JPH10169674A - Clutch device - Google Patents
Clutch deviceInfo
- Publication number
- JPH10169674A JPH10169674A JP8323961A JP32396196A JPH10169674A JP H10169674 A JPH10169674 A JP H10169674A JP 8323961 A JP8323961 A JP 8323961A JP 32396196 A JP32396196 A JP 32396196A JP H10169674 A JPH10169674 A JP H10169674A
- Authority
- JP
- Japan
- Prior art keywords
- input
- torque
- holding member
- output
- holding
- 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.)
- Granted
Links
Landscapes
- Braking Arrangements (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、入力部材の正回転
及び逆回転を出力部材に伝達することが可能であり、か
つ出力部材の正回転及び逆回転が入力部材に伝達されな
いようにしたクラッチ装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch capable of transmitting forward rotation and reverse rotation of an input member to an output member, and not transmitting forward rotation and reverse rotation of the output member to the input member. Related to the device.
【０００２】[0002]
【従来の技術】図１１はかかるクラッチ装置の従来例を
示すもので、８角形の断面を有する入力部材０１と、そ
の外周を囲むように配置された環状の出力部材０２との
間に、ロック部材としての８個のローラ０３…と、８個
のローラ０３…間を仕切る保持部材０４とを備えてい
る。保持部材０４の回転には所定の摩擦抵抗が与えられ
ており、（Ａ）の状態から入力部材０１が例えば矢印方
向に回転を始めた瞬間、摩擦力により停止状態にある保
持部材０４と入力部材０１との間に僅かな相対回転が生
じるため、（Ｂ）に示すように入力部材０１、出力部材
０２及び保持部材０４間の空間にローラ０３…が噛み込
み、入力部材０１の回転が出力部材０２に伝達される。
入力部材０１が逆方向に回転した場合も、前述のように
して入力部材０１から出力部材０２に回転が伝達され
る。しかしながら、出力部材０２が何れの方向に回転し
ても、ローラ０３…の噛み込みが発生しないために出力
部材０２から入力部材０１への回転の伝達は行われな
い。2. Description of the Related Art FIG. 11 shows a conventional example of such a clutch device, in which a lock is provided between an input member 01 having an octagonal cross section and an annular output member 02 arranged so as to surround the outer periphery thereof. And eight holding members 04 that partition between the eight rollers 03... A predetermined frictional resistance is given to the rotation of the holding member 04, and at the moment when the input member 01 starts to rotate in the direction of the arrow, for example, from the state of FIG. 01, a slight relative rotation occurs between the input member 01, the output member 02, and the holding member 04, as shown in FIG. 02.
Even when the input member 01 rotates in the opposite direction, the rotation is transmitted from the input member 01 to the output member 02 as described above. However, no matter which direction the output member 02 rotates, the rotation of the output member 02 to the input member 01 is not performed because the rollers 03 do not bite.
【０００３】[0003]
【発明が解決しようとする課題】ところで、保持部材０
４に与える摩擦力は入力軸０１が回転を開始してローラ
０３…の噛み込みが完了するまでの間は必要であるが、
ローラ０３…の噛み込みが完了して入力部材０１から出
力部材０２への動力伝達が開始された後は不要である。
しかしながら、上記従来のものは保持部材０４に常時摩
擦力が与えられているため、動力伝達中に保持部材０４
が前記摩擦力に抗して回転する必要があり、エネルギー
ロスが発生する問題がある。By the way, the holding member 0
4 is necessary until the input shaft 01 starts rotating and the biting of the rollers 03 is completed.
It is unnecessary after the transmission of the power from the input member 01 to the output member 02 is started after the engagement of the rollers 03 is completed.
However, in the above-mentioned conventional device, since the holding member 04 is constantly given a frictional force, the holding member 04 is not transmitted during power transmission.
However, it is necessary to rotate against the frictional force, and there is a problem that energy loss occurs.
【０００４】本発明は前述の事情に鑑みてなされたもの
で、ロック部材の確実な噛み込みが可能であり、しかも
保持部材に作用する摩擦力によるエネルギー損失を最小
限に抑えることが可能なクラッチ装置を提供することを
目的とする。[0004] The present invention has been made in view of the above circumstances, and a clutch capable of reliably engaging a lock member and minimizing energy loss due to frictional force acting on a holding member. It is intended to provide a device.
【０００５】[0005]
【課題を解決するための手段】上記目的を達成するため
に、請求項１に記載された発明では、入力部材にトルク
が入力されると、制動力制御手段により制動力を与えら
れて回転を規制された保持部材に対して入力部材が相対
回転するため、保持部材により円周方向の移動を規制さ
れたロック部材が入力部材及び出力部材間に噛み込ま
れ、入力部材のトルクが出力部材に伝達される。ロック
部材の噛み込みが完了すると、制動力制御手段により保
持部材に与えられる制動力が解除されるため、保持部材
は入力部材及び出力部材と共に自由に回転できるように
なり、摩擦抵抗によるエネルギーの損失が最小限に抑え
られる。In order to achieve the above object, according to the first aspect of the present invention, when a torque is input to an input member, a braking force is applied by a braking force control means to rotate the motor. Since the input member relatively rotates with respect to the restricted holding member, the lock member whose circumferential movement is restricted by the holding member is bitten between the input member and the output member, and the torque of the input member is applied to the output member. Is transmitted. When the engagement of the lock member is completed, the braking force applied to the holding member by the braking force control means is released, so that the holding member can freely rotate together with the input member and the output member, and energy loss due to frictional resistance. Is minimized.
