JP3983115B2 - Refrigerant circuit using CO2 refrigerant - Google Patents

Refrigerant circuit using CO2 refrigerant Download PDF

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Publication number
JP3983115B2
JP3983115B2 JP2002188023A JP2002188023A JP3983115B2 JP 3983115 B2 JP3983115 B2 JP 3983115B2 JP 2002188023 A JP2002188023 A JP 2002188023A JP 2002188023 A JP2002188023 A JP 2002188023A JP 3983115 B2 JP3983115 B2 JP 3983115B2
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refrigerant
rotary
compression element
bypass pipe
rotary compression
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JP2004028492A (en
Inventor
俊行 江原
兼三 松本
孝 佐藤
大 松浦
里　　和哉
裕之 松森
隆泰 斎藤
晴久 山崎
昌也 只野
悟 今井
淳志 小田
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

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

Description

【０００１】
【発明の属する技術分野】
本発明は、密閉容器内に電動要素と、該電動要素にて駆動される回転圧縮要素を備え、当該回転圧縮要素でＣＯ2冷媒ガスを圧縮して吐出するロータリコンプレッサを備えて構成された冷媒回路に関するものである。
【０００２】
【従来の技術】
従来より例えば自動車の車室内を空調するカーエアコンは、ロータリコンプレッサなどの圧縮機、ガスクーラ、減圧装置（膨張弁等）及びエバポレータ（蒸発器）等を順次環状に配管接続して冷媒回路が構成されている。そして、ロータリコンプレッサ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、吐出消音室を経て冷媒回路を構成するガスクーラに流入して放熱し、減圧装置で絞られてエバポレータ（蒸発器）に供給される。そこで冷媒が蒸発し、そのときに周囲から吸熱することにより冷却作用を発揮して車室内を空調するものであった。
【０００３】
【発明が解決しようとする課題】
ここで、近年では地球環境問題に対処するため、この種のカーエアコン等の冷媒回路においても、従来のフロンを用いずに自然冷媒であるＣＯ2（二酸化炭素）を冷媒として用いることが試みられているが、ＣＯ2冷媒は高低圧差の大きい冷媒であり、例えば２段圧縮の場合には、低圧側と高圧側で１００ＫＰａＧ程の差圧が生じる。また、ガス密度が高く、膨張弁などの絞り部があると通路抵抗を生じやすい。そのため、従来の冷媒を使用した場合より、コンプレッサが停止してから冷媒回路内の高低圧差が平衡するまでに長い時間を要するようになる。
【０００４】
この圧力平衡までの時間が長くなると、ロータリコンプレッサの低圧側から冷媒回路内に流出するオイルが多くなり、起動時に液圧縮を生じて信頼性が低下する問題がある。
【０００５】
また、この高低圧の圧力差が平衡しないうちに起動すると、ロータリコンプレッサに過大な負荷がかかって信頼性が低下してしまうため、通常はこの圧力平衡までの時間ロータリコンプレッサの起動を禁止する措置がとられるが、この時間中コンプレッサは停止するため、快適性が損なわれる結果となる。
【０００６】
更に、特にカーエアコンの場合は運転中の誤操作が多く、ロータリコンプレッサが頻繁に起動・停止操作され、それによって一層信頼性に悪影響が生じる問題もある。
【０００７】
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、ＣＯ2ガスを冷媒として用いた冷媒回路において、信頼性と快適性の双方を改善することを目的とする。
【０００８】
【課題を解決するための手段】
