JP3798823B2

JP3798823B2 - Rotary compressor

Info

Publication number: JP3798823B2
Application number: JP30340994A
Authority: JP
Inventors: 武和帯谷; 正典増田; 孝洋植松
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 1994-12-07
Filing date: 1994-12-07
Publication date: 2006-07-19
Anticipated expiration: 2021-07-19
Also published as: JPH08159070A

Description

【０００１】
【産業上の利用分野】
本発明は、主として冷凍装置に使用するロータリー圧縮機に関する。
【０００２】
【従来の技術】
従来、シリンダにシリンダ室を形成し、該シリンダ室に、駆動軸の偏心部の偏心回転に伴って公転するローラを内装すると共に、前記シリンダをフロントヘッド及びリヤヘッドで挟持したロータリー圧縮機として、例えば特開平６−５８２７７号公報に記載されたものが知られている。
【０００３】
即ち、従来のロータリー圧縮機は、図１１及び図１２で示したように、密閉ケーシングＡに、シリンダ室Ｂ１をもつシリンダＢと、該シリンダ室Ｂ１を閉鎖するようにシリンダＢを挟持するフロントヘッドＣ及びリヤヘッドＤからなる圧縮要素ＣＦを内装して、前記シリンダ室Ｂ１にローラＥを回転可能に内装すると共に、該ローラＥに駆動軸Ｆの偏心部Ｆ１を挿嵌させて、この偏心部Ｆ１の偏心回転によって前記ローラＥを前記シリンダ室Ｂ１内で偏心回転させて、吸入管Ｇが接続される吸入通路Ｈから前記シリンダ室Ｂ１内に吸入した低圧ガスを圧縮して、前記ケーシングＡ内に吐出するようにしている。
【０００４】
また、従来のロータリー圧縮機では、図１２に示すシリンダ室Ｂ１の概略図のように、前記シリンダ室Ｂ１内をブレードＪにより吐出ポートＫが開口する高圧室Ｘと前記吸入通路Ｈが開口する低圧室Ｙとに区画し、さらに、前記ローラＥ内周面と偏心部Ｆ１の外周面との間の摺接部に給油するために、前記ケーシングＡ底部に溜る高温高圧の油を駆動軸Ｆの主給油通路Ｆ２を介して前記摺接部に給油するようにしている。
【０００５】
さらに、このローラＥ内周側に給油される油がケーシングＡ内の高圧圧力を受けていることから、ローラＥ内周側に給油される油を差圧により前記ローラＥ端面と前記フロントヘッドＣ及びリヤヘッドＤとの間の隙間によって形成される給油通路を介して前記高圧室Ｘと低圧室Ｙとに給油することにより、前記ローラＥの端面の潤滑を行いながら、前記高圧室Ｘと低圧室Ｙとを区画するローラＥのシリンダ室Ｂ１内周面との摺接ポイントＰにおいて、ガス漏れを防ぐためにオイルシールをするようにしている。尚、前記摺接ポイントＰをオイルシールするための給油は、差圧の関係で主に前記高圧室Ｘに給油される油によって行われる。
【０００６】
【発明が解決しようとする課題】
ところで、従来のロータリー圧縮機では、前記高圧室Ｘと低圧室Ｙとを区画するローラＥのシリンダ室Ｂ１内周面との摺接ポイントＰをオイルシールするために、ローラＥ内周側に給油される油を差圧により前記ローラＥ端面と前記フロントヘッドＣ及びリヤヘッドＤとの間の隙間を介して前記高圧室Ｘに給油するようにしているが、前記ローラＥの径方向幅が一定の長さであるため、前記ローラＥ内周側の油が前記高圧室Ｘ側に供給される給油通路と前記低圧室Ｙ側に供給される給油通路とは、その長さが等しいため、高圧室Ｘ及び低圧室Ｙへの給油は、この高圧室Ｘ及び低圧室Ｙの圧力と油の圧力即ちケーシングＡ内の圧力との圧力差により給油量が決まることになる。
【０００７】
つまり、前記高圧室Ｘの圧力とケーシングＡ内の圧力との圧力差が、前記低圧室Ｙの圧力とケーシングＡ内の圧力との圧力差よりも小さいので、前記高圧室Ｘ側への給油量が少なくなり、前記高圧室Ｘから前記摺接ポイントＰへの給油量が不足してしまい、シール効果が得られないし、また、油の流入及び漏れを防止したい低圧室Ｙへの給油量が、差圧が大きいために多くなってしまい、全体として容積効率が低下する問題が生じていた。
【０００８】
本発明は、上記問題に鑑みてなしたもので、その目的は、高圧室への給油を良好に行って、ローラ外周面とシリンダ室内周面との間のシール効果が良好に得られて容積効率の向上が図れるロータリー圧縮機を提供することにある。
【０００９】
【課題を解決するための手段】
請求項１記載の発明は、シリンダ室３１に、駆動軸２の偏心部２１が挿嵌され、該偏心部２１の偏心回転に伴って公転する筒状ローラ５と、前記シリンダ室３１を高圧室Ｘと低圧室Ｙとに画成するブレード６とを内装し、前記駆動軸２に設ける主給油通路２２から前記偏心部２１と前記ローラ５との間に給油するようにしたロータリー圧縮機において、前記ローラ５の径方向外方に前記ブレード６を一体的に設けて、このブレード６の突出側先端部を、前記シリンダ室３１を形成するシリンダ３に回転可能に支持する支持体３４の受入溝３５に受け入れさせ、前記ローラ５の端面と、該ローラ５の端面と対向する固定部材４１，４２，４３との間に、前記主給油通路２２と前記高圧室Ｘとを結ぶ高圧側給油通路７と、前記主給油通路２２と前記低圧室Ｙとを結ぶ低圧側給油通路８とを形成し、前記高圧側給油通路７を形成する前記ローラ５端面に、該ローラ５の内周部に開放する切欠部５２を形成して、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくしたのである。
【００１０】
請求項２記載の発明は、シリンダ室３１に、駆動軸２の偏心部２１が挿嵌され、該偏心部２１の偏心回転に伴って公転する筒状ローラ５と、前記シリンダ室３１を高圧室Ｘと低圧室Ｙとに画成するブレード６とを内装し、前記駆動軸２に設ける主給油通路２２から前記偏心部２１と前記ローラ５との間に給油するようにしたロータリー圧縮機において、前記ローラ５の径方向外方に前記ブレード６を一体的に設けて、このブレード６の突出側先端部を、前記シリンダ室３１を形成するシリンダ３に回転可能に支持する支持体３４の受入溝３５に受け入れさせ、前記ローラ５の端面と、該ローラ５の端面と対向する固定部材４１，４２，４３との間に、前記主給油通路２２と前記高圧室Ｘとを結ぶ高圧側給油通路７と、前記主給油通路２２と前記低圧室Ｙとを結ぶ低圧側給油通路８とを形成し、前記高圧側給油通路７を形成する前記ローラ５端面の内外周間に、周縁の閉じた凹部５３を形成して、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくしたのである。
【００１１】
請求項３記載の発明は、シリンダ室３１に、駆動軸２の偏心部２１が挿嵌され、該偏心部２１の偏心回転に伴って公転する筒状ローラ５と、前記シリンダ室３１を高圧室Ｘと低圧室Ｙとに画成するブレード６とを内装し、前記駆動軸２に設ける主給油通路２２から前記偏心部２１と前記ローラ５との間に給油するようにしたロータリー圧縮機において、前記ローラ５の径方向外方に前記ブレード６を一体的に設けて、このブレード６の突出側先端部を、前記シリンダ室３１を形成するシリンダ３に回転可能に支持する支持体３４の受入溝３５に受け入れさせ、前記ローラ５の端面と、該ローラ５の端面と対向する固定部材４１，４２，４３との間に、前記主給油通路２２と前記高圧室Ｘとを結ぶ高圧側給油通路７と、前記主給油通路２２と前記低圧室Ｙとを結ぶ低圧側給油通路８とを形成し、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部と高圧室Ｘとを連通する方向に延びるスリット５４を形成して、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくしたのである。
【００１２】
【作用】
請求項１記載の発明では、前記ローラ５の径方向外方に前記ブレード６を一体的に設けて、このブレード６の突出側先端部を、前記シリンダ室３１を形成するシリンダ３に回転可能に支持する支持体３４の受入溝３５に受け入れさせたから、前記高圧室Ｘから前記ブレード６を介して前記低圧室Ｙに高圧ガスが漏れるのを阻止でき、容積効率を向上できるのである。さらに、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくしたから、駆動軸２の主給油通路２２から汲み上げられる油を高圧室Ｘ側へ良好に供給できるので、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られるし、低圧室Ｙへの油の流入も軽減できるので容積効率の向上がさらに図れるのである。
【００１３】
さらに、請求項１記載の発明では、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部に開放する切欠部５２を形成したから、この切欠部５２により、前記高圧側給油通路７の通路長さを前記低圧側給油通路８の通路長さよりも短くすることができ、通路長さが短くなる分前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるので、前記高圧室Ｘ側へ良好に供給して、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減できるので容積効率の向上が図れる。
【００１４】
しかも、前記ローラ５は、前記ブレード６が一体的に設けられ、このブレード６がシリンダ３で回転可能に支持されているので、前記ローラ５は自転することなく公転することから、前記ローラ５のシリンダ室３１での位置が決定されるので、前記切欠部５２の形成位置を容易に設定できるし、また、該切欠部５２の加工も容易に行え、さらに、前記切欠部５２に油を溜めておくことができるので、起動時において、液冷媒が多量に混入した油が前記主給油通路２２を介して給油されてきても、前記切欠部５２に溜る油により冷媒潤滑を軽減でき、それだけ信頼性を向上できる。
【００１５】