【０００６】また請求項２に記載された発明では、入力
部材にトルクが入力されないとき、保持部材は摩擦部材
に当接して制動力を与えられる。入力部材にトルクが入
力されると、カム機構により保持部材が軸方向にスライ
ドして摩擦部材から離反し、、保持部材に与えられる制
動力が解除される。According to the second aspect of the invention, when no torque is input to the input member, the holding member comes into contact with the friction member to apply a braking force. When torque is input to the input member, the cam mechanism slides the holding member in the axial direction to separate from the friction member, and the braking force applied to the holding member is released.
【０００７】また請求項３に記載された発明では、入力
トルクにより二部材が相対回転すると、その一方に設け
られたピンと他方に設けられて前記ピンが係合するカム
溝とによって保持部材が軸方向にスライドする。According to the third aspect of the present invention, when the two members rotate relative to each other due to the input torque, the holding member is pivoted by the pin provided on one of the members and the cam groove provided on the other to engage the pin. Slide in the direction.
【０００８】[0008]
【発明の実施の形態】以下、本発明の実施の形態を、添
付図面に示した本発明の実施例に基づいて説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.
【０００９】図１〜図１０は本発明の一実施例を示すも
ので、図１はクラッチ装置の側面図、図２はクラッチ装
置の縦断面図（図４の２−２線断面図）、図３はクラッ
チ装置の斜視図、図４は図２の４−４線断面図、図５は
図２の５−５線断面図、図６は図２の６方向拡大矢視
図、図７〜図１０は作用の説明図である。1 to 10 show an embodiment of the present invention. FIG. 1 is a side view of a clutch device, FIG. 2 is a longitudinal sectional view of the clutch device (a sectional view taken along line 2-2 in FIG. 4), 3 is a perspective view of the clutch device, FIG. 4 is a sectional view taken along line 4-4 of FIG. 2, FIG. 5 is a sectional view taken along line 5-5 of FIG. 2, FIG. 10 are explanatory diagrams of the operation.
【００１０】図１〜図３に示すように、クラッチ装置Ｃ
はハウジング１の内部に同軸に配置された入力軸２と、
入力輪３と、出力輪４と、トーションバー５と、保持部
材６と、スライダー７とを備える。入力軸２には、軸方
向一端側から他端側に向けて入力部２1 と、フランジ部
２2 と、スライダー支持部２3 と、軸受部２4 とが順次
形成されており、軸受部２4 及びスライダー支持部２3
内に緩く挿入されたトーションバー５の一端がピン８で
入力軸２に結合される。入力輪３には、軸方向一端側か
ら他端側に向けてスライダー支持部３1 と、第１軸受部
３2 と、第２軸受部３3 とが順次形成されており、第１
軸受部３2 及び第２軸受部３3 の間からカム部３4 が半
径方向外側に延びている。第１軸受部３2 の内周面が前
記入力軸２の軸受部２4 の外周にニードルベアリング９
を介して回転自在に支持されるとともに、第２軸受部３
3 に前記トーションバー５の他端が結合される。従っ
て、入力軸２と入力輪３とは、トーションバー５の捩じ
れ分だけ相対回転可能である。As shown in FIGS. 1 to 3, the clutch device C
Is an input shaft 2 coaxially arranged inside the housing 1,
The vehicle includes an input wheel 3, an output wheel 4, a torsion bar 5, a holding member 6, and a slider 7. The input shaft 2, an input section 2 1 toward the one axial end to the other end, a flange portion 2 2, a slider supporting unit 2 3, and the bearing portion 2 4 are sequentially formed, the bearing portion 2 4, and the slider supporting part 2 3
One end of the torsion bar 5 loosely inserted into the inside is connected to the input shaft 2 by a pin 8. The input wheel 3, a slider supporting part 3 1 toward the other end from the one axial end side, a first bearing portion 3 2, and a second bearing part 3 3 are sequentially formed, the first
Cam portion 3 4 extends radially outwardly from between the bearing portions 3 2 and a second bearing part 3 3. The first needle bearing 9 inner peripheral surface of the bearing portion 3 2 is the outer periphery of the bearing portion 2 4 of the input shaft 2
Is rotatably supported through the second bearing portion 3
The other end of the torsion bar 5 is coupled to 3. Therefore, the input shaft 2 and the input wheel 3 can be relatively rotated by the amount of twist of the torsion bar 5.
