JP3987975B2

JP3987975B2 - Motor and power window motor

Info

Publication number: JP3987975B2
Application number: JP2002358522A
Authority: JP
Inventors: 政彦安田
Original assignee: 自動車電機工業株式会社
Priority date: 2002-12-10
Filing date: 2002-12-10
Publication date: 2007-10-10
Anticipated expiration: 2022-12-10
Also published as: JP2004194411A

Description

【０００１】
【発明の属する技術分野】
本発明は、通電により回転するアーマチュアを備えた減速機構付きのモータ及びパワーウインドモータに関する。
【０００２】
【従来の技術】
例えば、自動車の各ドアのウインドガラスを開閉するウインドレギュレータには、駆動源として減速機構付きのパワーウインドモータが用いられている。このパワーウインドモータは、通電により回転（正回転または逆回転）するアーマチュアを備え、このアーマチュアのアーマチュア軸の回転を減速して出力軸によりウインドレギュレータを駆動させている。即ち、パワーウインドモータはアーマチュアの回転によりアーマチュア軸のウォームに噛合された出力ギヤが回転し、この出力ギヤの回転が該出力ギヤに内蔵されたゴム製のダンパを介して金属製のハブに伝わり、このハブに固定された出力軸が回転することにより、ウインドレギュレータを駆動させて各ドアのウインドガラスを開閉するようになっている。
【０００３】
【特許文献１】
特開２００１−３７１５６号公報
【０００４】
【発明が解決しようとする課題】
しかしながら、前記従来のウインドレギュレータに用いられるパワーウインドモータでは、ウインドガラスの全閉状態でのロック状態の維持はアーマチュア軸上のスラスト力及びアーマチュア軸を支持する軸受けと該アーマチュア軸間のラジアル方向の摩擦力を利用して行っているため、外部からウインドガラスを強い力で押し下げようとすると、出力軸を介して出力ギヤが逆回転してウインドガラスが開く場合があり、盗難等の対策が必要であった。
【０００５】
また、ウインドガラスがドアパネルに突き当たった全閉位置でロックされるため、出力ギヤの歯部とウインドガラス及びウンドレギュレータ等のパワーウインドシステム全体に大きなクリープ応力が加わり、これに対処するには、耐久性の高い出力ギヤ等が必要不可欠となって、その分モータが大型になると共にコスト高になった。
【０００６】
そこで、本発明は、前記した課題を解決すべくなされたものであり、出力軸から回転力が入力された時にクラッチで従動軸の回転を確実に阻止することができると共に小型で安価なものとすることができるモータ及びパワーウインドモータを提供することを目的とする。
【０００７】
【課題を解決するための手段】
請求項１の発明は、マグネットを内周面に固着したモータケースと、このモータケースに結合され、負荷に連結される出力軸を回転自在に支持したギヤケースと、これらモータケース及びギヤケースにそれぞれ回転自在に支持され、通電により回転するアーマチュアのアーマチュア軸と、前記ギヤケース内で該アーマチュア軸に形成されたウォームと、前記ギヤケースに回転自在に支持され、衝撃力を緩和するダンパを介して前記出力軸に連結されると共に前記ウォームに噛合された出力ギヤと、を備えたモータにおいて、前記アーマチュア軸を前記アーマチュアを有した駆動軸と前記ウォームを形成した従動軸とに分割形成し、これら駆動軸と従動軸との間に該従動軸の回転を断続するクラッチを介在し、このクラッチを、前記ギヤケースの軸穴内に収納した前記モータケースの先端円筒部内に回転自在に配置したクラッチケースと、このクラッチケースの内周面に沿って回転移動すると共に、該内周面に形成された凹部に収納される移動体と、前記クラッチケース内に回転自在に支持されると共に前記駆動軸に連結され、前記移動体を前記クラッチケースの凹部に収納させる凸部と該凹部より掻き出す掻き出し部を外周部にそれぞれ有した駆動回転体と、前記クラッチケース内に回転自在に支持されると共に前記従動軸に連結され、前記移動体を収納する凹部を外周部に有した従動回転体と、これら駆動回転体と従動回転体との間に介在され、当該両回転体の位置関係を前記駆動回転体の凸部と前記従動回転体の凹部及び前記クラッチケースの凹部の各位置がそれぞれ一致する中立位置に常に戻すように付勢するリターンスプリングとで構成し、外部から前記出力軸に回転力が入力された際の外力、または前記アーマチュアへの通電オンにより前記駆動軸が回転中に前記出力軸が拘束され該アーマチュアへの通電をオフした際に撓ませられた前記ダンパの復元力によって回転する前記従動軸の回転量を最大でも略１回転に規制する回転量規制手段を前記モータケースの先端円筒部と前記クラッチケース間に介在させたことを特徴とする。
【０００８】
請求項２の発明は、請求項１記載のモータであって、前記クラッチケースの内周面の互いに対称な位置に一対の凹部を形成し、前記移動体を前記クラッチケースの各凹部にそれぞれ収納させる一対の移動体として構成すると共に、前記駆動回転体の外周部に前記各移動体を前記クラッチケースの各凹部に収納させる一対の凸部と、この各凸部の両側に配置され前記各移動体を前記各凹部より掻き出す一対の掻き出し部とを形成し、前記従動回転体の外周部の互いに対称な位置に前記各移動体を収納する凹部を一対形成したことを特徴とする。
【０００９】
請求項３の発明は、請求項１または２記載のモータであって、前記回転量規制手段は、前記クラッチケースの外周面と前記モータケースの開口端に嵌合され該モータケースの一部を兼用するホルダベースの先端円筒部間に介在させたスプリングと、該クラッチケースの外周面に突出形成され前記スプリングの一方端を係止する第１スプリング係止部と、該ホルダベースの先端円筒部内に突出形成され該スプリングの他方端を係止する第２スプリング係止部とから構成され、前記クラッチケースは略１回転すると前記第１スプリング係止部に係止している前記スプリングの一方端が前記第２スプリング係止部に係止している前記スプリングの他方端に当接することで回転が阻止され、該クラッチケースと一体に回転する前記従動軸の回転を阻止したことを特徴とする。
【００１０】
この請求項１、２または３の発明のモータでは、外部から出力軸に回転力が入力された際の外力、またはアーマチュアへの通電オンにより駆動軸が回転中に出力軸が拘束され該アーマチュアへの通電をオフした際に撓ませられたダンパの復元力によって回転する従動軸の回転は、回転量規制手段により最大でも略１回転に規制され、それ以上の回転が確実に防止される。
【００１１】
また、出力軸が拘束された後にアーマチュアへの通電をオフすると、撓ませられていたダンパの復元力により出力ギヤ、従動軸、従動回転体、駆動回転体及び駆動軸が所定量（１回転以内）逆回転することにより、出力ギヤの歯部等に加わるクリープ応力が緩和される。
【００１２】
その結果、小型で安価な出力ギヤ等の使用が可能となり、その分モータの小型化及び低コスト化が図られる。
【００１３】
請求項４の発明は、マグネットを内周面に固着したモータケースと、このモータケースに結合され、ウインドレギュレータに連結される出力軸を回転自在に支持したギヤケースと、これらモータケース及びギヤケースにそれぞれ回転自在に支持され、通電により回転するアーマチュアのアーマチュア軸と、前記ギヤケース内で該アーマチュア軸に形成されたウォームと、前記ギヤケースに回転自在に支持され、衝撃力を緩和するダンパを介して前記出力軸に連結されると共に前記ウォームに噛合された出力ギヤと、を備えたパワーウインドモータにおいて、前記アーマチュア軸を前記アーマチュアを有した駆動軸と前記ウォームを形成した従動軸とに分割形成し、これら駆動軸と従動軸との間に該従動軸の回転を断続するクラッチを介在し、このクラッチを、前記ギヤケースの軸穴内に収納した前記モータケースの先端円筒部内に回転自在に配置したクラッチケースと、このクラッチケースの内周面に沿って回転移動すると共に、該内周面に形成された凹部に収納される移動体と、前記クラッチケース内に回転自在に支持されると共に前記駆動軸に連結され、前記移動体を前記クラッチケースの凹部に収納させる凸部と該凹部より掻き出す掻き出し部を外周部にそれぞれ有した駆動回転体と、前記クラッチケース内に回転自在に支持されると共に前記従動軸に連結され、前記移動体を収納する凹部を外周部に有した従動回転体と、これら駆動回転体と従動回転体との間に介在され、当該両回転体の位置関係を前記駆動回転体の凸部と前記従動回転体の凹部及び前記クラッチケースの凹部の各位置がそれぞれ一致する中立位置に常に戻すように付勢するリターンスプリングとで構成し、外部から前記出力軸に回転力が入力された際の外力、または前記アーマチュアへの通電オンにより前記駆動軸が回転中に前記出力軸が拘束され該アーマチュアへの通電をオフした際に撓ませられた前記ダンパの復元力によって回転する前記従動軸の回転量を最大でも略１回転に規制する回転量規制手段を前記モータケースの先端円筒部と前記クラッチケース間に介在させたことを特徴とする。
【００１４】
請求項５の発明は、請求項４記載のパワーウインドモータであって、前記クラッチケースの内周面の互いに対称な位置に一対の凹部を形成し、前記移動体を前記クラッチケースの各凹部にそれぞれ収納させる一対の移動体として構成すると共に、前記駆動回転体の外周部に前記各移動体を前記クラッチケースの各凹部に収納させる一対の凸部と、この各凸部の両側に配置され前記各移動体を前記各凹部より掻き出す一対の掻き出し部とを形成し、前記従動回転体の外周部の互いに対称な位置に前記各移動体を収納する凹部を一対形成したことを特徴とする。
【００１５】
請求項６の発明は、請求項４または５記載のパワーウインドモータであって、前記回転量規制手段は、前記クラッチケースの外周面と前記モータケースの開口端に嵌合され該モータケースの一部を兼用するホルダベースの先端円筒部間に介在させたスプリングと、該クラッチケースの外周面に突出形成され前記スプリングの一方端を係止する第１スプリング係止部と、該ホルダベースの先端円筒部内に突出形成され該スプリングの他方端を係止する第２スプリング係止部とから構成され、前記クラッチケースは略１回転すると前記第１スプリング係止部に係止している前記スプリングの一方端が前記第２スプリング係止部に係止している前記スプリングの他方端に当接することで回転が阻止され、該クラッチケースと一体に回転する前記従動軸の回転を阻止したことを特徴とする。
【００１６】
この請求項４，５または６の発明のパワーウインドモータでは、外部から出力軸に回転力が入力された際の外力、またはアーマチュアへの通電オンにより駆動軸が回転中に出力軸が拘束され該アーマチュアへの通電をオフした際に撓ませられたダンパの復元力によって回転する従動軸の回転は、回転量規制手段により最大でも略１回転に規制され、それ以上の回転が確実に防止される。その結果、ウインドガラスの全閉時に、外部からウインドガラスを強い力で押し下げようとしてもウインドガラスが開くことはない。
