JP3418963B2 - 2-way clutch unit - Google Patents

2-way clutch unit

Info

Publication number
JP3418963B2
JP3418963B2 JP10146394A JP10146394A JP3418963B2 JP 3418963 B2 JP3418963 B2 JP 3418963B2 JP 10146394 A JP10146394 A JP 10146394A JP 10146394 A JP10146394 A JP 10146394A JP 3418963 B2 JP3418963 B2 JP 3418963B2
Authority
JP
Japan
Prior art keywords
inner ring
peripheral surface
outer ring
drive source
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 - Fee Related
Application number
JP10146394A
Other languages
Japanese (ja)
Other versions
JPH07310766A (en
Inventor
博海 野尻
功 御厨
正浩 川合
元志 岡本
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.)
NTN Corp
Nippon Cable System Inc
Hi Lex Corp
Original Assignee
NTN Corp
Nippon Cable System Inc
Hi Lex Corp
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 NTN Corp, Nippon Cable System Inc, Hi Lex Corp filed Critical NTN Corp
Priority to JP10146394A priority Critical patent/JP3418963B2/en
Publication of JPH07310766A publication Critical patent/JPH07310766A/en
Application granted granted Critical
Publication of JP3418963B2 publication Critical patent/JP3418963B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D35/00—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/084—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate coupling members wedging by pivoting or rocking
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/10—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/10—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing
    • F16D41/105—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing the intermediate members being of circular cross-section, of only one size and wedging by rolling movement not having an axial component between inner and outer races, one of which is cylindrical
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、自動車のパワーウィン
ドや電動カーテン等において入力軸と出力軸との間のト
ルク伝達・遮断を行なう２ウェイクラッチユニットに関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-way clutch unit for transmitting / disconnecting torque between an input shaft and an output shaft in a power window or an electric curtain of an automobile.

【０００２】[0002]

【従来の技術】例えば、自動車のパワーウィンドでは、
通常、駆動モータの回転動力をウォーム＆ホイール機構
で減速して、ウィンドの開閉を行なう出力軸に伝達する
構成になっている。駆動モータの回転をウォーム＆ホイ
ール機構で減速する構成にしてあるのは、配置スペース
が狭いので小型モータを使用する必要があり、ウィンド
の開閉に必要な出力軸の低回転数、高トルクに比べ、駆
動モータが高回転数、低トルクであるためである。2. Description of the Related Art For example, in a power window of an automobile,
Normally, the rotational power of the drive motor is decelerated by a worm and wheel mechanism and transmitted to an output shaft that opens and closes the window. Since the rotation space of the drive motor is decelerated by the worm and wheel mechanism, it is necessary to use a small motor because the installation space is small. Compared to the low rotation speed and high torque of the output shaft required to open and close the window. This is because the drive motor has a high rotation speed and low torque.

【０００３】[0003]

【発明が解決しようとする課題】上記のようなパワーウ
ィンドにおいては、ウォーム＆ホイール機構の減速比が
一般に大きいため、駆動モータの停止時、出力軸側から
の手動入力、つまり、手動によるウィンドの開閉ができ
ない構造になっている。In the power window as described above, since the reduction ratio of the worm and wheel mechanism is generally large, when the drive motor is stopped, a manual input from the output shaft side, that is, a manual window operation is performed. It has a structure that cannot be opened and closed.

【０００４】ところが、駆動モータの停止時にウィンド
を手動で開閉することができないと、例えば、自動車が
海中に転落し、その際、電気系のショートにより駆動モ
ータが回転不能に陥った場合、運転者が車外へ脱出でき
なくなるような事態も予想される。However, if the window cannot be opened and closed manually when the drive motor is stopped, for example, if the car falls into the sea and the drive motor becomes unrotatable due to a short circuit in the electric system, the driver It is expected that the car will not be able to escape from the car.

【０００５】上記のような場合の対策として、駆動モー
タと出力軸との間に電磁クラッチを介在させ、モータ停
止時、電磁クラッチによって駆動モータと出力軸との連
結を開放する手段も考えられるが、消費電力量の増大
と、制御系の複雑化が懸念される。As a countermeasure against the above case, a means may be considered in which an electromagnetic clutch is interposed between the drive motor and the output shaft and the connection between the drive motor and the output shaft is released by the electromagnetic clutch when the motor is stopped. However, there is concern about an increase in power consumption and a complicated control system.

【０００６】そこで、本発明は、回転駆動源の停止時、
回転駆動源と出力軸との連結を機械的構造により自動的
に開放することのできる機構を提供しようとするもので
ある。[0006] Therefore, the present invention, when the rotation drive source is stopped,
An object of the present invention is to provide a mechanism capable of automatically opening the connection between the rotary drive source and the output shaft by a mechanical structure.

【０００７】[0007]

【課題を解決するための手段】本発明の２ウェイクラッ
チユニットは、外周面にカム面を備え、カム面で、外輪
の内周面との間に正逆両回転方向にくさび空間を形成す
る内輪と、カム面と外輪の内周面との間に配されたトル
ク伝達部材と、回転駆動源に連結され、トルク伝達部材
を収容するポケットを備えた保持器と、内輪と保持器と
を回転方向に連結する弾性部材と、静止系に制動固定さ
れた回転部材と内輪との間に介在する粘性流体とを備
え、回転駆動源の回転動力は、保持器からトルク伝達部
材を介して外輪へ伝達し、回転駆動源の停止時は、外輪
を入力系から正逆両回転方向に開放するものである。A two-way clutch unit according to the present invention has a cam surface on its outer peripheral surface, and the cam surface forms a wedge space between the inner peripheral surface of the outer ring and the inner peripheral surface of the outer ring. An inner ring, a torque transmitting member arranged between the cam surface and the inner peripheral surface of the outer ring, a cage connected to the rotary drive source and having a pocket for accommodating the torque transmitting member, and the inner ring and the cage. An elastic member connected in the rotational direction and a viscous fluid interposed between the rotating member fixed by braking in a stationary system and the inner ring are provided, and the rotational power of the rotational drive source is transferred from the retainer to the torque transmission unit.
Transmitted to the outer ring through the material, and when the rotation drive source is stopped, the outer ring
Is released from the input system in both forward and reverse rotation directions .

