JP2004239192A - Double-cylinder rotary compressor - Google Patents

Double-cylinder rotary compressor Download PDF

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Publication number
JP2004239192A
JP2004239192A JP2003030267A JP2003030267A JP2004239192A JP 2004239192 A JP2004239192 A JP 2004239192A JP 2003030267 A JP2003030267 A JP 2003030267A JP 2003030267 A JP2003030267 A JP 2003030267A JP 2004239192 A JP2004239192 A JP 2004239192A
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Japan
Prior art keywords
holes
overhang
rotary compressor
cylindrical
cylinder rotary
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JP2003030267A
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Japanese (ja)
Inventor
Yasuhiro Kishi
康弘 岸
Kazunori Tsukui
和則 津久井
Yukichi Nakada
裕吉 中田
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Hitachi Appliances Inc
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Hitachi Home and Life Solutions Inc
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Priority to JP2003030267A priority Critical patent/JP2004239192A/en
Priority to CNB2004100048596A priority patent/CN1325800C/en
Priority to MYPI20040372 priority patent/MY134655A/en
Publication of JP2004239192A publication Critical patent/JP2004239192A/en
Pending legal-status Critical Current

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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
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Landscapes

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double-cylinder rotary compressor having yield strength to a high-pressure gas. <P>SOLUTION: In the double-cylinder compressor, a compression mechanism provided with a first and second cylinders successively disposed along the axial direction of a crankshaft and an electric motor connected to the crankshaft are provided in a cylindrical sealed container. Two lateral holes are made in the axial direction of the crankshaft so as to pass pipes for connecting gas-suction holes of the 1st and 2nd cylinders in the compression mechanism and the external part of the sealed vessel. A bulged part is provided on both sides in the peripheral direction with respect to the surface between the holes in the cylindrical part of the sealed container. The distance between the bulged part and the center of the cylindrical part is different from that in other cylindrical part. Tensile stress produced between the holes due to expansion of a case is loaded radially on the sealed vessel. Since the bulged part is plastically deformed in different distance from the center of the cylindrical part, the expansion of the case is not directly transmitted to the cylindrical parts between the holes, and this makes small the tensile stress exerted on the part between the lateral holes. The lateral holes made in the cylindrical part of the sealed vessel may be provided in the bulged part. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、上下に近接して第１及び第２シリンダを配設し、そのシリンダの少なくとも一方から高圧の吐出ガスを密閉容器内に吐出する高圧容器形２シリンダロータリ圧縮機に関する。
