JP3745915B2

JP3745915B2 - Gas compressor

Info

Publication number: JP3745915B2
Application number: JP06385399A
Authority: JP
Inventors: 敬志神保; 誠井尻; 修八幡原
Original assignee: カルソニックコンプレッサー株式会社
Priority date: 1999-03-10
Filing date: 1999-03-10
Publication date: 2006-02-15
Anticipated expiration: 2019-03-10
Also published as: JP2000257576A

Description

【０００１】
【発明の属する技術分野】
本発明は、カーエアコンシステムの一部として車両に搭載される気体圧縮機に関し、特に、圧縮室内からの高圧冷媒ガスの漏れを低減し、気体圧縮機の性能向上を図ったものである。
【０００２】
【従来の技術】
従来、この種の気体圧縮機は、たとえば図６に示すように、内周略楕円状のシリンダ１を有し、このシリンダ１の両端面にはサイドブロック２、３が取り付けられ、またシリンダ１の内側にはロータ４が横架され、ロータ４はその軸心のロータ軸５とサイドブロックの軸受６、７を介して回転可能に支持されている。
【０００３】
ロータ４の外周面側にはスリット状のベーン溝８が複数形成されており（図７参照）、これらのベーン溝８にはベーン９がそれぞれ装着され、ベーン９はロータ４外周面からシリンダ１内壁に向って出没可能に設けられている。
【０００４】
図７に示すように、シリンダ１の内側はシリンダ１内壁、サイドブロック２、３内面、ロータ４外周面およびベーン９先端側両側面によって複数の小室に仕切られ、この仕切り形成された小室は圧縮室１０と称され、ロータ４が図中矢印イの方向に回転することにより容積の大小変化を繰り返す。圧縮室１０の容積変化が生じると、その容積増加時に、吸入室１１側から圧縮室１０側への低圧冷媒ガスの吸入が行われるとともに、圧縮室１０の容積減少時に、圧縮室１０での冷媒ガスの圧縮と、圧縮室１０から高圧室である吐出室１２側への高圧冷媒ガスの吐出が行なわれる。
【０００５】
すなわち、圧縮室１０の容積が最小から最大となるまでの吸入過程では、吸入室１１内の冷媒ガスが、シリンダ１等の吸入通路１３とこれに連通するサイドブロック２、３の吸入口１４とを介して圧縮室１０側に吸入される。そして、圧縮室１０の容積が最大付近になると、圧縮室１０が吸入口１４から離れて密閉空間となり、圧縮室１０内に低圧冷媒ガスが閉じ込められる。次に、この密閉空間である圧縮室１０の容積が最大から最小に移行すると、その容積減少量に応じて圧縮室１０内の低圧冷媒ガスが圧縮される。さらに、圧縮室１０の容積が最小付近になると、その圧縮された高圧冷媒ガスの圧力によって、シリンダ１の吐出孔１５に取り付けられているリードバルブ１６が開き、かつ圧縮室１０内の高圧冷媒ガスが吐出孔１５からシリンダ１外周面側の吐出チャンバ１７に流出する。吐出チャンバ１７内に流入した高圧冷媒ガスは、さらに、リア側サイドブロック３の吐出通路（図示省略）を通過した後、同サイドブロック３に取り付けられている油分離器１８を通って吐出室１２内に吐出する。
【０００６】
【発明が解決しようとする課題】
ところで、上記のような気体圧縮機の性能向上を図るには、図６中矢印イで示すように、冷媒ガスの圧縮末期付近等における圧縮室１０内の冷媒ガスが、ロータサイド４ａからロータ４とサイドブロック２、３との隙間１９（ロータサイド隙間ともいう。）を通って吸入口１４側に漏れることを防止する必要がある。
【０００７】
このような事情から、従来の気体圧縮機においては、ロータ４とサイドブロック２、３との部品間を組立上詰めることにより、ロータサイド４ａからの吸入口１４側へのガス漏れを少なくしていた。
【０００８】
しかしながら、ロータ４とサイドブロック２、３の両部品間は摺動部分であるため、その両部品間を詰めすぎると、ロータ４の回転時に、ロータ４とサイドブロック２、３の部品どうしのかじりや摩耗等が生じる。したがって、従来の気体圧縮機では、ロータ４とサイドブロック２、３間に、部品どうしのかじりや摩耗の発生防止に必要な最低限の隙間１９を確保する必要があり、このように最低限でも隙間である以上、該隙間１９を通って吸入口１４側に圧縮室１０内の高圧冷媒ガスが漏れることは避けられず、このガス漏れが気体圧縮機の性能向上の妨げとなっていた。
【０００９】
本発明は上述の事情に鑑みてなされたもので、その目的とするところは、圧縮室内からの高圧冷媒ガスの漏れを低減し、気体圧縮機の性能向上を図るのに好適な気体圧縮機を提供することにある。
【００１０】
【課題を解決するための手段】
上記目的を達成するために、請求項１記載の発明は、内周略楕円状のシリンダと、上記シリンダの両端面に取り付けられたサイドブロックと、上記シリンダの内側に回転可能に横架されたロータと、上記ロータの外周面からシリンダ内壁に向って出没可能に設けられた複数のベーンと、上記シリンダ、サイドブロック、ロータおよびベーンによって仕切り形成される圧縮室とを備え、上記ロータの回転により上記圧縮室の容積が大小変化を繰り返し、この圧縮室の容積変化により、低圧部から圧縮室側への冷媒ガスの吸入、圧縮室での冷媒ガスの圧縮、および圧縮室から高圧部側への冷媒ガスの吐出を行う気体圧縮機において、上記ロータとサイドブロックとの隙間に、上記圧縮室から該隙間を通って低圧部側に漏れようとする冷媒ガスのシール手段を設け、上記シール手段は、サイドブロック側に取り付けられるとともに、ロータの軸心回りを囲むように環状に形成されてなり、上記ロータのロータ軸の軸受隙間を介して供給され、かつ、上記シール手段の環内に溜まるオイルを、その環外の圧縮室側に供給する手段として、上記シール手段の環内に一端を開口し、他端を該シール手段の環外に開口するとともに、上記シール手段の環内から該シール手段の環下を潜って環外に抜けるように設けられたオイル通路を備えることを特徴とするものである。
【００１１】
請求項２記載の発明は、内周略楕円状のシリンダと、上記シリンダの両端面に取り付けられたサイドブロックと、上記シリンダの内側に回転可能に横架されたロータと、上記ロータの外周面からシリンダ内壁に向って出没可能に設けられた複数のベーンと、上記シリンダ、サイドブロック、ロータおよびベーンによって仕切り形成される圧縮室とを備え、
