JP4334828B2

JP4334828B2 - Energy storage spring device

Info

Publication number: JP4334828B2
Application number: JP2002209550A
Authority: JP
Inventors: 恭一大塚; 智仁森
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2002-07-18
Filing date: 2002-07-18
Publication date: 2009-09-30
Anticipated expiration: 2022-07-18
Also published as: JP2004055269A

Description

【０００１】
【発明の属する技術分野】
この発明は蓄勢ばね装置に関し、特にフレームに回転自在に支持されたクランク軸の回転により、ばねロッドを介して蓄勢、放勢される蓄勢ばねを備えた蓄勢ばね装置に関するものである。
【０００２】
【従来の技術】
図８は実公昭６３−４２４３３号公報に示された変電所や開閉所に設置される電力用開閉装置におけるしゃ断器の投入機構に用いられた蓄勢ばね装置の要部断面図である。蓄勢ばね装置は、フレーム１と、フレーム１に回転自在に取り付けられた回転軸２および回転軸２に固定されたクランクアーム３を備えたクランク軸４と、一端がクランクアーム３にピン５を用いて回転自在に連結されたばねロッド６と、ばねロッド６の他端と球面座７を介して回転自在に連結された可動ばね受け８と、可動ばね受け８とフレーム１に当接して圧縮されたコイルばねからなる蓄勢ばね９とを備えている。さらに蓄勢ばね９が蓄勢されると蓄勢ばね９のたわみや曲がりが発生しやすく、座屈の危険があるので、フレーム１に固定されて蓄勢ばね９を案内する円筒状の案内装置１０が設けられている。
【０００３】
図９は遮断部操作レバー１１の操作装置の要部断面図である。この図は遮断器の開放状態で、かつ蓄勢ばね９は蓄勢状態を示す。遮断部操作レバー１１の操作装置は、フレーム１に支持されたピン１２に回転自在に軸支された遮断部操作レバー１１と、遮断部操作レバー１１に形成された溝部１３にピン１４で回転自在に軸支されたローラ１５と、遮断部操作レバー１１に回転自在に軸支されたピン１６と、フレーム１にピン１７で回転自在に軸支されたカケガネ１８と、ピン１９で回転自在に軸支されたトリガ２０と、電磁石２１を作用することにより図９で右方向に移動してトリガ２０と衝突するプランジャ２２とを備えている。カケガネ１８とフレーム１との間及びトリガ２０とフレーム１との間にそれぞれ復帰ばね２３と復帰ばね２４が蓄勢されている。また回転軸２にはカム２５が固定的に取付られている。
【０００４】
遮断部操作レバー１１に支持されたピン２６は図示してない遮断部と連結されており、かつ、図示してない引はずしばねにより矢印Ａの方向に力を受けている。遮断部操作レバー１１はカケガネ１８との係合が外れて反時計方向に回転して停止した状態である。カケガネ１８とトリガ２０はプランジャ２２が図９に示す右方向に移動してトリガ２０を時計方向へ回転して係合が外れた状態である。
【０００５】
遮断器の投入動作について図８と図９を参照して説明する。クランク軸４に係合している図示してないピンとの係合が外れて、クランク軸４は蓄勢ばね９の力により図で反時計方向に回転し、クランク軸４の回転とともにカム２５も反時計方向に回転する。カム２５の回転とともにローラ１５がカム２５の外周面に沿って転動し、遮断部操作レバー１１はピン１２回りに時計方向に回転される。遮断部操作レバー１１の回転により、ピン２６に連結されている図示してない引きはずしばねが蓄勢される。遮断部操作レバー１１が時計方向に回転してピン１６がカケガネ１８に、カケガネ１８がトリガ２０にそれぞれ復帰ばね２３、２４により係合して、カム２５がさらに回転してローラ１５と接触しない状態になったとき、遮断部操作レバー１１が矢印Ａ方向の引きはずし力により反時計方向に回転するのを阻止し、投入状態を保持する。
【０００６】
【発明が解決しようとする課題】
従来の蓄勢ばね装置は以上のように構成されていたので、次のような問題点を有している。
図８に見られるように、ばねロッド６と可動ばね受け８とは球面座７で連結されているので、クランク軸４によって駆動されるばねロッド６の作用力は常にばねロッド６の中心軸上にある。また、クランク軸４が回転したときには蓄勢ばね９の中心軸９ａに対するばねロッド６の角度θが変化し、この角度θの変化は球面座７の回転中心２８を中心とした変化である。従って、ばねロッド６の作用力のばね受け８上の作用点は、球面座７の回転中心２８である。
【０００７】
一方、蓄勢ばね９の作用力は図示のコイルばねの場合は中心軸９ａ上にあり、可動ばね受け８に対してはばね受け面である当接面２９上で作用しているため、蓄勢ばね９のばね作用力は可動ばね受け８上の作用点Ｇで作用している。
【０００８】
これらの２つの作用点２８およびＧは、蓄勢ばね９の中心軸９ａの方向（単に軸方向ということもある）に距離Ｘだけ離れている。従って、ばねロッド６の軸心と蓄勢ばね９の中心軸９ａとが一致しているときはそれぞれの力の作用線も一致しているので、可動ばね受け８には可動ばね受け８を回転させるような回転モーメントは発生しない。
【０００９】
クランク軸４が回転したときには、蓄勢ばね９の中心軸９ａに対してばねロッド６が角度θだけ傾斜し、この角度θにより、ばねロッド６の作用力の作用線と蓄勢ばね９の作用力の作用線との間にずれが生じ、可動ばね受け８を回転させようとする力が発生する。この回転モーメントは、蓄勢ばね９の蓄勢荷重をＦとし、ばねロッド６の変位が角度θであると、２つの作用点２８と作用点Ｇとの間の軸方向の距離がＸであるので、可動ばね受け８を作用点２８を中心に時計方向に回転させようとするＦ・Ｘ・ｔａｎθなる回転モ−メントが発生する。可動ばね受け８は、このモーメントによって、蓄勢ばね９の変形による作用力の変化により回転モーメントが無くなる位置まで図８で時計方向に回動する。
【００１０】
このような可動ばね受け８の回動が起こると、円筒状あるいはロッド状の案内装置１０と可動ばね受け８の被案内面との間が平行でなくなり、その間の摩擦が大きくなってしまい、噛んでしまうことさえあり、蓄勢ばね装置の動作が滑らかに行われなくなるという欠点があった。このような摩擦を低減するために案内装置２７と可動ばね受け８の摺動部にベアリングなどを設けたり、複雑なリンク機構を追加して直線運動に変換後可動ばね受けに連結したりすることも提案されているが、新たな部品が必要になったり、体積が大きくなるなどの問題点があった。
【００１１】
従って、この発明の目的は、上述のような従来の蓄勢ばね装置の問題点を解消することであり、ベアリング、リンク機構などの部品を追加することなく、簡単な構造により安定な速度などの駆動性能を確保できる蓄勢ばね装置を得ることである。
【００１２】
【課題を解決するための手段】
この発明によれば、上述の課題を解決するための手段は次の通りである。
（１）蓄勢ばね装置は、フレームと、フレームに一端で支持された蓄勢ばねと、蓄勢ばねの他端に設けられ、蓄勢ばねのばね作用力を受ける可動ばね受けと、フレームに設けられたクランク軸と、一端でクランク軸に回転可能に連結され、他端で可動ばね受けに回転可能に連結され、上記クランク軸の回転に応じて可動ばね受けに作用力を加えて蓄勢ばねに蓄勢するばねロッドと、フレームに取り付けられて可動ばね受けが直線運動をするように案内する案内装置とを備え、蓄勢ばねのばね作用力の可動ばね受け上の作用点と、ばねロッドの作用力のばね受け上の作用点とが一致した位置に在る。
【００１３】
（２）また、蓄勢ばね装置は、フレームと、クランク軸と、一端でクランク軸に回転可能に連結されたばねロッドと、ばねロッドの他端に回転中心回りに回転可能に連結された可動ばね受けと、フレームに取り付けられて可動ばね受けが直線運動をするように案内する案内装置と、可動ばね受けおよびフレーム間に設けられ、中心軸を有する蓄勢ばねとを備え、回転中心が、蓄勢ばねの中心軸上に在り、かつ可動ばね受けの蓄勢ばねが当接する当接面内に在ってもよい。
【００１４】
