JP4275905B2

JP4275905B2 - Clutch device

Info

Publication number: JP4275905B2
Application number: JP2002174214A
Authority: JP
Inventors: 直人神保
Original assignee: Nifco Inc
Current assignee: Nifco Inc
Priority date: 2002-06-14
Filing date: 2002-06-14
Publication date: 2009-06-10
Anticipated expiration: 2022-06-14
Also published as: JP2004019757A; CN1467389A; KR100520676B1; KR20030095965A; CN1216236C

Description

【０００１】
【発明の属する技術分野】
本発明は、クラッチ装置に関し、特に被動側から駆動側が逆駆動されることを防止するための一方向クラッチとして用いるのに適したクラッチ装置に関するものである。
【０００２】
【従来の技術】
ファクシミリ装置やコピー機にあっては、所定の条件で給紙ローラを選択的に回転、停止させるために、モータの回転トルクが常時与えられる被動ギアと給紙ローラとの間にクラッチ装置が設けられている。このためのクラッチ装置として、遊星ギアを用いた一方向クラッチが知られている（実開平５−２２８６７号公報参照）。
【０００３】
この形式のクラッチ装置は、図７に示すように、内歯リングギア２２が形成されたアウタ部材１２と、アウタ部材１２と同軸上で回転自在に支持され且つ外周に複数（例えば３ヶ所）の凹所２３が形成されたインナ部材１１と、各凹所２３に回転自在に受容され且つ内歯リングギア２２にそれぞれが噛合する３つの遊星ギア１３とを有しており、例えばアウタ部材１２に右回りの駆動力が加わると、凹所２３の開口に形成されたエッジ２４に遊星ギア１３の歯が食い込んでアウタ部材１２の駆動力がインナ部材１１に伝達され、インナ部材１１に右回りの駆動力が加わると、エッジ２４に対する遊星ギア１３の食い込みが解除されてインナ部材１１からアウタ部材１２への駆動力伝達が断たれるようになっている。
【０００４】
【発明が解決しようとする課題】
上記形式のクラッチ装置は、３つの凹所の輪郭形状が互いに等しくされ、且つ円周を３等分する位置に設けられることが通例であった。また、内歯リングギアの歯数と凹所の数との関係にも格別な考慮が払われているわけではなかった。そのため、３個の遊星ギアを用いているにも関わらず、実際にエッジに歯が食い込むギアはその内の１つ（図７においては頂点に位置するもの）に過ぎなかった。
【０００５】
つまり、従来の遊星ギア式クラッチ装置によると、クラッチ接続状態でのトルク伝達に寄与する遊星ギアは１つでしかないため、伝達トルク容量を増大するには遊星ギアの歯厚あるいは歯幅を大きくするしかなく、大型化せずに伝達トルク容量を増大することが困難であった。
【０００６】
本発明は、このような従来技術の問題点を解消すべく案出されたものであり、その主な目的は、クラッチ装置を大型化せずに伝達トルク容量を増大させることが可能なように改良されたクラッチ装置を提供することにある。
【０００７】
【課題を解決するための手段】
このような目的を果たすために、本発明のクラッチ装置は、アウタ部材（１２）に設けられた内歯リングギア（２２）に噛合して転動する遊星ギア（１３）を、インナ部材（１１）に設けられた凹所（２３）内に回転自在に受容し、且つ凹所に形成されたエッジ（２４）に遊星ギアの歯の一部が係合するとアウタ部材とインナ部材とが一体回転し、エッジに対する遊星ギアの歯の一部の係合が解除されるとアウタ部材とインナ部材とが相対回転するようにしてなるクラッチ装置（４）において、前記複数の凹所の各エッジは、同一円周上に等間隔に配置され、前記複数の遊星ギアは、各々、前記アウタ部材及び前記インナ部材に回転自在に支持された遊星ギアベース（１６）に設けられた軸（１５）に各々回転自在に設けられ、前記内歯リングギアの歯数を前記凹所の数の整数倍とされ、前記遊星ギアの歯の一部が前記エッジに係合する動作が、前記凹所と前記遊星ギアとの組の全てについて同時に行われるものである。
