JPH06313444A - Clutch device - Google Patents
Clutch deviceInfo
- Publication number
- JPH06313444A JPH06313444A JP10441793A JP10441793A JPH06313444A JP H06313444 A JPH06313444 A JP H06313444A JP 10441793 A JP10441793 A JP 10441793A JP 10441793 A JP10441793 A JP 10441793A JP H06313444 A JPH06313444 A JP H06313444A
- Authority
- JP
- Japan
- Prior art keywords
- output shaft
- sprag
- input shaft
- shaft
- outer ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
- F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
- F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、クラッチ装置に関
し、例えば電動パワーステアリング装置の駆動力切換え
に使用される。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch device and is used, for example, for switching the driving force of an electric power steering device.
【０００２】[0002]
【従来の技術】自動車の電動パワーステアリング装置
は、図１１に示すようにハンドル３１を回転操作する
と、車輪３３からの抵抗によりハンドル軸３２に発生す
るトルクをセンサー３４が検出し、制御装置３５を通じ
て駆動されるモータ３６が、減速機３７を介してハンド
ル軸３２のピニオン３８を回転させ、これにかみ合った
ラック３９を介して車輪３３を操舵するようになってい
る。2. Description of the Related Art In an electric power steering apparatus for an automobile, when a steering wheel 31 is rotated as shown in FIG. 11, a sensor 34 detects a torque generated on a steering wheel shaft 32 due to a resistance from a wheel 33, and a controller 35 controls the torque. A driven motor 36 rotates a pinion 38 of the handle shaft 32 via a speed reducer 37, and steers wheels 33 via a rack 39 engaged with the pinion 38.
【０００３】上記の電動パワーステアリング装置におい
ては、制御装置３５やモータ３６、減速機３７等の駆動
系に異常が発生した場合、手動によるハンドル３１の操
作に切換ることができるように、減速機３７とピニオン
３８の間にクラッチ装置１を設け、ハンドル軸３２に対
する駆動経路を切換える構造がとられている。In the above electric power steering apparatus, the speed reducer is arranged so that the steering wheel 31 can be manually operated when an abnormality occurs in the drive system such as the controller 35, the motor 36, the speed reducer 37 and the like. The clutch device 1 is provided between the pinion 38 and the pinion 38 to switch the drive path for the handle shaft 32.
【０００４】このような駆動経路を機械的に切換えるク
ラッチ装置１として、従来図１２乃至図１４に示すよう
な構造のものが考えられている（特願昭６３−２３５７
３１号）。As a clutch device 1 for mechanically switching such a drive path, one having a structure as shown in FIGS. 12 to 14 has been conventionally considered (Japanese Patent Application No. 63-2357).
No. 31).
【０００５】この構造は、同軸上に配置した入力軸２と
出力軸３の外側に外輪４を嵌合させ、その出力軸３と外
輪４の対向面に形成した円筒面５、６の間に、入力軸２
と一体の保持器８と、出力軸３に固定される保持器７を
設け、この両保持器７、８に設けたポケット９、１０
に、外輪４と出力軸３の相対回転によって両円筒面５、
６に係合するスプラグ１１と、そのスプラグ１１を中立
状態に保持する弾性部材１２を組込んでいる。In this structure, an outer ring 4 is fitted outside the input shaft 2 and the output shaft 3 arranged coaxially, and between the output shaft 3 and the cylindrical surfaces 5 and 6 formed on the facing surface of the outer ring 4. , Input shaft 2
And a cage 8 fixed to the output shaft 3 are provided, and pockets 9 and 10 provided in both cages 7 and 8 are provided.
In addition, by the relative rotation of the outer ring 4 and the output shaft 3, both cylindrical surfaces 5,
6 and the elastic member 12 for holding the sprag 11 in a neutral state are incorporated.
【０００６】また、入力軸２に形成した角孔２１に、出
力軸３に設けた角軸２２を回転方向すき間Ｘを介して嵌
合させ、入力軸２と出力軸３の間に、その両者を回転方
向すき間Ｘの中立位置に保持すると共に、入力軸２に一
定以上の回転力が付与された時に回転方向すき間Ｘが無
くなるまで弾性変形するトルク設定弾性部材１３を組込
んでいる。Further, the square shaft 22 provided on the output shaft 3 is fitted into the square hole 21 formed on the input shaft 2 through the gap X in the rotational direction, and the square shaft 22 is provided between the input shaft 2 and the output shaft 3 and both. Is held at a neutral position in the rotational direction clearance X, and a torque setting elastic member 13 that is elastically deformed until the rotational direction clearance X disappears when a rotational force of a certain amount or more is applied to the input shaft 2 is incorporated.
