JP2023018310A

JP2023018310A - Reverse input cutoff clutch and clutch unit comprising the same

Info

Publication number: JP2023018310A
Application number: JP2021122342A
Authority: JP
Inventors: 卓俊中村; Takatoshi Nakamura; 康雅日比; Yasumasa Hibi; 恭兵笹沼; Kyohei Sasanuma
Original assignee: NTN Corp; NTN Toyo Bearing Co Ltd
Current assignee: NTN Corp
Priority date: 2021-07-27
Filing date: 2021-07-27
Publication date: 2023-02-08

Abstract

To appropriately exhibit a reverse input cutoff function.SOLUTION: In a second clutch part 20 comprising a reverse input cutoff clutch that cuts off reverse input torque input to an output shaft 22 by locking the rotation of the output shaft 22 with respect to a stationary member, on either one (for example, an end surface 22e) of an end surface 13f of an inner ring 13 and the end surface 22e of the output shaft 22 as input-side members 21 that face each other in an axial direction, a protrusion part 5 is provided so as to protrude to the other side and contact the other one.SELECTED DRAWING: Figure 1

Description

本発明は、逆入力遮断クラッチ及びこれを備えるクラッチユニットに関する。 The present invention relates to a reverse input cutoff clutch and a clutch unit having the same.

逆入力遮断クラッチは、入力側部材に入力されるトルクを出力側部材としての出力軸に伝達する一方、出力軸に入力される逆入力トルクを遮断する（入力側部材に伝達しない）機能を有する。この逆入力遮断クラッチには、逆入力トルクに対して出力軸をロックする、「ロック型」と称される方式のものがある。例えば、特許第５２０７７７９号公報（特許文献１）には、自動車の座席シートの座面高さを調整するシートリフタに組み込んで使用されるクラッチユニットであって、ロック型の逆入力遮断クラッチが組み込まれたクラッチユニットが記載されている。 The reverse input cut-off clutch has the function of transmitting torque input to the input side member to the output shaft as the output side member, while blocking reverse input torque input to the output shaft (not transmitting it to the input side member). . This reverse input cut-off clutch has a type called "lock type" that locks the output shaft against the reverse input torque. For example, Japanese Patent No. 5207779 (Patent Document 1) discloses a clutch unit incorporated in a seat lifter for adjusting the seat height of an automobile seat, in which a lock type reverse input cutoff clutch is incorporated. A clutch unit is described.

図７（ａ）に、従来のロック型の逆入力遮断クラッチを抜き出して示し、図７（ｂ）に、図７（ａ）のＰ－Ｐ線矢視断面図を示す。図７（ａ）（ｂ）に示す逆入力遮断クラッチ１００は、レバー操作に伴ってトルクが入力される入力側部材１０１と、入力側部材１０１に入力されたトルクを出力する出力側部材としての出力軸１０２と、出力軸１０２の外周面に設けられた複数のカム面１０４との間に楔すきま（周方向両側に向けてすきま幅が徐々に縮小した楔すきま）１０６を形成する円筒状内周面１０５を有する静止部材としての外輪１０３と、各楔すきま１０６内に配された係合子（トルク伝達部材）としての円筒ころ１０７とを備え、入力側部材１０１、出力軸１０２及び外輪１０３は同軸に配置されている。円筒ころ１０７は、各楔すきま１０６内に対をなすかたちで配されており、一対の円筒ころ１０７（１０７Ａ，１０７Ｂ）間には、ばね等の弾性部材１０８が周方向に圧縮された状態で介在している。入力側部材１０１には軸方向に延びる複数の柱部１０１ａが周方向等間隔で形成されており、各柱部１０１ａは、周方向で隣り合う楔すきま１０６の間に配されている。そのため、入力側部材１０１は、一対の円筒ころ１０７及び弾性部材１０８の組を周方向等間隔で保持する保持器としても機能する。 FIG. 7(a) shows a conventional lock-type reverse input interrupting clutch, and FIG. 7(b) shows a cross-sectional view taken along line PP of FIG. 7(a). The reverse input cut-off clutch 100 shown in FIGS. 7(a) and 7(b) includes an input side member 101 to which torque is input in accordance with lever operation, and an output side member which outputs the torque input to the input side member 101. A cylindrical interior forming a wedge clearance (a wedge clearance in which the width of the clearance gradually decreases toward both sides in the circumferential direction) between the output shaft 102 and a plurality of cam surfaces 104 provided on the outer peripheral surface of the output shaft 102. It comprises an outer ring 103 as a stationary member having a peripheral surface 105, and cylindrical rollers 107 as engaging elements (torque transmission members) arranged in the wedge clearances 106. The input side member 101, the output shaft 102 and the outer ring 103 are arranged coaxially. The cylindrical rollers 107 are arranged in pairs in the wedge gaps 106, and an elastic member 108 such as a spring is compressed in the circumferential direction between the pair of cylindrical rollers 107 (107A, 107B). is intervening. A plurality of columnar portions 101a extending in the axial direction are formed on the input side member 101 at regular intervals in the circumferential direction, and each columnar portion 101a is arranged between wedge gaps 106 adjacent to each other in the circumferential direction. Therefore, the input-side member 101 also functions as a retainer that retains a pair of cylindrical rollers 107 and elastic members 108 at regular intervals in the circumferential direction.

上記の逆入力遮断クラッチ１００において、入力側部材１０１へのトルク入力がない状態［図７（ｂ）参照］では、各楔すきま１０６内に配された一対の円筒ころ１０７Ａ，１０７Ｂが弾性部材１０８の弾性復元力によって楔すきま１０６の狭小部（周方向端部）に押し込まれている。そのため、図７（ｂ）に示すように、出力軸１０２に逆入力トルクＴ’が入力されても、出力軸１０２の回転方向後側の円筒ころ１０７Ｂが出力軸１０２及び外輪１０３と周方向で係合するため、出力軸１０２がロックされる。このロック状態では、逆入力トルクＴ’が入力側部材１０１に伝達されない。 In the reverse input cut-off clutch 100 described above, when there is no torque input to the input side member 101 [see FIG. is pushed into the narrow portion (circumferential end portion) of the wedge clearance 106 by the elastic restoring force of the wedge gap 106 . Therefore, as shown in FIG. 7B, even if a reverse input torque T′ is input to the output shaft 102, the cylindrical roller 107B on the rear side in the rotation direction of the output shaft 102 will not rotate with the output shaft 102 and the outer ring 103 in the circumferential direction. Due to engagement, the output shaft 102 is locked. In this locked state, the reverse input torque T' is not transmitted to the input side member 101. As shown in FIG.

