JPH05263841A - Electromagnetic control spring clutch mechanism - Google Patents

Electromagnetic control spring clutch mechanism

Info

Publication number
JPH05263841A
JPH05263841A JP5016847A JP1684793A JPH05263841A JP H05263841 A JPH05263841 A JP H05263841A JP 5016847 A JP5016847 A JP 5016847A JP 1684793 A JP1684793 A JP 1684793A JP H05263841 A JPH05263841 A JP H05263841A
Authority
JP
Japan
Prior art keywords
clutch mechanism
spring clutch
shaft member
rotor
spring
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
Application number
JP5016847A
Other languages
Japanese (ja)
Other versions
JP2720266B2 (en
Inventor
Kozo Nishimura
興三 西村
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kyocera Mita Industrial Co Ltd
Original Assignee
Mita Industrial Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mita Industrial Co Ltd filed Critical Mita Industrial Co Ltd
Priority to JP5016847A priority Critical patent/JP2720266B2/en
Publication of JPH05263841A publication Critical patent/JPH05263841A/en
Application granted granted Critical
Publication of JP2720266B2 publication Critical patent/JP2720266B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/105—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with a helical band or equivalent member co-operating with a cylindrical coupling surface

Abstract

PURPOSE:To ensure that the output rotation element of an electromagnetic control spring clutch mechanism is inhibited when an electromagnetic means is inactive. CONSTITUTION:An electromagnetic control spring clutch mechanism 2 has a shaft member 4 which is an output rotation element, an input rotation element rotatively attached to the shaft member 4, and a spring clutch mechanism 8, 10 which are disposed on the shaft member 4 and transmits a driving force from the input rotation element to the shaft member 4. This mechanism also has a brake means 180 for controlling the rotational motion of the shaft member 4, provided for the shaft member 4 which is an output rotation element.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、電磁制御ばねクラッチ
機構に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electromagnetically controlled spring clutch mechanism.

【０００２】[0002]

【従来の技術】従来から、回転駆動される入力回転要素
の駆動力を伝達するために、コイルばね手段を利用した
電磁制御ばねクラッチ機構が使用されている。この種の
電磁制御ばねクラッチ機構の一例として例えば特開昭５
９−１７５６３３号公報に開示されているものがあり、
かかる電磁制御ばねクラッチ機構は、入力回転要素が固
定され且つ出力回転要素が回転自在に装着された軸部材
と、軸部材と一体に回転せしめられるロータと、ロータ
の片側に配設されたアマチュア組立体であって、ロータ
の片面に対向して位置するアマチュア、軸部材に回転自
在に装着された支持部材、及びアマチュアをロータの片
面から離隔する方向に偏倚せしめる偏倚ばね部材を含む
アマチュア組立体と、偏倚ばね部材の弾性偏倚作用に抗
してアマチュアをロータの上記片面に磁気的に吸着せし
める電磁手段と、一端がアマチュア組立体に連結され、
他端が出力回転要素に連結されたコイルばね手段を備え
ている。かかるクラッチ機構においては、電磁手段が除
勢されているときには入力回転要素の駆動力は出力回転
要素に伝達されないが、電磁手段が付勢されるとアマチ
ュア組立体と出力回転要素が相対的に回転され、これに
よってコイルばね手段が収縮され、かくして入力回転要
素の駆動力が出力回転要素に伝達される。2. Description of the Related Art Conventionally, an electromagnetically controlled spring clutch mechanism utilizing coil spring means has been used to transmit a driving force of an input rotary element that is rotationally driven. An example of this type of electromagnetically controlled spring clutch mechanism is, for example, Japanese Patent Laid-Open No.
There is one disclosed in Japanese Patent Publication No. 9-175633,
Such an electromagnetically controlled spring clutch mechanism includes a shaft member to which an input rotary element is fixed and an output rotary element is rotatably mounted, a rotor rotated integrally with the shaft member, and an armature assembly arranged on one side of the rotor. An armature assembly that is three-dimensional and that includes an armature that faces one surface of the rotor, a support member that is rotatably mounted on a shaft member, and a biasing spring member that biases the armature in a direction away from the one surface of the rotor. An electromagnetic means for magnetically attracting the armature to the one side of the rotor against the elastic biasing action of the biasing spring member, and one end connected to the armature assembly,
The other end comprises a coil spring means connected to the output rotary element. In such a clutch mechanism, the driving force of the input rotary element is not transmitted to the output rotary element when the electromagnetic means is deenergized, but the armature assembly and the output rotary element relatively rotate when the electromagnetic means is biased. This causes the coil spring means to contract, thus transmitting the driving force of the input rotary element to the output rotary element.

【０００３】[0003]

【発明が解決しようとする課題】而して、上述した形態
の電磁制御ばねクラッチ機構に限定されるわけではない
が、電磁制御ばねクラッチ機構においては、入力回転要
素と、軸部材との間の摩擦力が大きいときには、電磁手
段が除勢されているときにも入力回転要素からの駆動力
が出力回転要素に伝達され、これによって出力回転要素
が回転する虞があった。The electromagnetically controlled spring clutch mechanism is not limited to the above-described electromagnetically controlled spring clutch mechanism, but the electromagnetically controlled spring clutch mechanism has a structure in which the input rotary element and the shaft member are connected to each other. When the frictional force is large, the driving force from the input rotary element is transmitted to the output rotary element even when the electromagnetic means is deenergized, which may cause the output rotary element to rotate.

【０００４】本発明は上記に点に鑑みてなされたもので
あり、その主たる技術的課題は、電磁制御ばねクラッチ
機構において、電磁手段が除勢されているときにおいて
出力回転要素が回転するのを確実に防止することであ
る。The present invention has been made in view of the above points, and its main technical problem is to prevent the output rotary element from rotating in the electromagnetically controlled spring clutch mechanism when the electromagnetic means is deenergized. To prevent it surely.

【０００５】[0005]

【課題を解決するための手段】上記技術的課題を達成す
るために、本発明によれば、該軸部材に回転自在に装着
され回転駆動される入力回転要素と、該回転軸と一体に
回転せしめられるロータと、該ロータに対向して位置す
るアマチュアと、該アマチュアを該ロータから離隔する
方向に弾性的に偏倚する偏倚ばね部材と、付勢されると
該偏倚ばね部材の弾性偏倚作用に抗して該アマチュアを
該ロータに磁気的に吸着せしめる電磁手段と、収縮する
ことによって該入力回転要素からの駆動力を該軸部材に
伝達するためのコイルばね手段とを具備するばねクラッ
チ機構と、を有する電磁制御ばねクラッチ機構におい
て、該軸部材の回動を制動するためのブレーキ手段を設
けた、ことを特徴とする電磁制御ばねクラッチ機構が提
供される。In order to achieve the above technical object, according to the present invention, an input rotary element rotatably mounted on the shaft member and driven to rotate, and a rotary shaft that rotates together with the input rotary element. A biased rotor, an armature facing the rotor, a biasing spring member that elastically biases the armature away from the rotor, and an elastic biasing action of the biasing spring member when biased. A spring clutch mechanism comprising: electromagnetic means for magnetically attracting the armature to the rotor, and coil spring means for contracting to transmit the driving force from the input rotary element to the shaft member. An electromagnetic control spring clutch mechanism is provided, in which brake means for braking the rotation of the shaft member is provided.

【０００６】[0006]

【作用】本発明の電磁制御ばねクラッチ機構において
は、出力回転要素である該軸部材は、該ブレーキ手段に
よって常時回転を抑制するための制動力が作用せしめら
れている。従って、電磁手段が除勢されているときにお
いて出力回転要素が回転するのを確実に防止することが
できるとともに、電磁手段の付勢後に除勢されたときに
おいても出力回転要素の回転を瞬時に停止することがで
きる。In the electromagnetically controlled spring clutch mechanism of the present invention, the shaft member, which is the output rotation element, is applied with a braking force for constantly suppressing rotation by the braking means. Therefore, it is possible to reliably prevent the output rotary element from rotating when the electromagnetic means is deenergized, and instantaneously rotate the output rotary element even when the electromagnetic means is deenergized after being biased. You can stop.

【０００７】[0007]

【実施例】以下、添付図面を参照して、本発明に従って
構成された電磁制御ばねクラッチ機構の一実施例につい
て説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an electromagnetically controlled spring clutch mechanism constructed according to the present invention will be described below with reference to the accompanying drawings.

【０００８】図示の実施例は所定方向及び所定方向と反
対方向に回転駆動される入力回転要素の駆動力を出力側
に伝達することができる電磁制御ばねクラッチ機構に本
発明を適用したものである。In the illustrated embodiment, the present invention is applied to an electromagnetically controlled spring clutch mechanism capable of transmitting the driving force of an input rotary element, which is rotationally driven in a predetermined direction and a direction opposite to the predetermined direction, to an output side. ..

【０００９】主として図１を参照して、全体を番号２で
示す図示の電磁制御ばねクラッチ機構は、軸部材４と、
該軸部材４に回転自在に装着された歯車６の如き入力回
転要素と、第１のばねクラッチ機構８、第２のばねクラ
ッチ機構１０及びブレーキ手段１８０とを備えている。
軸部材４は、図１に示す如く、例えば支持基体１２及び
１４に回転自在に装着され、軸部材４の支持基体１２及
び１４間の部位に歯車６、第１のばねクラッチ機構８及
び第２のばねクラッチ機構１０が配置されている。この
軸部材４には、例えば、接続手段１６を介して作動軸１
８（図１において二点鎖線で示す）が接続される。実施
例においては、軸部材４の一端部は支持基体１２を貫通
して外方に突出している（この突出端部の一部は、軸受
２０を介して回転自在に支持されている）。接続手段１
６は円筒状の接続部材２２を備えている。接続部材２２
の一端部には比較的大径の受け凹部２４ａが設けられて
おり、かかる受け凹部２４ａ内に作動軸１８の小径端部
１８ａを位置付けて固定用ねじ２６を螺着することによ
って接続部材２２と作動軸１８が連結されている。ま
た、接続部材２２の他端部にも比較的小径の受け凹部２
４ｂ（実施例では、受け凹部２４ａ及び２４ｂは相互に
連通している）が設けられており、かかる受け凹部２４
ｂ内に軸部材４の突出端部を位置付けて固定用ねじ２８
を螺着することによって接続部材２２と軸部材４が連結
されている。固定用ねじ２６及び２８に代えて、固定用
ピンによって両者を連結することもできる。従って、後
述する如く軸部材４が回転されると、接続手段２６を介
して作動軸１８も軸部材４と一体に回転せしめられる。Referring mainly to FIG. 1, the illustrated electromagnetically controlled spring clutch mechanism, generally designated by the numeral 2, includes a shaft member 4,
An input rotary element such as a gear 6 rotatably mounted on the shaft member 4, a first spring clutch mechanism 8, a second spring clutch mechanism 10 and a braking means 180 are provided.
As shown in FIG. 1, the shaft member 4 is rotatably attached to, for example, the support bases 12 and 14, and the gear 6, the first spring clutch mechanism 8 and the second spring clutch mechanism 8 and the second spring clutch mechanism 8 are provided on the shaft member 4 between the support bases 12 and 14. The spring clutch mechanism 10 of FIG. The operating shaft 1 is connected to the shaft member 4 via a connecting means 16, for example.
8 (indicated by a chain double-dashed line in FIG. 1) are connected. In the embodiment, one end of the shaft member 4 penetrates the support base 12 and projects outward (a part of this projecting end is rotatably supported via the bearing 20). Connection means 1
6 includes a cylindrical connecting member 22. Connection member 22
Is provided with a relatively large diameter receiving recess 24a at one end thereof, and the small diameter end 18a of the actuating shaft 18 is positioned in the receiving recess 24a and the fixing screw 26 is screwed into the receiving member 24a so that The operating shaft 18 is connected. Further, the receiving recess 2 having a relatively small diameter is also provided at the other end of the connecting member 22.
4b (in the embodiment, the receiving recesses 24a and 24b are in communication with each other) are provided.
Position the protruding end of the shaft member 4 in b and fix the screw 28 for fixing.
The connecting member 22 and the shaft member 4 are connected by screwing. Instead of the fixing screws 26 and 28, a fixing pin may be used to connect them. Therefore, when the shaft member 4 is rotated as described later, the operating shaft 18 is also rotated integrally with the shaft member 4 via the connecting means 26.

【００１０】次に、図１と共に図２を参照して、第１の
ばねクラッチ機構８及びそれに関連する要素について説
明する。実施例においては、軸部材４の支持基体１２及
び１４間の軸線方向実質上中央部には、大径部４ａが設
けられており、かかる大径部４ａに歯車６が回転自在に
装着され、かかる歯車６と片方の支持基体１２間に第１
のばねクラッチ機構８が配置され、上記歯車６と他方の
支持基体１４間に後述する第２のばねクラッチ機構１０
が配置されている。Next, the first spring clutch mechanism 8 and its related elements will be described with reference to FIG. 1 as well as FIG. In the embodiment, a large diameter portion 4a is provided substantially in the center in the axial direction between the support bases 12 and 14 of the shaft member 4, and the gear 6 is rotatably mounted on the large diameter portion 4a. Between the gear 6 and the one supporting base 12, the first
Second spring clutch mechanism 8 is arranged, and a second spring clutch mechanism 10 described later is provided between the gear 6 and the other support base 14.
Are arranged.