【０００８】また、本発明の２ウェイクラッチユニット
は、内周面にカム面を備え、カム面で、内輪の外周面と
の間に正逆両回転方向にくさび空間を形成する外輪と、
カム面と内輪の外周面との間に配されたトルク伝達部材
と、回転駆動源に連結され、トルク伝達部材を収容する
ポケットを備えた保持器と、外輪と保持器とを回転方向
に連結する弾性部材と、静止系に制動固定された回転部
材と外輪の間に介在する粘性流体とを備え、回転駆動源
の回転動力は、保持器からトルク伝達部材を介して内輪
へ伝達し、回転駆動源の停止時は、内輪を入力系から正
逆両回転方向に 開放するたものである。The two-way clutch unit of the present invention further comprises a cam surface on the inner peripheral surface, and the outer peripheral surface of the cam surface forming a wedge space between the outer peripheral surface of the inner ring and the outer peripheral surface of the inner ring in both forward and reverse rotation directions.
A torque transmission member disposed between the cam surface and the outer peripheral surface of the inner ring, a cage connected to the rotary drive source and having a pocket for accommodating the torque transmission member, and an outer ring and the cage coupled in the rotational direction. elastic member and, a viscous fluid interposed between the rotating member and an outer ring which is braked fixed to the stationary system, the rotation driving source for
The rotational power of the inner ring is generated from the cage via the torque transmission member.
To the inner ring from the input system when the rotary drive source is stopped.
It is opened in both reverse rotation directions .

【０００９】さらに、本発明の２ウェイクラッチユニッ
トは、正逆両回転方向にカム面を備え、カム面で、内輪
の外周面と外輪の内周面とに係合可能なトルク伝達部材
と、回転駆動源に連結され、トルク伝達部材を収容する
ポケットを備えた保持器と、内輪と保持器とを回転方向
に連結する弾性部材と、静止系に制動固定された回転部
材と内輪との間に介在する介在する粘性流体とを備え、
回転駆動源の回転動力は、保持器からトルク伝達部材を
介して外輪へ伝達し、回転駆動源の停止時は、外輪を入
力系から正逆両回転方向に開放するものである。Further, the two-way clutch unit of the present invention has a cam surface in both forward and reverse rotation directions, and a torque transmitting member which can be engaged with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring by the cam surface, Between the retainer, which is connected to the rotary drive source, and has a pocket for accommodating the torque transmission member, the elastic member that connects the inner ring and the retainer in the rotational direction, and the rotating member and the inner ring that are brake-fixed to the stationary system. With intervening viscous fluid,
The rotational power of the rotary drive source is transferred from the cage to the torque transmission member.
Transmitted to the outer ring via the outer ring.
It opens from the force system in both forward and reverse rotation directions .

【００１０】さらに、本発明の２ウェイクラッチユニッ
トは、正逆両回転方向にカム面を備え、カム面で、内輪
の外周面と外輪の内周面とに係合可能なトルク伝達部材
と、回転駆動源に連結され、トルク伝達部材を収容する
ポケットを備えた保持器と、外輪と保持器とを回転方向
に連結する弾性部材と、静止系に制動固定された回転部
材と外輪との間に介在する粘性流体とを備え、回転駆動
源の回転動力は、保持器からトルク伝達部材を介して内
輪へ伝達し、回転駆動源の停止時は、内輪を入力系から
正逆両回転方向に開放するものである。Further, the two-way clutch unit of the present invention has a cam surface in both forward and reverse rotation directions, and a torque transmitting member which can be engaged with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring by the cam surface. Between the retainer, which is connected to the rotary drive source and has a pocket for accommodating the torque transmission member, the elastic member that connects the outer ring and the retainer in the rotation direction, and the rotating member and the outer ring that are fixed by braking to the stationary system. and a viscous fluid interposed, the rotary drive
The rotational power of the source is transferred from the cage via the torque transmission member.
When the rotation drive source is stopped, the inner ring is transmitted from the input system.
It opens in both forward and reverse rotation directions .

【００１１】[0011]

【作用】回転駆動源が回転を始めると、その回転動力が
保持器に伝達され、保持器が回転する。そして、弾性部
材を介して内輪が保持器から回転動力を受けて回転する
が、この時、内輪は静止系に制動固定された回転部材と
の間に介在する粘性流体から粘性剪断抵抗を受ける。そ
のため、弾性部材が回転方向にたわみ、その分、保持器
と内輪との間に相対回転（内輪の回転遅れ）が生じる。When the rotary drive source starts rotating, the rotational power is transmitted to the holder, and the holder rotates. Then, the inner ring receives rotational power from the retainer via the elastic member to rotate, but at this time, the inner ring receives viscous shear resistance from the viscous fluid interposed between the inner ring and the rotating member brake-fixed to the stationary system. Therefore, the elastic member bends in the rotation direction, and relative rotation (rotation delay of the inner ring) occurs between the retainer and the inner ring by that amount.

【００１２】保持器と内輪との間に相対回転が生じる
と、保持器のポケットに収容されたトルク伝達部材が保
持器によって回転方向に押され、その方向のくさび空間
に係合する。これにより、保持器からトルク伝達部材を
介して外輪へ回転動力が伝達され、外輪が保持器および
内輪と一体となって回転する。When relative rotation occurs between the cage and the inner ring, the torque transmission member housed in the pocket of the cage is pushed in the rotational direction by the cage and engages with the wedge space in that direction. As a result, rotational power is transmitted from the retainer to the outer ring via the torque transmission member, and the outer ring rotates integrally with the retainer and the inner ring.