（３）更に、蓄勢ばね装置は、フレームと、クランク軸と、一端でクランク軸に回転可能に連結されたばねロッドと、ばねロッドの他端に回転中心回りに回転可能に連結された可動ばね受けと、フレームに取り付けられて可動ばね受けが直線運動をするように案内する案内装置と、可動ばね受けおよびフレーム間に設けられ、中心軸を有する蓄勢ばねとを備え、蓄勢ばねが、互いに同軸に重ねて配置され、それぞれ異なる当接面を持つ複数のコイルばねであり、回転中心が、蓄勢ばね、の中心軸上に在り、かつ回転中心から蓄勢ばねの軸方向に見た各当接面までの距離と各蓄勢ばねの蓄勢荷重との積の和が零近傍になる位置に在ってもよい。
【００１５】
（４）ばねロッドが蓄勢ばねを貫通することなく配置され、フレ−ムに固定された案内装置が蓄勢ばねの軸方向に可動ばね受けを貫通している。
【００１６】
【発明の実施の形態】
実施の形態１．
図１は、この発明の実施の形態１の蓄勢ばねが蓄勢状態の蓄勢ばね装置の断面図であり、従来例の図８に相当する蓄勢ばね機構部である。
蓄勢ばね装置は、フレーム１と、フレーム１に回転自由に支持されたクランク軸４１と、フレーム１に一端で垂直に当接し、中心軸を有する１個の円筒型コイルばねからなる蓄勢ばね４２と、蓄勢ばね４２の他端に設けられ、蓄勢ばね４２のばね作用力を受ける可動ばね受け４３とを備えられている。可動ばね受け４３が円板状で、円周状の当接面Ｓで蓄勢ばね４２を受けている。
【００１７】
蓄勢ばね装置はまた、一端でクランク軸４１に回転可能に連結され、他端で可動ばね受け４３に回転可能に連結され、クランク軸４１の回転に応じて可動ばね受け４３に作用力を加えて蓄勢ばね４２に蓄勢するばねロッド４４と、フレーム１に取り付けられて可動ばね受け４３が直線運動をするように案内する案内装置４５とを備えている。
【００１８】
さらに可動ばね受け４３には角柱の突起が中央に設けられ、その角柱の側面に孔が穿孔されている。またばねロッドの一端には音叉状の軸受けが設けられ、その音叉部分に孔が開けられている。そして可動ばね受け４３の角柱状突起の孔とばねロッドの音叉状軸受けの孔を位置を合わせ、ピンを挿入して回転中心４６を設けてある。回転中心４６は当接面Ｓ上及び蓄勢ばね４２の中心軸上に配置してある。
【００１９】
また、クランク軸４１は、回転軸４７とクランク４８からなり、回転軸４７はフレーム１に回転自由に支えられてその軸中心の回りに回転し、クランク４８は回転軸４７から突出したクランクアーム４９とクランクピン５０よりなり、回転軸４７中心の回りにクランクピン５０を回転する。
図１の状態で、ばねロッド４４の軸方向は蓄勢ばね４２の中心軸に対して角度θ１だけ傾いている。
【００２０】
次に閉極動作について説明する。図１は蓄勢ばね４２が蓄勢されており、遮断器が開極状態となっている。すなわち、可動ばね受け４３は蓄勢ばね４２の蓄勢荷重によってＡ方向に付勢されており、このばね作用力はばねロッド４４を介してクランクアーム４９に伝わり、クランク軸４１に回転軸４７回りに反時計方向のトルクが発生する。クランク軸４１は、図示以外の巻き上げ車、図示以外のピン、図示以外のカケガネおよび図示以外のトリガなどからなる保持機構によって回転することなくこのトルクに抗して保持されている。閉極指令が出されると、クランク軸４１の保持機構が解除され、蓄勢ばね４２の蓄勢荷重によってクランクアーム４９およびクランク軸４１が反時計方向に回転を開始し、可動ばね受け４３がＡ方向に移動を開始する。
【００２１】
図２は閉極動作の途中の状態を示している。クランクアーム４９のピン５０は回転軸４７を中心とする円弧の軌跡を描くので、ばねロッド４４の軸方向と蓄勢ばね４２の中心軸のなす角度は変化してθ２となっている。
【００２２】
図３は閉極動作の終了時の状態を表している。クランクアーム４９は回転軸４７の回りを反時計方向に回転し、可動ばね受け４３は図中左側に移動して蓄勢ばね４２が放勢状態となっている。このとき、ばねロッド４４の軸方向と蓄勢ばね４２の中心軸のなす角度はθ３に変化している。
【００２３】
蓄勢ばね４２の蓄勢動作について説明する。図３の状態から、動力源（図示せず）により、クランク軸４１に固着している巻き上げ車（図示せず）が回転して、クランクアーム４９が回転軸４７の回りを時計方向に回転するとともに可動ばね受け４３が図３のＢ方向に移動を開始する。図３の状態から、図２の状態となり、図１に示すように蓄勢ばね４２の蓄勢が完了すると、保持機構（図示せず）によって、クランク軸４１が反時計方向に回転しないように保持され、蓄勢動作を終了する。
【００２４】
この発明の実施の形態１に係る回転中心４６の位置は蓄勢ばね４２の中心軸と可動ばね受け４３の蓄勢ばね当接面Ｓの交点に配置しており、蓄勢ばね４２のばね力の作用点はコイルばねの中心軸上にあり、かつ当接面Ｓ上にあるので、回転中心４６にあるばねロッド４４の作用力の作用点と一致している。したがって、可動ばね受け４３に作用する力のモ−メントはほぼ零になり、蓄勢ばね４２が放勢するとき、可動ばね受け４３が傾くことがほとんどなくなり、案内装置４５と可動ばね受け４３の貫通孔との摩擦抵抗を小さく抑えられる。このように、本発明では、案内装置４５と可動ばね受け４３の摺動部にベアリング等を設けることなく、円筒型のコイルばねの中心軸と、蓄勢ばねの可動ばね受けの当接面の交点に回転中心４６を設けることで簡単に安定な速度等の駆動特性を有した遮断器の投入機構として蓄勢ばね装置が得られる。
【００２５】
なお、実施の形態１では、蓄勢ばね４３と可動ばね受け４３等から構成する機構を投入ばね機構として用いていたが、同様な構成であれば、遮断ばね機構にも適用可能である。
【００２６】
また、実施の形態１では、回転中心として回転自在なピン接続を用いているが、球面座、ボール受けでも同様な回転自在な接続が可能である。
【００２７】
実施の形態２．
図４は、この発明の実施の形態２による蓄勢ばね装置のばね機構部の断面図であり、蓄勢ばね４２が蓄勢されており、遮断器が開極状態となっている。
フレ−ム１、クランクアーム４９、クランク軸４１、回転中心４６、ピン５０、ばねロッド４４、蓄勢ばね４２、案内装置４５など、構成する部品は形態１とほぼ同様である。
【００２８】
ただし、案内装置４５の左端に固定ばね受け５１が固定されており、蓄勢ばね４２は固定ばね受け５１と可動ばね受け４３の間に圧縮されて設けられている。したがって、閉極指令が出されて蓄勢ばね４２が放勢を開始すると、Ｃ方向に可動ばね受け４３が押されてばねロッド４４がＣ方向に移動し、クランク軸４１が回転軸４７の回りに時計方向に回転する。また、蓄勢ばね４２の蓄勢動作時は、動力源（図示せず）によって、クランクアーム４９が回転軸４７の回りを反時計方向に回転し、可動ばね受け４２がＣ方向と反対方向に移動することによって、蓄勢ばね４２が蓄勢される。このように、遮断器の閉極動作または蓄勢ばね４２の蓄勢動作時の、クランクアーム４９の回転方向、可動ばね受け４３の移動方向等は、形態１のそれらと比べ、反対になる。
【００２９】
さて、回転中心４６は、図中の１点鎖線が示すように、蓄勢ばね４２の中心軸と可動ばね受け４３の蓄勢ばね当接面Ｓの交点に位置しており、蓄勢ばね４２のばね力の作用点はコイルばねの中心軸上にあり、かつ当接面Ｓ上にあるので、回転中心にあるばねロッド４４の作用力の作用点と一致している。したがって、可動ばね受け４３に発生するモ−メントはほぼ零になり、蓄勢ばね４２が放勢するとき、可動ばね受け４３が傾くことがほとんどなくなり、案内装置４５と可動ばね受け４３の貫通孔との摩擦抵抗を小さく抑えられる。このように、本発明では、案内装置４５と可動ばね受け４３の摺動部にベアリング等を設けることなく、円筒型のコイルばねの中心軸と、蓄勢ばねの可動ばね受けの当接面の交点に回転中心を設けることで簡単に安定な速度等を有する遮断器の投入機構として蓄勢ばね装置が得られる。
【００３０】
また、ばねロッド４４が蓄勢ばね４２を貫通していないので、可動ばね受け４３の全面を蓄勢ばね４２の当接面にするように断面形状が細長い長方形のコイルばねを用いることができて小形化が可能になり、さらに高蓄勢な蓄勢ばね装置が得られる。
さらに可動ばね受け４３が蓄勢ばね４２の軸方向に垂直の姿勢に配置出来て、蓄勢ばねが軸方向に安定して運動出来る。
【００３１】
なお、実施の形態２においても、蓄勢ばね４２と可動ばね受け４３等から構成する機構を投入ばね機構として用いていたが、同様な構成であれば、遮断ばね機構にも適用可能である。
【００３２】
実施の形態３．
図５は、この発明の実施の形態３の蓄勢ばねが蓄勢状態の蓄勢ばね装置の断面図である。実施の形態１との相違点は複数の蓄勢ばねを用いたことである。すなわちフレーム１に一端で垂直に当接し、直線上に支持された４本の円筒状コイルばねからなる蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄと、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄの他端に設けられ、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄのばね作用力を受ける可動ばね受け６２とを備えられている。