【００１１】図示の第１のばねクラッチ機構８は、ロー
タ３０、アマチュア組立体３２、電磁手段３４及びコイ
ルばね手段３６を含んでいる。更に説明すると、電磁手
段３４は、軸部材４の一端部、詳しくは軸部材４の支持
基体１２の内側部位に配置されている。図示の電磁手段
３４はフィールドコア３８と、フィールドコア３８に装
着された電磁コイル４０を有し、フィールドコア３８が
スリーブ部材４２を介して軸部材４に回転自在に装着さ
れている（図１参照）。フィールドコア３８の外周面に
は係止部４４が設けられ、係止部４４には切欠き４６が
形成されている。一方、支持基体１２には、その一部を
後方に折曲せしめることによって係止突起４８が設けら
れており、かかる係止突起４８が上記係止部４４の切欠
き４６に係止されている（図１参照）。従って、電磁手
段３４は、後述する軸部材４の回転によって回動される
ことがない。The illustrated first spring clutch mechanism 8 includes a rotor 30, an armature assembly 32, an electromagnetic means 34 and a coil spring means 36. More specifically, the electromagnetic means 34 is arranged at one end of the shaft member 4, specifically, at an inner portion of the support base 12 of the shaft member 4. The illustrated electromagnetic means 34 has a field core 38 and an electromagnetic coil 40 mounted on the field core 38, and the field core 38 is rotatably mounted on the shaft member 4 via a sleeve member 42 (see FIG. 1). ). A locking portion 44 is provided on the outer peripheral surface of the field core 38, and a cutout 46 is formed in the locking portion 44. On the other hand, the supporting base 12 is provided with a locking projection 48 by bending a part thereof rearward, and the locking projection 48 is locked in the notch 46 of the locking portion 44. (See Figure 1). Therefore, the electromagnetic means 34 is not rotated by the rotation of the shaft member 4 described later.

【００１２】また、軸部材４の電磁手段３４と歯車６と
の間の部位、即ち電磁手段３４の内側には、ロータ３０
及びアマチュア組立体３２が配設されている。具体例に
おいてはロータ３０及びアマチュア組立体３２が第１の
ボス部材５０に所要の通り装着され、ロータ３０、アマ
チュア組立体３２及び第１のボス部材５０がユニット化
されてユニット組立体を構成する。図３をも参照して、
第１のボス部材５０は、一端部（図１乃至図３において
左端部）に設けられた小径部５２と、他端部（図１乃至
図３において右端部）に設けられた大径部５４と、その
中間部に設けられた中径部５６とを有している。第１の
ボス部材５０の小径部５２にはピン受部を規定する一対
の切欠き５８が形成されており、かかる切欠き５８に軸
部材４を貫通して形成されたピン孔６０（図２）に装着
されるピン部材６２の両端部が受入れられる。また、図
示のロータ３０は、環状基部６４と、環状基部６４の外
側に配置された環状部６６と、環状基部６４及び環状部
６６を接続する接続部６８を有している。かかるロータ
３０は、環状基部６４を第１のボス部材５０の小径部５
２に圧入することによってその一端に固定され、第１の
ボス部材５０と一体に回転される。実施例では、ロータ
３０が第１のボス部材５０の小径部５２に固定されるこ
とに関連して、ロータ３０の環状基部６４の内周縁に
も、一対の凹部７０が形成されている。ロータ３０に形
成された凹部７０は、上記第１のボス部材５０に形成さ
れた切欠き５８と協働してピン受部を規定し、図４に拡
大して示す如く、軸部材４に装着されたピン部材６２の
両端部は上記切欠き５８及び上記凹部７０に受入れられ
る（従って、ロータ３０を第１のボス部材５０の小径部
５２に固定する際には、ロータ３０の凹部７０と小径部
５２の切欠き５８を整合させて圧入する）。かく構成す
ることによって、ロータ３０と第１のボス部材５０の小
径部５２の圧入状態が比較的弱い場合においても、ロー
タ３０はピン部材６２を介して軸部材４と一体に確実に
回転される。また、実施例のアマチュア組立体３２は、
アマチュア７２、支持部材７４及び偏倚ばね部材７６を
含んでいる。支持部材７４は短筒状の部材から構成さ
れ、第１のボス部材５０の中径部５６に回転自在に装着
されている。支持部材７４の一端面（図１乃至図４にお
いて左面）内周縁には、環状フランジ７８が設けられて
いる。この支持部材７４は、軽量のプラスチックから形
成するのが好ましい。アマチュア７２はロータ３０の環
状部６６の外径と略同一の外径を有する環状板から構成
され、偏倚ばね部材７６を介して上記支持部材７４に装
着されている。更に説明すると、偏倚ばね部材７６は支
持部材７４の環状フランジ７８に装着され、その環状中
央部８０が支持部材７４の一端面に後述する如く固定さ
れている。図示の偏倚ばね部材７６は環状中央部８０か
ら外側に鎌状に延びる複数個（実施例においては３個）
の突出部８２を有し、複数個の突出部８２の各々の自由
端部がアマチュア７２の片面（ロータ３０と対向する面
とは反対の面）にリベットの如き固定部材８４により固
定されている。従って、ロータ３０の片側、即ち図１に
おいて右側にアマチュア組立体３２が配設され、偏倚ば
ね部材７６はアマチュア７２をロータ３０の片面、即ち
図１において右面から離隔する方向に弾性的に偏倚せし
める作用をする。実施例に示す如く、偏倚ばね部材７６
は次の通りにして支持部材７６に固定されるのが好まし
い。図示のアマチュア組立体３２は、更に、プレート状
のばね固定部材を含んでいる。図示のばね固定部材は偏
倚ばね部材７６の環状中央部８０の形状に略対応した環
状のプレート部材８６から構成されている。このプレー
ト部材８６の周縁部には、その一部を折曲せしめること
によって周方向に間隔を置いて複数個（実施例では３
個）の係止突部８８が設けられている。一方、偏倚ばね
部材７６の環状中央部８０には上記係止突部８８の各々
に対応して複数個（実施例では３個）の矩形状の挿通孔
９０が形成され、更に支持部材７４には上記挿通孔９０
の各々に対応して矩形状の貫通孔９２が形成されてい
る。従って、支持部材７４の環状フランジ７８に偏倚ば
ね部材７６及びプレート部材８６を装着すると、プレー
ト部材８６の各係止突部８８は対応する偏倚ばね部材７
６の挿通孔９０及び支持部材７４の貫通孔９２を通して
支持部材７４の他側に突出するようになり（図５に実線
で示す如く突出される）、かかる係止突部８８の突出端
を所要の通り変形せしめて支持部材７４の他端部に係止
せしめることによって、偏倚ばね部材７６の環状中央部
８０はプレート部材８６と支持部材７４間に固定され
る。実施例におけるプレート部材８６の係止突部８８の
支持部材７４への係止は、図５に拡大して示す通りにす
るのが好ましい。即ち、図５に示す如く、支持部材７４
の各貫通孔９２の右端部（図１乃至図３及び図５におい
て右端部）を右方に向けて拡張せしめ、貫通孔９２の拡
張部９２ａ内に係止突部８８の変形部を収容せしめるよ
うにするのが好ましく、かくすることによって、支持部
材７４、偏倚ばね部材７６及びプレート部材８６から成
る組立要素を小型化することができる。尚、実施例のよ
うに貫通孔９２に拡張部９２ａを設けた場合には、係止
突部８８を変形せしめるためのポンチの如き加圧工具９
４の先端を凹状にし、その先端面９４ａが弧状面を規定
するようにするのが望ましい。かくすることにより、図
５に実線で示す如く突出せしめられている係止突部８８
の突出部を加圧工具９４の作用によって図５に一点鎖線
で示す如く所要の通り変形せしめてその変形部を貫通孔
９２の拡張部９２ａに確実に係止せしめることができ
る。The rotor 30 is provided at a portion of the shaft member 4 between the electromagnetic means 34 and the gear 6, that is, inside the electromagnetic means 34.
And an armature assembly 32 is provided. In the specific example, the rotor 30 and the armature assembly 32 are mounted on the first boss member 50 as required, and the rotor 30, the armature assembly 32, and the first boss member 50 are unitized to form a unit assembly. .. Referring also to FIG.
The first boss member 50 has a small diameter portion 52 provided at one end (the left end in FIGS. 1 to 3) and a large diameter portion 54 provided at the other end (the right end in FIGS. 1 to 3). And a medium diameter portion 56 provided in the middle portion thereof. The small diameter portion 52 of the first boss member 50 is formed with a pair of notches 58 that define a pin receiving portion, and a pin hole 60 formed by penetrating the shaft member 4 in the notches 58 (see FIG. 2). ), The both ends of the pin member 62 attached to () are received. Further, the illustrated rotor 30 includes an annular base portion 64, an annular portion 66 arranged outside the annular base portion 64, and a connecting portion 68 that connects the annular base portion 64 and the annular portion 66. In the rotor 30, the annular base portion 64 is provided in the small diameter portion 5 of the first boss member 50.
It is fixed to one end of the first boss member 50 by being press-fitted into the second boss member 50 and is rotated integrally with the first boss member 50. In the embodiment, as the rotor 30 is fixed to the small-diameter portion 52 of the first boss member 50, a pair of recesses 70 is also formed on the inner peripheral edge of the annular base portion 64 of the rotor 30. The recess 70 formed in the rotor 30 cooperates with the notch 58 formed in the first boss member 50 to define a pin receiving portion, and is attached to the shaft member 4 as shown in an enlarged view in FIG. Both ends of the pin member 62 thus formed are received in the notch 58 and the recess 70 (thus, when the rotor 30 is fixed to the small diameter portion 52 of the first boss member 50, the recess 70 and the small diameter portion of the rotor 30 are The notch 58 of the portion 52 is aligned and press-fitted). With this configuration, even when the press-fitted state of the rotor 30 and the small diameter portion 52 of the first boss member 50 is relatively weak, the rotor 30 is reliably rotated integrally with the shaft member 4 via the pin member 62. .. Further, the amateur assembly 32 of the embodiment is
The armature 72, the support member 74, and the bias spring member 76 are included. The support member 74 is composed of a short tubular member, and is rotatably attached to the medium diameter portion 56 of the first boss member 50. An annular flange 78 is provided on the inner peripheral edge of one end surface (left surface in FIGS. 1 to 4) of the support member 74. The support member 74 is preferably made of lightweight plastic. The armature 72 is composed of an annular plate having an outer diameter substantially the same as the outer diameter of the annular portion 66 of the rotor 30, and is mounted on the support member 74 via a biasing spring member 76. More specifically, the bias spring member 76 is mounted on the annular flange 78 of the support member 74, and the annular center portion 80 is fixed to one end surface of the support member 74 as described later. The bias spring members 76 shown in the figure are plural (three in the embodiment) extending outward from the annular central portion 80 in a sickle shape.
Of the plurality of protrusions 82, and the free end of each of the plurality of protrusions 82 is fixed to one surface of the armature 72 (the surface opposite to the surface facing the rotor 30) by a fixing member 84 such as a rivet. .. Therefore, the armature assembly 32 is disposed on one side of the rotor 30, that is, on the right side in FIG. 1, and the biasing spring member 76 elastically biases the armature 72 in the direction away from one side of the rotor 30, that is, the right side in FIG. To work. As shown in the embodiment, the biasing spring member 76
Is preferably fixed to the support member 76 as follows. The illustrated armature assembly 32 further includes a plate-shaped spring fixing member. The illustrated spring fixing member is composed of an annular plate member 86 substantially corresponding to the shape of the annular central portion 80 of the biasing spring member 76. The plate member 86 has a plurality of circumferentially spaced intervals (three in the embodiment) by bending a part of the plate member 86.
Locking projections 88 are provided. On the other hand, in the annular central portion 80 of the biasing spring member 76, a plurality of (three in the embodiment) rectangular insertion holes 90 are formed corresponding to each of the locking projections 88, and the supporting member 74 is further provided. Is the insertion hole 90
A rectangular through hole 92 is formed corresponding to each of the above. Therefore, when the bias spring member 76 and the plate member 86 are mounted on the annular flange 78 of the support member 74, the respective locking projections 88 of the plate member 86 are corresponding to the bias spring member 7.
6 through the through hole 90 of the support member 74 and the through hole 92 of the support member 74 to the other side of the support member 74 (projected as shown by the solid line in FIG. 5). The annular center portion 80 of the bias spring member 76 is fixed between the plate member 86 and the support member 74 by deforming as described above and engaging with the other end portion of the support member 74. The locking projection 88 of the plate member 86 in the embodiment is preferably locked to the support member 74 as enlargedly shown in FIG. That is, as shown in FIG.
The right end portion (the right end portion in FIGS. 1 to 3 and 5) of each through hole 92 is expanded rightward so that the deformed portion of the locking projection 88 is accommodated in the expanded portion 92a of the through hole 92. This is preferable, and the assembly element including the support member 74, the biasing spring member 76, and the plate member 86 can be downsized. When the expansion portion 92a is provided in the through hole 92 as in the embodiment, the pressing tool 9 such as a punch for deforming the locking projection 88 is formed.
It is desirable to make the tip of No. 4 concave so that its tip surface 94a defines an arcuate surface. By doing so, the locking projection 88 that is projected as shown by the solid line in FIG.
The projecting portion can be deformed as required by the action of the pressing tool 94 as shown by the one-dot chain line in FIG. 5, and the deformed portion can be securely locked to the expanded portion 92a of the through hole 92.