【００１３】一方、内輪の回転時、静止系に制動固定さ
れた回転部材は内輪との間に介在する粘性流体から粘性
剪断抵抗を受ける。この粘性剪断抵抗は内輪の回転に伴
って増大し、回転部材に対し回動力（回転トルク）とし
て作用する。そのため、回転部材は、この回動力が静止
系の制動力よりも小さい間は静止系に対し停止している
が、この回動力が制動力より大きくなると静止系に対し
回転を始め、定常回転に移行した後は、制動力に対応し
た量だけ内輪に対し遅れながら追随回転する。回転駆動
源が停止し、保持器および内輪の回転が止まると、粘性
流体の粘性剪断抵抗はなくなるので、弾性部材の弾性復
元力によって内輪が保持器に対し相対回転し、両者の円
周方向位置がセンタリングされる。内輪が保持器に対し
てセンタリングされると、トルク伝達部材がくさび空間
から離脱し、外輪が入力系から開放される。On the other hand, when the inner ring rotates, the rotating member fixed to the stationary system by braking receives viscous shear resistance from the viscous fluid interposed between the inner ring and the rotating member. This viscous shear resistance increases with the rotation of the inner ring and acts on the rotating member as turning force (rotating torque). Therefore, the rotating member stops with respect to the stationary system as long as this rotational power is smaller than the braking force of the stationary system, but when this rotational power becomes larger than the braking force, it starts rotating with respect to the stationary system and becomes steady rotation. After the shift, it rotates following the inner wheel with a delay corresponding to the braking force. When the rotation drive source stops and the cage and the inner ring stop rotating, the viscous shear resistance of the viscous fluid disappears, so the elastic restoring force of the elastic member causes the inner ring to rotate relative to the cage, and the circumferential position of both Is centered. When the inner ring is centered with respect to the cage, the torque transmission member separates from the wedge space, and the outer ring is released from the input system.

【００１４】上記の構成は外輪を出力軸とするものであ
るが、内輪を出力軸とする場合は、外輪と保持器とを弾
性部材で回転方向に連結すると共に、外輪と回転部材と
の間に粘性流体を介在させることにより、同様の作用が
得られる。In the above-mentioned structure, the outer ring serves as the output shaft. However, when the inner ring serves as the output shaft, the outer ring and the cage are connected in the rotational direction by the elastic member, and the outer ring and the rotating member are connected. The same effect can be obtained by interposing a viscous fluid in.

【００１５】また、上記の構成は内輪の外周面又は外輪
の内周面にカム面を設けたものであるが、正逆両回転方
向にカム面を備えたトルク伝達部材を用いることによっ
ても、同様の作用が得られる。In the above construction, the cam surface is provided on the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring. However, by using a torque transmitting member having cam surfaces in both forward and reverse rotation directions, Similar effects are obtained.

【００１６】[0016]

【実施例】以下、本発明の実施例を図面を参照しながら
説明する。Embodiments of the present invention will be described below with reference to the drawings.

【００１７】図１は、この実施例の２ウェイクラッチユ
ニットを使用した自動車のパワーウィンドの動力伝達系
を示す。２ウェイクラッチは、内輪１、出力軸としての
外輪２、内輪１の外周面と外輪２の内周面との間に介在
するトルク伝達部材としての複数のローラ３、入力軸と
しての保持器４を備えている。保持器４および外輪２
は、ケーシング５に回転自在に装着されている。また、
保持器４はウォーム＆ホイール機構６を介して回転駆動
源となるモータ７に連結され、外輪２はウィンドの開閉
機構（図示省略）に連結されている。尚、この実施例で
は、ウォーム＆ホイール機構６のホイールギヤ４ａを保
持器４の外径面に一体形成してある。FIG. 1 shows a power transmission system of an automobile power window using the 2-way clutch unit of this embodiment. The two-way clutch includes an inner ring 1, an outer ring 2 as an output shaft, a plurality of rollers 3 as a torque transmitting member interposed between an outer peripheral surface of the inner ring 1 and an inner peripheral surface of the outer ring 2, and a cage 4 as an input shaft. Is equipped with. Cage 4 and outer ring 2
Are rotatably mounted on the casing 5. Also,
The retainer 4 is connected via a worm & wheel mechanism 6 to a motor 7 that serves as a rotational drive source, and the outer ring 2 is connected to a window opening / closing mechanism (not shown). In this embodiment, the wheel gear 4a of the worm & wheel mechanism 6 is integrally formed on the outer diameter surface of the cage 4.

【００１８】内輪１の一方の端部側はカップ部１ａをな
し、このカップ部１ａに、軸部材８の他方の端部が軸方
向および半径方向の隙間をもって挿入されている。軸部
材８は、その一方の端部を制動部材９でケーシング５に
回転方向に摩擦固定されており、制動部材９の摩擦によ
る制動力よりも大きな回動力（回転トルク）を受けた場
合にのみ、ケーシング５に対して回転することができ
る。そして、内輪１と軸部材８との間の隙間に粘性流体
例えばシリコンオイル等の高粘性流体１０が封入され、
隙間内にシール１１で密封されている。One end portion side of the inner ring 1 forms a cup portion 1a, and the other end portion of the shaft member 8 is inserted into the cup portion 1a with a gap in the axial direction and the radial direction. The shaft member 8 has one end thereof frictionally fixed to the casing 5 by a braking member 9 in the rotation direction, and only when a rotational force (rotation torque) larger than the braking force due to the friction of the braking member 9 is received. , Can rotate with respect to the casing 5. Then, a viscous fluid, for example, a highly viscous fluid 10 such as silicon oil is sealed in a gap between the inner ring 1 and the shaft member 8,
A seal 11 is sealed in the gap.