【００１７】
また、出力軸が拘束された後にアーマチュアへの通電をオフすると、撓ませられていたダンパの復元力により出力ギヤ、従動軸、従動回転体、駆動回転体及び駆動軸が所定量（１回転以内）逆回転することにより、出力ギヤの歯部とウインドガラス及びウインドレギュレータ等のパワーウインドシステム全体に加わるクリープ応力が緩和される。その結果、小型で安価な出力ギヤ等の使用が可能となり、その分パワーウインドモータの小型化及び低コスト化が図られる。また、ウインドガラスの締め切り時に、出力軸、出力ギヤが所定量逆転されるので、ウインドガラスの開放の際の起動電圧の低減が図られる。
【００１８】
【発明の実施の形態】
以下、本発明の一実施形態を図面に基づいて説明する。
【００１９】
図１は本発明の一実施形態のパワーウインドモータを示す断面図、図２は同パワーウインドモータのギヤケース部分の断面図、図３は同パワーウインドモータの分解断面図、図４は同パワーウインドモータのモータ部分の分解断面図、図５は同パワーウインドモータに用いられるクラッチの正面図、図６は図５中Ａ−Ａ線に沿う断面図、図７は図６中Ｂ−Ｂ線に沿う断面図、図８は図７中Ｃ−Ｃ線に沿う断面図、図９は同クラッチに用いられる駆動回転体の背面図、図１０は同クラッチに用いられる一方の従動回転体の正面図、図１１〜図１８は同クラッチのニュートラル時から駆動回転体の掻き出し部の位置が切り替わる時までの各状態を順を追って示す各説明図、図１９は同パワーウインドモータの出力ギヤがダンパの復元力とスプリングの復元力の釣合いにより逆回転する場合の説明図、図２０は同ダンパとスプリングの特性関係を示す説明図である。
【００２０】
図１，図３に示すように、パワーウインドモータ（モータ）１は、一端側が開口した略円筒状のヨーク（モータケース）１０と、このヨーク１０の開口端１０ａに嵌合され、モータケースの一部を兼用するホルダベース（モータケース）１１と、ヨーク１０の開口端１０ａの周りのフランジ部１０ｂをゴム製のパッキン８及びビス（締結手段）９を介して締結固定したギヤケース２０とを備えている。
図１，図３，図４に示すように、ヨーク１０の内周面１０ｃには円弧状で一対のマグネット１２，１２を接着剤等を介して固着してある。また、ヨーク１０の開口端１０ａには合成樹脂製で略円筒状のホルダベース１１を合成樹脂製で略円筒状のスペーサ１１Ａを介して嵌合してある。これらヨーク１０の他端の有底筒部１０ｄに嵌合された軸受１３ａとホルダベース１１の中央の円環板状の仕切壁１１ｃ内に合成樹脂製の軸受支持ベース１１Ｂを介して嵌合された軸受１３ｂとの間でアーマチュア軸１４の駆動軸１４Ａを回転自在に支持してある。このアーマチュア軸１４の駆動軸１４Ａの一端１４ａは軸受１３ｂより外側に貫通してホルダベース１１の先端円筒部１１ａ内に突出していると共に、該駆動軸１４Ａの他端１４ａ′の端面の中央はスチールボール１３ｃに当接している。
【００２１】
また、アーマチュア軸１４の駆動軸１４Ａの一対のマグネット１２，１２に対向する位置には、アーマチュア１６を取り付けてある。このアーマチュア１６は、駆動軸１４Ａに固定され、所定のスロット数のコイル巻回部を持つアーマチュアコア１６ａと、このアーマチュアコア１６ａのコイル巻回部に巻き回されたアーマチュアコイル１６ｂとで構成されている。
【００２２】
さらに、アーマチュア軸１４の駆動軸１４Ａのスペーサ１１Ａに対向する位置には、コンミュテータ１７を固定してある。このコンミュテータ１７はアーマチュアコア１６ａのコイル巻回部と同数のコンミュテータ片１７ａを備えていて、各コンミュテータ片１７ａとアーマチュアコイル１６ｂとは電気的にそれぞれ接続されている。
【００２３】
ホルダベース１１の基端円筒部１１ｄの内周面１１ｅのコンミュテータ１７に対向する位置には、各ブラシホルダ１８を介して一対のブラシ１９，１９をそれぞれ取り付けてある。各ブラシ１９は図示しないパワーウインドモータ制御回路のガラス開，閉スイッチにそれぞれ電気的に接続されている。そして、このガラス開スイッチがオン切り替えされると、電源の電流がアーマチュア１６等に流れてアーマチュア軸１４の駆動軸１４Ａが正回転すると共に、ガラス閉スイッチがオン切り替えされると、電源の電流がアーマチュア１６等に流れてアーマチュア軸１４の駆動軸１４Ａが逆回転するようになっている。
【００２４】
図１〜図３に示すように、ギヤケース２０の略中央には軸穴２１を形成してあり、この軸穴２１に連通して円環凹状の減速機構収納部２１ａを形成してある。この軸穴２１には小径穴部２１ｂと大径穴部２１ｃとを同芯段差状に形成してある。この軸穴２１の小径穴部２１ｂ内には後述するクラッチ３０が収納されたモータケースとしてのホルダベース１１の先端円筒部１１ａを収納すると共に、該軸穴２１の大径穴部２１ｃ内にはホルダーベース１１の基端円筒部１１ｄを嵌合して固定してある。
【００２５】
そして、軸穴２１の奥に嵌合された軸受２２ａと該軸穴２１の小径穴部２１ｂ寄りの位置に嵌合された軸受２２ｂとの間でアーマチュア軸１４の従動軸１４Ｂを回転自在に支持してある。この従動軸１４Ｂの中央には、ウォーム１５を形成してある。即ち、アーマチュア軸１４をアーマチュア１６を有した駆動軸１４Ａとウォーム１５を形成した従動軸１４Ｂとにそれぞれ分割形成し、これら駆動軸１４Ａと従動軸１４Ｂとの間に該従動軸１４Ｂ側の回転（正回転または逆回転）を断続するクラッチ３０を介在してある。さらに、従動軸１４Ｂの一端１４ｂ及びその半円球部１４ｃはギヤケース２０の軸穴２１の小径穴部２１ｂ内に突出していると共に、該従動軸１４Ｂの他端１４ｂ′の端面の中央はスチールボール２２ｃに当接している。
【００２６】
図２に示すように、ギヤケース２０の減速機構収納部２１ａの中央には、円筒状の出力軸支持部２１ｄを一体突出形成してある。この出力軸支持部２１ｄと減速機構収納部２１ａの一端開口を覆う金属製のカバー２３の中央の円筒部２３ａとの間には、一対の軸受２４ａ，２４ｂを介して図示しないウインドレギュレータ（負荷）に連結される出力軸２５の両端部を回転自在に支持してある。この出力軸２５の一端近傍のセレーション部２５ａには、樹脂製の動力伝達部材２６と金属製のプレート２７及び衝撃力を緩和するゴム製のダンパ２８を介して出力ギヤ２９を連結してある。この出力ギヤ２９のはす歯（歯部）２９ａは従動軸１４Ｂのウォーム１５に噛合されている。これらウォーム１５、出力ギヤ２９、ダンパ２８、動力伝達部材２６、プレート２７及び出力軸２５は、それぞれギヤケース２０の減速機構収納部２１ａ内に収納され、減速機構を構成している。
【００２７】
図１，図３〜図８に示すように、クラッチ３０は、ホルダベース１１の先端円筒部１１ａ内に収納される合成樹脂製のクラッチケース３１と、このクラッチケース３１の内周面３１ｃに沿って回転移動すると共に、該内周面３１ｃの互いに対称な位置に形成された一対の凹部３１ｄ，３１ｄに収納される一対の移動体３２，３２と、クラッチケース３１内に回転自在に支持されると共に駆動軸１４Ａの一端１４ａに連結され、各移動体３２をクラッチケース３１の各凹部３１ｄに収納させる一対の凸部３３ｃ，３３ｃと該各凸部３３ｃの両側に配置され各移動体３２を前記各凹部３１ｄより掻き出す一対の掻き出し部３３ｄ，３３ｄを外周部３３ｂにそれぞれ有した合成樹脂製の駆動回転体３３と、クラッチケース３１内に回転自在に支持されると共に従動軸１４Ｂの一端１４ｂに連結され、各移動体３２を収納する一対の凹部３４ｃ，３４ｃ及び一対の凹部３５ｃ，３５ｃを外周部３４ａ及び外周部３５ａの互いに対称な位置にそれぞれ有した合成樹脂製で一対の従動回転体３４，３５と、これら駆動回転体３３と一方の従動回転体３４との間に介在され、駆動回転体３３と従動回転体３４，３５の両回転体の位置関係を駆動回転体３３の凸部３３ｃと一対の従動回転体３４，３５の各凹部３４ｃ，３５ｃ及びクラッチケース３１の各凹部３１ｄの各位置がそれぞれ一致する中立位置（図７に示すニュートラル位置）に常に戻すように付勢する捩りコイルバネ状のリターンスプリング３６とで構成されている。そして、ホルダベース１１の先端円筒部１１ａの内周面１１ｂとクラッチケース３１の外周面３１ａとの間には、スプリング４１が介在されている。
【００２８】
図５〜図８に示すように、クラッチケース３１は合成樹脂により略円筒状に形成してあり、その外周面３１ａにはスプリング係止部３１ｂを軸方向に延びるように一体突出形成してある。また、クラッチケース３１の内周面３１ｃの互いに対称な相対向する位置には半円状の凹部３１ｄをそれぞれ形成してある。
【００２９】
図６，図７に示すように、各移動体３２は例えば合成樹脂により円柱状に形成してあり、クラッチケース３１の各凹部３１ｄに収納されるようになっている。そして、各移動体３２がクラッチケース３１の内周面３１ｃに沿って回転移動する際に、パワーウインドモータ１のトルク伝達を行うようになっている。
【００３０】
図６〜図９に示すように、駆動回転体３３の中央には、外周に切欠きを有した駆動軸１４Ａの一端１４ａを嵌合して連結する平面略Ｄ字状の取付孔３３ａを形成してあると共に、その両側にはクラッチケース３１の内周面３１ｃを摺動する円弧状で一対の外周部３３ｂ，３３ｂを一体形成してある。また、駆動回転体３３の一対の外周部３３ｂ，３３ｂの両側中央には各移動体３２をクラッチケース３１の各凹部３１ｄに収納させる凸部３３ｃをそれぞれ一体突出形成してあると共に、該各凸部３３ｃの両側にはクラッチケース３１の各凹部３１ｄより各移動体３２を掻き出す半円凹状で各一対の掻き出し部３３ｄ，３３ｄをそれぞれ一体形成してある。また、駆動回転体３３の一対の外周部３３ｂ，３３ｂの内側には扇形の開口部３３ｅをそれぞれ形成してある。さらに、駆動回転体３３の裏面には取付孔３３ａより大径の円筒部３３ｆを一体突出形成してあると共に、その内部中央にはリターンスプリング３６の両端３６ａ，３６ａの一方が係止される鉤形柱状のスプリング係止部３３ｇを一体突出形成してある。
【００３１】
図６〜図８，図１０に示すように、一方の従動回転体３４はクラッチケース３１の内周面３１ｃを摺動する円板部（外周部）３４ａを有しており、この円板部３４ａの中央には、外周に切欠き有した従動軸１４Ｂの一端１４ｂを嵌合して連結する平面略Ｄ字状の取付孔３４ｂを形成してある。この取付孔３４ｂに嵌合して連結された従動軸１４Ｂの一端１４ｂの端面中央の半円球状の突起１４ｃは、駆動回転体３３の取付孔３３ａに嵌合して連結された駆動軸１４Ａの一端１４ａの端面中央に当たっている。さらに、円板部３４ａの表面の外周部の互いに対称な位置には各移動体３２の一端３２ａ側が収納される正面Ｕ字状に切り欠かれた一対の凹部３４ｃ，３４ｃを形成してあると共に、各凹部３４ｃと取付孔３４ｂとの間には柱状のスプリングガイド３４ｄをそれぞれ一体突出形成してある。
【００３２】
また、円板部３４ａの表面の各スプリングガイド３４ｄより９０度隔てた位置には駆動回転体３３の一対のスプリング係止部３３ｇ，３３ｇが嵌め込まれる円弧柱状で一対のスプリング係止部３４ｅ，３４ｅを一体突出形成してあると共に、その外側には駆動回転体３３の一対の開口部３３ｅ，３３ｅ内に挿通されて従動回転体３４の正回転または逆回転の回転量を規制する断面略台形柱状で一対の支柱部３４ｆ，３４ｆを一体突出形成してある。一対のスプリング係止部３４ｅ，３４ｅの一方のスプリング係止部３４ｅにはリターンスプリング３６の両端３６ａ，３６ａの他方が係止されるようになっている。