即ち、請求項１の発明は、密閉容器内に電動要素と、この電動要素にて駆動される第１及び第２の回転圧縮要素を備え、第１の回転圧縮要素で圧縮された中間圧のＣＯ2冷媒ガスを第２の回転圧縮要素に吸引し、圧縮して吐出する多段圧縮式のロータリコンプレッサを備えて構成された冷媒回路であって、ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスするバイパス配管と、このバイパス配管の流路を開閉する弁装置とを備え、弁装置は、ロータリコンプレッサの運転中は閉じており、停止した場合にバイパス配管の流路を開放するものとしたので、ロータリコンプレッサが停止した場合、その第２の回転圧縮要素の冷媒吐出側と冷媒吸込側はバイパス配管によって連通されることになる。
【０００９】
これにより、ロータリコンプレッサが停止してから第２の回転圧縮要素の冷媒吐出側である高圧と冷媒吸込側である中間圧とが平衡圧に達するまでの時間を短縮することができるようになり、所謂多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保しつつ、信頼性の低下を回避することができるようになる。
【００１０】
請求項２の発明は密閉容器内に電動要素と、この電動要素にて駆動される第１及び第２の回転圧縮要素を備え、第１の回転圧縮要素で圧縮された中間圧のＣＯ2冷媒ガスを第２の回転圧縮要素に吸引し、圧縮して吐出する多段圧縮式のロータリコンプレッサを備えて構成された冷媒回路であって、ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスする第１のバイパス配管と、ロータリコンプレッサの第１の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスする第２のバイパス配管と、ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と第１の回転圧縮要素の冷媒吸込側とをバイパスする第３のバイパス配管と、各バイパス配管の流路をそれぞれ開閉する弁装置とを備え、弁装置は、ロータリコンプレッサの運転中は第１、第２及び第３のバイパス配管の流路を閉じており、停止した場合に先ず第２のバイパス配管の流路を開放し、次に第１のバイパス配管、第３のバイパス配管の順で流路を開放するものとしたので、ロータリコンプレッサが停止した場合、先ず第１の回転圧縮要素の冷媒吐出側と冷媒吸込側が第２のバイパス配管によって連通されることになる。
【００１１】
これにより、ロータリコンプレッサが停止してから第１の回転圧縮要素の冷媒吐出側である中間圧と冷媒吸込側である低圧とが平衡圧に達するまでの時間を短縮することができるようになり、所謂多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保できるようになる。特に、第１の回転圧縮要素から冷媒回路内に流出するオイル量も削減できるので、再起動時の液圧縮の発生も解消し、信頼性の向上を図ることができるようになる。
【００１２】
次に、第２の回転圧縮要素の冷媒吐出側と冷媒吸込側がバイパス配管によって連通されることになるので、ロータリコンプレッサが停止してから第２の回転圧縮要素の冷媒吐出側である高圧と冷媒吸込側である中間圧とが平衡圧に達するまでの時間を短縮することができるようになり、これによっても多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保しつつ、信頼性の低下を回避することができるようになる。
【００１３】
そして、次に第２の回転圧縮要素の冷媒吐出側と第１の回転圧縮要素の冷媒吸込側が最終的に第３のバイパス配管によって連通されることになるので、ロータリコンプレッサが停止してから第２の回転圧縮要素の冷媒吐出側である高圧と第２の回転圧縮要素の冷媒吸込側である中間圧と第１の回転圧縮要素の冷媒吸込側である低圧の全てが連通され、迅速に平衡圧に達することができるようになり、総じて多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保できるようになる。また、同様に第１の回転圧縮要素から冷媒回路内に流出するオイル量も削減できるので、これによっても再起動時の液圧縮の発生も解消し、信頼性の向上を図ることができるようになる。
【００１４】
特に請求項３の如く車室内を空調する場合に、運転中誤って頻繁な運転・停止操作が成された場合にも、快適性と信頼性の双方を向上させることが可能となるものである。
【００１５】
【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は本発明の冷媒回路に使用するロータリコンプレッサの実施例として、第１及び第２の回転圧縮要素を備えた内部中間圧型多段（２段）圧縮式ロータリコンプレッサ１０の縦断側面図である。
