JP3783313B2

JP3783313B2 - Swash plate compressor

Info

Publication number: JP3783313B2
Application number: JP02542197A
Authority: JP
Inventors: 勇人池田; 亨竹市; 徹也高嶋
Original assignee: Toyota Industries Corp
Current assignee: Toyota Industries Corp
Priority date: 1997-02-07
Filing date: 1997-02-07
Publication date: 2006-06-07
Anticipated expiration: 2017-02-07
Also published as: JPH10220346A

Description

【０００１】
【発明の属する技術分野】
この発明は例えば車両空調装置に用いられる両頭ピストン型の斜板式圧縮機に関するものである。さらに詳しくは斜板式圧縮機のシリンダブロックに設けた吸入口から斜板室に吸入されたガスをフロント及びリヤの複数対の吸入通路を介してフロント及びリヤの吸入室へそれぞれ円滑に導くことができるガスの吸入構造に関するものである。
【０００２】
【従来の技術】
一般に、両頭ピストン型の斜板式圧縮機においては、複数のシリンダボアを有するシリンダブロックの前後両端面に吸入室と吐出室を区画形成するフロント及びリヤのハウジングが接合固定されている。シリンダブロックの中央部に形成した斜板室には駆動シャフトにより揺動回転する斜板が収容され、該斜板の前後両側面にはシューを介して前記シリンダボア内に収容された両頭ピストンが係留されている。前記シリンダブロックには前記斜板室へガスを導入する吸入口が設けられ、斜板室内のガスを前記フロント及びリヤの吸入室へ導くための複数対の吸入通路が設けられている。そして、該両頭ピストンが斜板の回転運動により往復動されると、前記吸入室からシリンダボア内の圧縮室へガスが吸入され、該圧縮室内で圧縮されたガスは前記吐出室へ吐出される。
【０００３】
図６に示すように、前記シリンダブロック１１，１２は中央部に斜板室２１を形成する関係で、フロント及びリヤ側に一対設けられ、リヤ側のシリンダブロック１２に外部冷媒回路から斜板室２１にガスを吸入するための吸入口１２２が設けられている。又、図６，７に示すようにシリンダブロック１１，１２には斜板室２１からフロント及びリヤのハウジング１５，１６内に形成した吸入室２４，２５へガスを導く吸入通路３０１，３０２，３０３、３１１，３１２，３１３がそれぞれ設けられている。なお、符号１７はシリンダブロック１１，１２及び両ハウジング１５，１６の締付ボルト、１８は駆動シャフト、２２は両頭ピストン、３４は駆動シャフト１８に嵌合固定されてピストン２２を往復動する斜板である。
【０００４】
【発明が解決しようとする課題】
ところが、上記斜板式圧縮機のガスの吸入構造においては、吸入口１２２から斜板室２１へガスが吸入される際、各対の吸入通路３０１，３０２，３０３、３１１，３１２，３１３へ吸入されるガス量が均等になり難いという問題があった。即ち、前述したように吸入口１２２が斜板室２１の中心よりリヤ側へ変位して設けられているので、斜板３４の外周面が吸入口１２２と対向する位置にあるときには一時的にガスの斜板室２１への導入量が制限される。斜板３４が図６に示すようにフロント側へ傾斜した状態では吸入口１２２から斜板室２１へ導入されたガスはリヤ側の吸入通路３１１，３１２，３１３へは図６の矢印のように吸入されるが、フロント側へは斜板３４が障害となって行き難い。このためフロント側の吸入通路３０１〜３０３及びリヤ側の吸入通路３１１〜３１３のガス吸入量に違いが生じて圧縮効率を低下するという問題があった。
【０００５】
又、図７に示すように前記吸入通路１２２が駆動シャフト１８を指向するように形成されている場合には、斜板室２１へ吸入されたガスが駆動シャフト１８へ向かう。このとき、左右両側の両頭ピストン２２の胴部に衝突したガス流は、図７に矢印で示すように吸入口１２２に最も近い吸入通路３０１（３１１）へ吸入され易く、他の吸入通路３０２（３１２）、３０３（３１３）へのガスの流量が減少し、リヤ側の各吸入通路３１１〜３１３のガス吸入量に違いが生じて圧縮効率が低下するという問題があった。
【０００６】
なお、斜板の片側のみにピストンを配設した片頭ピストン型の斜板式圧縮機においても、複数の吸入通路へのガスの吸入量に相違が生じるので、圧縮効率が低下するという問題があった。
【０００７】
この発明の目的は従来の技術に存する問題点を解消して、吸入口から斜板室に吸入されたガスを複数の吸入通路に適量吸入させることができ、ハウジングに形成した吸入室へのガスの供給を適正に行い、圧縮効率を向上することができる斜板式圧縮機を提供することにある。
【０００８】
この発明の別の目的は従来の技術に存する問題点を解消して、吸入口から斜板室に吸入されたガスを複数対のフロント側及びリヤ側の吸入通路に適量吸入させることができ、フロント側及びリヤ側のハウジングに形成した吸入室へのガスの供給を適正に行い、圧縮効率を向上することができる両頭ピストン型の斜板式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記載の発明は上記目的を達成するため、複数のシリンダボアを有するシリンダブロックの端面に吸入室と吐出室を区画形成するハウジングを接合固定し、斜板室に駆動シャフトにより回転する斜板を収容し、該斜板に前記シリンダボア内に収容されたピストンを連結し、前記斜板室には該斜板室へガスを導入する吸入口を設けるとともに、前記シリンダブロックには斜板室のガスを吸入室へ導くための複数の吸入通路を設け、前記ピストンを斜板の回転運動により往復動させて、前記吸入室からシリンダボア内の圧縮室へガスを吸入し、該圧縮室内で圧縮されたガスを前記吐出室へ吐出するようにした斜板式圧縮機において、前記斜板室内に前記吸入口から斜板室に吸入されるガスの流れを変えて前記各吸入通路へ吸入されるガス流量を均一化するための偏向部材を設け、前記偏向部材はガスの一部を斜板室内の周方向に分流するものであって、前記偏向部材は吸入口に最も近い吸入通路のガス吸入量を抑制する位置に設けられている。
【００１０】
請求項２記載の発明は、請求項１において、前記吸入口を前記駆動シャフトに指向するように形成している。
【００１１】
請求項３記載の発明は、請求項１又は２のいずれか１項において、前記吸入通路の横断面積を吸入口からの距離が大きくなる程、大きく設定している。
請求項４記載の発明は、請求項２において、前記偏向部材をシリンダブロックに設けた円弧状の偏向板としている。
【００１２】
請求項５記載の発明は、請求項１〜４のいずれか１項において、前記複数の吸入通路のうち一つの吸入通路を前記吸入口と対応して設けている。
【００１３】
請求項６記載の発明は、請求項５において、前記吸入通路をシリンダブロックとハウジングを締め付ける締付ボルトの挿通孔を兼用するようにし、偏向部材を前記締付ボルトの外周側を覆うようにシリンダブロックに設けている。
【００１４】
請求項７記載の発明は、請求項６において、前記偏向板を吸入口からのガスを偏向する円弧状の第１偏向板と、締付ボルトを挟んで第１偏向板と対向し、ピストンの外周面により反射されたガスの吸入口に最も近い吸入通路への流入を抑制する円弧状の第２偏向板とにより構成している。
【００１５】
請求項８記載の発明は、請求項１〜７のいずれか１項において、複数のシリンダボアを有するシリンダブロックの前後両端面に吸入室と吐出室を区画形成するフロント及びリヤのハウジングを接合固定し、シリンダブロックの中央部に形成した斜板室に駆動シャフトにより回転する斜板を収容し、該斜板の前後両側面にシューを介して前記シリンダボア内に収容された両頭ピストンを係留し、前記シリンダブロックには前記斜板室へガスを導入する吸入口を設けるとともに、斜板室のガスを前記フロント及びリヤの吸入室へそれぞれ導くための複数対の吸入通路を設けて両頭ピストン型の斜板式圧縮機としている。
【００１６】
請求項９記載の発明は、請求項８において、前記吸入口を斜板室の中心から軸方向へ変位した位置に設け、前記偏向部材は、吸入口からのガス流量を斜板室のフロント側とリヤ側に均一に分流するように、前記変位した位置側からその反対側へ向けてガスを導く。
【００１７】
【発明の実施の形態】
以下、この発明の１実施形態を図１〜図４に基づいて詳細に説明する。
図１に示すように互いに対設される前後（左右）一対のシリンダブロック１１，１２のフロント側端面及びリヤ側端面にはバルブプレート１３，１４を介してフロントハウジング１５及びリヤハウジング１６が接合されている。これらのシリンダブロック１１，１２、バルブプレート１３，１４及びフロントハウジング１５、リヤハウジング１６は複数の締付ボルト１７によって互いに接合固定されている。
【００１８】
前記シリンダブロック１１，１２の中心孔には駆動シャフト１８が前後一対のラジアルベアリング１９，２０を介して回転可能に支持されている。前記シリンダブロック１１，１２の接合部には斜板室２１が形成され、駆動シャフト１８まわりには図４に示すようにシリンダボア１１１，１２１が所定間隔をおいて複数箇所に形成されている。前記斜板室２１にはシリンダブロック１２の外周に設けた吸入口１２２から冷媒ガスが吸入されるようになっている。各シリンダボア１１１，１２１には図３に示すように両頭ピストン２２が前後方向の往復動可能に収容されており、両頭ピストン２２の端面とバルブプレート１３，１４との間には圧縮室２３が形成されている。
【００１９】
図１に示すように前記フロント及びリヤのハウジング１５，１６には外周寄りに吸入室２４，２５が中央部寄りに吐出室２６，２７がそれぞれ区画形成されている。前記バルブプレート１３，１４には図２，３に示すように各圧縮室２３と対応して吸入弁機構２９，２９が設けられている。フロント側のシリンダブロック１１のシリンダボア１１１間には第１〜第３の吸入通路３０１，３０２，３０３が軸方向に延びて形成されている。リヤ側のシリンダブロック１２のシリンダボア１２１間には第１〜第３の吸入通路３１１，３１２，３１３が軸方向に延びて形成されている。前記斜板室２１はフロント側の第１〜第３の吸入通路３０１，３０２，３０３によって前記フロント側の吸入室２４と連通されている。又、前記斜板室２１はリヤ側の第１〜第３の吸入通路３１１，３１２，３１３によって前記リヤ側の吸入室２５と連通されている。そして、フロント側の第１〜第３の吸入通路３０１，３０２，３０３とリヤ側の第１〜第３の吸入通路３１１，３１２，３１３とは互いに軸方向に整合されている。前後で対に形成された第１〜第３の吸入通路３０１（３１１），３０２（３１２），３０３（３１３）には前記締付ボルト１７が挿通されている。即ち、前記吸入通路は締付ボルト１７の挿通孔を兼用している。
【００２０】
前記バルブプレート１３，１４には図２，３に示すように各圧縮室２３と対応して吐出弁機構３２，３２が設けられている。吐出室２６，２７はバルブプレート１３，１４及びシリンダブロック１１，１２に形成した吐出通路３３１、マフラー室３３２及び吐出口１２３によって外部冷媒回路に接続される。
【００２１】
前記斜板室２１には前記駆動シャフト１８に嵌合固定した斜板３４が収容され、前記両頭ピストン２２はシュー３５，３６を介して斜板３４に係留されている。前記斜板３４のボス部とシリンダブロック１１，１２の斜板室２１を形成する側壁との間にはスラストベアリング３７，３８が介在されている。そして、駆動シャフト１８が回転されると斜板３４が揺動回転され、両頭ピストン２２がシリンダボア１１１，１２１内で前後方向に往復動され、圧縮動作が行われる。