上記ロータの回転により上記圧縮室の容積が大小変化を繰り返し、この圧縮室の容積変化により、低圧部から圧縮室側への冷媒ガスの吸入、圧縮室での冷媒ガスの圧縮、および圧縮室から高圧部側への冷媒ガスの吐出を行う気体圧縮機において、上記ロータとサイドブロックとの隙間に、上記圧縮室から該隙間を通って低圧部側に漏れようとする冷媒ガスのシール手段を設け、上記シール手段は、サイドブロック側に取り付けられるとともに、ロータの軸心回りを囲むように環状に形成されてなり、上記ロータのロータ軸の軸受隙間を介して供給され、かつ、上記シール手段の環内に溜まるオイルを、その環外の圧縮室側に供給する手段として、上記シール手段の環内に一端を開口し、他端を該シール手段の環外に開口するとともに、上記シール手段の環内から該シール手段の環下を潜って環外に抜けるように設けられたオイル通路を備えるとともに、上記オイル通路の流出口が、圧縮室の前壁を形成するベーンの近傍に開口していることを特徴とするものである。
【００１２】
請求項３記載の発明は、内周略楕円状のシリンダと、上記シリンダの両端面に取り付けられたサイドブロックと、上記シリンダの内側に回転可能に横架されたロータと、上記ロータの外周面からシリンダ内壁に向って出没可能に設けられた複数のベーンと、上記シリンダ、サイドブロック、ロータおよびベーンによって仕切り形成される圧縮室とを備え、上記ロータの回転により上記圧縮室の容積が大小変化を繰り返し、この圧縮室の容積変化により、低圧部から圧縮室側への冷媒ガスの吸入、圧縮室での冷媒ガスの圧縮、および圧縮室から高圧部側への冷媒ガスの吐出を行う気体圧縮機において、上記ロータとサイドブロックとの隙間に、上記圧縮室から該隙間を通って低圧部側に漏れようとする冷媒ガスのシール手段を設け、上記シール手段は、サイドブロック側に取り付けられ、かつサイドブロックに形成された冷媒ガスの吸入口とシリンダに形成された冷媒ガスの吐出孔との間に位置することを特徴とするものである。
【００１３】
請求項４記載の発明は、内周略楕円状のシリンダと、上記シリンダの両端面に取り付けられたサイドブロックと、上記シリンダの内側に回転可能に横架されたロータと、上記ロータの外周面からシリンダ内壁に向って出没可能に設けられた複数のベーンと、上記シリンダ、サイドブロック、ロータおよびベーンによって仕切り形成される圧縮室とを備え、
上記ロータの回転により上記圧縮室の容積が大小変化を繰り返し、この圧縮室の容積変化により、低圧部から圧縮室側への冷媒ガスの吸入、圧縮室での冷媒ガスの圧縮、および圧縮室から高圧部側への冷媒ガスの吐出を行う気体圧縮機において、上記ロータとサイドブロックとの隙間に、上記圧縮室から該隙間を通って低圧部側に漏れようとする冷媒ガスのシール手段を設け、上記シール手段は、ロータ側に取り付けられ、かつ圧縮室の前壁と後壁を形成する先行のベーンと後行のベーン間に位置するとともに、上記シール手段と上記先行のベーンとの間及び上記シール手段と上記後行のベーンとの間には、上記ロータのロータ軸の軸受隙間を介して供給されたオイルを上記圧縮室に供給するためのオイル通路が設けられていることを特徴とするものである。
【００１５】
本発明では、圧縮室から該隙間を通って低圧部側に漏れようとする冷媒ガスがシール手段によってシールされるので、圧縮室から低圧部側への高圧冷媒ガスの漏洩量が大幅に減少する。
【００１６】
【発明の実施の形態】
以下、本発明に係る気体圧縮機の実施形態について図１乃至図５を基に詳細に説明する。
【００１７】
なお、図１に示した気体圧縮機の基本的な構成、たとえば、気体圧縮機が内周略楕円状のシリンダ１を有し、シリンダ１の両端面にはサイドブロック２、３が取り付けられ、またシリンダ１の内側にはロータ４が回転可能に横架されていること、ロータ４の外周面からはシリンダ１内壁に向って複数のベーン９が出没可能に設けられていること、シリンダ１、サイドブロック２、３、ロータ４およびベーン９によって仕切り形成される圧縮室１０の容積がロータ４の回転により大小変化すると、この容積変化により、低圧室である吸入室１１側から吸気通路１３、吸入口１４を介して圧縮室１０側への低圧冷媒ガスの吸入と、圧縮室１０での冷媒ガスの圧縮、圧縮室１０から吐出孔１５等を通じて高圧室である吐出室１２側への冷媒ガスの吐出が行われること等は従来と同様なため、同一部材には同一符号を付し、その詳細説明は省略する。
【００１８】
図１に示すように、本実施形態の気体圧縮機では、フロント側のサイドブロック２とロータ４との隙間１９、およびリア側のサイドブロック３とロータ４との隙間１９に、シール部材４０を設けており、このシール部材４０は、図２に示すようにロータ４の軸心回りを囲むように環状に形成されているとともに、ロータ端面４ｂの外周縁部より少し内側に位置する。
【００１９】
また、シール部材４０は、ゴム材や樹脂材等の弾性材からなるとともに、サイドブロック２、３のロータ対向面２ａ、３ａに穿設された環状のシール取付溝４１に取り付け固定されている。
【００２０】
ロータ４の端面４ｂには、環状のシール部材４０の環内に溜まるオイルをその環外の圧縮室１０側に供給する手段として、溝状のオイル通路４２を設けている。このオイル通路４２の流入口（一端）４２ａは環状のシール部材４０の環内に開口され、オイル通路４２の流出口（他端）４２ｂは環状のシール部材４０の環外に開口されている。すなわち、このオイル通路４２は、ロータ４側からみると、シール部材４０の環内から該シール部材４０の環下を潜って環外に抜けるように設けられている。
【００２１】
圧縮室１０の前壁１０ａ、後壁１０ｂは、それぞれ先行のベーン９、その後を追う後行のベーン９によって形成されているが、上記のようなオイル通路４２の流出口４２ｂは、特に、圧縮室１０の前壁１０ａを形成する先行ベーン９の近傍に開口されている。なお、オイル通路４２の流入口４２ａはベーン９底部の背圧室付近に開口されている。
【００２２】
次に上記の如く構成された気体圧縮機の動作について図１および図２を用いて説明する。
【００２３】
なお、気体圧縮機の運転を開始すると、ロータ４の回転により圧縮室１０が容積の大小変化を繰り返し、この圧縮室１０の容積変化により、容積増加時に吸入室１１側から圧縮室１０側への低圧冷媒ガスの吸入が行われるとともに、その容積減少時に圧縮室１０での冷媒ガスの圧縮と、圧縮室１０から吐出室１２側への高圧冷媒ガスの吐出が行なわれることは従来と同様であり、その詳細説明は省略する。
【００２４】
