2 is press-fitted on the outer diameter side of the outer ring 20. In a normal state, the roller 22 moves the spring 24 so that the pocket 21
When the input system rotation member 1 is rotated in the narrow direction of the wedge-shaped space formed between the inclined surface 23 of the inner ring 26 and the outer diameter surface of the inner ring 26, the outer ring 20 and the inner ring 26 are rotated. The roller 22 engages between the outer ring 2 and the rotation from the input system rotary member 1
0 and the output system rotary member 2 integrated therewith. When the input system rotating member 1 rotates in the reverse direction, the roller 22 causes the spring 24 to move.
, The roller 22 is disengaged between the outer ring 20 and the inner ring 26, the input system rotating member 1 idles, and the rotation from the input system rotating member 1 causes the output system rotating member to rotate. Not transmitted to 2.
【００２６】ラチェットタイプのワンウェイクラッチ構
造は、図７に示すように入力系回転部材１に外嵌された
内輪２７と、その内輪２７と同心状に配置されて出力系
回転部材２に内嵌された外輪２８とからなり、内輪２７
はその外周面に凹状のポケット２９を円周等配置し、そ
のポケット２９内に爪３０を設けてばね（図示せず）に
より外方へ弾性的に付勢した構造を有する。一方、外輪
２８はその内周面に前述したポケット２９と対応させて
ノッチ３１を設けた構造を有する（特開平９−２９１９
５０号公報参照）。The ratchet type one-way clutch structure is, as shown in FIG. 7, an inner ring 27 fitted on the input system rotating member 1 and an inner ring 27 arranged concentrically with the inner ring 27 and fitted on the output system rotating member 2. Outer ring 28 and inner ring 27
Has a structure in which a concave pocket 29 is circumferentially arranged on the outer peripheral surface thereof, a claw 30 is provided in the pocket 29, and elastically biased outward by a spring (not shown). On the other hand, the outer ring 28 has a structure in which a notch 31 is provided on the inner peripheral surface of the outer ring 28 so as to correspond to the pocket 29 described above (JP-A-9-2919).
No. 50).
【００２７】このワンウェイクラッチでは、入力系回転
部材１を図示時計方向へ回転させると、内輪２７の各爪
３０がばねの弾性力により外方へ付勢されているので、
それら複数の爪３０のうち、一つの爪３０が外輪２８の
ノッチ３１に係合される。この内輪２７の爪３０が外輪
２８のノッチ３１に係合することにより、入力系回転部
材１からの回転が出力系回転部材２に伝達されてその出
力系回転部材２が回転する。逆に、入力系回転部材１を
図示反時計方向に回転させると、内輪２７の各爪３０が
ポケット２９に収納されながら外輪２８のノッチ３１か
ら離脱するので、外輪２８が回転せずに内輪２７のみが
空転し、入力系回転部材１からの回転が出力系回転部材
２へ伝達されない。In this one-way clutch, when the input system rotating member 1 is rotated clockwise in the drawing, each claw 30 of the inner ring 27 is urged outward by the elastic force of the spring.
One of the plurality of claws 30 is engaged with the notch 31 of the outer ring 28. By engaging the claw 30 of the inner ring 27 with the notch 31 of the outer ring 28, the rotation from the input system rotating member 1 is transmitted to the output system rotating member 2 and the output system rotating member 2 rotates. On the contrary, when the input system rotating member 1 is rotated counterclockwise in the drawing, the claws 30 of the inner ring 27 are removed from the notches 31 of the outer ring 28 while being housed in the pockets 29, so that the outer ring 28 does not rotate and the inner ring 27 does not rotate. Only the idle rotation occurs, and the rotation from the input system rotary member 1 is not transmitted to the output system rotary member 2.
【００２８】次に、図１に示す実施形態の減速装置の動
作例を以下に詳述する。Next, an example of the operation of the speed reducer of the embodiment shown in FIG. 1 will be described in detail below.
