JP2004218466A - Traverse-mounted compressor - Google Patents

Traverse-mounted compressor Download PDF

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Publication number
JP2004218466A
JP2004218466A JP2003004278A JP2003004278A JP2004218466A JP 2004218466 A JP2004218466 A JP 2004218466A JP 2003004278 A JP2003004278 A JP 2003004278A JP 2003004278 A JP2003004278 A JP 2003004278A JP 2004218466 A JP2004218466 A JP 2004218466A
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cylinder
rotary compression
compression element
oil
rotary
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JP2003004278A
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JP4225793B2 (en
Inventor
Hiroyuki Matsumori
裕之 松森
Takayasu Saito
隆泰 斎藤
Takashi Sato
孝 佐藤
Masaru Matsuura
大 松浦
Toshiyuki Ebara
俊行 江原
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To certainly feed a second rotary compression element with oil in a traverse-mounted compressor equipped with the second rotary element pressurized higher than the inside of an airtight container. <P>SOLUTION: A multistage compression rotary compressor 10 is equipped with a driving element 14 inside the traverse-mounted airtight container 12 and a compression mechanism 18 driven by the driving element 14. The compression mechanism 18 comprises first and second rotary compression elements 32, 34. A cooling medium compressed by the first rotary compression element 32 is discharged to the inside of the airtight container 12. Further, the discharged cooling medium with intermediate pressure is compressed by the second rotary compression element 34 to be discharged. In a cylinder 38 of the second rotary compression element 34, an oil feeding pathway 106 is formed which makes a low-pressure chamber LR of the cylinder 38 communicate with the bottom of the airtight container 12. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、横置き型の密閉容器内に駆動要素と、この駆動要素にて駆動される圧縮機構部とを備え、この圧縮機構部にて冷媒を圧縮して吐出する横置き型圧縮機に関するものである。
【０００２】
【従来の技術】
従来よりこの種圧縮機としてのロータリコンプレッサ、特に第１の回転圧縮要素と第２の回転圧縮要素から成る圧縮機構部を備える多段圧縮式のロータリコンプレッサにおいては、通常縦型の密閉容器内上部に駆動要素を配置し、下部に当該駆動要素の回転軸で駆動される圧縮機構部を配置して構成されている。そして、第１の回転圧縮要素の吸込ポートから冷媒ガスがシリンダの低圧室側に吸入され、ローラとベーンの動作により圧縮されて、シリンダの高圧室側より吐出ポート、吐出消音室を経て密閉容器内に吐出される。このとき密閉容器内は中間圧となる（特許文献１参照）。
【０００３】
この密閉容器内の中間圧の冷媒ガスは第２の回転圧縮要素の吸込ポートからシリンダの低圧室側に吸入され、ローラとベーンの動作により２段目の圧縮が行われて高温高圧の冷媒ガスとなり、高圧室側より吐出ポート、吐出消音室を経て、コンプレッサ外部の放熱器に流入する構成とされていた。
【０００４】
また、係る縦型のロータリコンプレッサでは、圧縮機構部の下方に位置する密閉容器内底部がオイル溜めとされており、回転軸下端に構成されたオイルポンプによりオイル溜めからオイルが吸引され、圧縮機構部に供給されて圧縮機構部や回転軸の摺動部の摩耗を防ぎ、また、シールを確保していた。
【０００５】
更に、この種ロータリコンプレッサでは、密閉容器を横置きとして高さ寸法を縮小したものもあり、その場合には回転軸は水平方向に延在して第１及び第２の回転圧縮要素は左右に並設されたかたちとなる。
【０００６】
【特許文献１】
特開平２−２９４５８７号公報（第４頁、第５頁）。
【０００７】
【発明が解決しようとする課題】
ところで、係る多段圧縮式のロータリコンプレッサの第２の回転圧縮要素を構成するシリンダ内は、中間圧の密閉容器内よりも高い圧力となる。また、第２の回転圧縮要素に吸い込まれる冷媒は、密閉容器内に吐出された段階でそれに溶け込んだオイルを分離させている。そのため、どうしても第２の回転圧縮要素のシリンダ内への給油が困難な状況となり、オイル切れが発生し易いと云う問題があった。
【０００８】
本発明は、係る従来の技術的課題を解決するために成されたものであり、密閉容器内よりも高圧となる第２の回転圧縮要素を備えた横置き型圧縮機において、当該第２の回転圧縮要素への給油を確実に行うものである。
【０００９】
【課題を解決するための手段】