【００１３】実施例のユニット組立体においては、更
に、支持部材７４の一端面に周方向に間隔を置いて複数
個（実施例においては３個）の突起９６が設けられ、ま
た偏倚ばね部材７６の環状中央部８０には上記突起９６
に対応して周方向に間隔を置いて突起受部を規定する複
数個の円形の開口９８が形成されている。各突起９６の
先端部は偏倚ばね部材７６の開口９８を貫通し、プレー
ト部材８６及びアマチュア７２を越えてロータ３０の片
面に向って延び、その先端はロータ３０の片面に接触乃
至近接せしめられている。実施例では、突起９６が上述
した如く延びていることに関連して、プレート部材８６
の周縁部には上記開口９８に対応して半円状の切欠き１
００が形成されている。かくの通りであるので、各突起
９６は開口９８及び切欠き１００に受入れられ、支持部
材７４と偏倚ばね部材７６間において駆動力を伝達する
作用をする（言い換えると、支持部材７４と偏倚ばね部
材７６間に生じるアジアル荷重、即ち回転方向の荷重を
受ける作用をする）と共に、後述する如く第１のばねク
ラッチ機構８における応答性を向上させる作用をする。
第１のばねクラッチ機構８の応答性を一層向上させるに
は、実施例に示す如く、支持部材７４の環状フランジ７
８の先端部も偏倚ばね部材７６及びプレート部材８６を
越えて突出させ、その先端をロータ３０の片面に接触乃
至近接せしめるのが好ましく、実施例においては、突起
９６の先端面及び環状フランジ７８の先端面がロータ３
０の片面に実質上平行である実質上同一平面を規定する
ように構成されている。In the unit assembly of the embodiment, a plurality of (three in the embodiment) projections 96 are further provided at one end surface of the support member 74 at circumferential intervals, and the bias spring member 76 is also provided. The annular center portion 80 of the
A plurality of circular openings 98 are formed at intervals in the circumferential direction to define the projection receiving portions. The tip of each protrusion 96 penetrates through the opening 98 of the biasing spring member 76, extends beyond the plate member 86 and the armature 72 toward one side of the rotor 30, and its tip is brought into contact with or close to one side of the rotor 30. There is. In the exemplary embodiment, plate member 86 is associated with protrusion 96 extending as described above.
A semi-circular cutout 1 is provided at the peripheral edge of the opening corresponding to the opening 98.
00 is formed. As such, each protrusion 96 is received in the opening 98 and the notch 100 and acts to transmit a driving force between the support member 74 and the bias spring member 76 (in other words, the support member 74 and the bias spring member). It acts to receive the Asian load generated between 76, that is, the load in the rotational direction) and to improve the response of the first spring clutch mechanism 8 as described later.
In order to further improve the responsiveness of the first spring clutch mechanism 8, as shown in the embodiment, the annular flange 7 of the support member 74 is used.
It is also preferable that the tip end portion of 8 also projects beyond the biasing spring member 76 and the plate member 86 so that the tip end thereof contacts or approaches one surface of the rotor 30, and in the embodiment, the tip end surface of the protrusion 96 and the annular flange 78. Tip surface is rotor 3
It is configured to define a substantially coplanar plane that is substantially parallel to one side of zero.

【００１４】図示の実施例においては、ユニット組立体
は第１のボス部材５０を圧入することによって軸部材４
に所要の通り装着されている。尚、実施例では軸部材４
の所要部位４ｂにはローレットの如き加工が施されてお
り、かかる部位４ｂに第１のボス部材５０の右端部が大
径部４ａの左端面に当接するように圧入され、第１のボ
ス部材５０は軸部材４と一体に回転せしめられる。In the illustrated embodiment, the unit assembly includes a shaft member 4 by press fitting a first boss member 50.
It is installed as required in. In the embodiment, the shaft member 4
The required portion 4b of the first boss member is processed such as knurling, and the right end portion of the first boss member 50 is press-fitted into the portion 4b so as to contact the left end surface of the large diameter portion 4a. 50 is rotated integrally with the shaft member 4.

【００１５】再び図１及び図２を参照して、歯車６の片
面（図１及び図２において左面）には、環状のボス部１
０２が一体に設けられ、ボス部１０２内には円筒状の第
２のボス部材１０４が装着されている。実施例では、こ
の第２のボス部材１０４は、歯車６の内周部（詳しくは
ボス部１０２の内側部位）に形成された貫通孔１０６
（実施例においては２個形成されている）内にその端面
に設けられた一対の突出部１０８を挿入することによっ
て歯車６と一体に回転するように装着されている。この
第２のボス部材１０４は、上記第１のボス部材５０に向
けて図１及び図２において左方に延びている。尚、第２
のボス部材１０４は歯車６と一体に形成することも可能
である。Referring again to FIGS. 1 and 2, the annular boss portion 1 is provided on one surface of the gear 6 (left surface in FIGS. 1 and 2).
02 is integrally provided, and a cylindrical second boss member 104 is mounted in the boss portion 102. In the embodiment, the second boss member 104 has the through hole 106 formed in the inner peripheral portion of the gear 6 (specifically, the inner portion of the boss portion 102).
By inserting a pair of projecting portions 108 provided on the end faces thereof (two are formed in the embodiment), they are mounted so as to rotate integrally with the gear 6. The second boss member 104 extends leftward in FIGS. 1 and 2 toward the first boss member 50. The second
The boss member 104 can be formed integrally with the gear 6.

【００１６】上記第１のボス部材５０及び第２のボス部
材１０４に跨ってコイルばね手段３６が被嵌されてい
る。ユニット組立体の第１のボス部材５０の大径部５４
は上記第２のボス部材１０４に向けて延び、両ボス部材
５０及び１０４の端面は相互に接触乃至近接せしめられ
ている。この第１のボス部材５０の大径部５４の外径と
第２のボス部材１０４の外径とは実質上等しく、実施例
ではコイルばね手段３６は上記第１のボス部材５０の大
径部５４と第２のボス部材１０４の両者に跨って被嵌さ
れている。実施例においては、コイルばね手段３６は図
１及び図２において左側から見て右巻（従って、歯車６
が矢印１１０（図２）で示す方向に回転されているとき
に、支持部材７４にその回動を阻止する力が作用して支
持部材７４が歯車６に対して相対的に回転せしめられる
と収縮される方向）に捲回されている。かかるコイルば
ね手段３６の一端３６ａは、支持部材７４の他端部に形
成された切欠き１１２（実施例では、周方向に間隔を置
いて複数個形成された切欠き１１２のいずれか）に挿入
されることによってこれに連結され、その他端３６ｂ
は、歯車６の環状ボス部１０２に形成された切欠き１１
４（実施例では、周方向に間隔を置いて４個形成された
切欠き１１４のいずれか）に挿入されることによってこ
れに連結されている。Coil spring means 36 is fitted over the first boss member 50 and the second boss member 104. Large diameter portion 54 of first boss member 50 of unit assembly
Extends toward the second boss member 104, and the end surfaces of both boss members 50 and 104 are in contact with or in close proximity to each other. The outer diameter of the large diameter portion 54 of the first boss member 50 and the outer diameter of the second boss member 104 are substantially equal, and in the embodiment, the coil spring means 36 is the large diameter portion of the first boss member 50. It is fitted over both 54 and the second boss member 104. In the embodiment, the coil spring means 36 is right-handed when viewed from the left side in FIGS.
Is rotated in the direction indicated by the arrow 110 (FIG. 2), the support member 74 contracts when the support member 74 is rotated relative to the gear 6 due to the force that prevents the rotation thereof. Direction). One end 36a of the coil spring means 36 is inserted into a notch 112 formed in the other end of the support member 74 (in the embodiment, any one of a plurality of notches 112 formed at intervals in the circumferential direction). By being connected to this, the other end 36b
Is a notch 11 formed in the annular boss portion 102 of the gear 6.
4 (in the embodiment, any one of the four notches 114 formed at intervals in the circumferential direction) is connected to this.

【００１７】かくの通りであるので、歯車６が矢印１１
０で示す方向に回転されているときに電磁手段３４が付
勢されると、後に詳述する如く、歯車６とアマチュア組
立体３２とが相対的に回転され、これによってコイルば
ね手段３６が収縮され、かくして歯車６から駆動力は第
２のボス部材１０４、コイルばね手段３６及び第１のボ
ス部材５０を介して軸部材４に伝達される。As described above, the gear 6 is indicated by the arrow 11
When the electromagnetic means 34 is energized while it is being rotated in the direction indicated by 0, the gear 6 and the armature assembly 32 are relatively rotated, which causes the coil spring means 36 to contract, as will be described later in detail. Thus, the driving force from the gear 6 is transmitted to the shaft member 4 via the second boss member 104, the coil spring means 36 and the first boss member 50.

【００１８】次いで、図１と共に図６を参照して、第２
のばねクラッチ機構１０及びこれに関連する要素につい
て説明する。歯車６と支持基体１４間に配置された第２
のばねクラッチ機構１０は、第１のばねクラッチ機構８
と同様に、ロータ１１６、アマチュア組立体１１８、電
磁手段１２０及びコイルばね手段１２２を含んでおり、
第２のばねクラッチ機構１０におけるロータ１１６、ア
マチュア組立体１１８、電磁手段１２０及びコイルばね
手段１２２の構成は、第１のばねクラッチ機構８におけ
るロータ３０、アマチュア組立体３２、電磁手段３４及
びコイルばね手段３６の構成と実質上同一である。従っ
て、第２のばねクラッチ機構１０については概略を説明
する。Next, referring to FIG. 6 together with FIG.
The spring clutch mechanism 10 and its related elements will be described. Second arranged between the gear 6 and the support base 14
The spring clutch mechanism 10 of FIG.
A rotor 116, an armature assembly 118, an electromagnetic means 120 and a coil spring means 122,
The rotor 116, the armature assembly 118, the electromagnetic means 120, and the coil spring means 122 in the second spring clutch mechanism 10 are configured as follows: the rotor 30, the armature assembly 32, the electromagnetic means 34, and the coil spring in the first spring clutch mechanism 8. The configuration of the means 36 is substantially the same. Therefore, the outline of the second spring clutch mechanism 10 will be described.

【００１９】第２のばねクラッチ機構１０における電磁
手段１２０は、軸部材４の他端部、詳しくは軸部材４の
他端部、更に詳しくは軸部材４の支持基体１４の内側部
位に配置されている。図示の電磁手段１２０は、フィー
ルドコア１２０と、フィールドコア１２０に装着された
電磁コイル１２２を有し、フィールドコア１２０がスリ
ーブ部材１２４を介して軸部材４に回転自在に装着され
ている（図１参照）。フィールドコア１２０の外周面に
は係止部１２６が設けられ、係止部１２６には切欠き１
２８が形成されている。一方、支持基体１４には、その
一部を後方に折曲せしめることによって係止突起１３０
が設けられており、かかる係止突起１３０が上記係止部
１２６の切欠き１２８に係止されている。（図１参
照）。従って、電磁手段１２０は、後述する軸部材４の
回転によって回動されることがない。The electromagnetic means 120 in the second spring clutch mechanism 10 is arranged at the other end of the shaft member 4, more specifically at the other end of the shaft member 4, and more specifically at an inner portion of the support base 14 of the shaft member 4. ing. The illustrated electromagnetic means 120 has a field core 120 and an electromagnetic coil 122 attached to the field core 120, and the field core 120 is rotatably attached to the shaft member 4 via a sleeve member 124 (FIG. 1). reference). A locking portion 126 is provided on the outer peripheral surface of the field core 120, and the notch 1 is formed in the locking portion 126.
28 is formed. On the other hand, on the support base 14, a part of the support base 14 is bent backward so that the locking projection 130
Is provided, and the locking projection 130 is locked in the notch 128 of the locking portion 126. (See Figure 1). Therefore, the electromagnetic means 120 is not rotated by the rotation of the shaft member 4 described later.