【００１６】
この図において、１０は二酸化炭素（ＣＯ2）を冷媒として使用する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は鋼板からなる円筒状の密閉容器１２と、この密閉容器１２の内部空間の上側に配置収納された電動要素１４及びこの電動要素１４の下側に配置され、電動要素１４の回転軸１６により駆動される第１の回転圧縮要素３２（１段目）及び第２の回転圧縮要素３４（２段目）からなる回転圧縮機構部１８にて構成されている。密閉容器１２は底部をオイル溜めとし、電動要素１４と回転圧縮機構部１８を収納する容器本体１２Ａと、この容器本体１２Ａの上部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、且つ、このエンドキャップ１２Ｂの上面中心には円形の取付孔１２Ｄが形成されており、この取付孔１２Ｄには電動要素１４に電力を供給するためのターミナル（配線を省略）２０が取り付けられている。
【００１７】
電動要素１４は、密閉容器１２の上部空間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は中心を通り鉛直方向に延びる回転軸１６に固定されている。
【００１８】
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。また、ロータ２４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との間には中間仕切板３６が狭持されている。即ち、第１の回転圧縮要素３２と第２の回転圧縮要素３４は、中間仕切板３６と、この中間仕切板３６の上下に配置された上シリンダ３８、下シリンダ４０と、この上下シリンダ３８、４０内を１８０度の位相差を有して回転軸１６に設けた上下偏心部４２、４４にて偏心回転する上下ローラ４６、４８と、この上下ローラ４６、４８に当接して上下シリンダ３８、４０内をそれぞれ低圧室側と高圧室側に区画するベーン５０、５２と、上シリンダ３８の上側の開口面及び下シリンダ４０の下側の開口面を閉塞して回転軸１６の軸受けを兼用する支持部材としての上部支持部材５４及び下部支持部材５６にて構成されている。
【００２０】
一方、上部支持部材５４及び下部支持部材５６には、図示しない吸込ポートにて上下シリンダ３８、４０の内部とそれぞれ連通する吸込通路６０（上側の吸込通路は図示せず）と、一部を凹陥させ、この凹陥部を上カバー６６、下カバー６８にて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。
【００２１】
尚、吐出消音室６４と密閉容器１２内とは、上下シリンダ３８、４０や中間仕切板３６を貫通する連通路にて連通されており、連通路の上端には中間吐出管１２１が立設され、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が密閉容器１２内に吐出される。
【００２２】
また、第２の回転圧縮要素３４の上シリンダ３８内部と連通する吐出消音室６２の上面開口部を閉塞する上部カバー６６は、密閉容器１２内を吐出消音室６２と電動要素１４側とに仕切る。
【００２３】
そして、この場合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述した二酸化炭素（ＣＯ2）を使用し、潤滑油としてのオイルは、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）等該存のオイルが使用される。
【００２４】
密閉容器１２の容器本体１２Ａの側面には、上部支持部材５４と下部支持部材５６の吸込通路６０（上側は図示せず）、吐出消音室６２、上部カバー６６の上側（電動要素１４の下端に略対応する位置）に対応する位置に、スリーブ１４１、１４２、１４３及び１４４がそれぞれ溶接固定されている。スリーブ１４１と１４２は上下に隣接すると共に、スリーブ１４３はスリーブ１４１の略対角線上にある。また、スリーブ１４４はスリーブ１４１と略９０度ずれた位置にある。
【００２５】
そして、スリーブ１４１内には上シリンダ３８に冷媒ガスを導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の一端は上シリンダ３８の図示しない吸込通路と連通する。この冷媒導入管９２は密閉容器１２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密閉容器１２内に連通する。
【００２６】