【００２２】
次に、本発明の要部である斜板室２１へのガスの吸入構造について説明する。図１に示すように、吸入口１２２はリヤ側のシリンダブロック１２に設けられ、斜板室２１の軸方向の中心からリヤ側に所定距離だけ変位している。又、図４に示すように、吸入口１２２は両頭ピストン２２の間（軸方向から見てシリンダボア１１１，１１２の間）に開口し、駆動シャフト１８に指向するように設けられている。図４に示すように複数対の第１〜第３の吸入通路３０１〜３０３，３１１〜３１３のうち一対の第１吸入通路３０１，３１１は前記吸入口１２２と対応して設けられている。即ち、リヤ側の第１吸入通路３１１が吸入口１２２に最も近い吸入通路となる。
【００２３】
シリンダブロック１２には、該ブロック１２に設けた第１吸入通路３１１の斜板室２１側の開口部を覆うように偏向部材としての第１及び第２の偏向板４１，４２が一体に設けられている。偏向部材４１，４２は図１に示すように吸入口１２２と対向する位置にまで軸方向に延在している。第１偏向板４１は図４に示すように締付ボルト１７の外周を覆うように円弧状に形成され、吸入口１２２から斜板室２１へ吸入されたガスを図１に矢印で示すように斜板室２１のフロント側へ導く。又、第１偏向板４１は図４に示すように斜板室２１の内周壁面に沿ってガスを第２吸入通路３１２、第３吸入通路３１３へと案内するようにしている。第２偏向板４２はピストン２２の外周面により反射されたガスのリヤ側の第１吸入通路３１１への吸入量を抑制するものである。
【００２４】
偏向部材である第１偏向板４１は、軸方向から見て吸入口１２２の開口部と吸入口１２２から最も近い吸入通路３１１の開口部との間に存在し、吸入口１２２からの冷媒ガスが吸入通路３１１へ直接流入することを抑制するとともに、冷媒ガスを軸方向及び周方向に分流するように設けられる。また、偏向部材である第２偏向板４２は、軸方向から見て吸入通路３１１の開口部とピストン２２の周面との間に存在し、吸入口１２２から流入し隣接するピストン２２により偏向された冷媒ガスが吸入通路３１１へ流入することを抑制するように設けられる。
【００２５】
次に、前記のように構成した斜板式圧縮機の動作を説明する。
今、駆動シャフト１８の回転により斜板３４が回転されるとシュー３５，３６を介して各両頭ピストン２２がシリンダボア１１１，１２１内で前後方向に往復動される。この両頭ピストン２２の往復運動により外部冷媒回路及び吸入口１２２から斜板室２１内に吸入された冷媒ガスは第１偏向板４１に衝突した後、図１に矢印で示すようにフロント側に流れるとともに、図４に矢印で示すように斜板室２１の内周面に沿って斜板室２１の底部へと流れる。その後、該斜板室２１からシリンダブロッ１１に形成したフロント側の第１〜第３の吸入通路３０１，３０２，３０３を通ってフロント側の吸入室２４に導かれる。又、リヤ側のシリンダブロッ１２に形成した第１〜第３の吸入通路３１１，３１２，３１３を通ってリヤ側の吸入室２５に導かれる。この吸入室２４，２５内の冷媒ガスはバルブプレート１３，１４に設けた吸入弁機構２９，２９からシリンダボア内の圧縮室２３に吸入される。圧縮されたガスは、吐出弁機構３２，３２から吐出室２６，２７へ吐出される。さらに、吐出室２６，２７に吐出された冷媒ガスは吐出通路３３１及びマフラー室３３２を介して吐出口１２３から外部冷媒回路に圧送され、例えば車両空調装置の蒸発器に送られて、室内の空調に供される。
【００２６】
次に、前記実施形態の構成により得られる作用効果について説明する。
○ 前記実施形態ではリヤ側のシリンダブロック１２に吸入口１２２を形成して、斜板室２１の中心から軸方向（リヤ側）へ変位させると共に、駆動シャフト１８を指向するようになし、斜板室２１のリヤ側壁面に第１吸入通路３１１と近接して円弧状の第１偏向板４１を設けた。
【００２７】
従って、吸入口１２２から斜板室２１へ吸入されるガスの一部はフロント側へ偏向され、斜板３４によりフロント側の第１〜第３の吸入通路３０１〜３０３へのガス流量の不足を補って、斜板室２１のフロント側及びリヤ側へのガスの供給量を均等化することができる。
【００２８】
又、斜板室２１のフロント側へ流れなかったガスは、図４に示すように第１偏向板４１により斜板室２１の内周面に沿って矢印で示すように二方向に分流されて一部のガスはピストン２２の外周面と斜板室２１の内周面との隙間を通って斜板室２１の底部へと導かれる。このため、第２吸入通路３１２及び第３吸入通路３１３へのガスの供給が円滑に行われ、両通路へのガスの吸入量が均一化される。
【００２９】
○ 前記実施形態では第１偏向板４１と対応して第２偏向板４２を設けたので、第１吸入通路３１１へのガス吸入量を適正にすることができる。すなわち、締付ボルト１７と該ボルトに最も近い位置にある二つのピストン２２，２２との隙間に流入したガスの一部は、ピストン２２，２２の外周面に当たって跳ね返り、第１吸入通路３１１へ流入しようとする。しかし、このガスは第２偏向板４２によって跳ね返されるので、第１吸入通路３１１へ吸入されるのが抑制され、ピストン２２，２２の隙間を通って駆動シャフト１８側に流れ、その後、第２及び第３の吸入通路３１２，３１３へ吸入される。この結果、第１吸入通路３１１へのガス吸入量が適正に制御され、第１〜３の吸入通路３１１〜３１３へのガスの吸入量が均一化される。
【００３０】
○ 前記実施形態ではフロント側の第１〜３の吸入通路３０１，３０２，３０３の通路断面積を小、中、大としたので、斜板室２１のフロント側に流れたガスが第１〜３の吸入通路３０１，３０２，３０３に均一に吸入される。もし、第１〜３の吸入通路３０１，３０２，３０３の通路断面積が同じである場合、吸入口１２２からの距離が遠い位置にある第３吸入通路３０３ほどガスの吸入量は斜板室２１内での流路抵抗（圧損）によって低下する。前記実施形態では、リヤ側の第１〜３の吸入通路３１１，３１２，３１３の通路断面積を小、中、大としたので、斜板室２１のリヤ側に流れたガスは第１〜３の吸入通路３１１，３１２，３１３に均一に吸入される。
【００３１】
○ 前記実施形態では第１偏向板４１を円弧状に形成したので、吸入口１２２からのガスを斜板室２１の周方向に円滑に偏向することができる。
なお、前記実施形態は、次のように変更することもできる。
【００３２】
・図４に示す実施形態において、第２偏向板４２を省略するとともに、第１偏向板４１の形成範囲を大きくして、リヤ側の第１吸入通路３１１へのガスの吸入量を適正に制御すること。
【００３３】
・前記吸入口１２２をフロント側のシリンダブロック１１のみに形成すること。
・前記実施形態では第１〜第３の吸入通路３０１〜３０３、３１１〜３１３を設けたが、これを二対、あるいは四対以上設けること。
【００３４】
・前述した実施形態において、図５に示すように、吸入口１２２の位置を斜板室２１の軸方向に関して中央部に形成するとともに、第１偏向板４１のみを設けること。
【００３５】
この実施形態では吸入口１２２から斜板室２１に向かうガスが図５の矢印で示すように、フロント側及びリヤ側に均等に分流されるとともに、第１偏向板４１の外周面によりガスが斜板室２１の周方向へも導かれるので、フロント側及びリヤ側の第１〜第３の吸入通路３０１〜３０３、３１１〜３１３へのガスの吸入量を均等にすることができる。
【００３６】
・斜板の片側のみにピストンを備える片頭ピストン型斜板式圧縮機に適用すること。
この場合には各吸入通路へのガスの吸入量を均一化することができて、圧縮効率を向上することができるとともに、斜板室のフロント側に分流されたガスは駆動シャフトのシャフトシール室へ積極的に導かれるので、シャフトシール機構の冷却・潤滑を確実に行うこともできる。
（定義）
この明細書において、偏向部材は円弧状の第１偏向板４１の他に、平板状の偏向板、山形状の偏向板、棒状の偏向部材、あるいは網状の偏向部材を含むものとする。
【００３７】
【発明の効果】
この発明は特許請求の範囲のように構成したので、次のような効果がある。
請求項１〜９記載の発明は吸入口から斜板室に吸入されたガスを複数の吸入通路に適量吸入させることができ、ハウジングに形成した吸入室へのガスの供給を適正に行い、圧縮効率を向上することができる。
【００３８】
また、吸入口から偏向部材に当たったガスが斜板室の内周面に沿って周方向に分流され、他の吸入通路へのガスの吸入量を適正化することができる。
【００３９】
請求項３記載の発明は、複数の吸入通路へのガスの吸入量をさらに均等化することができ、吸入室へのガスの供給を適正に行い、圧縮効率をさらに向上することができる。
【００４０】
請求項８記載の発明は吸入口から斜板室に吸入されたガスをフロント及びリヤ側の複数対の吸入通路に適量吸入させることができ、フロント及びリヤのハウジングに形成した吸入室へのガスの供給を適正に行い、圧縮効率を向上することができる。
【００４１】
請求項９記載の発明は斜板室の中心から軸方向に変位した吸入口から斜板室に吸入されたガスを斜板室内でフロント側及びリヤ側へ均等に分流することができ、フロント及びリヤのハウジングに形成した吸入室へのガスの供給を適正に行い、圧縮効率を向上することができる。
【図面の簡単な説明】
【図１】この発明を具体化した斜板式圧縮機の図４の１−１線断面図。
【図２】図１の２−２線におけるシリンダブロックを省略した断面図。
【図３】図４の３−３線断面図。
【図４】図１の４−４線断面図。
【図５】この発明の別の実施形態の要部断面図。
【図６】従来の斜板式圧縮機を示す部分断面図。
【図７】従来の斜板式圧縮機の横断面図。
【符号の説明】
１１，１２…シリンダブロック、１３，１４…バルブプレート、１５，１６…フロント及びリヤのハウシング、１８…駆動シャフト、２１…斜板室、２２…ピストン、２３…圧縮室、２４，２５…吸入室、２６，２７…吐出室、３４…斜板、４１…偏向部材としての第１偏向板、４２…偏向部材としての第２偏向板。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a double-headed piston type swash plate compressor used in, for example, a vehicle air conditioner. More specifically, the gas sucked into the swash plate chamber from the suction port provided in the cylinder block of the swash plate compressor can be smoothly guided to the front and rear suction chambers via the front and rear suction passages. The present invention relates to a gas suction structure.
[0002]
[Prior art]