【００２０】また、軸部材４の電磁手段１２０と歯車６
との間の部位、即ち電磁手段１２０の内側には、ロータ
１１６及びアマチュア組立体１１８が配設されている。
実施例においてはロータ１１６及びアマチュア組立体１
１８も第１のボス部材１３２に所要の通り装着され、ロ
ータ１１６、アマチュア組立体１１８及び第１のボス部
材１３２がユニット化されてユニット組立体を構成す
る。第１のボス部材１３２は、一端部（図１及び図６に
おいて左端部）に設けられた大径部１３４と、他端部
（図１及び図６において右端部）に設けられた小径部１
３６と、その中間部に設けられた中径部１３８とを有し
ている。第１のボス部材１３２の小径部１３６にはピン
受部を規定する一対の切欠き１４０が形成されており、
かかる切欠き１４０に軸部材４を貫通して形成された他
方のピン孔１４２（図６）に装着されるピン部材１１４
の両端部が受入れられる。また、図示のロータ１１６
は、環状基部１４６と、環状基部１４６の外側に配置さ
れた環状部１４８と、環状基部１４６及び環状部１４８
を接続する接続部１５０を有している。かかるロータ１
１６は、環状基部１４６を第１のボス部材１３２の小径
部１３６に圧入することによってその一端に固定され、
第１のボス部材１３２と一体に回転される。実施例で
は、ロータ１１６の環状基部１４６の内周縁にも、一対
の凹部１５２が形成されている。ロータ１１６に形成さ
れた凹部１５２は、上記第１のボス部材１３２に形成さ
れた切欠き１４０と協働してピン受部を規定し、軸部材
４に装着されたピン部材１４４の両端部は上記切欠き１
４０及び上記凹部１５２に受入れられる（従って、ロー
タ１１６を第１のボス部材１３２の小径部１３６に固定
する際には、ロータ１１６の凹部１５２と小径部１３６
の切欠き１４０を整合させて圧入する）。また、実施例
のアマチュア組立体１１８は、アマチュア１５４、支持
部材１５６及び偏倚ばね部材１５８を含んでいる。支持
部材１５６は短筒状の部材から構成され、第１のボス部
材１３２の中径部１３８に回転自在に装着されている。
支持部材１５６の端面（図１において右側）内周縁に
は、環状フランジ（図１）が設けられている。この支持
部材１５６は、軽量のプラスチックから形成するのが好
ましい。アマチュア１５４はロータ１１６の環状部１４
８の外径と略同一の外径を有する環状板から構成され、
偏倚ばね部材１５８を介して上記支持部材１５６に装着
されている。即ち、偏倚ばね部材１５８は支持部材１５
６の環状フランジに装着され、その環状中央部１６０が
支持部材１５６の端面に所要の通り固定されている。図
示の偏倚ばね部材１５８は環状中央部１６０から外側に
鎌状に延びる複数個（実施例においては３個）の突出部
１６２を有し、複数個の突出部１６２の各々の自由端部
がアマチュア１５４の片面（図１及び図６において左面
であって、ロータ１１６と対向する面とは反対の面）に
リベットの如き固定部材１６４により固定されている。
従って、第２のばねクラッチ機構１０においても、ロー
タ１１６の片側、即ち図１において左側にアマチュア組
立体１１８が配設され、偏倚ばね部材１５８はアマチュ
ア１５４をロータ１１６の片面、即ち図１において左面
から離隔する方向に弾性的に偏倚せしめる作用をする。
この第２のばねクラッチ機構１０においても、偏倚ばね
部材１５８は、第１のばねクラッチ機構８と実質上同様
に、ばね固定部材を構成する環状のプレート部材１６６
によって支持部材１５６に所要の通り固定されるのが好
ましい。The electromagnetic means 120 of the shaft member 4 and the gear 6
The rotor 116 and the armature assembly 118 are disposed in a portion between the two, that is, inside the electromagnetic means 120.
In the embodiment, the rotor 116 and the amateur assembly 1
18 is also attached to the first boss member 132 as required, and the rotor 116, the armature assembly 118, and the first boss member 132 are unitized to form a unit assembly. The first boss member 132 has a large-diameter portion 134 provided at one end (left end in FIGS. 1 and 6) and a small-diameter portion 1 provided at the other end (right end in FIGS. 1 and 6).
36 and a medium-diameter portion 138 provided in the middle portion thereof. The small diameter portion 136 of the first boss member 132 is formed with a pair of notches 140 that define a pin receiving portion,
The pin member 114 mounted in the other pin hole 142 (FIG. 6) formed through the shaft member 4 in the notch 140.
Both ends of are accepted. Also, the illustrated rotor 116
Is a ring-shaped base 146, a ring-shaped part 148 arranged outside the ring-shaped base 146, a ring-shaped base 146 and a ring-shaped part 148.
It has the connection part 150 which connects. Such rotor 1
16 is fixed to one end of the small diameter portion 136 of the first boss member 132 by press-fitting the annular base portion 146,
It is rotated integrally with the first boss member 132. In the embodiment, a pair of recesses 152 is also formed on the inner peripheral edge of the annular base portion 146 of the rotor 116. The recess 152 formed in the rotor 116 cooperates with the notch 140 formed in the first boss member 132 to define a pin receiving portion, and both ends of the pin member 144 mounted on the shaft member 4 are Notch 1 above
40 and the recess 152 (therefore, when fixing the rotor 116 to the small diameter portion 136 of the first boss member 132, the recess 152 and the small diameter portion 136 of the rotor 116 are received.
Align the notches 140 and press fit). The example armature assembly 118 also includes an armature 154, a support member 156, and a biasing spring member 158. The support member 156 is composed of a short tubular member, and is rotatably attached to the medium diameter portion 138 of the first boss member 132.
An annular flange (FIG. 1) is provided on the inner peripheral edge of the end surface (right side in FIG. 1) of the support member 156. The support member 156 is preferably formed from lightweight plastic. The amateur 154 is the annular portion 14 of the rotor 116.
8 is composed of an annular plate having an outer diameter substantially the same as the outer diameter,
It is attached to the support member 156 via the biasing spring member 158. That is, the biasing spring member 158 is the support member 15
6 is attached to an annular flange 6 of which an annular central portion 160 is fixed to an end surface of the support member 156 as required. The illustrated biasing spring member 158 has a plurality of (three in this embodiment) protrusions 162 extending outward from the annular central portion 160 in a sickle shape, and the free end of each of the plurality of protrusions 162 is an armature. It is fixed to one surface of 154 (the left surface in FIGS. 1 and 6 and the surface opposite to the surface facing the rotor 116) by a fixing member 164 such as a rivet.
Therefore, also in the second spring clutch mechanism 10, the armature assembly 118 is disposed on one side of the rotor 116, that is, on the left side in FIG. It acts to elastically deviate in the direction away from.
Also in the second spring clutch mechanism 10, the biasing spring member 158 is substantially the same as the first spring clutch mechanism 8 and the annular plate member 166 constituting the spring fixing member.
It is preferably secured to the support member 156 as required.

【００２１】第２のばねクラッチ機構１０においては、
更に、第１のばねクラッチ機構８と同様に、支持部材１
５６の端面には周方向に間隔を置いてロータ１１６の片
面に向って延びる複数個の突起１６８を設けるのが好ま
しく、また支持部材１５６に設けられた環状フランジの
先端をロータ１１６の上記片面に接触乃至近接せしめる
のが好ましい。In the second spring clutch mechanism 10,
Further, similarly to the first spring clutch mechanism 8, the support member 1
It is preferable to provide a plurality of projections 168 extending toward one surface of the rotor 116 at intervals on the end surface of the rotor 56, and the tip of an annular flange provided on the support member 156 is provided on the one surface of the rotor 116. It is preferable to bring them into contact with or close to each other.

【００２２】図示の実施例においては、ユニット組立体
は第１のボス部材１３２を圧入することによって軸部材
４に所要の通り装着されている。尚、実施例では軸部材
４の所要部位４Ｃにもローレットの如き加工が施されて
おり、かかる部位４Ｃに第１のボス部材１３２の左端部
が大径部４ａの右端面に当接するように圧入され、大１
のボス部材１３２は軸部材４と一体に回転せしめられ
る。In the illustrated embodiment, the unit assembly is mounted to the shaft member 4 as required by press fitting the first boss member 132. In the embodiment, the required portion 4C of the shaft member 4 is also processed such as knurling so that the left end portion of the first boss member 132 abuts the right end surface of the large diameter portion 4a. Pressed, large 1
The boss member 132 is rotated together with the shaft member 4.

【００２３】歯車６の他面（図１及び図６において右
面）にも、環状ボス部１７０が一体に設けられ、ボス部
１７０内には円筒状の第２のボス部材１７２が装着され
ている。実施例では、第２のボス部材１７２は歯車６に
形成された上記貫通孔１０６内に歯車６の他側から端面
に設けられた一対の突出部１７４を挿入することによっ
て歯車６と一体に回転するように装着されている。この
第２のボス部材１７２は、上記第１のボス部材１３２に
向けて図１及び図６において右方に延びている。第２の
ボス部材１７２も歯車６と一体に形成することができ
る。An annular boss portion 170 is integrally provided on the other surface of the gear 6 (right surface in FIGS. 1 and 6), and a cylindrical second boss member 172 is mounted in the boss portion 170. .. In the embodiment, the second boss member 172 rotates integrally with the gear 6 by inserting a pair of protrusions 174 provided on the end surface from the other side of the gear 6 into the through hole 106 formed in the gear 6. It is installed to do. The second boss member 172 extends rightward in FIGS. 1 and 6 toward the first boss member 132. The second boss member 172 can also be formed integrally with the gear 6.

【００２４】上記第１のボス部材１３２及び第２のボス
部材１７２に跨ってコイばね手段１２２が被嵌されてい
る。第２のばねクラッチ機構１０におけるユニット組立
体の第１のボス部材１３２の大径部１３４は上記第２の
ボス部材１７２に向けて延び、両ボス部材１３２及び１
７２の端面は相互に接触乃至近接せしめられている。こ
の第１のボス部材１３２の大径部１３４の外径と第２の
ボス部材１７２の外径とは実質上等しく、実施例ではコ
イルばね手段１２２は上記第１のボス部材１３２の大径
部１３４と第２のボス部材１７２の両者に跨って被嵌さ
れている。実施例においては、コイルばね手段１２２は
図１及び図６において右側から見て右巻（従って、歯車
６が矢印１７６（図６）で示す方向に回転されていると
きに、支持部材１５６にその回動を阻止する力が作用し
て支持部材１５６が歯車６に対して相対的に回転せしめ
られると収縮される方向）に捲回されている。かかるコ
イルばね手段１２２の一端１２２ａは、支持部材１５６
の他端部に形成された切欠き（実施例では、周方向に間
隔を置いて複数個形成された切欠きのいずれか）に挿入
されることによってこれに連結され、その他端１２２ｂ
は、歯車６の環状ボス部１７０に形成された切欠き１７
８（実施例では、周方向に間隔を置いて４個形成された
切欠き１７８のいずれか）に挿入されることによってこ
れに連結されている。The carp spring means 122 is fitted over the first boss member 132 and the second boss member 172. The large diameter portion 134 of the first boss member 132 of the unit assembly of the second spring clutch mechanism 10 extends toward the second boss member 172, and both boss members 132 and 1
The end faces of 72 are in contact with or in close proximity to each other. The outer diameter of the large diameter portion 134 of the first boss member 132 and the outer diameter of the second boss member 172 are substantially equal to each other. In the embodiment, the coil spring means 122 includes the large diameter portion of the first boss member 132. It is fitted over both 134 and the second boss member 172. In the exemplary embodiment, the coil spring means 122 has a right-handed winding when viewed from the right in FIGS. The support member 156 is wound in a direction in which it contracts when the support member 156 is caused to rotate relative to the gear 6 due to a force that prevents rotation. The one end 122a of the coil spring means 122 has a support member 156.
Is connected to the notch formed in the other end portion of the other end (in the embodiment, one of a plurality of notches formed at intervals in the circumferential direction), and the other end 122b.
Is a notch 17 formed in the annular boss portion 170 of the gear 6.
8 (in the embodiment, any one of four notches 178 formed at intervals in the circumferential direction) is connected to this.

【００２５】かくの通りであるので、歯車６が矢印１７
６で示す方向に回転されているときに電磁手段１２０が
付勢されると、後に詳述する如く、歯車６とアマチュア
組立体１１８とが相対的に回転され、これによってコイ
ルばね手段１２２が収縮され、かくして歯車６からの駆
動力は第２のボス部材１７２、コイルばね手段１２２及
び第１のボス部材１３２を介して軸部材４に伝達され
る。As described above, the gear 6 has the arrow 17
When the electromagnetic means 120 is biased while being rotated in the direction indicated by 6, the gear 6 and the armature assembly 118 are relatively rotated, which causes the coil spring means 122 to contract, as will be described in detail later. Thus, the driving force from the gear 6 is transmitted to the shaft member 4 via the second boss member 172, the coil spring means 122 and the first boss member 132.

【００２６】かくの通りの電磁制御ばねクラッチ機構２
においては、図１に示す通り、第１のばねクラッチ機構
８及び第２のばねクラッチ機構１０におけるロータ３０
及び１１６の片側にアマチュア組立体３２及び１１８が
配置され、ロータ３０及び１１６の他側に電磁手段３４
及び１２０が配置され、第１のばねクラッチ機構８にお
ける各種構成要素と第２のばねクラッチ機構１０におけ
る各種構成要素とが、歯車６を基準にして軸部材４の軸
線方向両側に実質上対象に配置されている。即ち、第１
のばねクラッチ機構８にあっては、歯車６の片面から図
１において左方に向って、第２のボス部材１０４、コイ
ルばね手段３６、第１のボス部材５０、アマチュア組立
体３２、ロータ３０及び電磁手段３４が配置され、第２
のばねクラッチ機構１０にあっては、歯車６の他面から
図１において右方に向って、第２のボス部材１７２、コ
イルばね手段１２２、第１のボス部材１３２、アマチュ
ア組立体１１８、ロータ１１６及び電磁手段１２０が配
置されている。The electromagnetically controlled spring clutch mechanism 2 as described above
In FIG. 1, the rotor 30 in the first spring clutch mechanism 8 and the second spring clutch mechanism 10 is shown in FIG.
And 116 are arranged on one side of the armature assemblies 32 and 118, and on the other side of the rotors 30 and 116 are electromagnetic means 34.
And 120 are arranged so that the various constituent elements of the first spring clutch mechanism 8 and the various constituent elements of the second spring clutch mechanism 10 are substantially symmetrical to each other on both axial sides of the shaft member 4 with respect to the gear 6. It is arranged. That is, the first
In the spring clutch mechanism 8 of FIG. 1, the second boss member 104, the coil spring means 36, the first boss member 50, the armature assembly 32, and the rotor 30 are directed from one surface of the gear 6 to the left in FIG. And an electromagnetic means 34 is arranged, the second
In the spring clutch mechanism 10 of FIG. 1, the second boss member 172, the coil spring means 122, the first boss member 132, the armature assembly 118, the rotor from the other surface of the gear 6 to the right in FIG. 116 and electromagnetic means 120 are arranged.

