JP2006342876A

JP2006342876A - Reverse input shutting-off clutch

Info

Publication number: JP2006342876A
Application number: JP2005168533A
Authority: JP
Inventors: Hiromi Nojiri; 博海野尻; Makoto Yasui; 誠安井; Yasushi Tateishi; 康司立石; Koji Sato; 光司佐藤
Original assignee: NTN Corp; NTN Toyo Bearing Co Ltd
Current assignee: NTN Corp
Priority date: 2005-06-08
Filing date: 2005-06-08
Publication date: 2006-12-21

Abstract

<P>PROBLEM TO BE SOLVED: To securely prevent the occurrence of continuous abnormal sound and vibration without causing rotation loss and reduction of a clutch function when driving. <P>SOLUTION: This reverse input shutting-off clutch is provided with an input side member 9 in which rotation torque is inputted, an output shaft 12 for outputting rotation torque, an outer ring 13 for restraining rotation, a torque transmission means 21 provided between the input side member 9 and the output shaft 12 to transmit input torque from the input side member 9 to the output shaft 12, and a lock means 22 provided between the outer ring 13 and the output shaft 12 and locking the output shaft 12 and the outer ring 13 for reverse input torque from the output shaft 12 to shut off torque transmission to the input side member 9. Input torque is transmitted to the output shaft 12 by the torque transmission means 21 while unlocking a locking state of the output shaft 12 and the outer ring 13 by the lock means 22 when loading input torque. The input side member 9 is constituted by other members of an input shaft 10 and a cage 11, and play in the direction of rotation is provided in a rotation transmission part 20 between the input shaft 10 and the cage 11. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、例えば自動車の操舵装置などに組み込まれ、入力側からの回転トルクを出力側へ伝達する機能と、出力側からの逆入力トルクを遮断する機能を併せ持った逆入力遮断クラッチに関する。 The present invention relates to a reverse input cutoff clutch that is incorporated in, for example, an automobile steering device and has both a function of transmitting rotational torque from the input side to the output side and a function of blocking reverse input torque from the output side.

例えば自動車の操舵装置に組み込まれる逆入力遮断クラッチの一構造例を図８および図９に示す。同図に示す逆入力遮断クラッチは、回転トルクが入力される入力側部材としての入力軸（保持器）１と、その入力軸１と同軸上に配置され、回転トルクが出力される出力側部材としての出力軸２と、入力軸１および出力軸２の外周側に同軸的に配置され、回転が拘束される静止側部材としての外輪３と、出力軸２の外周面に形成されたカム面２ａと外輪３の内周面３ａとの間に形成された楔隙間４に係合・離脱可能に介在した係合子としての一対のローラ５および一対のローラ５を相互に離間する方向に弾性力を付勢する弾性部材としてのばね６と、入力軸１の出力軸２と対向する軸端面にピン８を軸方向に向けて突出するように植設し、出力軸２の入力軸１と対向する軸端面に径方向に沿って形成された凹溝７に前述のピン８を挿入したトルク伝達手段とで構成されている（例えば、特許文献１，２参照）。 For example, FIG. 8 and FIG. 9 show an example of the structure of a reverse input cutoff clutch incorporated in an automobile steering device. The reverse input cutoff clutch shown in FIG. 1 is an input shaft (cage) 1 as an input side member to which rotational torque is input, and an output side member that is arranged coaxially with the input shaft 1 and that outputs rotational torque. As an output shaft 2, an outer ring 3 as a stationary member that is coaxially disposed on the outer peripheral side of the input shaft 1 and the output shaft 2, and whose rotation is restricted, and a cam surface formed on the outer peripheral surface of the output shaft 2 2a and a pair of rollers 5 as an engaging member interposed in a wedge gap 4 formed between the inner peripheral surface 3a of the outer ring 3 so as to be engageable and disengageable and an elastic force in a direction to separate the pair of rollers 5 from each other A spring 6 as an elastic member for urging the shaft and a shaft 8 facing the output shaft 2 of the input shaft 1 are planted so that a pin 8 protrudes in the axial direction and faces the input shaft 1 of the output shaft 2. The pin 8 is inserted into the groove 7 formed along the radial direction on the shaft end surface. Is composed of a click transmission means (for example, see Patent Documents 1 and 2).

この逆入力遮断クラッチでは、出力軸２からの逆入力トルクが負荷されると、ばね６により相互に離間する方向に付勢された一対のローラ５が楔隙間４に噛み込んで出力軸２と外輪３との間で係合することにより、静止系の外輪３に対して出力軸２がロックした状態となり、その結果、入力軸１に逆入力トルクが伝達されない。 In this reverse input shut-off clutch, when a reverse input torque from the output shaft 2 is applied, a pair of rollers 5 urged in a direction away from each other by the spring 6 are engaged with the wedge gap 4 and By engaging with the outer ring 3, the output shaft 2 is locked with respect to the stationary outer ring 3, and as a result, reverse input torque is not transmitted to the input shaft 1.