【０００２】
【従来の技術】
一般的な２シリンダロータリ圧縮機の一例として図９によってその構成を説明する。２シリンダロータリ圧縮機（以下、圧縮機）２１の密閉容器２２は、円筒状のケース２ａの上、下に、蓋チャンバ２２ｂと底チャンバ２２ｃを圧入した後、円周溶接し形成されている。密閉容器２２内部に、上部に電動機部２３、下部に圧縮機構部２４が収納配設されている。
【０００３】
電動機部２３は、ステータ２３ａが密閉容器２２の内周面に、焼嵌めなどで嵌合して取り付けられている。ステータ２３ａの内側にはロータ２３ｂが回転自在に配設され、ロータ２３ｂはクランクシャフト２６に、圧入などにより固接されている。
【０００４】
一方、圧縮機構部２４は以下のように構成されている。まず、フレーム２５は、密閉容器２２の円筒状のケース２ａの内径寸法と近似した最外径寸法のフランジ部２５ａと、ベアリング２５ｂとを有している。クランクシャフト２６は、そのベアリング２５ｂに貫通して支持されており、このフレーム２５の下側に突き出したクランクシャフト２６には２つの偏心部２６ａ、２６ｂが設けられている。この偏心部２６ａ、２６ｂに対応する位置には第１シリンダ２７、第２シリンダ２８が仕切り板２９を介して配設されている。そして、これらシリンダ２７、２８内に位置する偏心部２６ａ、２６ｂには第１ローラ３０、第２ローラ３１が設けられている。第２シリンダ２８の下には下部ベアリング３４が設けられている。
【０００５】
ローラ３０、３１には、シリンダ２７、２８の夫々の内面から弾性的に突設されたブレード（図示せず）が当接している。このブレードで、偏心して回転するローラ３０、３１とシリンダ２７、２８と仕切り板２９、下部ベアリング３４で形成される空間を仕切ることで圧縮室３５を形成する。
【０００６】
以上の部材を主構成要素として備えるこの圧縮機構部２４は、電動機部２３のステータ２３ａとロータ２３ｂとの間のエアギャップと、シリンダ２７、２８の吸込み穴２７ａ、２８ａと密閉容器２２の横穴２２ｄとの位置とがそれぞれ適切な位置で、フレーム２５の外径２５ｂと密閉容器２２とがスポット溶接（図示せず）され、密閉容器２２に固定される。
【０００７】
この圧縮機構部２４で圧縮された冷媒は、図示されていない各シリンダ２７、２８の吐出口より密閉容器２２内に吐き出され、密閉容器２２内を高圧（吐出圧力）にして吐出パイプ３７から圧縮機外部の冷凍サイクルへ吐き出される。
【０００８】
上下夫々に位置するシリンダ２７、２８の吸込み穴２７ａ、２８ａと、アキュームレータ３２の吸入管３２ａ、３２ｂの接続方法について、図１０を用いて説明する。密閉容器２２のケース２ａには、シリンダ２７、２８の吸込み穴２７ａ、２８ａに対応する部分に、２個の横穴２２ｄが、例えばその中心間距離Ａを横穴２２ｄの直径Ｄの２倍を最大寸法として、夫々独立して近接した位置に設けられている。この横穴２２ｄ内には継パイプ２２ｅが予めロウ付けされている。
【０００９】
密閉容器２２と圧縮機構部２４をスポット溶接により接合した後、段付形状のシールサクションパイプ３３はその先端３３ａを継パイプ２２ｅに圧入される。この圧入は、シールサクションパイプ３３の後端面３３ｂと継パイプ２２ｅの後端面との関係が、各シリンダに対して同等位置になるように行う。
【００１０】
次に、シリンダ２７、２８に圧入したシールサクションパイプ３３の拡管部３３ｃに、アキュームレータ３２の吸入管３２ａ、３２ｂが挿入された後、継パイプ２２ｅとシールサクションパイプ３３とアキュームレータ３２の吸入管３２ａ、３２ｂとが、気密性を備えるようにロウ付けされる。これによって密閉容器２２内部の圧縮機構部２４と密閉容器２２外部のアキュームレータ３２が機能的に連係、即ちアキュームレータ３２からの冷媒ガスは外気が混入されること無く圧縮機構部２４に導かれることになる。
【００１１】
他の圧縮機の例として、特開平７−２４３３８２号公報（特許文献１と称す。）がある。
【００１２】
【特許文献１】
特開平７−２４３３８２号公報
【００１３】
【発明が解決しようとする課題】
しかし、以上述べた従来公知の圧縮機は、図１１に示すように、密閉容器２２内部に負荷される高圧ガスによって、矢印のように密閉容器２２が膨張し、これによって生じる引張応力が、円筒状のケース２ａの側面に設けた２個の横穴２２ｄに白抜き矢印のように集中し、その結果、図１２に示すように強度的に脆弱な横穴２２ｄ間の円筒状のケース２ａに割れ３６が発生し、高圧容器としてその強度が低下する課題を有していた。
【００１４】
密閉容器２２の耐圧強度の増加を図るために、例えば従来は、密閉容器２２を形成するケース２ａの板厚を厚くすることが試みられた。その結果、ケース２ａの塑性成形性が低下し、鉄板からの丸め成形機の大型化による加工費の増加や、材料費の増加などの不具合が生じることとなった。また、特許文献１のように、横穴の配置を工夫したものもあるが、根本的な応力の発生要因は残ったままである。
【００１５】
本発明の目的は、上述の課題を解決して、高圧ガスに対する強度を備えた２シリンダ圧縮機を提供することにある。
【００１６】
【課題を解決するための手段】
上述の目的を達成するために本発明の２シリンダロータリ圧縮機は、クランクシャフトの軸方向に沿って順次配設された第１及び第２のシリンダを備えた圧縮機構部と、クランクシャフトと接続する電動機部とが、円筒状の密閉容器内に設けられ、圧縮機構部の第１及び第２シリンダのガス吸入穴と密閉容器の外部とを連係するパイプを貫通する２個の横穴が前記クランクシャフトの軸方向に設けられ、密閉容器の円筒部であって横穴間の表面部に対して周方向の両側に他の円筒部とは円筒部中心からの距離が異なる張出し部を備えた。
【００１７】
密閉容器の密閉容器の内径に全体的に負荷され、ケースが膨張することによって横穴間に生じる引張応力に対して、本発明の張出し部は円筒部中心からの距離が異なる塑性変形をしているためケースの膨張をそのまま横穴間の円筒部に伝えず、横穴間にかかる引張応力を小さくする。密閉容器の円筒部に設けられた横穴は、本発明の張出し部に設けられてもよい。
【００１８】
また、張出し部は外郭を規定する縁部とその縁部の間の表面部とを備え、表面部は平面であってもよい。また、その表面部は密閉容器の円筒部の内側に凹状であってもよい。
【００１９】
また、張出し部の縁部は横穴間の容器表面を挟んでその距離を変えてもよく、特に、その距離を短く設けるとさらによい。