【００３３】
図５，図６，図８に示すように、他方の従動回転体３５は合成樹脂により円板状に形成してあり、その外周部３５ａをクラッチケース３１の内周面３１ｃに摺動自在にしている。また、他方の従動回転体３５の中央には駆動回転体３３の取付孔３３ａの周りの円筒部３３ａ′が挿通する円形のセンター孔３５ｂを形成してあると共に、その外周部３５ａには一方の従動回転体３４の一対の支柱部３４ｆ，３４ｆの先端が挿入されて溶着等により固定される一対の取付孔３５ｄ，３５ｄを形成してある。これにより、一対の従動回転体３４，３５は駆動回転体３３を挟むようにして共に回転するようになっている。
【００３４】
また、他方の従動回転体３５の裏面の外周部３５ａの左右両側には各移動体３２の他端３２ｂ側が収納される背面Ｕ字状に切り欠かれた凹部３５ｃをそれぞれ形成してある。そして、一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃ間で各移動体３２を回転自在に支持するようになっている。
【００３５】
図４，図７，図１８に示すように、クラッチケース３１の外周面３１ａの周りに配置された捩り板状のスプリング４１の両端４１ａ，４１ａの一方端は、該クラッチケース３１の外周面３１ａに一体突出形成された第１スプリング係止部３１ｆに係止されている。また、スプリング４１の両端４１ａ，４１ａの他方端は、ホルダベース１１の仕切壁１１ｃより先端円筒部１１ａ内に一体突出形成された第２スプリング係止部１１ｆに係止されている。これらスプリング４１、第１スプリング係止部３１ｆおよび第２スプリング係止部１１ｆで回転量規制手段４０を構成している。この回転量規制手段４０は、外部から出力軸２５に回転力が入力された際の外力により、該出力軸２５、出力ギヤ２９を介して従動軸１４Ｂが回転する回転量を最大でも略１回転に規制するようになっている。
【００３６】
また、アーマチュア１６への通電オンにより駆動軸１４Ａが回転中に出力軸２５が拘束されると、出力ギヤ２９とウオーム１５を介して従動軸１４Ｂが拘束され、なおも回転を続行する駆動軸１４Ａの回転力によりダンパ２８が所定量撓ませられた後、該駆動軸１４Ａも拘束されて回転を停止する。その後、アーマチュア１６への通電をオフすると、撓ませられたダンパ２８の復元力によって、前記スプリング４１を捩り変形させながら出力ギヤ２９、従動軸１４Ｂ、一対の従動回転体３４，３５、各移動体３２、駆動回転体３３、駆動軸１４Ａおよびクラッチケース３１が一体となって逆回転するが、ダンパ２８の復元力とスプリング４１の捩り変形に要する負荷が釣合ったところで逆回転が停止するようになっている。
【００３７】
以上実施形態のパワーウインドモータ１に用いるクラッチ３０の作用を図１１〜図１９に沿って順に説明する。尚、図１１〜図１８は、駆動軸１４Ａとリターンスプリング３６と移動体３２と駆動回転体３３と一対の従動回転体３４，３５及び従動軸１４Ｂの各部に加わる負荷の大きさが、駆動軸１４Ａ側に加わる負荷＜リターンスプリング３６のセット荷重＜移動体３２を駆動回転体３３と一対の従動回転体３４，３５間に収納した時のリターンスプリング３６の反力＜従動軸１４Ｂ側に加わる負荷、の条件時において、駆動軸１４Ａ又は従動軸１４Ｂより回転力を入力した場合の移動体３２及び各部の位置関係を示す図である。
【００３８】
このクラッチ３０のニュートラル時の状態を図１１に示す。パワーウインドモータ１の外部から出力軸２５、出力ギヤ２９を介して従動軸１４Ｂに回転力を入力した場合、一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃにてクラッチケース３１の各凹部３１ｄから各移動体３２を掻き出そうとするが、駆動回転体３３がリタンスプリング３６のセット荷重にて保持されている（駆動回転体３３の各凸部３３ｃがクラッチケース３１の各凹部３１ｄに各移動体３２を押し付けて収納させている）ことから一対の従動回転体３４，３５は、各移動体３２、駆動回転体３３およびクラッチケース３１と一体となってスプリング４１を捩り変形させながら回転する。略１回転したところで、クラッチケース３１の外周面３１ａに一体突出形成した第１スプリング係止部３１ｂに係止したスプリング４１の一方端４１ａが、ホルダベース１１の先端円筒部１１ａ内に一体突出形成した第２スプリング係止部１１ｆに係止したスプリングの他方端４１ａに当接し、一対の従動回転体３４，３５の回転（正回転及び逆回転）が阻止される。つまり、外部から出力軸２５と出力ギヤ２９を介して従動軸１４Ｂに回転力が入力された時に、回転量規制手段４０により該従動軸１４Ｂの回転量を最大でも略１回転に規制することができる。この従動軸１４Ｂの略１回転は、出力軸２５の回転量に変換すると３６０°÷出力ギヤ２９の歯数（例えば７２枚）であり、５°程度と非常に少ないものである。これにより、ウインドガラスの全閉時に、ウインドガラスを下方に強く押し下げても出力軸２５に連結されたウインドレギュレータがほとんど駆動することがなく、ウインドガラスのガラス下がりを確実に防止することができる。その結果、ウインドガラスが不用意に開かれることなく、自動車の盗難を確実に防止することができる。
【００３９】
図１２は従動軸１４Ｂに負荷が加わっている場合のクラッチ３０の駆動回転体３３の作動時の状態を示す。駆動回転体３３が矢印方向に回転すると、駆動回転体３３の各凸部３３ｃがクラッチケース３１の各凹部３１ｄに収納された各移動体３２より離れ、各移動体３２は駆動回転体３３の各凸部３３ｃによる拘束状態から解放され、駆動回転体３３の一方の各掻き出し部３３ｄが移動体３２の掻き出しに向かう。
【００４０】
図１３はクラッチ３０の駆動回転体３３の作動により一対の従動回転体３４，３５にトルクを伝達中の状態を示す。このとき、駆動回転体３３の一方の各掻き出し部３３ｄによりクラッチケース３１の各凹部３１ｄから各移動体３２が掻き出され、各移動体３２は駆動回転体３３の一方の各掻き出し部３３ｄと一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃ間に保持され、この各移動体３２を介して駆動回転体３３の回転力を一対の従動回転体３４，３５に伝達し、従動軸１４Ｂを回転させる。
【００４１】
即ち、図１３の矢印に示すように、駆動回転体３３の回転時に、各移動体３２は駆動回転体３３の一方の各掻き出し部３３ｄと一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃとクラッチケース３１の内周面３１ｃと接している状態で、該各移動体３２は駆動回転体３３の一方の各掻き出し部３３ｄと一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃ間に保持されて回転する。
【００４２】
図１４は駆動回転体３３の停止時（各移動体３２がクラッチケース３１の各凹部３１ｄ以外で停止）の状態を示す。この状態は、リターンスプリング３６の反力及び駆動回転体３３により、各移動体３２がクラッチケース３１の内周面３１ｃへ押し出された状態である。そして、各移動体３２は、図１４中黒点で示すように、クラッチケース３１の内周面３１ｃと一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃと駆動回転体３３の各凸部３３ｃと接触する。
【００４３】
図１５はクラッチ３０の駆動軸１４Ａの回転停止時に従動軸１４Ｂ側より回転力が入力された場合を示し、図１６はクラッチ３０の各移動体３２がクラッチケース３１の各凹部３１ｄに収納される直前の状態を示し、図１７は各移動体３２がクラッチケース３１の各凹部３１ｄに収納された時の状態を示す。
【００４４】
図１５に示すように、従動軸１４Ｂの矢印方向の回転により各移動体３２が駆動回転体３３の各凸部３３ｃと一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃにより押され、クラッチケース３１の内周面３１ｃを回転しながら移動し、図１６に示すように、各移動体３２がクラッチケース３１の内周面３１ｃの各凹部３１ｄに到達すると、駆動回転体３３の各凸部３３ｃにより各移動体３２が押し出され、図１７に示すように、各移動体３２がクラッチケース３１の内周面３１ｃの各凹部３１ｄに収納される。一対の従動回転体３４，３５の相対向する各凹部３４ｃ，３５ｃによりクラッチケース３１の各凹部３１ｄから各移動体３２を掻き出そうとするが、駆動回転体３３と一方の従動回転体３４との間に掛け渡されたリターンスプリング３６の付勢力により中立位置に自動的に戻ろうとする駆動回転体３３の各凸部３３ｃにより各移動体３２は、クラッチケース３１の各凹部３１ｄから抜け出すことができず、図１１と同様にニュートラルの状態となる。
【００４５】
図１８は駆動回転体３３の各凸部３３ｃにて各移動体３２をクラッチケース３１の各凹部３１ｄに収納した駆動軸１４Ａの回転停止時から従動軸１４Ｂが一定量回転（最大約一回転）する状態を示す。即ち、駆動軸１４Ａの回転中に出力軸２５が拘束され、そのため駆動軸１４Ａが回転を停止し、その後アーマチュア１６への通電をオフした際のクラッチ３０と従動軸１４Ｂの動きを示す。
【００４６】
駆動軸１４Ａが回転中に出力軸２５が拘束されると、出力ギヤ２９とウオーム１５を介して従動軸１４Ｂが拘束され、なおも回転を続行する駆動軸１４Ａの回転力によりダンパ２８が所定量撓ませられた後、該駆動軸１４Ａも拘束されて回転を停止する。その後、アーマチュア１６への通電をオフすると、撓ませられたダンパ２８の復元力によって、スプリング４１を捩り変形させながら出力ギヤ２９、従動軸１４Ｂ、一対の従動回転体３４，３５、各移動体３２、駆動回転体３３およびクラッチケース３１が一体となって矢印方向に逆回転し、ダンパ２８の復元力とスプリング４１の捩り変形に要する負荷が釣合ったところで逆回転が停止する。
【００４７】
そして、図１９はパワーウインドモータ１の出力ギヤ２９がダンパ２８及びスプリング４１の復元力により逆回転（反転）する場合、例えば、駆動軸１４Ａが回転中に従動軸１４Ｂが拘束され、パワーウインドモータ１への通電をオフした時の状態を示し、図１９中矢印Ｘは出力軸２５が拘束されるまでの出力ギヤ２９の回転方向を示し、図１９中矢印Ｙはダンパ２８及びスプリング４１の復元力により出力ギヤ２９が逆回転された回転方向を示す。また、図２０はダンパ２８とスプリング４１の特性関係を示す。
【００４８】
即ち、駆動軸１４Ａが回転中に出力軸２５（出力ギヤ２９）の拘束により従動軸１４Ｂが拘束されると、ホルダベース１１に形成した第２スプリング係止部１１ｆとクラッチケース３１に形成した第１スプリング係止部３１ｆとに両端４１ａ，４１ａをそれぞれ係止させたスプリング４１がパワーウインドモータ１のトルクにて所定の角度撓ませられ、パワーウインドモータ１（アーマチュア１６）への通電をオフすることにより、この撓ませられたスプリング４１の復元力と出力ギヤ２９に結合（内蔵）されたダンパ２８の復元力とにより従動軸１４Ｂと一対の従動回転体３４，３５及び駆動回転体３３と駆動軸１４Ａを所定の範囲逆回転させ、出力ギヤ２９を拘束状態から解放する。これにより、出力ギヤ２９のはす歯（歯部）２９ａとウインドガラス及びウインドレギュレータ等のパワーウインドシステム全体に加わるクリープ応力や衝撃力を緩和することができる。その結果、小型で安価な出力ギヤ等を使用することができ、その分、全体の小型化及び低コスト化を図ることができる。また、ウインドガラスの閉め切り時に、出力軸２５および出力ギヤ２９を所定の範囲確実に逆転させることにより、起動電圧の低減を図ることができる。