図１に示した気体圧縮機によると、上記のような低圧冷媒ガスの吸入過程の段階における圧縮室１０内の圧力は低圧冷媒ガス圧相当の圧力しかないが、冷媒ガスの圧縮末期や吐出過程の段階に入ると、圧縮された高圧冷媒ガスの圧力によって圧縮室１０内の圧力が急激に高くなるため、圧縮室１０内の高圧冷媒ガスがロータ４とサイドブロック２との隙間（ロータサイド隙間１９）を通って低圧部側（吸入口１４、吸入通路１３、吸入室１２側）に漏れようとする。しかし、ロータサイド隙間１９には環状のシール手段４０があり、圧縮室１０からロータサイド隙間１９に流出しようとする高圧冷媒ガスはその大部分がシール手段４０によりシールされ圧縮室１０内に止まる。このため、低圧部側への高圧冷媒ガスの漏洩量が従来に比し減少する。
【００２５】
なお、高圧冷媒ガスは圧縮室１０からシール手段４０の環外を通過して低圧部側へ漏れようとするが、環状のシール部材４０はロータ端面４ａ、４ｂの外周縁部より少し内側に位置するだけであることから、シール手段４０の環外を通過する高圧冷媒ガスの漏洩ルートは極狭い。したがって、そのシール手段４０環外の漏洩ルートを経て低圧部側に移行する高圧冷媒ガスの漏洩量はきわめて微量である。
【００２６】
図１に示した気体圧縮機の運転時には、吐出室１２の底部に溜まっているオイル溜まり２０からサイドブロック２、３やシリンダ１の高圧油穴２１を通じて軸受６、６側に吐出圧相当のオイルが圧送され、さらに軸受６、７に達したオイルは、その軸受６、７隙間の通過時に減圧され中圧となった後、サイドブロック２、３の中圧油穴２２を通過して同サイドブロック２、３のサライ溝２３、２３に供給される。
【００２７】
このようにして供給されたサライ溝２３、２３内のオイルがベーン９底部の背圧室２４に供給され、この背圧室２４のオイル圧とロータ４の遠心力とによりベーン９がシリンダ１内壁に向って押し上げられる。
【００２８】
したがって、ロータ４の回転時には、ベーン９はシリンダ１内壁に押しつけられながら摺動するので、その摺動抵抗の増大や、それによるベーン等の摩耗や動力の増大等を回避する観点から、また、該ベーン９を挟んで隣接した圧縮室１０間の冷媒ガスの漏れを防止する観点から、ベーン９とシリンダ１内壁との摺動部には潤滑オイルを供給する必要がある。また、ベーン９を挟んで隣接した圧縮室１０間の冷媒ガスの漏れを防止するという意味においては、該ベーン９と両サイドブロック２、３との隙間部や、ロータサイド４ａと両サイドブロック２、３との隙間部（ロータサイド隙間１９）や、シリンダ１の楕円短径部とロータ４の外周部との隙間部にもオイルを供給する必要がある。
【００２９】
ここで、ベーン９とシリンダ１内壁との摺動部への潤滑オイル供給について説明すると、これは主に次のように行われる。
【００３０】
冷媒ガスの吸入過程段階にある圧縮室１０内の圧力は低圧冷媒ガス圧相当であって、サライ溝２３、２３内のオイル圧よりも低いため、サライ溝２３、２３に一度入ったオイルは、さらにロータサイド隙間１９を通って吸入過程段階にある圧縮室１０側に移行しようとする。このとき、オイルの流れ方向の先には環状のシール部材４０が存在するが、この環状のシール部材４０は圧縮室１０側へのオイル供給の障害にはならない。すなわち、サライ溝２３、２３から流出したオイルは、環状のシール部材４０の環内４０ａから直ちにオイル通路４２を通って該環状のシール部材４０の環外４０ｂに容易に流出し圧縮室１０側に移行して、ベーン９とシリンダ１内壁との摺動部やベーン９と両サイドブロック２、３との隙間に供給される。
【００３１】
また、圧縮室１０は先行のベーン９が吸入口１４を通過した直後から次第にその形が作られて行くが、本実施形態では、その先行のベーン９の近傍にオイル通路４２の流出口４２ｂが開口されているので、圧縮室１０の形が作られる比較的早い段階（低圧冷媒ガスの吸入初期過程）からオイル通路４２を通じて圧縮室１０側にオイルが供給される。このため、圧縮室１０側へオイル供給でき、ベーン９とシリンダ１内壁との摺動部には十分なオイルが供給され、摺動部の潤滑不良や、圧縮室１０間の冷媒ガスの漏れによる体積効率の低下が生じることはない。
【００３２】
以上のように、本実施形態の気体圧縮機にあっては、ロータ４とサイドブロック２、３との隙間１９に、圧縮室１０から該隙間１９を通って低圧部側に漏れようとする冷媒ガスのシール部材４０を設けたものである。このため、ロータ４とサイドブロック２、３の両部品間を詰めることなく、圧縮室１０から低圧部側への高圧冷媒ガスの漏洩量が大幅に減少し、従来この種のガス漏れにより制限されていた気体圧縮機の性能を飛躍的に向上させることができる。
【００３３】
図３はシール部材４０の他の実施形態を示したものである。同図のシール部材４０もまた上記実施形態のものと同じく、サイドブロック２、３のロータ対向面２ａ、３ａに取り付けられているが、その形状が上記実施形態のものとは異なり棒状に形成されている。また、このシール部材４０は、サイドブロック２、３に形成されている低圧冷媒ガスの吸入口１４と、シリンダ１に形成されている冷媒ガスの吐出孔１５との間に位置し、かつシリンダ１の楕円短軸付近にのみ部分的に配置されている。このような形状のシール手段４０によっても、圧縮室１０からロータサイド隙間１９を通って低圧部側へ漏れる高圧冷媒ガスをシールすることができる。なお、上述の実施形態ではシール部材４０が環状であるため、その環内から環外の圧縮室１０側にオイルを抜く必要があったが、この実施形態のシール部材４０は、環状でなく、吸入口１４と吐出孔１５との間にのみ部分的に配置されるものであるから、本シール手段４０がサライ溝２３から圧縮室１０側へのオイル供給の妨げとなることはなく、上記実施形態のように別途オイル通路４２を設けなくとも、圧縮室１０側へのオイル供給は十分確保されている。
【００３４】
図４もまたシール部材４０の他の実施形態を示したものである。同図のシール部材４０は上述の実施形態のものと異なり、ロータ端面４ｂに取り付けられているとともに、圧縮室１０の前壁１０ａと後壁１０ｂを形成する先行と後行のベーン９、９間に位置する。また、このシール部材４０は、輪型に形成され、その輪の外輪がロータ端面４ｂの外周縁部より少し内側の位置やベーン９の近傍にまで達するように形成されている。なお、先行のベーン９と後行のベーン９とにより挟まれたロータ端面４ｂの領域を１つのベーン区画領域とすると、本実施形態の気体圧縮機の場合、ベーン９の数が５枚であるから、ベーン区画領域は５つ存在する。本実施形態のシール手段４０は、この５つのベーン区画領域ごとに１つずつ配置されている。このような形態のシール手段４０によっても、圧縮室１０からロータサイド隙間１９を通って低圧部側へ漏れる高圧冷媒ガスをシールすることができる。なお、本シール手段４０の場合は、シール手段４０とベーン９との隙間がオイル通路４２となり、このオイル通路４２を介してサライ溝２３から圧縮室１０側へのオイルの供給が行われる。