請求項２記載の発明は、前記高圧側給油通路７を形成するローラ５端面の内外周間に、周縁の閉じた凹部５３を形成したから、この凹部５３により、前記高圧側給油通路７の通路長さを前記低圧側給油通路８の通路長さよりも短くして前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくして、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減して容積効率の向上が図れる。
【００１６】
しかも、前記凹部５３は、自転しない前記ローラ５の端面に形成するので、凹部５３形成位置を容易に設定できるし、その加工も容易にでき、さらに、前記凹部５３は、前記ローラ５の内周と外周との間に形成しているので、前記凹部５３を油溜とすることにより、ローラ５端面への潤滑も良好に行えるのである。
【００１７】
請求項３記載の発明では、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部と高圧室Ｘとを連通する径方向に延びるスリット５４を形成したから、このスリット５４により前記高圧側給油通路７の通路の通路面積が拡大され、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるのであり、前記スリット５４により前記高圧室Ｘに積極的に給油することができ、前記ローラ５の外周面とシリンダ室３１の内周面との間のシールを良好に行えるのである。
【００１８】
【実施例】
参考例について、図１及び図２に基づいて説明する。図１に示す参考例は、二気筒のロータリー圧縮機であって、内方底部に油溜１ａをもった密閉ケーシング１の内方上部側に、モータＭを配設すると共に、このモータＭの下部側に前記モータＭから延びる駆動軸２で回転駆動される圧縮要素ＣＦを配設している。
【００１９】
前記駆動軸２は、軸方向に、複数の偏心部２１，２１を備えており、また、前記圧縮要素ＣＦは、固定部材となるシリンダ３，３、フロントヘッド４１、リヤヘッド４２、ミドルプレート４３から構成し、前記シリンダ３，３に、前記偏心部２１，２１が内部に位置する複数のシリンダ室３１，３１を形成し、前記ミドルプレート４３は前記各シリンダ３，３間に介装している。そして、前記各シリンダ３，３の上下部位に前記フロントヘッド４１とリヤヘッド４２とを配設している。
【００２０】
さらに、前記各シリンダ室３１，３１の内部には、前記駆動軸２の偏心部２１，２１が挿嵌されるローラ５，５を配設し、該ローラ５，５の回転により摺動するブレード６によって前記各シリンダ室３１，３１を高圧室Ｘと低圧室Ｙとに区画して、前記ローラ５，５の偏心回転により、該各シリンダ室３１，３１でシリンダ３，３の吸入通路３２，３２に接続する吸入管１１から流入する吸入冷媒を圧縮すると共に、前記各シリンダ室３１，３１の高圧室Ｘで圧縮された圧縮ガスを前記吐出ポート３３を介してケーシング１内部空間へ吐出させるようにしている。
【００２１】
また、前記駆動軸２には、軸方向に延びる主給油通路２２を形成しており、該主給油通路２２の下端部に、前記ケーシング１底部の油溜１ａに開口する油ポンプ２３を設けて、前記主給油通路２２に前記油溜１ａの油を汲み上げて、該主給油通路２２から分岐する分岐通路２４，２４を介して前記偏心部２１と前記ローラ５との間に給油するようしている。
【００２２】
しかして、参考例では、以上の二気筒ロータリー圧縮機において、前記ローラ５の端面と、該ローラ５の端面と対向する前記フロントヘッド４１、リヤヘッド４２、ミドルプレート４３との間に、前記主給油通路２２に連通する前記ローラ５の内周部と前記高圧室Ｘとを結ぶ高圧側給油通路７と、前記主給油通路２２に連通する前記ローラ５の内周部と前記低圧室Ｙとを結ぶ低圧側給油通路８とを形成し、前記フロントヘッド４１、リヤヘッド４２、ミドルプレート４３における高圧側給油通路７形成部に、ローラ５の内周部への開放のみを許す凹部４４を形成して、この凹部４４形成により前記高圧側給油通路７の通路長さａを前記低圧側給油通路８の通路長さｂよりも短くすることにより前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくしたのである。
【００２３】
即ち、図２に示すように、前記フロントヘッド４１、リヤヘッド４２、ミドルプレート４３におけるシリンダ室３１への対向面で、前記吐出ポート３３近くで、かつ、前記ブレード６の最進出位置近くに、前記ローラ５が偏心回転する際、該ローラ５の端面が対向するか、または、ローラ５の内周側に位置する凹部４４を形成するのである。
【００２４】
該凹部４４は、前記ローラ５が偏心回転する際、ローラ５の外周側には開口しないようしており、吐出ポート３３側に向かう山なりに形成している。
【００２５】
斯くすることにより、前記フロントヘッド４１、リヤヘッド４２、ミドルプレート４３における高圧側給油通路７形成部に、ローラ５の内周部への開放のみを許す凹部４４を形成したから、この凹部４４により、前記高圧側給油通路７の通路長さａを前記低圧側給油通路８の通路長さｂよりも短くすることができ、通路長さが短くなった分前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるので、前記高圧室Ｘ側へ良好に供給して、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減できるので容積効率の向上が図れる。
【００２６】
しかも、前記フロントヘッド４１、リヤヘッド４２、ミドルプレート４３に前記凹部４４を形成するので、前記ローラ５が偏心回転する際に自転しても、このローラ５の自転に関係なく前記高圧室Ｘ側へ良好に供給できるし、また、前記凹部４４に油を溜めておくことができるので、起動時において、液冷媒が多量に混入した油が前記主給油通路２２を介して給油されてきても、前記凹部４４に溜る油により冷媒潤滑を軽減でき、それだけ信頼性を向上できる。
【００２７】
尚、前記参考例では、複数のシリンダを有する多気筒のロータリー圧縮機について述べたが、前記凹部４４の形成は、１シリンダからなる一気筒ロータリー圧縮機にも適用できることを云うまでもない。また、前記凹部４４は、参考例のように、前記ローラ５の両端面に対向させて形成してもよいし、一方の端面だけに対向させるように形成してもよい。
【００２８】
次に第１実施例について図３及び図４に基づいて説明する。第１実施例は、図４に示すように、ローラ５が自転することなく揺動する揺動形の一気筒ロータリー圧縮機で、モータＭを備え、圧縮要素ＣＦを前記シリンダ３、該シリンダ３を挟持するフロントヘッド４１、リヤヘッド４２から構成している。
【００２９】
そして、前記シリンダ３に吸入管１１を接続する吸入通路３２と、圧縮したガスをケーシング１内に吐出させる吐出ポート３３とを形成している。
【００３０】
さらに、前記シリンダ３のシリンダ室３１にローラ５を内装し、該ローラ５は、該ローラ５の径方向外方に、シリンダ室３１を高圧室Ｘと低圧室Ｙとに画成するブレード６を一体的に設けて、このブレード６の突出側先端部を、前記シリンダ３に回転可能に支持する支持体３４の受入溝３５に受け入れさせたのである。
【００３１】
つまり、前記ブレード６を前記ローラ５の外周一部に、該ローラ５の径方向外方に向けて突出するように一体成形すると共に、前記シリンダ３における前記吸入通路３２と吐出ポート３３との中間内方部に円筒形の筒状保持孔３６を設けて、この保持孔３６に、横断面が半円形状の２つの半円柱状部材３７，３７から成る支持体３４を、これら各半円柱状部材３７，３７の平坦面が相対向するように回動可能に保持して、これら各半円柱状部材３７，３７の平坦面の間に、一端が前記シリンダ室３１側に開口される受入溝３５を形成し、この受入溝３５内に前記ブレード６の突出側先端部を摺動可能に挿入させる。
【００３２】
尚、前記ローラ５の外周一部に前記ブレード６を設けるに際しては、前記ローラ５側に前記ブレード６の基端一部を挿入可能とした取付溝を形成し、この取付溝内に前記ブレード６の基端一部を挿入させて接着剤で接着一体化させるか或はロウ付けにより一体化させるようにしてもよいし、前記ブレード６の基端部をピン等により前記ローラ５に固定するようにしてもよい。
【００３３】
また、前記支持体３４は、一つの円柱状部材から形成し、この部材に前記ブレード６が摺動可能な切欠溝を形成して受入溝を形成するようにしてもよい。
【００３４】
そして、前記駆動軸２の駆動に伴い前記ローラ５に設けたブレード６を、その突出先端部を前記支持体３４の受入溝３５内で出入させ、かつ、該支持体３４の回動を伴い、揺動しながら径方向へと進退動させることにより、前記シリンダ室３１の内部を高圧室Ｘと低圧室Ｙとに画成するのである。
【００３５】
さらに、前記ローラ５は、内周側両端に環状の段部５１，５１を形成しており、この段部５１，５１の形成により内周面の面積を小さくして、前記偏心部２１との接触面積を小さくして摺動抵抗を少なくするようにしている。そして、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部に開放する切欠部５２を形成するのであって、該切欠部５２は、図４に示すように、前記吐出ポート３３近くで、かつ、ブレード６の根元近くに、円弧状で、前記段部５１，５１に連続するように形成するのである。
【００３６】
従って、第１実施例では、前記ローラ５の径方向外方に、ブレード６を一体的に設けたから、前記高圧室Ｘから前記ブレード６を介して前記低圧室Ｙに高圧ガスが漏れるのを阻止でき、容積効率を向上できるのである。
【００３７】
しかも、前記ローラ５に切欠部５２を形成したので、この切欠部５２により、前記高圧側給油通路７の通路長さａを前記低圧側給油通路８の通路長さｂよりも短くすることができ、通路長さが短くなった分前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるので、前記高圧室Ｘ側へ良好に供給して、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減できるのでさらに容積効率の向上が図れる。