【０００７】上記構造のクラッチ装置では、入力軸２に
加わる回転力が、トルク設定弾性部材１３の設定トルク
以下の時はクラッチが作動せず、入力軸２から出力軸３
に回転力が伝達されるが、入力軸２に加わる回転力が設
定トルク以上になると、スプラグ１１と両円筒面５、６
が係合してクラッチが成立し、外輪４からの回転力が出
力軸３に伝達される。In the clutch device having the above structure, when the torque applied to the input shaft 2 is less than the set torque of the torque setting elastic member 13, the clutch does not operate and the input shaft 2 to the output shaft 3 are not operated.
The rotational force is transmitted to the input shaft 2, but when the rotational force applied to the input shaft 2 exceeds the set torque, the sprag 11 and both cylindrical surfaces 5, 6 are
Are engaged to establish a clutch, and the rotational force from the outer ring 4 is transmitted to the output shaft 3.
【０００８】[0008]
【発明が解決しようとする課題】ところで、上記構造の
クラッチ装置において、スプラグ１１が中立状態から図
１５に示すように円周方向に傾動し、スプラグ両端部の
カム面１４、１５がそれぞれ外輪４の円筒面６と出力軸
３の円筒面５に接触すると、クラッチ噛み合い可能状態
となる。By the way, in the clutch device having the above structure, the sprag 11 is tilted in the circumferential direction from the neutral state as shown in FIG. 15, and the cam surfaces 14 and 15 at both ends of the sprag are the outer ring 4 respectively. When the cylindrical surface 6 and the cylindrical surface 5 of the output shaft 3 come into contact with each other, the clutch can engage with each other.
【０００９】そして、この状態から、外輪４が図１５の
矢印Ａ方向に回転すると、スプラグ１５が両円筒面５、
６に係合し、逆に外輪４が矢印Ｂ方向に回転すると、外
輪４がスプラグ１１に対してオーバーランニングし、空
転状態となる。From this state, when the outer ring 4 rotates in the direction of arrow A in FIG.
When the outer ring 4 rotates in the direction of the arrow B, the outer ring 4 overruns the sprags 11 and becomes idling.
【００１０】ところが、図１５に示すクラッチ噛み合い
可能状態の時、スプラグ１１の外径側カム面１４と外輪
４の円筒面６との間に異物１６が入り込み、その状態か
ら外輪４が出力軸３に対して矢印Ｂ方向に相対回転して
空転状態となると、図１６に示すように、円筒面６とス
プラグ１１のカム面１４との間に異物１６が噛み込み、
スプラグが入力軸２の回転方向とは逆方向に傾動する。
この場合、外輪４が矢印Ｂ方向に回転しているため、ス
プラグ１１は突然に衝撃を伴ってクランプし、その結
果、円筒面６やスプラグ１１のカム面１４に圧痕が生
じ、負荷耐久機能や空転機能に支障をきたす恐れがあ
る。However, when the clutch can engage with each other as shown in FIG. 15, a foreign substance 16 enters between the outer diameter side cam surface 14 of the sprag 11 and the cylindrical surface 6 of the outer ring 4, and from that state, the outer ring 4 outputs the output shaft 3 to the output shaft 3. When rotating relative to the direction of arrow B to the idling state, the foreign matter 16 is caught between the cylindrical surface 6 and the cam surface 14 of the sprag 11, as shown in FIG.
The sprag tilts in the direction opposite to the rotation direction of the input shaft 2.
In this case, since the outer ring 4 is rotating in the direction of arrow B, the sprag 11 is suddenly clamped with an impact, and as a result, an indentation is generated on the cylindrical surface 6 and the cam surface 14 of the sprag 11, and the load endurance function and There is a risk of impairing the idling function.