In general, in a double-headed piston type swash plate compressor, front and rear housings that form a suction chamber and a discharge chamber are joined and fixed to both front and rear end faces of a cylinder block having a plurality of cylinder bores. A swash plate chamber formed at the center of the cylinder block accommodates a swash plate that swings and rotates by a drive shaft. Both front and rear sides of the swash plate are tethered with double-headed pistons housed in the cylinder bore via shoes. ing. The cylinder block is provided with a suction port for introducing gas into the swash plate chamber, and a plurality of pairs of suction passages for guiding the gas in the swash plate chamber to the front and rear suction chambers. When the double-headed piston is reciprocated by the rotational movement of the swash plate, gas is sucked from the suction chamber into the compression chamber in the cylinder bore, and the gas compressed in the compression chamber is discharged into the discharge chamber.
[0003]
As shown in FIG. 6, a pair of cylinder blocks 11 and 12 are provided on the front and rear sides to form a swash plate chamber 21 at the center, and the cylinder block 12 on the rear side is connected to the swash plate chamber 21 from an external refrigerant circuit. An intake port 122 for inhaling gas is provided. As shown in FIGS. 6 and 7, the cylinder blocks 11 and 12 include suction passages 301, 302, and 303 for introducing gas from the swash plate chamber 21 to suction chambers 24 and 25 formed in the front and rear housings 15 and 16, respectively. 311, 312, and 313 are provided. Reference numeral 17 denotes a clamping bolt for the cylinder blocks 11 and 12 and the two housings 15 and 16; 18 denotes a drive shaft; 22 denotes a double-headed piston; 34 denotes a swash plate that is fitted and fixed to the drive shaft 18 and reciprocates the piston 22 It is.
[0004]
[Problems to be solved by the invention]
However, in the gas suction structure of the swash plate compressor, when the gas is sucked into the swash plate chamber 21 from the suction port 122, it is sucked into the respective suction passages 301, 302, 303, 311, 312, and 313. There was a problem that the amount of gas was difficult to equalize. That is, as described above, the suction port 122 is provided so as to be displaced from the center of the swash plate chamber 21 to the rear side, so that when the outer peripheral surface of the swash plate 34 is at a position facing the suction port 122, the gas is temporarily stored. The amount introduced into the swash plate chamber 21 is limited. When the swash plate 34 is inclined to the front side as shown in FIG. 6, the gas introduced from the suction port 122 into the swash plate chamber 21 is sucked into the rear suction passages 311, 312, and 313 as indicated by arrows in FIG. However, the swash plate 34 is difficult to go to the front side. For this reason, there is a problem in that the compression efficiency is lowered due to a difference in the amount of gas sucked in the suction passages 301 to 303 on the front side and the suction passages 311 to 313 on the rear side.
[0005]
Further, when the suction passage 122 is formed to face the drive shaft 18 as shown in FIG. 7, the gas sucked into the swash plate chamber 21 goes to the drive shaft 18. At this time, the gas flow that has collided with the body portions of the pistons 22 on both the left and right sides is easily sucked into the suction passage 301 (311) closest to the suction port 122 as shown by the arrows in FIG. 312) and 303 (313), there is a problem that the compression efficiency is reduced due to a difference in the amount of gas sucked in the suction passages 311 to 313 on the rear side.
[0006]
Even in the single-headed piston type swash plate compressor in which the piston is disposed only on one side of the swash plate, there is a difference in the amount of gas sucked into the plurality of suction passages, and there is a problem that the compression efficiency is lowered. .
[0007]
An object of the present invention is to solve the problems existing in the prior art, and to allow a suitable amount of gas sucked into the swash plate chamber from the suction port to be sucked into a plurality of suction passages, so that the gas is sucked into the suction chamber formed in the housing. An object of the present invention is to provide a swash plate compressor capable of appropriately supplying and improving the compression efficiency.
[0008]
Another object of the present invention is to solve the problems existing in the prior art, and to suck a suitable amount of gas sucked into the swash plate chamber from the suction port into a plurality of pairs of front and rear suction passages. An object of the present invention is to provide a double-headed piston-type swash plate compressor capable of appropriately supplying gas to suction chambers formed in the side and rear housings and improving the compression efficiency.
[0009]
[Means for Solving the Problems]