その一方、入力側部材１０１にトルクＴが入力されると、入力側部材１０１の各柱部１０１ａが、各楔すきま１０６に配された一対の円筒ころ１０７のうちの一方の円筒ころ１０７Ｂを弾性部材１０８の弾性復元力に抗して他方の円筒ころ１０７Ａ側に押圧するため、円筒ころ１０７Ｂと出力軸１０２及び外輪１０３との係合状態（上記のロック状態）が解除される。このロック解除状態では、入力側部材１０１に入力されるトルクＴが円筒ころ１０７Ａを介して出力軸１０２に伝達可能となる。なお、入力側部材１０１へのトルク入力がなくなると、一対の円筒ころ１０７間に介在する弾性部材１０８の弾性復元力が円筒ころ１０７Ｂを介して入力側部材１０１の柱部１０１ａに作用する。これにより、入力側部材１０１が中立位置（柱部１０１ａが円筒ころ１０７Ｂを押圧しない位置）に復帰し、ロック解除状態にあった逆入力遮断クラッチ１００がロック状態に移行する。 On the other hand, when a torque T is input to the input side member 101, each column portion 101a of the input side member 101 elastically pushes one cylindrical roller 107B out of the pair of cylindrical rollers 107 arranged in each wedge gap 106. Since the other cylindrical roller 107A is pressed against the elastic restoring force of the member 108, the engagement state (the locked state) between the cylindrical roller 107B and the output shaft 102 and the outer ring 103 is released. In this unlocked state, the torque T input to the input side member 101 can be transmitted to the output shaft 102 via the cylindrical rollers 107A. When the torque input to the input side member 101 ceases, the elastic restoring force of the elastic member 108 interposed between the pair of cylindrical rollers 107 acts on the column portion 101a of the input side member 101 via the cylindrical rollers 107B. As a result, the input side member 101 returns to the neutral position (the position where the column portion 101a does not press the cylindrical roller 107B), and the reverse input cutoff clutch 100, which has been in the unlocked state, shifts to the locked state.

特許第５２０７７７９号公報Japanese Patent No. 5207779

上記の逆入力遮断クラッチ１００においては、弾性部材１０８の弾性復元力（によるトルク）よりも大きな内部抵抗が生じる場合がある。この場合、弾性部材１０８の周方向両側に配された一対の円筒ころ１０７Ａ，１０７Ｂを楔すきま１０６の適正位置まで押し込む（入力側部材１０１を中立位置に復帰させる）ことができず、いわゆる甘噛み状態となる。この状態で出力軸１０２に逆入力トルクＴ’が入力されると、出力軸１０２の回転を適切に規制すること、つまり逆入力遮断機能を適切に発揮することができず、逆入力遮断クラッチ１００の信頼性を損ねる結果となる。 In the reverse input interrupting clutch 100 described above, an internal resistance greater than the elastic restoring force of the elastic member 108 (torque due to it) may occur. In this case, the pair of cylindrical rollers 107A and 107B arranged on both sides in the circumferential direction of the elastic member 108 cannot be pushed into the wedge clearance 106 to the appropriate position (the input side member 101 can be returned to the neutral position), which is a so-called soft engagement. state. If a reverse input torque T' is input to the output shaft 102 in this state, the rotation of the output shaft 102 cannot be properly regulated, that is, the reverse input blocking function cannot be properly exhibited, and the reverse input blocking clutch 100 As a result, the reliability of the

そこで、本発明は、ロック型の逆入力遮断クラッチにおいて、入力側部材に入力されたトルクが除荷された時に入力側部材を中立位置に確実に復帰させることを可能とし、もって、逆入力遮断機能を適切に発揮することができて信頼性に富む逆入力遮断クラッチを実現することを目的とする。 SUMMARY OF THE INVENTION Accordingly, the present invention provides a lock-type reverse input cut-off clutch capable of reliably returning an input-side member to a neutral position when a torque input to the input-side member is released, thereby blocking the reverse input. To provide a highly reliable reverse input cut-off clutch capable of properly exhibiting its functions.

本発明者らが検証を重ねた結果、前述した大きな内部抵抗は、出力軸１０２とその回転伝達対象との間でトルクが伝達される際に出力軸１０２が軸方向に対して傾き、その結果、入力側部材１０１と出力軸１０２が広範に亘って接触した状態で入力側部材１０１と出力軸１０２が相対回転する（両者１０１，１０２間で大きな摺動抵抗が生じる）ことを原因の一つとして発生することが確認された。そこで、入力側部材１０１及び出力軸１０２の機能性を損なうことなく、両者１０１，１０２の接触面積を低減することができれば、逆入力遮断クラッチ１００の動作時に生じる内部抵抗を減じ、入力側部材に入力されたトルクが除荷された時に入力側部材を中立位置に適切に復帰させることができると考えられる。 As a result of repeated verification by the present inventors, the large internal resistance described above causes the output shaft 102 to tilt with respect to the axial direction when torque is transmitted between the output shaft 102 and its rotation transmission target, resulting in One of the causes is that the input-side member 101 and the output shaft 102 rotate relative to each other in a state where the input-side member 101 and the output shaft 102 are in contact with each other over a wide area (a large sliding resistance is generated between the two members 101 and 102). was confirmed to occur as Therefore, if the contact area between the input side member 101 and the output shaft 102 can be reduced without impairing the functionality of the input side member 101 and the output shaft 102, the internal resistance generated during the operation of the reverse input cutoff clutch 100 can be reduced, It is considered that the input side member can be appropriately returned to the neutral position when the input torque is released.

上記の知見に基づいて創案された本発明は、
トルクが入力される入力側部材と、上記トルクを出力可能な出力軸と、回転が規制された静止部材とを備え、
静止部材の内周面との間に楔すきまを形成する複数のカム面が出力軸の外周面に周方向に間隔を空けて設けられ、各楔すきま内に、一対の係合子と、周方向に圧縮された状態で一対の係合子間に介在する弾性部材とが配設され、
弾性部材の弾性復元力を受けた一対の係合子が出力軸及び静止部材と周方向で係合することにより、出力軸に入力される逆入力トルクの入力側部材への伝達が遮断されるロック状態となり、入力側部材へのトルク入力に伴って、周方向で隣り合う楔すきま間に配された入力側部材の柱部が一対の係合子のうちの一方を上記弾性復元力に抗して他方の係合子側に押圧することにより、上記ロック状態が解除される逆入力遮断クラッチにおいて、
軸方向で互いに対向する前記入力側部材の端面及び前記出力軸の端面の何れか一方に、他方側に突出して他方と接触する凸部を設けたことを特徴とする。 The present invention invented based on the above knowledge,
An input side member to which torque is input, an output shaft capable of outputting the torque, and a stationary member whose rotation is restricted,
A plurality of cam surfaces forming wedge clearances with the inner peripheral surface of the stationary member are provided on the outer peripheral surface of the output shaft at intervals in the circumferential direction. and an elastic member interposed between the pair of engaging elements in a compressed state,
A lock that interrupts the transmission of reverse input torque input to the output shaft to the input side member by engaging a pair of engaging elements that receive the elastic restoring force of the elastic member with the output shaft and the stationary member in the circumferential direction. In response to the torque input to the input side member, the column portion of the input side member disposed between the wedge gaps adjacent in the circumferential direction pushes one of the pair of engagers against the elastic restoring force. In the reverse input interrupting clutch that is released from the locked state by pressing the other engaging element,
One of the end face of the input side member and the end face of the output shaft, which face each other in the axial direction, is provided with a convex portion that protrudes toward the other side and comes into contact with the other.

係る構成を有する逆入力遮断クラッチによれば、入力側部材と出力軸とが軸方向で接触するときには、上記一方の端面に設けた凸部を他方の端面に対して優先的に接触させることができる。そのため、凸部を上記一方の端面に比べて十分に小さく形成しておけば、入力側部材と出力軸の接触面積を小さくして両者間で生じる摺動抵抗、つまり当該クラッチの動作時に生じる内部抵抗を低減することができる。これにより、入力側部材に入力されたトルクが除荷された後には、入力側部材を中立位置に適切に復帰させること、つまり当該クラッチをロック解除状態からロック状態に適切に移行させることが可能となる。 According to the reverse input cut-off clutch having such a configuration, when the input side member and the output shaft come into contact with each other in the axial direction, the convex portion provided on the one end surface can preferentially come into contact with the other end surface. can. Therefore, if the convex portion is formed sufficiently smaller than the one end face, the contact area between the input side member and the output shaft can be reduced to reduce the sliding resistance generated between the two, that is, the internal friction generated during the operation of the clutch. resistance can be reduced. As a result, after the torque input to the input side member is released, the input side member can be appropriately returned to the neutral position, that is, the clutch can be appropriately shifted from the unlocked state to the locked state. becomes.