【００１１】上記の現象は、図１７に示すようにスプラ
グ１１が外輪４と接触した状態で空転し、スプラグ１１
の内径側のカム面１５と出力軸３の円筒面５との間に異
物１６が入り込んだ場合でも、同様に発生する。As shown in FIG. 17, the above-mentioned phenomenon causes the sprag 11 to idle when the sprag 11 is in contact with the outer race 4,
Even when the foreign matter 16 enters between the cam surface 15 on the inner diameter side and the cylindrical surface 5 of the output shaft 3, the foreign matter 16 similarly occurs.
【００１２】このような異物噛み込みによる現象は、空
転時のスプラグと外輪又は出力軸の間にできるすき間を
大きくすれば改善することでき、このため、従来その対
策案として、図１８に示すようにスプラグ１１の初期高
さＨを小さくし、空転時のすき間ｔを拡大する方法が考
えられている。Such a phenomenon caused by foreign matter biting can be improved by increasing the gap formed between the sprag and the outer ring or the output shaft during idling. Therefore, as a conventional countermeasure, as shown in FIG. In addition, a method of reducing the initial height H of the sprags 11 and enlarging the clearance t during idling has been considered.
【００１３】しかし、上記の方法では、スプラグ１１が
クラッチ噛み込み状態になるまでのスプラグの傾きが大
きくなるため、係合を確実に行なわせるにはスプラグ幅
Ｗを大きくし、カム面１４、１５の幅を広げなければな
らない欠点がある。However, in the above method, the inclination of the sprag until the sprag 11 is in the clutch engagement state becomes large. Therefore, in order to ensure the engagement, the sprag width W is increased and the cam surfaces 14 and 15 are made. There is a drawback that you have to widen the width.
【００１４】また、回転方向が左右に切替わる場合、噛
み込む状態になるためのスプラグの傾きが大きく、切替
わりの時間が長くなる。また、保持器７、８の相対ねじ
り角が大きくなるが、設定トルクは余り大きくできない
ので、弾性部材１３の弾性力を低下させる必要がある。
しかし、このような弾性力の低下は、クラッチ装置のト
ルク伝達構造の剛性を低下させ、トルク設定弾性部材１
３を介して操舵するときのステアリングが不安定になり
やすい問題を有している。Further, when the rotation direction is switched to the left or right, the inclination of the sprag to be in the engaged state is large and the switching time becomes long. Further, although the relative torsion angles of the cages 7 and 8 become large, the set torque cannot be increased so much, so that it is necessary to reduce the elastic force of the elastic member 13.
However, such a decrease in the elastic force decreases the rigidity of the torque transmission structure of the clutch device, and the torque setting elastic member 1
There is a problem that the steering is apt to be unstable when the steering is performed via the steering wheel 3.
【００１５】そこで、この発明は、上記の問題を解決
し、スプラグの初期高さやトルク設定部材の弾性力を変
化させることなく上述した異物噛み込みによる現象を防
止でき、確実で安定した作動が行なえるクラッチ装置を
提供することを目的としている。Therefore, the present invention solves the above-mentioned problems, and can prevent the above-mentioned phenomenon caused by foreign matter trapping without changing the initial height of the sprag and the elastic force of the torque setting member, and ensure a stable and stable operation. An object of the present invention is to provide a clutch device.