【００４９】
また、このパワーウインドモータ１では、図３及び図４に示すように、駆動軸１４Ａを回転自在に支持したモータケースとしてのホルダベース１１の先端円筒部１１ａ内にクラッチ３０を着脱自在に組み付けて駆動軸１４Ａの一端１４ａに駆動回転体３３を連結し、その後、従動軸１４Ｂを回転自在に支持したギヤケース２０にモータケースとしてのヨーク１０をビス９を介して着脱自在に組み付けて従動軸１４Ｂの一端１４ｂにクラッチ３０の一対の従動回転体３４，３５を連結するようにしたので、モータケース１０，１１をギヤケース２０に組み付ける前に、パワーウインドモータ１の駆動軸１４Ａ側（モータ部分）及びクラッチ３０の動作確認や検査等の性能確認を同時かつ容易に行うことができる。これにより、信頼性の高いパワーウインドモータ１を低コストで提供することができる。
【００５０】
【発明の効果】
以上説明したように、請求項１、２または３の発明のモータによれば、外部から出力軸に回転力が入力された際の外力、またはアーマチュアへの通電オンにより駆動軸が回転中に出力軸が拘束され該アーマチュアへの通電をオフした際に撓ませられたダンパの復元力によって回転する従動軸の回転は、回転量規制手段により最大でも略１回転に規制され、それ以上の回転を確実に阻止出来る。
【００５１】
また、出力軸が拘束された後にアーマチュアへの通電をオフすると、撓ませられていたダンパの復元力により出力ギヤ、従動軸、従動回転体、駆動回転体及び駆動軸が所定量（１回転以内）逆回転することにより、出力ギヤの歯部等に加わるクリープ応力が緩和される。
【００５２】
その結果、小型で安価な出力ギヤ等の使用が可能となり、その分モータの小型化及び低コスト化を図ることが出来る。
【００５３】
請求項４，５または６の発明のパワーウインドモータによれば、外部から出力軸に回転力が入力された際の外力、またはアーマチュアへの通電オンにより駆動軸が回転中に出力軸が拘束され該アーマチュアへの通電をオフした際に撓ませられたダンパの復元力によって回転する従動軸の回転は、回転量規制手段により最大でも略１回転に規制され、それ以上の回転を確実に阻止出来る。
【００５４】
その結果、ウインドガラスの全閉時に、外部からウインドガラスを強い力で押し下げようとしてもウインドガラスが開くことはない。
【００５５】
また、出力軸が拘束された後にアーマチュアへの通電をオフすると、撓ませられていたダンパの復元力により出力ギヤ、従動軸、従動回転体、駆動回転体及び駆動軸が所定量（１回転以内）逆回転することにより、出力ギヤの歯部とウインドガラス及びウインドレギュレータ等のパワーウインドシステム全体に加わるクリープ応力が緩和される。その結果、小型で安価な出力ギヤ等の使用が可能となり、その分パワーウインドモータの小型化及び低コスト化を図ることが出来る。また、ウインドガラスの締め切り時に、出力軸、出力ギヤが所定量逆転するので、ウインドガラスの開放の際の起動電圧の低減を図ることが出来る。
【図面の簡単な説明】
【図１】本発明の一実施形態のパワーウインドモータを示す断面図である。
【図２】上記パワーウインドモータのギヤケース部分の断面図である。
【図３】上記パワーウインドモータの分解断面図である。
【図４】上記パワーウインドモータのモータ部分の分解断面図である。
【図５】上記パワーウインドモータに用いられるクラッチの正面図である。
【図６】図５中Ａ−Ａ線に沿う断面図である。
【図７】図６中Ｂ−Ｂ線に沿う断面図である。
【図８】図７中Ｃ−Ｃ線に沿う断面図である。
【図９】上記クラッチに用いられる駆動回転体の背面図である。
【図１０】上記クラッチに用いられる一方の従動回転体の正面図である。
【図１１】上記クラッチのニュートラル時の状態を示す説明図である。
【図１２】上記クラッチの駆動回転体の作動時（従動軸に負荷が加わっている場合）の状態を示す説明図である。
【図１３】上記クラッチの駆動回転体の作動により従動回転体にトルクを伝達中の状態を示す説明図である。
【図１４】上記駆動回転体の停止時（移動体がクラッチケースの凹部以外で停止）の状態を示す説明図である。
【図１５】上記クラッチの駆動軸の回転停止時に従動軸側より回転力が入力された場合の説明図である。
【図１６】上記クラッチの移動体がクラッチケースの凹部に収納される直前の状態を示す説明図である。
【図１７】上記移動体がクラッチケースの凹部に収納された時の状態を示す説明図である。
【図１８】上記移動体がクラッチケースの凹部に収納された駆動軸の回転停止時から従動軸が一定量回転する状態を示す説明図である。
【図１９】上記パワーウインドモータの出力ギヤがダンパの復元力とスプリングの復元力の釣合いにより逆回転する場合の説明図である。
【図２０】上記ダンパとスプリングの特性関係を示す説明図である。
【符号の説明】
１パワーウインドモータ（モータ）
１０ヨーク（モータケース）
１０ａ開口端
１０ｃ内周面
１１ホルダベース（モータケース）
１１ａ先端円筒部
１１ｆ第２スプリング係止部
１２マグネット
１４アーマチュア軸
１４Ａ駆動軸
１４Ｂ従動軸
１５ウォーム
１６アーマチュア
２０ギヤケース
２１軸穴
２５出力軸
２８ダンパ
２９出力ギヤ
３０クラッチ
３１クラッチケース
３１ａ外周面
３１ｂ第１スプリング係止部
３１ｃ内周面
３１ｄ凹部
３２移動体
３３駆動回転体
３３ｂ外周部
３３ｃ凸部
３３ｄ掻き出し部
３４，３５従動回転体
３４ａ，３５ａ外周部
３４ｃ，３５ｃ凹部
３６リターンスプリング
４０回転量規制手段
４１スプリング[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a motor with a speed reduction mechanism including an armature that rotates when energized, and a power window motor.
[0002]
[Prior art]
For example, in a window regulator that opens and closes a window glass of each door of an automobile, a power window motor with a speed reduction mechanism is used as a drive source. The power window motor includes an armature that rotates (forward or reverse) when energized. The rotation of the armature shaft of the armature is reduced and the window regulator is driven by the output shaft. That is, in the power window motor, the output gear meshed with the worm of the armature shaft is rotated by the rotation of the armature, and the rotation of the output gear is transmitted to the metal hub via the rubber damper built in the output gear. When the output shaft fixed to the hub rotates, the window regulator is driven to open and close the window glass of each door.
[0003]
[Patent Document 1]
JP 2001-37156 A
[0004]
[Problems to be solved by the invention]
However, in the power window motor used in the conventional window regulator, the locked state of the window glass in the fully closed state is maintained in the radial direction between the thrust force on the armature shaft and the bearing supporting the armature shaft and the armature shaft. Because it uses frictional force, if you try to push down the window glass with a strong force from the outside, the output gear may reversely rotate through the output shaft and the window glass may open, and measures such as theft are necessary. Met.
[0005]
In addition, since the window glass is locked in the fully closed position where it hits the door panel, a large creep stress is applied to the entire power window system such as the output gear teeth and the window glass and the wind regulator. High-performance output gear and so on became indispensable, and the motor became larger and the cost increased accordingly.
[0006]
Therefore, the present invention has been made to solve the above-described problems, and can reliably prevent rotation of the driven shaft with a clutch when a rotational force is input from the output shaft, and is small and inexpensive. It is an object of the present invention to provide a motor and a power window motor that can be used.