【００２０】
【発明の実施の形態】
図１は本発明の一実施例の２シリンダロータリ圧縮機の全体構造を示す。この圧縮機１の密閉容器２は、円筒状のケース２ａの上、下に、圧入した後で円周溶接された蓋チャンバ２ｂと底チャンバ２ｃを備える。
【００２１】
密閉容器２の内部には、上部に電動機部３、下部に圧縮機構部４が収納配設されている。電動機部３は、ステータ３ａが密閉容器２の内周面に焼嵌めなどで嵌合して取り付けられており、ステータ３ａの内側にロータ３ｂが回転自在に配設されている。ステータ３ａには、クランクシャフト５が圧入などによって固定されている。
【００２２】
一方、圧縮機構部４は以下のように構成されている。まずフレーム６は、密閉容器２の内径寸法と近似した最外径寸法を持つフランジ部６ａと、ベアリング６ｂとを有する。クランクシャフト５はそのベアリング６ｂに貫通して支持されており、このフレーム６の下側に突き出たクランクシャフト５には２つの偏心部５ａ、５ｂが形成されている。
【００２３】
この偏心部５ａ、５ｂに対応する位置に、第１シリンダ７、第２シリンダ８が仕切り板９を介して配設している。これらシリンダ７、８内に位置するクランクシャフト５の偏心部５ａ、５ｂには、第１ローラ１０、第２ローラ１１が設けられている。第２シリンダ８の下部には下部ベアリング１２が配設されている。
【００２４】
前記のローラ１０、１１には、シリンダ７、８の夫々の内面から弾性的に突設されたブレード（図示せず）が当接している。このブレードで偏心して回転するローラ１０、１１とシリンダ７、８と仕切り板９とベアリング１２で形成される空間を仕切ることで圧縮室１３をが形成される。
【００２５】
以上の部材を主構成要素とするこの圧縮機構部４は、電動機部３のステータ３ａとロータ３ｂ間のエアギャップと、シリンダ７，８の吸込み穴７ａ、８ａと密閉容器２の横穴２ｄの位置とがそれぞれ適切な位置で、フレーム６のフランジ部６ａの外径と密閉容器２とがスポット溶接（図示せず）され、密閉容器２に固定される。
【００２６】
この圧縮機構部４で圧縮された冷媒は、図示されていない各シリンダ７、８の吐出口より密閉容器２内に吐き出され、密閉容器２内を高圧（吐出圧力）にして吐出パイプ１６から圧縮機外部の冷凍サイクルへ吐き出される。
【００２７】
次に前述のように上下に位置するシリンダ７、８の吸込み穴７ａ、８ａと、アキュームレータ１５の吸入管１５ａ、１５ｂの接続部とその接続方法について、図２で説明する。
【００２８】
密閉容器２のケース２ａには、シリンダ７、８の吸込み穴７ａ、８ａに対応する部分に、２個の横穴２ｄが、その中心間距離Ａを横穴２ｄの直径Ｄの２倍を最大寸法として夫々独立して近接した位置に設けられており、この横穴２ｄ内には予め継パイプ２ｅがロウ付けされている。
【００２９】
前述したように、密閉容器２と圧縮機構部４をスポット溶接で接合した後、段付形状のシールサクションパイプ１４は、その先端４ａを継パイプ２ｅに圧入させる。この圧入は、シールサクションパイプ１４の後端面１４ｂと継パイプ２ｅの端面とが同位置となるように行う。
【００３０】
更に、シリンダ７、８に圧入したシールサクションパイプ１４の拡管部１４ｃにアキュームレータ１５の吸入管１５ａ、１５ｂを挿入した後、継パイプ２ｅとシールサクションパイプ１４とアキュームレータ１５の吸入管１５ａ、１５ｂとが、気密性を備えるようにロウ付けされる。これによって密閉容器２内部の圧縮機構部４と密閉容器２の外部のアキュームレータ１５が機能的に連係、すなわちアキュームレータ１５からの冷媒が外気に触れることなく圧縮機構部４に導かれることになる。
【００３１】
ここで、本発明の一実施例では、第１シリンダ７と第２シリンダ８の吸込み穴７ａ、８ａと対応するケース２ａの２個の横穴２ｄの開口部を結ぶケース２ａの表面部の周囲に、塑性加工によって他の円筒部とは円筒部中心からの距離が異なる張出し部２ｆを設けた。
【００３２】
張出し部２ｆの大きさ或いは形状は、塑性加工によるケース２ａ全体へ及ぼす変形の範囲を極力小さくすること、また、横穴２ｄをプレス抜きで形成するに充分なものとし、以下に述べる範囲が好ましい。
【００３３】
すなわち、図３に示すようにこの張出し部２ｆの外周に沿って設けられる周辺部である縁部２ｇの高さＨが、ケース２ａの板厚Ｔの３０〜１００％の範囲内にあるのが好ましい。また、張出し部２ｆの大きさは、図４（ａ）に示すように夫々の横穴２ｄの中心から、横穴２ｄの直径Ｄ寸法を最大寸法とする半径Ｒの半円の範囲と、半円の接線を結ぶトラック形状をその範囲とするのが好ましい。
【００３４】
図５に示すように、横穴２ｄが張出し部２ｆに設けられることにより、張出し部２ｆと縁部２ｇとからなる塑性成形部が補強構造となって、高圧ガスによる白抜き矢印で表した引張応力が縁部２ｇの部分で区切られるため、横穴２ｄ間の円筒状ケース部の内側表面部にかかる引張応力が低減される。この引張応力は、ケースの内側表面に全体的に負荷される膨張圧力で生じる。この実施例では引張圧力による横穴２ｄ間の円筒状ケース部の内側表面部における変形を小さくすることが可能になり、よって、横穴間の円筒状ケース２ａの割れを防止することが可能になる。
【００３５】
図５に示す張出し部２ｆは、ケース２ａの内径と同心円の円弧形状をなしていることから、従来公知の圧縮機同様、密閉容器の内部圧力はケース２ａの中心から放射状に張出し部２ｆ面に負荷され、太線矢印に示すように小さいながらも引張応力が横穴２ｄ間のケース２ａ表面部に集中することが考えられる。
【００３６】
そこで、更なる強度アップを図る改善案を呈示する。
【００３７】
図６に示す他の実施例は、張出し部２ｆの張出し面の形状を平面とした。すなわち、ケース２ａの円筒面に対して張出し面を異なる表面形状とした。
【００３８】
その結果、密閉容器２への高圧ガスによる変形応力は張出し面に垂直に負荷されることから、図５に示す円弧形状の張出し面に比較し、横穴２ｄ間にかかる引張応力は小さくなる。
【００３９】
図７に示す他の実施例では、張出し部２ｆの張出し面の形状をケース２ａ内側から見て凸レンズ状とした。言い換えると、張出し面の断面形状を、円筒状のケース２ａの内径側に凹んだ形状とした。
【００４０】
その結果、張出し部２ｆに掛る変形応力は白抜き矢印に示すように、張出し面の長さを縮める方向、即ち、圧縮応力となって張出し部２ｆに加わることとなる。したがって、二つの横穴２ｄ間のケース２ａ部分に、従来の課題で説明した割れ３６（図１２参照）を引起す力とは異なる方向に変形応力を作用させることができ、最も強度的に弱い横穴間のケース割れの発生を防止することができる。
【００４１】
凹んだ形状は横穴２ｄを中心として凹ませるが、横穴２ｄ間の張出し面は平らにしても凹ませてもよい。