上記の凸部は、周方向の複数箇所に配置するのが好ましく、周方向等間隔で配置するのが一層好ましい。 It is preferable that the convex portions are arranged at a plurality of positions in the circumferential direction, and more preferably arranged at equal intervals in the circumferential direction.

レバー操作により入力されるトルクの伝達及び遮断を制御する第１クラッチ部と、本発明に係る逆入力遮断クラッチからなる第２クラッチ部とを備え、第１クラッチ部の出力（レバー操作により入力されるトルク）が逆入力遮断クラッチの入力側部材に入力されるクラッチユニットは、本発明に係る逆入力遮断クラッチが逆入力遮断機能を適切に発揮し得る信頼性に富むものであるから、逆入力トルクが頻繁に入力される用途、例えば自動車の座席シートの座面高さを調整するシートリフタに好ましく採用することができる。 A first clutch portion for controlling transmission and interruption of torque input by lever operation, and a second clutch portion comprising a reverse input interrupting clutch according to the present invention, the output of the first clutch portion (input by lever operation) is provided. Since the clutch unit in which the reverse input interrupting clutch according to the present invention can appropriately perform the reverse input interrupting function, the clutch unit in which the reverse input interrupting clutch receives the input side member of the reverse input interrupting torque is highly reliable. It can be preferably used for applications where frequent input is required, such as seat lifters for adjusting the seat height of automobile seats.

以上から、本発明によれば、ロック型の逆入力遮断クラッチにおいて、入力側部材に入力されたトルクが除荷されると、入力側部材を中立位置に適切に復帰させることが可能となる。これにより、逆入力遮断機能を適切に発揮することができて信頼性に富む逆入力遮断クラッチを実現することができる。 As described above, according to the present invention, in the lock type reverse input interrupting clutch, when the torque input to the input side member is released, the input side member can be appropriately returned to the neutral position. As a result, it is possible to realize a highly reliable reverse input cut-off clutch capable of appropriately exhibiting the reverse input cut-off function.

本発明の一実施形態に係る逆入力遮断クラッチを含むクラッチユニットの概略縦断面図である。1 is a schematic longitudinal sectional view of a clutch unit including a reverse input cutoff clutch according to one embodiment of the present invention; FIG. 図１のＡ－Ａ線断面図である。FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1; 図１のＢ－Ｂ線断面図である。FIG. 2 is a cross-sectional view taken along line BB of FIG. 1; 図１のＣ－Ｃ線矢視断面図である。FIG. 2 is a cross-sectional view taken along line CC of FIG. 1; （ａ）図は、図１に示すクラッチユニットに組み込まれた出力軸の概略斜視図、（ｂ）図は、同出力軸の概略正面図である。(a) is a schematic perspective view of an output shaft incorporated in the clutch unit shown in FIG. 1, and (b) is a schematic front view of the output shaft. 本発明の他の実施形態に係る逆入力遮断クラッチを構成する入力側部材の概略斜視図である。FIG. 8 is a schematic perspective view of an input-side member that constitutes a reverse input cut-off clutch according to another embodiment of the present invention; （ａ）図は、従来の逆入力遮断クラッチの概略縦断面図、（ｂ）図は（ａ）図のＰ－Ｐ線矢視断面図である。(a) is a schematic vertical cross-sectional view of a conventional reverse input cutoff clutch, and (b) is a cross-sectional view taken along line PP of FIG. (a).

以下、本発明の実施の形態を図面（図１～図６）に基づいて説明する。 BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings (FIGS. 1 to 6).

図１に、本発明の一実施形態に係る逆入力遮断クラッチを含むクラッチユニット１の概略縦断面図を示し、図２～図４のそれぞれに、図１のＡ－Ａ線断面図、Ｂ－Ｂ線断面図及びＣ－Ｃ線矢視断面図を示す。図１に示すクラッチユニット１は、例えば、自動車用座席シートの座面高さを調整するシートリフタに組み込んで使用されるものであって、第１クラッチ部１０と、ロック型の逆入力遮断クラッチからなる第２クラッチ部２０とを備える。以下、まずは第１クラッチ部１０の構造を説明してから、第２クラッチ部２０の構造を説明する。なお、以下の説明において方向性を示すために使用する「軸方向」、「径方向」及び「周方向」とは、それぞれ、第２クラッチ部２０（クラッチユニット１）の出力側部材を構成する出力軸２２の軸心Ｘと平行な方向、軸心Ｘを中心とする円（出力軸２２）の径方向、及び軸心Ｘを中心とする円の周方向である。 FIG. 1 shows a schematic longitudinal sectional view of a clutch unit 1 including a reverse input interrupting clutch according to one embodiment of the present invention, and FIGS. A cross-sectional view along line B and a cross-sectional view along line CC are shown. The clutch unit 1 shown in FIG. 1 is used, for example, by being incorporated in a seat lifter for adjusting the seat surface height of an automobile seat. A second clutch portion 20 is provided. Hereinafter, the structure of the first clutch portion 10 will be described first, and then the structure of the second clutch portion 20 will be described. In the following description, the terms "axial direction", "radial direction" and "circumferential direction" used to indicate directionality respectively constitute output side members of the second clutch portion 20 (clutch unit 1). A direction parallel to the axis X of the output shaft 22, a radial direction of a circle centered on the axis X (the output shaft 22), and a circumferential direction of a circle centered on the axis X. FIG.

図１、図２及び図４に示すように、第１クラッチ部１０は、出力軸２２の軸心Ｘ回りに回転可能な状態で出力軸２２の外周に嵌合された側板１１、外輪１２及び内輪１３と、側板１１を介して外輪１２に入力されるトルクを内輪１３に伝達する複数の係合子（円筒ころ）１４と、複数の円筒ころ１４を周方向等間隔で保持する保持器１５と、第１センタリングばね１６と、第１センタリングばね１６の径方向外側に配置された第２センタリングばね１７と、を備える。 As shown in FIGS. 1, 2, and 4, the first clutch portion 10 includes a side plate 11, an outer ring 12, and a side plate 11 fitted to the outer periphery of the output shaft 22 in a rotatable state around the axis X of the output shaft 22. An inner ring 13, a plurality of engaging elements (cylindrical rollers) 14 that transmit torque input to the outer ring 12 via the side plate 11 to the inner ring 13, and a retainer 15 that holds the plurality of cylindrical rollers 14 at regular intervals in the circumferential direction. , a first centering spring 16 and a second centering spring 17 arranged radially outside the first centering spring 16 .

外輪１２は、内周面に複数のカム面１２ａが周方向等間隔で形成された筒部を有する。この外輪１２は、シートリフタの操作レバー（図示省略）が取り付けられる側板１１と適宜の手段で連結され、側板１１とともに第１クラッチ部１０の入力側部材を構成する。 The outer ring 12 has a cylindrical portion having a plurality of cam surfaces 12a formed on the inner peripheral surface thereof at regular intervals in the circumferential direction. The outer ring 12 is connected by appropriate means to a side plate 11 to which an operating lever (not shown) of the seat lifter is attached, and constitutes an input side member of the first clutch portion 10 together with the side plate 11 .