一方、入力軸１からの入力トルクが負荷されると、入力軸１が一対のローラ５のうちの一方のローラ５をばね６による弾性力に抗して楔隙間４から離脱する方向に押圧するため、前述したロック状態が解除され、そのロック状態の解除後、入力軸１のピン８が出力軸２の凹溝７に係合することにより、そのピン８を介して入力トルクが出力軸２に直接的に伝達される。
特開２００３−２９４０６０号公報特開２００４−１９７２６号公報 On the other hand, when the input torque from the input shaft 1 is loaded, the input shaft 1 presses one of the pair of rollers 5 in a direction of separating from the wedge gap 4 against the elastic force of the spring 6. Therefore, the lock state described above is released, and after the lock state is released, the pin 8 of the input shaft 1 is engaged with the concave groove 7 of the output shaft 2 so that the input torque is output via the pin 8 to the output shaft 2. Is transmitted directly to.
JP 2003-294060 A Japanese Patent Laid-Open No. 2004-19726

ところで、前述の逆入力遮断クラッチでは、入力軸１に入力トルクが負荷されると、その前の逆入力トルクにより生じたローラ係合によるロック状態を解除した上で入力軸１からピン８を介して出力軸２へのトルク伝達が行われる。そのため、入力軸１に設けられたピン８とそのピン８が挿入された出力軸２の凹溝７との間には、ロック状態の解除を許容できるように回転方向の間隙ｍが設定されている。このことから、入力トルクの負荷が開始されてから、実際に出力軸２に入力トルクが伝達されるまでには、若干のタイムラグが生じる。 By the way, in the above-described reverse input cutoff clutch, when input torque is applied to the input shaft 1, the locked state due to the roller engagement caused by the previous reverse input torque is released and then the input shaft 1 is connected via the pin 8. Thus, torque transmission to the output shaft 2 is performed. Therefore, a clearance m in the rotational direction is set between the pin 8 provided on the input shaft 1 and the concave groove 7 of the output shaft 2 into which the pin 8 is inserted so as to allow the release of the locked state. Yes. For this reason, there is a slight time lag from when the load of the input torque is started until the input torque is actually transmitted to the output shaft 2.

入力トルクと逆入力トルクが出力軸２に対して同方向に作用する場合において、入力トルクによる入力軸１の回転数よりも逆入力トルクによる出力軸２の回転数の方が大きい場合には、入力トルクによるロック解除直後、入力軸１のピン８が出力軸２に接触するまでの間、出力軸２がフリー状態となる。 When the input torque and the reverse input torque act on the output shaft 2 in the same direction, when the rotational speed of the output shaft 2 due to the reverse input torque is larger than the rotational speed of the input shaft 1 due to the input torque, Immediately after releasing the lock by the input torque, until the pin 8 of the input shaft 1 contacts the output shaft 2, the output shaft 2 is in a free state.

ここで、入力軸１の回転数が出力軸２の回転数よりも大きければ、そのまま、入力軸１のピン８が出力軸２に接触して入力側から出力側へ入力トルクが伝達されるが、入力軸１の回転数よりも出力軸２の回転数の方が大きいと、入力軸１のピン８が出力軸２に接触する前に出力軸２が大きく回転して再度ロック状態となる。 Here, if the rotational speed of the input shaft 1 is larger than the rotational speed of the output shaft 2, the pin 8 of the input shaft 1 is brought into contact with the output shaft 2 and the input torque is transmitted from the input side to the output side. If the rotational speed of the output shaft 2 is greater than the rotational speed of the input shaft 1, the output shaft 2 rotates greatly before the pin 8 of the input shaft 1 contacts the output shaft 2, and the locked state is established again.

この場合、出力軸２の回転が一旦停止するので、再び、入力軸１からの入力トルクによりロック状態を解除することになる。以後、ロック解除状態と再ロック状態とが短時間で交互に繰り返されることになるため、クラッチ内部で連続的な異音や振動が発生するおそれがある。 In this case, since the rotation of the output shaft 2 is temporarily stopped, the locked state is released again by the input torque from the input shaft 1. Thereafter, the unlocked state and the relocked state are alternately repeated in a short time, and therefore, there is a possibility that continuous abnormal noise or vibration is generated inside the clutch.

この問題を解決するため、特許文献１に開示された逆入力遮断クラッチでは、静止系と出力軸の間に摩擦抵抗を設け、ローラの係合解除時に出力側に対してブレーキをかけることにより入力側に対して回転速度を低下させるようにしている。また、特許文献２に開示された逆入力遮断クラッチでは、入力軸と出力軸との間に摩擦抵抗を設け、ローラの係合解除時に入力側から出力側へ回転抵抗を付与するようにしている。 In order to solve this problem, in the reverse input cutoff clutch disclosed in Patent Document 1, a friction resistance is provided between the stationary system and the output shaft, and the input is performed by applying a brake to the output side when the roller is disengaged. The rotation speed is reduced with respect to the side. In the reverse input cutoff clutch disclosed in Patent Document 2, a frictional resistance is provided between the input shaft and the output shaft, and a rotational resistance is applied from the input side to the output side when the roller is disengaged. .