[0007]
[Means for Solving the Problems]
According to the first aspect of the present invention, a motor case having a magnet fixed to the inner peripheral surface, a gear case coupled to the motor case and rotatably supporting an output shaft connected to a load, and the motor case and the gear case are respectively rotated. The armature shaft of an armature that is freely supported and rotates when energized, a worm formed on the armature shaft in the gear case, and the output shaft via a damper that is rotatably supported by the gear case and reduces impact force And an output gear meshed with the worm, wherein the armature shaft is divided into a drive shaft having the armature and a driven shaft forming the worm, and the drive shaft and A clutch for intermittently rotating the driven shaft is interposed between the driven shaft and the clutch. A clutch case that is rotatably arranged in the tip cylindrical portion of the motor case housed in the shaft hole, and rotates and moves along the inner circumferential surface of the clutch case, and is housed in a recess formed in the inner circumferential surface. A movable body is rotatably supported in the clutch case and connected to the drive shaft, and has a convex portion for housing the movable body in a concave portion of the clutch case and a scraped portion that is scraped from the concave portion on the outer peripheral portion. A driven rotator, a driven rotator that is rotatably supported in the clutch case and connected to the driven shaft, and has a recess in the outer peripheral portion for housing the moving body, and the driven rotator and the driven rotation And the positions of the two rotating bodies coincide with each other in the positions of the convex portion of the driving rotary body, the concave portion of the driven rotary body, and the concave portion of the clutch case. A return spring that constantly biases the output shaft to return to an upright position, and the output when the drive shaft is rotating due to external force when a rotational force is input to the output shaft from the outside or energization to the armature is turned on. A rotation amount restricting means for restricting the rotation amount of the driven shaft, which is rotated by the restoring force of the damper bent when the shaft is constrained and the energization to the armature is turned off, to a maximum of approximately one rotation is provided on the motor case. It is characterized by being interposed between the tip cylindrical portion and the clutch case.
[0008]
A second aspect of the present invention is the motor according to the first aspect, wherein a pair of recesses are formed at symmetrical positions on the inner peripheral surface of the clutch case, and the movable body is housed in each recess of the clutch case. And a pair of convex portions for accommodating the movable bodies in the concave portions of the clutch case on the outer periphery of the drive rotating body, and the respective movements arranged on both sides of the convex portions. A pair of scraping portions that scrape the body from the respective recesses are formed, and a pair of recesses that house the respective moving bodies are formed at symmetrical positions on the outer peripheral portion of the driven rotating body.
[0009]
  A third aspect of the present invention is the motor according to the first or second aspect, wherein the rotation amount restricting means includes an outer peripheral surface of the clutch case and theFits into the open end of the motor case and also serves as part of the motor caseA spring interposed between the cylindrical end portions of the holder base, a first spring engaging portion that protrudes from the outer peripheral surface of the clutch case and engages one end of the spring, and protrudes into the cylindrical end portion of the holder base And a second spring locking portion that locks the other end of the spring. When the clutch case rotates approximately once, the one end of the spring locked to the first spring locking portion is The rotation is prevented by abutting against the other end of the spring locked to the second spring locking portion, and the rotation of the driven shaft rotating integrally with the clutch case is blocked.
[0010]
In the motor according to the first, second, or third aspect of the invention, the output shaft is restrained while the drive shaft is rotating due to external force when a rotational force is input to the output shaft from the outside, or energization to the armature, and to the armature. The rotation of the driven shaft, which is rotated by the restoring force of the damper deflected when the current is turned off, is restricted to approximately one rotation at most by the rotation amount restricting means, and further rotation is reliably prevented.
[0011]
When the power supply to the armature is turned off after the output shaft is constrained, the output gear, driven shaft, driven rotor, drive rotor, and drive shaft are set to a predetermined amount (within one rotation) by the restoring force of the deflected damper. ) By reverse rotation, the creep stress applied to the teeth of the output gear is alleviated.
[0012]
As a result, it is possible to use a small and inexpensive output gear or the like, and accordingly, the motor can be reduced in size and cost.
[0013]
According to a fourth aspect of the present invention, there is provided a motor case having a magnet fixed to the inner peripheral surface, a gear case coupled to the motor case and rotatably supporting an output shaft connected to a window regulator, and the motor case and the gear case, respectively. The armature shaft of an armature that is rotatably supported and rotates when energized, a worm formed on the armature shaft in the gear case, and the output that is rotatably supported by the gear case via a damper that reduces impact force. An output gear coupled to the shaft and meshed with the worm, wherein the armature shaft is divided into a drive shaft having the armature and a driven shaft forming the worm, A clutch for intermittently rotating the driven shaft is interposed between the drive shaft and the driven shaft; The clutch case is rotatably arranged in the cylindrical end portion of the motor case housed in the shaft hole of the gear case, and is rotated on the inner peripheral surface of the clutch case and formed on the inner peripheral surface. A movable body housed in the recessed portion, a convex portion which is rotatably supported in the clutch case and is connected to the drive shaft, and the movable body is housed in the concave portion of the clutch case, and a scrape which is scraped from the concave portion. A driving rotator each having an outer peripheral portion, a driven rotator that is rotatably supported in the clutch case and connected to the driven shaft, and has a recess in the outer peripheral portion for housing the moving body, The drive rotator and the driven rotator are interposed, and the positional relationship between the rotators is determined by the projections of the drive rotator, the recesses of the driven rotator, and And a return spring that constantly urges each position of the unit to return to the neutral position where they coincide with each other, and the external force when a rotational force is input from the outside to the output shaft, or the energization of the armature is turned on. Rotation that restricts the amount of rotation of the driven shaft, which is rotated by the restoring force of the damper deflected when the output shaft is constrained and the power supply to the armature is turned off while the drive shaft is rotating, to about one rotation at most. An amount regulating means is interposed between the tip cylindrical portion of the motor case and the clutch case.
[0014]
A fifth aspect of the present invention is the power window motor according to the fourth aspect, wherein a pair of recesses are formed at symmetrical positions on the inner peripheral surface of the clutch case, and the movable body is provided in each recess of the clutch case. It is configured as a pair of moving bodies to be housed respectively, a pair of convex portions for housing the respective moving bodies in the respective concave portions of the clutch case on the outer peripheral portion of the drive rotating body, and disposed on both sides of the respective convex portions. A pair of scraping portions for scraping each moving body from the respective recesses is formed, and a pair of recesses for storing the respective moving bodies is formed at symmetrical positions on the outer peripheral portion of the driven rotating body.
[0015]
  A sixth aspect of the present invention is the power window motor according to the fourth or fifth aspect, wherein the rotation amount regulating means includes the outer peripheral surface of the clutch case and theFits into the open end of the motor case and also serves as part of the motor caseA spring interposed between the cylindrical end portions of the holder base, a first spring engaging portion that protrudes from the outer peripheral surface of the clutch case and engages one end of the spring, and protrudes into the cylindrical end portion of the holder base And a second spring locking portion that locks the other end of the spring. When the clutch case rotates approximately once, the one end of the spring locked to the first spring locking portion is The rotation is prevented by abutting against the other end of the spring locked to the second spring locking portion, and the rotation of the driven shaft rotating integrally with the clutch case is blocked.
[0016]
In the power window motor of the invention of claim 4, 5 or 6, the output shaft is restrained while the drive shaft is rotating due to the external force when the rotational force is inputted from the outside to the output shaft or the energization to the armature is turned on. The rotation of the driven shaft that is rotated by the restoring force of the damper deflected when the energization to the armature is turned off is restricted to about one rotation at the maximum by the rotation amount regulating means, and further rotation is reliably prevented. . As a result, when the window glass is fully closed, the window glass does not open even if the window glass is pushed down from outside with a strong force.
[0017]
When the power supply to the armature is turned off after the output shaft is constrained, the output gear, driven shaft, driven rotor, drive rotor, and drive shaft are set to a predetermined amount (within one rotation) by the restoring force of the deflected damper. ) By reverse rotation, the creep stress applied to the entire power window system such as the tooth portion of the output gear and the window glass and the window regulator is alleviated. As a result, it is possible to use a small and inexpensive output gear or the like, and accordingly, the power window motor can be reduced in size and cost. Further, since the output shaft and the output gear are reversed by a predetermined amount when the window glass is closed, it is possible to reduce the starting voltage when the window glass is opened.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
[0019]
1 is a sectional view showing a power window motor according to an embodiment of the present invention, FIG. 2 is a sectional view of a gear case portion of the power window motor, FIG. 3 is an exploded sectional view of the power window motor, and FIG. 5 is an exploded cross-sectional view of the motor portion of the motor, FIG. 5 is a front view of a clutch used in the power window motor, FIG. 6 is a cross-sectional view taken along the line AA in FIG. 8 is a cross-sectional view taken along the line CC in FIG. 7, FIG. 9 is a rear view of a driving rotating body used in the clutch, and FIG. 10 is a front view of one driven rotating body used in the clutch. FIGS. 11 to 18 are explanatory views sequentially showing each state from the neutral time of the clutch to the time when the position of the scraping portion of the driving rotating body is switched, and FIG. 19 is a diagram illustrating that the output gear of the power window motor is a damper. Resilience and spring Illustration of the case of reverse rotation by the balance of the restoring force, and FIG. 20 is an explanatory diagram showing the characteristic relationships of the damper and the spring.
[0020]
As shown in FIGS. 1 and 3, a power window motor (motor) 1 is fitted into a substantially cylindrical yoke (motor case) 10 having an open end and an open end 10a of the yoke 10, A holder base (motor case) 11 also serving as a part, and a gear case 20 in which a flange portion 10b around the opening end 10a of the yoke 10 is fastened and fixed via rubber packing 8 and screws (fastening means) 9 are provided. ing.
As shown in FIGS. 1, 3, and 4, a pair of magnets 12 and 12 are fixed to the inner peripheral surface 10 c of the yoke 10 in an arc shape with an adhesive or the like. Further, a substantially cylindrical holder base 11 made of synthetic resin is fitted to the opening end 10a of the yoke 10 via a substantially cylindrical spacer 11A made of synthetic resin. These yokes 10 are fitted into bearings 13a fitted to the bottomed cylindrical portion 10d at the other end and a ring-shaped partition wall 11c at the center of the holder base 11 via a bearing support base 11B made of synthetic resin. The drive shaft 14A of the armature shaft 14 is rotatably supported between the bearing 13b. One end 14a of the drive shaft 14A of the armature shaft 14 penetrates outside the bearing 13b and protrudes into the tip cylindrical portion 11a of the holder base 11, and the center of the end surface of the other end 14a 'of the drive shaft 14A is steel. It is in contact with the ball 13c.