出力軸２２には、第１クラッチ部１０（外輪１２）と軸方向で係合可能な環状の抜け止め部材（例えば、ワッシャ）２が固定され、外輪１２と抜け止め部材２の間には軸方向に圧縮変形可能な弾性部材（例えば、ウェーブワッシャ）３が介在している。これにより、外輪１２（を含む第１クラッチ部１０の入力側部材）が円滑に回転可能であると共に、出力軸２２からの第１クラッチ部１０の抜脱が防止される。 An annular retaining member (for example, a washer) 2 that can be axially engaged with the first clutch portion 10 (outer ring 12 ) is fixed to the output shaft 22 . An elastic member (for example, a wave washer) 3 that is compressively deformable in a direction is interposed. As a result, the outer ring 12 (including the input-side member of the first clutch portion 10 ) can rotate smoothly, and the first clutch portion 10 is prevented from coming off from the output shaft 22 .

内輪１３は、外輪１２の内周面に設けられたカム面１２ａとの間に円筒ころ１４が配された楔すきまＧａ（図２参照）を形成する円筒状の外周面１３ａを有する筒部１３ｂと、筒部１３ｂの軸方向一方側（図１の紙面左側。以下「軸方向一方側」という場合も同様。）の端部から径方向外側に延びたフランジ部１３ｃと、フランジ部１３ｃの外周縁部から軸方向一方側に延び、周方向等間隔で設けられた複数の柱部１３ｄ（図３参照）とを一体に有する。図３に示すように、周方向で隣り合う２つの柱部１３ｄの間には、第２クラッチ部２０の構成部品である一対の係合子（円筒ころ）２４及び弾性部材２５の組が配置される。以上の構成を有する内輪１３は、第１クラッチ部１０の出力側部材として機能すると共に、第２クラッチ部２０の入力側部材２１としても機能する。従って、第１クラッチ部１０に入力されるトルクは、この内輪１３を介して第２クラッチ部２０に入力される。 The inner ring 13 has a tubular portion 13b having a cylindrical outer peripheral surface 13a forming a wedge gap Ga (see FIG. 2) between which the cylindrical rollers 14 are arranged and the cam surface 12a provided on the inner peripheral surface of the outer ring 12. , a flange portion 13c extending radially outward from the end portion of the cylindrical portion 13b on one side in the axial direction (the left side of the paper surface of FIG. 1; hereinafter, the same applies to the case of “one side in the axial direction”), and the outside of the flange portion 13c. It integrally has a plurality of pillars 13d (see FIG. 3) that extend from the peripheral portion to one side in the axial direction and are provided at regular intervals in the circumferential direction. As shown in FIG. 3, a set of a pair of engaging elements (cylindrical rollers) 24 and an elastic member 25, which are components of the second clutch portion 20, are arranged between two pillars 13d adjacent in the circumferential direction. be. The inner ring 13 having the above structure functions as the output side member of the first clutch portion 10 and also functions as the input side member 21 of the second clutch portion 20 . Therefore, torque input to the first clutch portion 10 is input to the second clutch portion 20 via the inner ring 13 .

図２に示すように、保持器１５は、円筒ころ１４を収容する複数のポケット部１５ａが周方向等間隔で形成された筒状部材であり、その軸方向一方側の端部には、周方向に延びる円弧状の切欠き１５ｂが２つ形成されている（図４参照）。このような切欠き１５ｂが形成されていることにより、２つの切欠き１５ｂの間に円弧状の爪部１５ｃが形成されている。 As shown in FIG. 2, the retainer 15 is a tubular member in which a plurality of pocket portions 15a for accommodating the cylindrical rollers 14 are formed at regular intervals in the circumferential direction. Two arcuate notches 15b extending in the direction are formed (see FIG. 4). By forming such cutouts 15b, an arcuate claw portion 15c is formed between the two cutouts 15b.

図４に示すように、第１センタリングばね１６は、周方向に延びる円弧部１６ａと、円弧部１６ａの周方向一方側及び他方側の端部を径方向内側に屈曲させることで形成された一対の係止部１６ｂとを一体に有する略Ｃ字形状の弾性部材である。この第１センタリングばね１６は、一対の係止部１６ｂの間に保持器１５の爪部１５ｃ及び第２クラッチ部２０の静止部材（外輪）２３に形成された内側爪部２３ｄが介挿されるようにして保持器１５の径方向外側に配置されている。 As shown in FIG. 4, the first centering spring 16 includes a pair of circular arc portions 16a extending in the circumferential direction and a pair of circular arc portions 16a formed by bending radially inwardly one and the other circumferential end portions of the circular arc portions 16a. It is a substantially C-shaped elastic member integrally having a locking portion 16b. The first centering spring 16 is arranged such that the claw portion 15c of the retainer 15 and the inner claw portion 23d formed on the stationary member (outer ring) 23 of the second clutch portion 20 are inserted between the pair of locking portions 16b. , and arranged radially outside of the retainer 15 .

そして、側板１１に取り付けられた操作レバーを操作することで外輪１２にトルクが入力されると、第１センタリングばね１６の一方の係止部１６ｂが保持器１５の爪部１５ｃと周方向で係合すると共に、第１センタリングばね１６の他方の係止部１６ｂが第２クラッチ部２０の外輪２３に形成された内側爪部２３ｄと周方向に係合した状態で、保持器１５が外輪１２とともに出力軸２２の軸心Ｘ回りに回転する。これに伴い、第１センタリングばね１６は拡径方向（一対の係止部１６ｂの周方向離間距離が拡大する方向）に弾性変形するので、第１センタリングばね１６に縮径方向の弾性復元力が蓄積される。そのため、レバー操作が停止されることで外輪１２に入力されているトルクが解放されると、第１センタリングばね１６が弾性復元力によって図４に示す初期状態に戻るのに伴い、保持器１５が中立位置に復帰する。 When a torque is input to the outer ring 12 by operating an operation lever attached to the side plate 11, one locking portion 16b of the first centering spring 16 engages the claw portion 15c of the retainer 15 in the circumferential direction. At the same time, the other engaging portion 16b of the first centering spring 16 is engaged with the inner claw portion 23d formed on the outer ring 23 of the second clutch portion 20 in the circumferential direction. It rotates around the axis X of the output shaft 22 . As a result, the first centering spring 16 is elastically deformed in the diameter-expanding direction (the direction in which the circumferential distance between the pair of locking portions 16b increases), so that the first centering spring 16 exerts an elastic restoring force in the diameter-reducing direction. accumulated. Therefore, when the lever operation is stopped and the torque input to the outer ring 12 is released, the first centering spring 16 returns to the initial state shown in FIG. Return to neutral position.