【００１９】内輪１と保持器４との間には、図２（図１
におけるＸ−Ｘ断面）に示すようなセンタリングバネ１
２が介装されている。センタリングバネ１２は環状部１
２ａと、環状部１２ａの両端から外径側に伸びた一対の
係合部１２ｂとからなり、環状部１２ａを、内輪１のカ
ップ部１ａの端部内径に設けられた環状の段部１ａ１に
挿入される。一方、一対の係合部１２ｂは内輪１のカッ
プ部１ａの端部に設けられたスリット１ａ２を貫通して
保持器４の係合孔４ｂに入り込んでいる。図２に示す状
態では、一対の係合部４ｂがスリット１ａ２および係合
孔４ｂの円周方向側壁にそれぞれ弾性力もって接触し、
これにより、内輪１と保持器４とが回転方向に連結さ
れ、かつ、内輪１の保持器４に対する円周方向位置決め
（センタリング）がなされる。Between the inner ring 1 and the cage 4 is shown in FIG.
Centering spring 1 as shown in FIG.
2 is installed. The centering spring 12 is the annular portion 1.
2a and a pair of engaging portions 12b extending from the both ends of the annular portion 12a to the outer diameter side. The annular portion 12a is attached to an annular step portion 1a1 provided on the inner diameter of the end portion of the cup portion 1a of the inner ring 1. Is inserted. On the other hand, the pair of engaging portions 12 b penetrates the slit 1 a 2 provided at the end of the cup portion 1 a of the inner ring 1 and enters the engaging hole 4 b of the cage 4. In the state shown in FIG. 2, the pair of engaging portions 4b come into contact with the slits 1a2 and the side walls in the circumferential direction of the engaging hole 4b with elastic force,
As a result, the inner ring 1 and the cage 4 are connected in the rotational direction, and the inner ring 1 is positioned in the circumferential direction (centering) with respect to the cage 4.

【００２０】図３（図１におけるＹ−Ｙ断面）および図
４に示すように、内輪１の他方の端部側外周面には複数
の平坦なカム面１ｂが円周等間隔に設けられ、各カム面
１ｂと外輪２の内周面との間に、正逆両回転方向にくさ
び空間が形成されている。各ローラ３はそれぞれ各カム
面１ｂと外輪２の内周面との間に配され、保持器４のポ
ケット４ｃに収容保持される。尚、図２〜図４は、内輪
１がセンタリングバネ１２によってセンタリングされた
状態を示しており、この状態では、図４に示すように、
保持器４のポケット４ｃの円周方向中心とカム面１ｂの
円周方向中心とが一致する。そのため、ローラ３はカム
面１ｂの略中央に位置し、正逆両回転方向のくさび空間
からそれぞれ離脱する。以下、この状態を中立位置とい
う。As shown in FIG. 3 (Y-Y cross section in FIG. 1) and FIG. 4, a plurality of flat cam surfaces 1b are provided on the outer peripheral surface on the other end side of the inner ring 1 at equal intervals around the circumference. A wedge space is formed between each cam surface 1b and the inner peripheral surface of the outer ring 2 in both forward and reverse rotation directions. Each roller 3 is arranged between each cam surface 1b and the inner peripheral surface of the outer ring 2, and is housed and held in the pocket 4c of the cage 4. 2 to 4 show a state in which the inner ring 1 is centered by the centering spring 12, and in this state, as shown in FIG.
The circumferential center of the pocket 4c of the cage 4 and the circumferential center of the cam surface 1b coincide. Therefore, the roller 3 is located substantially in the center of the cam surface 1b and separates from the wedge space in both the forward and reverse rotation directions. Hereinafter, this state is referred to as a neutral position.

【００２１】図１において、モータ７が回転を始める
と、その回転動力がウォーム＆ホイール機構６を介して
保持器４に減速伝達され、保持器４が回転する。そし
て、センタリングバネ１２を介して内輪１が保持器４か
ら回転動力を受けて回転するが、この時、内輪１は軸部
材８との間に介在する高粘性流体１０の粘性剪断抵抗を
受ける。そのため、センタリングバネ１２の係合部１２
ｂがたわみ、その分、保持器４と内輪１との間に相対回
転（内輪１の回転遅れ）が生じる。尚、この時のセンタ
リングバネ１２の弾性力をＫ１、高粘性流体１０の粘性
剪断抵抗をＫ２とすると、センタリングバネ１２の係合
部１２ｂがたわむためには、Ｋ１〈Ｋ２の関係が必要で
ある。In FIG. 1, when the motor 7 starts rotating, the rotational power thereof is decelerated and transmitted to the cage 4 via the worm & wheel mechanism 6, and the cage 4 rotates. Then, the inner ring 1 rotates by receiving the rotational power from the cage 4 via the centering spring 12, but at this time, the inner ring 1 receives the viscous shear resistance of the high-viscosity fluid 10 interposed between the inner ring 1 and the shaft member 8. Therefore, the engaging portion 12 of the centering spring 12
B is deflected, and relative rotation (rotation delay of the inner ring 1) occurs between the cage 4 and the inner ring 1 by that amount. When the elastic force of the centering spring 12 at this time is K1 and the viscous shear resistance of the high-viscosity fluid 10 is K2, the relationship of K1 <K2 is necessary for the engaging portion 12b of the centering spring 12 to bend. .

【００２２】保持器４と内輪１との間に相対回転が生じ
ると、図５に示すように、保持器４のポケット４ｃに収
容されたローラ３が保持器４によって回転方向（保持器
４の回転方向）に押され、その方向のくさび空間に係合
する。この時の、ローラ３とカム面１ｂおよび外輪２の
内周面との接触点をそれぞれＣ１、Ｃ２、保持器４がロ
ーラ３を押す力をＦとすると、力Ｆの法線方向分力Ｆ
１、Ｆ２によって、接触点Ｃ１、Ｃ２にはそれぞれ摩擦
力μＦ１、μＦ２（μ：摩擦係数）が発生する。これら
摩擦力によって、保持器４からローラ３を介して外輪２
へ回転動力が伝達され、外輪２が保持器４および内輪１
と一体となって回転する。外輪２の回転により、図示さ
れていないウィンドが開閉する。When relative rotation occurs between the cage 4 and the inner ring 1, as shown in FIG. 5, the roller 3 accommodated in the pocket 4c of the cage 4 is rotated by the cage 4 (in the cage 4). In the direction of rotation) to engage the wedge space in that direction. At this time, when the contact points of the roller 3 with the cam surface 1b and the inner peripheral surface of the outer ring 2 are C1 and C2, respectively, and the force with which the retainer 4 pushes the roller 3 is F, a force F in the normal direction F
1 and F2 generate frictional forces μF1 and μF2 (μ: friction coefficient) at the contact points C1 and C2, respectively. By these frictional forces, the outer ring 2 is passed from the cage 4 through the rollers 3.
Rotational power is transmitted to the outer ring 2 and the cage 4 and the inner ring 1
Rotates together with. The rotation of the outer ring 2 opens and closes a window (not shown).