即ち、請求項１の発明の横置き型圧縮機は、圧縮機構部を第１及び第２の回転圧縮要素から構成し、当該第１の回転圧縮要素で圧縮された冷媒を密閉容器内に吐出し、更にこの吐出された中間圧の冷媒を第２の回転圧縮要素で圧縮して吐出するものであって、第２の回転圧縮要素のシリンダに、当該シリンダの低圧室と密閉容器内の底部とを連通する給油通路を形成し、密閉容器内と低圧室が略同圧であるため、密閉容器内底部に溜まっているオイルが、低圧室側の吸い込み冷媒の流れに引かれて第２の回転圧縮要素のシリンダに形成した給油通路を介して当該シリンダの低圧室に供給することが可能となる。
【００１０】
また、請求項２の発明の横置き型圧縮機は、上記に加えて、第２の回転圧縮要素のシリンダ底部に形成された切欠を備え、給油通路をこの切欠内に開口させたので、密閉容器底部に溜まったオイルを切欠から給油通路内に円滑に流入させることができるようになるものである。
【００１１】
また、請求項３の発明の横置き型圧縮機は、圧縮機構部を第１及び第２の回転圧縮要素から構成し、当該第１の回転圧縮要素で圧縮された冷媒を密閉容器内に吐出し、更にこの吐出された中間圧の冷媒を第２の回転圧縮要素で圧縮して吐出するものであって、第１の回転圧縮要素のシリンダと第２の回転圧縮要素のシリンダ間に挟持される中間仕切板に、第２の回転圧縮要素のシリンダの低圧室と密閉容器内の底部とを連通する給油通路を形成したので、密閉容器内底部に溜まるオイルを、中間仕切板に形成した給油通路を介して第２の回転圧縮要素のシリンダの低圧室に供給することが可能となる。
【００１２】
また、請求項４の発明の横置き型圧縮機は、上記各発明に加えて給油通路を、第２の回転圧縮要素のシリンダに傾斜して形成された吸込ポートの傾斜面に開口させたので、吸込ポートの角度を利用してシリンダに吸い込まれる冷媒の流れによりエジェクタ効果を発揮させることが可能となる。
【００１３】
【発明の実施の形態】
次に、図面に基づき本発明の実施形態を詳述する。図１は本発明の横置き型圧縮機の実施例として、第１及び第２の回転圧縮要素３２、３４を備えた横置き型の内部中間圧型多段圧縮式（２段）ロータリコンプレッサ１０の縦断正面図、図２は多段圧縮式ロータリコンプレッサ１０の第２のシリンダ３８の縦断側面図をそれぞれ示している。
【００１４】
各図において、１０は二酸化炭素（ＣＯ２）を冷媒として使用する横置き型の内部中間圧型多段圧縮式ロータリコンプレッサで、この多段圧縮式ロータリコンプレッサ１０は両端が密閉された横長円筒状の横置き型密閉容器１２を備え、この密閉容器１２の底部をオイル溜め１５としている。密閉容器１２は、容器本体１２Ａとこの容器本体１２Ａの開口を閉塞する略椀状のエンドキャップ（蓋体）１２Ｂとで構成されている。
【００１５】
この密閉容器１２内には電動モータから成る駆動要素１４と、水平方向に延在する駆動要素１４の回転軸１６により駆動される第１の回転圧縮要素３２及び第２の回転圧縮要素３４からなる圧縮機構部１８が左右に並設して収納されている。また、密閉容器１２の駆動要素１４側の端部には円形の取付孔１２Ｄが形成されており、この取付孔１２Ｄには駆動要素１４に電力を供給するためのターミナル２０（配線を省略）が取り付けられている。
【００１６】
駆動要素１４は、密閉容器１２の内周面に沿って環状に取り付けられたステータ２２と、このステータ２２の内側に若干の間隔を設けて挿入設置されたロータ２４とからなる。このロータ２４は中心を通り密閉容器１２の軸心方向（水平方向）に延在する回転軸１６に固定されている。
【００１７】
回転軸１６の圧縮機構部１８側の端部には給油手段としてのオイルポンプ８０が設けられている。このオイルポンプ８０は、密閉容器１２内の底部に形成されたオイル溜め１５から潤滑油としてのオイルを吸い上げて圧縮機構部１８や回転軸１６の摺動部に供給し、摩耗を防止し、且つ、シール性をあげるために設けられており、このオイルポンプ８０からは密閉容器１２の底部に向かってオイル吸上パイプ８０Ａが降下し、オイル溜め１５内にて開口している。
【００１８】
また、前記ステータ２２は、ドーナッツ状の電磁鋼板を積層した積層体２６と、この積層体２６の歯部に直巻き（集中巻き）方式により巻装されたステータコイル２８を有している。そして、前記ロータ２４もステータ２２と同様に電磁鋼板の積層体３０で形成され、この積層体３０内に永久磁石ＭＧを挿入して形成されている。
【００１９】
前記第１の回転圧縮要素３２と第２の回転圧縮要素３４は第１及び第２のシリンダ４０、３８によりそれぞれ構成され、これらシリンダ４０、３８間には中間仕切板３６が挟持されている。即ち、圧縮機構部１８は、第１の回転圧縮要素３２及び第２の回転圧縮要素３４と、中間仕切板３６などから構成される。各シリンダ４０、３８の外周は密閉容器１２の内面に当接若しくは近接している。
【００２０】
即ち、第１及び第２の回転圧縮要素３２、３４は、それぞれ中間仕切板３６の両側（図１では左右）に配置された前記第１及び第２のシリンダ４０、３８と、１８０度の位相差を有して回転軸１６に設けられた第１及び第２の偏心部４４、４２に嵌合され、第１及び第２のシリンダ４０、３８内を偏心回転する第１及び第２のローラ４８、４６と、これらローラ４８、４６にそれぞれ当接し、往復動してシリンダ４０、３８内をそれぞれ低圧室ＬＲ側と高圧室ＨＲ側（図２）とに区画する第１及び第２のベーン５２、５０と、シリンダ３８の駆動要素１４側の開口面とシリンダ４０の駆動要素１４とは反対側の開口面をそれぞれ閉塞して回転軸１６の軸受けを兼用する支持部材５４、５６とから構成されている。
【００２１】
両シリンダ４０、３８には第１及び第２のベーン５２、５０を摺動自在に収納するための案内溝７０と、この案内溝７０の外側には、第１及び第２のベーン５２、５０の外側端部に当接して、常時第１及び第２のベーン５２、５０をローラ４８、４６側に付勢するスプリング７６、７４が設けられている。更に、スプリング７６、７４の密閉容器１２側には金属製のプラグ７６Ａ、７４Ａが設けられ、スプリング７６、７４の抜け止めの役目を果たす。また、第２のベーン５０には背圧室７０Ａが構成され、この背圧室７０Ａにはシリンダ３８内の高圧室ＨＲ側の圧力が背圧として印加される。
【００２２】
尚、実施例の多段圧縮式ロータリコンプレッサ１０では、ベーン５２、５０は各シリンダ４０、３８の最下部に位置して上下動するように構成されている（図２）また、各シリンダ４０、３８内部の低圧室ＬＲに連通する吸込ポート１６２、１６１は図２に示す如く各ベーン５２、５０に隣接して形成されている。特に、吸込ポート１６２、１６１は、図３に示す如く支持部材５６、５４側が低く、中間仕切板３６側が高くなるように傾斜して形成され、そこを傾斜面１６２Ａ、１６１Ａとされている。
【００２３】
一方、支持部材５４、５６には、吸込ポート１６１、１６２にてシリンダ３８、４０内部の低圧室側ＬＲとそれぞれ連通する吸込通路５８、６０と、一部を凹陥させ、この凹陥部をカバー６６、６８にてそれぞれ閉塞することにより形成される吐出消音室６２、６４とが設けられている。尚、図３において１６３は、シリンダ３８内部の高圧室ＨＲに連通して形成された吐出ポートである（シリンダ４０側は図示せず）。
【００２４】
第２の回転圧縮要素３４のシリンダ３８の吸込ポート１６１の延長線上に対応する位置の底部は、中間仕切板３６側と支持部材５４側に渡って内側に切り欠かれ、そこに回転軸１６方向に所定寸法凹陥した切欠３８Ａが形成されている（図２、図３）。この切欠３８Ａは、密閉容器１２底部のオイル溜め１５内に位置している。そして、シリンダ３８内には、この切欠３８Ａと吸込ポート１６１間に渡る給油通路１０６が形成されている。