【００３５】
【発明の効果】
本発明に係る気体圧縮機にあっては、上記の如くロータとサイドブロックとの隙間に、圧縮室から該隙間を通って低圧部側に漏れようとする冷媒ガスのシール手段を設けたため、ロータとサイドブロックの両部品間を詰めることなく、圧縮室から低圧部側への高圧冷媒ガスの漏洩量が大幅に減少し、従来この種のガス漏れにより制限されていた気体圧縮機の性能を飛躍的に向上させることができる等の効果がある。
【００３６】
また、本発明によると、気体圧縮機の性能向上に伴い、その向上分だけ圧縮機全体の容量を小型にすることができ、容量低減による動力の削減等をも図れ、エンジンへの負荷の小さい気体圧縮機を提供できるほか、車両の軽量化にも寄与する。
【図面の簡単な説明】
【図１】本発明に係る気体圧縮機の一実施形態を示す断面図。
【図２】図１のＡ−Ａ線断面図。
【図３】本発明におけるシール手段の他の実施形態を示した説明図。
【図４】本発明におけるシール手段の他の実施形態を示した説明図。
【図５】従来の気体圧縮機の断面図。
【図６】図５のＡ−Ａ線断面図。
【符号の説明】
１シリンダ
２フロント側のサイドブロック
２ａフロント側サイドブロックのロータ対向面
３リア側のサイドブロック
３ａリア側サイドブロックのロータ対向面
４ロータ
４ａロータサイド
４ｂロータ端面
５ロータ軸
６、７軸受
８ベーン溝
９ベーン
１０圧縮室
１０ａ圧縮室の前壁
１０ｂ圧縮室の後壁
１１吸入室
１２吐出室
１３吸入通路
１４吸入口
１５吐出孔
１６リードバルブ
１７吐出チャンバ
１８油分離器
１９ロータサイド隙間
２０オイル溜まり
２１高圧油穴
２２中圧油穴
２３サライ溝
２４背圧室
４０シール部材（シール手段）
４１シール取付溝
４２オイル通路
４２ａオイル通路の流入口（一端）
４２ｂオイル通路の流出口（他端）[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a gas compressor mounted on a vehicle as a part of a car air conditioner system, and in particular, reduces leakage of high-pressure refrigerant gas from a compression chamber and improves the performance of the gas compressor.
[0002]
[Prior art]
Conventionally, this type of gas compressor has, for example, a cylinder 1 having a substantially elliptical inner periphery as shown in FIG. 6, and side blocks 2 and 3 are attached to both end faces of the cylinder 1. The rotor 4 is horizontally mounted inside the rotor, and the rotor 4 is rotatably supported via a rotor shaft 5 at the center of the rotor 4 and bearings 6 and 7 of the side blocks.
[0003]
A plurality of slit-like vane grooves 8 are formed on the outer peripheral surface side of the rotor 4 (see FIG. 7), and vanes 9 are respectively attached to these vane grooves 8. The vanes 9 are connected to the cylinder 1 from the outer peripheral surface of the rotor 4. It is provided so that it can invade toward the inner wall.
[0004]
As shown in FIG. 7, the inside of the cylinder 1 is partitioned into a plurality of small chambers by the inner wall of the cylinder 1, the side blocks 2 and 3, the outer peripheral surface of the rotor 4, and both side surfaces on the tip side of the vane 9. It is called a chamber 10, and the volume of the rotor 4 changes repeatedly as the rotor 4 rotates in the direction of arrow A in the figure. When the volume change of the compression chamber 10 occurs, the low-pressure refrigerant gas is sucked from the suction chamber 11 side to the compression chamber 10 side when the volume increases, and the refrigerant in the compression chamber 10 when the volume of the compression chamber 10 decreases. Gas compression and high-pressure refrigerant gas discharge from the compression chamber 10 to the discharge chamber 12 side, which is a high-pressure chamber, are performed.