【００２７】図示の電磁制御ばねクラッチ機構２には、
電磁手段３４及び１２０の除勢時に歯車６からの駆動力
が直接軸部材４に伝達されて軸部材４が回転するおそれ
がある故に、軸部材４に常時回転を抑制する制動力を作
用せしめるためのブレーキ手段１８０（図１）が付設さ
れている。The illustrated electromagnetically controlled spring clutch mechanism 2 includes:
Since the driving force from the gear 6 may be directly transmitted to the shaft member 4 when the electromagnetic means 34 and 120 are deenergized, and the shaft member 4 may rotate, a braking force that constantly suppresses rotation is applied to the shaft member 4. Brake means 180 (FIG. 1) is attached.

【００２８】図１と共に図７を参照して、実施例のブレ
ーキ手段１８０について説明する。図示のブレーキ手段
１８０は回転部材１８２を含んでいる。軸部材４の他端
部は支持基体１４を貫通して外方に突出し、かかる突出
端に短筒状の回転部材１８２が装着されている。実施例
では、回転部材１８２にはこれを貫通して貫通孔１８４
が形成されており、この貫通孔１８４及び軸部材４に形
成された孔（図示せず）にピン部材１８６を圧入するこ
とによって回転部材１８２が軸部材４に固定されてい
る。従って、回転部材１８２は軸部材４と一体に回転す
る。実施例では、更に、回転部材１８２の内面（即ち、
支持基体１４に対向する面）に、合成皮又は合成ゴムの
如き高摩擦係数の材料から形成された摩擦部材１８８が
貼着されている。With reference to FIG. 7 together with FIG. 1, the braking means 180 of the embodiment will be described. The illustrated braking means 180 includes a rotating member 182. The other end of the shaft member 4 penetrates the support base 14 and projects outward, and a short tubular rotating member 182 is attached to the projecting end. In the embodiment, the rotary member 182 penetrates through the through hole 184.
The rotary member 182 is fixed to the shaft member 4 by press-fitting the pin member 186 into the through hole 184 and a hole (not shown) formed in the shaft member 4. Therefore, the rotating member 182 rotates integrally with the shaft member 4. In the exemplary embodiment, the inner surface (ie,
A friction member 188 made of a material having a high coefficient of friction such as synthetic leather or synthetic rubber is attached to a surface facing the support base 14).

【００２９】一方、軸部材４の他端部はスリーブ部材１
９０を介して支持基体１４に支持されている。スリーブ
部材１９０の一端にはフランジ部１９６が一体に設けら
れている。このスリーブ部材１９０は、フランジ部１９
６が支持基体１４の内側に位置する、即ちフランジ部１
９６が支持基体１４と電磁手段１２０間に位置するよう
に支持基体１４に装着され、そのスリーブ本体１９７は
支持基体１４に形成された開口を通して外方に延びてい
る。実施例では、図７に明確に示す通り、スリーブ本体
１９７の対向する外面には一対の平坦面１９０ａ（図７
において一方のみ示す）が形成されており、また支持基
体１４にはスリーブ本体１９７の縦断面の外形に対応し
た形状の開口が形成されており、それ故に、スリーブ本
体１９７を上記開口内に位置付けた状態においては、ス
リーブ部材１９０が支持基体１４に対して相対的に回転
することはない。ブレーキ手段１８０は、更に、制動部
材１９２を含んでいる。スリーブ状の部材から構成され
る制動部材１９２には、スリーブ本体１９７の縦断面の
外形に対応した形状の貫通孔１９９が形成されており、
（従って、制動部材１９２の貫通孔１９９を規定する内
周面には、スリーブ本体１９７の外周面に存在する一対
の平坦面１９０ａに対応した一対の平坦面１９２ａが形
成されている）、この制動部材１９２がスリーブ部材１
９２のスリーブ本体１９７の外側に装着されている。従
って、容易に理解される如く、制動部材１９２はスリー
ブ部材１９０に対して相対的に回動することはないが、
スリーブ部材１９０の軸線方向、即ち図１において左右
方向に相対的に移動自在である。実施例では、制動部材
１９２の右端にも回転部材１８２の外形に対応したフラ
ンジ部１９８が一体に形成されている。そして、更に、
このフランジ部１９８と支持基体１４間には、制動部材
１９２を被嵌してコイルばね１９４（偏倚手段を構成す
る）が配設されている。このコイルばね１９４はフラン
ジ部１９８に作用して制動部材１９２を回転部材１８２
に向けて、即ち図１において右方に向けて偏倚せしめる
作用をし、従って制動部材１９２のフランジ部１９８の
端面は、コイルばね１９４の作用によって回転部材１８
２の内面に配設された摩擦部材１８８の表面に弾性的に
圧接される。尚、実施例においては、回転部材１８２に
摩擦部材１８８を設けているが、これに代えて、制動部
材１９２、或いは回転部材１８２と制動部材１９２の双
方に摩擦部材を設けてもよい。On the other hand, the other end of the shaft member 4 is the sleeve member 1
It is supported by the support base 14 via 90. A flange portion 196 is integrally provided at one end of the sleeve member 190. The sleeve member 190 includes the flange portion 19
6 is located inside the support base 14, that is, the flange portion 1
96 is mounted on the support base 14 so as to be located between the support base 14 and the electromagnetic means 120, and a sleeve body 197 thereof extends outward through an opening formed in the support base 14. In the embodiment, as clearly shown in FIG. 7, a pair of flat surfaces 190a (FIG.
(Only one of which is shown in FIG. 2) is formed, and the supporting base 14 is formed with an opening having a shape corresponding to the outer shape of the longitudinal cross section of the sleeve body 197. Therefore, the sleeve body 197 is positioned in the opening. In the state, the sleeve member 190 does not rotate relative to the support base 14. The braking means 180 further includes a braking member 192. The braking member 192 composed of a sleeve-shaped member is provided with a through hole 199 having a shape corresponding to the outer shape of the sleeve body 197 in a vertical cross section.
(Therefore, a pair of flat surfaces 192a corresponding to the pair of flat surfaces 190a existing on the outer peripheral surface of the sleeve body 197 are formed on the inner peripheral surface defining the through hole 199 of the braking member 192). The member 192 is the sleeve member 1
It is attached to the outside of the sleeve body 197 of 92. Therefore, as can be easily understood, the braking member 192 does not rotate relative to the sleeve member 190,
It is relatively movable in the axial direction of the sleeve member 190, that is, in the left-right direction in FIG. In the embodiment, the flange portion 198 corresponding to the outer shape of the rotating member 182 is also integrally formed at the right end of the braking member 192. And further,
Between the flange portion 198 and the support base 14, a braking member 192 is fitted and a coil spring 194 (which constitutes a biasing means) is disposed. The coil spring 194 acts on the flange portion 198 to move the braking member 192 to the rotating member 182.
1, that is, toward the right in FIG. 1, the end face of the flange portion 198 of the braking member 192 is rotated by the action of the coil spring 194.
2 is elastically pressed against the surface of the friction member 188 disposed on the inner surface of 2. In the embodiment, the rotary member 182 is provided with the friction member 188, but instead of this, the braking member 192, or both the rotary member 182 and the braking member 192 may be provided with friction members.

【００３０】次に、上述した構成の電磁制御ばねクラッ
チ機構２の作用効果について説明する。Next, the function and effect of the electromagnetically controlled spring clutch mechanism 2 having the above-described structure will be described.

【００３１】まず、図１、図２及び図６を参照して、歯
車６が矢印１１０（図２）で示す所定方向に回転されて
いる場合について説明すると、かかる場合には第１のば
ねクラッチ機構８の電磁手段３４が付勢及び除勢され、
これによって歯車６の駆動力が選択的に軸部材４（軸部
材４は出力要素を構成する）に伝達される。First, referring to FIGS. 1, 2 and 6, the case where the gear 6 is rotated in a predetermined direction shown by an arrow 110 (FIG. 2) will be described. In such a case, the first spring clutch The electromagnetic means 34 of the mechanism 8 is energized and deenergized,
As a result, the driving force of the gear 6 is selectively transmitted to the shaft member 4 (the shaft member 4 constitutes an output element).

【００３２】即ち、歯車６が矢印１１０で示す方向に回
転されているときに電磁手段３４が付勢されると、電磁
手段３４の磁気的吸引力によってアマチュア７２が偏倚
ばね部材７６の弾性偏倚作用に抗して図１において左方
に移動してロータ３０の片面に磁気的に吸着せしめら
れ、アマチュア７２とロータ３０とが接続状態になる。
一方、歯車６は矢印１１０（図２）で示す方向に回転さ
れ、コイルばね手段３６を介して支持部材７４も同じ方
向に回転されている（支持部材７４と一体に偏倚ばね部
材７６及びアマチュア７２も回転されている）。従っ
て、アマチュア７２とロータ３０が磁気的に吸着されて
接続状態になると、軸部材４が停止していることも起因
して支持部材７４にその回動を阻止する力が作用する。
かくすると、かかる回動阻止力によって歯車６と支持部
材７４間に相対的速度が生じ、かかる速度差に起因して
コイルばね手段３６が収縮される。かくすると、コイル
ばね手段３６を介して第２のボス部材１０４と第１のボ
ス部材５０とが接続され、軸部材４は第１のボス部材５
０、コイルばね手段３６及び第２のボス部材１０４を介
して歯車６に駆動連結される。かくして、歯車６の矢印
１０で示す方向の回動力は軸部材４に伝達され、軸部材
４、従ってこれに接続された作動軸１８は歯車６の回転
に付随して矢印１１０で示す方向に回転される。That is, when the electromagnetic means 34 is biased while the gear 6 is rotated in the direction indicated by the arrow 110, the armature 72 is elastically biased by the biasing spring member 76 by the magnetic attraction force of the electromagnetic means 34. 1 to move to the left in FIG. 1 to be magnetically attracted to one surface of the rotor 30, and the armature 72 and the rotor 30 are connected.
On the other hand, the gear 6 is rotated in the direction indicated by the arrow 110 (FIG. 2), and the support member 74 is also rotated in the same direction via the coil spring means 36 (the bias spring member 76 and the armature 72 are integrated with the support member 74). Has also been rotated). Therefore, when the armature 72 and the rotor 30 are magnetically attracted and brought into a connected state, a force that prevents the rotation of the support member 74 acts due to the fact that the shaft member 4 is stopped.
By doing so, a relative speed is generated between the gear 6 and the support member 74 due to the rotation inhibiting force, and the coil spring means 36 is contracted due to the speed difference. In this way, the second boss member 104 and the first boss member 50 are connected via the coil spring means 36, and the shaft member 4 becomes the first boss member 5.
0, the coil spring means 36 and the second boss member 104 are drivingly connected to the gear 6. Thus, the rotational force of the gear 6 in the direction indicated by the arrow 10 is transmitted to the shaft member 4, and the shaft member 4, and thus the operating shaft 18 connected thereto, rotates in the direction indicated by the arrow 110, following the rotation of the gear 6. To be done.