【００２５】
この給油通路１０６の上端は、シリンダ３８に傾斜して形成された前記吸込ポート１６１の傾斜面１６１Ａに開口すると共に、給油通路１０６の下端は切欠３８Ａ内に開口している。即ち、給油通路１０６は傾斜面１６１Ａにおいて斜めの開口部１０６Ａを有し、シリンダ３８の低圧室ＬＲ側と密閉容器１２底部のオイル溜め１５とを連通させる。
【００２６】
前記吐出消音室６４と密閉容器１２内は、シリンダ４０、３８や中間仕切板３６、カバー６６を貫通し、更に、このカバー６６から離間して設けられた後述するバッフル板１００も貫通して駆動要素１４側に開口する図示しない連通路にて連通されており、連通路の端部には中間吐出管１２１が突設されている。この中間吐出管１２１から第１の回転圧縮要素３２で圧縮された中間圧の冷媒ガスが密閉容器１２内の駆動要素１４側に吐出される。このとき冷媒ガス中には第１の回転圧縮要素３２に供給されたオイルが混入しているが、このオイルも密閉容器１２内の駆動要素１４側に吐出されることになる。ここで、冷媒ガス中に混入したオイルは冷媒ガスから分離して密閉容器１２内底部のオイル溜め１５に貯留される。
【００２７】
そして、前述したバッフル板１００は密閉容器１２内を駆動要素１４側と圧縮機構部１８側とに区画して、密閉容器１２内に差圧を構成するために設けられる。このバッフル板１００は、密閉容器１２の内面との間に少許間隔を存して配設されたドーナッツ状の鋼板からなる。この場合、第１の回転圧縮要素３２で圧縮され、密閉容器１２内の駆動要素１４側に吐出された中間圧の冷媒ガスは、密閉容器１２とバッフル板１００の間に形成された隙間を通って圧縮機構部１８側に流入することになるが、係るバッフル板１００の存在により、密閉容器１２内にはバッフル板１００の駆動要素１４側の圧力は高く、圧縮機構部１８側が低い差圧が構成される。
【００２８】
そして、この差圧によって密閉容器１２内底部のオイル溜め１５に貯溜されたオイルは圧縮機構部１８側に移動し、バッフル板１００より圧縮機構部１８側のオイルレベルが上昇する。この場合、密閉容器１２底部のオイル溜め１５に貯溜されたオイルの上面は、少なくともオイル吸上パイプ８０Ａ下端及び給油通路１０６の下端開口（切欠３８Ａ）より上まで満たされる。
【００２９】
ここで、吸込ポート１６１の傾斜面１６１Ａに開口させた給油通路１０６の開口部１０６Ａと、吸込ポート１６１の傾斜面１６１Ａの角度（第２の回転圧縮要素３４の冷媒の吸気の流れ方向の角度）は、エジェクタ機能を生じやすい角度に構成する。これにより、吸込ポート１６１からシリンダ３８の低圧室ＬＲ側に吸い込まれる冷媒ガスによって開口部１０６Ａにエジェクタ機能が発生し、給油通路１０６内は低圧となるので、密閉容器１２底部のオイル溜め１５に貯溜されたオイルは、給油通路１０６内を吸い上げられて開口部１０６Ａからシリンダ３８の低圧室ＬＲ側に吸い込まれるようになる。一方、オイル吸上パイプ８０Ａの開口はオイル中に浸漬されるので、オイルポンプ８０による圧縮機構部１８の摺動部へのオイルの供給も円滑に行われる。
【００３０】
そして、この場合の冷媒としては、地球環境にやさしく可燃性及び毒性等を考慮して自然冷媒である前記ＣＯ２（二酸化炭素）を使用し、密閉容器１２内に封入される潤滑油としてのオイルとしては、例えば鉱物油（ミネラルオイル）、アルキルベンゼン油、エーテル油、エステル油、ＰＡＧ（ポリアルキルグリコール）等既存のオイルが使用される。
【００３１】
密閉容器１２の側面には、支持部材５６と支持部材５４の側部に対応する位置にスリーブ１４１、１４２、１４３がそれぞれ溶接固定されている。そして、スリーブ１４２内にはシリンダ４０に冷媒を導入するための冷媒導入管９４の一端が挿入接続され、吸込通路６０に連通されている。そして、スリーブ１４１内にはシリンダ３８に冷媒ガスを流入するための冷媒導入管９２の一端が挿入接続され、この冷媒導入管９２の一端はシリンダ３８の吸込通路５８と連通する。
【００３２】
この冷媒導入管９２は密閉容器１２外の上側を通過してスリーブ１４４に至り、他端はスリーブ１４４内に挿入接続されてバッフル板１００の駆動要素１４側（駆動要素１４とバッフル板１００との間）の密閉容器１２内上部に連通する。また、スリーブ１４３内には冷媒吐出管９６が挿入され、この冷媒吐出管９６の一端は吐出消音室６２に連通されている。更に、密閉容器１２の底部には取付用台座１１０が設けられている（図１）。
【００３３】
以上の構成で次に動作を説明する。ターミナル２０及び図示されない配線を介して駆動要素１４のステータコイル２８に通電されると、駆動要素１４が起動してロータ２４が回転する。この回転により回転軸１６と一体に設けた第１及び第２の偏心部４４、４２に嵌合されたローラ４８、４６がシリンダ４０、３８内を偏心回転する。
【００３４】
これにより、冷媒導入管９４及び支持部材５６に形成された吸込通路６０を経由して吸込ポート１６２から第１の回転圧縮要素３２のシリンダ４０の低圧室ＬＲ側に吸入された冷媒（低圧）は、ローラ４８とベーン５２の動作により圧縮されて中間圧となり、シリンダ４０の高圧室ＨＲ側より吐出消音室６４に吐出され、そこから前述した連通路を経て中間吐出管１２１より密閉容器１２内に吐出される。これによって、密閉容器１２内は中間圧となり、冷媒ガスに混入しているオイルは密閉容器１２の内面に付着し、密閉容器１２の内面を伝わって底部のオイル溜め１５に帰還する。
【００３５】
そして、密閉容器１２内の中間圧の冷媒ガスは、冷媒導入管９２に流入して密閉容器１２外の上側を通過し、吸込通路５８から吸込ポート１６１を経て第２の回転圧縮要素３４のシリンダ３８の低圧室ＬＲ側に吸入される。このとき、吸込ポート１６１から冷媒が吸入される課程で吸込ポート１６１の傾斜面１６１Ａと開口１０６Ａの角度がエジェクタとして機能するので、密閉容器１２内底部のオイル溜め１５に貯溜されたオイルは給油通路１０６内に吸い上げられ、開口部１０６Ａからシリンダ３８の低圧室ＬＲ側に吸い込まれる。これによって、第２の回転圧縮要素３４の摺動部へオイルの供給を極めて確実に行うことができる。給油通路１０６はシリンダ３８に形成された切欠３８Ａ内において密閉容器１２内面から離間して開口しているので、オイル溜め１５内のオイルは円滑に流入できる。
【００３６】
そして、シリンダ３８の低圧室ＬＲ側に吸入された中間圧の冷媒ガスは、ローラ４６とベーン５０の動作により２段目の圧縮が行われて高温・高圧の冷媒ガスとなる。高温・高圧の冷媒ガスは、高圧室ＨＲ側から吐出ポート１６３を通り、支持部材５４内に形成された吐出消音室６２を経て、冷媒吐出管９６から外部の図示しないガスクーラ（放熱器）などに流入する。このガスクーラで冷媒は放熱した後、図示しない減圧装置などで減圧され、これもまた図示しないエバポレータに流入する。
【００３７】
そこで冷媒が蒸発し、その後、前記アキュムレータを経て冷媒導入管９４から第１の回転圧縮要素３２内に吸い込まれるサイクルを繰り返す。
【００３８】