[0005]
That is, in the suction process until the volume of the compression chamber 10 reaches the maximum from the minimum, the refrigerant gas in the suction chamber 11 flows into the suction passage 13 such as the cylinder 1 and the suction ports 14 of the side blocks 2 and 3 communicating with the suction passage 13. And is sucked into the compression chamber 10 side. When the volume of the compression chamber 10 becomes near the maximum, the compression chamber 10 is separated from the suction port 14 and becomes a sealed space, and the low-pressure refrigerant gas is confined in the compression chamber 10. Next, when the volume of the compression chamber 10 that is the sealed space is shifted from the maximum to the minimum, the low-pressure refrigerant gas in the compression chamber 10 is compressed according to the volume reduction amount. Further, when the volume of the compression chamber 10 becomes near the minimum, the pressure of the compressed high-pressure refrigerant gas opens the reed valve 16 attached to the discharge hole 15 of the cylinder 1 and the high-pressure refrigerant gas in the compression chamber 10 Flows out from the discharge hole 15 to the discharge chamber 17 on the outer peripheral surface side of the cylinder 1. The high-pressure refrigerant gas that has flowed into the discharge chamber 17 further passes through a discharge passage (not shown) of the rear side block 3 and then passes through an oil separator 18 attached to the side block 3. Discharge inside.
[0006]
[Problems to be solved by the invention]
By the way, in order to improve the performance of the gas compressor as described above, as indicated by an arrow A in FIG. 6, the refrigerant gas in the compression chamber 10 near the end of the compression of the refrigerant gas is transferred from the rotor side 4a to the rotor 4. It is necessary to prevent leakage to the suction port 14 side through a gap 19 (also referred to as a rotor side gap) between the side blocks 2 and 3.
[0007]
For this reason, in the conventional gas compressor, gas leakage from the rotor side 4a to the inlet 14 side is reduced by assembling the parts between the rotor 4 and the side blocks 2 and 3 in assembly. It was.
[0008]
However, since both the parts of the rotor 4 and the side blocks 2 and 3 are sliding parts, if the gap between the two parts is excessive, the parts of the rotor 4 and the side blocks 2 and 3 are galled when the rotor 4 rotates. And wear. Therefore, in the conventional gas compressor, it is necessary to secure a minimum gap 19 necessary for preventing the occurrence of galling and wear between components between the rotor 4 and the side blocks 2 and 3, and at least as described above. As long as it is a gap, it is inevitable that high-pressure refrigerant gas in the compression chamber 10 leaks to the suction port 14 side through the gap 19, and this gas leakage hinders improvement in performance of the gas compressor.
[0009]
The present invention has been made in view of the above-described circumstances, and an object thereof is to provide a gas compressor suitable for reducing the leakage of high-pressure refrigerant gas from the compression chamber and improving the performance of the gas compressor. It is to provide.
[0010]
[Means for Solving the Problems]
In order to achieve the above-mentioned object, the invention described in claim 1 is characterized in that a substantially elliptical inner cylinder, side blocks attached to both end faces of the cylinder, and rotatably mounted inside the cylinder. A rotor, a plurality of vanes provided so as to protrude from the outer peripheral surface of the rotor toward the inner wall of the cylinder, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vane, and by rotation of the rotor The volume of the compression chamber repeatedly changes in size, and due to the volume change of the compression chamber, the suction of the refrigerant gas from the low pressure portion to the compression chamber side, the compression of the refrigerant gas in the compression chamber, and the compression chamber to the high pressure portion side. In a gas compressor that discharges refrigerant gas, a refrigerant gas that tends to leak into the gap between the rotor and the side block from the compression chamber to the low-pressure part side through the gap. Only set Le means, the sealing means may be attached to the side block side, is formed annularly to surround the axial center of the rotor, it is supplied through the bearing clearance of the rotor shaft of the rotor, and As a means for supplying oil accumulated in the ring of the sealing means to the compression chamber side outside the ring, one end is opened in the ring of the sealing means and the other end is opened outside the ring of the sealing means. And an oil passage provided so as to dive from the inside of the ring of the seal means to the outside of the ring under the ring of the seal means .
[0011]
According to a second aspect of the present invention, there is provided a substantially elliptical inner peripheral cylinder, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and an outer peripheral face of the rotor. A plurality of vanes provided so as to be able to protrude from the inner wall toward the cylinder inner wall, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vanes,
The volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and by the volume change of the compression chamber, the refrigerant gas is sucked from the low pressure portion to the compression chamber, the refrigerant gas is compressed in the compression chamber, and the compression chamber In the gas compressor that discharges the refrigerant gas to the high-pressure part side, a refrigerant gas sealing means for leaking from the compression chamber to the low-pressure part side through the gap is provided in the gap between the rotor and the side block. The sealing means is attached to the side block side, and is formed in an annular shape so as to surround the rotor shaft center. The sealing means is supplied via a bearing clearance of the rotor shaft of the rotor, and the sealing means As means for supplying the oil accumulated in the ring to the compression chamber side outside the ring, one end is opened in the ring of the sealing means, the other end is opened outside the ring of the sealing means, and the seal And an oil passage provided so as to dive under the seal means from the inside of the ring means and out of the ring, and the outlet of the oil passage is in the vicinity of the vane forming the front wall of the compression chamber It is characterized by opening .
[0012]
According to a third aspect of the present invention, there is provided a substantially elliptical inner cylinder, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and an outer peripheral face of the rotor. A plurality of vanes provided so as to be able to protrude from the cylinder toward the inner wall of the cylinder, and a compression chamber that is partitioned by the cylinder, the side block, the rotor, and the vane, and the volume of the compression chamber is changed by the rotation of the rotor. This is a gas compression that sucks refrigerant gas from the low pressure part to the compression chamber side, compresses refrigerant gas in the compression chamber, and discharges refrigerant gas from the compression chamber to the high pressure part side by changing the volume of the compression chamber. In the machine, in the gap between the rotor and the side block, there is provided a refrigerant gas sealing means for leaking from the compression chamber to the low pressure part side through the gap, and the seal Stage is mounted to the side block side and is characterized in that located between the discharge hole of the refrigerant gas formed in the suction port and the cylinder of the refrigerant gas formed in the side block.