【０００８】
このようにすれば、複数の遊星ギアに伝達トルクが分散されるので、１つ当たりの遊星ギアの負担を軽減することができる。
【００１０】
【発明の実施の形態】
以下に添付の図面を参照して本発明について詳細に説明する。
【００１１】
図１は、本発明によるクラッチ装置が適用されるファクシミリ装置などにおける給紙機構の一部を模式的に示す斜視図である。この給紙機構１は、モータの駆動軸（図示せず）に直結されたピニオン２と、ピニオン２に噛合した被動ギア３と、被動ギア３にクラッチ装置４を介して連結された給紙ローラ５とからなっている。この給紙機構１においては、ファクシミリ装置の運転中はピニオン２が常時回転しており、被動ギア３から給紙ローラ５へのトルク伝達が、ソレノイド式ロック機構６の作用で作動するクラッチ装置４によって断続される。
【００１２】
図２〜図４は、本発明によるクラッチ装置４を示している。このクラッチ装置４は、例えばキー手段をもって給紙ローラ５の中心軸７に結合されるインナ部材１１と、インナ部材１１に回転自在に支持されたアウタ部材１２と、インナ部材１１とアウタ部材１２との間に設けられた遊星ギア１３と、その円板部１４に突設された軸１５上に遊星ギア１３を回転自在に支持した状態でインナ部材１１及びアウタ部材１２に回転自在に支持された遊星ギアベース１６と、遊星ギアベース１６の筒状軸部１７に軸方向移動不能に且つ回転自在に支持されたクラッチ解除部材１８と、遊星ギアベース１６とクラッチ解除部材１８との間を弾発力を伴って連動連結すべく遊星ギアベース１６の筒状軸部１７に巻装された捻りばね１９とからなっている。
【００１３】
アウタ部材１２には、ピニオン２に噛合する外歯リングギアをなす被動ギア３がその外周面に形成され、且つ遊星ギア１３が噛合する内歯リングギア２２がその内周面に形成されている。
【００１４】
インナ部材１１の外周部には、半径方向外向きに開放された概ね半円形の凹所２３が円周を３等分する位置のそれぞれに設けられている。これら３つの凹所２３には、遊星ギアベース１６に支持され、且つ内歯リングギア２２に噛合した状態の遊星ギア１３が受容されている。また各凹所２３の開口における円周方向についての一方（アウタ部材１２の回転方向の前側）は、インナ部材１１の外接円の接線に平行し、且つ遊星ギア１３の中心を通る面Ｓに沿って切除されており、これにより、遊星ギア１３の歯の１つが噛み込むエッジ２４が３つの凹所２３のそれぞれに形成されている。
【００１５】
クラッチ装置４には、上記の通り、ソレノイド式ロック機構６が付設されている。このロック機構６は、実質的に回動不能なステー部材３１に固設されたソレノイド３２と、ソレノイドベース３３にその一端をヒンジ結合し、且つクラッチ解除部材１８にその他端を接する向きにコイルばね３４で弾発付勢されたストッパ部材３５とからなっている。
【００１６】
そしてクラッチ解除部材１８には、突出時のストッパ部材３５の他端と係合可能な半径方向突条２７が、円周方向の適宜な位置に設けられている。
【００１７】
次に本発明装置の作動要領について説明する。
【００１８】
通常は、モータ軸に直結されたピニオン２を介して外歯リングギアからなる被動ギア３、即ちアウタ部材１２にモータの駆動力が加わり、モータの運転中はアウタ部材１２は常に回転している。
【００１９】
他方、ソレノイド３２は所定の条件で電流が断続され、励磁すると、アーマチュアとしてのストッパ部材３５がソレノイド３２のコアに吸着されるので、クラッチ解除部材１８の突条２７からストッパ部材３５の他端が離れてクラッチ解除部材１８の回転が許容され（図２の実線の状態）、消磁すると、コイルばね３４の弾発力によってストッパ部材３５の他端がクラッチ解除部材１８の突条２７に係合し（図２の想像線の状態）、クラッチ解除部材１８の回転が阻止されるようになっている。
【００２０】
ソレノイド３２が励磁状態にあり、クラッチ解除部材１８の突条２７からストッパ部材３５が離れた状態では、捻りばね１９を介してクラッチ解除部材１８と連動連結された遊星ギアベース１６もクラッチ解除部材１８と共に自由である。この状態では、捻りばね１９には荷重が加わらないので、反力も発生しない。
【００２１】