【００３３】
ここで蓄勢ばねの合力の作用点とばねロッドの作用力の作用点を合わせる方法を説明する。ばねロッドの作用力の可動ばね受け上の作用点は回転中心４６である。一方、蓄勢ばねは円筒形コイルばねであるので、可動ばね受けには円筒形コイルばねの中心軸上で蓄勢ばねのばね作用力が作用していると考えられる。そこで可動ばね受け上に蓄勢ばねが当接しているフレーム１の面に垂直にｘ軸を設け、蓄勢ばねが当接しているフレーム１の面に平行で４個の蓄勢ばねの並びの方向をｙ軸とし、回転中心４６を原点とするｘ−ｙ平面を考える。そして、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄの可動ばね受け上の作用点の座標をそれぞれ（Ｘ１,Ｙ１）、（Ｘ２,Ｙ２）、（Ｘ３,Ｙ３）、（Ｘ４,Ｙ４）とし、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄのばね作用力を蓄勢状態でＦａ、Ｆｂ、Ｆｃ、Ｆｄとする。
【００３４】
複数の蓄勢ばねの力の合力の作用点は、作用点の回りのばね作用力のモーメントが零になる点から求めることができる。この作用点の座標を（Ｘ０，Ｙ０）とすると、力のモーメントはΣ｛（Ｘｉ―Ｘ０）×Ｆｉ｝（ｉ＝ａ〜ｄ）＝０とΣ｛（Ｙｉ―Ｙ０）×Ｆｉ｝（ｉ＝ａ〜ｄ）＝０がともに満足する式から、Ｘ１、Ｘ２、Ｘ３、Ｘ４とＹ１、Ｙ２、Ｙ３、Ｙ４およびＦａ、Ｆｂ、Ｆｃ、Ｆｄを変量として求められる。この可動ばね受け４４の座標（Ｘ０，Ｙ０）が回転中心４６の座標（０、０）に合うと、蓄勢ばね力の合力の作用点とばねロッドの作用力の作用点が一致させることができるので、Σ（Ｘｉ×Ｆｉ）（ｉ＝ａ〜ｄ）＝０、Σ（Ｙｉ×Ｆｉ）（ｉ＝ａ〜ｄ）＝０からＸｉ、Ｙｉを求めた。
尚、この実施の形態１では力の作用点を力のモーメントの計算から求めることができたが、図形を用いて求めることもできる。
【００３５】
さらに蓄勢状態から放勢状態の間で作用点が変化しないように、蓄勢状態での可動ばね受けの当接面Ｓ１、Ｓ２、Ｓ３、Ｓ４とフレーム１の長さをＬ１、Ｌ２、Ｌ３、Ｌ４とし、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄの無荷重での長さをＲ１、Ｒ２、Ｒ３、Ｒ４との差が一定になるように蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄの長さを決めた。その結果、力のモーメントは放勢状態でも０となり、蓄勢ばね力の合力の作用点とばねロッドの作用力の作用点が一致したままで駆動する。
【００３６】
上述の可動ばね受け６２に加わる力は、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄのばね力Ｆａ、Ｆｂ、Ｆｃ、Ｆｄの合力と、ばねロッド４４の作用力であり、この実施の形態１では両方の力の作用点を一致させてあるので回転中心４６の周りでの可動ばね受け６２の回転は起こらず、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄが放勢するとき、可動ばね受け６２が傾くことがほとんどなくなり、案内装置４５と可動ばね受け６２との摩擦抵抗を小さく抑えられる。このように、本発明では、案内装置４５と可動ばね受け６２の摺動部にベアリング等を設けることなく、安定な速度を有した遮断器の投入機構として蓄勢ばね装置が得られる。
【００３７】
また蓄勢ばねの組み合わせ方を変化させて、蓄勢ばねのばね作用力の合力の作用点を可動ばね受けの周囲部にも配置することが可能になり、蓄勢ばね装置の設計の自由度が広がる。
【００３８】
なお、実施の形態３では、蓄勢ばね６１ａ、６１ｂ、６１ｃ、６１ｄと可動ばね受け６２等から構成する機構を投入ばね機構として用いていたが、同様な構成であれば、遮断ばね機構にも適用可能である。
【００３９】
実施の形態４．
図６は、この発明の実施の形態４による操作装置のばね機構部の断面図であり、蓄勢ばね６３ａおよび蓄勢ばね６３ｂが蓄勢されており、遮断器が開極状態となっている。形態１と形態４の主な相異点は、２個の蓄勢ばね６３ａおよび蓄勢ばね６３ｂが同心円で配置されていること、これらの蓄勢ばね６３ａ、６３ｂを、それぞれ可動ばね受け６４の当接面Ｓ１およびＳ２で受けていることである。
【００４０】
また、回転中心４６と、可動ばね受け６４の当接面Ｓ１およびＳ２の距離をそれぞれＸ１、Ｘ２とし、Ｘ１、Ｘ２の符号については、蓄勢ばね６３ａ及び蓄勢ばね６３ｂの中心軸上に座標軸を採用し、原点を回転中心４６とし、回転中心４６の左側に当接面Ｓ１もしくはＳ２がある場合負とする。また、蓄勢ばね６３ａおよび蓄勢ばね６３ｂの蓄勢時の荷重をそれぞれＦ１およびＦ２としている。そこで積Ｘ１・Ｆ１と積Ｘ２・Ｆ２の和が零近傍になるように値を設定してある。ここで和が零になるように設定しているが、蓄勢ばねの変位―荷重特性のずれや組立精度などから和が零近傍になることがあるが効果に大きな違いは見られない。
【００４１】
積Ｘ１・Ｆ１と積Ｘ２・Ｆ２の和が零近傍にあることの作用を説明する。蓄勢ばね６３ａと蓄勢ばね６３ｂは同心で配置されているので、蓄勢荷重は蓄勢ばねの中心軸上で作用している。さらに、可動ばね受け６４に発生するモ−メントＭは
Ｍ＝Ｆ１・Ｘ１・ｔａｎθ＋Ｆ２・Ｘ２・ｔａｎθ
となり、積Ｘ１・Ｆ１と積Ｘ２・Ｆ２の和が零近傍から力のモーメントは零近傍になる。すなわち、積Ｘ１・Ｆ１と積Ｘ２・Ｆ２の和が零近傍にあれば、可動ばね受け上の回転中心４６の回りのモーメントが零近傍になる作用がある。それゆえ、蓄勢ばね６３ａと蓄勢ばね６３ｂのばね力の合力の作用点は回転中心４６にあることになり、ばねロッドの作用力の作用点と一致する。
【００４２】
さらに蓄勢状態から放勢状態の間で作用点が変化しないように、蓄勢状態での可動ばね受けの当接面Ｓ１、Ｓ２とフレーム１の長さをＬ１、Ｌ２とし、蓄勢ばね６３ａ、６３ｂの無荷重での長さをＲ１、Ｒ２との差が一定になるように蓄勢ばね６３ａ、６３ｂの長さを決めた。その結果、力のモーメントは放勢状態でも０となり、蓄勢ばね力の合力の作用点とばねロッドの作用力の作用点が一致したままで駆動する。
【００４３】
したがって、可動ばね受け６４に発生するモ−メントはほぼ零になり、蓄勢ばね６３ａと蓄勢ばね６３ｂが放勢するとき、可動ばね受け６４が傾くことがほとんどなくなり、案内装置４５と可動ばね受け６４との貫通孔の摩擦抵抗を小さく抑えられる。このように、本発明では、案内装置４５と可動ばね受け６４の摺動部にベアリング等を設けることなく、安定な速度を有する遮断器の投入機構として蓄勢ばね装置が得られる。
また２個の蓄勢ばねのばね特性を色々組み合わせることで遮断器の投入操作に適した蓄勢ばね装置が得られる。
【００４４】
なお、実施の形態４においても、蓄勢ばね６３ａ、６３ｂおよび可動ばね受け６４等から構成する機構を投入ばね機構として用いていたが、同様な構成であれば、遮断ばね機構にも適用可能である。
【００４５】
実施の形態５．
図７は、この発明の実施の形態５による操作装置のばね機構部の断面図であり、蓄勢ばね６５ａ、６５ｂ、６５ｃが蓄勢されており、遮断器が開極状態となっている。実施の形態１と実施の形態５の主な相異点は、３個の蓄勢ばね６５ａ、６５ｂ、６５ｃが同心で配置されていること、これらの蓄勢ばねをそれぞれ、可動ばね受け６６の当接面Ｓ１、Ｓ２およびＳ３で受けていることである。
【００４６】
また、回転中心４６と、可動ばね受け６６の当接面Ｓ１、Ｓ２およびＳ３の距離をそれぞれＸ１、Ｘ２およびＸ３とし、Ｘ１、Ｘ２、Ｘ３の符号については、蓄勢ばね６５ａ、６５ｂ、６５ｃの中心軸上に座標軸を採用し、原点を回転中心４６とし、回転中心４６の左側に当接面Ｓ１、Ｓ２もしくはＳ３がある場合負とする。また、蓄勢ばね６５ａ、６５ｂ、６５ｃの蓄勢時の荷重をそれぞれＦ１、Ｆ２およびＦ３とする。そこで積Ｘ１・Ｆ１と積Ｘ２・Ｆ２と積Ｘ３・Ｆ３の和が零近傍になるように値を設定してある。ここで和が零になるように設定をするが、蓄勢ばねの変位―荷重特性のずれや組立精度などから和が零近傍になることがあるが効果に大きな違いは見られない。
【００４７】