しかしながら、特許文献１に開示された逆入力遮断クラッチでは、静止系から出力側に常に回転抵抗が付与されているため、入力側からの駆動時に回転抵抗による損失が発生するという問題があった。また、特許文献２に開示された逆入力遮断クラッチでは、入力軸と出力軸の間に回転抵抗が付与されているため、この摩擦抵抗は入力軸と出力軸の相対回転を阻害しない程度の抵抗しか付与できないことから、出力軸への回転抵抗としては不十分であったり、回転抵抗が大きすぎると、クラッチとして十分に機能することが困難になるという問題があった。 However, the reverse input cutoff clutch disclosed in Patent Document 1 has a problem in that a loss due to the rotational resistance occurs during driving from the input side because the rotational resistance is always applied from the stationary system to the output side. Further, in the reverse input cutoff clutch disclosed in Patent Document 2, since rotational resistance is applied between the input shaft and the output shaft, this frictional resistance is a resistance that does not hinder the relative rotation of the input shaft and the output shaft. Therefore, if the rotational resistance to the output shaft is insufficient, or if the rotational resistance is too large, it is difficult to sufficiently function as a clutch.

そこで、本発明は前述の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、駆動時の回転損失やクラッチ機能の低下を発生させることなく、連続的な異音や振動の発生を確実に防止し得る逆入力遮断クラッチを提供することにある。 Therefore, the present invention has been proposed in view of the above-described problems, and the object of the present invention is to generate continuous abnormal noise and vibration without causing rotation loss during driving and lowering of the clutch function. It is an object of the present invention to provide a reverse input shut-off clutch that can surely prevent the above-described problem.

前述の目的を達成するための技術的手段として、本発明は、回転トルクが入力される入力側部材と、回転トルクが出力される出力側部材と、回転が拘束される静止側部材と、入力側部材と出力側部材との間に設けられ、入力側部材からの入力トルクを出力側部材に伝達するトルク伝達手段と、静止側部材と出力側部材との間に設けられ、出力側部材からの逆入力トルクに対して出力側部材と静止側部材とをロックして入力側部材へのトルク伝達を遮断するロック手段とを備え、入力トルクの負荷時に、ロック手段による出力側部材と静止側部材とのロック状態を解除した上で、トルク伝達手段で入力トルクを出力側部材に伝達する逆入力遮断クラッチにおいて、入力側部材を入力部材およびロック解除部材の別部材で構成し、入力部材とロック解除部材の間の回転伝達部に回転方向のガタを設けたことを特徴とする。 As technical means for achieving the aforementioned object, the present invention includes an input side member to which rotational torque is input, an output side member to which rotational torque is output, a stationary side member to which rotation is constrained, and an input Provided between the side member and the output side member, provided between the stationary side member and the output side member, and torque transmitting means for transmitting the input torque from the input side member to the output side member. Locking means for locking the output side member and the stationary side member against the reverse input torque of the motor and blocking torque transmission to the input side member, and when the input torque is applied, the output side member and the stationary side by the locking means In the reverse input shut-off clutch that transmits the input torque to the output side member by the torque transmission means after releasing the locked state with the member, the input side member is constituted by another member of the input member and the unlocking member, Lo Characterized in that a rotational direction of the backlash in the rotation transmitting portion between the release member.

ここで、入力トルクと逆入力トルクが出力側部材に対して同方向に作用する場合、入力側部材に入力トルクを負荷するモータ等の回転駆動源は、その回転開始直後における回転速度が出力側部材の回転速度よりも遅いことから、前述したように入力側部材と出力側部材間で、ロック解除状態と再ロック状態とが短時間で交互に繰り返され、クラッチ内部で連続的な異音や振動が発生しやすい。 Here, when the input torque and the reverse input torque act on the output side member in the same direction, the rotational drive source such as a motor that applies the input torque to the input side member has a rotational speed immediately after the start of rotation. Since it is slower than the rotation speed of the member, the unlocked state and the relocked state are alternately repeated in a short time between the input side member and the output side member as described above, Vibration is likely to occur.

そこで、本発明のように入力側部材を入力部材およびロック解除部材の別部材で構成し、入力部材とロック解除部材の間の回転伝達部に回転方向のガタを設けることで、回転駆動源により入力側部材から入力トルクが負荷されても、その回転駆動源の回転速度が上昇するまで回転方向のガタでもって入力部材からロック解除部材に入力トルクが伝達されなようにする。 Therefore, as in the present invention, the input side member is configured as a separate member of the input member and the unlocking member, and the rotation transmission portion between the input member and the unlocking member is provided with a backlash in the rotational direction, thereby Even when input torque is applied from the input side member, input torque is prevented from being transmitted from the input member to the lock release member with backlash in the rotational direction until the rotational speed of the rotational drive source increases.

そして、回転駆動源の回転速度が上昇した時点で、入力部材からロック解除部材に入力トルクを伝達してロック解除する。このロック解除後は、回転駆動源の回転速度が上昇した状態となり、出力側部材の回転速度に対して入力側部材の回転速度が遅くなることはないので、ロック解除状態（入力側部材と出力側部材が位相角をある程度保持した状態）を維持することができ、再ロック状態を回避することができるので、ロック解除状態と再ロック状態とを交互に繰り返すことがなくなる。 Then, when the rotational speed of the rotational drive source increases, the input torque is transmitted from the input member to the lock release member to release the lock. After unlocking, the rotational speed of the rotational drive source is increased, and the rotational speed of the input side member does not become slower than the rotational speed of the output side member. The state in which the side member maintains the phase angle to some extent) can be maintained, and the relock state can be avoided, so that the unlocked state and the relock state are not repeated alternately.