[0013]
According to a fourth aspect of the present invention, there is provided a substantially elliptical inner cylinder, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and an outer peripheral face of the rotor. A plurality of vanes provided so as to be able to protrude from the inner wall toward the cylinder inner wall, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vanes,
The volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and by the volume change of the compression chamber, the refrigerant gas is sucked from the low pressure portion to the compression chamber, the refrigerant gas is compressed in the compression chamber, and the compression chamber In the gas compressor that discharges the refrigerant gas to the high-pressure part side, a refrigerant gas sealing means for leaking from the compression chamber to the low-pressure part side through the gap is provided in the gap between the rotor and the side block. The sealing means is mounted on the rotor side and is located between the preceding vane and the trailing vane forming the front wall and the rear wall of the compression chamber, and between the sealing means and the preceding vane and between the said sealing means and said trailing vane, and characterized in that the supplied oil through the bearing clearance of the rotor shaft of the rotor oil passage for supplying to said compression chamber is provided Is shall.
[0015]
In the present invention, the refrigerant gas that is about to leak from the compression chamber through the gap to the low pressure part side is sealed by the sealing means, so that the amount of leakage of the high pressure refrigerant gas from the compression chamber to the low pressure part side is greatly reduced. .
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of a gas compressor according to the present invention will be described in detail with reference to FIGS. 1 to 5.
[0017]
In addition, the basic structure of the gas compressor shown in FIG. 1, for example, the gas compressor has a cylinder 1 having a substantially inner circumference, and side blocks 2 and 3 are attached to both end faces of the cylinder 1. Further, the rotor 4 is rotatably mounted on the inner side of the cylinder 1, a plurality of vanes 9 are provided from the outer peripheral surface of the rotor 4 toward the inner wall of the cylinder 1, and the cylinder 1, When the volume of the compression chamber 10 partitioned by the side blocks 2 and 3, the rotor 4, and the vanes 9 is changed by the rotation of the rotor 4, the volume change causes the intake passage 13 and the suction passage from the suction chamber 11 side, which is a low-pressure chamber. The suction of the low-pressure refrigerant gas to the compression chamber 10 side through the port 14, the compression of the refrigerant gas in the compression chamber 10, the refrigerant gas from the compression chamber 10 to the discharge chamber 12 side that is the high-pressure chamber through the discharge holes 15, etc. Vomiting Because it is similar to the prior art that such be done, the same reference numerals denote the same members, and detailed description thereof will be omitted.
[0018]
As shown in FIG. 1, in the gas compressor of the present embodiment, seal members 40 are provided in the gap 19 between the front side block 2 and the rotor 4 and the gap 19 between the rear side block 3 and the rotor 4. As shown in FIG. 2, the seal member 40 is formed in an annular shape so as to surround the axis of the rotor 4, and is located slightly inside the outer peripheral edge of the rotor end surface 4b.
[0019]
The seal member 40 is made of an elastic material such as a rubber material or a resin material, and is fixedly attached to an annular seal attachment groove 41 formed in the rotor facing surfaces 2a and 3a of the side blocks 2 and 3.
[0020]
The end face 4b of the rotor 4 is provided with a groove-like oil passage 42 as means for supplying oil accumulated in the ring of the annular seal member 40 to the compression chamber 10 side outside the ring. An inlet (one end) 42 a of the oil passage 42 is opened in the ring of the annular seal member 40, and an outlet (other end) 42 b of the oil passage 42 is opened outside the ring of the annular seal member 40. That is, when viewed from the rotor 4 side, the oil passage 42 is provided so as to dive from the inside of the ring of the seal member 40 under the ring of the seal member 40 and out of the ring.
[0021]
The front wall 10a and the rear wall 10b of the compression chamber 10 are respectively formed by the preceding vane 9 and the subsequent vane 9 following the vane 9, but the outlet 42b of the oil passage 42 as described above is particularly compressed. An opening is formed in the vicinity of the preceding vane 9 that forms the front wall 10 a of the chamber 10. The inlet 42a of the oil passage 42 is opened near the back pressure chamber at the bottom of the vane 9.
[0022]
Next, the operation of the gas compressor configured as described above will be described with reference to FIGS.
[0023]
When the operation of the gas compressor is started, the compression chamber 10 repeatedly changes in volume due to the rotation of the rotor 4, and the volume change of the compression chamber 10 causes the suction chamber 11 to move toward the compression chamber 10 when the volume increases. The suction of the low-pressure refrigerant gas is performed, and the compression of the refrigerant gas in the compression chamber 10 and the discharge of the high-pressure refrigerant gas from the compression chamber 10 to the discharge chamber 12 when the volume is reduced are the same as before. Detailed description thereof will be omitted.
[0024]
According to the gas compressor shown in FIG. 1, the pressure in the compression chamber 10 at the stage of the low-pressure refrigerant gas suction process is only a pressure corresponding to the low-pressure refrigerant gas pressure. In this stage, the pressure in the compression chamber 10 suddenly increases due to the pressure of the compressed high-pressure refrigerant gas, so that the high-pressure refrigerant gas in the compression chamber 10 flows between the rotor 4 and the side block 2 (rotor side gap). 19) to leak to the low pressure part side (suction port 14, suction passage 13, suction chamber 12 side). However, the rotor-side gap 19 has an annular sealing means 40, and most of the high-pressure refrigerant gas that flows out of the compression chamber 10 into the rotor-side gap 19 is sealed by the sealing means 40 and stops in the compression chamber 10. For this reason, the amount of leakage of the high-pressure refrigerant gas to the low-pressure part side is reduced as compared with the conventional case.
[0025]
The high-pressure refrigerant gas tries to leak from the compression chamber 10 to the low-pressure part side through the outside of the seal means 40, but the annular seal member 40 is located slightly inside the outer peripheral edge of the rotor end faces 4a and 4b. Therefore, the leakage route of the high-pressure refrigerant gas passing outside the ring of the sealing means 40 is extremely narrow. Therefore, the leakage amount of the high-pressure refrigerant gas that moves to the low-pressure part side through the leakage route outside the sealing means 40 is extremely small.