【００２９】まず、入力系回転部材１からの回転を遊星
歯車機構３および第一のワンウェイクラッチ４を介して
出力系回転部材２に伝達する。このとき、遊星歯車機構
３では、入力系回転部材１からの回転入力に基づいて、
その入力系回転部材１に設けられた太陽歯車６が回転
し、キャリア１１に対して回転自在に支持された遊星歯
車９が自転しつつ太陽歯車６の回りを公転することによ
り、入力系回転部材１の回転が所定の減速比でもってキ
ャリア１１に伝達される。First, the rotation from the input system rotary member 1 is transmitted to the output system rotary member 2 via the planetary gear mechanism 3 and the first one-way clutch 4. At this time, in the planetary gear mechanism 3, based on the rotation input from the input system rotation member 1,
The sun gear 6 provided on the input system rotating member 1 rotates, and the planetary gear 9 rotatably supported by the carrier 11 revolves around the sun gear 6 while rotating about its own axis. The rotation of 1 is transmitted to the carrier 11 with a predetermined reduction ratio.
【００３０】さらに、遊星歯車機構３のキャリア１１を
介して、入力系回転部材１からの回転は、第一のワンウ
ェイクラッチ４のトルク伝達部材（スプラグ、ローラあ
るいはラチェット）の係合により伝達し得るため、遊星
歯車機構３により所定の減速比でもって減速した上で第
一のワンウェイクラッチ４を介して出力系回転部材２に
伝達される（図１の破線矢印参照）。Further, the rotation from the input system rotating member 1 can be transmitted through the carrier 11 of the planetary gear mechanism 3 by the engagement of the torque transmitting member (sprag, roller or ratchet) of the first one-way clutch 4. Therefore, the planetary gear mechanism 3 reduces the speed at a predetermined speed reduction ratio, and then transmits it to the output system rotating member 2 via the first one-way clutch 4 (see the broken line arrow in FIG. 1).
【００３１】このとき、第二のワンウェイクラッチ５
は、そのトルク伝達部材の係合方向が第一のワンウェイ
クラッチ４と逆向きであるために空転可能な状態にあ
り、入力系回転部材１と出力系回転部材２との間は、第
二のワンウェイクラッチ５を介して離脱した状態にある
ため、入力系回転部材１からの回転が第二のワンウェイ
クラッチ５を介して出力系回転部材２へ伝達されること
はない。At this time, the second one-way clutch 5
Is in a state in which the torque transmission member is engaged in the opposite direction to the first one-way clutch 4 and thus is in a state in which it can rotate idly, and between the input system rotary member 1 and the output system rotary member 2, Since it is disengaged via the one-way clutch 5, the rotation from the input system rotary member 1 is not transmitted to the output system rotary member 2 via the second one-way clutch 5.
【００３２】一方、出力系回転部材２からの回転逆入力
があった場合には、その出力系回転部材２からの回転
は、第二のワンウェイクラッチ５のトルク伝達部材の係
合により伝達し得るため、その第二のワンウェイクラッ
チ５を介して入力系回転部材１に伝達される（図２の破
線矢印参照）。On the other hand, when there is a reverse rotation input from the output system rotary member 2, the rotation from the output system rotary member 2 can be transmitted by the engagement of the torque transmission member of the second one-way clutch 5. Therefore, it is transmitted to the input system rotary member 1 through the second one-way clutch 5 (see the broken line arrow in FIG. 2).
【００３３】このとき、第一のワンウェイクラッチ４
は、そのトルク伝達部材の係合方向が第二のワンウェイ
クラッチ５と逆向きであるために空転可能な状態にあ
り、入力系回転部材１と出力系回転部材２との間は、第
一のワンウェイクラッチ４を介して離脱した状態にある
ことから、出力系回転部材２からの回転逆入力は、第一
のワンウェイクラッチ４を介して入力系回転部材１へ伝
達されることはない。つまり、出力系回転部材２の回転
は、遊星歯車機構３を介さないので増速されることな
く、第二のワンウェイクラッチ５を介して１：１で入力
系回転部材に伝達される。At this time, the first one-way clutch 4
Is in a state in which the torque transmission member is engaged in the opposite direction to the second one-way clutch 5, so that the torque transmission member is in the idling state, and between the input system rotation member 1 and the output system rotation member 2, Since it is disengaged via the one-way clutch 4, the reverse rotation input from the output system rotary member 2 is not transmitted to the input system rotary member 1 via the first one-way clutch 4. That is, the rotation of the output system rotary member 2 is transmitted to the input system rotary member 1: 1 via the second one-way clutch 5 without being accelerated because it does not pass through the planetary gear mechanism 3.