前述の構成における回転伝達部としては、入力部材とロック解除部材とを同軸上に配置し、そのロック解除部材の軸端面に設けられた凹孔に入力軸の軸端部を回転方向のガタを持って嵌合させた構造とすることが望ましい。また、回転方向のガタは、入力部材の外径面の一部にフラット面を形成すると共に、ロック解除部材の凹孔の内径面に径方向に向けて傾斜したテーパ面を形成し、入力部材のフラット面とロック解除部材のテーパ面との間隙とする構造が可能である。 As the rotation transmission portion in the above-described configuration, the input member and the unlocking member are arranged coaxially, and the shaft end portion of the input shaft is moved in the rotational direction in the concave hole provided in the shaft end surface of the unlocking member. It is desirable to have a structure that is held and fitted. Further, the backlash in the rotation direction forms a flat surface on a part of the outer diameter surface of the input member, and forms a tapered surface inclined in the radial direction on the inner diameter surface of the concave hole of the unlocking member. A structure in which the gap between the flat surface and the tapered surface of the unlocking member is used is possible.

前述の構成におけるロック手段としては、出力側部材と静止側部材との間に形成された楔隙間と、この楔隙間に対して係合可能な係合子とからなる構造が望ましい。なお、係合子としては、ローラあるいはスプラグのいずれかが使用可能である。 As the locking means in the above-described configuration, a structure including a wedge gap formed between the output side member and the stationary side member and an engagement element that can be engaged with the wedge gap is desirable. As the engagement element, either a roller or a sprag can be used.

本発明によれば、入力側部材からの入力トルクの負荷時、入力トルクと逆入力トルクが出力側部材に対して同方向に作用する場合において、入力トルクによる入力側部材の回転数よりも逆入力トルクによる出力側部材の回転数の方が大きい場合であっても、その入力側部材の回転速度が上昇するまで回転方向のガタでもって入力部材からロック解除部材に入力トルクが伝達されない。そして、ロック解除時には、入力側部材の回転速度が上昇した状態となることから、出力側部材の回転速度に対して入力側部材の回転速度が遅くなることはない。その結果、ロック解除状態と再ロック状態とを交互に繰り返すことがなくなるので、連続的な異音や振動の発生を確実に防止することができ、しかも、駆動時の回転損失やクラッチ機能の低下を発生させることもなく、高性能で信頼性の高い逆入力遮断クラッチを提供することができる。 According to the present invention, when an input torque is applied from the input side member, when the input torque and the reverse input torque act on the output side member in the same direction, the rotation speed of the input side member is reversed from the input torque. Even when the rotational speed of the output side member due to the input torque is larger, the input torque is not transmitted from the input member to the lock release member with backlash in the rotational direction until the rotational speed of the input side member increases. When the lock is released, the rotational speed of the input side member is increased, so that the rotational speed of the input side member does not become slower than the rotational speed of the output side member. As a result, the unlocked state and the re-locked state are not repeated alternately, so that it is possible to reliably prevent the occurrence of continuous abnormal noise and vibration, and to reduce rotational loss and clutch function during driving. Thus, it is possible to provide a high-performance and highly reliable reverse input cutoff clutch.

図１〜図３は、本発明の実施形態で逆入力遮断クラッチの全体構成を示す。同図に示す逆入力遮断クラッチは、回転トルクが入力される入力側部材９と、その入力側部材９と同軸上に配置され、回転トルクが出力される出力側部材としての出力軸１２と、入力側部材９および出力軸１２の外周側に同軸的に配置され、回転が拘束される静止側部材としての外輪１３と、入力側部材９と出力軸１２との間に設けられ、入力側部材９からの入力トルクを出力軸１２に伝達するトルク伝達手段２１と、外輪１３と出力軸１２との間に設けられ、出力軸１２からの逆入力トルクに対して出力軸１２と外輪１３とをロックして入力側部材９へのトルク伝達を遮断するロック手段２２とを備える。 1 to 3 show an overall configuration of a reverse input cutoff clutch according to an embodiment of the present invention. The reverse input shut-off clutch shown in the figure includes an input side member 9 to which rotational torque is input, an output shaft 12 that is arranged coaxially with the input side member 9 and that outputs rotational torque, The input side member 9 is provided between the input side member 9 and the output shaft 12 and the outer ring 13 as a stationary side member that is coaxially disposed on the outer peripheral side of the input side member 9 and the output shaft 12 and whose rotation is restricted. 9 is provided between the outer ring 13 and the output shaft 12, and the output shaft 12 and the outer ring 13 are connected to the reverse input torque from the output shaft 12. Locking means 22 for locking and blocking torque transmission to the input side member 9.