図４に示すように、第２センタリングばね１７は、周方向に延びる円弧部１７ａと、円弧部１７ａの周方向一方側及び他方側の端部を径方向外側に屈曲させることで形成された一対の係止部１７ｂとを一体に有する略Ｃ字形状の弾性部材である。この第２センタリングばね１７は、一対の係止部１７ｂの間に外輪１２に形成された爪部１２ｂ及び第２クラッチ部２０の外輪２３に形成された外側爪部２３ｅが介挿されるようにして、第１クラッチ部１０の外輪１２と第２クラッチ部２０の外輪２３の間に配置される。なお、第２センタリングばね１７は、係止部１７ｂが第１センタリングばね１６の係止部１６ｂに対して周方向にずれた位置に位置するように配置される。 As shown in FIG. 4, the second centering spring 17 includes a pair of circular arc portions 17a extending in the circumferential direction and a pair of circular arc portions 17a formed by bending radially outward ends of the circular arc portions 17a on one side and the other side in the circumferential direction. It is a substantially C-shaped elastic member integrally having a locking portion 17b. The second centering spring 17 is arranged such that the claw portion 12b formed on the outer ring 12 and the outer claw portion 23e formed on the outer ring 23 of the second clutch portion 20 are inserted between the pair of locking portions 17b. , between the outer ring 12 of the first clutch part 10 and the outer ring 23 of the second clutch part 20 . The second centering spring 17 is arranged such that the engaging portion 17b is positioned at a position shifted in the circumferential direction with respect to the engaging portion 16b of the first centering spring 16. As shown in FIG.

そして、操作レバーを操作することで外輪１２にトルクが入力されると、第２センタリングばね１７に設けられた一対の係止部１７ｂのうち、一方の係止部１７ｂが外輪２１の爪部１２ｂと周方向で係合すると共に、他方の係止部１７ｂが第２クラッチ部２０の外輪２３に形成された外側爪部２３ｅと周方向に係合した状態で外輪１２が出力軸２２の軸心Ｘ回りに回転する。これに伴い、第２センタリングばね１７は拡径方向（一対の係止部１７ｂの周方向離間距離が拡大する方向）に弾性変形するので、第２センタリングばね１７に縮径方向の弾性復元力が蓄積される。そのため、レバー操作が停止されることで外輪１２に入力されているトルクが解放され、第２センタリングばね１７が弾性復元力によって図４に示す初期状態に戻るのに伴い、外輪１２は中立位置に復帰する。 Then, when torque is input to the outer ring 12 by operating the operation lever, one of the pair of locking portions 17b provided on the second centering spring 17 engages the claw portion 12b of the outer ring 21. and the other engaging portion 17b is engaged with the outer claw portion 23e formed on the outer ring 23 of the second clutch portion 20 in the circumferential direction. Rotate around X. As a result, the second centering spring 17 is elastically deformed in the diameter-expanding direction (the direction in which the circumferential distance between the pair of locking portions 17b increases), so that the second centering spring 17 exerts an elastic restoring force in the diameter-reducing direction. accumulated. Therefore, when the lever operation is stopped, the torque input to the outer ring 12 is released, and the second centering spring 17 returns to the initial state shown in FIG. return.

次に、逆入力遮断クラッチからなる第２クラッチ部２０について説明する。 Next, the second clutch portion 20, which is a reverse input cutoff clutch, will be described.

図１及び図３に示すように、第２クラッチ部２０は、第１クラッチ部１０からトルクが入力される入力側部材２１と、入力側部材２１に入力されるトルクを出力可能な出力側部材としての出力軸２２と、回転が規制された静止部材を構成する外輪２３、側板２６及び摩擦リング２７と、出力軸２２と外輪２３の間に配された複数の係合子（円筒ころ）２４及び弾性部材２５とを備える。入力側部材２１は、前述したとおり、第１クラッチ部１０の内輪１３で構成される。 As shown in FIGS. 1 and 3, the second clutch portion 20 includes an input side member 21 to which torque is input from the first clutch portion 10, and an output side member capable of outputting the torque input to the input side member 21. , an outer ring 23, a side plate 26 and a friction ring 27 that constitute a stationary member whose rotation is restricted, a plurality of engaging elements (cylindrical rollers) 24 arranged between the output shaft 22 and the outer ring 23, and and an elastic member 25 . The input side member 21 is composed of the inner ring 13 of the first clutch portion 10 as described above.

出力軸２２は、内輪１３のフランジ部１３ｃの軸方向一方側に隣接配置されたフランジ部２２ａと、フランジ部２２ａの外周縁部から軸方向一方側に延びた筒部２２ｂとが一体的に設けられたカップ状部を一体に有し、筒部２２ｂ（カップ状部）の外周面には複数の平坦なカム面２２ｃが周方向等間隔で形成されている。また、出力軸２２は、その回転（出力）を回転伝達対象に対して伝達するためのギヤ部２２ｆを有する。 The output shaft 22 is integrally provided with a flange portion 22a adjacent to the flange portion 13c of the inner ring 13 on one side in the axial direction, and a cylindrical portion 22b extending from the outer peripheral edge portion of the flange portion 22a to the one side in the axial direction. A plurality of flat cam surfaces 22c are formed at equal intervals in the circumferential direction on the outer peripheral surface of the tubular portion 22b (cup-shaped portion). The output shaft 22 also has a gear portion 22f for transmitting its rotation (output) to a rotation transmission target.

図５（ａ）（ｂ）にも示すように、出力軸２２のフランジ部２２ａには、軸方向他方側に突出した複数（ここでは、８つ）の突起２２ｄが周方向に間隔を空けて設けられており、各突起２２ｄは、内輪１３のフランジ部１３ｃに形成された孔部１３ｅに対して所定のクリアランスをもって嵌合している。なお、図示例の形態とは逆に、突起を内輪１３のフランジ部１３ｃに形成し、この突起がクリアランスをもって嵌合される孔部を出力軸２２のフランジ部２２ａに形成することも可能である。 As shown in FIGS. 5A and 5B, the flange portion 22a of the output shaft 22 has a plurality of (here, eight) projections 22d projecting to the other side in the axial direction at intervals in the circumferential direction. Each protrusion 22d is fitted into a hole 13e formed in the flange portion 13c of the inner ring 13 with a predetermined clearance. It is also possible to form a projection in the flange portion 13c of the inner ring 13 and form a hole in the flange portion 22a of the output shaft 22 in which the projection is fitted with a clearance, contrary to the illustrated example. .

外輪２３は、径方向に延び、内輪１３の筒部１３ｂを介して出力軸２２の外周に嵌合されたフランジ部２３ａと、フランジ部２３ａの外周縁部から軸方向一方側に延びた筒部２３ｂとを一体に有する。筒部２３ｂの内周面２３ｃは円筒面状に形成され、出力軸２２の筒部２２ｂの外周面に設けられたカム面２２ｃとの間に楔すきまＧｂを形成する。各楔すきまＧｂには、一対の係合子（円筒ころ）２４と、周方向に圧縮された状態で一対の円筒ころ２４の間に介在する弾性部材（板ばね）２５とが配設されている。前述したように、外輪２３のフランジ部２３ａには、第１センタリングばね１６の係止部１６ｂと周方向で係合する内側爪部２３ｄと、第２センタリングばね１７の係止部１７ｂと周方向で係合する外側爪部２３ｅとが形成されている。 The outer ring 23 includes a flange portion 23a extending in the radial direction and fitted to the outer periphery of the output shaft 22 via the cylindrical portion 13b of the inner ring 13, and a cylindrical portion extending from the outer peripheral edge portion of the flange portion 23a to one side in the axial direction. 23b integrally. An inner peripheral surface 23c of the tubular portion 23b is formed in a cylindrical shape, and forms a wedge clearance Gb with a cam surface 22c provided on an outer peripheral surface of the tubular portion 22b of the output shaft 22. As shown in FIG. Each wedge gap Gb is provided with a pair of engaging elements (cylindrical rollers) 24 and an elastic member (leaf spring) 25 interposed between the pair of cylindrical rollers 24 in a circumferentially compressed state. . As described above, the flange portion 23a of the outer ring 23 includes the inner claw portion 23d that engages with the locking portion 16b of the first centering spring 16 in the circumferential direction, and the locking portion 17b of the second centering spring 17 in the circumferential direction. An outer claw portion 23e that engages with is formed.