In order to achieve the above-mentioned object, the invention according to claim 1 has a housing for defining a suction chamber and a discharge chamber joined and fixed to an end face of a cylinder block having a plurality of cylinder bores, and a swash plate rotated by a drive shaft is provided in the swash plate chamber. The piston housed in the cylinder bore is connected to the swash plate, the suction chamber for introducing gas into the swash plate chamber is provided in the swash plate chamber, and the gas in the swash plate chamber is sucked into the cylinder block. A plurality of suction passages for guiding the gas to a compression chamber in a cylinder bore by reciprocating the piston by a rotational movement of a swash plate, and the gas compressed in the compression chamber is In the swash plate compressor that discharges into the discharge chamber, the gas flow sucked into the suction passages by changing the flow of gas sucked into the swash plate chamber from the suction port into the swash plate chamber. The deflection member for uniformizing the provided the deflection member has been made to divert part of the gas in the circumferential direction of the swash plate chamber, the deflection member is a gas suction amount of the closest suction passage to the suction port It is provided at a position to be suppressed .
[0010]
According to a second aspect of the invention, according to claim 1, to form the inlet to direct the drive shaft.
[0011]
According to a third aspect of the present invention, in any one of the first or second aspect, the cross-sectional area of the suction passage is set to be larger as the distance from the suction port is larger.
According to a fourth aspect of the present invention, in the second aspect, the deflecting member is an arc-shaped deflecting plate provided in a cylinder block.
[0012]
According to a fifth aspect of the invention, in any one of claims 1 to 4, which only set one of the suction passage of the plurality of suction passage corresponding to the inlet.
[0013]
According to a sixth aspect of the present invention, in the fifth aspect, the suction passage is used as an insertion hole for a tightening bolt that tightens the cylinder block and the housing, and the deflection member is covered with the outer peripheral side of the tightening bolt. It is provided in the block.
[0014]
According to a seventh aspect of the present invention, in the sixth aspect of the present invention, the deflecting plate is opposed to the first deflecting plate with an arc-shaped first deflecting plate that deflects the gas from the suction port, and a clamping bolt, An arc-shaped second deflecting plate that suppresses inflow of the gas reflected by the outer peripheral surface to the suction passage closest to the suction port is configured.
[0015]
According to an eighth aspect of the present invention, in any one of the first to seventh aspects, the front and rear housings defining the suction chamber and the discharge chamber are joined and fixed to the front and rear end surfaces of the cylinder block having a plurality of cylinder bores. A swash plate rotated by a drive shaft is housed in a swash plate chamber formed in the center of the cylinder block, and double-headed pistons housed in the cylinder bore are moored on both front and rear sides of the swash plate via shoes, The block is provided with a suction port for introducing gas into the swash plate chamber, and is provided with a plurality of pairs of suction passages for guiding the gas in the swash plate chamber to the front and rear suction chambers respectively. It is said.
[0016]
The invention of claim 9, wherein, in claim 8, provided at a position displaced the inlet from the center of the swash plate chamber in the axial direction, the deflection member, the front side and the rear of the gas flow from the inlet port swash plate chamber The gas is guided from the displaced position side toward the opposite side so as to be uniformly diverted to the side .
[0017]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, one embodiment of the present invention will be described in detail with reference to FIGS.
As shown in FIG. 1, a front housing 15 and a rear housing 16 are joined to front and rear end faces of a pair of front and rear (left and right) cylinder blocks 11 and 12 that are opposed to each other via valve plates 13 and 14, respectively. ing. The cylinder blocks 11 and 12, the valve plates 13 and 14, the front housing 15 and the rear housing 16 are joined and fixed to each other by a plurality of fastening bolts 17.
[0018]
A drive shaft 18 is rotatably supported in the center holes of the cylinder blocks 11 and 12 via a pair of front and rear radial bearings 19 and 20. A swash plate chamber 21 is formed at the joint between the cylinder blocks 11 and 12, and cylinder bores 111 and 121 are formed at a plurality of locations around the drive shaft 18 at predetermined intervals as shown in FIG. Refrigerant gas is sucked into the swash plate chamber 21 from a suction port 122 provided on the outer periphery of the cylinder block 12. As shown in FIG. 3, each cylinder bore 111, 121 accommodates a double-ended piston 22 so as to be able to reciprocate in the front-rear direction, and a compression chamber 23 is formed between the end face of the double-ended piston 22 and the valve plates 13, 14. Has been.