【００４２】
更に、図８に他の実施例を示す。ここでは縁部２ｇの形状を改良して、高圧のガス圧力による変形応力が作用する張出し部２ｆの幅を小さくした。具体的には、図８に示された張出し部２ｆの平面形状を、夫々の横穴２ｄの同心円の交点を結んだ、言うなればトラック状の外縁における直線部が絞られ接近した形とした。図８には、夫々の横穴２ｄと同心円の交点を、任意の小さな円弧で結んだ略８の字状の縁部２ｇが示されている。図８は密閉容器２のケース２ａの内径側から見た形状を示している。横穴２ｄの同心円の直径Ｃは、横穴２ｄの直径Ｄの２倍を最大寸法とするのが好ましい。また、その縁部２ｇの高さＨは、ケース２ａの板厚Ｔの３０〜１００％の範囲内にあるのが望ましい。
【００４３】
従って、内部から負荷される応力が二つの横穴２ｄ間に作用しても、張出し部２ｆの幅が狭くなっていて縁部２ｇ間の距離が狭くなっていることから、結果的に剛性が向上して割れが発生しにくくなる。
【００４４】
また、この略８の字の張出し部２ｆの上面の状態を、前述のように平面状或いは凹状とすることにより、更に張出し部の剛性が向上し、益々、横穴２ｄ間に割れが発生しにくくなり、密閉容器２の耐圧強度が向上し、２シリンダロータリ圧縮機の信頼性の向上が図れる。
【００４５】
上述のように、本発明の実施例の縁部２ｇや張出し部２ｆを、ケース２ａの円筒面に設けた横穴２ｄの周囲に適宜形成することで、ケース２ａの横穴２ｄ間の割れが発生しにくくなる。また、本発明の実施例の張出し部２ｆと共に縁部２ｇを含む形状が横穴２ｄ間の剛性向上に効果がある。そのためケース２ａの板厚を薄くすることが可能となり、材料費の低減と塑性加工効率が上がり、比較的小型の成形機によるケースの丸め加工も可能になり、加工費の低減も図れる。
【００４６】
また、圧縮機の全体重量の相当範囲を占める密閉容器の重量を軽減することが可能であり、圧縮機の取扱い性の向上も出来、本発明の各実施例の効果はきわめて大きい。
【００４７】
【発明の効果】
本発明によれば、密閉容器の二つの横穴間の強度が上がり耐圧強度が向上した２シリンダロータリ圧縮機を実現できる。
【図面の簡単な説明】
【図１】本発明の一実施例の２シリンダロータリ圧縮機の構造の一例を示す側断面図。
【図２】図１のシリンダ吸込み穴とアキュームレータの連繋部の構造の一例を示す即断面図。
【図３】本発明の一実施例のケースの張出し形状の一例を示す側断面図。
【図４】（ａ）は図３のＡ矢視図。（ｂ）は図４（ａ）のＢ−Ｂ線に沿う断面図。
【図５】本発明の一実施例のケースの円弧状張出し部に掛る応力の一例を示す平断面図。
【図６】本発明の一実施例のケースの平面状張出し部に掛る応力の一例を示す平断面図。
【図７】本発明の一実施例のケースのレンズ状張出し部に掛る応力の一例を示す平断面図。
【図８】本発明の一実施例のケースの８の字状張出し部の形状の一例を示す側面図。
【図９】従来公知２シリンダロータリ圧縮機の構造の一例を示す側断面図。
【図１０】図９のシリンダ吸込み穴とアキュームレータの連繋部の構造の一例を示す側断面図。
【図１１】従来のケースに掛る高圧ガスによる内部応力の一例を示す平断面図。
【図１２】従来の圧縮機でケースの横穴間に発生する割れの一例を示す斜視図。
【符号の説明】
１…２シリンダロータリ圧縮機、２…密閉容器、２ａ…ケース、２ｂ…蓋チャンバ、２ｃ…底チャンバ、２ｄ…横穴、２ｅ…継パイプ、２ｆ…張出し部、２ｇ…縁部、３…電動機部、３ａ…ステータ、３ｂ…ロータ、４…圧縮機構部、５…クランクシャフト、５ａ…偏心部、５ｂ…偏心部、６…フレーム、６ａ…フランジ部、６ｂ…ベアリング、７…第１シリンダ、７ａ……吸込み穴、８…第２シリンダ、８ａ…吸込み穴、９…仕切り板、１０…第１ローラ、１１…第２ローラ、１２…下部ベアリング、１３…圧縮室、１４…シールサクションパイプ、１４ａ…先端、１４ｂ…後端、１４ｃ…拡管部、１５…アキュームレータ、１５ａ…吸入管、１５ｂ…吸入管。[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a high-pressure container type two-cylinder rotary compressor in which first and second cylinders are arranged vertically close to each other, and high-pressure discharge gas is discharged from at least one of the cylinders into a closed container.
[0002]
[Prior art]
The configuration of an example of a general two-cylinder rotary compressor will be described with reference to FIG. The sealed container 22 of the two-cylinder rotary compressor (hereinafter, compressor) 21 is formed by press-fitting a lid chamber 22b and a bottom chamber 22c above and below a cylindrical case 2a, and then performing circumferential welding. Inside the hermetically sealed container 22, an electric motor portion 23 is accommodated at an upper portion, and a compression mechanism portion 24 is accommodated and arranged at a lower portion.
[0003]
The motor unit 23 has a stator 23a fitted and attached to the inner peripheral surface of the closed casing 22 by shrink fitting or the like. A rotor 23b is rotatably disposed inside the stator 23a, and the rotor 23b is firmly connected to the crankshaft 26 by press fitting or the like.