このように、密閉容器１２内底部のオイル溜め１５に貯溜されたオイルを給油通路１０６から直接吸込ポート１６１に吸い上げることができる。これにより、密閉容器１２内よりも高圧となる第２の回転圧縮要素３４のシリンダ３８内の潤滑とシール性の確保がなされる。
【００３９】
次に、図４には本発明の他の実施例の横置き型圧縮機としての多段圧縮式ロータリコンプレッサ１０を示している。尚、この図において図１乃至図３と同一符号は同一若しくは同様の作用を奏するものとする。この場合もシリンダ３８に設けられた吸込ポート１６１と密閉容器１２内の底部のオイル溜め１５との間に給油通路１１４を形成しているが、この給油通路１１４は、中間仕切板３６に形成された縦通路１１６と第２のシリンダ３８に形成された横通路１１８にて構成されている。
【００４０】
第２のシリンダ３８に形成された横通路１１８の一端は吸込ポート１６１の傾斜面１６１Ａに位置して前述同様に開口すると共に、他端は中間仕切板３６まで延在している。また、中間仕切板３６に形成された縦通路１１６は下端が密閉容器１２内の底部に開口すると共に、上端は第２のシリンダ３８に形成された横通路１１８の高さまで延在し、そこで折れ曲がって横通路１１８の他端に連通している。即ち、給油通路１１４は吸込ポート１６１から横通路１１８、縦通路１１６を経て密閉容器１２内の底部のオイル溜め１５に開口している。そして、給油通路１１４は、吸込ポート１６１内の斜めの開口を開口部１１８Ａとしている。他は前述同様に構成されている。
【００４１】
これによって、前述同様に２段目の第２の回転圧縮要素３４のシリンダ３８内に円滑に給油を行うことができるようになる。特に、この場合には給油通路１１４の殆ど（縦通路１１６）が中間仕切板３６に形成されることになるので、全てシリンダ３８内に形成する場合に比して加工が容易となり、生産コストの低減が図れるようになる。
【００４２】
【発明の効果】
以上詳述した如く本願の発明によれば、第２の回転圧縮要素のシリンダに、当該シリンダの低圧室と密閉容器内の底部とを連通する給油通路を形成したので、密閉容器内底部に溜まるオイルを、第２の回転圧縮要素のシリンダに形成した給油通路を介して当該シリンダの低圧室に供給することが可能となる。これにより、密閉容器内よりも高圧となる第２の回転圧縮要素のシリンダ内に確実に給油を行うことができるようになり、摺動部の潤滑とシール性を確保することができるようになるものである。
【００４３】
また、請求項３の発明によれば、第１の回転圧縮要素のシリンダと第２の回転圧縮要素のシリンダ間に挟持される中間仕切板に、第２の回転圧縮要素のシリンダの低圧室と密閉容器内の底部とを連通する給油通路を形成したので、密閉容器内底部に溜まるオイルを、中間仕切板に形成した給油通路を介して第２の回転圧縮要素のシリンダの低圧室に供給することが可能となる。これにより、密閉容器内よりも高圧となる第２の回転圧縮要素のシリンダ内に確実に給油を行うことができるようになり、摺動部の潤滑とシール性を確保することができるようになる。特に、この場合は加工が比較的容易となるので、生産コストの高騰も抑制できるものである。
【００４４】
また、請求項４の発明によれば、密閉容器内底部に溜まったオイルを給油通路内に円滑に吸い上げることができるようになり、第２の回転圧縮要素のシリンダ内への給油性能の更なる向上を図ることができるようになるものである。
【図面の簡単な説明】
【図１】本発明の実施例の横置き型の内部中間圧型多段圧縮式ロータリコンプレッサの縦断正面図（図２のＡ−Ａ線断面に相当）である。
【図２】図１の多段圧縮式ロータリコンプレッサの第２のシリンダの縦断側面図である。
【図３】本発明の多段圧縮式ロータリコンプレッサの図２のＢ−Ｂ線断面図である。
【図４】本発明の他の実施例における多段圧縮式ロータリコンプレッサの図２のＢ−Ｂ線断面図である。
【符号の説明】
１０ 多段圧縮式ロータリコンプレッサ
１２ 密閉容器
１２Ａ 容器本体
１５ オイル溜め
１８ 圧縮機構部
３２ 第１の回転圧縮要素
３４ 第２の回転圧縮要素
３６ 中間仕切板
３８、４０ シリンダ
３８Ａ 切欠
４２、４４ 偏心部
４６、４８ ローラ
５０ 第２のベーン
５２ 第１のベーン
５４ 支持部材
５８ 吸込通路
１０６ 給油通路
１０６Ａ 開口部
１６１ 吸込ポート
１６１Ａ 傾斜面[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a horizontal compressor in which a driving element and a compression mechanism driven by the driving element are provided in a horizontal closed container, and the compression mechanism compresses and discharges the refrigerant. Things.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, in a rotary compressor as a compressor of this type, particularly in a multistage compression type rotary compressor having a compression mechanism section including a first rotary compression element and a second rotary compression element, usually a vertical compressor has an upper portion inside a closed container. A driving element is arranged, and a compression mechanism driven by a rotating shaft of the driving element is arranged below the driving element. Refrigerant gas is sucked into the low pressure chamber side of the cylinder from the suction port of the first rotary compression element, is compressed by the operation of the rollers and vanes, and is discharged from the high pressure chamber side of the cylinder through the discharge port and the discharge muffling chamber. It is discharged into. At this time, the inside of the sealed container has an intermediate pressure (see Patent Document 1).