[0019]
As shown in FIG. 1, the front and rear housings 15 and 16 are formed with suction chambers 24 and 25 near the outer periphery and discharge chambers 26 and 27 near the center, respectively. The valve plates 13 and 14 are provided with intake valve mechanisms 29 and 29 corresponding to the compression chambers 23 as shown in FIGS. Between the cylinder bores 111 of the front cylinder block 11, first to third suction passages 301, 302, and 303 are formed extending in the axial direction. Between the cylinder bores 121 of the rear cylinder block 12, first to third suction passages 311, 312, and 313 are formed extending in the axial direction. The swash plate chamber 21 is communicated with the front suction chamber 24 by front-side first to third suction passages 301, 302, and 303. The swash plate chamber 21 is communicated with the rear suction chamber 25 through first to third suction passages 311, 312, and 313 on the rear side. The front-side first to third suction passages 301, 302, and 303 and the rear-side first to third suction passages 311, 312, and 313 are aligned with each other in the axial direction. The tightening bolts 17 are inserted through first to third suction passages 301 (311), 302 (312), and 303 (313) formed in a pair at the front and rear. That is, the suction passage also serves as an insertion hole for the tightening bolt 17.
[0020]
The valve plates 13 and 14 are provided with discharge valve mechanisms 32 and 32 corresponding to the compression chambers 23 as shown in FIGS. The discharge chambers 26 and 27 are connected to an external refrigerant circuit by a discharge passage 331, a muffler chamber 332 and a discharge port 123 formed in the valve plates 13 and 14 and the cylinder blocks 11 and 12.
[0021]
The swash plate chamber 21 accommodates a swash plate 34 fitted and fixed to the drive shaft 18, and the double-headed piston 22 is anchored to the swash plate 34 via shoes 35 and 36. Thrust bearings 37 and 38 are interposed between the boss portion of the swash plate 34 and the side walls forming the swash plate chamber 21 of the cylinder blocks 11 and 12. When the drive shaft 18 is rotated, the swash plate 34 is oscillated and rotated, and the double-headed piston 22 is reciprocated back and forth in the cylinder bores 111 and 121 to perform a compression operation.
[0022]
Next, a structure for sucking gas into the swash plate chamber 21, which is a main part of the present invention, will be described. As shown in FIG. 1, the suction port 122 is provided in the cylinder block 12 on the rear side, and is displaced from the center in the axial direction of the swash plate chamber 21 by a predetermined distance. As shown in FIG. 4, the suction port 122 opens between the two-headed pistons 22 (between the cylinder bores 111 and 112 when viewed from the axial direction) and is provided so as to face the drive shaft 18. As shown in FIG. 4, the pair of first suction passages 301 and 311 among the plurality of pairs of first to third suction passages 301 to 303 and 311 to 313 are provided corresponding to the suction port 122. That is, the first suction passage 311 on the rear side is the suction passage closest to the suction port 122.
[0023]
The cylinder block 12 is integrally provided with first and second deflection plates 41 and 42 as deflection members so as to cover the opening on the swash plate chamber 21 side of the first suction passage 311 provided in the block 12. Yes. As shown in FIG. 1, the deflecting members 41 and 42 extend in the axial direction to a position facing the suction port 122. The first deflection plate 41 is formed in an arc shape so as to cover the outer periphery of the fastening bolt 17 as shown in FIG. 4, and the gas sucked into the swash plate chamber 21 from the suction port 122 is inclined as shown by an arrow in FIG. Lead to the front side of the plate chamber 21. Further, the first deflection plate 41 guides gas to the second suction passage 312 and the third suction passage 313 along the inner peripheral wall surface of the swash plate chamber 21 as shown in FIG. The second deflection plate 42 suppresses the intake amount of the gas reflected by the outer peripheral surface of the piston 22 into the first suction passage 311 on the rear side.
[0024]
The first deflecting plate 41 that is a deflecting member exists between the opening of the suction port 122 and the opening of the suction passage 311 closest to the suction port 122 when viewed from the axial direction. While suppressing direct inflow into the suction passage 311, the refrigerant gas is provided to be diverted in the axial direction and the circumferential direction. Further, the second deflecting plate 42 as a deflecting member exists between the opening of the suction passage 311 and the peripheral surface of the piston 22 when viewed from the axial direction, flows from the suction port 122 and is deflected by the adjacent piston 22. The refrigerant gas is provided so as to prevent the refrigerant gas from flowing into the suction passage 311.