【００１１】保持部材６は半径方向内側の軸受部６
1 と、軸受部６1 から半径方向外側に延びる受圧部６2
と、受圧部６2 から更に半径方向外側に延びる摩擦部６
3 と、受圧部６2 から軸方向に延びる３個のローラ保持
部６4 …（図５参照）とを備えており、軸受部６1 の内
周面が前記入力輪３の第１軸受部３2 の外周にニードル
ベアリング１０を介して回転自在に支持される。スライ
ダー７は筒状部７1 と、筒状部７1 から半径方向外側に
延びる押圧部７2 とを備えており、筒状部７1 は前記入
力軸２のスライダー支持部２3 及び前記入力輪３のスラ
イダー支持部３1 の外周に軸方向摺動自在に嵌まってい
る。保持部材６の受圧部６2 とスライダー７の押圧部７
2 とはスラストベアリング１１を挟んで相互に対向して
おり、保持部材６は入力輪３のカム部３4 との間に設け
た圧縮スプリング１２によりスライダー７に向けて付勢
されるとともに、スライダー７は入力軸２のフランジ部
２2 に固定したスプリングシート１３との間に設けた圧
縮スプリング１４により保持部材６に向けて付勢され
る。The holding member 6 includes a bearing portion 6 on the radially inner side.
1, the pressure receiving portion 6 2 which extends radially outward from the bearing portion 6 1
When the friction part 6 which extends further radially outwardly from the pressure receiving portion 6 2
3, three rollers holding portion 6 4 ... extending from the pressure receiving portion 6 2 in the axial direction (see FIG. 5) includes a first bearing portion of the inner peripheral surface of the bearing portion 61 is the input wheel 3 3 2 of the outer circumference via a needle bearing 10 is rotatably supported. Slider 7 and the cylindrical portion 71, and a pressing portion 7 2 extending radially outwardly from the cylindrical portion 71, the cylindrical portion 71 is a slider supporting part 2 3 and the input of the input shaft 2 It is fitted axially slidably on the outer periphery of the slider supporting portion 3 1 of the wheel 3. The pressing portion 7 of the pressure receiving portion 6 2 and the slider 7 of the holding member 6
The 2 faces to each other across the thrust bearing 11, the holding member 6 while being biased toward the slider 7 by a compression spring 12 provided between the cam portion 3 4 of the input wheel 3, the slider 7 is urged toward the holding member 6 by a compression spring 14 provided between the spring seat 13 fixed to the flange portion 2 second input shaft 2.
【００１２】図４を併せて参照すると明らかなように、
入力輪３のスライダー支持部３1 には直径方向に貫通す
る切欠３5 が形成されており、この切欠３5 に偏平に形
成された前記入力軸２のスライダー支持部２3 が嵌まり
合う。このとき、入力軸２と入力輪３とは、正転方向及
び逆転方向にそれぞれ角度αずつ相対回転可能である。
入力軸２に入力されるトルクが設定トルク（例えば、
０．１ｋｇｍ）になると、トーションバー前記角度αだ
け捩じれ、それ以上の捩じれが規制される。入力軸２の
スライダー支持部２3 の外周に軸方向に延びる２本のガ
イド溝３6 ，３6が形成されており、このガイド溝
３6 ，３6 にスライダー６の軸受部６1 に内向きに固定
した２本のピン１８，１８が係合する。従って、スライ
ダー７は入力軸２に対して相対回転不能かつ軸方向摺動
自在である。Referring to FIG. 4 together, it is apparent that
The slider supporting part 3 1 of the input wheel 3 is formed with notches 35 which penetrates in the radial direction, the slider supporting part 2 3 of the notch 35 to the flatly formed the input shaft 2 fits fits. At this time, the input shaft 2 and the input wheel 3 are relatively rotatable by an angle α in the normal rotation direction and the reverse rotation direction.
The torque input to the input shaft 2 is equal to the set torque (for example,
0.1 kgm), the torsion bar is twisted by the angle α, and further twisting is restricted. Slider support 2 3 periphery two guide grooves extending in the axial direction of 3 6 of the input shaft 2, 3 and 6 is formed, the guide groove 3 6, 3 6 on the inner bearing portion 61 of the slider 6 The two pins 18, 18 fixed in the direction are engaged. Therefore, the slider 7 cannot rotate relative to the input shaft 2 and can slide in the axial direction.
【００１３】図６を併せて参照すると明らかなように、
入力輪３のスライダー支持部３1 から半径方向外側に突
出するピン１９，１９が、スライダー７の筒状部７1 を
貫通するように形成した概略「く」字状のカム溝７3 ，
７3 に係合する。カム溝７3，７3 は、中央に円周方向
に延びる不感帯部ａを備えるとともに、その両端に保持
部材６に向けて左右斜め方向に延びる傾斜部ｂ，ｃを備
えている。As is apparent from FIG.
Pins 19, 19 projecting radially outwardly from the slider support section 3 of the input wheel 3, the formed outline "V" so as to penetrate the cylindrical portion 71 of the slider 7 shaped cam groove 7 3,
To engage the 7 3. Cam groove 7 3, 7 3 is provided with a dead zone portion a extending in the circumferential direction in the center, the inclined portion b extending in the left-right oblique direction toward the holding member 6 at its opposite ends, a or c.