[0003]
The intermediate-pressure refrigerant gas in the closed container is sucked into the low-pressure chamber side of the cylinder from the suction port of the second rotary compression element, and the second-stage compression is performed by the operation of the roller and the vane, so that the high-temperature and high-pressure refrigerant gas is discharged. Thus, the configuration is such that the gas flows from the high-pressure chamber through a discharge port and a discharge muffling chamber to a radiator outside the compressor.
[0004]
Further, in such a vertical rotary compressor, an oil reservoir is provided at the bottom of the sealed container located below the compression mechanism, and oil is sucked from the oil reservoir by an oil pump formed at the lower end of the rotating shaft, and the compression mechanism To prevent abrasion of the compression mechanism and the sliding part of the rotating shaft, and to secure a seal.
[0005]
Furthermore, in this type of rotary compressor, there is also a type in which the height is reduced by placing the closed container horizontally, and in this case, the rotating shaft extends in the horizontal direction, and the first and second rotary compression elements are moved to the left and right. It is in the form of juxtaposition.
[0006]
[Patent Document 1]
JP-A-2-294587 (pages 4 and 5).
[0007]
[Problems to be solved by the invention]
By the way, the pressure inside the cylinder constituting the second rotary compression element of the multistage compression type rotary compressor is higher than the pressure inside the closed vessel of the intermediate pressure. Further, the refrigerant sucked into the second rotary compression element separates oil dissolved therein at the stage when the refrigerant is discharged into the closed container. Therefore, it is difficult to supply the second rotary compression element into the cylinder, and there is a problem that oil shortage is likely to occur.
[0008]
The present invention has been made in order to solve such a conventional technical problem, and in a horizontal compressor having a second rotary compression element having a higher pressure than that in an airtight container, the present invention relates to This ensures that the rotary compression element is refueled.
[0009]
[Means for Solving the Problems]
That is, in the horizontal compressor according to the first aspect of the present invention, the compression mechanism section includes the first and second rotary compression elements, and the refrigerant compressed by the first rotary compression element is discharged into the closed container. Further, the discharged intermediate-pressure refrigerant is compressed and discharged by the second rotary compression element, and the cylinder of the second rotary compression element is provided with a low-pressure chamber of the cylinder and a bottom portion in the closed container. And the low-pressure chamber has substantially the same pressure in the closed container, so that the oil accumulated in the bottom of the closed container is drawn by the flow of the suction refrigerant on the low-pressure chamber side to the second pressure. The oil can be supplied to the low pressure chamber of the rotary compression element via an oil supply passage formed in the cylinder.
[0010]
In addition to the above, the horizontal type compressor according to the second aspect of the present invention further includes a notch formed in the bottom of the cylinder of the second rotary compression element, and the oil supply passage is opened in the notch. The oil accumulated in the bottom of the container can smoothly flow into the oil supply passage from the notch.
[0011]
Further, in the horizontal compressor according to the third aspect of the present invention, the compression mechanism section includes the first and second rotary compression elements, and the refrigerant compressed by the first rotary compression element is discharged into the closed container. Further, the discharged intermediate-pressure refrigerant is compressed and discharged by the second rotary compression element, and is sandwiched between the cylinder of the first rotary compression element and the cylinder of the second rotary compression element. The intermediate partition plate is provided with an oil supply passage communicating the low pressure chamber of the cylinder of the second rotary compression element with the bottom of the sealed container. It is possible to supply the low-pressure chamber of the cylinder of the second rotary compression element via the passage.
[0012]
Also, in the horizontal compressor according to the fourth aspect of the present invention, in addition to the above inventions, the oil supply passage is opened on the inclined surface of the suction port formed to be inclined in the cylinder of the second rotary compression element. The ejector effect can be exhibited by the flow of the refrigerant sucked into the cylinder using the angle of the suction port.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
Next, an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 shows, as an embodiment of a horizontal compressor of the present invention, a longitudinal section of a horizontal internal multi-stage compression type (two-stage) rotary compressor 10 having first and second rotary compression elements 32 and 34. FIG. 2 is a front view, and FIG. 2 is a vertical sectional side view of a second cylinder 38 of the multistage rotary compressor 10.
[0014]
In each of the figures, reference numeral 10 denotes a horizontal internal-pressure multistage compression type rotary compressor using carbon dioxide (CO 2 ) as a refrigerant. The multistage compression type rotary compressor 10 has a horizontally long cylindrical shape with both ends sealed. The closed container 12 is provided with an oil reservoir 15 at the bottom. The closed container 12 includes a container body 12A and a substantially bowl-shaped end cap (lid) 12B for closing an opening of the container body 12A.
[0015]
A drive element 14 composed of an electric motor, a first rotary compression element 32 and a second rotary compression element 34 driven by the rotation shaft 16 of the drive element 14 extending in the horizontal direction are provided in the closed container 12. The compression mechanism units 18 are housed side by side on the left and right. A circular mounting hole 12D is formed at the end of the closed container 12 on the driving element 14 side, and a terminal 20 (wiring is omitted) for supplying power to the driving element 14 is formed in the mounting hole 12D. Installed.
[0016]
The driving element 14 includes a stator 22 annularly mounted along the inner peripheral surface of the closed casing 12, and a rotor 24 inserted inside the stator 22 with a slight space therebetween. The rotor 24 is fixed to a rotating shaft 16 that extends through the center in the axial direction (horizontal direction) of the sealed container 12.
[0017]
An oil pump 80 is provided at the end of the rotary shaft 16 on the side of the compression mechanism 18 as oil supply means. The oil pump 80 sucks up oil as a lubricating oil from an oil reservoir 15 formed at the bottom of the closed container 12 and supplies the lubricating oil to a sliding portion of the compression mechanism 18 and the rotary shaft 16 to prevent abrasion, and An oil suction pipe 80A descends from the oil pump 80 toward the bottom of the sealed container 12, and is opened in the oil reservoir 15.
[0018]
The stator 22 has a laminated body 26 in which donut-shaped electromagnetic steel sheets are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method. The rotor 24 is also formed of a laminated body 30 of electromagnetic steel sheets, like the stator 22, and is formed by inserting a permanent magnet MG into the laminated body 30.