[0025]
Next, the operation of the swash plate compressor configured as described above will be described.
Now, when the swash plate 34 is rotated by the rotation of the drive shaft 18, the double-ended pistons 22 are reciprocated in the front and rear directions in the cylinder bores 111 and 121 via the shoes 35 and 36. The refrigerant gas sucked into the swash plate chamber 21 from the external refrigerant circuit and the suction port 122 by the reciprocating motion of the double-headed piston 22 collides with the first deflection plate 41, and then flows to the front side as indicated by an arrow in FIG. 4 flows along the inner peripheral surface of the swash plate chamber 21 to the bottom of the swash plate chamber 21 as indicated by an arrow in FIG. Thereafter, the air is guided from the swash plate chamber 21 to the front suction chamber 24 through first to third suction passages 301, 302, 303 formed in the cylinder block 11. Further, the air is guided to the rear suction chamber 25 through first to third suction passages 311, 312 and 313 formed in the rear cylinder block 12. The refrigerant gas in the suction chambers 24 and 25 is sucked into the compression chamber 23 in the cylinder bore from suction valve mechanisms 29 and 29 provided in the valve plates 13 and 14. The compressed gas is discharged from the discharge valve mechanisms 32 and 32 to the discharge chambers 26 and 27. Further, the refrigerant gas discharged into the discharge chambers 26 and 27 is pumped from the discharge port 123 to the external refrigerant circuit via the discharge passage 331 and the muffler chamber 332, and is sent, for example, to the evaporator of the vehicle air conditioner to be air-conditioned in the room. To be served.
[0026]
Next, functions and effects obtained by the configuration of the embodiment will be described.
In the above-described embodiment, the suction port 122 is formed in the cylinder block 12 on the rear side and is displaced in the axial direction (rear side) from the center of the swash plate chamber 21, and is directed to the drive shaft 18. An arc-shaped first deflecting plate 41 is provided on the rear side wall surface of the rear side wall in the vicinity of the first suction passage 311.
[0027]
Therefore, a part of the gas sucked into the swash plate chamber 21 from the suction port 122 is deflected to the front side, and the swash plate 34 compensates for the shortage of gas flow to the first to third suction passages 301 to 303 on the front side. Thus, the amount of gas supplied to the front side and the rear side of the swash plate chamber 21 can be equalized.
[0028]
Further, as shown in FIG. 4, the gas that did not flow to the front side of the swash plate chamber 21 is partly divided in two directions along the inner peripheral surface of the swash plate chamber 21 by the first deflector plate 41 as shown by arrows. This gas is guided to the bottom of the swash plate chamber 21 through a gap between the outer peripheral surface of the piston 22 and the inner peripheral surface of the swash plate chamber 21. Therefore, the gas is smoothly supplied to the second suction passage 312 and the third suction passage 313, and the amount of gas sucked into both passages is made uniform.
[0029]
In the above embodiment, since the second deflection plate 42 is provided in correspondence with the first deflection plate 41, the amount of gas sucked into the first suction passage 311 can be made appropriate. That is, part of the gas flowing into the gap between the fastening bolt 17 and the two pistons 22, 22 located closest to the bolt bounces off the outer peripheral surface of the piston 22, 22 and flows into the first suction passage 311. try to. However, since this gas is bounced back by the second deflecting plate 42, it is suppressed from being sucked into the first suction passage 311 and flows to the drive shaft 18 side through the gap between the pistons 22 and 22, and then the second and The air is sucked into the third suction passages 312 and 313. As a result, the amount of gas sucked into the first suction passage 311 is appropriately controlled, and the amount of gas sucked into the first to third suction passages 311 to 313 is made uniform.
[0030]
In the above embodiment, since the passage cross-sectional areas of the first to third suction passages 301, 302, and 303 on the front side are small, medium, and large, the gas that flows to the front side of the swash plate chamber 21 The suction passages 301, 302, and 303 are uniformly sucked. If the first to third suction passages 301, 302, and 303 have the same passage cross-sectional area, the third suction passage 303 located far from the suction port 122 has a gas suction amount in the swash plate chamber 21. It decreases due to the flow path resistance (pressure loss). In the above embodiment, since the passage cross-sectional areas of the first to third suction passages 311, 312, and 313 on the rear side are small, medium, and large, the gas that flows to the rear side of the swash plate chamber 21 is the first to third. The suction passages 311, 312, and 313 are uniformly sucked.