[0004]
On the other hand, the compression mechanism 24 is configured as follows. First, the frame 25 has a flange portion 25a having an outermost diameter approximating the inner diameter of the cylindrical case 2a of the closed container 22, and a bearing 25b. The crankshaft 26 is supported by being penetrated by its bearing 25b. The crankshaft 26 protruding below the frame 25 is provided with two eccentric portions 26a and 26b. At positions corresponding to the eccentric portions 26a and 26b, a first cylinder 27 and a second cylinder 28 are disposed via a partition plate 29. A first roller 30 and a second roller 31 are provided on the eccentric portions 26a and 26b located in the cylinders 27 and 28, respectively. Below the second cylinder 28, a lower bearing 34 is provided.
[0005]
Blades (not shown) elastically projecting from the inner surfaces of the cylinders 27 and 28 abut against the rollers 30 and 31. The compression chamber 35 is formed by partitioning a space formed by the rollers 30 and 31 eccentrically rotating, the cylinders 27 and 28, the partition plate 29, and the lower bearing 34 with the blade.
[0006]
The compression mechanism 24 having the above members as main components includes an air gap between the stator 23 a and the rotor 23 b of the electric motor 23, suction holes 27 a and 28 a of the cylinders 27 and 28, and a lateral hole 22 d of the closed casing 22. The outer diameter 25b of the frame 25 and the closed container 22 are spot-welded (not shown) and fixed to the closed container 22 at appropriate positions.
[0007]
The refrigerant compressed by the compression mechanism 24 is discharged from the discharge ports of the cylinders 27 and 28 (not shown) into the closed container 22, and the inside of the closed container 22 is set to a high pressure (discharge pressure) and compressed from the discharge pipe 37. Exhaled into the refrigeration cycle outside the machine.
[0008]
A method of connecting the suction holes 27a, 28a of the cylinders 27, 28 located at the upper and lower sides and the suction pipes 32a, 32b of the accumulator 32 will be described with reference to FIG. In the case 2a of the closed container 22, two lateral holes 22d are formed at portions corresponding to the suction holes 27a and 28a of the cylinders 27 and 28, for example, by setting the distance A between the centers to twice the diameter D of the lateral hole 22d to the maximum dimension. , Are independently provided at close positions. A connecting pipe 22e is previously brazed in the side hole 22d.
[0009]
After joining the hermetically sealed container 22 and the compression mechanism 24 by spot welding, the stepped seal suction pipe 33 is press-fitted at its distal end 33a into the connecting pipe 22e. This press-fitting is performed so that the relationship between the rear end face 33b of the seal suction pipe 33 and the rear end face of the connecting pipe 22e is at the same position with respect to each cylinder.
[0010]
Next, after the suction pipes 32a and 32b of the accumulator 32 are inserted into the expansion section 33c of the seal suction pipe 33 press-fitted into the cylinders 27 and 28, the connecting pipe 22e, the seal suction pipe 33, and the suction pipe 32a of the accumulator 32, 32b is brazed so as to have airtightness. As a result, the compression mechanism 24 inside the closed container 22 and the accumulator 32 outside the closed container 22 are functionally linked, that is, the refrigerant gas from the accumulator 32 is guided to the compression mechanism 24 without mixing the outside air. .
[0011]
As another example of the compressor, there is JP-A-7-243382 (referred to as Patent Document 1).
[0012]
[Patent Document 1]
JP-A-7-243382
[Problems to be solved by the invention]
However, in the conventional compressor described above, as shown in FIG. 11, the closed container 22 expands as shown by the arrow due to the high-pressure gas loaded inside the closed container 22, and the tensile stress generated by this increases the cylindrical stress. As shown in FIG. 12, the two lateral holes 22d provided on the side surfaces of the case 2a are concentrated as indicated by the white arrows, and as a result, as shown in FIG. And the strength of the high-pressure container is reduced.
[0014]
In order to increase the pressure resistance of the sealed container 22, for example, conventionally, an attempt has been made to increase the plate thickness of the case 2 a forming the sealed container 22. As a result, the plastic formability of the case 2a is reduced, and problems such as an increase in processing cost due to an increase in the size of the rounding machine for forming an iron plate and an increase in material cost are caused. Further, as in Patent Document 1, there is a device in which the arrangement of the lateral holes is devised, but the fundamental factor of the occurrence of stress remains.
[0015]
An object of the present invention is to solve the above-mentioned problems and to provide a two-cylinder compressor having high pressure gas strength.
[0016]
[Means for Solving the Problems]
In order to achieve the above object, a two-cylinder rotary compressor according to the present invention includes a compression mechanism having first and second cylinders sequentially arranged along an axial direction of a crankshaft, and a compression mechanism connected to the crankshaft. An electric motor section is provided in a cylindrical hermetic container, and two lateral holes penetrating a pipe that connects gas suction holes of first and second cylinders of a compression mechanism section and the outside of the hermetic container are formed by the crank. An overhang provided in the axial direction of the shaft and having a distance from the center of the cylindrical portion different from that of the other cylindrical portions is provided on both sides in the circumferential direction with respect to the surface portion between the horizontal holes.
[0017]
The overhang of the present invention is plastically deformed at different distances from the center of the cylindrical portion, against the tensile stress generated between the lateral holes due to the overall load applied to the inner diameter of the closed container and the expansion of the case. Therefore, the expansion of the case is not directly transmitted to the cylindrical portion between the side holes, and the tensile stress applied between the side holes is reduced. The lateral hole provided in the cylindrical portion of the closed container may be provided in the overhang portion of the present invention.
[0018]
Further, the overhang portion may include an edge defining an outer shell and a surface portion between the edges, and the surface portion may be flat. Further, the surface portion may be concave inside the cylindrical portion of the closed container.