側板２６は、出力軸２２が挿通される中心孔と、軸方向他方側に向けて突設された環状突起２６ａと、クラッチユニット１を取付対象（ここでは、自動車用座席シート）に対してボルト止めするためのボルト孔（図示省略）とを有する円板状の部材であり、出力軸２２の筒部２２ｂと外輪２３の筒部２３ｂの間に形成される開口部に環状突起２６ａを配置した状態で外輪２３と連結されている。これにより、出力軸２２の筒部２２ｂと外輪２３の筒部２３ｂの間（楔すきまＧｂ）に配された円筒ころ２４及び弾性部材２５の脱落が防止される。 The side plate 26 has a center hole through which the output shaft 22 is inserted, an annular projection 26a projecting toward the other side in the axial direction, and bolts to which the clutch unit 1 is attached (in this case, an automobile seat). It is a disk-shaped member having a bolt hole (not shown) for fastening, and an annular projection 26a is arranged in an opening formed between the cylindrical portion 22b of the output shaft 22 and the cylindrical portion 23b of the outer ring 23. It is connected with the outer ring 23 in a state. As a result, the cylindrical rollers 24 and the elastic member 25 arranged between the cylindrical portion 22b of the output shaft 22 and the cylindrical portion 23b of the outer ring 23 (wedge clearance Gb) are prevented from coming off.

摩擦リング２７は、周方向に沿って凸部と凹部を交互に配した環状の樹脂部品であり、凸部の外周面を出力軸２２の筒部２２ｂの内周面に圧接させた状態で側板２６に固定されている。このような摩擦リング２７が設けられていることにより、出力軸２２に回転抵抗が付与されるので、入力側部材２１にトルクが入力されたときに出力軸２２が必要以上に回転するのを防止することができる。 The friction ring 27 is a ring-shaped resin component having convex portions and concave portions alternately arranged along the circumferential direction. 26 is fixed. Rotational resistance is applied to the output shaft 22 by providing the friction ring 27, so that the output shaft 22 is prevented from rotating more than necessary when torque is input to the input side member 21. can do.

以上の構成を有する本実施形態のクラッチユニット１は以下のように動作する。 The clutch unit 1 of this embodiment having the above configuration operates as follows.

まず、第１クラッチ部１０において、図示しない操作レバーが操作されることにより側板１１を介して外輪１２にトルクが入力されると、外輪１２と内輪１３の間の楔すきまＧａに円筒ころ１４が係合するので、円筒ころ１４を介して内輪１３にトルクが伝達されて内輪１３が回転する。このとき、外輪１２及び保持器１５の回転に伴って両センタリングばね１６，１７に弾性復元力が蓄積される。レバー操作が停止されて外輪１２へのトルク入力がなくなると、両センタリングばね１６，１７の弾性復元力によって外輪１２及び保持器１５は中立状態に復帰する一方で、内輪１３は与えられた回転位置をそのまま維持する。従って、レバー操作により内輪１３は寸動回転する。 First, in the first clutch portion 10, when a torque is input to the outer ring 12 through the side plate 11 by operating an operation lever (not shown), the cylindrical rollers 14 are formed in the wedge clearance Ga between the outer ring 12 and the inner ring 13. Since they are engaged, torque is transmitted to the inner ring 13 via the cylindrical rollers 14 to rotate the inner ring 13 . At this time, elastic restoring force is accumulated in both centering springs 16 and 17 as the outer ring 12 and retainer 15 rotate. When the lever operation is stopped and the torque input to the outer ring 12 is stopped, the elastic restoring force of both the centering springs 16 and 17 causes the outer ring 12 and the retainer 15 to return to the neutral state, while the inner ring 13 is moved to the given rotational position. be kept as is. Therefore, the inner ring 13 is inching rotated by operating the lever.

一方、第２クラッチ部２０において、入力側部材２１としての内輪１３へのトルク入力がなく、内輪１３の柱部１３ｄが中立位置に位置した状態（図３参照）では、周方向に圧縮された状態で楔すきまＧｂ内に介在する弾性部材２５の弾性復元力により、弾性部材２５の周方向両側に配された一対の円筒ころ２４（２４Ａ，２４Ｂ）が楔すきまＧｂの狭小部（周方向両端部）に押し込まれて出力軸２２及び外輪２３と周方向で係合する。これにより、出力軸２２が外輪２３に対してロックされるロック状態となるので、この状態で出力軸２２に逆入力トルクＴ’（図３参照）が入力されても、この逆入力トルクＴ’が内輪１３、ひいては第１クラッチ部１０に伝達（還流）されるのを阻止することができる。 On the other hand, in the second clutch portion 20, when there is no torque input to the inner ring 13 as the input-side member 21 and the column portion 13d of the inner ring 13 is positioned at the neutral position (see FIG. 3), it is compressed in the circumferential direction. In this state, the pair of cylindrical rollers 24 (24A, 24B) disposed on both sides of the elastic member 25 in the circumferential direction move to narrow portions (both circumferential ends) of the wedge clearance Gb due to the elastic restoring force of the elastic member 25 interposed in the wedge clearance Gb portion) to engage with the output shaft 22 and the outer ring 23 in the circumferential direction. As a result, the output shaft 22 is in a locked state in which it is locked with respect to the outer ring 23. Therefore, even if a reverse input torque T' (see FIG. 3) is input to the output shaft 22 in this state, the reverse input torque T' can be prevented from being transmitted (returned) to the inner ring 13 and thus to the first clutch portion 10 .

上記のロック状態で、第１クラッチ部１０でのレバー操作に伴って内輪１３にトルクＴ（図３参照）が入力されると、内輪１３の柱部１３ｄが一対の円筒ころ２４（２４Ａ，２４Ｂ）のうちの一方の円筒ころ２４Ｂを弾性部材２５の弾性復元力に抗して他方の円筒ころ２４Ａ側に押圧し、上記一方の円筒ころ２４Ｂを楔すきまＧｂの狭小部から離脱させる。これにより、上記のロック状態が解除される。そして、内輪１３がさらに回転すると、内輪１３のフランジ部１３ｃに設けられた孔部１３ｅと出力軸２２のフランジ部２２ａに設けられた突起２２ｄの間のクリアランスが詰まって内輪１３が出力軸２２と周方向で係合するので、内輪１３のトルクが出力軸２２に伝達される。これにより、出力軸２２が回転する。 In the above-described locked state, when torque T (see FIG. 3) is input to the inner ring 13 as the lever is operated in the first clutch portion 10, the column portion 13d of the inner ring 13 engages the pair of cylindrical rollers 24 (24A, 24B). ) is pushed toward the other cylindrical roller 24A against the elastic restoring force of the elastic member 25, and the one cylindrical roller 24B is separated from the narrow portion of the wedge clearance Gb. As a result, the above lock state is released. When the inner ring 13 rotates further, the clearance between the hole 13e provided in the flange portion 13c of the inner ring 13 and the projection 22d provided in the flange portion 22a of the output shaft 22 is closed, and the inner ring 13 and the output shaft 22 are separated. Since they engage in the circumferential direction, the torque of the inner ring 13 is transmitted to the output shaft 22 . This causes the output shaft 22 to rotate.