【００３８】
しかも、前記ローラ５は、前記ブレード６が一体的に設けられ、このブレード６がシリンダ３で回転可能に支持されているので、前記ローラ５は自転することなく公転することから、前記ローラ５のシリンダ室３１での位置が決定され、前記切欠部５２の形成位置を容易に設定できるし、また、該切欠部５２の加工も容易に行えるのである。
【００３９】
さらに、前記段部５１，５１と前記切欠部５２に油を溜めておくことができるので、起動時において、液冷媒が多量に混入した油が前記主給油通路２２を介して給油されてきても、前記段部５１，５１及び切欠部５２に溜る油により冷媒潤滑を軽減でき、それだけ信頼性を向上できるのである。
【００４０】
次に、第２実施例について図５及び図６に基づいて説明する。第２実施例は、前記第１実施例と同様の揺動形ロータリー圧縮機で、基本的構成及びローラ５にブレード６が一体に形成されている点では、共通しているので、その説明は省略する。
【００４１】
前記第１実施例では、ローラ５の内周側に段部５１，５１を形成し、この段部５１，５１に連続するように切欠部５２を形成したが、第２実施例では、前記ローラ５の内周側に形成する段部５１，５１を利用して、前記第１実施例のような切欠部を形成するようにしたもので、前記ローラ５の内周側に環状の段部５１，５１を形成する際、ローラ５の中心に対し、吐出ポート３３側に向かって偏心させた位置を中心とした環状の段部５１，５１を形成することにより、該段部５１，５１を吐出ポート３３側に偏って形成して、吐出ポート３３側の段部５１，５１の容積を周方向反対側よりも大きくすることにより、結果的に切欠量を多くすることができるのである。
【００４２】
従って、前記段部５１，５１の形成により、前記高圧側給油通路７の通路長さａを前記低圧側給油通路８の通路長さｂよりも短くすることができ、しかも、前記低圧側給油通路８の通路長さｂは、第１実施例のローラ５に比べて、通路長さを長くできるのである。その結果、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりもより効果的に小さくできるので、前記高圧室Ｘ側へ良好に供給して、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も通路抵抗が大きくなるので、さらに軽減できるのである。
【００４３】
しかも、第２実施例においても、前記ローラ５に前記ブレード６を一体的に設けているので、前記ブレード６形成部における高圧室Ｘから低圧室Ｙへのガス漏れを阻止できながら、前記ローラ５が公転することから、前記段部５１，５１を変位させて形成するのも容易に行えるのである。
【００４４】
さらに、前記段部５１，５１に油を溜めておくことができるので、起動時において、液冷媒が多量に混入した油が前記主給油通路２２を介して給油されてきても、前記段部５１，５１及び切欠部５２に溜る油により冷媒潤滑を軽減できる。
【００４５】
次に、第３実施例について図７及び図８に基づいて説明する。第３実施例も、前記第１及び第２実施例と同様の揺動形ロータリー圧縮機で、基本的構成及びローラ５にブレード６が一体に形成されている点では、共通しているので、その説明は省略する。
【００４６】
前記第３実施例は、内周側に環状の段部５１，５１が形成されたローラ５の両端面で、前記高圧側給油通路７を形成する内外周間に、周縁の閉じた凹部５３を形成したものであって、端面における吐出ポート３３の近くに一つの凹部５３を形成している。また、図８では、凹部５３は、一つしか形成していないが、複数形成してもよいし、どちらか一方の端面に形成するだけでもよい。
【００４７】
第３実施例では、前記凹部５３により、前記高圧側給油通路７の全体としての通路長さを前記低圧側給油通路８の通路長さよりも短くして前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるのである。
【００４８】
従って、第３実施例においても、前記ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減して容積効率の向上が図れる。
【００４９】
しかも、前記凹部５３は、自転しない前記ローラ５の端面に形成するので、凹部５３形成位置を容易に設定できるし、その加工も容易にでき、さらに、前記凹部５３は、前記ローラ５の内周と外周との間の形成しているので、前記凹部５３を油溜とすることにより、ローラ５端面への潤滑も良好に行えるのである。
【００５０】
次に、第４実施例について図９及び図１０に基づいて説明する。第４実施例も、前記第１乃至第３実施例と同様の揺動形ロータリー圧縮機で、基本的構成及びローラ５にブレード６が一体に形成されている点では、共通しているので、その説明は省略する。
【００５１】
前記第４実施例は、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部と高圧室Ｘとを連通する径方向に延びる複数のスリット５４を形成したものであって、該スリット５４は、吐出ポート３３近くに形成されている。尚、このスリット５４は、複数形成してもよいし、１本だけ形成するようにしてもよい。
【００５２】
第４実施例では、前記スリット５４により前記高圧側給油通路７の通路の通路面積が拡大され、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるのであり、前記スリット５４により前記高圧室Ｘに積極的に給油することができ、前記ローラ５の外周面とシリンダ室３１の内周面との間のシールを良好に行えるのである。
【００５３】
尚、前記参考例では、固定部材であるフロントヘッド、リヤヘッド、ミドルプレートにローラ外周側には開放しない凹部を形成したが、各固定部材にローラ内周側と高圧室とを連通するようにスリットを形成するようにしてもよい。
【００５４】
斯くするときは、第４実施例と同様に前記高圧側給油通路の通路面積が拡大され、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくでき、シール効果を良好にできる。
【００５５】
【発明の効果】
請求項１記載の発明では、前記ローラ５の径方向外方に、前記ブレード６を一体的に設けて、このブレード６の突出側先端部を、前記シリンダ室３１を形成するシリンダ３に回転可能に支持する支持体３４の受入溝３５に受け入れさせたから、前記高圧室Ｘから前記ブレード６を介して前記低圧室Ｙに高圧ガスが漏れるのを阻止でき、容積効率を向上できるのである。さらに、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくしたから、駆動軸２の主給油通路２２から汲み上げられる油を高圧室Ｘ側へ良好に供給できるので、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られるし、低圧室Ｙへの油の流入も軽減できるので容積効率の向上がさらに図れるのである。
【００５６】
さらに、請求項１記載の発明では、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部に開放する切欠部５２を形成したから、この切欠部５２により、前記高圧側給油通路７の通路長さを前記低圧側給油通路８の通路長さよりも短くすることができ、通路長さが短くなる分前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるので、前記高圧室Ｘ側へ良好に供給して、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減できるので容積効率の向上が図れる。
【００５７】
しかも、前記ローラ５は、前記ブレード６が一体的に設けられ、このブレード６がシリンダ３で回転可能に支持されているので、前記ローラ５は自転することなく公転することから、前記ローラ５のシリンダ室３１での位置が決定されるので、前記切欠部５２の形成位置を容易に設定できるし、また、該切欠部５２の加工も容易に行え、さらに、前記切欠部５２に油を溜めておくことができるので、起動時において、液冷媒が多量に混入した油が前記主給油通路２２を介して給油されてきても、前記切欠部５２に溜る油により冷媒潤滑を軽減でき、それだけ信頼性を向上できる。
【００５８】
請求項２記載の発明では、前記高圧側給油通路７を形成するローラ５端面の内外周間に、周縁の閉じた凹部５３を形成したから、この凹部５３により、前記高圧側給油通路７の通路長さを前記低圧側給油通路８の通路長さよりも短くして前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくして、ローラ５の外周面とシリンダ室３１の内周面との間のシール効果が良好に得られながら、前記低圧室Ｙへの油の流入も軽減して容積効率の向上が図れる。
【００５９】
しかも、前記凹部５３は、自転しない前記ローラ５の端面に形成するので、凹部５３形成位置を容易に設定できるし、その加工も容易にでき、さらに、前記凹部５３は、前記ローラ５の内周と外周との間に形成しているので、前記凹部５３を油溜とすることにより、ローラ５端面への潤滑も良好に行えるのである。
【００６０】
請求項３記載の発明では、前記高圧側給油通路７を形成するローラ５端面に、該ローラ５の内周部と高圧室Ｘとを連通する方向に延びるスリット５４を形成したから、このスリット５４により前記高圧側給油通路７の通路の通路面積が拡大され、前記高圧側給油通路７の通路抵抗を、前記低圧側給油通路８の通路抵抗よりも小さくできるのであり、前記スリット５４により前記高圧室Ｘに積極的に給油することができ、前記ローラ５の外周面とシリンダ室３１の内周面との間のシールを良好に行えるのである。
【図面の簡単な説明】
【図１】本発明の参考例のロータリー圧縮機を示す圧縮機下部側の縦断面図。
【図２】同参考例のシリンダ室内部を示す概略説明図。
【図３】本発明のロータリー圧縮機の第１実施例を示す圧縮機下部側の縦断面図。
【図４】同第１実施例のシリンダ室内部を示す概略説明図。