【００３４】[0034]
【発明の効果】本発明によれば、入力系回転部材と出力
系回転部材との間に、入力系回転部材からの回転を減速
する遊星機構を設けた動力伝達装置において、入力系回
転部材と出力系回転部材との間に第一のワンウェイクラ
ッチと第二のワンウェイクラッチとを設け、第一のワン
ウェイクラッチのトルク伝達部材の係合方向と第二のワ
ンウェイクラッチのトルク伝達部材の係合方向とを逆向
きにしたことにより、出力系回転部材からの回転逆入力
があっても、入力系回転部材の回転が増速してしまうこ
とはないので、入力系回転部材の駆動源における許容回
転数を超えることを未然に防止でき、安全性が大幅に向
上する。According to the present invention, in a power transmission device provided with a planetary mechanism for decelerating the rotation from the input system rotating member, between the input system rotating member and the output system rotating member, A first one-way clutch and a second one-way clutch are provided between the output system rotating member, and the engaging direction of the torque transmitting member of the first one-way clutch and the engaging direction of the torque transmitting member of the second one-way clutch. By reversing the and, the rotation of the input system rotating member will not be accelerated even if there is a reverse rotation input from the output system rotating member. It is possible to prevent exceeding the number, and the safety is greatly improved.
【図１】本発明に係る動力伝達装置の実施形態で、遊星
歯車機構を利用した減速装置の概略構成を示す断面図で
ある。FIG. 1 is a cross-sectional view showing a schematic configuration of a speed reducer using a planetary gear mechanism in an embodiment of a power transmission device according to the present invention.
【図２】図１の減速装置において、出力系回転部材から
入力系回転部材への回転逆入力状態を示す概略構成図で
ある。FIG. 2 is a schematic configuration diagram showing a reverse rotation input state from an output system rotating member to an input system rotating member in the reduction gear transmission of FIG.
【図３】図１の減速装置に組み込まれた遊星歯車機構を
示す構成図である。3 is a configuration diagram showing a planetary gear mechanism incorporated in the reduction gear transmission of FIG. 1. FIG.
【図４】図１の減速装置に組み込まれた遊星ローラ機構
を示す構成図である。4 is a configuration diagram showing a planetary roller mechanism incorporated in the speed reducer of FIG. 1. FIG.
【図５】図１の減速装置に組み込まれたスプラグタイプ
のワンウェイクラッチを示す構成図である。5 is a configuration diagram showing a sprag type one-way clutch incorporated in the reduction gear transmission of FIG. 1. FIG.
【図６】図１の減速装置に組み込まれたローラタイプの
ワンウェイクラッチを示す構成図である。6 is a configuration diagram showing a roller type one-way clutch incorporated in the speed reducer of FIG.
【図７】図１の減速装置に組み込まれたラチェットタイ
プのワンウェイクラッチを示す構成図である。7 is a configuration diagram showing a ratchet type one-way clutch incorporated in the reduction gear transmission of FIG. 1. FIG.