[0019]
The first rotary compression element 32 and the second rotary compression element 34 are constituted by first and second cylinders 40 and 38, respectively, and an intermediate partition plate 36 is sandwiched between the cylinders 40 and 38. That is, the compression mechanism section 18 includes a first rotary compression element 32 and a second rotary compression element 34, an intermediate partition plate 36, and the like. The outer periphery of each of the cylinders 40 and 38 is in contact with or close to the inner surface of the closed container 12.
[0020]
That is, the first and second rotary compression elements 32 and 34 are respectively connected to the first and second cylinders 40 and 38 disposed on both sides (left and right in FIG. 1) of the intermediate partition plate 36 by 180 degrees. First and second rollers that are fitted to first and second eccentric portions 44 and 42 provided on the rotating shaft 16 with a phase difference and that rotate eccentrically in the first and second cylinders 40 and 38. First and second vanes 48, 46 contact the rollers 48, 46, respectively, and reciprocate to partition the cylinders 40, 38 into a low-pressure chamber LR side and a high-pressure chamber HR side (FIG. 2). 52, 50, and support members 54, 56 which respectively close the opening surface of the cylinder 38 on the drive element 14 side and the opening surface of the cylinder 40 on the side opposite to the drive element 14 and also serve as a bearing for the rotary shaft 16. Have been.
[0021]
Guide grooves 70 for slidably storing the first and second vanes 52, 50 are provided in both cylinders 40, 38, and first and second vanes 52, 50 are provided outside the guide grooves 70. Springs 76 and 74 are provided to contact the outer ends of the rollers and constantly bias the first and second vanes 52 and 50 toward the rollers 48 and 46. Further, metal plugs 76A and 74A are provided on the closed container 12 side of the springs 76 and 74, and serve to prevent the springs 76 and 74 from coming off. A back pressure chamber 70A is formed in the second vane 50, and the pressure on the high pressure chamber HR side in the cylinder 38 is applied to the back pressure chamber 70A as a back pressure.
[0022]
In the multi-stage compression type rotary compressor 10 of the embodiment, the vanes 52 and 50 are located at the lowermost positions of the cylinders 40 and 38 so as to move up and down (FIG. 2). The suction ports 162 and 161 communicating with the internal low pressure chamber LR are formed adjacent to the vanes 52 and 50 as shown in FIG. In particular, the suction ports 162 and 161 are formed so as to be inclined such that the support members 56 and 54 are lower and the intermediate partition plate 36 is higher as shown in FIG. 3, and are formed as inclined surfaces 162A and 161A.
[0023]
On the other hand, suction members 58 and 60 communicating with the low pressure chamber LR inside the cylinders 38 and 40 at the suction ports 161 and 162, respectively, are partially recessed in the support members 54 and 56, and these recesses are covered with a cover 66. , 68 are provided, respectively. In FIG. 3, reference numeral 163 denotes a discharge port formed so as to communicate with the high-pressure chamber HR inside the cylinder 38 (the cylinder 40 side is not shown).
[0024]
The bottom of the second rotary compression element 34 at a position corresponding to the extension of the suction port 161 of the cylinder 38 is cut inward across the intermediate partition plate 36 side and the support member 54 side, where Is formed with a notch 38A having a predetermined size (FIGS. 2 and 3). The notch 38A is located in the oil reservoir 15 at the bottom of the closed container 12. In the cylinder 38, an oil supply passage 106 is formed to extend between the notch 38A and the suction port 161.
[0025]
The upper end of the oil supply passage 106 is open to the inclined surface 161A of the suction port 161 formed to be inclined to the cylinder 38, and the lower end of the oil supply passage 106 is open to the notch 38A. That is, the oil supply passage 106 has an oblique opening portion 106A on the inclined surface 161A, and connects the low pressure chamber LR side of the cylinder 38 to the oil reservoir 15 at the bottom of the sealed container 12.
[0026]
The discharge muffling chamber 64 and the inside of the sealed container 12 penetrate through the cylinders 40 and 38, the intermediate partition plate 36, and the cover 66, and further drive through a baffle plate 100 described later provided separately from the cover 66. It communicates with a communication passage (not shown) that opens to the element 14 side, and an intermediate discharge pipe 121 is protruded from an end of the communication passage. The intermediate-pressure refrigerant gas compressed by the first rotary compression element 32 is discharged from the intermediate discharge pipe 121 toward the drive element 14 in the closed casing 12. At this time, the oil supplied to the first rotary compression element 32 is mixed in the refrigerant gas, and this oil is also discharged to the drive element 14 side in the closed container 12. Here, the oil mixed in the refrigerant gas is separated from the refrigerant gas and stored in the oil reservoir 15 at the bottom of the closed container 12.
[0027]
The above-mentioned baffle plate 100 is provided to divide the inside of the closed container 12 into the drive element 14 side and the compression mechanism section 18 side, and to form a differential pressure in the closed container 12. The baffle plate 100 is made of a donut-shaped steel plate disposed at a small distance from the inner surface of the closed container 12. In this case, the intermediate-pressure refrigerant gas compressed by the first rotary compression element 32 and discharged to the drive element 14 side in the sealed container 12 passes through a gap formed between the sealed container 12 and the baffle plate 100. However, due to the presence of the baffle plate 100, the pressure on the drive element 14 side of the baffle plate 100 is high and the differential pressure on the compression mechanism portion 18 side is low due to the presence of the baffle plate 100. Be composed.
[0028]
Then, due to this differential pressure, the oil stored in the oil reservoir 15 at the bottom of the closed container 12 moves to the compression mechanism 18 side, and the oil level on the compression mechanism 18 side rises from the baffle plate 100. In this case, the upper surface of the oil stored in the oil reservoir 15 at the bottom of the sealed container 12 is filled at least above the lower end of the oil suction pipe 80A and the lower end opening (notch 38A) of the oil supply passage 106.
[0029]
Here, the angle between the opening 106A of the oil supply passage 106 opened to the inclined surface 161A of the suction port 161 and the inclined surface 161A of the suction port 161 (the angle in the flow direction of the intake air of the refrigerant of the second rotary compression element 34). Are formed at an angle that easily causes the ejector function. Thereby, an ejector function is generated in the opening 106A by the refrigerant gas sucked from the suction port 161 to the low pressure chamber LR side of the cylinder 38, and the pressure in the oil supply passage 106 becomes low, so that the oil is stored in the oil reservoir 15 at the bottom of the closed container 12. The sucked oil is sucked up in the oil supply passage 106 and is sucked into the low pressure chamber LR side of the cylinder 38 from the opening 106A. On the other hand, the opening of the oil suction pipe 80A is immersed in the oil, so that the oil pump 80 smoothly supplies the oil to the sliding portion of the compression mechanism 18.