[0026]
During operation of the gas compressor shown in FIG. 1, oil corresponding to the discharge pressure is transferred from the oil reservoir 20 accumulated at the bottom of the discharge chamber 12 to the bearings 6 and 6 through the high pressure oil holes 21 of the side blocks 2 and 3 and the cylinder 1. Is further pumped and the oil that has reached the bearings 6 and 7 is reduced in pressure when passing through the clearances of the bearings 6 and 7, and then passes through the intermediate pressure oil holes 22 of the side blocks 2 and 3. It is supplied to the Sarai grooves 23 and 23 of the blocks 2 and 3.
[0027]
The oil in the Sarai grooves 23, 23 thus supplied is supplied to the back pressure chamber 24 at the bottom of the vane 9, and the vane 9 is connected to the inner wall of the cylinder 1 by the oil pressure in the back pressure chamber 24 and the centrifugal force of the rotor 4. It is pushed up toward.
[0028]
Accordingly, when the rotor 4 is rotated, the vane 9 slides while being pressed against the inner wall of the cylinder 1. From the viewpoint of avoiding an increase in the sliding resistance, an abrasion of the vane and the like, and an increase in power. From the viewpoint of preventing refrigerant gas from leaking between the compression chambers 10 adjacent to each other with the vane 9 interposed therebetween, it is necessary to supply lubricating oil to the sliding portion between the vane 9 and the inner wall of the cylinder 1. Further, in the sense of preventing the refrigerant gas from leaking between the compression chambers 10 adjacent to each other with the vane 9 interposed therebetween, the gap between the vane 9 and both side blocks 2 and 3, the rotor side 4 a and both side blocks 2. 3 (rotor side gap 19) and the gap between the elliptical short diameter portion of the cylinder 1 and the outer peripheral portion of the rotor 4 must be supplied.
[0029]
Here, a description will be given of the supply of the lubricating oil to the sliding portion between the vane 9 and the inner wall of the cylinder 1. This is mainly performed as follows.
[0030]
Since the pressure in the compression chamber 10 in the refrigerant gas suction process is equivalent to the low-pressure refrigerant gas pressure and is lower than the oil pressure in the salai grooves 23, 23, the oil once entered in the salai grooves 23, 23 is Furthermore, it tries to shift to the compression chamber 10 side in the suction process stage through the rotor side gap 19. At this time, an annular seal member 40 exists at the tip of the oil flow direction, but this annular seal member 40 does not hinder oil supply to the compression chamber 10 side. That is, oil that has flowed out of the saray grooves 23, 23 easily flows out from the inner ring 40 a of the annular seal member 40 through the oil passage 42 to the outer ring 40 b of the annular seal member 40 and enters the compression chamber 10 side. It shifts and is supplied to the sliding part between the vane 9 and the inner wall of the cylinder 1 and the gap between the vane 9 and both side blocks 2 and 3.
[0031]
In addition, the compression chamber 10 is gradually formed immediately after the preceding vane 9 passes through the suction port 14. In this embodiment, the outlet 42 b of the oil passage 42 is provided in the vicinity of the preceding vane 9. Since the opening is made, oil is supplied to the compression chamber 10 through the oil passage 42 from a relatively early stage (the initial suction process of the low-pressure refrigerant gas) when the shape of the compression chamber 10 is formed. For this reason, oil can be supplied to the compression chamber 10 side, and sufficient oil is supplied to the sliding portion between the vane 9 and the inner wall of the cylinder 1 due to poor lubrication of the sliding portion or leakage of refrigerant gas between the compression chambers 10. There is no reduction in volumetric efficiency.
[0032]
As described above, in the gas compressor of the present embodiment, the refrigerant that is about to leak into the gap 19 between the rotor 4 and the side blocks 2 and 3 from the compression chamber 10 through the gap 19 to the low pressure portion side. A gas sealing member 40 is provided. For this reason, the leakage amount of the high-pressure refrigerant gas from the compression chamber 10 to the low-pressure part side is greatly reduced without closing between the rotor 4 and the side blocks 2 and 3, which is conventionally limited by this type of gas leakage. The performance of the existing gas compressor can be improved dramatically.
[0033]
FIG. 3 shows another embodiment of the seal member 40. The seal member 40 in the figure is also attached to the rotor facing surfaces 2a and 3a of the side blocks 2 and 3 in the same manner as in the above embodiment, but the shape thereof is different from that in the above embodiment and is formed in a bar shape. ing. The seal member 40 is located between the low-pressure refrigerant gas inlet 14 formed in the side blocks 2 and 3 and the refrigerant gas discharge hole 15 formed in the cylinder 1. It is partially arranged only near the elliptical minor axis. The sealing means 40 having such a shape can also seal the high-pressure refrigerant gas leaking from the compression chamber 10 through the rotor side gap 19 to the low-pressure part side. In the above-described embodiment, since the seal member 40 is annular, it is necessary to drain oil from the ring to the compression chamber 10 side outside the ring. However, the seal member 40 of this embodiment is not annular, Since the seal means 40 is only partially disposed between the suction port 14 and the discharge hole 15, the seal means 40 does not hinder oil supply from the Sarai groove 23 to the compression chamber 10 side. Even if the oil passage 42 is not separately provided as in the embodiment, the oil supply to the compression chamber 10 side is sufficiently ensured.
[0034]
FIG. 4 also shows another embodiment of the seal member 40. Unlike the above-described embodiment, the seal member 40 in the same figure is attached to the rotor end surface 4b and between the leading and trailing vanes 9, 9 forming the front wall 10a and the rear wall 10b of the compression chamber 10. Located in. The seal member 40 is formed in a ring shape so that the outer ring of the ring reaches a position slightly inside the outer peripheral edge of the rotor end surface 4b and the vicinity of the vane 9. If the region of the rotor end surface 4b sandwiched between the preceding vane 9 and the succeeding vane 9 is defined as one vane partition region, the number of vanes 9 is five in the case of the gas compressor of this embodiment. Therefore, there are five vane partition areas. The sealing means 40 of this embodiment is arrange | positioned 1 each for every five vane division area. The high-pressure refrigerant gas leaking from the compression chamber 10 through the rotor side gap 19 to the low-pressure part side can be sealed also by the sealing means 40 having such a configuration. In the case of the present sealing means 40, the gap between the sealing means 40 and the vane 9 serves as an oil passage 42, and oil is supplied from the Sarai groove 23 to the compression chamber 10 via the oil passage 42.