【図５】本発明のロータリー圧縮機の第２実施例を示す圧縮機下部側の縦断面図。
【図６】同第２実施例のシリンダ室内部を示す概略説明図。
【図７】本発明のロータリー圧縮機の第３実施例を示す圧縮機下部側の縦断面図。
【図８】同第３実施例のシリンダ室内部を示す概略説明図。
【図９】本発明のロータリー圧縮機の第４実施例を示す圧縮機下部側の縦断面図。
【図１０】同第４実施例のシリンダ室内部を示す概略説明図。
【図１１】従来のロータリー圧縮機の下部側縦断面図。
【図１２】同従来のロータリー圧縮機におけるシリンダ室内部概略説明図。
【符号の説明】
２駆動軸５ローラ
２１偏心部５２切欠部
２２主給油通路５３凹部
３シリンダ５４スリット
３１シリンダ室６ブレード
３４支持体７高圧側給油通路
３５受入溝８低圧側給油通路
４１固定部材（フロントヘッド）
４２固定部材（リヤヘッド）
４３固定部材（ミドルプレート）
４４凹部[0001]
[Industrial application fields]
The present invention relates to a rotary compressor mainly used for a refrigeration apparatus.
[0002]
[Prior art]
Conventionally, as a rotary compressor in which a cylinder chamber is formed in a cylinder, and a roller that revolves with an eccentric rotation of an eccentric portion of a drive shaft is provided in the cylinder chamber, and the cylinder is sandwiched between a front head and a rear head. A device described in Japanese Patent Laid-Open No. 6-58277 is known.
[0003]
That is, as shown in FIGS. 11 and 12, the conventional rotary compressor includes a cylinder B having a cylinder chamber B1 in a sealed casing A and a front head that sandwiches the cylinder B so as to close the cylinder chamber B1. A compression element CF composed of C and a rear head D is provided, and a roller E is rotatably provided in the cylinder chamber B1, and an eccentric portion F1 of a drive shaft F is inserted into the roller E, and the eccentric portion F1 is inserted. The eccentric rotation of the roller E causes the roller E to rotate eccentrically in the cylinder chamber B1 and compresses the low-pressure gas sucked into the cylinder chamber B1 from the suction passage H to which the suction pipe G is connected, into the casing A. I am trying to discharge.
[0004]
In the conventional rotary compressor, as shown in the schematic view of the cylinder chamber B1 shown in FIG. 12, the high pressure chamber X in which the discharge port K is opened by the blade J and the suction passage H is opened in the cylinder chamber B1. In order to supply oil to the sliding contact portion between the inner peripheral surface of the roller E and the outer peripheral surface of the eccentric portion F1, high-temperature and high-pressure oil accumulated at the bottom of the casing A is supplied to the drive shaft F. Oil is supplied to the sliding contact portion via the main oil supply passage F2.
[0005]
Further, since the oil supplied to the inner peripheral side of the roller E is subjected to the high pressure in the casing A, the oil supplied to the inner peripheral side of the roller E is changed by the differential pressure between the end face of the roller E and the front head C. The high pressure chamber X and the low pressure chamber are lubricated while lubricating the end face of the roller E by supplying oil to the high pressure chamber X and the low pressure chamber Y through an oil supply passage formed by a gap between the rear head D and the rear head D. In order to prevent gas leakage at the sliding contact point P with the inner circumferential surface of the cylinder chamber B1 of the roller E that divides Y, an oil seal is provided. In addition, the oil supply for oil-sealing the sliding contact point P is performed mainly by the oil supplied to the high-pressure chamber X because of the differential pressure.
[0006]
[Problems to be solved by the invention]
By the way, in the conventional rotary compressor, in order to oil-seal the sliding contact point P with the cylinder chamber B1 inner peripheral surface of the roller E that divides the high pressure chamber X and the low pressure chamber Y, oil is supplied to the inner peripheral side of the roller E. The oil to be supplied is supplied to the high-pressure chamber X through a gap between the end face of the roller E and the front head C and the rear head D by differential pressure, but the radial width of the roller E is constant. Since the length of the oil supply passage to which the oil on the inner peripheral side of the roller E is supplied to the high pressure chamber X side is equal to the length of the oil supply passage to be supplied to the low pressure chamber Y side, the high pressure chamber The amount of oil supplied to X and the low pressure chamber Y is determined by the pressure difference between the pressure in the high pressure chamber X and the low pressure chamber Y and the pressure of the oil, that is, the pressure in the casing A.