積Ｘ１・Ｆ１と積Ｘ２・Ｆ２と積Ｘ３・Ｆ３の和が零近傍にあることの作用を説明する。蓄勢ばね６５ａ、６５ｂ、６５ｃは同心で配置されているので、蓄勢荷重は蓄勢ばねの中心軸上で作用している。さらに、可動ばね受け６６に発生するモ−メントＭは、
Ｍ＝Ｆ１・Ｘ１・ｔａｎθ＋Ｆ２・Ｘ２・ｔａｎθ＋Ｆ３・Ｘ３・ｔａｎθ
となり、積Ｘ１・Ｆ１と積Ｘ２・Ｆ２と積Ｘ３・Ｆ３の和が零近傍から力のモーメントは零近傍になる。すなわち、積Ｘ１・Ｆ１と積Ｘ２・Ｆ２と積Ｘ３・Ｆ３の和が零近傍にあれば、可動ばね受け６６上の回転中心４６の回りのモーメントが零近傍になる作用がある。それゆえ、蓄勢ばね６５ａ、６５ｂ、６５ｃのばね力の合力の作用点は回転中心４６にあることになり、ばねロッドの作用力の作用点と一致する。
【００４８】
さらに蓄勢状態から放勢状態の間で作用点が変化しないように、蓄勢状態での可動ばね受けの当接面Ｓ１、Ｓ２、Ｓ３とフレーム１の間隔をＬ１、Ｌ２、Ｌ３とし、蓄勢ばね６５ａ、６５ｂ、６５ｃの無荷重での長さをＲ１、Ｒ２、Ｒ３との差が一定になるように蓄勢ばね６５ａ、６５ｂ、６５ｃの長さを決めた。その結果、力のモーメントは放勢状態でも零近傍となり、蓄勢ばね力の合力の作用点とばねロッドの作用力の作用点が一致したままで駆動する。
【００４９】
したがって、可動ばね受け６６に発生するモ−メントはほぼ零になり、蓄勢ばね６５ａ、６５ｂ、６５ｃが放勢するとき、可動ばね受け６６の傾きが小さくなり、案内装置４５と可動ばね受け６６の貫通孔との摩擦抵抗を小さく抑えられる。このように、蓄勢ばね６５ａ、６５ｂ、６５ｃとして円筒形コイルばねを同心円状に配置し、回転中心４６の回りの力のモーメントを零にすることで、案内装置４５と可動ばね受け６６の摺動部にベアリング等を設けることなく、安定な速度を有する遮断器の投入機構として蓄勢ばね装置が得られる。
【００５０】
なお、実施の形態５においても、蓄勢ばね６５ａ、６５ｂ、６５ｃと、可動ばね受け６６等から構成する機構を投入ばね機構として用いていたが、同様な構成であれば、遮断ばね機構にも適用可能である。
【００５１】
さらに、ｎ個の蓄勢ばね６５ｉ（ｉ＝１〜ｎ）が同心に配置されているとき、可動ばね受け６６の当接面Ｓｉ（ｉ＝１〜ｎ）と回転中心４６との距離をそれぞれＸｉ（ｉ＝１〜ｎ）とし、蓄勢ばね６６ｉ（ｉ＝１〜ｎ）の荷重をそれぞれＦｉ（ｉ＝１〜ｎ）とする。そこで蓄勢ばね６５ｉ毎に、距離Ｘｉと荷重Ｆｉの積を計算し、次にそれらの積をすべて加えて和が求められる。このように求めた和が零になるように、Ｘｉ（ｉ＝１〜ｎ）、Ｆｉ（ｉ＝１〜ｎ）を設計すると、可動ばね受け６６に発生するモ−メントはほぼ零になる。
さらに蓄勢状態から放勢状態の間で作用点が変化しないように、蓄勢状態での可動ばね受けの当接面Ｓｉ（ｉ＝１〜ｎ）とフレーム１の間隔をＬｉ（ｉ＝１〜ｎ）とし、蓄勢ばね６５ｉ（ｉ＝１〜ｎ）の無荷重での長さをＲｉ（ｉ＝１〜ｎ）との差が一定になるように蓄勢ばね６５ｉ（ｉ＝１〜ｎ）の長さを決めた。その結果、力のモーメントは放勢状態でも０となり、蓄勢ばね力の合力の作用点とばねロッドの作用力の作用点が一致したままで駆動する。
【００５２】
そこで可動ばね受け６６の傾きが少ないので、案内装置４８と可動ばね受け６６の貫通孔との摩擦抵抗を小さく抑えられ、ベアリングなど特別な摺動部材を追加しなくても、安定な速度等の駆動特性を有する遮断器の投入機構として蓄勢ばね装置が得られる。
【００５３】
また複数の蓄勢ばねのばね特性を色々組み合わせることで遮断器の投入操作に適した蓄勢ばね装置が得られる。
上記のように複数の蓄勢ばねを同心円状に配置することにより、蓄勢ばね装置が小形化する効果がある。
【００５４】
【発明の効果】
以上の如くこの発明の蓄勢ばね装置による効果は次の通りである。
（１）蓄勢ばね装置は、フレームと、フレームに一端で支持された蓄勢ばねと、蓄勢ばねの他端に設けられ、蓄勢ばねのばね作用力を受ける可動ばね受けと、フレームに設けられたクランク軸と、一端でクランク軸に回転可能に連結され、他端で可動ばね受けに回転可能に連結され、クランク軸の回転に応じて可動ばね受けに作用力を加えて蓄勢ばねに蓄勢するばねロッドと、フレームに取り付けられて可動ばね受けが直線運動をするように案内する案内装置とを備え、蓄勢ばねのばね作用力の可動ばね受け上の作用点と、ばねロッドの作用力のばね受け上の作用点とが一致した位置に在るので、可動ばね受けが受ける蓄勢ばねのばね作用力とばねロッドの作用力のモーメントが零近傍になるので、可動ばね受けの傾きが少なくなり、可動ばね受けと案内装置の摩擦抵抗が減少することから、ベアリング等を用いなくても安定な速度を有した蓄勢ばね装置が得られる。
さらに複数の蓄勢ばねを組み合わせることで小形化、高蓄勢が可能になる。
さらに蓄勢ばねのばね力と作用点を組み合わせることで、ばねロッドの作用力の可動ばね受け上の自由な位置に作用点を設けることができる。
【００５５】
（２）蓄勢ばね装置は、フレームと、クランク軸と、一端でクランク軸に回転可能に連結されたばねロッドと、ばねロッドの他端に回転中心回りに回転可能に連結された可動ばね受けと、フレームに取り付けられて可動ばね受けが直線運動をするように案内する案内装置と、可動ばね受けおよびフレーム間に設けられ、中心軸を有する蓄勢ばねとを備え、回転中心が、蓄勢ばねの中心軸上に在り、かつ蓄勢ばねが当接する可動ばね受けの当接面内に在るので、ばねロッドが可動ばね受けから受ける力の方向が蓄勢ばねの中心軸からずれることによる可動ばね受けが受けるモ−メントが零近傍であるので、可動ばね受けが傾くことが少なくなるので可動ばね受けと案内装置の摩擦抵抗が減少することにより、ベアリング等を用いなくても安定な速度が得られる。
【００５６】
（２）蓄勢ばね装置は、フレームと、クランク軸と、一端でクランク軸に回転可能に連結されたばねロッドと、ばねロッドの他端に回転中心回りに回転可能に連結された可動ばね受けと、フレームに取り付けられて可動ばね受けが直線運動をするように案内する案内装置と、可動ばね受けおよびフレーム間に設けられ、中心軸を有する蓄勢ばねとを備え、回転中心が、蓄勢ばねの中心軸上に在り、かつ可動ばね受けの蓄勢ばねが当接する当接面内に在るので、ばねロッドが可動ばね受けから受ける力の方向が蓄勢ばねの中心軸からずれることによる可動ばね受けが受けるモ−メントが零近傍であるので、可動ばね受けが傾くことが少なくなるので可動ばね受けと案内装置の摩擦抵抗が減少することにより、ベアリング等を用いなくても安定な速度が得られる。
【００５７】
（４）ばねロッドが蓄勢ばねを貫通することなく配置され、フレ−ムに固定された案内装置が蓄勢ばねの軸方向に可動ばね受けを貫通しているので、蓄勢ばねを空間的に最大限使用することが出来て、小形化、高蓄勢が可能になる。
さらに可動ばね受けが蓄勢ばねの軸方向に垂直の姿勢に配置出来て、蓄勢ばねが軸方向に安定して運動出来る。
【図面の簡単な説明】
【図１】この発明の形態１の蓄勢状態の蓄勢ばね装置の要部断面図である。
【図２】この発明の形態１の放勢途中の蓄勢ばね装置の要部断面図である。
【図３】この発明の形態１の放勢状態の蓄勢ばね装置の要部断面図である。
【図４】この発明の形態２の蓄勢状態の蓄勢ばね装置の要部断面図である。
【図５】この発明の形態３の蓄勢状態の蓄勢ばね装置の要部断面図である。
【図６】この発明の形態４の蓄勢状態の蓄勢ばね装置の要部断面図である。
【図７】この発明の形態５の蓄勢状態の蓄勢ばね装置の要部断面図である。
【図８】従来の技術の蓄勢ばね装置の要部断面図である。
【図９】従来の技術の蓄勢ばね装置の投入機構部分の要部断面図である。
【符号の説明】
１フレ−ム、４１クランク軸、４２、６１ａ、６１ｂ、６１ｃ、６１ｄ、６３ａ、６３ｂ、６５ａ、６５ｂ、６５ｃ蓄勢ばね、４３、６２、６４、６６可動ばね受け、４４ばねロッド、４７回転軸、４９クランクアーム、５０ピン、５１固定ばね受け。[0001]
BACKGROUND OF THE INVENTION
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an energy storage spring device, and more particularly to an energy storage spring device provided with an energy storage spring that stores and releases energy via a spring rod by rotation of a crankshaft rotatably supported by a frame. .