【００２３】一方、内輪１の回転時、軸部材８は内輪１
との間に介在する高粘性流体１０から粘性剪断抵抗を受
ける。この粘性剪断抵抗は内輪１の回転に伴って増大
し、軸部材８に対し回動力（回転トルク）として作用す
る。軸部材８はこの回動力が制動部材９の制動力より小
さい間はケーシング５に対し停止しているが、この回動
力が制動力より大きくなるとケーシング５に対し回転を
始め、そして定常回転に移行した後は、制動部材９の制
動力に対応した量だけ内輪１に対し遅れながら追随回転
する。したがって、定常回転移行後（クラッチがトルク
伝達状態に切り替わった後）は、高粘性流体１０の粘性
剪断抵抗は制動部材９の制動力に対応した所定値にな
り、これよりも大きくはならない。高粘性流体１０の粘
性剪断抵抗は、本来的には、保持器４と内輪１との間に
相対回転を生じさせる、つまり、クラッチを自動的にト
ルク伝達状態に切り替えるために必要な要素であり、ク
ラッチの切り替わり時以降はできるだけ小さいほうが望
ましい。ここで、制動部材９の制動力をＫ３とすると、
Ｋ３≧Ｋ２（クラッチ切り替わり時の粘性剪断抵抗）〉
Ｋ１（センタリングバネ１２の弾性力）の関係が必要で
あり、制動力Ｋ３はこの関係を満たす範囲内で最小値に
設定すると良い。この実施例では、制動部材９としてＯ
リングを使用し、Ｏリングの締代調整によって、制動力
Ｋ３が最適値になるよう設定してある。ただし、制動部
材９は、軸部材８に所定の制動力を及ぼし得るものであ
れば特にＯリングには限られない。また、制動力は摩擦
力には限られない。On the other hand, when the inner ring 1 is rotated, the shaft member 8 is
A viscous shear resistance is received from the high-viscosity fluid 10 interposed between and. This viscous shear resistance increases with the rotation of the inner ring 1, and acts on the shaft member 8 as a turning force (rotating torque). The shaft member 8 is stopped with respect to the casing 5 while the turning force is smaller than the braking force of the braking member 9, but when the turning force is larger than the braking force, the shaft member 8 starts rotating with respect to the casing 5 and shifts to steady rotation. After that, the inner ring 1 is rotated with a delay corresponding to the braking force of the braking member 9 with a delay. Therefore, after the steady rotation shift (after the clutch is switched to the torque transmission state), the viscous shear resistance of the high-viscosity fluid 10 becomes a predetermined value corresponding to the braking force of the braking member 9, and does not become larger than this. The viscous shear resistance of the high-viscosity fluid 10 is essentially an element necessary for causing relative rotation between the cage 4 and the inner ring 1, that is, for automatically switching the clutch to the torque transmission state. , It is desirable to be as small as possible after switching the clutch. If the braking force of the braking member 9 is K3,
K3 ≧ K2 (viscous shear resistance when switching clutch)>
The relationship of K1 (elastic force of the centering spring 12) is necessary, and the braking force K3 may be set to the minimum value within the range that satisfies this relationship. In this embodiment, the braking member 9 is O
The braking force K3 is set to an optimum value by using a ring and adjusting the interference of the O-ring. However, the braking member 9 is not particularly limited to the O-ring as long as it can exert a predetermined braking force on the shaft member 8. Further, the braking force is not limited to the frictional force.

【００２４】モータ７が停止し、保持器４および内輪１
の回転が止まると、高粘性流体１０の粘性剪断抵抗はな
くなるので、センタリングバネ１２の弾性復元力によっ
て内輪１が保持器４に対し相対回転し、図２〜図４に示
す中立位置にセンタリングされる。尚、内輪１は中立位
置まで相対回転する際に高粘性流体１０から粘性剪断抵
抗を受けるが、粘性剪断抵抗は相対回転速度に比例する
ので、内輪１はモータ７よりも遅い速度ではあるが、回
転することはできる。このようにして、内輪１が保持器
４に対しセンタリングされると、ローラ３がくさび空間
から離脱し中立位置に戻るので、外輪２が保持器４およ
び内輪１に対しフリーになって、入力系から開放され
る。したがって、この状態では外輪２を手動で回転させ
ることができ、これにより、モータ７の停止時であって
も、ウィンドを手動で開閉することが可能となる。The motor 7 stops, and the cage 4 and the inner ring 1
When the rotation is stopped, the viscous shear resistance of the high-viscosity fluid 10 disappears, so that the inner ring 1 relatively rotates with respect to the retainer 4 by the elastic restoring force of the centering spring 12 and is centered at the neutral position shown in FIGS. It When the inner ring 1 relatively rotates to the neutral position, it receives viscous shear resistance from the high-viscosity fluid 10, but since the viscous shear resistance is proportional to the relative rotation speed, the inner ring 1 is slower than the motor 7, It can rotate. In this way, when the inner ring 1 is centered with respect to the cage 4, the roller 3 is released from the wedge space and returns to the neutral position, so that the outer ring 2 becomes free with respect to the cage 4 and the inner ring 1, and the input system is released. Is released from. Therefore, in this state, the outer ring 2 can be manually rotated, and thus the window can be manually opened and closed even when the motor 7 is stopped.