【００１４】図２に戻り、ハウジング１の内周にリング
状の摩擦部材１５が複数のノックピン１６…及びクリッ
プ１７で回転不能に固定されており、この摩擦部材１４
に前記保持部材６の摩擦部６3 が当接可能に対向する。Returning to FIG. 2, a ring-shaped friction member 15 is fixed to the inner periphery of the housing 1 by a plurality of knock pins 16 and clips 17 so as not to rotate.
Friction unit 6 3 of the holding member 6 can come into contact opposite to.
【００１５】出力輪４は、中央の出力部４1 と、その半
径方向外側に連なる軸受部４2 と、更にその半径方向外
側に連なるローラガイド部４3 とを備えており、軸受部
４2の内周がボールベアリング２０を介して前記入力輪
３の第２軸受部３3 の外周に回転自在に支持される。The output wheel 4 is provided with a central output portion 4 1, and the bearing portion 4 2 continuous with the radially outer, further comprising a roller guide portion 4 3 connecting to the radially outer bearing portion 4 2 the inner periphery is rotatably supported on the outer periphery of the second bearing part 3 3 of the input wheel 3 via a ball bearing 20.
【００１６】図５を併せて参照すると明らかなように、
出力輪４の環状に形成されたローラガイド部４3 内周に
沿って前記保持部材６の３個のローラ保持部６4 …が１
２０°間隔で配置されて折り、その内側に前記入力輪３
のカム部３4 が配置される。各ローラ保持部６4 の両側
には２個のローラ２１，２１が配置されており、これら
ローラ２１，２１は圧縮スプリング２２によってローラ
保持部６4 に向けて付勢される。３個のローラ保持部６
4 …の内周に対向するカム部３4 の外周に、半径方向外
側に突出する３個のカム突起３7 …が形成される。ロー
ラ２１…の軸方向両端部は、出力輪４のローラガイド部
４3 と入力輪３のカム部３4 との間に配置したリング状
の軌道輪２３と、前記保持部材６とによって位置決めさ
れる（図２参照）。Referring to FIG. 5 together, it is apparent that
Three rollers holding portion 6 of the holding member 6 along the inner periphery of the roller guide portion 4 3 formed in an annular output wheel 4 4 ... 1
Folded at intervals of 20 °, the input wheel 3
Of the cam portion 3 4 is arranged. On both sides of the roller holding portion 6 4 are arranged two rollers 21 and 21, the rollers 21, 21 is biased toward the roller holding portion 6 4 by the compression spring 22. Three roller holding parts 6
4 ... on the inner circumferential periphery of the cam portion 3 4 facing the of the three cam projections 3 7 projecting radially outwardly ... are formed. Both axial ends of the roller 21 ... includes a ring-shaped bearing ring 23 arranged between the roller guide portion 4 third output wheel 4 and the cam portion 3 4 of the input wheel 3, is positioned by said holding member 6 (See FIG. 2).
【００１７】尚、前記ピン１９，１９及びカム溝７3 ，
７3 は本発明のカム機構２４を構成し、また前記入力軸
２、入力輪３、出力輪４、トーションバー５、保持部材
６、スライダー７、摩擦部材１５及びカム機構２４は本
発明の制動力制御手段２５を構成する。The pins 19, 19 and the cam grooves 7 3 ,
7 3 control of constitute a cam mechanism 24 of the present invention, also the input shaft 2, input wheel 3, the output wheel 4, the torsion bar 5, the holding member 6, the slider 7, the friction member 15 and the cam mechanism 24 according to the present invention The power control means 25 is constituted.
【００１８】次に、前述の構成を備えた本発明の実施例
の作用について説明する。尚、図７〜図１０の（Ｂ）
は、理解を容易にするために模式的に示されており、図
５に示す実際の形状とは異なっている。Next, the operation of the embodiment of the present invention having the above configuration will be described. 7B to 10B.
Are schematically shown for easy understanding, and are different from the actual shape shown in FIG.
【００１９】入力軸２にトルクが入力されないとき、図
７に示すように入力輪３のピン１９，１９はスライダー
７のカム溝７3 ，７3 の不感帯部ａ（図６参照）に位置
しており、スライダー７の押圧部７2 にスラストベアリ
ング１１を介して受圧部６2を押圧された保持部材６
は、その摩擦部６3 を摩擦部材１５に当接させた制動状
態にある。[0019] When the torque on the input shaft 2 is not input, pin 19, 19 of the input wheel 3 as shown in FIG. 7 is located in the cam groove 7 of the slider 7 3, 7 3 of the dead band section a (see FIG. 6) and the holding member is pressed pressure receiving portion 6 2 the pressing portion 7 2 of the slider 7 via the thrust bearing 11 6
Is in the braking state of being contact with the friction part 6 3 the friction member 15.