[0021]
An armature 16 is attached to a position of the drive shaft 14A of the armature shaft 14 facing the pair of magnets 12 and 12. The armature 16 is composed of an armature core 16a fixed to the drive shaft 14A and having a coil winding portion having a predetermined number of slots, and an armature coil 16b wound around the coil winding portion of the armature core 16a. Yes.
[0022]
Further, a commutator 17 is fixed at a position facing the spacer 11A of the drive shaft 14A of the armature shaft 14. This commutator 17 includes the same number of commutator pieces 17a as the coil winding portion of the armature core 16a, and each commutator piece 17a and the armature coil 16b are electrically connected to each other.
[0023]
A pair of brushes 19 and 19 are attached to the inner peripheral surface 11e of the base end cylindrical portion 11d of the holder base 11 at positions facing the commutator 17 via the brush holders 18, respectively. Each brush 19 is electrically connected to a glass open / close switch of a power window motor control circuit (not shown). When the glass opening switch is turned on, the current of the power source flows to the armature 16 and the like, the drive shaft 14A of the armature shaft 14 rotates forward, and when the glass closing switch is turned on, the current of the power source is changed. The drive shaft 14A of the armature shaft 14 is rotated in the reverse direction by flowing through the armature 16 and the like.
[0024]
As shown in FIGS. 1 to 3, a shaft hole 21 is formed substantially at the center of the gear case 20, and an annular concave reduction mechanism housing portion 21 a is formed in communication with the shaft hole 21. The shaft hole 21 is formed with a small-diameter hole portion 21b and a large-diameter hole portion 21c in a concentric step shape. In the small-diameter hole portion 21b of the shaft hole 21, a cylindrical end portion 11a of the holder base 11 as a motor case in which a clutch 30 described later is housed is housed, and in the large-diameter hole portion 21c of the shaft hole 21. The proximal end cylindrical portion 11d of the holder base 11 is fitted and fixed.
[0025]
The driven shaft 14B of the armature shaft 14 is rotatably supported between a bearing 22a fitted in the back of the shaft hole 21 and a bearing 22b fitted in a position near the small-diameter hole portion 21b of the shaft hole 21. It is. A worm 15 is formed in the center of the driven shaft 14B. That is, the armature shaft 14 is divided into a drive shaft 14A having an armature 16 and a driven shaft 14B having a worm 15, and the driven shaft 14B is rotated between the drive shaft 14A and the driven shaft 14B. A clutch 30 for intermittently rotating (forward rotation or reverse rotation) is interposed. Further, one end 14b of the driven shaft 14B and its semicircular spherical portion 14c protrude into the small diameter hole portion 21b of the shaft hole 21 of the gear case 20, and the center of the end surface of the other end 14b 'of the driven shaft 14B is a steel ball. 22c.
[0026]
As shown in FIG. 2, a cylindrical output shaft support portion 21 d is integrally formed at the center of the speed reduction mechanism housing portion 21 a of the gear case 20. A window regulator (load) (not shown) is interposed between the output shaft support portion 21d and the central cylindrical portion 23a of the metal cover 23 covering the one end opening of the speed reduction mechanism housing portion 21a via a pair of bearings 24a and 24b. The both ends of the output shaft 25 connected to are rotatably supported. An output gear 29 is connected to a serration portion 25a in the vicinity of one end of the output shaft 25 through a resin power transmission member 26, a metal plate 27, and a rubber damper 28 that reduces impact force. The helical gear (tooth portion) 29a of the output gear 29 is engaged with the worm 15 of the driven shaft 14B. The worm 15, the output gear 29, the damper 28, the power transmission member 26, the plate 27, and the output shaft 25 are housed in the speed reduction mechanism housing portion 21a of the gear case 20 to constitute a speed reduction mechanism.
[0027]
As shown in FIGS. 1, 3 to 8, the clutch 30 is formed along a synthetic resin clutch case 31 housed in the tip cylindrical portion 11 a of the holder base 11 and an inner peripheral surface 31 c of the clutch case 31. And a pair of moving bodies 32, 32 housed in a pair of recesses 31d, 31d formed at symmetrical positions on the inner peripheral surface 31c, and rotatably supported in the clutch case 31. And a pair of convex portions 33c, 33c that are connected to one end 14a of the drive shaft 14A and accommodate each moving body 32 in each concave portion 31d of the clutch case 31, and are arranged on both sides of each convex portion 33c. A synthetic resin drive rotating body 33 having a pair of scraped portions 33d and 33d scraped from the respective recesses 31d on the outer peripheral portion 33b, and rotatably supported in the clutch case 31. And a pair of recesses 34c, 34c for accommodating each moving body 32 and a pair of recesses 35c, 35c, which are coupled to one end 14b of the driven shaft 14B, and are provided at positions symmetrical to each other on the outer peripheral portion 34a and the outer peripheral portion 35a. A pair of driven rotators 34, 35 made of resin, interposed between the drive rotator 33 and one driven rotator 34, and the positional relationship between the drive rotator 33 and the driven rotators 34, 35. In the neutral position (neutral position shown in FIG. 7) in which the projections 33c of the drive rotator 33, the recesses 34c and 35c of the pair of driven rotators 34 and 35, and the recesses 31d of the clutch case 31 coincide with each other. The return spring 36 is a torsion coil spring that is always biased to return. A spring 41 is interposed between the inner peripheral surface 11 b of the tip cylindrical portion 11 a of the holder base 11 and the outer peripheral surface 31 a of the clutch case 31.
[0028]
As shown in FIGS. 5 to 8, the clutch case 31 is formed of a synthetic resin in a substantially cylindrical shape, and a spring locking portion 31b is integrally formed on the outer peripheral surface 31a so as to extend in the axial direction. . In addition, semicircular recesses 31d are respectively formed at symmetrically opposed positions on the inner peripheral surface 31c of the clutch case 31.
[0029]
As shown in FIG. 6 and FIG. 7, each moving body 32 is formed in a cylindrical shape from, for example, a synthetic resin, and is accommodated in each recess 31 d of the clutch case 31. And when each moving body 32 rotationally moves along the inner peripheral surface 31c of the clutch case 31, torque transmission of the power window motor 1 is performed.
[0030]
As shown in FIGS. 6 to 9, a substantially D-shaped mounting hole 33 a is formed in the center of the drive rotating body 33 to fit and connect one end 14 a of the drive shaft 14 </ b> A having a notch on the outer periphery. In addition, on both sides thereof, a pair of outer peripheral portions 33b and 33b are integrally formed in an arc shape that slides on the inner peripheral surface 31c of the clutch case 31. In addition, at the center of both sides of the pair of outer peripheral portions 33b and 33b of the drive rotator 33, convex portions 33c for accommodating the respective moving bodies 32 in the respective concave portions 31d of the clutch case 31 are integrally formed, and the respective convex portions are formed. A pair of scraping portions 33d and 33d are integrally formed on both sides of the portion 33c in a semicircular concave shape that scrapes each moving body 32 from each recess 31d of the clutch case 31. In addition, fan-shaped openings 33e are formed inside the pair of outer peripheral portions 33b and 33b of the drive rotator 33, respectively. Further, a cylindrical portion 33f having a larger diameter than the mounting hole 33a is integrally formed on the back surface of the drive rotator 33, and one end of both ends 36a, 36a of the return spring 36 is locked at the inner center thereof. A columnar spring locking portion 33g is integrally formed.
[0031]
As shown in FIGS. 6 to 8 and 10, one driven rotor 34 has a disk portion (outer peripheral portion) 34 a that slides on the inner peripheral surface 31 c of the clutch case 31, and this disk portion. A substantially D-shaped mounting hole 34b is formed in the center of 34a to fit and connect one end 14b of the driven shaft 14B having a notch on the outer periphery. A semi-spherical protrusion 14c at the center of the end surface of one end 14b of the driven shaft 14B fitted and connected to the mounting hole 34b is connected to the mounting hole 33a of the drive rotating body 33 and connected to the driving shaft 14A. It hits the center of the end face of the one end 14a. Further, a pair of recesses 34c and 34c cut out in a front U shape in which the one end 32a side of each moving body 32 is housed are formed at symmetrical positions on the outer peripheral portion of the surface of the disk portion 34a. A columnar spring guide 34d is integrally formed between each recess 34c and the mounting hole 34b.
[0032]
Further, a pair of spring locking portions 34e, 34e in a circular arc column shape into which the pair of spring locking portions 33g, 33g of the drive rotating body 33 are fitted at positions 90 degrees apart from the respective spring guides 34d on the surface of the disc portion 34a. Are formed so as to project integrally, and on the outer side thereof, a substantially trapezoidal columnar shape that is inserted into the pair of openings 33e and 33e of the drive rotator 33 and regulates the amount of forward rotation or reverse rotation of the driven rotator 34. Thus, a pair of support columns 34f and 34f are integrally formed. The other end 36a, 36a of the return spring 36 is locked to one spring locking portion 34e of the pair of spring locking portions 34e, 34e.
[0033]
As shown in FIGS. 5, 6, and 8, the other driven rotor 35 is formed in a disc shape from a synthetic resin, and its outer peripheral portion 35 a is slidable on the inner peripheral surface 31 c of the clutch case 31. ing. In addition, a circular center hole 35b through which the cylindrical portion 33a 'around the mounting hole 33a of the drive rotator 33 is inserted is formed at the center of the other driven rotator 35. A pair of mounting holes 35d and 35d are formed in which the tips of the pair of support columns 34f and 34f of the driven rotating body 34 are inserted and fixed by welding or the like. As a result, the pair of driven rotating bodies 34 and 35 rotate together with the driving rotating body 33 interposed therebetween.
[0034]
Further, on the left and right sides of the outer peripheral portion 35a on the back surface of the other driven rotating body 35, recesses 35c cut out in a U-shape on the back side in which the other end 32b side of each moving body 32 is housed are formed. The movable bodies 32 are rotatably supported between the concave portions 34c and 35c facing each other of the pair of driven rotary bodies 34 and 35.
[0035]
As shown in FIGS. 4, 7, and 18, one end of both ends 41 a and 41 a of the torsion plate-like spring 41 disposed around the outer peripheral surface 31 a of the clutch case 31 is the outer peripheral surface 31 a of the clutch case 31. The first spring locking portion 31f formed integrally with the first spring locking portion 31f is locked. The other ends of both ends 41 a and 41 a of the spring 41 are locked to a second spring locking portion 11 f that is integrally formed in the distal end cylindrical portion 11 a from the partition wall 11 c of the holder base 11. The spring 41, the first spring locking portion 31f, and the second spring locking portion 11f constitute a rotation amount restricting means 40. The rotation amount restricting means 40 has a maximum rotation amount of approximately one rotation of the driven shaft 14B through the output shaft 25 and the output gear 29 by an external force when a rotational force is input to the output shaft 25 from the outside. It has come to regulate.