アウタ部材１２には、図４における矢印Ａの方向、つまり右回転のトルクが常時作用しているので、内歯リングギア２１との噛み合いで遊星ギア１３が右回転すると、遊星ギア１３は、凹所２３における回転方向に対して後側の側壁から離間して凹所２３の開口に設けられたエッジ２４に歯を食い込ませる。これにより、インナ部材１１とアウタ部材１２とが遊星ギア１３を介して一体的に結合し、モータの駆動力はインナ部材１１に結合された給紙ローラ５に伝達される。
【００２２】
ソレノイド３２を消磁すると、ストッパ部材３５の他端がクラッチ解除部材１８側に接近する。そしてストッパ部材３５の他端に突条２７が引っ掛かると、クラッチ解除部材１８が停止させられる。
【００２３】
ここでクラッチ解除部材１８と遊星ギアベース１６との間が捻りばね１９を介して弾性的に結合しているので、クラッチ解除部材１８が回転を停止すると、捻りばね１９が撓むことで凹所２３のエッジ２４に対する遊星ギア１３の歯の食い込み力が緩む。すると捻りばね１９の押圧力は、遊星ギア１３を凹所２３における回転方向に対して後側の側壁に近接させる向き、つまりエッジ２４から歯を離間させる向きに作用しているので、凹所２３のエッジ２４に対する遊星ギア１３の歯の食い込みが完全に外れる。
【００２４】
これにより、インナ部材１１とアウタ部材１２との間のトルク伝達が断たれ、アウタ部材１２が空転して給紙ローラ５は停止することとなる。
【００２５】
さて、１つ当たりの遊星ギア１３の負担を軽減してクラッチ装置４の実質的な伝達トルク容量を増大するために、本発明においては、３つの遊星ギア１３が対応するエッジ２４に同時に食い込み得るようにした。具体的には、図５に示したように、３つの凹所２３の各エッジ２４を同一円周上に等間隔（Ａ＝Ｂ＝Ｃ＝１２０°）に配置し、且つ内歯リングギア２２の歯数を、凹所２３の数（３）の整数倍、例えば４８枚とした。これにより、３つの遊星ギア１３の回転角度が互いに同期するので、同一円周上に等間隔に配置された３つの凹所２３の各エッジ２４に３つの遊星ギア１３の歯が同時に食い込むこととなる。
【００２６】
この３つの凹所２３の各エッジ２４に３つの遊星ギア１３の歯を同時に食い込ませる手法としては、図６に示したように、３つの遊星ギア１３同士間の回転角度の違いに対応させ、３つの凹所２３の各エッジ２４の径方向位置を等しく（ａ＝ｂ＝ｃ）して周方向間隔を不等長（Ａ≠Ｂ≠Ｃ）にしたり、あるいは３つの凹所２３の各エッジ２４の周方向間隔を等しく（Ａ＝Ｂ＝Ｃ）して径方向位置を不等（ａ≠ｂ≠ｃ）にしたりすることでも良い。
【００２７】
【発明の効果】
以上詳述した通り本発明によれば、複数の遊星ギアに伝達トルクが分散されるので、１つ当たりの遊星ギアの負担を軽減することができることから、遊星ギアの歯のサイズを大きくせずに伝達トルク容量を増大することができる。従って、本発明により、大型化を伴わずにクラッチ装置の伝達トルク容量を増大する上に多大な効果を奏することができる。
【図面の簡単な説明】
【図１】本発明が適用される給紙ローラの駆動機構の概略斜視図
【図２】本発明によるクラッチ装置のソレノイド式ロック機構を装着した状態の上面図
【図３】本発明によるクラッチ装置の図４中のIII−III線に沿う縦断面図
【図４】本発明によるクラッチ装置の下半分を図３中のIV−IV線に沿って切除して示す側面図
【図５】本発明の一実施例によるクラッチ接続状態を示す各部の関係説明図
【図６】本発明の別の実施例によるクラッチ接続状態を示す各部の関係説明図
【図７】従来のクラッチ接続状態を示す各部の関係説明図
【符号の説明】
１給紙機構
２ピニオン
３被動ギア
４クラッチ装置
５給紙ローラ
６ソレノイド式ロック機構
７中心軸
１１インナ部材
１２アウタ部材
１３遊星ギア
１４円板部
１５軸
１６遊星ギアベース
１７筒状軸部
１８クラッチ解除部材
１９捻りばね
２２内歯リングギア
２３凹所
２４エッジ[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a clutch device, and more particularly to a clutch device suitable for use as a one-way clutch for preventing a drive side from being driven reversely from a driven side.