【００３３】他方、電磁手段３４が除勢されると、偏倚
ばね部材７６の弾性偏倚作用によってアマチュア７２が
図１において右方に移動してロータ３０の片面から離
れ、アマチュア７２とロータ３０との上記接続状態が解
除される（即ち、アマチュア７２は偏倚ばね部材７６の
作用によって図１に示す位置に復帰する）。このアマチ
ュア７２の復帰時には、支持部材７４とアマチュア７２
間に介在されている偏倚ばね部材７６の弾性偏倚作用に
よってロータ３０の片面から離隔する方向に移動される
ため、アマチュア７２とロータ３０の接続が迅速に解除
される。また、この復帰時には第１のボス部材５０の中
径部５６の外径と支持部材７４の内径部に存在する間隙
に起因してアマチュア７２が軸部材４に対して幾分傾斜
する傾向にあるが、実施例においては支持部材７４の一
端面に設けられた突起９６がロータ３０の片面に接触乃
至近接せしめられている故に、アマチュア７２が若干傾
動した際には支持部材７４の突起９６の前端面がロータ
３０の片面に接触するようになり、アマチュア７２がロ
ータ３０の片面に接触することによる応答性の低下が効
果的に防止される。更に、実施例においては、支持部材
７４の環状フランジ７８の先端もロータ３０の片面に接
触乃至近接されている故に、支持部材７４自体の所謂ガ
タも少なくすることができ、応答性の低下が一層防止さ
れる。アマチュア７２とロータ３０の接続状態が解除さ
れると、上述した駆動伝達時に蓄えられたコイルばね手
段３６の弾性力によって支持部材７４が矢印１１０で示
す方向に更に若干回動され、コイルばね手段３６は拡張
される。コイルばね手段３６の拡張の際には、支持部材
７４が第１のボス部材５０に回転自在に装着され、かか
る支持部材７４には偏倚ばね部材７６、アマチュア７２
及びプレート部材８６が装着されているのみであるた
め、支持部材７４は大きい抵抗を受けることなくコイル
ばね手段３６の弾性力によって容易に迅速に所要の通り
回転される。かくの如くコイルばね手段３６が拡張する
と、第２のボス部材１０４と第１のボス部材５０とのコ
イルばね手段３６による接続が解除され、かくして歯車
６と軸部材４の駆動連結が解除される。かかる電磁手段
３４の除勢時においては、容易に理解される如く、歯車
６の回転に付随してコイルばね手段３６を介して支持部
材７４、偏倚ばね部材７６及びアマチュア７２が回転す
るのみである。また、歯車６が矢印１１０で示す方向に
回転されているときには、第２のばねクラッチ機構１０
の電磁手段１２０は付勢されず、それ故に、第２のばね
クラッチ機構１０においては、歯車６の矢印１１０で示
す方向の回転に付随してコイルばね手段１２２を介して
支持部材１５６、偏倚ばね部材１５８及びアマチュア１
５４が回転するのみである。On the other hand, when the electromagnetic means 34 is de-energized, the elastic biasing action of the biasing spring member 76 causes the armature 72 to move to the right in FIG. 1 and separate from one side of the rotor 30 to separate the armature 72 from the rotor 30. The connection state is released (that is, the armature 72 is returned to the position shown in FIG. 1 by the action of the biasing spring member 76). When the amateur 72 returns, the support member 74 and the amateur 72
Due to the elastic biasing action of the biasing spring member 76 interposed therebetween, the biasing spring member 76 is moved in a direction away from one surface of the rotor 30, so that the connection between the armature 72 and the rotor 30 is quickly released. Further, at the time of this return, the armature 72 tends to be slightly inclined with respect to the shaft member 4 due to the gap between the outer diameter of the middle diameter portion 56 of the first boss member 50 and the inner diameter portion of the support member 74. However, in the embodiment, since the projection 96 provided on one end surface of the support member 74 is brought into contact with or close to one surface of the rotor 30, the front end of the projection 96 of the support member 74 is slightly tilted when the armature 72 is slightly tilted. Since the surface comes into contact with one surface of the rotor 30, the decrease in responsiveness due to the contact of the armature 72 with the one surface of the rotor 30 is effectively prevented. Further, in the embodiment, since the tip of the annular flange 78 of the support member 74 is also in contact with or close to one surface of the rotor 30, so-called rattling of the support member 74 itself can be reduced, and the responsiveness is further reduced. To be prevented. When the connection between the armature 72 and the rotor 30 is released, the elastic force of the coil spring means 36 accumulated during the above-described drive transmission causes the support member 74 to further rotate slightly in the direction indicated by the arrow 110, and the coil spring means 36. Is expanded. When the coil spring means 36 is expanded, the support member 74 is rotatably attached to the first boss member 50, and the bias spring member 76 and the armature 72 are attached to the support member 74.
Since only the plate member 86 is attached, the supporting member 74 can be easily and quickly rotated by the elastic force of the coil spring means 36 without receiving a large resistance. When the coil spring means 36 expands in this way, the connection between the second boss member 104 and the first boss member 50 by the coil spring means 36 is released, and thus the drive connection between the gear 6 and the shaft member 4 is released. .. When the electromagnetic means 34 is deenergized, as is easily understood, the support member 74, the bias spring member 76, and the armature 72 only rotate via the coil spring means 36 in association with the rotation of the gear 6. .. Further, when the gear 6 is rotated in the direction indicated by the arrow 110, the second spring clutch mechanism 10
The electromagnetic means 120 is not biased, and therefore, in the second spring clutch mechanism 10, accompanying the rotation of the gear 6 in the direction indicated by the arrow 110, via the coil spring means 122, the support member 156, the bias spring. Member 158 and amateur 1
Only 54 rotates.

【００３４】上述したとは反対に、歯車６が矢印１７６
（図６）で示す方向に回転されている場合には第２のば
ねクラッチ機構１０の電磁手段１２０が付勢及び除勢さ
れ、これによって歯車６の駆動力が選択的に軸部材４に
伝達される。Contrary to the above, the gear 6 is indicated by the arrow 176.
When rotating in the direction shown in FIG. 6, the electromagnetic means 120 of the second spring clutch mechanism 10 is energized and deenergized, whereby the driving force of the gear 6 is selectively transmitted to the shaft member 4. To be done.

【００３５】即ち、歯車６が矢印１７６で示す方向に回
転されているときに電磁手段１２０が付勢されると、電
磁手段１２０の磁気的吸引によってアマチュア１５４が
偏倚ばね部材１５８の弾性偏倚作用に抗して図１におい
て右方に移動してロータ１１６の片面に磁気的に吸着せ
しめられ、アマチュア１５４とロータ１１６とが接続状
態になる。かくすると、歯車６と支持部材１５６間に相
対的速度差が生じ、かかる速度差に起因してコイルばね
手段１２２が収縮される。かく収縮されると、コイルば
ね手段１２２を介して第２のボス部材１７２と第１のボ
ス部材１３２とが接続され、軸部材４は第１のボス部材
１３２、コイルばね手段１２２及び第２のボス部材１７
２を介して歯車６に駆動連結される。かくして、歯車６
の矢印１７６で示す方向の回動力は軸部材４に伝達さ
れ、軸部材４、従ってこれに接続された作動軸１８は歯
車６の回転に付随して矢印１７６で示す方向に回転され
る。That is, when the electromagnetic means 120 is energized while the gear 6 is rotated in the direction shown by the arrow 176, the magnetic attraction of the electromagnetic means 120 causes the armature 154 to act on the elastic biasing action of the biasing spring member 158. On the contrary, it moves rightward in FIG. 1 and is magnetically attracted to one surface of the rotor 116, so that the armature 154 and the rotor 116 are connected. This causes a relative speed difference between the gear 6 and the support member 156, and the coil spring means 122 contracts due to the speed difference. When contracted in this manner, the second boss member 172 and the first boss member 132 are connected to each other via the coil spring means 122, and the shaft member 4 has the first boss member 132, the coil spring means 122, and the second boss member 132. Boss member 17
It is drivingly connected to the gear 6 via 2. Thus, gear 6
The rotational force in the direction indicated by the arrow 176 is transmitted to the shaft member 4, and the shaft member 4, and thus the operating shaft 18 connected thereto, is rotated in the direction indicated by the arrow 176 in association with the rotation of the gear 6.

【００３６】他方、電磁手段１２０が除勢されると、偏
倚ばね部材１５８の弾性偏倚作用によってアマチュア１
５４が図１において左方に移動してロータ１１６の片面
から離れ、アマチュア１５４とロータ１１６との上記接
続状態が解除される（即ち、アマチュア１５４は偏倚ば
ね部材１５８の作用によって図１に示す位置に復帰す
る）。かくすると、上述した駆動伝達時に蓄えられたコ
イルばね手段１２２の弾性力によって支持部材１５６が
矢印１７６で示す方向に更に若干回動され、コイルばね
手段１２２は拡張される。かくの如くコイルばね手段１
２２が拡張すると、第２のボス部材１７２と第１のボス
部材１３２とのコイルばね手段１２２による接続が解除
され、かくして歯車６と軸部材４の駆動連結が解除され
る。かかる電磁手段１２０の除勢時においては、容易に
理解される如く、歯車６の回転に付随してコイルばね手
段１２２を介して支持部材１５６、偏倚ばね部材１５８
及びアマチュア１５４が回転するのみである。従って、
第２のばねクラッチ機構１０においても、第１のばねク
ラッチ機構８と同様の効果が達成される。また、歯車６
が矢印１７６で示す方向に回転されているときには、第
１のばねクラッチ機構８の電磁手段３４は付勢されず、
それ故に、第１のばねクラッチ機構８においては、歯車
６の矢印１７６で示す方向の回転に付随してコイルばね
手段３６を介して支持部材７４、偏倚ばね部材７６及び
アマチュア７２が回転するのみである。On the other hand, when the electromagnetic means 120 is de-energized, the elastic biasing action of the biasing spring member 158 causes the amateur 1
54 moves to the left in FIG. 1 and separates from one side of the rotor 116, and the above-mentioned connection state between the armature 154 and the rotor 116 is released (that is, the armature 154 is moved to the position shown in FIG. 1 by the action of the biasing spring member 158). Return to). By doing so, the elastic force of the coil spring means 122 stored at the time of drive transmission described above causes the support member 156 to further rotate slightly in the direction indicated by the arrow 176, and the coil spring means 122 is expanded. Thus, the coil spring means 1
When 22 is expanded, the connection between the second boss member 172 and the first boss member 132 by the coil spring means 122 is released, and thus the drive connection between the gear 6 and the shaft member 4 is released. When the electromagnetic means 120 is deenergized, as will be easily understood, the support member 156 and the bias spring member 158 are accompanied by the rotation of the gear 6 via the coil spring means 122.
And the amateur 154 only rotates. Therefore,
Also in the second spring clutch mechanism 10, the same effect as that of the first spring clutch mechanism 8 is achieved. Also, the gear 6
Is rotating in the direction indicated by the arrow 176, the electromagnetic means 34 of the first spring clutch mechanism 8 is not biased,
Therefore, in the first spring clutch mechanism 8, the support member 74, the bias spring member 76, and the armature 72 are only rotated via the coil spring means 36 in association with the rotation of the gear 6 in the direction indicated by the arrow 176. is there.

【００３７】上述の作動において、ブレーキ手段１８０
を備えていない場合には軸部材４が回転するおそれがあ
った。更に詳細に説明すると、歯車６と軸部材４との間
の摩擦係数が大きいと電磁手段３４及び１２０の除勢時
に歯車６の回動力が直接軸部材４に伝達され、かく伝達
される比較的小さい力によって軸部材４が回転するおそ
れがあった。かかる傾向は、歯車６と軸部材４間の摩擦
力、言い換えると歯車６と軸部材４間の摩擦係数、歯車
６に作用する歯車６の半径方向（即ち軸部材４の軸線に
対して実質上垂直な方向）の負荷等に影響され、上記摩
擦力が大きいときに軸部材４が回転して電磁手段３４及
び１２０が除勢されているにもかかわらず作動軸１８が
回転する不都合が存在する。In the above operation, the braking means 180
If the shaft member 4 is not provided, the shaft member 4 may rotate. More specifically, when the coefficient of friction between the gear 6 and the shaft member 4 is large, the rotational force of the gear 6 is directly transmitted to the shaft member 4 when the electromagnetic means 34 and 120 are deenergized, and thus relatively transmitted. The shaft member 4 may be rotated by a small force. This tendency is due to the frictional force between the gear 6 and the shaft member 4, in other words, the coefficient of friction between the gear 6 and the shaft member 4, and the radial direction of the gear 6 acting on the gear 6 (that is, substantially with respect to the axis of the shaft member 4). When the frictional force is large, the shaft member 4 rotates and the electromagnetic means 34 and 120 are de-energized, but the working shaft 18 rotates due to the influence of the load in the vertical direction). ..

【００３８】これに対して、実施例の如く、軸部材４に
関連してブレーキ手段１８０を付設した場合には、比較
的弱い力による軸部材４の回動をブレーキ手段１８０の
作用、即ち回転部材１８２と制動部材１９２間の摩擦力
によって確実に阻止することができ、かくして電磁手段
３４及び１２０の除勢時における軸部材４の回転を防止
することができる。実施例においては、回転部材１８２
と制動部材１９２間に摩擦部材１８８が介在され、更に
コイルばね１９４の作用によって回転部材１８２と制動
部材１９２とが圧接される構成であり、それ故に、電磁
手段３４及び１２０の除勢時における軸部材４の回転を
一層確実に防止することができる。On the other hand, when the braking means 180 is provided in association with the shaft member 4 as in the embodiment, the rotation of the shaft member 4 by a relatively weak force causes the braking means 180 to act, that is, rotate. The frictional force between the member 182 and the braking member 192 can surely prevent the rotation of the shaft member 4 when the electromagnetic means 34 and 120 are deenergized. In the exemplary embodiment, rotating member 182
The friction member 188 is interposed between the brake member 192 and the braking member 192, and the rotating member 182 and the braking member 192 are pressed against each other by the action of the coil spring 194. Therefore, the shafts when the electromagnetic means 34 and 120 are de-energized. The rotation of the member 4 can be prevented more reliably.

【００３９】尚、上述したブレーキ手段１８０は、図示
の電磁制御ばねクラッチ機構２に限定されず、例えば特
願昭６０−７８４３９号の明細書及び図面に開示されて
いる電磁制御ばねクラッチ機構等にも同様に適用するこ
とができる。The braking means 180 described above is not limited to the electromagnetic control spring clutch mechanism 2 shown in the drawings, and may be the electromagnetic control spring clutch mechanism disclosed in the specification and drawings of Japanese Patent Application No. 60-78439. Can be similarly applied.

【００４０】尚、上述の実施例における電磁制御ばねク
ラッチ機構２においては、第１のばねクラッチ機構８及
び第２のばねクラッチ機構１０におけるロータ３０及び
１１６、アマチュア組立体３２及び１１８、並びに第１
のボス部材５０及び１３２がユニット組立体としてユニ
ット化されている故に、組立要素が少なくなり、特に重
要であるロータ３０及び１１６とアマチュア７２及び１
５８の間隔をも一定に保持することができる。また、ア
マチュア７２及び１５４が偏倚ばね部材７６及び１５８
を介してプレート部材８６及び１６６によって支持部材
７４及び１５６の一端面に固定される故に、プレート部
材８６及び１６６がアマチュア７２及び１５４の環状中
央部８０及び１６０のほぼ全域に実質上均一に作用し、
かかる環状中央部８０及び１６０をプレート部材８６及
び１６６と支持部材７４及び１５６間に確実に固定する
ことができると共に偏倚ばね部材７６及び１５８、支持
部材７４及び１５６並びにプレート部材８６及び１６６
から成る組立要素を小型化することもできる。更に、か
くすることによって、支持部材７４及び１５６への固定
に伴うアマチュア７２及び１５４の変形も防止すること
ができ、このことに起因して応答性も向上する。In the electromagnetically controlled spring clutch mechanism 2 of the above-described embodiment, the rotors 30 and 116, the armature assemblies 32 and 118, and the first spring clutch mechanism 8 and the second spring clutch mechanism 10 of the first and second spring clutch mechanisms 10 and 1st, respectively.
Since the boss members 50 and 132 of FIG. 1 are unitized as a unit assembly, the number of assembly elements is reduced, and the rotors 30 and 116 and the armatures 72 and 1 which are particularly important
The spacing of 58 can also be kept constant. Also, the amateurs 72 and 154 are biased spring members 76 and 158.
Since the plate members 86 and 166 are fixed to one end surfaces of the support members 74 and 156 by the plate members 86 and 166, the plate members 86 and 166 act substantially uniformly over the entire annular central portions 80 and 160 of the armatures 72 and 154. ,
The annular central portions 80 and 160 can be securely fixed between the plate members 86 and 166 and the support members 74 and 156, and the bias spring members 76 and 158, the support members 74 and 156, and the plate members 86 and 166 are also included.
The assembly element consisting of can also be miniaturized. Furthermore, by doing so, it is possible to prevent the deformation of the armatures 72 and 154 due to the fixing to the support members 74 and 156, and the response is also improved due to this.