【００１６】[0016]
【課題を解決するための手段】上記の課題を解決するた
め、この発明は、同軸上に配置した入力軸と出力軸の外
側に外輪を嵌合させ、この外輪と出力軸の各対向面にそ
れぞれ同軸の円筒面を形成し、その両円筒面間に、入力
軸に固定される保持器と、出力軸に固定される保持器を
設け、この両保持器に設けた径方向に対向するポケット
に、スプラグの両端部を挿入し、このスプラグの両端部
に、それぞれスプラグが周方向に傾いた時に上記両円筒
面に係合するカム面を設け、上記入力軸と出力軸を回転
方向すき間を介して共回り可能に連結し、この入力軸と
出力軸の間に、両軸を上記回転方向すき間の中立位置に
保持すると共に、入力軸に設定トルク以上の回転力が付
与された時に回転方向すき間がなくなるまで弾性変形す
るトルク設定弾性部材を組込み、上記スプラグの両端部
の一方又は両方のカム面の両側部を、上記両円筒面に係
合する円弧面で形成し、そのカム面の中央部を、上記両
側部の円弧面と連続する円弧に対して内方側へ後退させ
た構造としたのである。In order to solve the above-mentioned problems, according to the present invention, an outer ring is fitted on the outer side of an input shaft and an output shaft which are coaxially arranged, and the outer ring and the output shaft face each other. Formed coaxial cylindrical surfaces respectively, and between the cylindrical surfaces, a cage fixed to the input shaft and a cage fixed to the output shaft are provided, and the pockets provided in both cages and facing each other in the radial direction. , Both ends of the sprag are inserted, and both ends of the sprag are provided with cam surfaces that engage the cylindrical surfaces when the sprags are inclined in the circumferential direction, respectively, and the input shaft and the output shaft are provided with a clearance in the rotational direction. Through the input shaft and the output shaft, both shafts are held in the neutral position between the rotation direction gaps, and the rotation direction is applied when the input shaft is given a torque equal to or greater than the set torque. Torque setting elasticity that elastically deforms until there is no gap Incorporating a material, forming one or both cam surfaces of both ends of the sprag with arcuate surfaces that engage with both the cylindrical surfaces, and the center of the cam surface with the arcuate surfaces of the both sides. The structure is such that it recedes inward with respect to continuous arcs.
【００１７】[0017]
【作用】上記のようにスプラグのカム面の中央部を後退
させることにより、空転時にスプラグと外輪又は出力軸
の円筒面との間にできるすき間が大きくなり、クラッチ
内に異物が侵入しても、異物の噛み込みによるスプラグ
と円筒面との異常接触が防止される。By retracting the central portion of the cam surface of the sprag as described above, the gap formed between the sprag and the outer ring or the cylindrical surface of the output shaft during idling increases, and even if foreign matter enters the clutch. Abnormal contact between the sprag and the cylindrical surface due to foreign matter being caught is prevented.
【００１８】また、スプラグのカム面の両側部分は形状
を変化させる必要がなく、スプラグの幅寸法や左右方向
の切り替え時間の増大を防止することができる。Further, it is not necessary to change the shape of the both sides of the cam surface of the sprag, and it is possible to prevent the width dimension of the sprag and the switching time in the left-right direction from increasing.
【００１９】[0019]
【実施例】以下、この発明の実施例を図１乃至図６に基
づいて説明する。なお、クラッチ装置の基本的構造につ
いては、先に従来技術の項で述べたので、ここでは実施
例の特徴について説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described below with reference to FIGS. Since the basic structure of the clutch device has been described in the section of the prior art, the features of the embodiment will be described here.
【００２０】図１乃至図３に示すように、この実施例で
は、入力軸２の端部に角軸２２を、出力軸３にその角軸
２２が嵌合する角孔２１を設け、この角軸２２と角孔２
１との間に、コイルバネ等からなるトルク設定弾性部材
１３を組込んでいる。As shown in FIGS. 1 to 3, in this embodiment, a square shaft 22 is provided at the end of the input shaft 2 and a square hole 21 into which the square shaft 22 is fitted is provided in the output shaft 3, and the square shaft 21 is provided. Shaft 22 and square hole 2
A torque setting elastic member 13 composed of a coil spring or the like is incorporated between the first and second members.
【００２１】また、入力軸２と外側保持器８をピン２８
により一体に固定し、内側保持器７を出力軸３の外周面
に圧入して固定している。Further, the input shaft 2 and the outer cage 8 are connected to the pin 28.
, And the inner cage 7 is press-fitted and fixed to the outer peripheral surface of the output shaft 3.
【００２２】一方、図４及び図５は、クラッチ装置の要
部を示す断面図、図６はスプラグを拡大して示す図であ
り、このスプラグ１１は、内径側と外径側の端部にそれ
ぞれカム面１５と１４を備えている。On the other hand, FIG. 4 and FIG. 5 are sectional views showing the main part of the clutch device, and FIG. 6 is an enlarged view of the sprags. The sprags 11 are provided at the inner diameter side and outer diameter side ends. Each has cam surfaces 15 and 14.