【００２０】この状態から、入力軸２に図８の矢印Ａ方
向のトルクが入力すると、入力軸２にトーションバー５
を介して接続された入力輪３のカム部３4 が図８の矢印
Ａ方向に回転する。このとき、保持部材６は摩擦部６3
を摩擦部材１５に当接させた制動状態にあるために回転
することができず、カム部３4 は停止した保持部材６の
ローラ保持部６4 …に対して相対回転する。その結果、
圧縮スプリング２２…が圧縮され、図８に斜線で示した
回転方向遅れ側の３個のローラ２１…がカム部３4 のカ
ム突起３7 …と出力輪４のローラガイド部４3 との間に
噛み込み、入力輪３、出力輪４及び保持部材６は一体に
なって矢印Ａ方向に回転する。In this state, when a torque is input to the input shaft 2 in the direction of arrow A in FIG.
Cam portion 3 4 of the input wheel 3 connected via a rotates in the direction of arrow A in FIG. 8. At this time, the holding member 6 is friction portion 6 3
The can not be rotated because of the brake being in contact with the friction member 15, the cam portion 3 4 rotates relative to the roller holder 6 4 ... of the holding member 6 has been stopped. as a result,
Compressed spring 22 ... compression, between the roller guide portion 4 3 in the rotational direction behind the roller 21 ... are of the cam portion 3 4 3 side cam projection 3 7 ... and the output wheel 4 shown by hatching in FIG. 8 , The input wheel 3, the output wheel 4, and the holding member 6 rotate integrally in the direction of arrow A.
【００２１】このようにして入力軸２から出力輪４にト
ルクが伝達されると、負荷の増加によってトーションバ
ー５が捩じれるため、入力軸２は入力輪３に対して前記
角度αだけ相対回転する。その結果、入力軸２に対して
トーションバー５の捩じれ分だけ相対回転する入力輪３
と、入力軸２に対して回転不能なスライダー７との間に
も相対回転が発生し、入力輪３に設けたピン１９，１９
がスライダー７のカム溝７3 ，７3 が不感帯部ａから傾
斜部ｂに沿って移動することにより、スライダー７が図
９の矢印Ｂ方向に移動する。而して、スライダー７が保
持部材６から離反する方向に移動し、保持部材６は圧縮
スプリング１２の弾発力でスライダー７を追う方向に移
動して摩擦部材１５から離反する。When the torque is transmitted from the input shaft 2 to the output wheel 4 as described above, the torsion bar 5 is twisted due to an increase in load, so that the input shaft 2 rotates relative to the input wheel 3 by the angle α. I do. As a result, the input wheel 3 relatively rotates with respect to the input shaft 2 by the torsion of the torsion bar 5.
Relative to the slider 7 that cannot rotate with respect to the input shaft 2, and the pins 19, 19 provided on the input wheel 3 are rotated.
There the cam groove 7 3, 7 3 of the slider 7 moves along the inclined portion b from the dead zone portion a, the slider 7 is moved in the direction of arrow B in FIG. Thus, the slider 7 moves in the direction away from the holding member 6, and the holding member 6 moves in the direction following the slider 7 by the elastic force of the compression spring 12 and separates from the friction member 15.
【００２２】入力軸２にトルクが入力されなくなると、
トーションバー５の捩じれがなくなって入力軸２と入力
輪３との相対回転、つまりスライダー７と入力輪３との
相対回転もなくなるため、ピン１９，１９がカム溝
７3 ，７3 の傾斜部ｂから不感帯部ａに復帰する。その
結果、図７に示す初期状態に復帰し、保持部材６の摩擦
部６3 は再び摩擦部材１５に当接する。When torque is no longer input to the input shaft 2,
Relative rotation between the input wheel 3 with the input shaft 2 gone torsion of the torsion bar 5, i.e. for eliminating the relative rotation between the slider 7 and the input wheel 3, pins 19, 19 cam groove 7 3, 7 3 of the inclined portion b returns to the dead zone a. As a result, it returned to the initial state shown in FIG. 7, the friction part 6 3 of the holding member 6 comes into contact with the friction member 15 again.
【００２３】尚、入力軸２に前述と逆方向のトルクが入
力された場合にも、前述と同様にして入力軸２から出力
輪４にトルクが伝達される。この場合には、ピン１９，
１９が図６の不感帯部ａから他方の傾斜部ｃに進入する
ことにより、前述と同様にして保持部材６を摩擦部材１
５から離反させることができる。When a torque in the opposite direction is input to the input shaft 2, the torque is transmitted from the input shaft 2 to the output wheel 4 in the same manner as described above. In this case, the pins 19,
19 enters the other inclined portion c from the dead zone portion a in FIG.
5 can be separated.
【００２４】一方、図１０に示すように、出力輪４側か
ら矢印Ｃ方向或いはその逆方向にトルクが入力された場
合には、出力輪４だけが回転してローラ２１…の噛み込
みは発生せず、入力軸２へのトルクの逆伝達は行われな
い。On the other hand, as shown in FIG. 10, when torque is input from the output wheel 4 side in the direction of arrow C or in the opposite direction, only the output wheel 4 rotates, and the rollers 21. No reverse transmission of torque to the input shaft 2 is performed.