[0002]
[Prior art]
In facsimile machines and copiers, a clutch device is provided between a driven gear to which a rotational torque of a motor is constantly applied and a paper feed roller in order to selectively rotate and stop the paper feed roller under predetermined conditions. It has been. A one-way clutch using a planetary gear is known as a clutch device for this purpose (see Japanese Utility Model Laid-Open No. 5-22867).
[0003]
As shown in FIG. 7, this type of clutch device includes an outer member 12 having an internal ring gear 22 formed thereon, and is rotatably supported coaxially with the outer member 12 and a plurality of (for example, three) outer peripheral members. The inner member 11 having the recesses 23 and the three planetary gears 13 rotatably received in the respective recesses 23 and meshing with the internal ring gears 22 are provided. When the clockwise driving force is applied, the teeth of the planetary gear 13 bite into the edge 24 formed in the opening of the recess 23 and the driving force of the outer member 12 is transmitted to the inner member 11, and the clockwise rotation is applied to the inner member 11. When driving force is applied, the planetary gear 13 bites into the edge 24 is released, and transmission of driving force from the inner member 11 to the outer member 12 is cut off.
[0004]
[Problems to be solved by the invention]
The clutch device of the above type is usually provided at a position where the contour shapes of the three recesses are equal to each other and the circumference is equally divided into three. Also, no special consideration has been given to the relationship between the number of teeth of the internal ring gear and the number of recesses. Therefore, even though three planetary gears are used, only one of the gears (the one located at the apex in FIG. 7) whose teeth actually bite into the edge is present.
[0005]
In other words, according to the conventional planetary gear type clutch device, there is only one planetary gear that contributes to torque transmission in the clutch engaged state, so in order to increase the transmission torque capacity, the planetary gear tooth thickness or tooth width is increased. However, it is difficult to increase the transmission torque capacity without increasing the size.
[0006]
The present invention has been devised to solve such problems of the prior art, and its main purpose is to increase the transmission torque capacity without increasing the size of the clutch device. An object of the present invention is to provide an improved clutch device.
[0007]
[Means for Solving the Problems]
In order to achieve such an object, the clutch device of the present invention is configured so that the planetary gear (13) that meshes with the internal ring gear (22) provided on the outer member (12) rolls to the inner member (11). The outer member and the inner member rotate together when a part of the teeth of the planetary gear engages with the edge (24) formed in the recess. In the clutch device (4) in which the outer member and the inner member rotate relative to each other when the engagement of a part of the teeth of the planetary gear with respect to the edge is released, each edge of the plurality of recesses includes: are arranged at equal intervals on the same circumference, said plurality of planet gears, each respectively, to the axis (15) provided in the outer member and rotatably supported planet gear base on said inner member (16) The internal tooth phosphorus The number of teeth of the gear is an integral multiple of the number of the recesses, and the operation of engaging a part of the teeth of the planetary gear with the edge is performed simultaneously for all the pairs of the recesses and the planetary gear. Is.
[0008]
In this way, since the transmission torque is distributed to the plurality of planetary gears, the burden on each planetary gear can be reduced.
[0010]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.
[0011]
FIG. 1 is a perspective view schematically showing a part of a paper feed mechanism in a facsimile machine to which a clutch device according to the present invention is applied. The paper feed mechanism 1 includes a pinion 2 directly connected to a drive shaft (not shown) of a motor, a driven gear 3 meshed with the pinion 2, and a paper feed roller connected to the driven gear 3 via a clutch device 4. It consists of five. In this paper feed mechanism 1, the pinion 2 is always rotating during operation of the facsimile machine, and the clutch device 4 in which torque transmission from the driven gear 3 to the paper feed roller 5 is activated by the action of the solenoid type lock mechanism 6. Interrupted by.
[0012]
2 to 4 show a clutch device 4 according to the present invention. The clutch device 4 includes, for example, an inner member 11 coupled to the central shaft 7 of the paper feed roller 5 with key means, an outer member 12 rotatably supported by the inner member 11, an inner member 11 and an outer member 12. The planetary gear 13 provided between the inner member 11 and the outer member 12 is rotatably supported in a state where the planetary gear 13 is rotatably supported on the shaft 15 protruding from the disk portion 14. The planetary gear base 16, the clutch release member 18 that is supported on the cylindrical shaft portion 17 of the planetary gear base 16 so as not to be axially movable and rotatable, and between the planetary gear base 16 and the clutch release member 18 The torsion spring 19 is wound around the cylindrical shaft portion 17 of the planetary gear base 16 so as to be interlocked with force.