第１クラッチ部１０でのレバー操作が中止され、内輪１３へのトルク入力がなくなると、上記のとおり、弾性部材２５の弾性復元力によってその周方向両側に配された一対の円筒ころ２４Ａ，２４Ｂが楔すきまＧｂの狭小部に押し込まれる。このとき、内輪１３の各柱部１３ｄには、一対の円筒ころ２４Ａ，２４Ｂのうち内輪１３の回転方向後側に位置する円筒ころ２４Ｂを介して弾性部材２５の弾性復元力が作用する。これにより、内輪１３は、柱部１３ｄが円筒ころ２４（特に２４Ｂ）を周方向に押圧しない中立位置（図３参照）に復帰する。 When the lever operation in the first clutch portion 10 is stopped and the torque input to the inner ring 13 is stopped, the elastic restoring force of the elastic member 25 causes the pair of cylindrical rollers 24A and 24B arranged on both sides in the circumferential direction to move as described above. is pushed into the narrow portion of the wedge clearance Gb. At this time, the elastic restoring force of the elastic member 25 acts on each column portion 13d of the inner ring 13 via the cylindrical roller 24B positioned on the rear side in the rotational direction of the inner ring 13 among the pair of cylindrical rollers 24A and 24B. As a result, the inner ring 13 returns to the neutral position (see FIG. 3) where the column portion 13d does not press the cylindrical rollers 24 (especially 24B) in the circumferential direction.

但し、入力側部材２１としての内輪１３が出力軸２２や外輪２３などの他部材と接触することにより生じる内部抵抗が弾性部材２５の弾性復元力（によるトルク）よりも大きくなる場合がある。本発明者らの検証によれば、出力軸２２は、その回転伝達対象との間でトルクを伝達する際に軸方向に対して傾きが生じ易く、出力軸２２が傾いた状態で出力軸２２と内輪１３が相対回転すると両者間で大きな摺動抵抗が生じ、このことが、逆入力遮断クラッチからなる第２クラッチ部２０の内部抵抗増加を招来する大きな一因となっている。特に、図７（ａ）（ｂ）に示す従来の逆入力遮断クラッチ１００のように、出力軸１０２のフランジ部の軸方向他方側の端面全域が入力側部材１０１のフランジ部の軸方向一方側の端面と一定間隔で対向していると、出力軸１０２が軸方向に対して傾いたときに入力側部材１０１と出力軸１０２とが広範に亘って接触するため、両者１０１，１０２間で大きな摺動抵抗が生じ易い。 However, the internal resistance generated by the contact of the inner ring 13 as the input side member 21 with other members such as the output shaft 22 and the outer ring 23 may be greater than the elastic restoring force of the elastic member 25 (torque due to it). According to the verification by the present inventors, the output shaft 22 tends to be inclined with respect to the axial direction when torque is transmitted between the rotation transmission target, and the output shaft 22 is inclined in a state where the output shaft 22 is inclined. When the inner ring 13 and the inner ring 13 rotate relative to each other, a large sliding resistance is generated between them, which is a major cause of an increase in the internal resistance of the second clutch portion 20, which is a reverse input cutoff clutch. In particular, like the conventional reverse input cutoff clutch 100 shown in FIGS. , the input side member 101 and the output shaft 102 are in contact with each other over a wide area when the output shaft 102 is tilted with respect to the axial direction. Sliding resistance is likely to occur.

このような場合、弾性部材２５の周方向両側に配された一対の円筒ころ２４Ａ，２４Ｂを楔すきまＧｂの適正位置まで押し込む（内輪１３を中立位置に復帰させる）ことができず、いわゆる甘噛み状態となる。この状態で出力軸２２に逆入力トルクＴ’（図３参照）が入力されると、出力軸２２の回転を適切に規制すること、つまり逆入力遮断機能を適切に発揮することができない可能性がある。 In such a case, the pair of cylindrical rollers 24A and 24B arranged on both sides in the circumferential direction of the elastic member 25 cannot be pushed in to the appropriate position of the wedge clearance Gb (the inner ring 13 cannot be returned to the neutral position), resulting in so-called soft engagement. state. If a reverse input torque T' (see FIG. 3) is input to the output shaft 22 in this state, it may not be possible to properly regulate the rotation of the output shaft 22, that is, to properly exhibit the reverse input blocking function. There is

そこで、本実施形態の第２クラッチ部２０においては、図１及び図５（ａ）（ｂ）に示すように、軸方向で互いに対向する出力軸２２のフランジ部２２ａの端面（軸方向他方側の端面）２２ｅ及び内輪１３のフランジ部１３ｃの端面（軸方向一方側の端面）１３ｆのうち、出力軸２２の端面２２ｅに、軸方向他方側に突出して内輪１３の端面１３ｆと接触する凸部５を設けている。図１には、凸部５の先端が対向する内輪１３の端面１３ｆに接触した形態を示しているが、両者間に軸方向のすきまが介在する場合もある。 Therefore, in the second clutch portion 20 of the present embodiment, as shown in FIGS. ) 22e and the end surface (end surface on one side in the axial direction) 13f of the flange portion 13c of the inner ring 13, the end surface 22e of the output shaft 22 protrudes toward the other side in the axial direction and contacts the end surface 13f of the inner ring 13. 5 is provided. Although FIG. 1 shows a configuration in which the tip of the protrusion 5 contacts the opposing end surface 13f of the inner ring 13, there may be an axial gap between the two.

係る構成によれば、入力側部材２１としての内輪１３と出力軸２２とが軸方向で接触するときには、内輪１３及び出力軸２２の何れか一方（ここでは出力軸２２）に設けた凸部５を他方（ここでは内輪１３）に対して優先的に接触させることができる。そのため、図示例のように、先端面（内輪１３との接触面）の面積が、凸部５が形成される出力軸２２の端面２２ｅの面積よりも格段に小さくなるような凸部５を形成しておけば、内輪１３と出力軸２２の接触面積を減じて両者１３，２２間で生じる摺動抵抗、つまり第２クラッチ部２０の動作時に生じる内部抵抗を減じることができる。これにより、内輪１３に入力されたトルクが除荷された後には、内輪１３を中立位置に適切に復帰させること、つまりクラッチユニット１をロック解除状態からロック状態に適切に移行させることができる。従って、本発明に係る逆入力遮断クラッチ（を含むクラッチユニット１）は、逆入力遮断機能を適切に発揮することができて信頼性に富む、という特徴を有する。 According to such a configuration, when the inner ring 13 as the input side member 21 and the output shaft 22 come into contact with each other in the axial direction, the convex portion 5 provided on either the inner ring 13 or the output shaft 22 (here, the output shaft 22) is displaced. can be preferentially brought into contact with the other (here, the inner ring 13). Therefore, as shown in the illustrated example, the convex portion 5 is formed so that the area of the tip surface (the contact surface with the inner ring 13) is much smaller than the area of the end surface 22e of the output shaft 22 on which the convex portion 5 is formed. By doing so, the contact area between the inner ring 13 and the output shaft 22 can be reduced to reduce the sliding resistance generated between them 13 and 22, that is, the internal resistance generated when the second clutch portion 20 operates. Thus, after the torque input to the inner ring 13 is released, the inner ring 13 can be properly returned to the neutral position, that is, the clutch unit 1 can be properly shifted from the unlocked state to the locked state. Therefore, the reverse input cut-off clutch (including the clutch unit 1) according to the present invention is characterized by being able to appropriately exhibit the reverse input cut-off function and being highly reliable.