【００２５】而して、入力軸２にトルクが入力された瞬
間には保持部材６に制動力を作用させてローラ２１…の
噛み込みを促進し、入力軸２から出力輪４へのトルク伝
達をスムーズに開始させることができる。そして、一旦
トルク伝達が開始されると、入力トルクによりスライダ
ー７がスライドして保持部材６を摩擦部材１５から離反
させるので、保持部材６と摩擦部材１５との間に不要な
摩擦力が発生するのを回避してエネルギー損失を最小限
に抑えることができる。At the moment when the torque is input to the input shaft 2, the braking force is applied to the holding member 6 to promote the engagement of the rollers 21, and the torque is transmitted from the input shaft 2 to the output wheel 4. Can be started smoothly. Then, once the torque transmission is started, the slider 7 slides by the input torque to separate the holding member 6 from the friction member 15, so that an unnecessary frictional force is generated between the holding member 6 and the friction member 15. And energy loss can be minimized.
【００２６】以上、本発明の実施例を詳述したが、本発
明は前記実施例に限定されるものでなく、種々の設計変
更を行うことが可能である。Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made.
【００２７】例えば、請求項１に記載された発明におい
て、電磁アクチュエータ、油圧アクチュエータ、空圧ア
クチュエータ等のアクチュエータを有する制動力制御手
段を設け、入力軸２から出力輪４への動力伝達が確認さ
れた後に前記アクチュエータで保持部材６をスライドさ
せて摩擦部材１５から離間させても良い。For example, in the first aspect of the present invention, braking force control means having an actuator such as an electromagnetic actuator, a hydraulic actuator, or a pneumatic actuator is provided, and power transmission from the input shaft 2 to the output wheel 4 is confirmed. After that, the holding member 6 may be slid by the actuator to be separated from the friction member 15.
【００２８】また実施例では保持部材６の隣接するロー
ラ保持部６4 ，６4 間に２個のローラ２１，２１と１個
の圧縮スプリング２２とを配置しているが、圧縮スプリ
ングを用いずに１個のローラだけを配置することができ
る。またロック部材はローラ２１…に限定されず、入力
輪３及び出力輪４に対する傾斜により噛み込みが発生す
る非円形のスプラグを用いることも可能である。In the embodiment, two rollers 21 and 21 and one compression spring 22 are arranged between the adjacent roller holding portions 6 4 and 6 4 of the holding member 6, but no compression spring is used. Only one roller can be arranged at a time. The lock members are not limited to the rollers 21. It is also possible to use non-circular sprags in which engagement occurs due to inclination with respect to the input wheel 3 and the output wheel 4.
【００２９】[0029]
【発明の効果】以上のように、請求項１に記載された発
明によれば、入力部材へのトルク入力開始時に保持部材
の回転を規制する制動力を発生させ、ロック部材の噛み
込み完了後に制動力を解除する制動力制御手段を備えた
ことにより、トルク入力開始時にロック部材を確実に噛
み込ませてトルク伝達をスムーズに開始させることが可
能となり、またトルク伝達が開始された後は保持部材の
制動力を解除して摩擦力によるエネルギーロスを最小限
に抑えることができる。As described above, according to the first aspect of the present invention, a braking force for regulating the rotation of the holding member is generated at the time of starting the input of torque to the input member, and after the engagement of the lock member is completed. The provision of the braking force control means for releasing the braking force makes it possible to securely engage the lock member at the start of torque input and smoothly start torque transmission, and to maintain the torque transmission after it has been started. Energy loss due to frictional force can be minimized by releasing the braking force of the member.
【００３０】また請求項２に記載された発明によれば、
制動力制御手段は、入力部材に加わる入力トルクにより
保持部材を軸方向にスライドさせるカム機構と、入力ト
ルクの不作用時に保持部材に当接して制動力を発生する
摩擦部材とを備えてなり、入力トルクの作用時に保持部
材を軸方向にスライドさせて摩擦部材から離反させるの
で、カム機構と摩擦板とを用いた簡単な構造で保持部材
の制動力を制御することができる。According to the second aspect of the present invention,
The braking force control means includes a cam mechanism that slides the holding member in the axial direction by an input torque applied to the input member, and a friction member that generates a braking force by contacting the holding member when no input torque is applied, When the input torque is applied, the holding member is slid in the axial direction and separated from the friction member, so that the braking force of the holding member can be controlled with a simple structure using the cam mechanism and the friction plate.
【００３１】また請求項３に記載された発明によれば、
カム機構は、入力トルクにより相対回転する二部材の一
方に設けられたピンと、他方に設けられて前記ピンが係
合するカム溝とから構成されるので、回転方向のトルク
を軸方向の推力に変換してスライダーを確実にスライド
させることができる。According to the invention described in claim 3,
The cam mechanism is composed of a pin provided on one of the two members that relatively rotate by the input torque, and a cam groove provided on the other and engaged with the pin, so that the torque in the rotational direction is converted to the thrust in the axial direction. By converting, the slider can be reliably slid.