[0013]
The outer member 12 has a driven gear 3 that forms an external ring gear meshing with the pinion 2 formed on the outer peripheral surface thereof, and an internal tooth ring gear 22 that meshes with the planetary gear 13 formed on the inner peripheral surface thereof. .
[0014]
On the outer peripheral portion of the inner member 11, a substantially semicircular recess 23 opened outward in the radial direction is provided at each position where the circumference is equally divided into three. The three recesses 23 receive the planetary gear 13 that is supported by the planetary gear base 16 and meshed with the internal ring gear 22. Further, one of the openings of the recesses 23 in the circumferential direction (the front side in the rotation direction of the outer member 12) is parallel to the tangent to the circumscribed circle of the inner member 11 and is along a plane S passing through the center of the planetary gear 13. As a result, an edge 24 into which one of the teeth of the planetary gear 13 is engaged is formed in each of the three recesses 23.
[0015]
As described above, the solenoid lock mechanism 6 is attached to the clutch device 4. The lock mechanism 6 includes a solenoid 32 fixed to a substantially non-rotatable stay member 31 and a coil spring in a direction in which one end is hinged to the solenoid base 33 and the other end is in contact with the clutch release member 18. And a stopper member 35 which is urged and urged by a spring 34.
[0016]
The clutch release member 18 is provided with a radial protrusion 27 that can be engaged with the other end of the stopper member 35 when protruding, at an appropriate position in the circumferential direction.
[0017]
Next, the operating procedure of the device of the present invention will be described.
[0018]
Normally, the driving force of the motor is applied to the driven gear 3, that is, the outer member 12, which is an external ring gear through the pinion 2 directly connected to the motor shaft, and the outer member 12 is always rotating during operation of the motor. .
[0019]
On the other hand, when the solenoid 32 is energized and energized under a predetermined condition, the stopper member 35 as an armature is attracted to the core of the solenoid 32, so that the other end of the stopper member 35 extends from the protrusion 27 of the clutch release member 18. When the clutch releasing member 18 is allowed to rotate away (solid line in FIG. 2) and demagnetized, the other end of the stopper member 35 is engaged with the protrusion 27 of the clutch releasing member 18 by the elastic force of the coil spring 34. (The state of the imaginary line in FIG. 2), the rotation of the clutch release member 18 is prevented.
[0020]
When the solenoid 32 is in an excited state and the stopper member 35 is separated from the protrusion 27 of the clutch release member 18, the planetary gear base 16 that is linked to the clutch release member 18 via the torsion spring 19 is also connected to the clutch release member 18. And freedom. In this state, since no load is applied to the torsion spring 19, no reaction force is generated.
[0021]
Since the outer member 12 is always applied with the torque in the direction of arrow A in FIG. 4, that is, clockwise rotation, when the planetary gear 13 rotates clockwise by meshing with the internal ring gear 21, the planetary gear 13 is recessed. The tooth is bitten into the edge 24 provided in the opening of the recess 23 so as to be separated from the rear side wall with respect to the rotation direction at the location 23. As a result, the inner member 11 and the outer member 12 are integrally coupled via the planetary gear 13, and the driving force of the motor is transmitted to the paper feeding roller 5 coupled to the inner member 11.
[0022]
When the solenoid 32 is demagnetized, the other end of the stopper member 35 approaches the clutch release member 18 side. When the protrusion 27 is caught on the other end of the stopper member 35, the clutch release member 18 is stopped.
[0023]
Here, since the clutch release member 18 and the planetary gear base 16 are elastically coupled via the torsion spring 19, when the clutch release member 18 stops rotating, the torsion spring 19 bends to cause a recess. The tooth biting force of the planetary gear 13 with respect to the edge 24 of 23 is loosened. Then, the pressing force of the torsion spring 19 acts in the direction in which the planetary gear 13 is brought closer to the rear side wall with respect to the rotation direction in the recess 23, that is, in the direction in which the teeth are separated from the edge 24. The teeth of the planetary gear 13 are completely disengaged from the edge 24.