入力側部材９は、入力部材としての入力軸１０とロック解除部材としての保持器１１からなる別部材で構成されている。保持器１１の出力軸側の一端部を拡径させて軸方向に延びる柱部１１ａをその端部の円周方向複数箇所に設け、各柱部１１ａ間に係合子としての一対のローラ１５および弾性部材としてのばね１６を収容したポケット２３をその軸方向の一方側が開口した状態で形成され、このポケット２３により一対のローラ１５およびばね１６を円周方向に所定間隔で保持する。また、入力軸１０には、回転トルクが入力される。なお、この実施形態では、係合子としてローラ１５を例示しているが、このローラ以外の係合子して、スプラグを使用することも可能である。 The input side member 9 is comprised by another member which consists of the input shaft 10 as an input member, and the holder | retainer 11 as a lock release member. One end portion on the output shaft side of the retainer 11 is expanded in diameter and provided with column portions 11a extending in the axial direction at a plurality of locations in the circumferential direction of the end portion, and a pair of rollers 15 serving as engaging members between the column portions 11a and A pocket 23 accommodating the spring 16 as an elastic member is formed in a state where one side in the axial direction is opened, and the pair of rollers 15 and the spring 16 are held at a predetermined interval in the circumferential direction by the pocket 23. Further, rotational torque is input to the input shaft 10. In this embodiment, the roller 15 is illustrated as an engagement element, but it is also possible to use a sprag as an engagement element other than this roller.

出力軸１２の一方の端部は、保持器１１の柱部１１ａの内周側に挿入され、その柱部１１ａの内周面との対向する外周面に、ローラ１５が転動するカム面１２ａが形成され、そのカム面１２ａと外輪１３の軸方向中央部に位置する円筒状内周面１３ａとの間で楔隙間１４が形成されている。この楔隙間１４に係合・離脱可能に介在した一対のローラ１５および一対のローラ１５を相互に離間する方向に弾性力を付勢するばね１６とでロック手段２２を構成する。この出力軸１２の他方の端部には、入力軸１０からの入力トルクが出力され、あるいは、逆入力トルクが負荷される。 One end portion of the output shaft 12 is inserted on the inner peripheral side of the column portion 11a of the retainer 11, and the cam surface 12a on which the roller 15 rolls on the outer peripheral surface facing the inner peripheral surface of the column portion 11a. A wedge gap 14 is formed between the cam surface 12a and the cylindrical inner peripheral surface 13a located at the axial center of the outer ring 13. A pair of rollers 15 interposed in the wedge gap 14 so as to be able to be engaged and disengaged, and a spring 16 that urges an elastic force in a direction to separate the pair of rollers 15 from each other constitute a lock means 22. Input torque from the input shaft 10 is output to the other end of the output shaft 12, or reverse input torque is loaded.

保持器１１の出力軸１２と対向する軸端面で軸中心から偏心した位置にピン１８を軸方向に向けて突出するように植設すると共に、出力軸１２の保持器１１と対向する軸端面で軸中心を通る位置に前述のピン１８が挿入される凹溝１７を径方向に沿って形成している。この凹溝１７の幅寸法は、ピン１８の外径よりも若干大きく設定されており、回転方向に所定の間隙ｎが設けられている（図３参照）。 The pin 18 is implanted so as to protrude in the axial direction at a position eccentric from the shaft center at the shaft end surface facing the output shaft 12 of the cage 11, and at the shaft end surface facing the cage 11 of the output shaft 12. A concave groove 17 into which the pin 18 is inserted is formed along the radial direction at a position passing through the axial center. The width dimension of the concave groove 17 is set to be slightly larger than the outer diameter of the pin 18, and a predetermined gap n is provided in the rotation direction (see FIG. 3).

この逆入力遮断クラッチでは、入力軸１０に入力トルクが負荷されると、その前の逆入力トルクにより生じたローラ係合によるロック状態を解除した上で入力軸１０からピン１８を介して出力軸１２へトルクが伝達される。このことから、ピン１８と凹溝１７間の回転方向の間隙ｎは、ロック状態の解除を許容できるように寸法設定されている。この保持器１１のピン１８が出力軸１２の凹溝１７に挿入配置され、このピン１８により入力軸１０と出力軸１２とが連結可能となっていることにより、トルク伝達手段２１を構成している。 In this reverse input cutoff clutch, when input torque is applied to the input shaft 10, the locked state due to the roller engagement caused by the previous reverse input torque is released, and then the input shaft 10 is connected to the output shaft via the pin 18. Torque is transmitted to 12. Therefore, the clearance n in the rotational direction between the pin 18 and the concave groove 17 is dimensioned so as to allow the release of the locked state. The pin 18 of the retainer 11 is inserted and disposed in the concave groove 17 of the output shaft 12, and the input shaft 10 and the output shaft 12 can be connected by this pin 18, thereby constituting the torque transmission means 21. Yes.

外輪１３は、図示しないフレーム等の静止系に連結され、その軸方向両端部の内周面と、保持器１１および出力軸１２の外周面との間に転がり軸受２４，２５を介在させている。この転がり軸受２４，２５により、保持器１１および出力軸１２を外輪１３に対して回転自在に同軸的に軸支している。なお、図面では、転がり軸受２４，２５を例示しているが、これに代えて、例えば滑り軸受などの他の軸受を使用することも可能である。また、保持器１１の柱部１１ａのポケット２３が軸方向の一方側に開口していることから、ポケット２３内でのローラ１５の軸方向移動を規制するため、柱部１１ａと転がり軸受２５との間には、間座２６が配置されている。 The outer ring 13 is connected to a stationary system such as a frame (not shown), and rolling bearings 24 and 25 are interposed between inner peripheral surfaces of both axial end portions thereof and outer peripheral surfaces of the retainer 11 and the output shaft 12. . By these rolling bearings 24 and 25, the cage 11 and the output shaft 12 are rotatably and coaxially supported with respect to the outer ring 13. Although the rolling bearings 24 and 25 are illustrated in the drawings, other bearings such as a sliding bearing can be used instead. Further, since the pocket 23 of the pillar portion 11a of the cage 11 is opened on one side in the axial direction, the pillar portion 11a, the rolling bearing 25, and the like are used to restrict the axial movement of the roller 15 within the pocket 23. A spacer 26 is disposed between the two.