【図１】クラッチ装置の側面図FIG. 1 is a side view of a clutch device.
【図２】クラッチ装置の縦断面図（図４の２−２線断面
図）FIG. 2 is a longitudinal sectional view of the clutch device (a sectional view taken along line 2-2 in FIG. 4).
【図３】クラッチ装置の斜視図FIG. 3 is a perspective view of a clutch device.
【図４】図２の４−４線断面図FIG. 4 is a sectional view taken along line 4-4 in FIG. 2;
【図５】図２の５−５線断面図FIG. 5 is a sectional view taken along line 5-5 of FIG. 2;
【図６】図２の６方向拡大矢視図FIG. 6 is an enlarged view in the direction of arrow 6 in FIG. 2;
【図７】入力軸にトルクが入力されないときの作用説明
図FIG. 7 is an explanatory diagram of an operation when torque is not input to the input shaft.
【図８】入力軸にトルクが入力された瞬間の作用説明図FIG. 8 is a diagram illustrating an operation at the moment when torque is input to the input shaft.
【図９】入力軸から出力輪にトルクが伝達されていると
きの作用説明図FIG. 9 is an operation explanatory diagram when torque is transmitted from the input shaft to the output wheel.
【図１０】出力輪にトルクが伝達されたときの作用説明
図FIG. 10 is an explanatory diagram of an operation when torque is transmitted to an output wheel.
【図１１】従来のクラッチ装置の縦断面図FIG. 11 is a longitudinal sectional view of a conventional clutch device.
３ 入力輪（入力部材） ４ 出力輪（出力部材） ６ 保持部材 ７3 カム溝 １５ 摩擦部材 １９ ピン ２１ ローラ（ロック部材） ２４ カム機構 ２５ 制動力制御手段Reference Signs List 3 input wheel (input member) 4 output wheel (output member) 6 holding member 7 3 cam groove 15 friction member 19 pin 21 roller (lock member) 24 cam mechanism 25 braking force control means
───────────────────────────────────────────────────── フロントページの続き (72)発明者 有村 豊 埼玉県和光市中央１丁目４番１号 株式会 社本田技術研究所内 ──────────────────────────────────────────────────の Continued on the front page (72) Inventor Yutaka Arimura 1-4-1 Chuo, Wako-shi, Saitama
Claims (3)
在な入力部材（３）と、半径方向内外の他方に配置され
た回転自在な出力部材（４）と、入力部材（３）及び出
力部材（４）間に噛み込み可能な複数のロック部材（２
１）と、入力部材（３）及び出力部材（４）間に回転自
在に配置され、ロック部材（２１）の円周方向の移動を
規制して該ロック部材（２１）の噛み込みを補助する保
持部材（６）とを備えてなり、入力部材（３）にトルク
が入力されたときには、ロック部材（２１）の噛み込み
を発生させてトルクを出力部材（４）に伝達するととも
に、出力部材（４）にトルクが入力されたときには、ロ
ック部材（２１）の噛み込みを発生させずにトルクを入
力部材（３）に伝達しないようにしたクラッチ装置にお
いて、 入力部材（３）へのトルク入力開始時に前記保持部材
（６）の回転を規制する制動力を発生させ、ロック部材
（２１）の噛み込み完了後に前記制動力を解除する制動
力制御手段（２５）を備えたことを特徴とするクラッチ
装置。1. A rotatable input member (3) disposed on one of the radially inner and outer sides, a rotatable output member (4) disposed on the other of the radially inner and outer sides, an input member (3) and an output. A plurality of lock members (2
1) and is rotatably arranged between the input member (3) and the output member (4) to regulate the circumferential movement of the lock member (21) to assist in the engagement of the lock member (21). When torque is input to the input member (3), the lock member (21) is engaged to transmit the torque to the output member (4), and to output the torque to the output member (4). When a torque is input to the input member (3), the torque is not transmitted to the input member (3) without causing the lock member (21) to bite. At the start, a braking force controlling means (25) for generating a braking force for regulating the rotation of the holding member (6) and releasing the braking force after the engagement of the lock member (21) is completed is provided. Clutch device.
材（３）に加わる入力トルクにより保持部材（６）を軸
方向にスライドさせるカム機構（２４）と、入力トルク
の不作用時に保持部材（６）に当接して制動力を発生す
る摩擦部材（１５）とを備えてなり、入力トルクの作用
時に保持部材（６）を軸方向にスライドさせて摩擦部材
（１５）から離反させることを特徴とする、請求項１記
載のクラッチ装置。2. The braking force control means (25) includes a cam mechanism (24) for sliding the holding member (6) in an axial direction by an input torque applied to the input member (3), and a holding mechanism when the input torque is not applied. A friction member (15) that generates a braking force by contacting the member (6), and slides the holding member (6) in the axial direction when the input torque is applied to separate the holding member (6) from the friction member (15). The clutch device according to claim 1, wherein:
より相対回転する二部材の一方に設けられたピン（１
９）と、他方に設けられて前記ピン（１９）が係合する
カム溝（７3 ）とから構成されることを特徴とする、請
求項２記載のクラッチ装置。3. The cam mechanism (24) includes a pin (1) provided on one of two members relatively rotated by an input torque.