[0035]
【The invention's effect】
In the gas compressor according to the present invention, since the gap between the rotor and the side block as described above is provided with the refrigerant gas sealing means that attempts to leak from the compression chamber to the low-pressure part side through the gap, the rotor The amount of high-pressure refrigerant gas leaking from the compression chamber to the low-pressure part side is greatly reduced without packing between the two parts of the side block and the performance of the gas compressor, which has been limited by this type of gas leakage. There is an effect that it can be improved.
[0036]
Further, according to the present invention, along with the improvement of the performance of the gas compressor, the capacity of the entire compressor can be reduced by the amount of the improvement, the power can be reduced by reducing the capacity, and the load on the engine is small. In addition to providing a gas compressor, it also contributes to lighter vehicles.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing an embodiment of a gas compressor according to the present invention.
FIG. 2 is a cross-sectional view taken along line AA in FIG.
FIG. 3 is an explanatory view showing another embodiment of the sealing means in the present invention.
FIG. 4 is an explanatory view showing another embodiment of the sealing means in the present invention.
FIG. 5 is a cross-sectional view of a conventional gas compressor.
6 is a cross-sectional view taken along line AA in FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Cylinder 2 Front side block 2a Front side block rotor facing surface 3 Rear side block 3a Rear side block rotor facing surface 4 Rotor 4a Rotor side 4b Rotor end surface 5 Rotor shaft 6, 7 Bearing 8 Vane groove 9 Vane 10 Compression chamber 10a Front wall 10b of compression chamber Rear wall 11 of compression chamber Suction chamber 12 Discharge chamber 13 Suction passage 14 Suction port 15 Discharge hole 16 Reed valve 17 Discharge chamber 18 Oil separator 19 Rotor side clearance 20 Oil reservoir 21 High pressure oil hole 22 Medium pressure oil hole 23 Saray groove 24 Back pressure chamber 40 Seal member (sealing means)
41 Seal mounting groove 42 Oil passage 42a Oil passage inlet (one end)
42b Oil passage outlet (other end)

Claims

An inner cylinder with a substantially elliptical shape, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and can protrude from the outer peripheral surface of the rotor toward the inner wall of the cylinder A plurality of vanes provided in the chamber, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vanes,
The volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and by the volume change of the compression chamber, the refrigerant gas is sucked from the low pressure portion to the compression chamber, the refrigerant gas is compressed in the compression chamber, and the compression chamber In the gas compressor that discharges the refrigerant gas to the high-pressure part side,
The gap between the rotor and the side blocks, set the sealing means of the refrigerant gas to be to leak to the low pressure side through the gap from the compression chamber,
The sealing means is attached to the side block side, and is formed in an annular shape so as to surround the axis of the rotor,
One end is opened in the ring of the sealing means as means for supplying oil supplied through the bearing gap of the rotor shaft of the rotor and collecting in the ring of the sealing means to the compression chamber side outside the ring. And the other end is opened to the outside of the ring of the sealing means, and an oil passage is provided so as to dive under the ring of the sealing means from the inside of the ring of the sealing means and to come out of the ring. Gas compressor.

An inner cylinder with a substantially elliptical shape, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and can protrude from the outer peripheral surface of the rotor toward the inner wall of the cylinder A plurality of vanes provided in the chamber, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vanes,
The volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and by the volume change of the compression chamber, the refrigerant gas is sucked from the low pressure portion to the compression chamber, the refrigerant gas is compressed in the compression chamber, and the compression chamber In the gas compressor that discharges the refrigerant gas to the high-pressure part side,
Provided in the gap between the rotor and the side block is a refrigerant gas sealing means for leaking from the compression chamber to the low pressure part side through the gap,
The sealing means is attached to the side block side, and is formed in an annular shape so as to surround the axis of the rotor,
One end is opened in the ring of the sealing means as means for supplying oil supplied through the bearing gap of the rotor shaft of the rotor and collecting in the ring of the sealing means to the compression chamber side outside the ring. And having an oil passage provided to open the other end outside the ring of the sealing means and to dive under the ring of the sealing means from inside the ring of the sealing means and to come out of the ring,
A gas compressor characterized in that the outlet of the oil passage opens in the vicinity of a vane forming the front wall of the compression chamber .

An inner cylinder with a substantially elliptical shape, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and can protrude from the outer peripheral surface of the rotor toward the inner wall of the cylinder A plurality of vanes provided in the chamber, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vanes,
The volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and by the volume change of the compression chamber, the refrigerant gas is sucked from the low pressure portion to the compression chamber, the refrigerant gas is compressed in the compression chamber, and the compression chamber In the gas compressor that discharges the refrigerant gas to the high-pressure part side,
Provided in the gap between the rotor and the side block is a refrigerant gas sealing means for leaking from the compression chamber to the low pressure part side through the gap,
The gas compressor is characterized in that the sealing means is attached to the side block side and located between a refrigerant gas inlet formed in the side block and a refrigerant gas discharge hole formed in the cylinder .

An inner cylinder with a substantially elliptical shape, side blocks attached to both end faces of the cylinder, a rotor horizontally mounted on the inner side of the cylinder, and can protrude from the outer peripheral surface of the rotor toward the inner wall of the cylinder A plurality of vanes provided in the chamber, and a compression chamber partitioned by the cylinder, the side block, the rotor, and the vanes,
The volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and by the volume change of the compression chamber, the refrigerant gas is sucked from the low pressure portion to the compression chamber, the refrigerant gas is compressed in the compression chamber, and the compression chamber In the gas compressor that discharges the refrigerant gas to the high-pressure part side,
Provided in the gap between the rotor and the side block is a refrigerant gas sealing means for leaking from the compression chamber to the low pressure part side through the gap,
The sealing means is attached to the rotor side and located between the preceding vane and the trailing vane forming the front wall and the rear wall of the compression chamber,
In order to supply oil supplied through the bearing clearance of the rotor shaft of the rotor to the compression chamber between the sealing means and the preceding vane and between the sealing means and the following vane. A gas compressor characterized in that an oil passage is provided .