前述した構成からなる逆入力遮断クラッチにおいて、前述した入力側部材９を入力軸１０と保持器１１との二部材で構成している。この入力軸１０と保持器１１を同軸上に配置し、その保持器１１の軸端面に設けられた凹孔１１ｂに入力軸１０の軸端部を回転方向のガタを持って嵌合させて回転伝達部２０を構成している。 In the reverse input cutoff clutch having the above-described configuration, the input side member 9 described above is configured by two members of the input shaft 10 and the cage 11. The input shaft 10 and the cage 11 are arranged coaxially, and the shaft end portion of the input shaft 10 is fitted in a concave hole 11b provided in the shaft end surface of the cage 11 with a backlash in the rotational direction to rotate. The transmission part 20 is comprised.

この回転伝達部２０では、入力軸１０の外径面の一部、つまり、１８０°反対位置の二箇所にフラット面１０ｃを形成すると共に、保持器１１の凹孔１１ｂの内径面に径方向内側に向けて傾斜したテーパ面１１ｃ₁，１１ｃ₂を形成する。隣接する二つのテーパ面１１ｃ₁，１１ｃ₂を一組として１８０°反対方向で入力軸１０のフラット面１０ｃと対向する位置に形成する。この入力軸１０のフラット面１０ｃと保持器１１のテーパ面１１ｃ₁，１１ｃ₂との間隙ｐを回転方向のガタθ（例えばθ＝２０°）としている（図２参照）。 In the rotation transmitting portion 20, a flat surface 10c is formed at a part of the outer diameter surface of the input shaft 10, that is, at two positions opposite to each other by 180 °, and at the radially inner side of the inner diameter surface of the concave hole 11b of the cage 11. Tapered surfaces 11c ₁ and 11c ₂ inclined toward the surface are formed. Two adjacent tapered surfaces 11c ₁ and 11c ₂ are formed as a pair at a position facing the flat surface 10c of the input shaft 10 in the opposite direction by 180 °. A gap p between the flat surface 10c of the input shaft 10 and the tapered surfaces 11c ₁ and 11c ₂ of the retainer 11 is set as a backlash θ (for example, θ = 20 °) in the rotational direction (see FIG. 2).

図４に示す中立状態で、例えば出力軸１２に時計方向の逆入力トルクが入力されると（入力軸１０には入力トルクは作用していない）、一対のローラ１５のうち、反時計方向（回転方向後方）に位置するローラ１５が、そのローラ１５同士に離反力を付勢するばね１６により、出力軸１２と外輪１３との間の楔隙間１４に噛み込んで係合し、出力軸１２が外輪１３に対して時計方向にロックされる。反対に、出力軸１２に反時計方向の逆入力トルクが入力されると、時計方向（回転方向後方）に位置するローラ１５が楔隙間１４に噛み込んで係合し、出力軸１２が外輪１３に対して反時計方向にロックされる。従って、出力軸１２からの逆入力トルクは、正逆両回転方向にロックされ、入力軸１０にはトルクが伝達されない。 In the neutral state shown in FIG. 4, for example, when a counterclockwise reverse input torque is input to the output shaft 12 (no input torque acts on the input shaft 10), the counterclockwise direction ( A roller 15 positioned rearward in the rotation direction is engaged with and engaged with a wedge gap 14 between the output shaft 12 and the outer ring 13 by a spring 16 that biases a separation force between the rollers 15. Is locked clockwise with respect to the outer ring 13. On the other hand, when counterclockwise reverse input torque is input to the output shaft 12, the roller 15 positioned in the clockwise direction (backward in the rotational direction) is engaged with the wedge gap 14, and the output shaft 12 is engaged with the outer ring 13. Is locked counterclockwise. Therefore, the reverse input torque from the output shaft 12 is locked in both forward and reverse rotation directions, and no torque is transmitted to the input shaft 10.

図５は、入力軸１０に作用する入力トルクで入力軸１０が反時計方向に回転を始めた状態を示す。入力軸１０の時計方向（回転方向後方）に位置するポケット２３の柱部１１ａの側面がその時計方向（回転方向後方）に位置するローラ１５と係合して、これをばね１６の弾性力に抗して反時計方向（回転方向前方）に押圧する。これにより、時計方向（回転方向後方）に位置するローラ１５が出力軸１２と外輪１３間の楔隙間１４から離脱して空転可能となり、出力軸１２のロック状態が解除される（なお、反時計方向のローラ１５は、出力軸１２と外輪１３の間の楔隙間１４に噛み込まずに係合しない）。従って、出力軸１２は反時計方向に回転可能となる。 FIG. 5 shows a state in which the input shaft 10 starts to rotate counterclockwise by the input torque acting on the input shaft 10. The side surface of the column portion 11a of the pocket 23 positioned in the clockwise direction (backward in the rotational direction) of the input shaft 10 is engaged with the roller 15 positioned in the clockwise direction (backward in the rotational direction), and this is used as the elastic force of the spring 16. Push it counterclockwise (forward in the rotational direction). As a result, the roller 15 positioned in the clockwise direction (rear in the rotational direction) is separated from the wedge gap 14 between the output shaft 12 and the outer ring 13 and can idle, and the locked state of the output shaft 12 is released (the counterclockwise state) The direction roller 15 does not engage with the wedge gap 14 between the output shaft 12 and the outer ring 13 and does not engage therewith). Accordingly, the output shaft 12 can rotate counterclockwise.