[0030]
As the refrigerant in this case, the CO 2 (carbon dioxide), which is a natural refrigerant in consideration of flammability and toxicity, which is friendly to the global environment, is used, and an oil as a lubricating oil sealed in the closed container 12 is used. For example, existing oils such as mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil, and PAG (polyalkyl glycol) are used.
[0031]
Sleeves 141, 142, and 143 are fixed to the side surfaces of the sealed container 12 at positions corresponding to the side portions of the support members 56 and 54, respectively, by welding. One end of a refrigerant introduction pipe 94 for introducing refrigerant into the cylinder 40 is inserted and connected into the sleeve 142, and communicates with the suction passage 60. One end of a refrigerant introduction pipe 92 for flowing refrigerant gas into the cylinder 38 is inserted into the sleeve 141 and one end of the refrigerant introduction pipe 92 communicates with the suction passage 58 of the cylinder 38.
[0032]
The refrigerant introduction pipe 92 passes through the upper side of the outside of the closed container 12 to reach the sleeve 144, and the other end is inserted and connected into the sleeve 144 to be connected to the drive element 14 side of the baffle plate 100 (the drive element 14 and the baffle plate 100 The upper part of the closed container 12 communicates with the upper part. A refrigerant discharge pipe 96 is inserted into the sleeve 143, and one end of the refrigerant discharge pipe 96 is connected to the discharge muffling chamber 62. Further, a mounting pedestal 110 is provided at the bottom of the sealed container 12 (FIG. 1).
[0033]
Next, the operation of the above configuration will be described. When the stator coil 28 of the driving element 14 is energized via the terminal 20 and the wiring (not shown), the driving element 14 starts and the rotor 24 rotates. By this rotation, the rollers 48 and 46 fitted to the first and second eccentric portions 44 and 42 provided integrally with the rotating shaft 16 eccentrically rotate inside the cylinders 40 and 38.
[0034]
As a result, the refrigerant (low pressure) sucked from the suction port 162 to the low pressure chamber LR side of the cylinder 40 of the first rotary compression element 32 via the refrigerant introduction pipe 94 and the suction passage 60 formed in the support member 56. , Are compressed to an intermediate pressure by the operation of the roller 48 and the vane 52, discharged from the high pressure chamber HR side of the cylinder 40 to the discharge muffling chamber 64, and from there through the communication passage into the closed container 12 through the intermediate discharge pipe 121. Discharged. As a result, the pressure inside the closed container 12 becomes an intermediate pressure, and the oil mixed in the refrigerant gas adheres to the inner surface of the closed container 12 and returns to the bottom oil reservoir 15 along the inner surface of the closed container 12.
[0035]
Then, the intermediate-pressure refrigerant gas in the sealed container 12 flows into the refrigerant introduction pipe 92 and passes above the outside of the sealed container 12, and passes from the suction passage 58 to the cylinder of the second rotary compression element 34 through the suction port 161. It is sucked into the low pressure chamber LR side of 38. At this time, the angle between the inclined surface 161A of the suction port 161 and the opening 106A functions as an ejector in a process in which the refrigerant is sucked from the suction port 161. It is sucked up into the inside 106 and is sucked into the low pressure chamber LR side of the cylinder 38 from the opening 106A. This makes it possible to supply the oil to the sliding portion of the second rotary compression element 34 very reliably. Since the oil supply passage 106 is open in the notch 38A formed in the cylinder 38 at a distance from the inner surface of the closed container 12, the oil in the oil reservoir 15 can flow in smoothly.
[0036]
Then, the intermediate-pressure refrigerant gas sucked into the low-pressure chamber LR side of the cylinder 38 is subjected to the second-stage compression by the operation of the roller 46 and the vane 50 to become a high-temperature and high-pressure refrigerant gas. The high-temperature and high-pressure refrigerant gas passes through the discharge port 163 from the high-pressure chamber HR, passes through the discharge muffling chamber 62 formed in the support member 54, and flows from the refrigerant discharge pipe 96 to an external gas cooler (radiator) (not shown). Inflow. After the refrigerant radiates heat in the gas cooler, the pressure is reduced by a pressure reducing device (not shown) or the like, and also flows into an evaporator (not shown).
[0037]
Then, a cycle in which the refrigerant evaporates and thereafter is sucked into the first rotary compression element 32 from the refrigerant introduction pipe 94 through the accumulator is repeated.
[0038]
In this manner, the oil stored in the oil reservoir 15 at the bottom of the closed container 12 can be sucked directly from the oil supply passage 106 to the suction port 161. As a result, lubrication and sealing performance in the cylinder 38 of the second rotary compression element 34, which has a higher pressure than in the sealed container 12, are ensured.
[0039]
Next, FIG. 4 shows a multi-stage rotary compressor 10 as a horizontal compressor according to another embodiment of the present invention. In this figure, the same reference numerals as those in FIGS. 1 to 3 have the same or similar functions. In this case as well, an oil supply passage 114 is formed between the suction port 161 provided in the cylinder 38 and the oil reservoir 15 at the bottom in the sealed container 12, and this oil supply passage 114 is formed in the intermediate partition plate 36. A vertical passage 116 and a horizontal passage 118 formed in the second cylinder 38.
[0040]
One end of the horizontal passage 118 formed in the second cylinder 38 is located on the inclined surface 161A of the suction port 161 and is opened as described above, and the other end extends to the intermediate partition plate 36. The vertical passage 116 formed in the intermediate partition plate 36 has a lower end opening to the bottom in the closed container 12 and an upper end extending to the height of the horizontal passage 118 formed in the second cylinder 38, where it is bent. And communicates with the other end of the lateral passage 118. That is, the oil supply passage 114 is opened from the suction port 161 to the oil reservoir 15 at the bottom in the sealed container 12 via the horizontal passage 118 and the vertical passage 116. The oil supply passage 114 has an oblique opening in the suction port 161 as an opening 118A. Others are configured as described above.
[0041]
This makes it possible to smoothly supply oil into the cylinder 38 of the second rotary compression element 34 in the second stage as described above. In particular, in this case, most of the oil supply passage 114 (vertical passage 116) is formed in the intermediate partition plate 36, so that processing is easier than when all are formed in the cylinder 38, and production costs are reduced. The reduction can be achieved.