１ 入力系回転部材 ２ 出力系回転部材 ３ 遊星機構（遊星歯車機構） ４ 第一のワンウェイクラッチ ５ 第二のワンウェイクラッチ ６ 太陽歯車 ７ 静止部材（ハウジング） ８ 内歯車 ９ 遊星歯車 １１ キャリア 1 Input system rotating member 2 Output system rotating member 3 Planetary mechanism (planetary gear mechanism) 4 First one-way clutch 5 Second one-way clutch 6 sun gear 7 Stationary member (housing) 8 Internal gear 9 planetary gears 11 careers
───────────────────────────────────────────────────── フロントページの続き (72)発明者 里田 雅彦 愛知県安城市箕輪町正福田１−100 エヌ ティエヌ株式会社内 Ｆターム(参考） 3J027 FA50 GC13 GC22 GD04 GD08 GD12 GE29 3J051 AA02 BA03 BB06 BC01 BD02 BE04 CA09 ED04 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Masahiko Satota 1-100 Masafukuda, Minowa-cho, Anjo City, Aichi Prefecture Inside Thien Co., Ltd. F term (reference) 3J027 FA50 GC13 GC22 GD04 GD08 GD12 GE29 3J051 AA02 BA03 BB06 BC01 BD02 BE04 CA09 ED04
Claims (4)
部材と、その入力系回転部材から伝達された回転トルク
を外部へ取り出すための出力系回転部材と、前記入力系
回転部材と出力系回転部材との間に、入力系回転部材か
らの回転を減速する遊星機構を介して設けられ、入力系
回転部材から出力系回転部材への回転入力をトルク伝達
部材の係合により伝達し、出力系回転部材から入力系回
転部材への回転逆入力を前記トルク伝達部材の離脱によ
り遮断する第一のワンウェイクラッチと、前記入力系回
転部材と出力系回転部材との間に設けられ、入力系回転
部材から出力系回転部材への回転入力をトルク伝達部材
の離脱により遮断し、出力系回転部材から入力系回転部
材への回転逆入力を前記トルク伝達部材の係合により伝
達する第二のワンウェイクラッチとを具備したことを特
徴とする動力伝達装置。1. An input system rotating member which is rotationally driven by a drive source, an output system rotating member for taking out the rotational torque transmitted from the input system rotating member to the outside, the input system rotating member and the output system rotating member. It is provided between the input system rotating member and a planetary mechanism that reduces the rotation from the input system rotating member, and transmits the rotation input from the input system rotating member to the output system rotating member by the engagement of the torque transmitting member to output the output system. A first one-way clutch that blocks reverse rotation input from the rotating member to the input system rotating member by disengagement of the torque transmission member; and an input system rotating member that is provided between the input system rotating member and the output system rotating member. From the output system rotating member to the output system rotating member by disconnecting the torque transmitting member, and transmitting the reverse rotational input from the output system rotating member to the input system rotating member by engagement of the torque transmitting member. A power transmission device comprising a power clutch.
た内歯車と、その内側に前記入力系回転部材と同軸上に
配設された太陽歯車と、この太陽歯車と前記内歯車との
間にそれら両者と噛合するように介装された複数の遊星
歯車と、これら遊星歯車を円周方向等間隔に回転自在に
保持するキャリアとで構成されていることを特徴とする
請求項１に記載の動力伝達装置。2. The planetary mechanism comprises an internal gear provided on a stationary system member, a sun gear arranged inside the planetary gear, coaxially with the input system rotating member, and the sun gear and the internal gear. A plurality of planetary gears, which are interposed between the planetary gears, and a carrier that rotatably holds these planetary gears at equal intervals in the circumferential direction. The power transmission device described.
た固定輪と、その内側に前記入力系回転部材と同軸上に
配設された太陽ローラと、この太陽ローラと前記固定輪
との間にそれら両者と圧接する状態で介装された複数の
遊星ローラと、これら遊星ローラを円周方向等間隔に回
転自在に保持するキャリアとで構成されていることを特
徴とする請求項１に記載の動力伝達装置。3. The planetary mechanism comprises a stationary ring provided on a stationary system member, a sun roller arranged inside the stationary ring coaxially with the input system rotating member, and the sun roller and the stationary ring. 2. A plurality of planetary rollers interposed between them in pressure contact with each other, and a carrier for rotatably holding these planetary rollers at equal intervals in the circumferential direction. The power transmission device described.