[0031]
In the above embodiment, since the first deflection plate 41 is formed in an arc shape, the gas from the suction port 122 can be smoothly deflected in the circumferential direction of the swash plate chamber 21.
In addition, the said embodiment can also be changed as follows.
[0032]
In the embodiment shown in FIG. 4, the second deflection plate 42 is omitted, and the formation range of the first deflection plate 41 is increased to appropriately control the amount of gas sucked into the first suction passage 311 on the rear side. To do.
[0033]
The suction port 122 is formed only in the cylinder block 11 on the front side.
In the embodiment, the first to third suction passages 301 to 303 and 311 to 313 are provided, but two pairs or four or more pairs are provided.
[0034]
In the above-described embodiment, as shown in FIG. 5, the position of the suction port 122 is formed in the center with respect to the axial direction of the swash plate chamber 21, and only the first deflection plate 41 is provided.
[0035]
In this embodiment, the gas from the suction port 122 toward the swash plate chamber 21 is evenly divided into the front side and the rear side as indicated by arrows in FIG. 5, and the gas is swashed by the outer peripheral surface of the first deflection plate 41. Accordingly, the amount of gas sucked into the first to third suction passages 301 to 303 and 311 to 313 on the front side and the rear side can be equalized.
[0036]
・ Apply to a single-head piston type swash plate compressor that has a piston only on one side of the swash plate.
In this case, the amount of gas sucked into each suction passage can be made uniform, the compression efficiency can be improved, and the gas diverted to the front side of the swash plate chamber is transferred to the shaft seal chamber of the drive shaft. Since the shaft is actively guided, the shaft seal mechanism can be reliably cooled and lubricated.
(Definition)
In this specification, the deflection member includes, in addition to the arc-shaped first deflection plate 41, a flat plate-shaped deflection plate, a mountain-shaped deflection plate, a rod-shaped deflection member, or a net-like deflection member.
[0037]
【The invention's effect】
Since the present invention is configured as in the claims, the following effects are obtained.
According to the first to ninth aspects of the present invention, an appropriate amount of gas sucked into the swash plate chamber from the suction port can be sucked into a plurality of suction passages, gas is properly supplied to the suction chamber formed in the housing, and compression efficiency is improved. Can be improved.
[0038]
Further , the gas striking the deflecting member from the suction port is diverted in the circumferential direction along the inner peripheral surface of the swash plate chamber, and the amount of gas sucked into the other suction passages can be optimized.
[0039]
The invention according to claim 3 can further equalize the amount of gas sucked into the plurality of suction passages, appropriately supply the gas to the suction chamber, and further improve the compression efficiency.
[0040]
According to the eighth aspect of the present invention, an appropriate amount of gas sucked into the swash plate chamber from the suction port can be sucked into a plurality of pairs of suction passages on the front and rear sides, and the gas to the suction chamber formed in the front and rear housings can be sucked. Supply can be performed appropriately and compression efficiency can be improved.
[0041]
According to the ninth aspect of the present invention, the gas sucked into the swash plate chamber from the suction port displaced in the axial direction from the center of the swash plate chamber can be evenly divided into the front side and the rear side in the swash plate chamber. The gas can be appropriately supplied to the suction chamber formed in the housing, and the compression efficiency can be improved.
[Brief description of the drawings]
FIG. 1 is a sectional view taken along line 1-1 of FIG. 4 of a swash plate compressor embodying the present invention.
FIG. 2 is a cross-sectional view in which a cylinder block taken along line 2-2 in FIG. 1 is omitted.
3 is a cross-sectional view taken along line 3-3 in FIG.
4 is a cross-sectional view taken along line 4-4 of FIG.
FIG. 5 is a cross-sectional view of a main part of another embodiment of the present invention.
FIG. 6 is a partial cross-sectional view showing a conventional swash plate compressor.
FIG. 7 is a cross-sectional view of a conventional swash plate compressor.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 11, 12 ... Cylinder block, 13, 14 ... Valve plate, 15, 16 ... Front and rear housing, 18 ... Drive shaft, 21 ... Swash plate chamber, 22 ... Piston, 23 ... Compression chamber, 24, 25 ... Suction chamber, 26, 27 ... discharge chamber, 34 ... swash plate, 41 ... first deflection plate as deflection member, 42 ... second deflection plate as deflection member.