【００２３】内径側のカム面１５は、Ｏ1 を中心とする
曲率半径Ｒ1 の円弧面１７で形成されている。一方、外
径側のカム面１４は、両側部が、Ｏ2 を中心とする曲率
半径Ｒ2 の円弧面１８、１８で形成され、その中央部に
フラット面１９が形成されている。このカム面１４の中
央部は、クラッチの作動時においてトルク負荷に使用さ
れない部分であり、そのフラット面１９は、両側の円弧
面１８と連続する円弧２０に対して内方側に後退してい
る。The cam surface 15 on the inner diameter side is formed by an arc surface 17 having a radius of curvature R 1 centered on O 1 . On the other hand, the outer diameter side cam surface 14 is formed by arcuate surfaces 18, 18 having a radius of curvature R 2 centered on O 2 on both sides, and a flat surface 19 is formed at the center thereof. The central portion of the cam surface 14 is a portion that is not used for torque load during the operation of the clutch, and the flat surface 19 of the cam surface 14 is retracted inward with respect to an arc 20 continuous with the arc surfaces 18 on both sides. .
【００２４】上記のスプラグ１１は、図４に示すように
外輪４と出力軸３の円筒面５、６の間に組込み、傾動し
たクラッチ噛み込み可能状態から矢印Ａ方向に回転する
外輪４の回転数が出力軸３の回転数を上回ると、内外の
カム面１４、１５の円弧面１７と円弧面１８が各円筒面
５、６に係合し、トルク負荷状態となる。As shown in FIG. 4, the sprag 11 is installed between the outer ring 4 and the cylindrical surfaces 5 and 6 of the output shaft 3 to rotate the outer ring 4 which rotates in the direction of arrow A from the tilted clutch engageable state. When the number exceeds the number of rotations of the output shaft 3, the arcuate surfaces 17 and 18 of the inner and outer cam surfaces 14 and 15 engage with the respective cylindrical surfaces 5 and 6, and a torque load state is established.
【００２５】一方、クラッチ噛み込み状態から図５の矢
印Ｂ方向に外輪４が相対回転し、クラッチが空転するよ
うになると、スプラグ１１の外径側のカム面１４と外輪
４の間にすき間が生じる。この場合、カム面１４の中央
部をフラット面１９として後退させたことにより、その
中央部と外輪４の円筒面６の間には、図１３に示す従来
構造に比べて大きなすき間ｔが形成される。このため、
クラッチ内部に異物が侵入しても、スプラグ１１と外輪
４の間で異物の噛み込みによる接触が生じず、スプラグ
の位相の逆転現象が発生しない。On the other hand, when the outer ring 4 is relatively rotated in the direction of arrow B in FIG. 5 from the clutch engaged state and the clutch is idling, there is a gap between the outer race 4 and the cam surface 14 on the outer diameter side of the sprag 11. Occurs. In this case, since the central portion of the cam surface 14 is retracted as the flat surface 19, a large gap t is formed between the central portion and the cylindrical surface 6 of the outer ring 4 as compared with the conventional structure shown in FIG. It For this reason,
Even if foreign matter enters the inside of the clutch, contact between the sprag 11 and the outer ring 4 due to biting of the foreign matter does not occur, and the phase inversion phenomenon of the sprag does not occur.
【００２６】また、図４と図１２に示すように、スプラ
グ１１の各カム面１４、１５と両円筒面５、６の接触位
置を同一にでき、スプラグの初期高さを低くする必要が
ないため、スプラグの幅寸法や左右の切替え角度を変化
させることがなく、切替りの時間や噛み込み時の衝撃を
増大させることがない。このため、トルク設定弾性部材
１３の弾性力を低く設定する必要がないため、電動パワ
ーステアリング装置への適用においてトルク伝達構造の
剛性を向上でき、操舵時のステアリングを安定させるこ
とができる。Further, as shown in FIGS. 4 and 12, the contact positions of the cam surfaces 14 and 15 of the sprag 11 and the cylindrical surfaces 5 and 6 of the sprag 11 can be made the same, and it is not necessary to lower the initial height of the sprag. Therefore, the width dimension of the sprag and the left / right switching angle are not changed, and the switching time and the impact at the time of biting are not increased. Therefore, since it is not necessary to set the elastic force of the torque setting elastic member 13 to be low, the rigidity of the torque transmission structure can be improved in application to the electric power steering device, and the steering during steering can be stabilized.