[0019]
Further, the distance between the edges of the overhanging portion may be changed with the container surface between the lateral holes interposed therebetween. In particular, it is more preferable that the distance be short.
[0020]
BEST MODE FOR CARRYING OUT THE INVENTION
FIG. 1 shows the overall structure of a two-cylinder rotary compressor according to one embodiment of the present invention. The sealed container 2 of the compressor 1 includes a lid chamber 2b and a bottom chamber 2c which are press-fitted and then circumferentially welded above and below a cylindrical case 2a.
[0021]
Inside the closed container 2, an electric motor unit 3 is housed and arranged at an upper part, and a compression mechanism part 4 is housed and arranged at a lower part. The electric motor unit 3 has a stator 3a fitted and attached to the inner peripheral surface of the closed casing 2 by shrink fitting or the like, and a rotor 3b is rotatably disposed inside the stator 3a. The crankshaft 5 is fixed to the stator 3a by press fitting or the like.
[0022]
On the other hand, the compression mechanism 4 is configured as follows. First, the frame 6 has a flange portion 6a having an outermost diameter approximating the inner diameter of the sealed container 2, and a bearing 6b. The crankshaft 5 is supported by being penetrated by its bearing 6b. The crankshaft 5 protruding below the frame 6 is formed with two eccentric portions 5a and 5b.
[0023]
A first cylinder 7 and a second cylinder 8 are disposed at positions corresponding to the eccentric portions 5a and 5b via a partition plate 9. A first roller 10 and a second roller 11 are provided on the eccentric portions 5a and 5b of the crankshaft 5 located in the cylinders 7 and 8, respectively. A lower bearing 12 is provided below the second cylinder 8.
[0024]
Blades (not shown) elastically projecting from the respective inner surfaces of the cylinders 7 and 8 are in contact with the rollers 10 and 11. The compression chamber 13 is formed by partitioning a space formed by the rollers 10 and 11 eccentrically rotating, the cylinders 7 and 8, the partition plate 9, and the bearing 12 with the blades.
[0025]
The compression mechanism 4 having the above-mentioned members as main components is provided with an air gap between the stator 3a and the rotor 3b of the electric motor 3, and positions of the suction holes 7a and 8a of the cylinders 7 and 8 and the lateral hole 2d of the closed casing 2. At the appropriate positions, the outer diameter of the flange portion 6a of the frame 6 and the closed container 2 are spot-welded (not shown) and fixed to the closed container 2.
[0026]
The refrigerant compressed by the compression mechanism 4 is discharged from the discharge ports of the cylinders 7 and 8 (not shown) into the closed container 2, and the inside of the closed container 2 is set to a high pressure (discharge pressure) and compressed from the discharge pipe 16. Exhaled into the refrigeration cycle outside the machine.
[0027]
Next, the connection between the suction holes 7a and 8a of the upper and lower cylinders 7 and 8 and the suction pipes 15a and 15b of the accumulator 15 and the connection method thereof will be described with reference to FIG.
[0028]
In the case 2a of the closed container 2, two lateral holes 2d are formed at portions corresponding to the suction holes 7a and 8a of the cylinders 7 and 8, with the distance A between the centers being the maximum dimension of twice the diameter D of the lateral hole 2d. The pipes 2e are independently provided at close positions, and a connecting pipe 2e is previously brazed in the lateral hole 2d.
[0029]
As described above, after the hermetically sealed container 2 and the compression mechanism 4 are joined by spot welding, the stepped seal suction pipe 14 has its tip 4a pressed into the joint pipe 2e. This press fitting is performed so that the rear end face 14b of the seal suction pipe 14 and the end face of the joint pipe 2e are located at the same position.
[0030]
Further, after the suction pipes 15a, 15b of the accumulator 15 are inserted into the expanded portion 14c of the seal suction pipe 14 press-fitted into the cylinders 7, 8, the connecting pipe 2e, the seal suction pipe 14, and the suction pipes 15a, 15b of the accumulator 15 are connected. , And are brazed so as to be airtight. Thus, the compression mechanism 4 inside the closed container 2 and the accumulator 15 outside the closed container 2 are functionally linked, that is, the refrigerant from the accumulator 15 is guided to the compression mechanism 4 without contacting the outside air.
[0031]
Here, in one embodiment of the present invention, around the surface of the case 2a connecting the openings of the two side holes 2d of the case 2a corresponding to the suction holes 7a, 8a of the first cylinder 7 and the second cylinder 8, respectively. An overhang portion 2f having a distance from the center of the cylindrical portion different from that of the other cylindrical portion was formed by plastic working.
[0032]
The size or shape of the overhang portion 2f is preferably such that the range of deformation exerted on the entire case 2a by plastic working is made as small as possible, and that the side hole 2d is formed sufficiently by press punching.
[0033]
That is, as shown in FIG. 3, the height H of the edge portion 2g, which is a peripheral portion provided along the outer periphery of the overhang portion 2f, is within the range of 30 to 100% of the plate thickness T of the case 2a. preferable. Also, as shown in FIG. 4 (a), the size of the overhang portion 2f ranges from the center of each lateral hole 2d to a range of a semicircle having a radius R having the maximum dimension of the diameter D of the lateral hole 2d, and It is preferable that the shape of the track connecting the tangents is set as the range.
[0034]
As shown in FIG. 5, by providing the side hole 2d in the overhang portion 2f, the plastic forming portion composed of the overhang portion 2f and the edge portion 2g has a reinforcing structure, and the tensile stress represented by a white arrow due to the high-pressure gas. Is separated by the edge 2g, so that the tensile stress applied to the inner surface of the cylindrical case between the lateral holes 2d is reduced. This tensile stress occurs at the inflation pressure that is entirely applied to the inner surface of the case. In this embodiment, it is possible to reduce the deformation of the inner surface of the cylindrical case portion between the horizontal holes 2d due to the tensile pressure, thereby preventing the cylindrical case 2a from being cracked between the horizontal holes.