[0007]
That is, since the pressure difference between the pressure in the high pressure chamber X and the pressure in the casing A is smaller than the pressure difference between the pressure in the low pressure chamber Y and the pressure in the casing A, the amount of oil supplied to the high pressure chamber X side. The amount of oil supplied from the high-pressure chamber X to the sliding contact point P is insufficient, a sealing effect is not obtained, and the amount of oil supplied to the low-pressure chamber Y to prevent oil inflow and leakage is Since the differential pressure is large, the differential pressure increases, resulting in a problem that the volume efficiency is lowered as a whole.
[0008]
The present invention has been made in view of the above-described problems, and its purpose is to satisfactorily lubricate the high-pressure chamber and to obtain a good sealing effect between the roller outer peripheral surface and the cylinder inner peripheral surface. The object is to provide a rotary compressor capable of improving efficiency.
[0009]
[Means for Solving the Problems]
According to the first aspect of the present invention, the eccentric portion 21 of the drive shaft 2 is inserted into the cylinder chamber 31 and the cylindrical roller 5 revolves with the eccentric rotation of the eccentric portion 21. In a rotary compressor that includes a blade 6 defined in X and a low-pressure chamber Y and supplies oil between the eccentric portion 21 and the roller 5 from a main oil supply passage 22 provided in the drive shaft 2; The blade 6 is integrally provided on the outer side in the radial direction of the roller 5, and a receiving groove of a support body 34 that rotatably supports the protruding end portion of the blade 6 on the cylinder 3 that forms the cylinder chamber 31. 35, and the high-pressure side oil supply passage 7 connecting the main oil supply passage 22 and the high-pressure chamber X between the end surface of the roller 5 and the fixing members 41, 42, 43 facing the end surface of the roller 5. And the main oil supply passage 22 and the front Forming a low-pressure side oil supply passage 8 connecting the low-pressure chamber Y, On the end surface of the roller 5 that forms the high-pressure side oil supply passage 7, a notch 52 that opens to the inner peripheral portion of the roller 5 is formed, The passage resistance of the high pressure side oil supply passage 7 is made smaller than the passage resistance of the low pressure side oil supply passage 8.
[0010]
Claim 2 The described invention An eccentric portion 21 of the drive shaft 2 is inserted into the cylinder chamber 31, and the cylindrical roller 5 that revolves with the eccentric rotation of the eccentric portion 21, and the cylinder chamber 31 is divided into a high pressure chamber X and a low pressure chamber Y. In a rotary compressor in which a blade 6 is formed and oil is supplied between the eccentric portion 21 and the roller 5 from a main oil supply passage 22 provided in the drive shaft 2. The blade 6 is provided integrally with the front end of the blade 6 and is received in a receiving groove 35 of a support 34 that is rotatably supported by the cylinder 3 forming the cylinder chamber 31. Between the main oil supply passage 22 and the high pressure chamber X, and the main oil supply passage 22 between the end face of the roller 5 and the fixing members 41, 42, 43 facing the end face of the roller 5. Low pressure connecting the low pressure chamber Y To form an oil supply passage 8, Between the inner and outer circumferences of the end surface of the roller 5 forming the high-pressure side oil supply passage 7, a recessed portion 53 having a closed periphery is formed. Thus, the passage resistance of the high pressure side oil supply passage 7 is made smaller than the passage resistance of the low pressure side oil supply passage 8. It was.
[0011]
Claim 3 The described invention An eccentric portion 21 of the drive shaft 2 is inserted into the cylinder chamber 31, and the cylindrical roller 5 that revolves with the eccentric rotation of the eccentric portion 21, and the cylinder chamber 31 is divided into a high pressure chamber X and a low pressure chamber Y. In a rotary compressor in which a blade 6 is formed and oil is supplied between the eccentric portion 21 and the roller 5 from a main oil supply passage 22 provided in the drive shaft 2. The blade 6 is provided integrally with the front end of the blade 6 and is received in a receiving groove 35 of a support 34 that is rotatably supported by the cylinder 3 forming the cylinder chamber 31. Between the main oil supply passage 22 and the high pressure chamber X, and the main oil supply passage 22 between the end face of the roller 5 and the fixing members 41, 42, 43 facing the end face of the roller 5. Low pressure connecting the low pressure chamber Y To form an oil supply passage 8, The inner peripheral portion of the roller 5 and the high pressure chamber X are communicated with the end surface of the roller 5 forming the high pressure side oil supply passage 7. Who Shaped slit 54 extending in the direction Thus, the passage resistance of the high pressure side oil supply passage 7 is made smaller than the passage resistance of the low pressure side oil supply passage 8. It was.
[0012]
[Action]
In the first aspect of the present invention, the blade 6 is integrally provided on the outer side in the radial direction of the roller 5, and the protruding end portion of the blade 6 can be rotated to the cylinder 3 forming the cylinder chamber 31. Since it is received in the receiving groove 35 of the support 34 to be supported, the high pressure gas can be prevented from leaking from the high pressure chamber X to the low pressure chamber Y through the blade 6, and the volumetric efficiency can be improved. Further, since the passage resistance of the high-pressure side oil supply passage 7 is made smaller than the passage resistance of the low-pressure side oil supply passage 8, oil pumped up from the main oil supply passage 22 of the drive shaft 2 can be satisfactorily supplied to the high-pressure chamber X side. Therefore, a good sealing effect between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 can be obtained, and the inflow of oil into the low-pressure chamber Y can be reduced, so that the volumetric efficiency can be further improved.
[0013]
And claims 1 In the described invention, the notch 52 that opens to the inner peripheral portion of the roller 5 is formed on the end surface of the roller 5 that forms the high-pressure side oil supply passage 7. The passage length can be made shorter than the passage length of the low-pressure side oil supply passage 8, and the passage resistance of the high-pressure side oil supply passage 7 can be made smaller than the passage resistance of the low-pressure side oil supply passage 8. Since it can be made small, the oil is supplied to the low pressure chamber Y while being well supplied to the high pressure chamber X side and a good sealing effect between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 is obtained. Since inflow can be reduced, volumetric efficiency can be improved.
[0014]
In addition, the roller 5 is integrally provided with the blade 6, and the blade 6 is rotatably supported by the cylinder 3. Therefore, the roller 5 revolves without rotating. Since the position in the cylinder chamber 31 is determined, the formation position of the notch 52 can be easily set, the machining of the notch 52 can be easily performed, and oil can be accumulated in the notch 52. Therefore, even when oil in which a large amount of liquid refrigerant is mixed is supplied through the main oil supply passage 22 at the time of start-up, refrigerant lubrication can be reduced by the oil accumulated in the notch 52, and reliability is increased accordingly. Can be improved.
[0015]
Claim 2 In the described invention, the recessed portion 53 having a closed periphery is formed between the inner and outer periphery of the end surface of the roller 5 forming the high pressure side oil supply passage 7, so that the passage length of the high pressure side oil supply passage 7 is increased by the recessed portion 53. The passage resistance of the high pressure side oil supply passage 7 is made shorter than the passage length of the low pressure side oil supply passage 8 to be smaller than the passage resistance of the low pressure side oil supply passage 8, so that the outer peripheral surface of the roller 5 and the cylinder chamber 31 While the sealing effect between the inner peripheral surface and the inner peripheral surface can be satisfactorily obtained, the inflow of oil into the low pressure chamber Y can be reduced and the volume efficiency can be improved.
[0016]
In addition, since the concave portion 53 is formed on the end surface of the roller 5 that does not rotate, the formation position of the concave portion 53 can be easily set and processed easily. Further, the concave portion 53 has an inner periphery of the roller 5. Since the recess 53 is used as an oil reservoir, the end face of the roller 5 can be well lubricated.
[0017]
Claim 3 In the described invention, the slit 54 extending in the radial direction that connects the inner peripheral portion of the roller 5 and the high-pressure chamber X is formed on the end surface of the roller 5 that forms the high-pressure side oil supply passage 7. The passage area of the high-pressure side oil supply passage 7 is enlarged, and the passage resistance of the high-pressure side oil supply passage 7 can be made smaller than the passage resistance of the low-pressure side oil supply passage 8. Oil can be positively supplied, and the seal between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 can be satisfactorily performed.