【００２７】図７は、上記実施例のクラッチ装置１を電
動パワーステアリング装置に適用した時の取付け例を示
しており、クラッチ装置１の入力軸２に、ハンドル３１
を備えるハンドル軸３２を接続し、出力軸３にラック３
９と噛み合うピニオン３８の軸４０を接続する。また、
ハンドル軸３２のねじれを検出するセンサ３４を設け、
このセンサ３４により制御装置３５を通じてモータ３６
を駆動させ、このモータ３６の回転をギヤ等の減速機３
７を介してクラッチ装置１の外輪４に伝えるようにす
る。FIG. 7 shows an example of attachment when the clutch device 1 of the above-mentioned embodiment is applied to an electric power steering device. The handle 31 is attached to the input shaft 2 of the clutch device 1.
Is connected to the handle shaft 32, and the rack 3 is attached to the output shaft 3.
The shaft 40 of the pinion 38 that meshes with 9 is connected. Also,
A sensor 34 for detecting the twist of the handle shaft 32 is provided,
This sensor 34 causes a motor 36 through a control device 35.
To drive the rotation of the motor 36 to reduce the speed of the reduction gear 3 such as a gear.
It is transmitted to the outer ring 4 of the clutch device 1 via 7.
【００２８】一方、図８及び図９はクラッチ装置の第２
の実施例を示している。この例では、入力軸２と出力軸
３にそれらを連通する軸方向の孔２３を設け、その孔２
３に、トーションバーから成るトルク設定弾性部材１３
を挿入し、このトルク設定弾性部材１３をピン２４を介
して入力軸２と出力軸３に固定している。On the other hand, FIGS. 8 and 9 show the second clutch device.
The example of is shown. In this example, an axial hole 23 that connects the input shaft 2 and the output shaft 3 to each other is provided, and the hole 2
3, a torque setting elastic member 13 including a torsion bar
And the torque setting elastic member 13 is fixed to the input shaft 2 and the output shaft 3 via a pin 24.
【００２９】また、出力軸３に角孔２１を、入力軸２に
その角孔２１に嵌合する角軸２２を設け、その角孔２１
と角軸２２の間に回転方向すき間Ｘを設けている。Further, the output shaft 3 is provided with a square hole 21, and the input shaft 2 is provided with a square shaft 22 fitted into the square hole 21.
A gap X in the direction of rotation is provided between and the angular axis 22.
【００３０】上記トルク設定弾性部材１３のばね力は、
入力軸２に一定以上の回転力が作用したとき、回転方向
すき間Ｘが無くなるまでトルク設定弾性部材１３が変形
し、入力軸２と出力軸３が係合するように設定されてい
る。The spring force of the torque setting elastic member 13 is
The torque setting elastic member 13 is deformed and the input shaft 2 and the output shaft 3 are engaged with each other until the rotational direction clearance X disappears when the input shaft 2 receives a rotational force of a certain amount or more.
【００３１】なお、上記トルク設定弾性部材１３は、図
３及び図８に示すコイルバネやトーションバーに代え
て、板ばねや他の弾性部材を使用することができる。As the torque setting elastic member 13, a leaf spring or another elastic member can be used instead of the coil spring and the torsion bar shown in FIGS. 3 and 8.
【００３２】また、上記の各実施例では、スプラグ１１
のカム面１４の中央部を、フラット面１９に形成した
が、両側の円弧面１８と連続する円弧２０より後退する
面であれば任意の形状で形成することできる。例えば、
カム面１４の中央部を、フラット面からさらにカム面の
曲率中心側にへこむ凹面で形成してもよい。In each of the above embodiments, the sprag 11
Although the central portion of the cam surface 14 is formed as the flat surface 19, it may be formed in any shape as long as it is a surface receding from the arc 20 continuous with the arc surfaces 18 on both sides. For example,
The center portion of the cam surface 14 may be formed as a concave surface that is further recessed from the flat surface toward the center of curvature of the cam surface.