【００２５】図６に示す実施例は、上記平坦なカム面１
ｂに代えて、外輪２の内周面に溝状のカム面２ｂを設け
たものである。外輪２のカム面２ｂと内輪１の外周面と
の間に正逆両回転方向にくさび空間が形成される。この
場合、保持器４と外輪２との間に、上記センタリングバ
ネ１２に相当する弾性部材を介在させると共に、外輪２
と、上記軸部材８に相当する回転部材（静止系に制動固
定する）との間に高粘性流体１０を介在させることによ
り、上記実施例の構成と同様の作用効果を得ることがで
きる。あるいは、図示は省略するが、内輪１の外周面
に、平坦なカム面１ｂに代えて、溝状のカム面を形成し
ても良い。In the embodiment shown in FIG. 6, the flat cam surface 1 is used.
Instead of b, a groove-shaped cam surface 2b is provided on the inner peripheral surface of the outer ring 2. A wedge space is formed between the cam surface 2b of the outer ring 2 and the outer peripheral surface of the inner ring 1 in both forward and reverse rotation directions. In this case, an elastic member corresponding to the centering spring 12 is interposed between the cage 4 and the outer ring 2 and the outer ring 2
By interposing the high-viscosity fluid 10 between the rotary member corresponding to the shaft member 8 (braking fixed to the stationary system), it is possible to obtain the same effect as the structure of the above-described embodiment. Alternatively, although not shown, a groove-shaped cam surface may be formed on the outer peripheral surface of the inner ring 1 instead of the flat cam surface 1b.

【００２６】図７に示す実施例は、トルク伝達部材とし
てスプラグ３’を用いたものである。その他の基本的な
構成は、図１に示すものと同様である。スプラグ３’は
正逆両回転方向にカム面３’ａ１、３’ａ２、３’ａ
３、３’ａ４を備え、外側保持器４’のポケット４’ｃ
と内側保持器４”のポケット４”ｃとに、それぞれバネ
４’ｃ１、４’ｃ２、４”ｃ１、４”２を介して収容保
持される。外側保持器４’は図１に示すウォーム＆ホイ
ール機構６を介してモータ７に連結され、内側保持器
４”は適宜の手段で内輪１に固定される。また、内輪１
と外側保持器４’と間には図１に示すセンタリングバネ
１２が介装され、内輪１と図１に示す軸部材８との間の
隙間には高粘性流体１０が密封される。図７に示す状態
では、スプラグ３’はバネ４’ｃ１、４’ｃ２、４”ｃ
１、４”２によって円周方向の両側から均等に押圧さ
れ、中立位置を保っている。この状態では、スプラグ
３’は内輪１の外周面および外輪２の内周面とは係合し
ない。一方、モータ７が回転を始めると、前述した態様
で、外側保持器４’と内輪１およびこれに固定された内
側保持器４”との間に相対回転が生じ（内側保持器４”
の回転遅れ）、図８に示すように、スプラグ３’が外側
保持器４’によって回転方向（外側保持器４’の回転方
向）に押されて揺動し、カム面３’ａ２、３’ａ３が内
輪１の外周面および外輪２の内周面の双方に係合する。
これにより、外側保持器４’からスプラグ３’を介して
外輪２へ回転動力が伝達され、外輪２が外側保持器
４’、内輪１および内側保持器４”と一体となって回転
する。The embodiment shown in FIG. 7 uses a sprag 3'as a torque transmission member. Other basic configurations are the same as those shown in FIG. The sprags 3'are cam surfaces 3'a1, 3'a2, 3'a in both forward and reverse rotation directions.
3, 3'a4, pocket 4'c of outer cage 4 '
And in the pocket 4 "c of the inner cage 4" via springs 4'c1, 4'c2, 4 "c1, 4" 2, respectively. The outer cage 4'is connected to the motor 7 via the worm and wheel mechanism 6 shown in Fig. 1, and the inner cage 4 "is fixed to the inner ring 1 by an appropriate means.
The centering spring 12 shown in FIG. 1 is interposed between the outer holder 4'and the outer retainer 4 ', and the high-viscosity fluid 10 is sealed in the gap between the inner ring 1 and the shaft member 8 shown in FIG. In the state shown in FIG. 7, the sprags 3 ′ have springs 4′c1, 4′c2, 4 ″ c.
It is uniformly pressed from both sides in the circumferential direction by 1, 4 "2 and maintains the neutral position. In this state, the sprag 3'does not engage with the outer peripheral surface of the inner ring 1 and the inner peripheral surface of the outer ring 2. On the other hand, when the motor 7 starts to rotate, relative rotation occurs between the outer cage 4 ′ and the inner ring 1 and the inner cage 4 ″ fixed to the inner cage 4 ′ in the manner described above (the inner cage 4 ″).
8), as shown in FIG. 8, the sprag 3'is pushed by the outer retainer 4'in the rotational direction (the rotational direction of the outer retainer 4 ') and rocks, and the cam surfaces 3'a2, 3'. a3 engages with both the outer peripheral surface of the inner ring 1 and the inner peripheral surface of the outer ring 2.
As a result, rotational power is transmitted from the outer cage 4 ′ to the outer ring 2 via the sprag 3 ′, and the outer ring 2 rotates integrally with the outer cage 4 ′, the inner ring 1 and the inner cage 4 ″.

【００２７】一方、モータ７が停止すると、前述した態
様で、内輪１および内側保持器４”が外側保持器４’に
対しセンタリングされるので、スプラグ３’は図７に示
す中立位置に戻り、外輪２が入力系から開放される。On the other hand, when the motor 7 is stopped, the inner ring 1 and the inner cage 4 "are centered with respect to the outer cage 4'in the manner described above, so that the sprag 3'returns to the neutral position shown in FIG. The outer ring 2 is released from the input system.

【００２８】尚、内側保持器４”をモータ７に連結する
場合は、内側保持器４”と外輪２との間に図１に示すセ
ンタリングバネ１２に相当する弾性部材を介在させると
共に、外輪２と、図１に示す軸部材８に相当する回転部
材との間に高粘性流体１０を介在させる。また、上記実
施例において、バネ４’ｃ１および４’ｃ２を省略、ま
たは、バネ４”ｃ１および４”２を省略しても良く、あ
るいは、双方とも省略しても良い。When the inner cage 4 "is connected to the motor 7, an elastic member corresponding to the centering spring 12 shown in FIG. The high-viscosity fluid 10 is interposed between the rotary member and the rotary member corresponding to the shaft member 8 shown in FIG. Further, in the above embodiment, the springs 4′c1 and 4′c2 may be omitted, or the springs 4 ″ c1 and 4 ″ 2 may be omitted, or both may be omitted.