[0035]
Since the overhang portion 2f shown in FIG. 5 has an arc shape concentric with the inner diameter of the case 2a, the internal pressure of the sealed container is radially applied from the center of the case 2a to the surface of the overhang portion 2f as in a conventionally known compressor. It is conceivable that the tensile stress is concentrated on the surface of the case 2a between the lateral holes 2d while being loaded, as shown by the thick arrow.
[0036]
Therefore, an improvement plan for further increasing the strength is presented.
[0037]
In another embodiment shown in FIG. 6, the shape of the overhang surface of the overhang portion 2f is a flat surface. That is, the projecting surface has a different surface shape from the cylindrical surface of the case 2a.
[0038]
As a result, the deformation stress due to the high-pressure gas applied to the closed container 2 is applied perpendicularly to the overhang surface, so that the tensile stress applied between the lateral holes 2d is smaller than that of the arc-shaped overhang surface shown in FIG.
[0039]
In another embodiment shown in FIG. 7, the shape of the overhang surface of the overhang portion 2f is a convex lens shape when viewed from inside the case 2a. In other words, the cross-sectional shape of the overhanging surface is formed to be concave toward the inner diameter side of the cylindrical case 2a.
[0040]
As a result, the deformation stress applied to the overhang portion 2f is applied to the overhang portion 2f in a direction of reducing the length of the overhang surface, that is, a compressive stress, as indicated by a white arrow. Therefore, a deformation stress can be applied to the case 2a between the two lateral holes 2d in a direction different from the force causing the cracks 36 (see FIG. 12) described in the conventional problem, and the lateral hole having the weakest strength can be applied. It is possible to prevent occurrence of a case crack between them.
[0041]
The concave shape is recessed around the horizontal hole 2d, but the overhang surface between the horizontal holes 2d may be flat or concave.
[0042]
FIG. 8 shows another embodiment. Here, the shape of the edge 2g is improved, and the width of the overhang 2f on which the deformation stress due to the high gas pressure acts is reduced. More specifically, the planar shape of the overhang portion 2f shown in FIG. 8 is a shape in which the intersections of the concentric circles of the respective lateral holes 2d are connected, in other words, the linear portion at the outer edge of the track is narrowed and approached. FIG. 8 shows an approximately figure-shaped edge 2g in which the intersections of the respective horizontal holes 2d and the concentric circles are connected by an arbitrary small arc. FIG. 8 shows the shape of the closed container 2 as viewed from the inner diameter side of the case 2a. It is preferable that the maximum dimension of the diameter C of the concentric circle of the side hole 2d be twice the diameter D of the side hole 2d. The height H of the edge 2g is preferably in the range of 30 to 100% of the plate thickness T of the case 2a.
[0043]
Therefore, even if a stress applied from the inside acts between the two lateral holes 2d, the width of the overhang portion 2f is reduced and the distance between the edge portions 2g is reduced, resulting in an improvement in rigidity. Cracks are less likely to occur.
[0044]
Also, by making the state of the upper surface of the overhang portion 2f having a figure of eight into a flat or concave shape as described above, the rigidity of the overhang portion is further improved, and cracks are less likely to occur between the side holes 2d. Thus, the pressure resistance of the sealed container 2 is improved, and the reliability of the two-cylinder rotary compressor can be improved.
[0045]
As described above, by appropriately forming the edge portion 2g and the overhang portion 2f of the embodiment of the present invention around the horizontal hole 2d provided on the cylindrical surface of the case 2a, cracks between the horizontal holes 2d of the case 2a occur. It becomes difficult. Further, the shape including the edge 2g together with the overhang 2f of the embodiment of the present invention is effective in improving the rigidity between the lateral holes 2d. Therefore, the thickness of the case 2a can be reduced, the material cost can be reduced and the plastic working efficiency can be increased, the case can be rounded by a relatively small molding machine, and the working cost can be reduced.
[0046]
Further, it is possible to reduce the weight of the closed container, which occupies a considerable range of the entire weight of the compressor, and it is possible to improve the handleability of the compressor, and the effects of each embodiment of the present invention are extremely large.
[0047]
【The invention's effect】
According to the present invention, it is possible to realize a two-cylinder rotary compressor in which the strength between two side holes of a closed container is increased and the pressure resistance is improved.
[Brief description of the drawings]
FIG. 1 is a side sectional view showing an example of the structure of a two-cylinder rotary compressor according to one embodiment of the present invention.
FIG. 2 is an immediate sectional view showing an example of a structure of a connecting portion between a cylinder suction hole and an accumulator in FIG. 1;
FIG. 3 is a side sectional view showing an example of an overhang shape of a case according to an embodiment of the present invention.
FIG. 4A is a view taken in the direction of arrow A in FIG. (B) is sectional drawing which follows the BB line | wire of FIG.4 (a).
FIG. 5 is a plan sectional view showing an example of a stress applied to an arc-shaped overhang portion of the case according to the embodiment of the present invention.
FIG. 6 is a plan sectional view showing an example of a stress applied to a planar overhang portion of the case according to the embodiment of the present invention.
FIG. 7 is a plan sectional view showing an example of a stress applied to a lens-shaped overhang portion of the case according to the embodiment of the present invention.
FIG. 8 is a side view showing an example of the shape of the figure-eight protruding portion of the case according to the embodiment of the present invention.
FIG. 9 is a side sectional view showing an example of the structure of a conventionally known two-cylinder rotary compressor.