【００３３】また、図１０（ａ）に示すように、スプラ
グ１１の内径側のカム面１５の中央部をフラット面１９
とし、両側部を円弧面１８、１８としてもよく、この場
合は、スプラグ１１と出力軸３の円筒面５との間の異物
噛み込みを防止することができる。さらに、図１０
（ｂ）に示すようにスプラグ１１の両端部のカム面１
４、１５の中央部に、それぞれフラット面１９、１９を
形成することもできる。Further, as shown in FIG. 10A, the central portion of the cam surface 15 on the inner diameter side of the sprag 11 is provided with a flat surface 19
Alternatively, the both sides may be arcuate surfaces 18, 18, and in this case, it is possible to prevent foreign matter from being caught between the sprag 11 and the cylindrical surface 5 of the output shaft 3. Furthermore, FIG.
As shown in (b), the cam surfaces 1 at both ends of the sprag 11
Flat surfaces 19 and 19 may be formed in the central portions of 4 and 15, respectively.
【００３４】[0034]
【効果】以上のように、この発明は、スプラグのトルク
負荷部分のカム面形状を変化させることなく、スプラグ
のカム面の中央部を後退させ、スプラグと外輪又は出力
軸との間にできるすき間を大きくしたので、スプラグの
切替り時間を変化させることなく、異物の噛み込みによ
るスプラグと外輪又は出力軸との異常接触を防止するこ
とができ、優れたクラッチの負荷耐久機能と空転機能を
維持できる。As described above, according to the present invention, the central portion of the cam surface of the sprag is retracted without changing the shape of the cam surface of the torque load portion of the sprag, and the gap formed between the sprag and the outer ring or the output shaft is formed. Since it has been made larger, it is possible to prevent abnormal contact between the sprag and the outer ring or the output shaft due to foreign matter being caught without changing the sprag switching time, and maintain the excellent load endurance function and idling function of the clutch. it can.
【００３５】また、スプラグの切替り時間が変化せず、
トルク設定弾性部材の弾性力を低く設定する必要がない
ため、このクラッチ装置を電動パワーステアリング装置
の適用した場合、トルク設定弾性部材を介して操舵する
際のステアリングを安定させることでき、ステアリング
剛性を向上させることができる。Further, the switching time of the sprag does not change,
Since it is not necessary to set the elastic force of the torque setting elastic member to a low value, when this clutch device is applied to the electric power steering device, it is possible to stabilize steering when steering through the torque setting elastic member and to improve steering rigidity. Can be improved.
【図１】実施例のクラッチ装置を示す縦断正面図FIG. 1 is a vertical sectional front view showing a clutch device according to an embodiment.
【図２】同上の縦断側面図FIG. 2 is a vertical sectional side view of the above.
【図３】図１のIII −III 線の断面図FIG. 3 is a sectional view taken along line III-III in FIG.
【図４】クラッチ装置の要部を拡大して示す断面図FIG. 4 is an enlarged cross-sectional view showing a main part of the clutch device.
【図５】同上のクラッチの空転状態を示す断面図FIG. 5 is a sectional view showing the idling state of the above clutch.
【図６】同上のスプラグの拡大図FIG. 6 is an enlarged view of the same sprag.
【図７】実施例のクラッチ装置を電動パワーステアリン
グ装置に使用した例を示す図FIG. 7 is a diagram showing an example in which the clutch device of the embodiment is used in an electric power steering device.
【図８】第２の実施例を示す縦断正面図FIG. 8 is a vertical sectional front view showing a second embodiment.
【図９】図８のＩＸ−ＩＸ線に沿った断面図9 is a sectional view taken along line IX-IX in FIG.
【図１０】（ａ）及び（ｂ）はそれぞれスプラグの他の
実施例を示す図10 (a) and 10 (b) are views showing other examples of sprags.
【図１１】電動パワーステアリング装置の概略構造を示
す図FIG. 11 is a diagram showing a schematic structure of an electric power steering device.
【図１２】従来例を示す縦断正面図FIG. 12 is a vertical sectional front view showing a conventional example.
【図１３】図１２のXIII−XIII線の断面図13 is a sectional view taken along line XIII-XIII in FIG.
【図１４】図１２のXIV −XIV 線の断面図14 is a sectional view taken along line XIV-XIV in FIG.
【図１５】従来のクラッチ構造を拡大して示す断面図FIG. 15 is an enlarged sectional view showing a conventional clutch structure.