【００２９】[0029]

【発明の効果】以上説明したように、本発明の２方向ク
ラッチユニットは、回転駆動源の停止時、入力系と出力
系との間のトルク伝達を自動的に遮断し、出力系を入力
系から自動的に開放する機能を有するものである。した
がって、本発明の２方向クラッチユニットを、例えば、
自動車のパワーウィンドや電動カーテンの動力伝達系に
使用することにより、駆動モータの停止時に、出力軸側
から手動その他の手段でウィンドやカーテンを開閉する
ことが可能になるので、これら装置の利便性、安全性を
より一層向上させることができる。しかも、本発明の２
方向クラッチユニットはトルク伝達・遮断を自動的にか
つ機械的に行なうものであるから、消費電力の増大、制
御系の複雑化といった懸念もない。As described above, the two-way clutch unit according to the present invention automatically shuts off the torque transmission between the input system and the output system when the rotary drive source is stopped, so that the output system has the input system. It has a function to automatically release from. Therefore, the two-way clutch unit of the present invention is, for example,
By using it in the power transmission system of automobile power windows and electric curtains, it becomes possible to open and close the windows and curtains from the output shaft side manually or by other means when the drive motor is stopped. The safety can be further improved. Moreover, 2 of the present invention
Since the directional clutch unit automatically and mechanically performs torque transmission / disconnection, there is no concern about an increase in power consumption and a complicated control system.

【００３０】尚、本発明は、以上に例示した用途に限ら
ず、回転駆動源の停止時に、出力系を入力系から開放す
る必要がある用途一般に適用することができる。The present invention can be applied not only to the above-exemplified applications but also to general applications in which it is necessary to open the output system from the input system when the rotary drive source is stopped.

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

【図１】本発明の２方向クラッチユニットを使用した自
動車のパワーウィンドの動力伝達系を示す断面図であ
る。FIG. 1 is a sectional view showing a power transmission system of a power window of an automobile using a two-way clutch unit of the present invention.

【図２】図１におけるＸ−Ｘ断面図を示す断面図であ
る。FIG. 2 is a sectional view showing an XX sectional view in FIG.

【図３】図１におけるＹ−Ｙ断面図を示す断面図であ
る。3 is a cross-sectional view showing a YY cross-sectional view in FIG.

【図４】カム面とトルク伝達部材の周辺部を示す拡大断
面図である。FIG. 4 is an enlarged cross-sectional view showing a peripheral portion of a cam surface and a torque transmission member.

【図５】カム面とトルク伝達部材の周辺部を示す拡大断
面図である。FIG. 5 is an enlarged cross-sectional view showing a peripheral portion of a cam surface and a torque transmission member.

【図６】本発明の他の実施例に係わるカム面とトルク伝
達部材の周辺部を示す拡大断面図である。FIG. 6 is an enlarged cross-sectional view showing a cam surface and a peripheral portion of a torque transmission member according to another embodiment of the present invention.

【図７】本発明の他の実施例に係わるトルク伝達部材の
周辺部を示す拡大断面図である。FIG. 7 is an enlarged cross-sectional view showing a peripheral portion of a torque transmission member according to another embodiment of the present invention.

【図８】本発明の他の実施例に係わるトルク伝達部材の
周辺部を示す拡大断面図である。FIG. 8 is an enlarged cross-sectional view showing a peripheral portion of a torque transmission member according to another embodiment of the present invention.

【符号の説明】[Explanation of symbols]

１ 内輪 １ｂ カム面 ２ 外輪 ３ ローラ（トルク伝達部材） ４ 保持器（入力軸） ７ モータ ８ 軸部材（回転部材） １０ 高粘性流体 １２ センタリングバネ 1 inner ring 1b Cam surface 2 outer ring 3 rollers (torque transmission member) 4 Cage (input shaft) 7 motor 8 shaft members (rotating members) 10 High viscosity fluid 12 Centering spring

───────────────────────────────────────────────────── フロントページの続き (72)発明者 岡本 元志 大阪府豊中市末広町２丁目９番地33号 (56)参考文献 特開 平３−14924（ＪＰ，Ａ) 特開 平６−33957（ＪＰ，Ａ) 特開 平４−228939（ＪＰ，Ａ) 特開 平４−171325（ＪＰ，Ａ) 特公 昭41−363（ＪＰ，Ｂ１) (58)調査した分野(Int.Cl.7，ＤＢ名) F16D 41/00 - 47/06 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Motoshi Okamoto 2-9, Suehiro-cho, Toyonaka City, Osaka Prefecture (56) Reference JP-A-3-14924 (JP, A) JP-A-6-33957 ( JP, A) JP 4-228939 (JP, A) JP 4-171325 (JP, A) JP 41-363 (JP, B1) (58) Fields investigated (Int. Cl. 7 , DB name) F16D 41/00-47/06