[0002]
[Prior art]
FIG. 8 is a cross-sectional view of the main part of the accumulator spring device used for the circuit breaker closing mechanism in the power switchgear installed in the substation and switchgear disclosed in Japanese Utility Model Publication No. 63-42433. The accumulator spring device includes a frame 1, a crankshaft 4 provided with a rotating shaft 2 rotatably attached to the frame 1 and a crankarm 3 fixed to the rotating shaft 2, and a pin 5 attached to the crankarm 3 at one end. A spring rod 6 that is rotatably connected using the movable rod 8, a movable spring receiver 8 that is rotatably connected to the other end of the spring rod 6 via the spherical seat 7, and a movable spring receiver 8 that is in contact with the frame 1 and compressed. And an accumulator spring 9 comprising a coil spring. Further, when the accumulator spring 9 is accumulated, the accumulator spring 9 is likely to bend and bend, and there is a risk of buckling. Therefore, a cylindrical guide device that is fixed to the frame 1 and guides the accumulator spring 9. 10 is provided.
[0003]
FIG. 9 is a cross-sectional view of the main part of the operating device for the blocking unit operating lever 11. This figure shows the circuit breaker in the open state, and the energy storage spring 9 indicates the energy storage state. The operating device for the blocking unit operating lever 11 includes a blocking unit operating lever 11 rotatably supported by a pin 12 supported by the frame 1 and a pin 13 in a groove 13 formed in the blocking unit operating lever 11. A roller 15 pivotally supported by the shaft, a pin 16 pivotally supported by the shut-off portion operating lever 11, a chisel 18 rotatably supported by the pin 17 on the frame 1, and a pin 19 rotatable by the pin 19 A supported trigger 20 and a plunger 22 that moves to the right in FIG. A return spring 23 and a return spring 24 are stored between the crack 18 and the frame 1 and between the trigger 20 and the frame 1, respectively. A cam 25 is fixedly attached to the rotary shaft 2.
[0004]
The pin 26 supported by the blocking unit operating lever 11 is connected to a blocking unit (not shown) and receives a force in the direction of arrow A by a tripping spring (not shown). The shut-off portion operation lever 11 is in a state where it is disengaged from the clasp 18 and rotated counterclockwise and stopped. The crack 18 and the trigger 20 are in a state where the plunger 22 has moved in the right direction shown in FIG. 9 and the trigger 20 has been rotated clockwise to disengage.
[0005]
The closing operation of the circuit breaker will be described with reference to FIGS. Engagement with a pin (not shown) engaged with the crankshaft 4 is disengaged, and the crankshaft 4 is rotated counterclockwise in the figure by the force of the accumulator spring 9, and the cam 25 is rotated along with the rotation of the crankshaft 4. Rotates counterclockwise. As the cam 25 rotates, the roller 15 rolls along the outer peripheral surface of the cam 25, and the blocking unit operating lever 11 rotates around the pin 12 in the clockwise direction. The tripping spring (not shown) connected to the pin 26 is accumulated by the rotation of the shut-off unit operating lever 11. The shut-off unit operating lever 11 is rotated clockwise, the pin 16 is engaged with the crack 18 and the crack 18 is engaged with the trigger 20 by the return springs 23 and 24, respectively, and the cam 25 is further rotated and does not contact the roller 15. , The blocking portion operating lever 11 is prevented from rotating counterclockwise by the pulling force in the direction of arrow A, and the closed state is maintained.
[0006]
[Problems to be solved by the invention]
Since the conventional accumulator spring device is configured as described above, it has the following problems.
As shown in FIG. 8, since the spring rod 6 and the movable spring receiver 8 are connected by the spherical seat 7, the acting force of the spring rod 6 driven by the crankshaft 4 is always on the central axis of the spring rod 6. It is in. Further, when the crankshaft 4 rotates, the angle θ of the spring rod 6 with respect to the central axis 9 a of the accumulator spring 9 changes, and the change in the angle θ is a change around the rotation center 28 of the spherical seat 7. Accordingly, the point of action of the acting force of the spring rod 6 on the spring receiver 8 is the rotation center 28 of the spherical seat 7.
[0007]
On the other hand, the acting force of the accumulating spring 9 is on the central axis 9a in the case of the illustrated coil spring, and acts on the abutting surface 29 which is the spring receiving surface with respect to the movable spring receiver 8. The spring acting force of the urging spring 9 acts at an action point G on the movable spring receiver 8.
[0008]
These two action points 28 and G are separated by a distance X in the direction of the central axis 9a of the energy storage spring 9 (sometimes simply referred to as the axial direction). Accordingly, when the axial center of the spring rod 6 and the central axis 9a of the accumulator spring 9 coincide with each other, the action lines of the respective forces also coincide, so that the movable spring receiver 8 is rotated. No rotating moment is generated.
[0009]
When the crankshaft 4 rotates, the spring rod 6 is inclined by an angle θ with respect to the central axis 9 a of the energy storage spring 9, and the action line of the acting force of the spring rod 6 and the operation of the energy storage spring 9 are caused by this angle θ. A deviation occurs between the force acting line and a force to rotate the movable spring receiver 8 is generated. In this rotational moment, when the stored load of the stored spring 9 is F and the displacement of the spring rod 6 is an angle θ, the axial distance between the two operating points 28 and G is X. Therefore, a rotation moment of F, X, and tan θ is generated to try to rotate the movable spring receiver 8 about the action point 28 in the clockwise direction. Due to this moment, the movable spring receiver 8 rotates clockwise in FIG. 8 to a position where the rotational moment disappears due to a change in the acting force due to the deformation of the energy storage spring 9.
[0010]
When such rotation of the movable spring receiver 8 occurs, the space between the cylindrical or rod-shaped guide device 10 and the guided surface of the movable spring receiver 8 is not parallel, and the friction therebetween increases, and the bite There is a drawback that the operation of the accumulator spring device is not performed smoothly. In order to reduce such friction, a bearing or the like is provided on the sliding portion of the guide device 27 and the movable spring receiver 8, or a complicated link mechanism is added to convert the linear motion into a linear motion and then connected to the movable spring receiver. Have also been proposed, but there are problems such as the need for new parts and an increase in volume.
[0011]
Accordingly, an object of the present invention is to eliminate the problems of the conventional accumulator spring device as described above, and without adding parts such as a bearing and a link mechanism, a stable structure such as a stable speed can be obtained. It is to obtain an accumulator spring device that can ensure driving performance.
[0012]
[Means for Solving the Problems]
According to the present invention, means for solving the above-described problems are as follows.
(1) The energy storage spring device includes a frame, an energy storage spring supported at one end of the frame, a movable spring receiver provided at the other end of the energy storage spring and receiving the spring acting force of the energy storage spring, One end of the crankshaft is rotatably connected to the crankshaft, the other end is rotatably connected to a movable spring receiver, and an actuating force is applied to the movable spring receiver in response to the rotation of the crankshaft to store energy. A spring rod that stores energy in the spring; a guide device that is attached to the frame and guides the movable spring receiver so as to perform linear motion; The operating point on the spring receiver of the acting force of the rod is in a position where it coincides.
[0013]
(2) Further, the energy storage spring device includes a frame, a crankshaft, a spring rod that is rotatably connected to the crankshaft at one end, and a movable spring that is rotatably connected to the other end of the spring rod around a rotation center. A receiving device, a guide device attached to the frame and guiding the movable spring receiver so as to make a linear motion, and an accumulating spring provided between the movable spring receiver and the frame and having a central axis. On the central axis of the spring and The accumulator spring contacts It may be in the contact surface.
[0014]
(3) Furthermore, the accumulator spring device includes a frame, a crankshaft, a spring rod that is rotatably connected to the crankshaft at one end, and a movable spring that is rotatably connected to the other end of the spring rod around the rotation center. A receiving device, a guide device that is attached to the frame and guides the movable spring receiver so as to move linearly, and an accumulator spring that is provided between the movable spring receiver and the frame and has a central axis, A plurality of coil springs arranged on the same axis and having different contact surfaces, the rotation center being on the central axis of the energy storage spring, and viewed from the rotation center in the axial direction of the energy storage spring You may exist in the position where the sum of the product of the distance to each contact surface and the stored load of each stored spring becomes near zero.
[0015]
(4) The spring rod is arranged without penetrating the accumulator spring, and the guide device fixed to the frame penetrates the movable spring receiver in the axial direction of the accumulator spring.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Embodiment 1 FIG.