FIG. 10 is a side sectional view showing an example of the structure of a connecting portion between the cylinder suction hole and the accumulator in FIG. 9;
FIG. 11 is a cross-sectional plan view showing an example of internal stress caused by high-pressure gas applied to a conventional case.
FIG. 12 is a perspective view showing an example of a crack generated between side holes of a case in a conventional compressor.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... 2 cylinder rotary compressor, 2 ... airtight container, 2a ... case, 2b ... lid chamber, 2c ... bottom chamber, 2d ... side hole, 2e ... joint pipe, 2f ... overhang part, 2g ... edge part, 3 ... electric motor part , 3a ... stator, 3b ... rotor, 4 ... compression mechanism, 5 ... crankshaft, 5a ... eccentric part, 5b ... eccentric part, 6 ... frame, 6a ... flange part, 6b ... bearing, 7 ... first cylinder, 7a ... suction hole, 8 ... second cylinder, 8a ... suction hole, 9 ... partition plate, 10 ... first roller, 11 ... second roller, 12 ... lower bearing, 13 ... compression chamber, 14 ... seal suction pipe, 14a ... Top end, 14b Back end, 14c Expanding section, 15 Accumulator, 15a Suction pipe, 15b Suction pipe.

Claims (6)

クランクシャフトの軸方向に沿って順次配設された第１及び第２のシリンダを備えた圧縮機構部と、前記クランクシャフトと接続する電動機部とが、円筒状の密閉容器内に設けられ、前記圧縮機構部の第１及び第２シリンダのガス吸入穴と前記密閉容器の外部とを連係するパイプが貫通する２個の横穴を前記密閉容器の円筒部に備え、前記密閉容器の円筒部であって前記横穴間の表面部に対して周方向の両側に他の円筒部とは円筒部中心からの距離が異なる張出し部を備えた２シリンダロータリ圧縮機。A compression mechanism unit having first and second cylinders sequentially arranged along the axial direction of the crankshaft, and an electric motor unit connected to the crankshaft are provided in a cylindrical hermetic container, The cylindrical portion of the hermetic container is provided with two lateral holes through which a pipe that connects the gas suction holes of the first and second cylinders of the compression mechanism portion and the outside of the hermetic container penetrates. A two-cylinder rotary compressor comprising a projection portion on both sides in a circumferential direction with respect to a surface portion between the lateral holes, the projection portion having a different distance from the center of the cylindrical portion with respect to the other cylindrical portion. 請求項１記載の２シリンダロータリ圧縮機において、前記張出し部はトラック状の外縁部を有し、前記横穴は前記張出し部に設けられた２シリンダロータリ圧縮機。2. The two-cylinder rotary compressor according to claim 1, wherein the overhang portion has a track-shaped outer edge, and the lateral hole is provided in the overhang portion. 3. 請求項２記載の２シリンダロータリ圧縮機において、前記張出し部に設けられる横穴間の距離は、前記横穴の直径の２倍の中心間距離を最大として、前記張出し部の縁部の高さを前記密閉容器の板厚の３０％〜１００％とする２シリンダロータリ圧縮機。3. The two-cylinder rotary compressor according to claim 2, wherein the distance between the side holes provided in the overhang portion is a maximum of a center-to-center distance of twice the diameter of the side hole, and the height of the edge of the overhang portion is A two-cylinder rotary compressor in which the thickness of the closed container is 30% to 100%. 請求項２記載の２シリンダロータリ圧縮機において、前記張出し部の張出し面が、張出し範囲内で前記密閉容器の内側に凹状の表面を備えた２シリンダロータリ圧縮機。3. The two-cylinder rotary compressor according to claim 2, wherein the overhang surface of the overhang portion has a concave surface inside the closed container within an overhang area. 請求項２記載の２シリンダロータリ圧縮機において、前記縁部の形状を略８の字形状とした２シリンダロータリ圧縮機。3. The two-cylinder rotary compressor according to claim 2, wherein the shape of the edge is substantially eight-shaped. 請求項５記載の２シリンダロータリ圧縮機において、前記張出し部の張出し面が平面或いは前記密閉容器の内側に凹んだ形状を備えた２シリンダロータリ圧縮機。6. The two-cylinder rotary compressor according to claim 5, wherein the overhang surface of the overhang portion has a flat shape or a concave shape inside the closed container.
JP2003030267A 2003-02-07 2003-02-07 Double-cylinder rotary compressor Pending JP2004239192A (en)

Priority Applications (3)

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JP2003030267A JP2004239192A (en) 2003-02-07 2003-02-07 Double-cylinder rotary compressor
CNB2004100048596A CN1325800C (en) 2003-02-07 2004-02-06 Double-cylinder rotary compressor
MYPI20040372 MY134655A (en) 2003-02-07 2004-02-07 2-cylinders rotary compressor

Applications Claiming Priority (1)

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CN101476552B (en) * 2009-01-06 2011-09-07 浙江鸿友压缩机制造有限公司 Multi-cylinder translation compression device
CN102477984B (en) * 2010-11-26 2015-05-27 上海日立电器有限公司 Rotary compressor structure with uniform stator and rotor clearance
JP5528379B2 (en) * 2011-03-10 2014-06-25 三菱電機株式会社 Rotary compressor
CN114382675B (en) * 2022-03-24 2022-06-10 河北晖普采暖设备有限公司 Continuous heating air source heat pump hot water unit

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JP3418470B2 (en) * 1994-12-20 2003-06-23 東芝キヤリア株式会社 Rotary compressor

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WO2009004961A1 (en) * 2007-07-03 2009-01-08 Daikin Industries, Ltd. Sealed compressor

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