Claims (4)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】 外周面にカム面を備え、カム面で、外輪
の内周面との間に正逆両回転方向にくさび空間を形成す
る内輪と、前記カム面と外輪の内周面との間に配された
トルク伝達部材と、回転駆動源に連結され、前記トルク
伝達部材を収容するポケットを備えた保持器と、前記内
輪と保持器とを回転方向に連結する弾性部材と、静止系
に制動固定された回転部材と前記内輪との間に介在する
粘性流体とを備え、前記回転駆動源の回転動力は、前記保持器からトルク伝
達部材を介して外輪へ伝達し、前記回転駆動源の停止時
は、前記外輪を入力系から正逆両回転方向に開放する こ
とを特徴とする２ウェイクラッチユニット。1. An inner ring having a cam surface on an outer peripheral surface, the inner peripheral surface forming a wedge space between the inner peripheral surface of the outer ring and the inner peripheral surface of the outer ring, and the inner peripheral surface of the cam surface and the outer ring. A torque transmission member arranged between the two, a retainer that is connected to the rotary drive source and has a pocket that accommodates the torque transmission member, an elastic member that connects the inner ring and the retainer in a rotational direction, and a stationary member. A viscous fluid is interposed between a rotating member that is fixed to the system by braking and a viscous fluid, and the rotational power of the rotational drive source is transmitted from the retainer by torque transmission.
When the rotation drive source is stopped by transmitting to the outer ring via the reaching member
The two-way clutch unit is characterized in that the outer ring is released from the input system in both forward and reverse rotation directions . 【請求項２】 内周面にカム面を備え、カム面で、内輪
の外周面との間に正逆両回転方向にくさび空間を形成す
る外輪と、前記カム面と内輪の外周面との間に配された
トルク伝達部材と、回転駆動源に連結され、前記トルク
伝達部材を収容するポケットを備えた保持器と、前記外
輪と保持器とを回転方向に連結する弾性部材と、静止系
に制動固定された回転部材と前記外輪との間に介在する
粘性流体とを備え、前記回転駆動源の回転動力は、前記保持器からトルク伝
達部材を介して内輪へ伝達し、前記回転駆動源の停止時
は、前記内輪を入力系から正逆両回転方向に開放する こ
とを特徴とする２ウェイクラッチユニット。2. An outer ring having a cam surface on its inner peripheral surface, the outer peripheral surface forming a wedge space between the outer peripheral surface of the inner ring and the outer peripheral surface of the inner ring, and the outer peripheral surface of the cam surface and the inner ring. A torque transmission member arranged in between, a retainer connected to the rotary drive source and having a pocket for accommodating the torque transmission member, an elastic member connecting the outer ring and the retainer in a rotational direction, and a stationary system. A viscous fluid interposed between the rotating member and the outer ring, the rotational power of the rotary drive source is transmitted from the cage by torque transmission.
When the rotation drive source is stopped, transmitted to the inner ring via the reaching member
The two-way clutch unit is characterized in that the inner ring is released from the input system in both forward and reverse rotation directions . 【請求項３】 正逆両回転方向にカム面を備え、カム面
で、内輪の外周面と外輪の内周面とに係合可能なトルク
伝達部材と、回転駆動源に連結され、前記トルク伝達部
材を収容するポケットを備えた保持器と、前記内輪と保
持器とを回転方向に連結する弾性部材と、静止系に制動
固定された回転部材と前記内輪との間に介在する介在す
る粘性流体とを備え、前記回転駆動源の回転動力は、前記保持器からトルク伝
達部材を介して外輪へ伝達し、前記回転駆動源の停止時
は、前記外輪を入力系から正逆両回転方向に開放する こ
とを特徴とする２ウェイクラッチユニット。3. A torque transmitting member, comprising a cam surface in both forward and reverse rotation directions, the cam surface being engageable with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, the torque transmitting member being coupled to a rotary drive source, A retainer having a pocket for accommodating a transmission member, an elastic member for connecting the inner ring and the retainer in a rotational direction, and an intervening viscosity interposed between a rotating member brake-fixed to a stationary system and the inner ring. And a fluid, and rotational power of the rotary drive source is transmitted from the cage by torque transmission.
When the rotation drive source is stopped by transmitting to the outer ring via the reaching member
The two-way clutch unit is characterized in that the outer ring is released from the input system in both forward and reverse rotation directions . 【請求項４】 正逆両回転方向にカム面を備え、カム面
で、内輪の外周面と外輪の内周面とに係合可能なトルク
伝達部材と、回転駆動源に連結され、前記トルク伝達部
材を収容するポケットを備えた保持器と、前記外輪と保
持器とを回転方向に連結する弾性部材と、静止系に制動
固定された回転部材と前記外輪との間に介在する粘性流
体とを備え、前記回転駆動源の回転動力は、前記保持器からトルク伝
達部材を介して内輪へ伝達し、前記回転駆動源の停止時
は、前記内輪を入力系から正逆両回転方向に開放する こ
とを特徴とする２ウェイクラッチユニット。4. A torque transmission member, comprising a cam surface in both forward and reverse rotation directions, the cam surface being engageable with the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, and being connected to a rotary drive source, A retainer having a pocket for accommodating a transmission member, an elastic member for connecting the outer ring and the retainer in a rotational direction, and a viscous fluid interposed between a rotating member brake-fixed to a stationary system and the outer ring. The rotary power of the rotary drive source is transmitted from the cage by torque.
When the rotation drive source is stopped, transmitted to the inner ring via the reaching member
The two-way clutch unit is characterized in that the inner ring is released from the input system in both forward and reverse rotation directions .
JP10146394A 1994-05-17 1994-05-17 2-way clutch unit Expired - Fee Related JP3418963B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP10146394A JP3418963B2 (en) 1994-05-17 1994-05-17 2-way clutch unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP10146394A JP3418963B2 (en) 1994-05-17 1994-05-17 2-way clutch unit

Publications (2)

Publication Number Publication Date
JPH07310766A JPH07310766A (en) 1995-11-28
JP3418963B2 true JP3418963B2 (en) 2003-06-23

Family

ID=14301410

Family Applications (1)

Application Number Title Priority Date Filing Date
JP10146394A Expired - Fee Related JP3418963B2 (en) 1994-05-17 1994-05-17 2-way clutch unit

Country Status (1)

Country Link
JP (1) JP3418963B2 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3418964B2 (en) * 1994-12-26 2003-06-23 Ｎｔｎ株式会社 Clutch unit
US5806246A (en) * 1995-02-28 1998-09-15 Nippon Cable System Inc. Powered sliding-door system and actuating devices for the same
JP2000035061A (en) * 1998-07-16 2000-02-02 Ntn Corp Power intermittent device for hybrid vehicle
JP2010221959A (en) * 2009-03-25 2010-10-07 Aisin Seiki Co Ltd Vehicular sunshade device

Also Published As

Publication number Publication date
JPH07310766A (en) 1995-11-28

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