[0018]
【Example】
reference An example is demonstrated based on FIG.1 and FIG.2. As shown in FIG. reference An example is a two-cylinder rotary compressor, in which a motor M is disposed on the inner upper side of a sealed casing 1 having an oil reservoir 1a at the inner bottom, and the motor is disposed on the lower side of the motor M. A compression element CF that is rotationally driven by a drive shaft 2 extending from M is disposed.
[0019]
The drive shaft 2 includes a plurality of eccentric portions 21 and 21 in the axial direction, and the compression element CF includes cylinders 3 and 3, a front head 41, a rear head 42, and a middle plate 43 that are fixing members. A plurality of cylinder chambers 31 and 31 in which the eccentric portions 21 and 21 are located are formed in the cylinders 3 and 3, and the middle plate 43 is interposed between the cylinders 3 and 3. . The front head 41 and the rear head 42 are disposed at the upper and lower portions of the cylinders 3 and 3.
[0020]
Further, rollers 5, 5 into which the eccentric parts 21, 21 of the drive shaft 2 are inserted are disposed inside the cylinder chambers 31, 31, and the blades slide by the rotation of the rollers 5, 5. 6 divides the cylinder chambers 31, 31 into a high pressure chamber X and a low pressure chamber Y, and the eccentric rotation of the rollers 5, 5 causes the suction passages 32, The refrigerant sucked in from the suction pipe 11 connected to 32 is compressed, and the compressed gas compressed in the high-pressure chamber X of each of the cylinder chambers 31, 31 is discharged to the internal space of the casing 1 through the discharge port 33. I have to.
[0021]
The drive shaft 2 is formed with a main oil supply passage 22 extending in the axial direction, and an oil pump 23 that opens to the oil reservoir 1a at the bottom of the casing 1 is provided at the lower end of the main oil supply passage 22. The oil in the oil reservoir 1a is pumped into the main oil supply passage 22 and is supplied between the eccentric portion 21 and the roller 5 via branch passages 24 and 24 branched from the main oil supply passage 22. Yes.
[0022]
But reference In the example, in the above-described two-cylinder rotary compressor, the main oil supply passage 22 is communicated between the end surface of the roller 5 and the front head 41, the rear head 42, and the middle plate 43 facing the end surface of the roller 5. The high pressure side oil supply passage 7 connecting the inner peripheral portion of the roller 5 and the high pressure chamber X, and the low pressure side oil supply passage connecting the inner peripheral portion of the roller 5 communicating with the main oil supply passage 22 and the low pressure chamber Y. 8 is formed in the front head 41, the rear head 42, and the middle plate 43 in the high pressure side oil supply passage 7 forming portion, and a recess 44 that allows only the inner periphery of the roller 5 to be opened is formed. Accordingly, the passage length a of the high-pressure side oil supply passage 7 is made shorter than the passage length b of the low-pressure side oil supply passage 8, thereby reducing the passage resistance of the high-pressure side oil supply passage 7 and the passage of the low-pressure side oil supply passage 8. Than it was smaller than the resistance.
[0023]
That is, as shown in FIG. 2, the front head 41, the rear head 42, and the middle plate 43 are opposed to the cylinder chamber 31, near the discharge port 33 and near the most advanced position of the blade 6. When the roller 5 rotates eccentrically, the end surfaces of the roller 5 face each other, or the concave portion 44 located on the inner peripheral side of the roller 5 is formed.
[0024]
The concave portion 44 is formed so as not to open on the outer peripheral side of the roller 5 when the roller 5 rotates eccentrically, and is formed in a mountain shape toward the discharge port 33 side.
[0025]
As a result, a recess 44 that allows only opening to the inner peripheral portion of the roller 5 is formed in the high pressure side oil supply passage 7 forming portion in the front head 41, the rear head 42, and the middle plate 43. The passage length a of the high-pressure side oil supply passage 7 can be made shorter than the passage length b of the low-pressure side oil supply passage 8, and the passage resistance of the high-pressure side oil supply passage 7 is reduced by the amount of the shortened passage length. Since it can be made smaller than the passage resistance of the low-pressure side oil supply passage 8, a good sealing effect is obtained between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31. However, since the inflow of oil into the low pressure chamber Y can be reduced, the volumetric efficiency can be improved.
[0026]
Moreover, since the recess 44 is formed in the front head 41, the rear head 42, and the middle plate 43, even if the roller 5 rotates eccentrically, the roller 5 moves toward the high pressure chamber X regardless of the rotation of the roller 5. Since the oil can be supplied satisfactorily and the oil can be stored in the recess 44, even when oil mixed with a large amount of liquid refrigerant is supplied through the main oil supply passage 22 at the time of start-up, Refrigerant lubrication can be reduced by the oil accumulated in the recess 44, and the reliability can be improved accordingly.
[0027]
The above reference In the example, a multi-cylinder rotary compressor having a plurality of cylinders has been described. Needless to say, the formation of the recess 44 can also be applied to a single-cylinder rotary compressor including one cylinder. The recess 44 is reference As an example, it may be formed so as to face both end faces of the roller 5, or may be formed so as to face only one end face.
[0028]
Next 1 An embodiment will be described with reference to FIGS. First 1 As shown in FIG. 4, the embodiment is a swing type single-cylinder rotary compressor in which the roller 5 swings without rotating. The motor M is provided, the compression element CF is sandwiched between the cylinder 3, and the cylinder 3 is sandwiched. The front head 41 and the rear head 42 are configured.
[0029]
A suction passage 32 for connecting the suction pipe 11 to the cylinder 3 and a discharge port 33 for discharging the compressed gas into the casing 1 are formed.
[0030]
Further, a roller 5 is housed in the cylinder chamber 31 of the cylinder 3, and the roller 5 has a blade 6 that defines the cylinder chamber 31 into a high pressure chamber X and a low pressure chamber Y outside the roller 5 in the radial direction. Provided integrally, the projecting side tip of the blade 6 is received in the receiving groove 35 of the support 34 that is rotatably supported by the cylinder 3.
[0031]
That is, the blade 6 is integrally formed on a part of the outer periphery of the roller 5 so as to protrude outward in the radial direction of the roller 5, and between the suction passage 32 and the discharge port 33 in the cylinder 3. A cylindrical cylindrical holding hole 36 is provided in the inward portion, and a support body 34 composed of two semi-columnar members 37 and 37 having a semicircular cross section is provided in the holding hole 36. A receiving groove whose one end is opened to the cylinder chamber 31 side between the flat surfaces of the semi-cylindrical members 37 and 37, which are rotatably held so that the flat surfaces of the members 37 and 37 face each other. 35 is formed, and the protruding end portion of the blade 6 is slidably inserted into the receiving groove 35.
[0032]
When the blade 6 is provided on a part of the outer periphery of the roller 5, a mounting groove is formed on the roller 5 side so that a part of the base end of the blade 6 can be inserted, and the blade 6 is inserted in the mounting groove. The base end portion of the blade 6 may be inserted and integrated with an adhesive or may be integrated by brazing, or the base end portion of the blade 6 may be fixed to the roller 5 with a pin or the like. It may be.
[0033]
In addition, the support 34 may be formed from a single cylindrical member, and a notch groove in which the blade 6 can slide is formed in this member to form a receiving groove.
[0034]
As the drive shaft 2 is driven, the blade 6 provided on the roller 5 has its projecting tip portion moved in and out of the receiving groove 35 of the support body 34, and with the rotation of the support body 34, The cylinder chamber 31 is divided into a high pressure chamber X and a low pressure chamber Y by advancing and retreating in the radial direction while swinging.
[0035]
Further, the roller 5 is formed with annular step portions 51, 51 at both ends on the inner peripheral side. By forming the step portions 51, 51, the area of the inner peripheral surface is reduced, The contact area is reduced to reduce sliding resistance. And the notch part 52 opened to the inner peripheral part of the roller 5 is formed on the end face of the roller 5 forming the high-pressure side oil supply passage 7, and the notch part 52 is, as shown in FIG. In the vicinity of the discharge port 33 and near the root of the blade 6, it is formed in an arc shape so as to be continuous with the stepped portions 51, 51.