1 is a cross-sectional view of an energy storage spring device in which an energy storage spring according to Embodiment 1 of the present invention is in an energy storage state, and is an energy storage spring mechanism corresponding to FIG. 8 of a conventional example.
The accumulator spring device includes a frame 1, a crankshaft 41 that is rotatably supported by the frame 1, and one accumulator spring that is vertically abutted on one end of the frame 1 and has a central axis. 42 and a movable spring receiver 43 that is provided at the other end of the energy storage spring 42 and receives the spring acting force of the energy storage spring 42. The movable spring receiver 43 is disk-shaped and receives the accumulator spring 42 with a circumferential contact surface S.
[0017]
The accumulator spring device is also rotatably connected to the crankshaft 41 at one end and rotatably connected to the movable spring receiver 43 at the other end, and applies an acting force to the movable spring receiver 43 as the crankshaft 41 rotates. And a guide rod 45 attached to the frame 1 for guiding the movable spring receiver 43 to move linearly.
[0018]
Further, the movable spring receiver 43 is provided with a prismatic projection at the center, and a hole is formed in the side surface of the prism. Also, a tuning fork-shaped bearing is provided at one end of the spring rod, and a hole is formed in the tuning fork portion. The hole of the prismatic protrusion of the movable spring receiver 43 and the hole of the tuning fork bearing of the spring rod are aligned, and a pin is inserted to provide a rotation center 46. The rotation center 46 is disposed on the contact surface S and the central axis of the energy storage spring 42.
[0019]
The crankshaft 41 includes a rotating shaft 47 and a crank 48. The rotating shaft 47 is supported by the frame 1 so as to freely rotate and rotates around the center of the shaft. The crank 48 protrudes from the rotating shaft 47. And the crankpin 50 is rotated around the center of the rotary shaft 47.
In the state of FIG. 1, the axial direction of the spring rod 44 is inclined by the angle θ <b> 1 with respect to the central axis of the energy storage spring 42.
[0020]
Next, the closing operation will be described. In FIG. 1, the energy storage spring 42 is stored, and the circuit breaker is in an open state. That is, the movable spring receiver 43 is urged in the A direction by the stored load of the stored spring 42, and this spring acting force is transmitted to the crank arm 49 via the spring rod 44, and the crankshaft 41 rotates around the rotation shaft 47. Counterclockwise torque is generated. The crankshaft 41 is held against this torque without being rotated by a holding mechanism including a hoisting wheel other than that shown in the drawing, a pin other than that shown in FIG. When the closing command is issued, the holding mechanism of the crankshaft 41 is released, and the crank arm 49 and the crankshaft 41 start to rotate counterclockwise by the stored load of the stored spring 42, and the movable spring receiver 43 is moved to A. Start moving in the direction.
[0021]
FIG. 2 shows a state during the closing operation. Since the pin 50 of the crank arm 49 draws a circular arc locus centering on the rotation shaft 47, the angle formed by the axial direction of the spring rod 44 and the central axis of the energy storage spring 42 changes to θ2.
[0022]
FIG. 3 shows a state at the end of the closing operation. The crank arm 49 rotates counterclockwise around the rotation shaft 47, and the movable spring receiver 43 moves to the left side in the figure, so that the accumulator spring 42 is in a released state. At this time, the angle formed by the axial direction of the spring rod 44 and the central axis of the energy storage spring 42 changes to θ3.
[0023]
The accumulating operation of the accumulating spring 42 will be described. From the state of FIG. 3, a hoisting wheel (not shown) fixed to the crankshaft 41 is rotated by a power source (not shown), and the crank arm 49 is rotated around the rotating shaft 47 in the clockwise direction. At the same time, the movable spring receiver 43 starts moving in the direction B of FIG. When the state of FIG. 3 is changed to the state of FIG. 2 and the accumulation of the accumulation spring 42 is completed as shown in FIG. 1, the holding mechanism (not shown) prevents the crankshaft 41 from rotating counterclockwise. The energy storage operation is terminated.
[0024]
The position of the rotation center 46 according to the first embodiment of the present invention is arranged at the intersection of the central axis of the energy storage spring 42 and the energy storage spring contact surface S of the movable spring receiver 43, and the spring force of the energy storage spring 42. Is on the central axis of the coil spring and on the contact surface S, and therefore coincides with the point of action of the acting force of the spring rod 44 at the rotation center 46. Therefore, the moment of the force acting on the movable spring receiver 43 becomes almost zero, and when the accumulator spring 42 is released, the movable spring receiver 43 hardly tilts, and the guide device 45 and the movable spring receiver 43 The frictional resistance with the through hole can be kept small. Thus, in the present invention, without providing a bearing or the like on the sliding portion between the guide device 45 and the movable spring receiver 43, the contact between the central axis of the cylindrical coil spring and the contact surface of the movable spring receiver of the accumulator spring is provided. By providing the center of rotation 46 at the intersection, an accumulator spring device can be obtained as a closing mechanism for a circuit breaker having driving characteristics such as a stable speed.
[0025]
In the first embodiment, the mechanism constituted by the accumulator spring 43 and the movable spring receiver 43 is used as the closing spring mechanism. However, the same structure can be applied to the cutoff spring mechanism.
[0026]
In the first embodiment, a rotatable pin connection is used as the center of rotation, but the same rotatable connection is possible with a spherical seat and a ball receiver.
[0027]
Embodiment 2. FIG.
FIG. 4 is a cross-sectional view of the spring mechanism portion of the energy storage spring device according to Embodiment 2 of the present invention, in which the energy storage spring 42 is stored and the circuit breaker is in the open state.
Components such as the frame 1, the crank arm 49, the crankshaft 41, the rotation center 46, the pin 50, the spring rod 44, the energy storage spring 42, and the guide device 45 are substantially the same as those in the first embodiment.
[0028]
However, the fixed spring receiver 51 is fixed to the left end of the guide device 45, and the accumulator spring 42 is compressed between the fixed spring receiver 51 and the movable spring receiver 43. Therefore, when a closing command is issued and the accumulator spring 42 starts releasing, the movable spring receiver 43 is pushed in the C direction, the spring rod 44 moves in the C direction, and the crankshaft 41 rotates around the rotation shaft 47. Rotate clockwise. Further, during the accumulating operation of the accumulating spring 42, the crank arm 49 is rotated counterclockwise around the rotation shaft 47 by a power source (not shown), and the movable spring receiver 42 is moved in the direction opposite to the C direction. The energy storage spring 42 is stored by moving. Thus, the rotation direction of the crank arm 49 and the moving direction of the movable spring receiver 43 during the closing operation of the circuit breaker or the storing operation of the storing spring 42 are opposite to those in the first embodiment.
[0029]
The rotation center 46 is located at the intersection of the central axis of the accumulator spring 42 and the accumulator spring contact surface S of the movable spring receiver 43 as indicated by the one-dot chain line in the figure. Since the point of action of the spring force is on the central axis of the coil spring and on the contact surface S, it coincides with the point of action of the acting force of the spring rod 44 at the center of rotation. Therefore, the moment generated in the movable spring receiver 43 becomes almost zero, and when the accumulator spring 42 is released, the movable spring receiver 43 hardly tilts, and the guide device 45 and the through hole of the movable spring receiver 43 And the frictional resistance can be kept small. Thus, in the present invention, without providing a bearing or the like on the sliding portion between the guide device 45 and the movable spring receiver 43, the contact between the central axis of the cylindrical coil spring and the contact surface of the movable spring receiver of the accumulator spring is provided. By providing the center of rotation at the intersection point, the accumulator spring device can be obtained as a closing mechanism for a circuit breaker having a stable speed.
[0030]
In addition, since the spring rod 44 does not penetrate the accumulator spring 42, a rectangular coil spring having an elongated cross-sectional shape can be used so that the entire surface of the movable spring receiver 43 is a contact surface of the accumulator spring 42. Miniaturization is possible, and a highly accumulating spring device is obtained.
Furthermore, the movable spring receiver 43 can be disposed in a posture perpendicular to the axial direction of the energy storage spring 42, and the energy storage spring can move stably in the axial direction.
[0031]
In the second embodiment, the mechanism constituted by the accumulator spring 42 and the movable spring receiver 43 is used as the closing spring mechanism. However, the same structure can be applied to the cutoff spring mechanism.
[0032]
Embodiment 3 FIG.
FIG. 5 is a cross-sectional view of the energy storage spring device in the energy storage state of the energy storage spring according to the third embodiment of the present invention. The difference from the first embodiment is that a plurality of energy storage springs are used. That is, the accumulator springs 61a, 61b, 61c, 61d composed of four cylindrical coil springs that are vertically abutted on one end and supported on a straight line, and the accumulator springs 61a, 61b, 61c, 61d. A movable spring receiver 62 is provided at the end and receives the spring acting force of the accumulator springs 61a, 61b, 61c, 61d.