【００４１】更にまた、図示の電磁制御ばねクラッチ機
構２においては、第１のばねクラッチ機構８における第
１のボス部材５０が軸部材４の片側から圧入されて大径
部４ａの片端面に当接し、るた第２のばねクラッチ機構
１０における第１のボス部材１３２が軸部材４の他側か
ら圧入されて大径部４ａの他端面に当接している故に、
第１のボス部材５０及び１３２と共に第１のボス部材５
０及び１３２間に位置する歯車６並びに第２のボス部材
１０４及び１７２の軸部材４に対する移動が確実に阻止
され、更には、例えば電磁制御ばねクラッチ機構２を縦
に配置した（軸部材４を縦に配置する）場合において
も、大径部４ａが設けられていることに起因して各種構
成要素間の間隙が一個所に集中的に累積されることはな
く、従って第１のボス部材５０及び１３２と第２のボス
部材１０４及び１７２間にコイルばね手段３６及び１２
２の一部が侵入するのも確実に防止される。Furthermore, in the electromagnetically controlled spring clutch mechanism 2 shown, the first boss member 50 of the first spring clutch mechanism 8 is press-fitted from one side of the shaft member 4 to contact one end surface of the large diameter portion 4a. Since the first boss member 132 of the slack second spring clutch mechanism 10 is press-fitted from the other side of the shaft member 4 and is in contact with the other end surface of the large diameter portion 4a,
The first boss member 5 together with the first boss members 50 and 132
The movement of the gear 6 located between 0 and 132 and the second boss members 104 and 172 with respect to the shaft member 4 is reliably prevented, and further, for example, the electromagnetically controlled spring clutch mechanism 2 is vertically arranged (the shaft member 4 is Even in the case of arranging vertically, the gaps between the various components are not concentrated in one place due to the large diameter portion 4a being provided, and therefore the first boss member 50 And 132 and the second boss members 104 and 172 between the coil spring means 36 and 12
It is also surely prevented that a part of 2 enters.

【００４２】以上、図１乃至図７に基づいて説明した電
磁制御ばねクラッチ機構は、例えば図８及び図９に示す
通りに組合せて用いることによって、例えばマッサージ
器等に好都合に適用することができる。図８及び図９に
おいて、支持基体１２及び１４間には、所定間隔を置い
て２個の電磁制御ばねクラッチ機構２ａ及び２ｂが配設
されている。各電磁制御ばねクラッチ機構２ａ及び２ｂ
は、図１乃至図７に示す電磁制御ばねクラッチ機構２と
実質上同一の構成であり、それ故にその詳細な説明につ
いては省略する。The electromagnetically controlled spring clutch mechanism described above with reference to FIGS. 1 to 7 can be conveniently applied to, for example, a massager by using it in combination as shown in FIGS. 8 and 9. .. In FIG. 8 and FIG. 9, two electromagnetic control spring clutch mechanisms 2a and 2b are arranged between the supporting bases 12 and 14 at a predetermined interval. Each electromagnetic control spring clutch mechanism 2a and 2b
Has substantially the same structure as the electromagnetically controlled spring clutch mechanism 2 shown in FIGS. 1 to 7, and therefore its detailed description is omitted.

【００４３】支持基体１２及び１４間には、更に、回転
軸２００が回転自在に装着されている。この回転軸２０
０には歯車２０２が装着され、歯車２０２は片方の電磁
制御ばねクラッチ機構２ａにおける歯車６ａに噛合さ
れ、上記歯車６ａは他方の電磁制御ばねクラッチ機構２
ｂにおける歯車６ｂに噛合されている。回転軸２００
は、図示していないが正逆転可能な伝動モータの如き駆
動源に駆動連結されている。従って、図８に示す通り、
駆動源（図示せず）の正転によって回転軸２００が矢印
２０４で示す方向に回転されると、歯車２０２を介して
歯車６ａが矢印２１０で示す方向に回転され、更に歯車
６ｂが矢印２１２で示す方向に回転される。一方、駆動
源（図示せず）の逆転によって回転軸２００が矢印２０
６で示す方向に回転されると、歯車２０２を介して歯車
６ａが矢印２０８で示す方向に回転され、更に歯車６ｂ
が矢印２１４で示す方向に回転される。A rotary shaft 200 is further rotatably mounted between the support bases 12 and 14. This rotating shaft 20
The gear 202 is attached to the gear 0, the gear 202 is meshed with the gear 6a in one electromagnetic control spring clutch mechanism 2a, and the gear 6a is the other electromagnetic control spring clutch mechanism 2a.
It is meshed with the gear 6b at b. Rotating shaft 200
Is drivingly connected to a drive source such as a transmission motor (not shown) capable of forward and reverse rotation. Therefore, as shown in FIG.
When the rotary shaft 200 is rotated in the direction indicated by the arrow 204 by the normal rotation of the drive source (not shown), the gear 6a is rotated in the direction indicated by the arrow 210 via the gear 202, and the gear 6b is further indicated by the arrow 212. It is rotated in the direction shown. On the other hand, the rotation of the drive shaft (not shown) causes the rotary shaft 200 to move in the direction of the arrow 20.
When the gear 6a is rotated in the direction indicated by 6, the gear 6a is rotated in the direction indicated by the arrow 208 via the gear 202, and the gear 6b is further rotated.
Is rotated in the direction indicated by arrow 214.

【００４４】図示の複合クラッチ機構においては、上述
した記載から容易に理解される如く、回転軸２００が矢
印２０４で示す方向に回転されているときには、片方の
電磁制御ばねクラッチ機構２ａにおける第１のばねクラ
ッチ機構８ａと他方の電磁制御ばねクラッチ機構２ｂに
おける第２のばねクラッチ機構１０ｂとが付勢及び除勢
され（このとき、片方の電磁制御ばねクラッチ機構２ａ
における第２のばねクラッチ機構１０ａ及び他方の電磁
制御ばねクラッチ機構２ｂにおける第１のばねクラッチ
機構８ｂは付勢されることはない）、上述したとは反対
に回転軸２００が矢印２０６で示す方向に回転されてい
るときには、片方の電磁制御ばねクラッチ機構２ａにお
ける第２のばねクラッチ機構１０ａと他方の電磁制御ば
ねクラッチ機構２ｂにおける第１のばねクラッチ機構８
ｂとが付勢及び除勢される（このとき、片方の電磁制御
ばねクラッチ機構２ａにおける第１のばねクラッチ機構
８ａ及び他方の電磁制御ばねクラッチ機構２ｂにおける
第２のばねクラッチ機構１０ｂは付勢されることはな
い）。尚、図示の実施例では歯車６ａと歯車６ｂとが反
対方向に回転されるように噛合されているが、歯車６ａ
と歯車６ｂとが同一方向に回転されるように駆動連結さ
れている（例えば歯車６ａと歯車６ｂの間にアイドル歯
車が介在されている）場合には、回転軸２００が矢印２
０４で示す方向に回転されているときには電磁制御ばね
クラッチ機構２ａ及び２ｂにおける第１のばねクラッチ
機構８ａ及び８ｂが付勢及び除勢され（このとき、電磁
制御ばねクラッチ機構２ａ及び２ｂにおける第２のばね
クラッチ機構１０ａ及び１０ｂが付勢されることはな
い）、上述したは反対に回転軸２００が矢印２０６で示
す方向に回転されているときには電磁制御ばねクラッチ
機構２ａ及び２ｂにおける第２のばねクラッチ機構１０
ａ及び１０ｂが付勢及び除勢される（このとき、電磁制
御ばねクラッチ機構２ａ及び２ｂにおける第１のばねク
ラッチ機構８ａ及び８ｂが付勢されることはない）。In the illustrated composite clutch mechanism, as will be easily understood from the above description, when the rotary shaft 200 is rotated in the direction indicated by the arrow 204, the first clutch in the electromagnetically controlled spring clutch mechanism 2a is rotated. The spring clutch mechanism 8a and the second spring clutch mechanism 10b in the other electromagnetically controlled spring clutch mechanism 2b are energized and deenergized (at this time, one electromagnetically controlled spring clutch mechanism 2a
The second spring clutch mechanism 10a in FIG. 4 and the first spring clutch mechanism 8b in the other electromagnetically controlled spring clutch mechanism 2b are not urged), but in the opposite direction to the above, the rotation shaft 200 is in the direction indicated by the arrow 206. The second spring clutch mechanism 10a in the one electromagnetically controlled spring clutch mechanism 2a and the first spring clutch mechanism 8 in the other electromagnetically controlled spring clutch mechanism 2b when being rotated to the right.
b is energized and deenergized (at this time, the first spring clutch mechanism 8a in one electromagnetically controlled spring clutch mechanism 2a and the second spring clutch mechanism 10b in the other electromagnetically controlled spring clutch mechanism 2b are energized. Never be done). In the illustrated embodiment, the gear 6a and the gear 6b are meshed so as to rotate in opposite directions.
And the gear 6b are drivingly connected so as to rotate in the same direction (for example, an idle gear is interposed between the gear 6a and the gear 6b), the rotary shaft 200 is indicated by the arrow 2
When being rotated in the direction indicated by 04, the first spring clutch mechanisms 8a and 8b in the electromagnetic control spring clutch mechanisms 2a and 2b are urged and deenergized (at this time, the second spring clutch mechanisms 2a and 2b in the electromagnetic control spring clutch mechanisms 2a and 2b are activated). The spring clutch mechanisms 10a and 10b are not biased), and the second spring in the electromagnetically controlled spring clutch mechanisms 2a and 2b when the rotary shaft 200 is rotated in the direction indicated by the arrow 206, conversely to the above. Clutch mechanism 10
a and 10b are energized and deenergized (at this time, the first spring clutch mechanisms 8a and 8b in the electromagnetically controlled spring clutch mechanisms 2a and 2b are not energized).

【００４５】回転軸２００が矢印２０４で示す方向に回
転されているときに、電磁制御ばねクラッチ機構２ａの
第１のばねクラッチ機構８ａが付勢されると、かかる第
１のばねクラッチ機構８ａを介して歯車６ａの矢印２１
０で示す方向の回動力が軸部材４ａに伝達され、かくし
て作動軸１８ａは矢印２１０で示す方向に回転される。
また、上述したときに電磁制御ばねクラッチ機構２ｂの
第２のばねクラッチ機構１０ｂが付勢されると、第２の
ばねクラッチ機構１０ｂを介して歯車６ｂの矢印２１２
で示す方向の回動力が軸部材４ｂに伝達され、かくして
作動軸１８ｂは矢印２１２で示す方向に回転される。When the first spring clutch mechanism 8a of the electromagnetically controlled spring clutch mechanism 2a is biased while the rotary shaft 200 is rotating in the direction indicated by the arrow 204, the first spring clutch mechanism 8a is activated. Through the arrow 21 of the gear 6a
The rotational force in the direction indicated by 0 is transmitted to the shaft member 4a, and thus the operating shaft 18a is rotated in the direction indicated by the arrow 210.
Further, when the second spring clutch mechanism 10b of the electromagnetically controlled spring clutch mechanism 2b is biased at the time described above, the arrow 212 of the gear 6b passes through the second spring clutch mechanism 10b.
The turning force in the direction indicated by is transmitted to the shaft member 4b, and thus the operating shaft 18b is rotated in the direction indicated by arrow 212.

【００４６】他方、回転軸２００が矢印２０６で示す方
向に回転されているときに、電磁制御ばねクラッチ機構
２ａの第２のばねクラッチ機構８ｂが付勢されると、か
かる第１のばねクラッチ機構８ｂを介して歯車６ａの矢
印２０８で示す方向の回動力が軸部材４ａに伝達され、
かくして作動軸１８ａは矢印２０８で示す方向に回転さ
れる。また、上述したときに電磁制御ばねクラッチ機構
２ｂの第１のばねクラッチ機構１０ａが付勢されると、
第１のばねクラッチ機構１０ａを介して歯車６ｂの矢印
２１４で示す方向の回動力が軸部材４ｂに伝達され、か
くして作動軸１８ｂは矢印２１４で示す方向に回転され
る。On the other hand, when the second spring clutch mechanism 8b of the electromagnetically controlled spring clutch mechanism 2a is biased while the rotary shaft 200 is rotating in the direction indicated by the arrow 206, the first spring clutch mechanism is activated. The rotational force of the gear 6a in the direction indicated by the arrow 208 is transmitted to the shaft member 4a via 8b,
Thus, the operating shaft 18a is rotated in the direction indicated by the arrow 208. Further, when the first spring clutch mechanism 10a of the electromagnetically controlled spring clutch mechanism 2b is biased at the time described above,
The rotational force of the gear 6b in the direction indicated by the arrow 214 is transmitted to the shaft member 4b via the first spring clutch mechanism 10a, and thus the operating shaft 18b is rotated in the direction indicated by the arrow 214.