【図１６】同上の異物噛み込み状態を示す断面図FIG. 16 is a cross-sectional view showing the same foreign matter biting state.
【図１７】他の異物噛み込み状態を示す断面図FIG. 17 is a sectional view showing another foreign matter biting state.
【図１８】他の従来例を示す断面図FIG. 18 is a cross-sectional view showing another conventional example.
１ クラッチ装置 ２ 入力軸 ３ 出力軸 ４ 外輪 ５、６ 円筒面 ７、８ 保持器 ９、１０ ポケット １１ スプラグ １２ 弾性部材 １３ トルク設定弾性部材 １４、１５ カム面 １７、１８ 円弧面 １９ フラット面 ２０ 円弧 1 Clutch device 2 Input shaft 3 Output shaft 4 Outer ring 5, 6 Cylindrical surface 7, 8 Cage 9, 9 Pocket 11 Sprag 12 Elastic member 13 Torque setting elastic member 14, 15 Cam surface 17, 18 Arc surface 19 Flat surface 20 Arc
Claims (1)
に外輪を嵌合させ、この外輪と出力軸の各対向面にそれ
ぞれ同軸の円筒面を形成し、その両円筒面間に、入力軸
に固定される保持器と、出力軸に固定される保持器を設
け、この両保持器に設けた径方向に対向するポケット
に、スプラグの両端部を挿入し、このスプラグの両端部
に、それぞれスプラグが周方向に傾いた時に上記両円筒
面に係合するカム面を設け、上記入力軸と出力軸を回転
方向すき間を介して共回り可能に連結し、この入力軸と
出力軸の間に、両軸を上記回転方向すき間の中立位置に
保持すると共に、入力軸に設定トルク以上の回転力が付
与された時に回転方向すき間がなくなるまで弾性変形す
るトルク設定弾性部材を組込んだクラッチ装置におい
て、上記スプラグの両端部の一方又は両方のカム面の両
側部を、上記両円筒面に係合する円弧面で形成し、その
カム面の中央部を、上記両側部の円弧面と連続する円弧
に対して内方側へ後退させたことを特徴とするクラッチ
装置。1. An outer ring is fitted on the outer side of an input shaft and an output shaft arranged coaxially, coaxial cylindrical surfaces are formed on respective facing surfaces of the outer ring and the output shaft, and between the cylindrical surfaces, A cage that is fixed to the input shaft and a cage that is fixed to the output shaft are provided, and both ends of the sprags are inserted into the pockets facing each other in the radial direction provided on both cages. , Providing cam surfaces that engage the cylindrical surfaces when the sprags are tilted in the circumferential direction, and rotatably connecting the input shaft and the output shaft through a gap in the rotation direction, and connecting the input shaft and the output shaft to each other. In the meantime, a clutch that holds both shafts in a neutral position in the rotational gap and that incorporates a torque setting elastic member that elastically deforms until the rotational gap disappears when a rotational force equal to or greater than the set torque is applied to the input shaft In the device, both ends of the sprag Both sides of one or both of the cam surfaces are formed with arcuate surfaces that engage with both of the cylindrical surfaces, and the center of the cam surface is inward with respect to an arc that is continuous with the arcuate surfaces of both sides. A clutch device characterized by being retracted to the side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10441793A JPH06313444A (en) | 1993-04-30 | 1993-04-30 | Clutch device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10441793A JPH06313444A (en) | 1993-04-30 | 1993-04-30 | Clutch device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06313444A true JPH06313444A (en) | 1994-11-08 |
Family
ID=14380123
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10441793A Pending JPH06313444A (en) | 1993-04-30 | 1993-04-30 | Clutch device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06313444A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011015181A1 (en) * | 2009-08-06 | 2011-02-10 | Schaeffler Technologies Gmbh & Co. Kg | Freewheel, in particular for a crank-cvt transmission |
-
1993
- 1993-04-30 JP JP10441793A patent/JPH06313444A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011015181A1 (en) * | 2009-08-06 | 2011-02-10 | Schaeffler Technologies Gmbh & Co. Kg | Freewheel, in particular for a crank-cvt transmission |
| CN102472337A (en) * | 2009-08-06 | 2012-05-23 | 舍弗勒技术两合公司 | Freewheel, in particular for a crank-cvt transmission |
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