[0036]
Further, when the output shaft 25 is restrained while the drive shaft 14A is rotating due to the energization of the armature 16, the driven shaft 14B is restrained via the output gear 29 and the worm 15, and the drive shaft 14A continues to rotate. After the damper 28 is bent by a predetermined amount by the rotational force, the drive shaft 14A is also restrained and stops rotating. Thereafter, when the energization of the armature 16 is turned off, the output gear 29, the driven shaft 14B, the pair of driven rotating bodies 34 and 35, and the respective moving bodies while the spring 41 is twisted and deformed by the restoring force of the deflected damper 28. 32, the drive rotator 33, the drive shaft 14A, and the clutch case 31 are integrally rotated reversely, but the reverse rotation is stopped when the restoring force of the damper 28 and the load required for the torsional deformation of the spring 41 are balanced. It has become.
[0037]
The operation of the clutch 30 used in the power window motor 1 of the embodiment will be described in order with reference to FIGS. 11 to 18 show that the drive shaft 14A, the return spring 36, the moving body 32, the drive rotator 33, the pair of driven rotators 34 and 35, and the load applied to each part of the driven shaft 14B are different from each other in the drive shaft. Load applied to the 14A side <Set load of the return spring 36 <Reaction force of the return spring 36 when the movable body 32 is accommodated between the drive rotating body 33 and the pair of driven rotating bodies 34, 35 <Load applied to the driven shaft 14B side It is a figure which shows the positional relationship of the moving body 32 at the time of inputting the rotational force from 14 A of drive shafts, or the driven shaft 14B, and each part on the conditions of these.
[0038]
FIG. 11 shows the state of the clutch 30 in the neutral state. When a rotational force is input from the outside of the power window motor 1 to the driven shaft 14B via the output shaft 25 and the output gear 29, the clutch case 31 is formed at the concave portions 34c, 35c facing each other of the pair of driven rotating bodies 34, 35. The drive body 33 is held by the set load of the return spring 36 (the projections 33c of the drive rotor 33 are provided in the clutch case 31). Since each moving body 32 is pressed against and stored in the recess 31d), the pair of driven rotating bodies 34 and 35 are twisted together with each moving body 32, the driving rotating body 33, and the clutch case 31 to deform the spring 41. Rotate while letting After approximately one rotation, one end 41a of the spring 41 locked to the first spring locking portion 31b formed integrally protruding on the outer peripheral surface 31a of the clutch case 31 is formed integrally protruding into the tip cylindrical portion 11a of the holder base 11. The abutting against the other end 41a of the spring locked to the second spring locking portion 11f is prevented, and the rotation (forward rotation and reverse rotation) of the pair of driven rotating bodies 34 and 35 is prevented. That is, when a rotational force is input to the driven shaft 14B from the outside via the output shaft 25 and the output gear 29, the rotation amount of the driven shaft 14B can be regulated to about one rotation at most by the rotation amount regulating means 40. it can. The rotation of the driven shaft 14B when converted into the rotation amount of the output shaft 25 is 360 ° ÷ the number of teeth of the output gear 29 (for example, 72), which is very small, about 5 °. As a result, when the window glass is fully closed, the window regulator connected to the output shaft 25 is hardly driven even if the window glass is strongly pushed down, and the window glass can be reliably prevented from falling. As a result, theft of the automobile can be reliably prevented without the window glass being opened carelessly.
[0039]
FIG. 12 shows a state during operation of the drive rotor 33 of the clutch 30 when a load is applied to the driven shaft 14B. When the drive rotator 33 rotates in the direction of the arrow, each convex portion 33 c of the drive rotator 33 moves away from each movable body 32 stored in each concave portion 31 d of the clutch case 31, and each movable body 32 corresponds to each drive rotator 33. It is released from the restrained state by the convex portion 33 c, and each of the scraping portions 33 d of the drive rotating body 33 heads for scraping of the moving body 32.
[0040]
FIG. 13 shows a state in which torque is being transmitted to the pair of driven rotating bodies 34 and 35 by the operation of the driving rotating body 33 of the clutch 30. At this time, each moving body 32 is scraped from each recess 31 d of the clutch case 31 by each one of the scraping portions 33 d of the driving rotating body 33, and each moving body 32 is paired with each of the scraping portions 33 d of the driving rotating body 33. The driven rotating bodies 34, 35 are held between the opposing concave portions 34c, 35c, and the rotational force of the driving rotating body 33 is transmitted to the pair of driven rotating bodies 34, 35 via the respective moving bodies 32. The shaft 14B is rotated.
[0041]
That is, as indicated by the arrows in FIG. 13, when the drive rotator 33 rotates, each moving body 32 has each of the scraped portions 33 d of the drive rotator 33 and the corresponding recesses of the pair of driven rotators 34 and 35. Each moving body 32 is in contact with the inner peripheral surface 31c of the clutch case 31 and each scraping portion 33d of one of the drive rotating bodies 33 and the pair of driven rotating bodies 34, 35 are opposed to each other. It is held between the recesses 34c and 35c and rotates.
[0042]
FIG. 14 shows a state when the drive rotator 33 is stopped (each moving body 32 is stopped except for each recess 31 d of the clutch case 31). This state is a state in which each moving body 32 is pushed out to the inner peripheral surface 31 c of the clutch case 31 by the reaction force of the return spring 36 and the drive rotating body 33. Each moving body 32 has an inner peripheral surface 31 c of the clutch case 31 and each of the concave portions 34 c and 35 c facing each other of the pair of driven rotating bodies 34 and 35 and each of the driving rotating bodies 33 as indicated by black dots in FIG. 14. It contacts the convex portion 33c.
[0043]
FIG. 15 shows a case where a rotational force is input from the driven shaft 14B side when the rotation of the drive shaft 14A of the clutch 30 is stopped, and FIG. 16 shows that each moving body 32 of the clutch 30 is housed in each recess 31d of the clutch case 31. FIG. 17 shows a state immediately before, and FIG. 17 shows a state when each moving body 32 is housed in each recess 31 d of the clutch case 31.
[0044]
As shown in FIG. 15, each movable body 32 is pushed by each convex portion 33c of the driving rotary body 33 and the concave portions 34c and 35c facing each other of the pair of driven rotary bodies 34 and 35 by the rotation of the driven shaft 14B in the arrow direction. When the movable bodies 32 reach the recesses 31d of the inner peripheral surface 31c of the clutch case 31 as shown in FIG. Each movable body 32 is pushed out by each convex portion 33c, and each movable body 32 is accommodated in each concave portion 31d of the inner peripheral surface 31c of the clutch case 31, as shown in FIG. Each of the movable bodies 32 is scraped from the recesses 31d of the clutch case 31 by the opposing recesses 34c and 35c of the pair of driven rotors 34 and 35. The drive rotor 33 and one of the driven rotors 34 Each moving body 32 can come out of each recessed portion 31d of the clutch case 31 by each projecting portion 33c of the drive rotating body 33 which automatically tries to return to the neutral position by the urging force of the return spring 36 stretched between them. This is not possible and the neutral state is obtained as in FIG.
[0045]
In FIG. 18, the driven shaft 14B rotates by a certain amount (up to about one rotation) from the stop of rotation of the drive shaft 14A in which each movable body 32 is accommodated in each concave portion 31d of the clutch case 31 by each convex portion 33c of the drive rotary body 33. Indicates the state to be performed. That is, the output shaft 25 is constrained during the rotation of the drive shaft 14A, so that the drive shaft 14A stops rotating, and thereafter the movement of the clutch 30 and the driven shaft 14B when the energization to the armature 16 is turned off is shown.
[0046]
When the output shaft 25 is constrained while the drive shaft 14A is rotating, the driven shaft 14B is constrained via the output gear 29 and the worm 15, and the damper 28 has a predetermined amount due to the rotational force of the drive shaft 14A that continues to rotate. After being bent, the drive shaft 14A is also restrained and stops rotating. Thereafter, when the energization of the armature 16 is turned off, the output gear 29, the driven shaft 14B, the pair of driven rotating bodies 34 and 35, and the respective moving bodies 32 while the spring 41 is torsionally deformed by the restoring force of the deflected damper 28. The drive rotating body 33 and the clutch case 31 are integrally rotated in the reverse direction in the direction of the arrow, and the reverse rotation is stopped when the restoring force of the damper 28 and the load required for the torsional deformation of the spring 41 are balanced.
[0047]
FIG. 19 shows the case where the output gear 29 of the power window motor 1 rotates reversely (reverses) by the restoring force of the damper 28 and the spring 41, for example, the driven shaft 14B is restrained while the drive shaft 14A is rotating, and the power window motor 1 shows the state when the power supply to 1 is turned off, the arrow X in FIG. 19 indicates the rotation direction of the output gear 29 until the output shaft 25 is restrained, and the arrow Y in FIG. 19 indicates the restoration of the damper 28 and the spring 41. The rotation direction in which the output gear 29 is reversely rotated by force is shown. FIG. 20 shows the characteristic relationship between the damper 28 and the spring 41.
[0048]
That is, when the driven shaft 14B is restrained by the restraint of the output shaft 25 (the output gear 29) while the drive shaft 14A is rotating, the second spring locking portion 11f formed on the holder base 11 and the second formed on the clutch case 31. A spring 41 having both ends 41a and 41a locked to one spring locking portion 31f is bent at a predetermined angle by the torque of the power window motor 1, and the power supply to the power window motor 1 (armature 16) is turned off. Thus, the driven shaft 14B, the pair of driven rotating bodies 34 and 35, and the driving rotating body 33 are driven by the restoring force of the bent spring 41 and the restoring force of the damper 28 coupled (incorporated) to the output gear 29. The shaft 14A is reversely rotated by a predetermined range, and the output gear 29 is released from the restrained state. Thereby, the creep stress and impact force applied to the entire power window system such as the helical teeth (tooth portion) 29a of the output gear 29, the window glass, and the window regulator can be reduced. As a result, a small and inexpensive output gear or the like can be used, and the overall size and cost can be reduced accordingly. In addition, when the window glass is closed, the output shaft 25 and the output gear 29 are reversely rotated within a predetermined range to reduce the starting voltage.
[0049]
Further, in this power window motor 1, as shown in FIGS. 3 and 4, a clutch 30 is detachably assembled in a distal end cylindrical portion 11a of a holder base 11 as a motor case that rotatably supports a drive shaft 14A. A drive rotator 33 is connected to one end 14a of the drive shaft 14A, and then a yoke 10 as a motor case is removably assembled via a screw 9 to a gear case 20 that rotatably supports the driven shaft 14B. Since the pair of driven rotors 34 and 35 of the clutch 30 are connected to the one end 14b, before the motor cases 10 and 11 are assembled to the gear case 20, the drive shaft 14A side (motor portion) of the power window motor 1 and the clutch 30 performance confirmations and performance confirmations such as inspections can be performed simultaneously and easily. Thereby, the reliable power window motor 1 can be provided at low cost.