【００４７】尚、電磁制御ばねクラッチ機構２ａ、２ｂ
の軸部材４ａ、４ｂにはブレーキ手段１８０ａ、１８０
ｂが各々配設されており、軸部材４ａ、４ｂには常に回
転を抑制する作動力が作用せしめられているので、第１
のばねクラッチ機構８ａ（又は８ｂ）及び第２のばねク
ラッチ機構１０ａ（又は１０ｂ）が除勢されているとき
には、ブレーキ手段１８０ａ、１８０ｂの制動作用によ
り、軸部材４ａ（又は４ｂ）の回転は確実に防止され
る。Incidentally, the electromagnetically controlled spring clutch mechanisms 2a, 2b.
Brake means 180a, 180
b are provided respectively, and the operating force for suppressing the rotation is always applied to the shaft members 4a and 4b.
When the second spring clutch mechanism 8a (or 8b) and the second spring clutch mechanism 10a (or 10b) are deenergized, the rotation of the shaft member 4a (or 4b) is ensured by the braking action of the braking means 180a, 180b. To be prevented.

【００４８】[0048]

【発明の効果】本発明による電磁制御ばねクラッチ機構
は以上のように構成され、出力回転要素である軸部材に
該軸部材の回動を制動するためのブレーキ手段を設けた
ので、該軸部材は、該ブレーキ手段によって常時回転を
抑制するための制動力が作用せしめられている。従っ
て、電磁手段が除勢されているときにおいて出力回転要
素が回転するのを確実に防止することができるととも
に、電磁手段の付勢後に除勢されたときにおいても出力
回転要素の回転を瞬時に停止することができる。The electromagnetically controlled spring clutch mechanism according to the present invention is constructed as described above, and the shaft member which is the output rotary element is provided with the brake means for braking the rotation of the shaft member. The braking means always applies a braking force for suppressing the rotation. Therefore, it is possible to reliably prevent the output rotary element from rotating when the electromagnetic means is deenergized, and instantaneously rotate the output rotary element even when the electromagnetic means is deenergized after being biased. You can stop.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明による電磁制御ばねクラッチ機構の一実
施例を示す断面図。FIG. 1 is a sectional view showing an embodiment of an electromagnetically controlled spring clutch mechanism according to the present invention.

【図２】図１の電磁制御ばねクラッチ機構における第１
のばねクラッチ機構を分解して示す分解斜視図。FIG. 2 is a first view of the electromagnetically controlled spring clutch mechanism of FIG.
FIG. 3 is an exploded perspective view showing the spring clutch mechanism of FIG.

【図３】図２の第１のばねクラッチ機構におけるユニッ
ト組立体を分解して示す分解斜視図。FIG. 3 is an exploded perspective view showing an exploded unit assembly of the first spring clutch mechanism of FIG.

【図４】図２の第１のばねクラッチ機構におけるユニッ
ト組立体を軸部材に装着した状態を示す断面図。4 is a cross-sectional view showing a state in which the unit assembly in the first spring clutch mechanism of FIG. 2 is attached to the shaft member.

【図５】図２のユニット組立体の偏倚ばね部材の固定方
法を説明するための部分拡大断面図。5 is a partially enlarged cross-sectional view for explaining a method of fixing the bias spring member of the unit assembly of FIG.

【図６】図１の電磁制御ばねクラッチ機構における第２
のばねクラッチ機構を分解して示す分解斜視図。6 is a second view of the electromagnetically controlled spring clutch mechanism of FIG.
FIG. 3 is an exploded perspective view showing the spring clutch mechanism of FIG.

【図７】図１の電磁制御ばねクラッチ機構におけるブレ
ーキ手段のスリーブ部材及び回転阻止部材を示す斜視
図。7 is a perspective view showing a sleeve member and a rotation blocking member of the braking means in the electromagnetically controlled spring clutch mechanism of FIG.

【図８】図１に示す電磁制御ばねクラッチ機構を用いた
一適用例を示す側面図。8 is a side view showing an application example using the electromagnetically controlled spring clutch mechanism shown in FIG.

【図９】図８におけるＡーＡ線からみたところを示す
図。FIG. 9 is a diagram showing a view seen from the line AA in FIG. 8.

【符号の説明】[Explanation of symbols]

２，２ａ及び２ｂ：電磁制御ばねクラッチ機構 ４，４ａ及び４ｂ：軸部材 ６，６ａ及び６ｂ：歯車 ８，８ａ及び８ｂ：第１のばねクラッチ機構 １０，１０ａ及び１０ｂ：第２のばねクラッチ機構 ３０及び１１６：ロータ ３２及び１１８：アマチュア組立体 ３４及び１２０：電磁手段 ３６及び１２２：コイルばね手段 ５０及び１３２：第１のボス部材 ７２及び１５４：アマチュア ７４及び１５６：支持部材 ７６及び１５８：偏倚ばね部材 １０４及び１７２：第１のボス部材 １８０，１８０ａ及び１８０ｂ：ブレーキ手段 １８２：回転部材 １８８：摩擦部材 １９２：制動部材 2, 2a and 2b: Electromagnetically controlled spring clutch mechanism 4, 4a and 4b: Shaft member 6, 6a and 6b: Gears 8, 8a and 8b: First spring clutch mechanism 10, 10a and 10b: Second spring clutch mechanism 30 and 116: Rotor 32 and 118: Amateur assembly 34 and 120: Electromagnetic means 36 and 122: Coil spring means 50 and 132: First boss member 72 and 154: Amateur 74 and 156: Support member 76 and 158: Bias Spring members 104 and 172: First boss members 180, 180a and 180b: Brake means 182: Rotating member 188: Friction member 192: Braking member

Claims (7)

【特許請求の範囲】[Claims] 【請求項１】 回転自在に装着された軸部材と、 該軸部材に回転自在に装着され回転駆動される入力回転
要素と、 該回転軸と一体に回転せしめられるロータと、該ロータ
に対向して位置するアマチュアと、該アマチュアを該ロ
ータから離隔する方向に弾性的に偏倚する偏倚ばね部材
と、付勢されると該偏倚ばね部材の弾性偏倚作用に抗し
て該アマチュアを該ロータに磁気的に吸着せしめる電磁
手段と、収縮することによって該入力回転要素からの駆
動力を該軸部材に伝達するためのコイルばね手段とを具
備するばねクラッチ機構と、 を有する電磁制御ばねクラッチ機構において、 該軸部材の回動を制動するためのブレーキ手段を備え
た、ことを特徴とする電磁制御ばねクラッチ機構。1. A shaft member rotatably mounted, an input rotary element rotatably mounted on the shaft member, and driven to rotate, a rotor rotatable integrally with the rotary shaft, and a rotor facing the rotor. And a biasing spring member that elastically biases the amateur in a direction away from the rotor, and when biased, resists the elastic biasing action of the biasing spring member to magnetically actuate the amateur to the rotor. An electromagnetically controlled spring clutch mechanism including: a spring clutch mechanism including: electromagnetic means for mechanically adsorbing, and a coil spring means for contracting to transmit the driving force from the input rotary element to the shaft member, An electromagnetically controlled spring clutch mechanism, comprising a braking means for braking the rotation of the shaft member. 【請求項２】 該ばねクラッチ機構は、第１のばねクラ
ッチ機構と第２のばねクラッチ機構とを有し、該第１の
ばねクラッチ機構と該第２のばねクラッチ機構が該入力
回転要素に対して対象的に該軸部材上に配設されてお
り、該第１のばねクラッチ機構と該第２のばねクラッチ
機構の一方が付勢されると該入力回転要素の所定方向の
回転を該軸部材に伝達し、他方が付勢されると該入力回
転要素の所定方向と反対方向の回転を該軸部材に伝達す
るように構成された、請求項１記載の電磁制御ばねクラ
ッチ機構。2. The spring clutch mechanism has a first spring clutch mechanism and a second spring clutch mechanism, and the first spring clutch mechanism and the second spring clutch mechanism serve as the input rotary element. In contrast, it is symmetrically disposed on the shaft member, and when one of the first spring clutch mechanism and the second spring clutch mechanism is energized, the rotation of the input rotary element in the predetermined direction is prevented. The electromagnetically controlled spring clutch mechanism according to claim 1, wherein the electromagnetically controlled spring clutch mechanism is configured to transmit to the shaft member the rotation of the input rotary element in a direction opposite to a predetermined direction when the other is biased. 【請求項３】 該アマチュア及び該偏倚ばね部材は該ロ
ータの片側に配設されたアマチュア組立体を構成し、該
アマチュア組立体は更に該軸部材に回転自在に装着され
た支持部材を有し、該支持部材と該アマチュアとの間に
該偏倚ばね部材が配設されており、該電磁手段は該ロー
タの他側に配設されている、請求項１又は２記載の電磁
制御ばねクラッチ機構。3. The armature and the biasing spring member constitute an armature assembly disposed on one side of the rotor, and the armature assembly further includes a supporting member rotatably mounted on the shaft member. 3. The electromagnetically controlled spring clutch mechanism according to claim 1 or 2, wherein the biasing spring member is disposed between the support member and the armature, and the electromagnetic means is disposed on the other side of the rotor. .. 【請求項４】 該軸部材と一体に回転する第１のボス部
材と、該第１のボス部材に隣接して配設され該入力回転
要素と一体に回転する第２のボス部材とを更に備え、該
コイルばね手段は該第１のボス部材と該第２のボス部材
とに跨がって被嵌され、該アマチュア組立体に連結され
た一端から該入力回転要素に連結された他端まで、該入
力回転要素の所定方向への回転に付随して該アマチュア
組立体と該入力回転要素とが相対的に回転せしめられる
と収縮される方向に捲回されている、請求項３記載の電
磁制御ばねクラッチ機構。4. A first boss member that rotates integrally with the shaft member, and a second boss member that is disposed adjacent to the first boss member and that rotates integrally with the input rotary element. The coil spring means is fitted over the first boss member and the second boss member, and is connected from the one end connected to the armature assembly to the other end connected to the input rotary element. The winding according to claim 3, wherein the armature assembly and the input rotary element are wound in a direction in which the armature assembly and the input rotary element are contracted when the armature assembly and the input rotary element are rotated relative to each other. Electromagnetically controlled spring clutch mechanism. 【請求項５】 該ブレーキ手段は、該軸部材と一体に回
転する回転部材と、該回転部材の回転を制動する制動部
材を含んでいる、請求項１乃至４のいずれかに記載の電
磁制御ばねクラッチ機構。5. The electromagnetic control according to claim 1, wherein the brake means includes a rotating member that rotates integrally with the shaft member and a braking member that brakes the rotation of the rotating member. Spring clutch mechanism. 【請求項６】 該ブレーキ手段は、該軸部材と該制動部
材を圧接するための偏倚手段を含んでいる、請求項５記
載の電磁制御ばねクラッチ機構。6. The electromagnetically controlled spring clutch mechanism according to claim 5, wherein the braking means includes a biasing means for press-contacting the shaft member and the braking member. 【請求項７】 該軸部材及び該制動部材の相互に接触す
る面の少なくとも一方に、摩擦部材が装着されている、
請求項５又は６記載の電磁制御ばねクラッチ機構。7. A friction member is mounted on at least one of the surfaces of the shaft member and the braking member that contact each other.
The electromagnetically controlled spring clutch mechanism according to claim 5.
JP5016847A 1993-01-08 1993-01-08 Electromagnetic control spring clutch mechanism Expired - Lifetime JP2720266B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP5016847A JP2720266B2 (en) 1993-01-08 1993-01-08 Electromagnetic control spring clutch mechanism

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP5016847A JP2720266B2 (en) 1993-01-08 1993-01-08 Electromagnetic control spring clutch mechanism

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
JP61178822A Division JPH0819970B2 (en) 1986-07-31 1986-07-31 Electromagnetically controlled spring clutch mechanism

Publications (2)

Publication Number Publication Date
JPH05263841A true JPH05263841A (en) 1993-10-12
JP2720266B2 JP2720266B2 (en) 1998-03-04

Family

ID=11927607

Family Applications (1)

Application Number Title Priority Date Filing Date
JP5016847A Expired - Lifetime JP2720266B2 (en) 1993-01-08 1993-01-08 Electromagnetic control spring clutch mechanism

Country Status (1)

Country Link
JP (1) JP2720266B2 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5332518U (en) * 1976-08-27 1978-03-22
JPS57195930A (en) * 1981-05-27 1982-12-01 Mita Ind Co Ltd Clutch capable of both normal and reverse rotation
JPS59142525U (en) * 1983-03-14 1984-09-22 小倉クラツチ株式会社 electromagnetic spring clutch
JPS59175633A (en) * 1983-03-23 1984-10-04 Mita Ind Co Ltd Solenoid controlled spring clutch mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5332518U (en) * 1976-08-27 1978-03-22
JPS57195930A (en) * 1981-05-27 1982-12-01 Mita Ind Co Ltd Clutch capable of both normal and reverse rotation
JPS59142525U (en) * 1983-03-14 1984-09-22 小倉クラツチ株式会社 electromagnetic spring clutch
JPS59175633A (en) * 1983-03-23 1984-10-04 Mita Ind Co Ltd Solenoid controlled spring clutch mechanism

Also Published As

Publication number Publication date
JP2720266B2 (en) 1998-03-04

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