[0036]
Therefore, the second 1 In the embodiment, since the blade 6 is integrally provided on the outer side in the radial direction of the roller 5, it is possible to prevent the high pressure gas from leaking from the high pressure chamber X to the low pressure chamber Y through the blade 6. Can be improved.
[0037]
In addition, since the notch 52 is formed in the roller 5, the notch 52 can make the passage length a of the high pressure side oil supply passage 7 shorter than the passage length b of the low pressure side oil supply passage 8. Since the passage resistance of the high-pressure side oil supply passage 7 can be made smaller than the passage resistance of the low-pressure side oil supply passage 8 as the passage length is shortened, the roller 5 is fed well to the high-pressure chamber X side. While a good sealing effect between the outer peripheral surface and the inner peripheral surface of the cylinder chamber 31 can be obtained, the inflow of oil into the low-pressure chamber Y can be reduced, so that the volume efficiency can be further improved.
[0038]
In addition, the roller 5 is integrally provided with the blade 6, and the blade 6 is rotatably supported by the cylinder 3. Therefore, the roller 5 revolves without rotating. The position in the cylinder chamber 31 is determined, the formation position of the notch 52 can be easily set, and the notch 52 can be easily processed.
[0039]
Further, since oil can be stored in the step portions 51 and 51 and the notch portion 52, even when oil mixed with a large amount of liquid refrigerant is supplied through the main oil supply passage 22 at the time of startup. The oil accumulated in the step portions 51 and 51 and the cutout portion 52 can reduce refrigerant lubrication, and can improve the reliability accordingly.
[0040]
Next 2 An embodiment will be described with reference to FIGS. First 2 The embodiment is the first 1 The swing type rotary compressor similar to the embodiment is common in that the blade 6 is formed integrally with the roller 5 and the basic configuration, and the description thereof is omitted.
[0041]
Said 1 In the embodiment, the step portions 51 and 51 are formed on the inner peripheral side of the roller 5, and the notch portion 52 is formed so as to be continuous with the step portions 51 and 51. 2 In the embodiment, the step portions 51, 51 formed on the inner peripheral side of the roller 5 are used to make the first 1 A notch portion as in the embodiment is formed, and when the annular step portions 51, 51 are formed on the inner peripheral side of the roller 5, the discharge port 33 side is directed toward the center of the roller 5. By forming the annular step portions 51 and 51 centered on the eccentric position, the step portions 51 and 51 are formed to be biased toward the discharge port 33 side, and the step portions 51 and 51 on the discharge port 33 side are formed. By making the volume larger than that on the opposite side in the circumferential direction, the amount of cutout can be increased as a result.
[0042]
Therefore, by forming the step portions 51, 51, the passage length a of the high pressure side oil supply passage 7 can be made shorter than the passage length b of the low pressure side oil supply passage 8, and the low pressure side oil supply passage can be formed. 8 passage length b is 1 Compared to the roller 5 of the embodiment, the passage length can be increased. As a result, the passage resistance of the high-pressure side oil supply passage 7 can be reduced more effectively than the passage resistance of the low-pressure side oil supply passage 8. While the sealing effect between the cylinder chamber 31 and the inner peripheral surface of the cylinder chamber 31 can be satisfactorily obtained, the inflow of oil into the low pressure chamber Y also increases the passage resistance, which can be further reduced.
[0043]
Moreover, the second 2 Also in the embodiment, since the blade 6 is provided integrally with the roller 5, the roller 5 revolves while preventing gas leakage from the high pressure chamber X to the low pressure chamber Y in the blade 6 forming portion. Therefore, the step portions 51 and 51 can be easily formed by being displaced.
[0044]
Further, since oil can be stored in the step portions 51 and 51, even when oil in which a large amount of liquid refrigerant is mixed is supplied through the main oil supply passage 22 at the time of startup, the step portion 51. , 51 and the oil accumulated in the notch 52 can reduce refrigerant lubrication.
[0045]
Next 3 An embodiment will be described with reference to FIGS. First 3 Examples are also described above. 1 And the second 2 The swing type rotary compressor similar to the embodiment is common in that the blade 6 is formed integrally with the roller 5 and the basic configuration, and the description thereof is omitted.
[0046]
Said 3 In the embodiment, a recessed portion 53 having a closed periphery is formed between the inner and outer peripheries forming the high-pressure side oil supply passage 7 on both end faces of the roller 5 having annular step portions 51, 51 formed on the inner peripheral side. In addition, one recess 53 is formed near the discharge port 33 on the end face. In FIG. 8, only one recess 53 is formed, but a plurality of recesses 53 may be formed, or only one of the end faces may be formed.
[0047]
First 3 In the embodiment, the recess 53 reduces the passage length of the high-pressure side oil supply passage 7 by making the overall passage length of the high-pressure side oil supply passage 7 shorter than the passage length of the low-pressure side oil supply passage 8. It can be made smaller than the passage resistance of the side oil supply passage 8.
[0048]
Therefore, the second 3 Also in the embodiment, while the sealing effect between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 can be satisfactorily obtained, the inflow of oil into the low-pressure chamber Y is reduced and the volume efficiency is improved. I can plan.
[0049]
In addition, since the concave portion 53 is formed on the end surface of the roller 5 that does not rotate, the formation position of the concave portion 53 can be easily set and processed easily. Further, the concave portion 53 has an inner periphery of the roller 5. Since the recess 53 is used as an oil reservoir, the end face of the roller 5 can be well lubricated.
[0050]
Next 4 An embodiment will be described with reference to FIGS. 9 and 10. First 4 Examples are also described above. 1 Thru 3 The swing type rotary compressor similar to the embodiment is common in that the blade 6 is formed integrally with the roller 5 and the basic configuration, and the description thereof is omitted.
[0051]
Said 4 In the embodiment, a plurality of slits 54 extending in the radial direction communicating the inner peripheral portion of the roller 5 and the high pressure chamber X are formed on the end face of the roller 5 forming the high pressure side oil supply passage 7, The slit 54 is formed near the discharge port 33. A plurality of slits 54 may be formed, or only one slit 54 may be formed.
[0052]
First 4 In the embodiment, the passage area of the passage of the high-pressure side oil supply passage 7 is enlarged by the slit 54, and the passage resistance of the high-pressure side oil supply passage 7 can be made smaller than the passage resistance of the low-pressure side oil supply passage 8. The slit 54 can positively supply oil to the high-pressure chamber X, and the seal between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 can be satisfactorily performed.
[0053]
The above reference In the example, the front member, the rear head, and the middle plate, which are fixing members, have recesses that do not open on the outer peripheral side of the roller. However, slits are formed in each fixing member so that the inner peripheral side of the roller communicates with the high pressure chamber It may be.
[0054]
When doing so, 4 Similarly to the embodiment, the passage area of the high pressure side oil supply passage is enlarged, the passage resistance of the high pressure side oil supply passage 7 can be made smaller than the passage resistance of the low pressure side oil supply passage 8, and the sealing effect can be improved.
[0055]
【The invention's effect】
According to the first aspect of the present invention, the blade 6 is integrally provided on the outer side in the radial direction of the roller 5, and the protruding end portion of the blade 6 can be rotated to the cylinder 3 forming the cylinder chamber 31. Therefore, the high-pressure gas can be prevented from leaking from the high-pressure chamber X to the low-pressure chamber Y through the blade 6 and the volumetric efficiency can be improved. Further, since the passage resistance of the high-pressure side oil supply passage 7 is made smaller than the passage resistance of the low-pressure side oil supply passage 8, oil pumped up from the main oil supply passage 22 of the drive shaft 2 can be satisfactorily supplied to the high-pressure chamber X side. Therefore, a good sealing effect between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 can be obtained, and the inflow of oil into the low-pressure chamber Y can be reduced, so that the volumetric efficiency can be further improved.
[0056]
further, Claim 1 In the described invention, the notch 52 that opens to the inner peripheral portion of the roller 5 is formed on the end surface of the roller 5 that forms the high-pressure side oil supply passage 7. The passage length can be made shorter than the passage length of the low-pressure side oil supply passage 8, and the passage resistance of the high-pressure side oil supply passage 7 can be made smaller than the passage resistance of the low-pressure side oil supply passage 8. Since it can be made small, the oil is supplied to the low pressure chamber Y while being well supplied to the high pressure chamber X side and a good sealing effect between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 is obtained. Since inflow can be reduced, volumetric efficiency can be improved.