3. The clutch device according to claim 2, wherein the clutch device comprises a cam groove (7 3 ) provided on the other side and engaged with the pin (19).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32396196A JP3631866B2 (en) | 1996-12-04 | 1996-12-04 | Clutch device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32396196A JP3631866B2 (en) | 1996-12-04 | 1996-12-04 | Clutch device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10169674A true JPH10169674A (en) | 1998-06-23 |
| JP3631866B2 JP3631866B2 (en) | 2005-03-23 |
Family
ID=18160569
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32396196A Expired - Fee Related JP3631866B2 (en) | 1996-12-04 | 1996-12-04 | Clutch device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3631866B2 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2001027486A1 (en) * | 1999-10-14 | 2001-04-19 | Koyo Seiko Co., Ltd. | Clutch device |
| JP2003097605A (en) * | 2001-09-25 | 2003-04-03 | Ntn Corp | Clutch unit |
| JP2004314452A (en) * | 2003-04-16 | 2004-11-11 | Makita Corp | Chain saw |
| JP2005188742A (en) * | 2003-12-02 | 2005-07-14 | Pentax Corp | One-way input/output rotation transmission mechanism |
| EP1457414A3 (en) * | 2003-03-11 | 2007-07-18 | Ntn Corporation | Electric assisted bicycle |
| JP2008267437A (en) * | 2007-04-17 | 2008-11-06 | Ntn Corp | Normal-reverse driving force change-over device |
| JP2012101786A (en) * | 2010-11-10 | 2012-05-31 | Faurecia Sieges D'automobile | Adjustment mechanism for vehicle seat |
| DE102008061606B4 (en) * | 2007-12-13 | 2017-05-04 | Asmo Co., Ltd. | Brake device and engine with speed reduction mechanism |
| JP2019108983A (en) * | 2017-12-19 | 2019-07-04 | フスコ オートモーティブ ホールディングス エル・エル・シーＨＵＳＣＯ Ａｕｔｏｍｏｔｉｖｅ Ｈｏｌｄｉｎｇｓ ＬＬＣ | Systems and methods for two-way clutch with predetermined interference |
| JP2019173893A (en) * | 2018-03-29 | 2019-10-10 | トヨフレックス株式会社 | Restiform body brake |
-
1996
- 1996-12-04 JP JP32396196A patent/JP3631866B2/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6464061B1 (en) | 1999-10-14 | 2002-10-15 | Koyo Seiko Co., Ltd. | Clutch device |
| WO2001027486A1 (en) * | 1999-10-14 | 2001-04-19 | Koyo Seiko Co., Ltd. | Clutch device |
| JP2003097605A (en) * | 2001-09-25 | 2003-04-03 | Ntn Corp | Clutch unit |
| EP1457414A3 (en) * | 2003-03-11 | 2007-07-18 | Ntn Corporation | Electric assisted bicycle |
| JP2004314452A (en) * | 2003-04-16 | 2004-11-11 | Makita Corp | Chain saw |
| JP4593251B2 (en) * | 2003-12-02 | 2010-12-08 | Ｈｏｙａ株式会社 | Unidirectional input / output rotation transmission mechanism |
| JP2005188742A (en) * | 2003-12-02 | 2005-07-14 | Pentax Corp | One-way input/output rotation transmission mechanism |
| JP2008267437A (en) * | 2007-04-17 | 2008-11-06 | Ntn Corp | Normal-reverse driving force change-over device |
| WO2008133045A1 (en) * | 2007-04-17 | 2008-11-06 | Ntn Corporation | Device for switching direction of driving force between normal and reverse directions |
| US8505404B2 (en) | 2007-04-17 | 2013-08-13 | Ntn Corporation | Switching device for switching driving force between forward and reverse directions |
| DE102008061606B4 (en) * | 2007-12-13 | 2017-05-04 | Asmo Co., Ltd. | Brake device and engine with speed reduction mechanism |
| JP2012101786A (en) * | 2010-11-10 | 2012-05-31 | Faurecia Sieges D'automobile | Adjustment mechanism for vehicle seat |
| KR101290723B1 (en) * | 2010-11-10 | 2013-07-29 | 포레시아 시에쥐 도또모빌 | Adjustment mechanism for vehicle seat |
| JP2019108983A (en) * | 2017-12-19 | 2019-07-04 | フスコ オートモーティブ ホールディングス エル・エル・シーＨＵＳＣＯ Ａｕｔｏｍｏｔｉｖｅ Ｈｏｌｄｉｎｇｓ ＬＬＣ | Systems and methods for two-way clutch with predetermined interference |
| JP2019173893A (en) * | 2018-03-29 | 2019-10-10 | トヨフレックス株式会社 | Restiform body brake |
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