Claims

A housing for defining a suction chamber and a discharge chamber is joined and fixed to an end face of a cylinder block having a plurality of cylinder bores, and a swash plate rotated by a drive shaft is accommodated in the swash plate chamber, and the swash plate is accommodated in the cylinder bore. A piston is connected, and the swash plate chamber is provided with a suction port for introducing gas into the swash plate chamber, and the cylinder block is provided with a plurality of suction passages for guiding gas in the swash plate chamber to the suction chamber. In the swash plate type compressor that is reciprocated by the rotational movement of the swash plate, sucks gas from the suction chamber to the compression chamber in the cylinder bore, and discharges the gas compressed in the compression chamber to the discharge chamber.
A deflection member is provided in the swash plate chamber for changing the flow of gas sucked from the suction port into the swash plate chamber to equalize the flow rate of gas sucked into the suction passages, and the deflection member is a part of the gas. Is a swash plate type compressor in which the deflection member is provided at a position for suppressing the amount of gas suction in the suction passage closest to the suction port .

In claim 1, the swash plate type compressor wherein the inlet is intended to be formed to direct to the drive shaft.

3. The swash plate compressor according to claim 1, wherein a cross-sectional area of the suction passage is set to be larger as a distance from the suction port is larger.

3. The swash plate compressor according to claim 2, wherein the deflecting member is an arcuate deflecting plate provided in a cylinder block.

In any one of claims 1 to 4, the swash plate type compressor, one of the suction passage are found provided corresponding to the suction port of the plurality of suction passages.

6. The suction passage according to claim 5, wherein the suction passage serves as an insertion hole for a tightening bolt for tightening the cylinder block and the housing, and the deflection member is provided in the cylinder block so as to cover an outer peripheral side of the tightening bolt. Swash plate compressor.

7. The deflecting plate according to claim 6, wherein the deflecting plate is a first arc-shaped deflecting plate that deflects the gas from the suction port, the first deflecting plate across the fastening bolt, and the gas reflected by the outer peripheral surface of the piston. A swash plate type compressor constituted by an arcuate second deflecting plate that suppresses inflow into the suction passage closest to the suction port.

The swash plate compressor according to any one of claims 1 to 7, wherein the front and rear housings defining the suction chamber and the discharge chamber are joined and fixed to the front and rear end faces of a cylinder block having a plurality of cylinder bores. A swash plate rotated by a drive shaft is accommodated in a swash plate chamber formed in the center of the block, and double-headed pistons accommodated in the cylinder bore are moored on both front and rear side surfaces of the swash plate via shoes. Is a double-headed piston type swash plate compressor provided with a suction port for introducing gas into the swash plate chamber and provided with a plurality of pairs of suction passages for guiding the gas in the swash plate chamber to the front and rear suction chambers, respectively.

According to claim 8, wherein the suction port is provided at a position displaced from the center of the swash plate chamber in the axial direction, the deflection member so as to uniformly split into front and rear side of the swash plate chamber gas flow from the inlet port And a swash plate compressor that guides the gas from the displaced position to the opposite side .