[0024]
As a result, torque transmission between the inner member 11 and the outer member 12 is cut off, the outer member 12 idles, and the paper feed roller 5 stops.
[0025]
Now, in order to reduce the burden of one planetary gear 13 and increase the substantial transmission torque capacity of the clutch device 4, in the present invention, the three planetary gears 13 can bite into the corresponding edges 24 simultaneously. I did it. Specifically, as shown in FIG. 5, the edges 24 of the three recesses 23 are arranged on the same circumference at equal intervals (A = B = C = 120 °), and the internal ring gear 22 The number of teeth was an integral multiple of the number (3) of the recesses 23, for example, 48. Thereby, since the rotation angles of the three planetary gears 13 are synchronized with each other, the teeth of the three planetary gears 13 bite into the respective edges 24 of the three recesses 23 arranged at equal intervals on the same circumference at the same time. Become.
[0026]
As a method of simultaneously biting the teeth of the three planetary gears 13 into the respective edges 24 of the three recesses 23, as shown in FIG. 6, it is made to correspond to the difference in rotation angle between the three planetary gears 13, The radial positions of the edges 24 of the three recesses 23 are made equal (a = b = c) to make the circumferential intervals unequal (A ≠ B ≠ C), or the edges of the three recesses 23 The circumferential intervals of 24 may be equal (A = B = C), and the radial positions may be unequal (a ≠ b ≠ c).
[0027]
【The invention's effect】
As described above in detail, according to the present invention, the transmission torque is distributed to a plurality of planetary gears, so that the burden on each planetary gear can be reduced. Therefore, the size of the planetary gear teeth is not increased. In addition, the transmission torque capacity can be increased. Therefore, according to the present invention, a great effect can be obtained in increasing the transmission torque capacity of the clutch device without increasing the size.
[Brief description of the drawings]
FIG. 1 is a schematic perspective view of a driving mechanism of a paper feed roller to which the present invention is applied. FIG. 2 is a top view of a clutch device according to the present invention with a solenoid lock mechanism installed. Fig. 4 is a longitudinal sectional view taken along line III-III in Fig. 4. Fig. 4 is a side view of the lower half of the clutch device according to the present invention cut along line IV-IV in Fig. 3. FIG. 6 is a diagram illustrating the relationship between the components indicating the clutch engagement state according to one embodiment of the present invention. FIG. 6 is a diagram illustrating the relationship between the components indicating the clutch connection state according to another embodiment of the present invention. Relationship diagram [Explanation of symbols]
1 Feeding mechanism 2 Pinion 3 Driven gear 4 Clutch device 5 Feeding roller 6 Solenoid locking mechanism 7 Central shaft 11 Inner member 12 Outer member 13 Planetary gear 14 Disk 15 Shaft 16 Planetary gear base 17 Cylindrical shaft 18 Clutch Release member 19 Torsion spring 22 Internal ring gear 23 Recess 24 Edge

Claims

An outer member having an internal ring gear; an inner member rotatably supported on the same axis as the outer member and having a plurality of recesses on the outer periphery; and each of the plurality of recesses rotatably received and A plurality of planetary gears each meshing with the inner ring gear, and when a part of the teeth of the planetary gear engages with an edge formed in the opening of the recess with respect to the outer peripheral surface of the inner member, the outer gear The clutch device is configured such that the outer member and the inner member rotate relative to each other when the member and the inner member rotate together and the engagement of a part of the teeth of the planetary gear with respect to the edge is released. And
The edges of the plurality of recesses are arranged at equal intervals on the same circumference,
Said plurality of planet gears, each respectively rotatably provided on the shaft provided in the outer member and the planetary gear base which is rotatably supported by the inner member,
The number of teeth of the internal ring gear is an integral multiple of the number of recesses,
The clutch device is characterized in that an operation in which a part of the teeth of the planetary gear engages with the edge is simultaneously performed for all the sets of the recess and the planetary gear.

A clutch release member provided rotatably on the same axis as the planetary gear base;
A torsion spring provided between the planetary gear base and the clutch release member;
A solenoid-type lock mechanism that selectively engages with the clutch release member to prevent rotation of the clutch release member;
In the torsion spring, rotation of the clutch release member is blocked by the solenoid-type lock mechanism, whereby a part of the planetary gear teeth is separated from the edge by engagement with the planetary gear base. The clutch device according to claim 1, wherein a pressing force is applied.