[0057]
In addition, the roller 5 is integrally provided with the blade 6, and the blade 6 is rotatably supported by the cylinder 3. Therefore, the roller 5 revolves without rotating. Since the position in the cylinder chamber 31 is determined, the formation position of the notch 52 can be easily set, the machining of the notch 52 can be easily performed, and oil can be accumulated in the notch 52. Therefore, even when oil in which a large amount of liquid refrigerant is mixed is supplied through the main oil supply passage 22 at the time of start-up, refrigerant lubrication can be reduced by the oil accumulated in the notch 52, and reliability is increased accordingly. Can be improved.
[0058]
Claim 2 In the described invention, since the recessed portion 53 having a closed periphery is formed between the inner and outer periphery of the end surface of the roller 5 forming the high pressure side oil supply passage 7, the passage length of the high pressure side oil supply passage 7 is increased by the recessed portion 53. The passage resistance of the high pressure side oil supply passage 7 is made shorter than the passage length of the low pressure side oil supply passage 8 to be smaller than the passage resistance of the low pressure side oil supply passage 8, so that the outer peripheral surface of the roller 5 and the cylinder chamber 31 While the sealing effect between the inner peripheral surface and the inner peripheral surface can be satisfactorily obtained, the inflow of oil into the low pressure chamber Y can be reduced and the volume efficiency can be improved.
[0059]
In addition, since the concave portion 53 is formed on the end surface of the roller 5 that does not rotate, the formation position of the concave portion 53 can be easily set and processed easily. Further, the concave portion 53 has an inner periphery of the roller 5. Since the recess 53 is used as an oil reservoir, the end face of the roller 5 can be well lubricated.
[0060]
Claim 3 In the described invention, since the slit 54 extending in the direction in which the inner peripheral portion of the roller 5 communicates with the high pressure chamber X is formed on the end surface of the roller 5 forming the high pressure side oil supply passage 7, the slit 54 allows the high pressure. The passage area of the side oil supply passage 7 is enlarged, and the passage resistance of the high pressure side oil supply passage 7 can be made smaller than the passage resistance of the low pressure side oil supply passage 8. Therefore, the seal between the outer peripheral surface of the roller 5 and the inner peripheral surface of the cylinder chamber 31 can be satisfactorily performed.
[Brief description of the drawings]
FIG. 1 of the present invention Reference example The longitudinal cross-sectional view of the compressor lower part side which shows a rotary compressor.
[Figure 2] reference The schematic explanatory drawing which shows the cylinder chamber inside of an example.
FIG. 3 shows a rotary compressor according to the present invention. 1 The longitudinal cross-sectional view of the compressor lower part side which shows an Example.
Fig. 4 1 The schematic explanatory drawing which shows the cylinder chamber inside of an Example.
FIG. 5 shows the rotary compressor of the present invention. 2 The longitudinal cross-sectional view of the compressor lower part side which shows an Example.
FIG. 6 2 The schematic explanatory drawing which shows the cylinder chamber inside of an Example.
FIG. 7 shows the rotary compressor according to the present invention. 3 The longitudinal cross-sectional view of the compressor lower part side which shows an Example.
Fig. 8 3 The schematic explanatory drawing which shows the cylinder chamber inside of an Example.
FIG. 9 shows a rotary compressor of the present invention 4 The longitudinal cross-sectional view of the compressor lower part side which shows an Example.
FIG. 10 4 The schematic explanatory drawing which shows the cylinder chamber inside of an Example.
FIG. 11 is a vertical sectional view of the lower side of a conventional rotary compressor.
FIG. 12 is a schematic explanatory diagram of the inside of a cylinder chamber in the conventional rotary compressor.
[Explanation of symbols]
2 Drive shaft 5 Roller
21 Eccentric part 52 Notch
22 Main oil supply passage 53 Recess
3 cylinder 54 slit
31 Cylinder chamber 6 Blade
34 Support body 7 High-pressure side oil supply passage
35 Receiving groove 8 Low pressure side oil supply passage
41 Fixing member (front head)
42 Fixing member (rear head)
43 Fixing member (middle plate)
44 recess

Claims

An eccentric portion (21) of the drive shaft (2) is inserted into the cylinder chamber (31), and the cylindrical roller (5) revolves with the eccentric rotation of the eccentric portion (21). The cylinder chamber (31) ) In the high-pressure chamber (X) and the low-pressure chamber (Y), and the eccentric portion (21) and the above-described eccentricity (21) from the main oil supply passage (22) provided in the drive shaft (2). In the rotary compressor that supplies oil to the roller (5), the blade (6) is integrally provided on the outer side in the radial direction of the roller (5), and the tip of the protruding side of the blade (6) Part is received in the receiving groove (35) of the support (34) rotatably supported by the cylinder (3) forming the cylinder chamber (31),
The main oil supply passage (22) and the high pressure chamber (X) are connected between the end face of the roller (5) and the fixing member (41, 42, 43) facing the end face of the roller (5). The high pressure side oil supply passage (7), the low pressure side oil supply passage (8) connecting the main oil supply passage (22) and the low pressure chamber (Y) are formed, and the high pressure side oil supply passage (7) is formed. A notch portion (52) that opens to the inner peripheral portion of the roller (5) is formed on the end surface of the roller (5), and the passage resistance of the high-pressure side oil supply passage (7) is reduced to the low-pressure side oil supply passage (8). A rotary compressor that is smaller than the passage resistance.

An eccentric portion (21) of the drive shaft (2) is inserted into the cylinder chamber (31), and the cylindrical roller (5) revolves with the eccentric rotation of the eccentric portion (21). The cylinder chamber (31) ) In the high-pressure chamber (X) and the low-pressure chamber (Y), and the eccentric portion (21) and the above-described eccentricity (21) from the main oil supply passage (22) provided in the drive shaft (2). In the rotary compressor that supplies oil to the roller (5), the blade (6) is integrally provided on the outer side in the radial direction of the roller (5), and the tip of the protruding side of the blade (6) Part is received in the receiving groove (35) of the support (34) rotatably supported by the cylinder (3) forming the cylinder chamber (31),
The main oil supply passage (22) and the high pressure chamber (X) are connected between the end face of the roller (5) and the fixing member (41, 42, 43) facing the end face of the roller (5). The high pressure side oil supply passage (7), the low pressure side oil supply passage (8) connecting the main oil supply passage (22) and the low pressure chamber (Y) are formed, and the high pressure side oil supply passage (7) is formed. A recess (53) having a closed periphery is formed between the inner and outer peripheries of the roller (5) end surface so that the passage resistance of the high-pressure side oil supply passage (7) is greater than the passage resistance of the low-pressure side oil supply passage (8). A small rotary compressor.

An eccentric portion (21) of the drive shaft (2) is inserted into the cylinder chamber (31), and the cylindrical roller (5) revolves with the eccentric rotation of the eccentric portion (21). The cylinder chamber (31) ) In the high-pressure chamber (X) and the low-pressure chamber (Y), and the eccentric portion (21) and the above-described eccentricity (21) from the main oil supply passage (22) provided in the drive shaft (2). In the rotary compressor that supplies oil to the roller (5), the blade (6) is integrally provided on the outer side in the radial direction of the roller (5), and the tip of the protruding side of the blade (6) Part is received in the receiving groove (35) of the support (34) rotatably supported by the cylinder (3) forming the cylinder chamber (31),
The main oil supply passage (22) and the high pressure chamber (X) are connected between the end face of the roller (5) and the fixing member (41, 42, 43) facing the end face of the roller (5). The high pressure side oil supply passage (7), the low pressure side oil supply passage (8) connecting the main oil supply passage (22) and the low pressure chamber (Y) are formed, and the high pressure side oil supply passage (7) is formed. A slit (54) extending in a direction communicating the inner peripheral portion of the roller (5) and the high pressure chamber (X) is formed on the end surface of the roller (5), thereby reducing the passage resistance of the high pressure side oil supply passage (7). The rotary compressor is made smaller than the passage resistance of the low-pressure side oil supply passage (8) .