入力軸１０がさらに反時計方向に回転すると、図６に示すように入力軸１０のピン１８が出力軸１２の凹溝１７と回転方向で係合する。これにより、入力軸１０からの反時計方向の入力トルクが出力軸１２にピン１８を介して直接的に伝達され、出力軸１２が反時計方向に回転する。入力軸１０に時計方向の入力トルクが入力された場合は、上記とは逆の動作で出力軸１２が時計方向に回転する。従って、入力軸１０からの正逆回転方向の入力トルクは、トルク伝達手段２１としてのピン１８を介して出力軸１２に伝達され、出力軸１２が正逆両回転方向に回転する。なお、入力軸１０からの入力トルクがなくなると、ばね１６の弾性力によって図４に示す中立位置に復帰する。 When the input shaft 10 further rotates counterclockwise, the pin 18 of the input shaft 10 engages with the concave groove 17 of the output shaft 12 in the rotational direction as shown in FIG. Thereby, the counterclockwise input torque from the input shaft 10 is directly transmitted to the output shaft 12 via the pin 18, and the output shaft 12 rotates counterclockwise. When the clockwise input torque is input to the input shaft 10, the output shaft 12 rotates in the clockwise direction by the reverse operation to the above. Therefore, the input torque in the forward / reverse rotation direction from the input shaft 10 is transmitted to the output shaft 12 via the pin 18 as the torque transmission means 21, and the output shaft 12 rotates in both forward and reverse rotation directions. When the input torque from the input shaft 10 is lost, the spring 16 returns to the neutral position shown in FIG.

ここで、入力トルクと逆入力トルクが出力軸１２に対して同方向に作用する場合、入力軸１０に入力トルクを負荷するモータ等の回転駆動源は、その回転開始直後における回転速度が出力軸１２の回転速度よりも遅いことから、前述したように入力側部材９と出力軸１２間で、ロック解除状態と再ロック状態とが短時間で交互に繰り返され、クラッチ内部で連続的な異音や振動が発生しやすい。 Here, when the input torque and the reverse input torque act on the output shaft 12 in the same direction, the rotational drive source such as a motor that loads the input torque on the input shaft 10 has a rotational speed immediately after the start of the rotation. As described above, the unlocked state and the relocked state are alternately repeated in a short time between the input side member 9 and the output shaft 12 as described above. And vibration is likely to occur.

そこで、この実施形態の逆入力遮断クラッチでは、入力側部材９を入力軸１０および保持器１１の別部材で構成し、入力軸１０と保持器１１の間の回転伝達部２０に回転方向のガタθを設けることで、回転駆動源により入力軸１０から入力トルクが負荷されても、その回転駆動源の回転速度が上昇するまで回転方向のガタθでもって入力軸１０から保持器１１に入力トルクが伝達されない。つまり、入力軸１０のフラット面１０ｃが保持器１１の凹孔１１ｂのテーパ面１１ｃ₁，１１ｃ₂に当接するまでが回転方向のガタθとなり、この間では入力軸１０からの入力トルクが保持器１１に伝達されない。 Therefore, in the reverse input cutoff clutch of this embodiment, the input side member 9 is configured as a separate member of the input shaft 10 and the retainer 11, and the rotation transmission portion 20 between the input shaft 10 and the retainer 11 has a backlash in the rotational direction. By providing θ, even if an input torque is applied from the input shaft 10 by the rotational drive source, the input torque from the input shaft 10 to the cage 11 with a backlash θ in the rotational direction until the rotational speed of the rotational drive source increases. Is not transmitted. That is, until the flat surface 10c of the input shaft 10 comes into contact with the tapered surfaces 11c ₁ and 11c ₂ of the concave hole 11b of the retainer 11, there is a backlash θ in the rotational direction. During this time, the input torque from the input shaft 10 is retained by the retainer 11. Not transmitted to.

そして、回転駆動源の回転速度が上昇した時点で、図７に示すように入力軸１０のフラット面１０ｃが保持器１１のテーパ面１１ｃ₁に当接した時点で、入力軸１０から保持器１１に入力トルクが伝達開始され、前述したようにロック状態を解除する。なお、入力軸１０が反時計方向に回転する場合には、図示のように入力軸１０のフラット面１０ｃが保持器１１のテーパ面１１ｃ₁に当接し、時計方向に回転する場合には、入力軸１０のフラット面１０ｃが保持器１１のテーパ面１１ｃ₂に当接することになる。 Then, when the rotational speed of the rotary drive source is increased, when the flat surface 10c of the input shaft 10 as shown in FIG. 7 is in contact with the tapered surface 11c ₁ of the retainer 11, the retainer from the input shaft 10 11 The input torque is started to be transmitted, and the locked state is released as described above. Incidentally, when the input shaft 10 rotates in the counterclockwise direction, when the flat surface 10c of the input shaft 10, as shown in contact with the tapered surface 11c ₁ of the cage 11 to rotate in the clockwise direction, input The flat surface 10 c of the shaft 10 comes into contact with the tapered surface 11 c ₂ of the cage 11.