材は、スプラグ、ローラあるいはラチェットのうちから
選択されるいずれか一つであることを特徴とする請求項
１乃至３のいずれかに記載の動力伝達装置。4. The power transmission device according to claim 1, wherein the torque transmission member of the one-way clutch is any one selected from a sprag, a roller, and a ratchet. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002023803A JP2003222204A (en) | 2002-01-31 | 2002-01-31 | Power transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002023803A JP2003222204A (en) | 2002-01-31 | 2002-01-31 | Power transmission device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003222204A true JP2003222204A (en) | 2003-08-08 |
Family
ID=27746410
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002023803A Pending JP2003222204A (en) | 2002-01-31 | 2002-01-31 | Power transmission device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003222204A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010077819A (en) * | 2008-09-24 | 2010-04-08 | Honda Motor Co Ltd | Starting and power generation device for motorcycle |
| KR101251804B1 (en) | 2011-10-26 | 2013-04-09 | 현대 파워텍 주식회사 | Planetary gear deceleration apparatus capable of keeping one-way rotation |
| JP2016098816A (en) * | 2014-11-20 | 2016-05-30 | ヴァンダイン スーパーターボ，インコーポレーテッド | Eccentric planetary traction drive type super turbocharger |
| KR101755943B1 (en) | 2015-12-15 | 2017-07-07 | 현대자동차주식회사 | Harmonic drive having improved back drivabilituy, driving module comprising the harmonic drive and method for controlling the driving module |
| CN109707761A (en) * | 2019-01-30 | 2019-05-03 | 张克军 | Retarder with clutch function |
| JP2019078308A (en) * | 2017-10-23 | 2019-05-23 | Ｎｓｋワーナー株式会社 | One-way clutch |
-
2002
- 2002-01-31 JP JP2002023803A patent/JP2003222204A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010077819A (en) * | 2008-09-24 | 2010-04-08 | Honda Motor Co Ltd | Starting and power generation device for motorcycle |
| KR101251804B1 (en) | 2011-10-26 | 2013-04-09 | 현대 파워텍 주식회사 | Planetary gear deceleration apparatus capable of keeping one-way rotation |
| JP2016098816A (en) * | 2014-11-20 | 2016-05-30 | ヴァンダイン スーパーターボ，インコーポレーテッド | Eccentric planetary traction drive type super turbocharger |
| KR101755943B1 (en) | 2015-12-15 | 2017-07-07 | 현대자동차주식회사 | Harmonic drive having improved back drivabilituy, driving module comprising the harmonic drive and method for controlling the driving module |
| US10274070B2 (en) | 2015-12-15 | 2019-04-30 | Hyundai Motor Company | Harmonic drive having improved back drivability, driving module including the harmonic drive and method for controlling the drive module |
| JP2019078308A (en) * | 2017-10-23 | 2019-05-23 | Ｎｓｋワーナー株式会社 | One-way clutch |
| CN109707761A (en) * | 2019-01-30 | 2019-05-03 | 张克军 | Retarder with clutch function |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7464801B2 (en) | Selectable one-way clutch | |
| US9086103B2 (en) | Rotation transmission device | |
| JPH0650358A (en) | Torque limitter equipped with automatic reset function | |
| JPH0261654B2 (en) | ||
| EP1049883A1 (en) | Spiral-type coupling | |
| SE518727C2 (en) | Building system for synchronization devices for a gearbox | |
| JP2003222204A (en) | Power transmission device | |
| JP2012177328A (en) | Turning device | |
| US3845666A (en) | Multi-speed motion transmitting mechanism | |
| JPH0925959A (en) | Two-way differential clutch | |
| JP2008151327A (en) | Rotation transmitting device | |
| JP2010144846A (en) | Speed increasing system with clutch mechanism | |
| JP2004308778A (en) | Power transmission device | |
| JP2008082457A (en) | One-way clutch with torque limiter | |
| JP2009078598A (en) | Driving force transmission device of hybrid vehicle | |
| JP2017160937A (en) | Oneway clutch | |
| JP2004084946A (en) | Motive power transmission device | |
| JP2004263760A (en) | Power transmission device | |
| JP2004263762A (en) | One-way clutch unit and one-way clutch | |
| JP2012017820A (en) | Reduction gear device | |
| JP2004324693A (en) | Clutch for intercepting reversed direction input | |
| KR950001130A (en) | Rotary transmission | |
| CN214036590U (en) | Controllable bidirectional overrunning clutch and transmission mechanism | |
| JP2007162814A (en) | One-way clutch built-in type pulley device | |
| JPH09264392A (en) | Planetary roller-type power transmitting device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20041124 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20060912 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20060915 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20061102 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20070517 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20070717 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20071120 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20080121 |
|
| A911 | Transfer of reconsideration by examiner before appeal (zenchi) |
Free format text: JAPANESE INTERMEDIATE CODE: A911 Effective date: 20080130 |
|
| A912 | Removal of reconsideration by examiner before appeal (zenchi) |
Free format text: JAPANESE INTERMEDIATE CODE: A912 Effective date: 20080425 |