[0033]
Here, a method of matching the action point of the resultant force of the energy storage spring and the action point of the action force of the spring rod will be described. The point of action of the acting force of the spring rod on the movable spring receiver is the rotation center 46. On the other hand, since the energy storing spring is a cylindrical coil spring, it is considered that the spring acting force of the energy storing spring acts on the movable spring receiver on the central axis of the cylindrical coil spring. Therefore, an x-axis is provided perpendicularly to the surface of the frame 1 on which the energy storage spring is in contact with the movable spring receiver, and the four energy storage springs are arranged in parallel to the surface of the frame 1 on which the energy storage spring is in contact. Consider an xy plane whose direction is the y-axis and whose rotation center 46 is the origin. Then, the coordinates of the action points on the movable spring receivers of the accumulator springs 61a, 61b, 61c, 61d are respectively (X1, Y1), (X2, Y2), (X3, Y3), (X4, Y4) and stored. The spring acting forces of the force springs 61a, 61b, 61c, and 61d are set to Fa, Fb, Fc, and Fd in the stored state.
[0034]
The action point of the resultant force of the plurality of energy storage springs can be obtained from the point where the moment of the spring action force around the action point becomes zero. When the coordinates of the action point are (X0, Y0), the moment of force is Σ {(Xi−X0) × Fi} (i = a to d) = 0 and Σ {(Yi−Y0) × Fi} (i = A to d) = 0, X1, X2, X3, X4 and Y1, Y2, Y3, Y4 and Fa, Fb, Fc, Fd are obtained as variables. When the coordinate (X0, Y0) of the movable spring receiver 44 matches the coordinate (0, 0) of the rotation center 46, the action point of the resultant force of the stored spring force and the action point of the action force of the spring rod may coincide. Therefore, Xi and Yi were obtained from Σ (Xi × Fi) (i = a to d) = 0 and Σ (Yi × Fi) (i = a to d) = 0.
In the first embodiment, the point of action of the force can be obtained from the calculation of the moment of force, but it can also be obtained using a figure.
[0035]
Further, the lengths of the contact surfaces S1, S2, S3, S4 of the movable spring receiver and the frame 1 in the stored state are set to L1, L2, L3 so that the operating point does not change between the stored state and the released state. , L4, and the lengths of the energy storage springs 61a, 61b, 61c, 61d so that the lengths of the energy storage springs 61a, 61b, 61c, 61d with no load are constant from R1, R2, R3, R4. I decided. As a result, the moment of force becomes zero even in the released state, and the driving is performed while the point of action of the resultant force of the stored spring force and the point of action of the acting force of the spring rod coincide.
[0036]
The force applied to the movable spring receiver 62 described above is the resultant force of the spring forces Fa, Fb, Fc, Fd of the accumulator springs 61a, 61b, 61c, 61d and the acting force of the spring rod 44. Since the action points of both forces are made coincident, the movable spring receiver 62 does not rotate around the rotation center 46, and when the accumulator springs 61a, 61b, 61c, 61d are released, the movable spring receiver 62 Inclination hardly occurs, and the frictional resistance between the guide device 45 and the movable spring receiver 62 can be kept small. As described above, in the present invention, the accumulator spring device can be obtained as a circuit breaker closing mechanism having a stable speed without providing a bearing or the like in the sliding portion of the guide device 45 and the movable spring receiver 62.
[0037]
In addition, by changing the combination of the energy storage springs, it is possible to place the action point of the resultant spring acting force of the energy storage spring also on the periphery of the movable spring receiver. Spread.
[0038]
In the third embodiment, the mechanism composed of the accumulator springs 61a, 61b, 61c, 61d and the movable spring receiver 62 is used as the closing spring mechanism. Applicable.
[0039]
Embodiment 4 FIG.
FIG. 6 is a cross-sectional view of the spring mechanism portion of the operating device according to Embodiment 4 of the present invention, in which the accumulating spring 63a and the accumulating spring 63b are energized and the circuit breaker is in an open state. . The main difference between Embodiment 1 and Embodiment 4 is that the two energy storage springs 63a and 63b are concentrically arranged, and these energy storage springs 63a and 63b are respectively connected to the movable spring receiver 64. It is received by the contact surfaces S1 and S2.
[0040]
The distances between the rotation center 46 and the contact surfaces S1 and S2 of the movable spring receiver 64 are X1 and X2, respectively, and the signs of X1 and X2 are coordinate axes on the central axes of the energy storage spring 63a and the energy storage spring 63b. And the origin is the rotation center 46, and the contact surface S1 or S2 on the left side of the rotation center 46 is negative. Further, the loads at the time of energy storage of the energy storage spring 63a and the energy storage spring 63b are F1 and F2, respectively. Therefore, the value is set so that the sum of the product X1 · F1 and the product X2 · F2 is close to zero. Here, the sum is set to be zero, but the sum may be close to zero due to the displacement of the accumulator spring-deviation in load characteristics, assembly accuracy, etc., but there is no significant difference in the effect.
[0041]
The operation of the sum of the product X1 · F1 and the product X2 · F2 being near zero will be described. Since the energy storage spring 63a and the energy storage spring 63b are arranged concentrically, the energy storage load acts on the central axis of the energy storage spring. Furthermore, the moment M generated in the movable spring receiver 64 is
M = F1 · X1 · tan θ + F2 · X2 · tan θ
Thus, the sum of the product X1 · F1 and the product X2 · F2 is near zero, and the moment of force is near zero. That is, if the sum of the product X1 · F1 and the product X2 · F2 is near zero, there is an effect that the moment around the rotation center 46 on the movable spring receiver becomes near zero. Therefore, the action point of the resultant force of the energy storage spring 63a and the energy storage spring 63b is at the rotation center 46, and coincides with the action point of the action force of the spring rod.
[0042]
Further, the lengths of the contact surfaces S1 and S2 of the movable spring receiver and the frame 1 in the stored state are set to L1 and L2 so that the operating point does not change between the stored state and the released state, and the stored spring 63a. The lengths of the energy storage springs 63a and 63b are determined so that the difference between R1 and R2 is constant. As a result, the moment of force becomes zero even in the released state, and the driving is performed while the point of action of the resultant force of the stored spring force and the point of action of the acting force of the spring rod coincide.
[0043]
Therefore, the moment generated in the movable spring receiver 64 becomes almost zero, and when the accumulating spring 63a and the accumulating spring 63b are released, the movable spring receiver 64 hardly tilts, and the guide device 45 and the movable spring The frictional resistance of the through hole with the receiver 64 can be kept small. As described above, in the present invention, an accumulator spring device can be obtained as a circuit breaker closing mechanism having a stable speed without providing a bearing or the like in the sliding portion between the guide device 45 and the movable spring receiver 64.
Further, by combining various spring characteristics of the two energy storage springs, an energy storage spring device suitable for the operation of closing the circuit breaker can be obtained.
[0044]
In the fourth embodiment, the mechanism composed of the accumulator springs 63a and 63b and the movable spring receiver 64 is used as the closing spring mechanism. However, the same structure can be applied to the cutoff spring mechanism. is there.
[0045]
Embodiment 5 FIG.
FIG. 7 is a cross-sectional view of the spring mechanism portion of the operating device according to the fifth embodiment of the present invention, in which the accumulating springs 65a, 65b, 65c are accumulating and the circuit breaker is in the open state. The main difference between the first embodiment and the fifth embodiment is that the three energy storage springs 65a, 65b, 65c are arranged concentrically, and these energy storage springs are respectively connected to the movable spring receiver 66. It is received by the contact surfaces S1, S2 and S3.
[0046]
Further, the distances between the rotation center 46 and the contact surfaces S1, S2 and S3 of the movable spring receiver 66 are X1, X2 and X3, respectively, and the signs of X1, X2 and X3 are those of the accumulating springs 65a, 65b and 65c. A coordinate axis is adopted on the central axis, the origin is the rotation center 46, and the contact surface S1, S2 or S3 is negative on the left side of the rotation center 46. Further, the loads at the time of accumulating the accumulating springs 65a, 65b, and 65c are F1, F2, and F3, respectively. Therefore, the values are set so that the sum of the products X1, F1, X2, F2, and X3, F3 is close to zero. Here, the sum is set to be zero, but the sum may be close to zero due to the displacement of the accumulator spring-shift in load characteristics, assembly accuracy, etc., but there is no significant difference in the effect.
[0047]
The operation of the sum of the product X1, F1, the product X2, F2, and the product X3, F3 being near zero will be described. Since the energy storage springs 65a, 65b, and 65c are arranged concentrically, the energy storage load acts on the central axis of the energy storage spring. Furthermore, the moment M generated in the movable spring receiver 66 is:
M = F1, X1, tan θ + F2, X2, tan θ + F3, X3, tan θ
Thus, the sum of the products X1, F1, X2, F2, and X3, F3 is near zero, and the moment of force is near zero. In other words, if the sum of the products X1, F1, X2, F2, and X3, F3 is near zero, there is an effect that the moment around the rotation center 46 on the movable spring receiver 66 becomes near zero. Therefore, the action point of the resultant force of the springs 65a, 65b, 65c is at the rotation center 46, and coincides with the action point of the action force of the spring rod.
[0048]
Further, the distance between the contact surfaces S1, S2, S3 of the movable spring receiver and the frame 1 in the stored state is set to L1, L2, L3 so that the operating point does not change between the stored state and the released state. The lengths of the energy storage springs 65a, 65b, and 65c are determined so that the lengths of the force springs 65a, 65b, and 65c with no load are constant from R1, R2, and R3. As a result, the moment of force becomes near zero even in the released state, and driving is performed with the action point of the resultant force of the stored spring force and the action point of the action force of the spring rod being matched.