このロック解除後は、回転駆動源の回転速度が上昇した状態となり、出力軸１２の回転速度に対して入力軸１０の回転速度が遅くなることはないので、ロック解除状態（入力軸１０と出力軸１２が位相角をある程度保持した状態）を維持することができ、これにより、再ロック状態を回避することができるので、ロック解除状態と再ロック状態とを交互に繰り返すことがなくなる。 After unlocking, the rotational speed of the rotational drive source is increased, and the rotational speed of the input shaft 10 does not become slower than the rotational speed of the output shaft 12. Therefore, the unlocked state (input shaft 10 and output The state in which the shaft 12 retains the phase angle to some extent) can be maintained, whereby the relock state can be avoided, so that the unlocked state and the relocked state are not repeated alternately.

本発明に係る逆入力遮断クラッチの実施形態で、図３のＢ−Ｂ線に沿う断面図である。FIG. 5 is a cross-sectional view taken along line BB in FIG. 3 in the embodiment of the reverse input cutoff clutch according to the present invention. 図１のＡ−Ａ線に沿う断面図である。It is sectional drawing which follows the AA line of FIG. 図１のＣ−Ｃ線に沿う断面図である。It is sectional drawing which follows the CC line of FIG. 図３の逆入力遮断クラッチの動作を説明するためのもので、出力軸のロック状態を示す断面図である。FIG. 4 is a cross-sectional view illustrating an operation of the reverse input cutoff clutch of FIG. 3 and showing a locked state of the output shaft. 図３の逆入力遮断クラッチの動作を説明するためのもので、出力軸のロック解除状態を示す断面図である。FIG. 4 is a cross-sectional view illustrating an operation of the reverse input cutoff clutch of FIG. 3 and showing an unlocked state of the output shaft. 図３の逆入力遮断クラッチの動作を説明するためのもので、出力軸の回転状態を示す断面図である。FIG. 4 is a sectional view for explaining the operation of the reverse input cutoff clutch of FIG. 3 and showing the rotation state of the output shaft. 図２の逆入力遮断クラッチの動作を説明するためのもので、入力軸の回転状態を示す断面図である。FIG. 3 is a cross-sectional view for explaining the operation of the reverse input cutoff clutch of FIG. 2 and showing the rotation state of the input shaft. 逆入力遮断クラッチの従来例で、図９のＥ−Ｅ線に沿う断面図である。FIG. 10 is a cross-sectional view taken along line E-E in FIG. 9, showing a conventional example of a reverse input cutoff clutch. 図８のＤ−Ｄ線に沿う断面図である。It is sectional drawing which follows the DD line | wire of FIG.

Explanation of symbols

９入力側部材
１０入力部材（入力軸）
１０ｃフラット面
１１ロック解除部材（保持器）
１１ｂ凹孔
１１ｃ₁，１１ｃ₂ テーパ面
１２出力側部材（出力軸）
１３静止側部材（外輪）
１４楔隙間
１５係合子（ローラ）
２０回転伝達部
２１トルク伝達手段
２２ロック手段

9 Input side member 10 Input member (input shaft)
10c flat surface 11 unlocking member (retainer)
11b recessed hole 11c _1, 11c ₂ tapered surface 12 output member (output shaft)
13 Static side member (outer ring)
14 Wedge clearance 15 Engagement element (roller)
20 Rotation transmission part 21 Torque transmission means 22 Locking means

Claims

An input side member provided between an input side member to which rotational torque is input, an output side member from which rotational torque is output, a stationary side member to which rotation is restricted, and the input side member and the output side member. Torque transmission means for transmitting the input torque from the output side member to the output side member, and the output side member and the stationary side member with respect to the reverse input torque from the output side member. And locking means for blocking torque transmission to the input side member, and when the input torque is applied, the locked state between the output side member and the stationary side member by the locking means is released, and then the torque transmission is performed. In the reverse input cutoff clutch that transmits the input torque to the output side member by means,
A reverse input shut-off clutch, wherein the input side member is constituted by a separate member of an input member and an unlocking member, and a rotation transmission portion is provided in a rotation transmitting portion between the input member and the unlocking member.

In the input side member, the input member and the unlocking member are arranged coaxially, and the shaft end of the input shaft is fitted in a concave hole provided in the shaft end surface of the unlocking member with a backlash in the rotational direction. The reverse input cutoff clutch according to claim 1 combined.

A flat surface is formed on a part of the outer diameter surface of the input member, and a tapered surface inclined in the radial direction is formed on the inner diameter surface of the concave hole of the unlocking member, and the flat surface of the input member and the lock The reverse input cutoff clutch according to claim 2, wherein a gap between the release member and the tapered surface is a backlash in a rotational direction.

The said lock | rock means consists of the wedge clearance gap formed between the output side member and the stationary side member, and the engagement element which can be engaged with this wedge clearance gap. Reverse input cutoff clutch.

The reverse input cutoff clutch according to claim 4, wherein the engagement element is either a roller or a sprag.