[0042]
【The invention's effect】
According to the invention of the present application, as described in detail above, the cylinder of the second rotary compression element is formed with the oil supply passage that communicates the low-pressure chamber of the cylinder with the bottom of the closed vessel, and thus accumulates at the bottom of the closed vessel. The oil can be supplied to the low pressure chamber of the second rotary compression element via an oil supply passage formed in the cylinder. Accordingly, it is possible to reliably supply oil to the cylinder of the second rotary compression element having a higher pressure than in the closed container, and it is possible to ensure lubrication and sealing of the sliding portion. Things.
[0043]
According to the invention of claim 3, the low pressure chamber of the cylinder of the second rotary compression element is provided on the intermediate partition plate sandwiched between the cylinder of the first rotary compression element and the cylinder of the second rotary compression element. Since the oil supply passage communicating with the bottom in the closed container is formed, the oil accumulated in the bottom in the closed container is supplied to the low pressure chamber of the cylinder of the second rotary compression element via the oil supply passage formed in the intermediate partition plate. It becomes possible. Accordingly, it is possible to reliably supply oil to the cylinder of the second rotary compression element having a higher pressure than in the closed container, and it is possible to ensure lubrication and sealing of the sliding portion. . In particular, in this case, since the processing is relatively easy, it is possible to suppress a rise in production cost.
[0044]
According to the fourth aspect of the present invention, it is possible to smoothly suck up the oil accumulated in the bottom of the closed container into the oil supply passage, and further improve the oil supply performance of the second rotary compression element into the cylinder. It is possible to improve it.
[Brief description of the drawings]
FIG. 1 is a vertical sectional front view (corresponding to a cross section taken along line AA in FIG. 2) of a horizontal type internal intermediate pressure type multistage compression type rotary compressor of an embodiment of the present invention.
FIG. 2 is a vertical sectional side view of a second cylinder of the multi-stage compression type rotary compressor of FIG. 1;
FIG. 3 is a cross-sectional view of the multi-stage compression type rotary compressor of the present invention, taken along line BB of FIG. 2;
FIG. 4 is a cross-sectional view of the multi-stage compression type rotary compressor according to another embodiment of the present invention, taken along line BB of FIG. 2;
[Explanation of symbols]
Reference Signs List 10 multistage rotary compressor 12 closed container 12A container body 15 oil reservoir 18 compression mechanism 32 first rotary compression element 34 second rotary compression element 36 intermediate partition plate 38, 40 cylinder 38A notch 42, 44 eccentric part 46, 48 roller 50 second vane 52 first vane 54 support member 58 suction passage 106 oil supply passage 106A opening 161 suction port 161A inclined surface

Claims (4)

圧縮機構部を第１及び第２の回転圧縮要素から構成し、当該第１の回転圧縮要素で圧縮された冷媒を前記密閉容器内に吐出し、更にこの吐出された中間圧の冷媒を前記第２の回転圧縮要素で圧縮して吐出する横置き型圧縮機において、
前記第２の回転圧縮要素のシリンダに、当該シリンダの低圧室と前記密閉容器内の底部とを連通する給油通路を形成したことを特徴とする横置き型圧縮機。The compression mechanism section includes first and second rotary compression elements, discharges the refrigerant compressed by the first rotary compression element into the closed container, and further discharges the discharged intermediate-pressure refrigerant to the second container. In a horizontal compressor that compresses and discharges with a rotary compression element of 2,
A horizontal compressor in which a cylinder of the second rotary compression element is provided with an oil supply passage for communicating a low-pressure chamber of the cylinder with a bottom of the closed vessel. 前記第２の回転圧縮要素のシリンダ底部に形成された切欠を備え、前記給油通路は該切欠内に開口することを特徴とする請求項１の横置き型圧縮機。2. The horizontal compressor according to claim 1, further comprising a notch formed in a bottom of a cylinder of the second rotary compression element, wherein the oil supply passage is opened in the notch. 圧縮機構部を第１及び第２の回転圧縮要素から構成し、当該第１の回転圧縮要素で圧縮された冷媒を前記密閉容器内に吐出し、更にこの吐出された中間圧の冷媒を前記第２の回転圧縮要素で圧縮して吐出する横置き型圧縮機において、
前記第１の回転圧縮要素のシリンダと第２の回転圧縮要素のシリンダ間に挟持される中間仕切板に、前記第２の回転圧縮要素のシリンダの低圧室と前記密閉容器内の底部とを連通する給油通路を形成したことを特徴とする横置き型圧縮機。The compression mechanism section includes first and second rotary compression elements, discharges the refrigerant compressed by the first rotary compression element into the closed container, and further discharges the discharged intermediate-pressure refrigerant to the second container. In a horizontal compressor that compresses and discharges with a rotary compression element of 2,
The low pressure chamber of the cylinder of the second rotary compression element and the bottom of the closed vessel are communicated with an intermediate partition plate sandwiched between the cylinder of the first rotary compression element and the cylinder of the second rotary compression element. A horizontal compressor having a refueling passage formed therein. 前記給油通路は、前記第２の回転圧縮要素のシリンダに傾斜して形成された吸込ポートの傾斜面に開口することを特徴とする請求項１、請求項２又は請求項３の横置き型圧縮機。4. The horizontal type compression according to claim 1, wherein said oil supply passage opens on an inclined surface of a suction port formed to be inclined in a cylinder of said second rotary compression element. Machine.
JP2003004278A 2003-01-10 2003-01-10 Horizontal type compressor Expired - Fee Related JP4225793B2 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1520989A3 (en) * 2003-09-30 2008-11-05 Sanyo Electric Co., Ltd. Horizontal type rotary compressor
WO2013069071A1 (en) * 2011-11-09 2013-05-16 三洋電機株式会社 Horizontally mounted compressor
CN106704186A (en) * 2017-01-24 2017-05-24 广东美芝制冷设备有限公司 Compressor and vehicle with same

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1520989A3 (en) * 2003-09-30 2008-11-05 Sanyo Electric Co., Ltd. Horizontal type rotary compressor
WO2013069071A1 (en) * 2011-11-09 2013-05-16 三洋電機株式会社 Horizontally mounted compressor
JP2013100778A (en) * 2011-11-09 2013-05-23 Sanyo Electric Co Ltd Horizontally mounted compressor
CN103917781A (en) * 2011-11-09 2014-07-09 三洋电机株式会社 Horizontally mounted compressor
CN106704186A (en) * 2017-01-24 2017-05-24 广东美芝制冷设备有限公司 Compressor and vehicle with same

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