本実施形態では、図５（ｂ）に示すように、複数（３つ）の凸部５を周方向に間隔を空けて設けている。出力軸２２の傾き方向は一定ではなく、随時変化することから、本実施形態のように複数の凸部５を周方向に間隔を空けて配置しておけば、出力軸２２が様々な方向に傾いたときにも凸部５と相手面とを接触させ易くなる。なお、図示例では、出力軸２２のフランジ部２２ａに８つの突起２２ｄを周方向等間隔で設けている関係上、計３つの凸部５を周方向不等間隔で配置しているが、例えば凸部５を４つ又は８つ設ければ（図示省略）、凸部５を周方向等間隔で配置することができる。このように、複数の凸部５を周方向等間隔で配置した場合、複数の凸部５を設けることにより享受される上記の作用効果をより有効に享受することができる。 In this embodiment, as shown in FIG. 5B, a plurality (three) of protrusions 5 are provided at intervals in the circumferential direction. Since the tilt direction of the output shaft 22 is not constant and changes at any time, if a plurality of protrusions 5 are arranged at intervals in the circumferential direction as in the present embodiment, the output shaft 22 can be tilted in various directions. Even when tilted, the projection 5 and the mating surface are easily brought into contact with each other. In the illustrated example, since eight protrusions 22d are provided on the flange portion 22a of the output shaft 22 at equal intervals in the circumferential direction, a total of three protrusions 5 are arranged at uneven intervals in the circumferential direction. If four or eight protrusions 5 are provided (not shown), the protrusions 5 can be arranged at regular intervals in the circumferential direction. In this way, when a plurality of protrusions 5 are arranged at regular intervals in the circumferential direction, the above-described effects obtained by providing the plurality of protrusions 5 can be enjoyed more effectively.

本実施形態では、先端が相手面に対して点接触（小さな面で接触）するようなピン状の凸部５を形成しているが、内輪１３と出力軸２２の間の摺動抵抗を低減させ得る限りにおいて凸部５の形状は任意に変更することができる。図示は省略するが、凸部５は、例えば周方向で有端の円弧状に形成することも可能である。 In this embodiment, the pin-shaped protrusion 5 is formed such that the tip makes point contact (contacts on a small surface) with the mating surface, but the sliding resistance between the inner ring 13 and the output shaft 22 is reduced. The shape of the convex portion 5 can be arbitrarily changed as long as it is possible. Although illustration is omitted, the convex portion 5 can also be formed, for example, in an arc shape having an end in the circumferential direction.

以上、本発明の一実施形態に係る逆入力遮断クラッチとしての第２クラッチ部２０を含むクラッチユニット１について説明を行ったが、本発明の実施の形態はこれに限られない。 Although the clutch unit 1 including the second clutch portion 20 as the reverse input cutoff clutch according to one embodiment of the present invention has been described above, the embodiment of the present invention is not limited to this.

例えば、以上で説明した実施形態で出力軸２２のフランジ部２２ａに設けた凸部５は、図６に示すように、フランジ部２２ａと対向配置される内輪１３のフランジ部１３ｃ（の端面１３ｆ）に設けても良い。係る構成によっても、上記同様の作用効果を享受することができる。 For example, as shown in FIG. 6, the convex portion 5 provided on the flange portion 22a of the output shaft 22 in the above-described embodiment is arranged to face the flange portion 22a and the flange portion 13c of the inner ring 13 (the end surface 13f thereof). may be set to With such a configuration, it is possible to obtain the same effect as described above.

以上で説明した逆入力遮断クラッチを含むクラッチユニット１は、自動車用座席シートの座面高さを調整するシートリフタ以外にも、例えば、電動スライドドア、パワーウィンドウ、電動ステアリング等の駆動機構に組み込むことが可能である。 The clutch unit 1 including the reverse input cut-off clutch described above can be incorporated in a drive mechanism such as an electric sliding door, a power window, an electric steering, etc., in addition to a seat lifter for adjusting the seat surface height of an automobile seat. is possible.

以上、本発明の実施形態に係る逆入力遮断クラッチとしての第２クラッチ部２０を含むクラッチユニット１について説明したが、本発明は以上で説明した実施形態に何ら限定されるものではなく、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは言うまでもない。本発明の範囲は、特許請求の範囲によって示され、さらに特許請求の範囲に記載の均等の意味、及び範囲内のすべての変更を含む。 Although the clutch unit 1 including the second clutch portion 20 as the reverse input cut-off clutch according to the embodiment of the present invention has been described above, the present invention is not limited to the embodiment described above. Needless to say, various forms can be implemented without departing from the gist of the above. The scope of the present invention is indicated by the scope of the claims, and includes equivalent meanings and all changes within the scope of the claims.

１クラッチユニット
５凸部
１０第１クラッチ部
１３内輪（入力側部材）
１３ｄ柱部
２０第２クラッチ部（逆入力遮断クラッチ）
２１入力側部材
２２出力軸
２２ｃカム面
２３外輪（静止部材）
２４円筒ころ（係合子）
２５弾性部材
Ｇｂ楔すきま
Ｔトルク
Ｔ’ 逆入力トルク 1 clutch unit 5 convex portion 10 first clutch portion 13 inner ring (input side member)
13d Column 20 Second clutch (reverse input cut-off clutch)
21 Input side member 22 Output shaft 22c Cam surface 23 Outer ring (stationary member)
24 Cylindrical roller (engagement)
25 Elastic member Gb Wedge clearance T Torque T' Reverse input torque

Claims

An input side member to which torque is input, an output shaft capable of outputting the torque, and a stationary member whose rotation is restricted,
A plurality of cam surfaces forming wedge clearances with the inner peripheral surface of the stationary member are provided on the outer peripheral surface of the output shaft at intervals in the circumferential direction, and each wedge clearance includes a pair of engaging elements, and an elastic member interposed between the pair of engaging elements in a state of being compressed in the circumferential direction,
By engaging the pair of engaging elements with the elastic restoring force of the elastic member with the output shaft and the stationary member in the circumferential direction, reverse input torque input to the output shaft is transferred to the input side member. A locked state in which transmission is interrupted is established, and as torque is input to the input side member, the column portion of the input side member disposed between the wedge gaps adjacent in the circumferential direction is moved to one of the pair of engaging elements. in a reverse input interrupting clutch in which the locked state is released by pressing against the elastic restoring force against the other engaging element side,
A reverse input cut-off clutch, wherein a convex portion is provided on either one of the end face of the input side member and the end face of the output shaft, which face each other in the axial direction, so as to protrude toward the other side and come into contact with the other.

2. A reverse input interrupting clutch according to claim 1, wherein said protrusions are arranged at a plurality of locations in the circumferential direction.

3. A reverse input interrupting clutch according to claim 2, wherein a plurality of said projections are arranged at regular intervals in the circumferential direction.

A first clutch part for controlling transmission and interruption of torque input by lever operation, and a second clutch part comprising the reverse input interruption clutch according to any one of claims 1 to 3, wherein the first A clutch unit in which an output of a clutch portion is input to the input side member.