[0049]
Therefore, the moment generated in the movable spring receiver 66 becomes almost zero, and when the accumulator springs 65a, 65b, 65c are released, the inclination of the movable spring receiver 66 becomes small, and the guide device 45 and the movable spring receiver 66 are reduced. The frictional resistance with the through hole can be kept small. As described above, cylindrical coil springs are concentrically arranged as the accumulator springs 65a, 65b, 65c, and the moment of the force around the rotation center 46 is made zero, so that the sliding between the guide device 45 and the movable spring receiver 66 is reduced. An accumulator spring device can be obtained as a closing mechanism for a circuit breaker having a stable speed without providing a bearing or the like in the moving part.
[0050]
In the fifth embodiment, the mechanism composed of the accumulator springs 65a, 65b, 65c and the movable spring receiver 66 is used as the closing spring mechanism. Applicable.
[0051]
Further, when n energy storage springs 65i (i = 1 to n) are arranged concentrically, the distance between the contact surface Si (i = 1 to n) of the movable spring receiver 66 and the rotation center 46 is set respectively. Xi (i = 1 to n), and the load of the energy storage spring 66i (i = 1 to n) is Fi (i = 1 to n), respectively. Therefore, for each energy storage spring 65i, the product of the distance Xi and the load Fi is calculated, and then all these products are added to obtain the sum. If Xi (i = 1 to n) and Fi (i = 1 to n) are designed so that the sum obtained in this way becomes zero, the moment generated in the movable spring receiver 66 becomes almost zero.
Further, the distance between the contact surface Si (i = 1 to n) of the movable spring receiver and the frame 1 in the stored state is set to Li (i = 1) so that the operating point does not change between the stored state and the released state. ˜n), and the length of the energy storage spring 65i (i = 1 to n) with no load is constant so that the difference from Ri (i = 1 to n) is constant. The length of n) was decided. As a result, the moment of force becomes zero even in the released state, and the driving is performed while the point of action of the resultant force of the stored spring force and the point of action of the acting force of the spring rod coincide.
[0052]
Therefore, since the inclination of the movable spring receiver 66 is small, the frictional resistance between the guide device 48 and the through hole of the movable spring receiver 66 can be kept small, and a stable speed or the like can be achieved without adding a special sliding member such as a bearing. An accumulator spring device is obtained as a closing mechanism for a circuit breaker having driving characteristics.
[0053]
Further, by combining various spring characteristics of the plurality of energy storage springs, an energy storage spring device suitable for the operation of closing the circuit breaker can be obtained.
By arranging a plurality of energy storage springs concentrically as described above, there is an effect that the energy storage spring device is reduced in size.
[0054]
【The invention's effect】
As described above, the effects of the energy storage spring device of the present invention are as follows.
(1) The energy storage spring device includes a frame, an energy storage spring supported at one end of the frame, a movable spring receiver provided at the other end of the energy storage spring and receiving the spring acting force of the energy storage spring, A crankshaft provided at one end thereof is rotatably connected to the crankshaft, and at the other end is rotatably connected to a movable spring receiver. An accumulator spring is applied by applying an acting force to the movable spring receiver according to the rotation of the crankshaft. And a guide device attached to the frame for guiding the movable spring receiver so that the movable spring receiver moves linearly, an action point of the spring acting force of the energy storage spring on the movable spring receiver, and a spring rod Therefore, the moment of the spring acting force of the accumulator spring and the acting force of the spring rod received by the movable spring receiver is near zero. If the inclination of the Received from the frictional resistance of the guide device is reduced and, energizing spring device also having a stable speed without using a bearing and the like is obtained.
Further, by combining a plurality of energy storage springs, it becomes possible to reduce the size and increase the energy storage.
Further, by combining the spring force of the accumulator spring and the action point, the action point can be provided at a free position on the movable spring receiver of the action force of the spring rod.
[0055]
(2) The accumulator spring device includes a frame, a crankshaft, a spring rod that is rotatably connected to the crankshaft at one end, and a movable spring receiver that is rotatably connected to the other end of the spring rod around the center of rotation. A guide device that is attached to the frame and guides the movable spring receiver so as to perform a linear motion; and an accumulator spring that is provided between the movable spring receiver and the frame and has a central axis, and the center of rotation is the accumulator spring. Since it is on the contact surface of the movable spring receiver with which the accumulator spring abuts, the direction of the force that the spring rod receives from the movable spring receiver deviates from the central axis of the accumulator spring. Since the moment received by the spring receiver is close to zero, the movable spring receiver is less likely to tilt, and the frictional resistance between the movable spring receiver and the guide device is reduced. Degree is obtained.
[0056]
(2) The accumulator spring device includes a frame, a crankshaft, a spring rod that is rotatably connected to the crankshaft at one end, and a movable spring receiver that is rotatably connected to the other end of the spring rod around the center of rotation. A guide device that is attached to the frame and guides the movable spring receiver so as to perform a linear motion; and an accumulator spring that is provided between the movable spring receiver and the frame and has a central axis, and the center of rotation is the accumulator spring. On the center axis of the The accumulator spring contacts Since the moment of the force received by the spring rod from the central axis of the accumulator spring is near zero because the spring rod is in the contact surface, the movable spring receiver is Since the tilting is reduced, the frictional resistance between the movable spring receiver and the guide device is reduced, so that a stable speed can be obtained without using a bearing or the like.
[0057]
(4) Since the spring rod is disposed without penetrating the accumulator spring and the guide device fixed to the frame penetrates the movable spring receiver in the axial direction of the accumulator spring, the accumulator spring is spatially Can be used as much as possible, miniaturization and high energy storage.
Furthermore, the movable spring receiver can be arranged in a posture perpendicular to the axial direction of the energy storage spring, and the energy storage spring can move stably in the axial direction.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a main part of an energy storage spring device in an energy storage state according to a first embodiment of the present invention.
FIG. 2 is a cross-sectional view of an essential part of the accumulator spring device in the midst of release of Embodiment 1 of the present invention.
FIG. 3 is a cross-sectional view of an essential part of the energy storage spring device in a released state according to the first embodiment of the present invention.
FIG. 4 is a cross-sectional view of a main part of an energy storage spring device in an energy storage state according to a second embodiment of the present invention.
FIG. 5 is a cross-sectional view of a main part of an energy storage spring device in an energy storage state according to a third embodiment of the present invention.
FIG. 6 is a cross-sectional view of a main part of an energy storage spring device in an energy storage state according to a fourth embodiment of the present invention.
FIG. 7 is a cross-sectional view of a main part of an energy storage spring device in an energy storage state according to a fifth embodiment of the present invention.
FIG. 8 is a cross-sectional view of a main part of a conventional accumulator spring device.
FIG. 9 is a cross-sectional view of a main part of a closing mechanism portion of a conventional accumulator spring device.
[Explanation of symbols]
1 frame, 41 crankshaft, 42, 61a, 61b, 61c, 61d, 63a, 63b, 65a, 65b, 65c accumulating spring, 43, 62, 64, 66 movable spring receiver, 44 spring rod, 47 rotating shaft , 49 Crank arm, 50 pins, 51 Fixed spring holder.

Claims

A frame, an energy storage spring supported at one end of the frame, a movable spring receiver provided at the other end of the energy storage spring and receiving the spring acting force of the energy storage spring, and a crankshaft provided at the frame One end of which is rotatably connected to the crankshaft, the other end is rotatably connected to the movable spring receiver, and an actuating force is applied to the movable spring receiver in response to the rotation of the crankshaft. And a guide device attached to the frame for guiding the movable spring receiver so that the movable spring receiver moves linearly, and the action of the spring acting force of the energy storage spring on the movable spring receiver. The accumulator spring device, wherein the point and the action point on the spring receiver of the action force of the spring rod coincide with each other.

A frame, a crankshaft, a spring rod that is rotatably connected to the crankshaft at one end, a movable spring receiver that is rotatably connected to the other end of the spring rod around a rotation center, and attached to the frame A guide device that guides the movable spring receiver so as to perform a linear motion; and an accumulator spring that is provided between the movable spring receiver and the frame and has a central axis, and the center of rotation is the above-mentioned of the accumulator spring. An accumulator spring device, wherein the accumulator spring device is located on a central axis and in a contact surface with which the accumulator spring of the movable spring receiver abuts.

A frame, a crankshaft, a spring rod that is rotatably connected to the crankshaft at one end, a movable spring receiver that is rotatably connected to the other end of the spring rod around a rotation center, and attached to the frame A guide device that guides the movable spring receiver so as to move linearly; and an accumulator spring that is provided between the movable spring receiver and the frame and has a central axis, and the accumulator springs are arranged concentrically with each other. A plurality of coil springs having different contact surfaces, wherein the center of rotation is on the center axis of the energy storage spring, and each of the above-mentioned is viewed from the center of rotation in the axial direction of the energy storage spring. An energy storage spring device characterized in that the sum of the products of the distance to the contact surface and the energy storage load of each energy storage spring is near zero.

Spring rod is arranged without penetrating the prestressing spring, frame - claim beam which is fixed to the guide device is characterized in that through the movable spring bearing in the axial direction of the prestressing spring 1 to 3 The accumulator spring device according to any one of the above .