[0050]
【The invention's effect】
As described above, according to the motor of the first, second, or third aspect of the invention, the output is output while the drive shaft is rotating due to the external force when the rotational force is input from the outside to the output shaft or the energization to the armature. The rotation of the driven shaft that is rotated by the restoring force of the damper bent when the shaft is restrained and the energization to the armature is turned off is restricted to about one rotation at the maximum by the rotation amount restricting means, and further rotation is not allowed. It can be surely stopped.
[0051]
When the power supply to the armature is turned off after the output shaft is constrained, the output gear, driven shaft, driven rotor, drive rotor, and drive shaft are set to a predetermined amount (within one rotation) by the restoring force of the deflected damper. ) By reverse rotation, the creep stress applied to the teeth of the output gear is alleviated.
[0052]
As a result, it is possible to use a small and inexpensive output gear and the like, and accordingly, the motor can be reduced in size and cost.
[0053]
According to the power window motor of the invention of claim 4, 5 or 6, the output shaft is restrained while the drive shaft is rotating due to the external force when the rotational force is input from the outside to the output shaft or the energization to the armature. The rotation of the driven shaft, which is rotated by the restoring force of the damper deflected when the energization to the armature is turned off, is regulated to about one rotation at the maximum by the rotation amount regulating means, and further rotation can be reliably prevented. .
[0054]
As a result, when the window glass is fully closed, the window glass does not open even if the window glass is pushed down from outside with a strong force.
[0055]
When the power supply to the armature is turned off after the output shaft is constrained, the output gear, driven shaft, driven rotor, drive rotor, and drive shaft are set to a predetermined amount (within one rotation) by the restoring force of the deflected damper. ) By reverse rotation, the creep stress applied to the entire power window system such as the tooth portion of the output gear and the window glass and the window regulator is alleviated. As a result, it is possible to use a small and inexpensive output gear and the like, and accordingly, the power window motor can be reduced in size and cost. Further, since the output shaft and the output gear are reversed by a predetermined amount when the window glass is closed, it is possible to reduce the starting voltage when the window glass is opened.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a power window motor according to an embodiment of the present invention.
FIG. 2 is a sectional view of a gear case portion of the power window motor.
FIG. 3 is an exploded cross-sectional view of the power window motor.
FIG. 4 is an exploded cross-sectional view of a motor portion of the power window motor.
FIG. 5 is a front view of a clutch used in the power window motor.
6 is a cross-sectional view taken along line AA in FIG.
7 is a cross-sectional view taken along line BB in FIG.
FIG. 8 is a cross-sectional view taken along the line CC in FIG.
FIG. 9 is a rear view of a drive rotator used for the clutch.
FIG. 10 is a front view of one driven rotor used for the clutch.
FIG. 11 is an explanatory view showing a state of the clutch in a neutral state.
FIG. 12 is an explanatory diagram showing a state when the driving rotating body of the clutch is in operation (when a load is applied to the driven shaft).
FIG. 13 is an explanatory diagram showing a state in which torque is being transmitted to the driven rotor by the operation of the driving rotor of the clutch.
FIG. 14 is an explanatory view showing a state when the driving rotating body is stopped (the moving body is stopped at a position other than the concave portion of the clutch case).
FIG. 15 is an explanatory diagram when a rotational force is input from the driven shaft side when the rotation of the drive shaft of the clutch is stopped.
FIG. 16 is an explanatory view showing a state immediately before the moving body of the clutch is housed in the recess of the clutch case.
FIG. 17 is an explanatory view showing a state when the moving body is housed in the recess of the clutch case.
FIG. 18 is an explanatory view showing a state in which the driven shaft rotates by a certain amount from the time when the rotation of the drive shaft stored in the recess of the clutch case is stopped.
FIG. 19 is an explanatory diagram in the case where the output gear of the power window motor rotates in reverse due to the balance between the restoring force of the damper and the restoring force of the spring.
FIG. 20 is an explanatory diagram showing a characteristic relationship between the damper and the spring.
[Explanation of symbols]
  1 Power window motor (motor)
  10 Yoke (motor case)
  10a Open end
  10c Inner peripheral surface
  11 Holder base (motor case)
  11a End cylindrical part
  11f Second spring locking part
  12 Magnet
  14 Armature axis
  14A Drive shaft
  14B driven shaft
  15 Warm
  16 Armature
  20 Gear case
  21 Shaft hole
  25 Output shaft
  28 Damper
  29 Output gear
  30 clutch
  31 Clutch case
  31a outer peripheral surface
  31b 1st spring latching part
  31c Inner peripheral surface
  31d recess
  32 Mobile
  33 Rotating body for driving
  33b Outer periphery
  33c Convex part
  33d scraping part
  34, 35 Followed rotating body
  34a, 35a outer periphery
  34c, 35c recess
  36 Return spring
  40 Rotation amount regulating means
  41 Spring

Claims

A motor case in which a magnet is fixed to the inner peripheral surface, a gear case coupled to the motor case and rotatably supporting an output shaft connected to a load, and a motor case and a gear case that are rotatably supported by the motor case. An armature shaft of a rotating armature, a worm formed on the armature shaft in the gear case, and a worm rotatably supported by the gear case and connected to the output shaft via a damper for reducing impact force and the worm And an output gear meshed with the motor,
The armature shaft is divided into a drive shaft having the armature and a driven shaft forming the worm, and a clutch for intermittently rotating the driven shaft is interposed between the drive shaft and the driven shaft,
The clutch is rotatably disposed in the cylindrical end portion of the motor case housed in the shaft hole of the gear case, and is rotated on the inner peripheral surface of the clutch case and formed on the inner peripheral surface. A movable body housed in the recessed portion, a convex portion which is rotatably supported in the clutch case and is connected to the drive shaft, and the movable body is housed in the concave portion of the clutch case, and a scrape which is scraped from the concave portion. A driving rotator each having an outer peripheral portion, a driven rotator that is rotatably supported in the clutch case and connected to the driven shaft, and has a recess in the outer peripheral portion for housing the moving body, These drive rotators are interposed between the driven rotator and the positional relationship between the two rotators. Each position of the parts is constituted by a return spring for biasing to return always to the neutral position matching each
Deflection occurs when external force is applied to the output shaft from the outside, or when the drive shaft is rotated and the output shaft is constrained while the armature is turned off by turning on the power to the armature. Further, a rotation amount restricting means for restricting the rotation amount of the driven shaft, which is rotated by the restoring force of the damper, to a maximum of approximately one rotation is interposed between the tip cylindrical portion of the motor case and the clutch case. motor.

The motor according to claim 1,
A pair of recesses are formed at symmetrical positions on the inner peripheral surface of the clutch case, and the movable body is configured as a pair of moving bodies that are respectively housed in the respective recesses of the clutch case, and the outer peripheral portion of the drive rotor Forming a pair of convex portions for accommodating the respective moving bodies in the respective concave portions of the clutch case, and a pair of scraping portions disposed on both sides of the respective convex portions to scrape the respective movable bodies from the respective concave portions, A motor characterized in that a pair of recesses for storing the respective moving bodies are formed at positions symmetrical to each other on the outer peripheral portion of the driven rotating body.

The motor according to claim 1 or 2,
The rotation amount restricting means includes a spring that is fitted between the outer peripheral surface of the clutch case and the opening end of the motor case and interposed between the cylindrical end portions of the holder base that also serves as a part of the motor case , and the clutch case A first spring locking portion that protrudes from the outer peripheral surface of the holder base and locks one end of the spring, and a second spring locking portion that protrudes from the front end cylindrical portion of the holder base and locks the other end of the spring. The one end of the spring locked to the first spring locking portion is locked to the second spring locking portion when the clutch case is rotated approximately once, and the other end of the spring is locked to the second spring locking portion. Rotation of the driven shaft that rotates integrally with the clutch case is prevented by contacting with the motor.

A motor case with a magnet fixed to the inner peripheral surface, a gear case coupled to the motor case and rotatably supporting an output shaft connected to a window regulator, and a motor case and a gear case that are rotatably supported by the motor case and the gear case, respectively. The armature shaft of the armature that rotates by the above, a worm formed on the armature shaft in the gear case, and rotatably supported by the gear case, and connected to the output shaft via a damper that reduces impact force and In a power window motor having an output gear meshed with a worm,
The armature shaft is divided into a drive shaft having the armature and a driven shaft forming the worm, and a clutch for intermittently rotating the driven shaft is interposed between the drive shaft and the driven shaft,
The clutch is rotatably disposed in the cylindrical end portion of the motor case housed in the shaft hole of the gear case, and is rotated on the inner peripheral surface of the clutch case and formed on the inner peripheral surface. A movable body housed in the recessed portion, a convex portion which is rotatably supported in the clutch case and is connected to the drive shaft, and the movable body is housed in the concave portion of the clutch case, and a scrape which is scraped from the concave portion. A driving rotator each having an outer peripheral portion, a driven rotator that is rotatably supported in the clutch case and connected to the driven shaft, and has a recess in the outer peripheral portion for housing the moving body, These drive rotators are interposed between the driven rotator and the positional relationship between the two rotators. Each position of the parts is constituted by a return spring for biasing to return always to the neutral position matching each
Deflection occurs when external force is applied to the output shaft from the outside, or when the drive shaft is rotated and the output shaft is constrained while the armature is turned off by turning on the power to the armature. Further, a rotation amount restricting means for restricting the rotation amount of the driven shaft, which is rotated by the restoring force of the damper, to a maximum of approximately one rotation is interposed between the tip cylindrical portion of the motor case and the clutch case. Power window motor.

A power window motor according to claim 4,
A pair of recesses are formed at symmetrical positions on the inner peripheral surface of the clutch case, and the movable body is configured as a pair of moving bodies that are respectively housed in the respective recesses of the clutch case, and the outer peripheral portion of the drive rotor Forming a pair of convex portions for accommodating the respective moving bodies in the respective concave portions of the clutch case, and a pair of scraping portions disposed on both sides of the respective convex portions to scrape the respective movable bodies from the respective concave portions, A power window motor characterized in that a pair of recesses for housing the moving bodies are formed at positions symmetrical to each other on the outer peripheral portion of the driven rotating body.

A power window motor according to claim 4 or 5,
The rotation amount restricting means includes a spring that is fitted between the outer peripheral surface of the clutch case and the opening end of the motor case and interposed between the cylindrical end portions of the holder base that also serves as a part of the motor case , and the clutch case A first spring locking portion that protrudes from the outer peripheral surface of the holder base and locks one end of the spring, and a second spring locking portion that protrudes from the front end cylindrical portion of the holder base and locks the other end of the spring. The one end of the spring locked to the first spring locking portion is locked to the second spring locking portion when the clutch case is rotated approximately once, and the other end of the spring is locked to the second spring locking portion. Rotation of the driven shaft that rotates integrally with the clutch case is prevented by contact with the power window motor.