また、スリーブ１４２内には下シリンダ４０に冷媒ガスを導入するための冷媒導入管９４の一端が挿入接続され、この冷媒導入管９４の一端は下シリンダ４０の吸込通路６０と連通する。この冷媒導入管９４の他端はアキュムレータ１５８の下側に接続されている。また、スリーブ１４３内には冷媒吐出管９６が挿入接続され、この冷媒導入管９６の一端は吐出消音室６２と連通する。
【００２７】
前記アキュムレータ１５８は吸込冷媒の気液分離を行うタンクであり、密閉容器１２の容器本体１２Ａの上部側面に溶接固定された密閉容器１２側のブラケット１４７に図２に示すアキュムレータ１５８側のブラケットを介して取り付けられている。
【００２８】
次に、図２は本発明をカーエアコン（空気調和機）に適用した場合の冷媒回路を示しており、上述した多段圧縮式ロータリコンプレッサ１０は図２に示すカーエアコンの冷媒回路の一部を構成する。即ち、多段圧縮式ロータリコンプレッサ１０の冷媒吐出管９６はガスクーラ１５４の入口に接続される。このガスクーラ１５４を出た配管は内部熱交換器１６０を介して減圧装置としての膨張弁１５６を経て、エバポレータ（蒸発器）１５７の入口に至り、エバポレータ１５７の出口は内部熱交換器１６０、前記アキュムレータ１５８を介して冷媒導入管９４に接続される。
【００２９】
また、密閉容器１２内の冷媒を第２の回転圧縮要素３４に導入するための冷媒導入管（冷媒通路）９２の途中には第２の回転圧縮要素３４の冷媒吸込側と冷媒吐出側を連通する第１のバイパス配管１７０の一端が接続されており、このバイパス配管１７０の他端は冷媒吐出管９６に接続されている。そして、バイパス配管１７０にはこのバイパス配管１７０の流路を開閉する第１の弁装置（電磁弁）１７１が設けられている。
【００３０】
一方、第１の回転圧縮要素３２の冷媒導入管９４には第１の回転圧縮要素３２の冷媒吸込側と冷媒吐出側とを連通する第２のバイパス配管１７２の一端が接続されており、このバイパス配管１７２の他端は冷媒導入管９２の途中に接続されている。そして、このバイパス配管１７２にはこのバイパス配管１７２の流路を開閉する第２の弁装置（電磁弁）１７３が設けられている。
【００３１】
更に、弁装置１７１の冷媒吐出管９６側のバイパス配管１７０には第３のバイパス配管１７４の一端が接続され、このバイパス配管１７４の他端は弁装置１７３の冷媒導入管９４側のバイパス配管１７２に接続されている。このバイパス配管１７４は第２回転圧縮要素３４の冷媒吐出側と第１の回転圧縮要素３２の冷媒吸込側と連通するもので、このバイパス配管１７４には当該バイパス配管１７４の流路を開閉する第３の弁装置（電磁弁）１７５が設けられている。
【００３２】
これらバイパス配管１７０、１７２及び１７４の各々に設けられている弁装置１７１、１７３及び１７５は図示しない制御装置により開閉制御される。即ち、多段圧縮式ロータリコンプレッサ１０が運転されているときは、これら弁装置１７１、１７３及び１７５は閉じられており、ロータリコンプレッサ１０が停止すると、弁装置１７３、１７１、１７５の順で開放される。これにより、冷媒ガスはこれらバイパス配管１７２、１７０及び１７４を自由に移動することができるようになり、多段圧縮式ロータリコンプレッサ１０の第１の回転圧縮要素３２の冷媒吐出側と冷媒吸込側、第２の回転圧縮要素３４の冷媒吐出側と冷媒吸込側、第２の回転圧縮要素の冷媒吐出側と第１の回転圧縮要素の冷媒吸込側との間に生じた冷媒回路内の圧力差を短時間で平衡させることができるようになる。
【００３３】
これにより、ロータリコンプレッサ１０の運転禁止期間を短縮しながら、圧力差がある状態で起動することによる過負荷の発生を解消し、信頼性を向上させることができるようになる。特に、最初に弁装置１７３を開放して第１の回転圧縮要素３２の冷媒吐出側と冷媒吸込側とを連通させているので、第１の回転圧縮要素３２から冷媒回路のアキュムレータ１５８側へオイルが多量に流出し、再起動時に液圧縮が生じる不都合を効果的に解消するようにしている。
【００３４】
尚、また、コンプレッサを起動する際には、図示しない制御装置によりこれら弁装置１７１、１７３及び１７５は閉じられ、通常の運転が行われるようになる。
【００３５】
以上の構成で次に動作を説明する。尚、前記制御装置により多段圧縮式ロータリコンプレッサ１０の起動時には弁装置１７１、１７３及び１７５は前述の如く閉じられている。ターミナル２０及び図示されない配線を介して電動要素１４のステータコイル２８に通電されると、電動要素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と一体に設けた上下偏心部４２、４４に嵌合された上下ローラ４６、４８が上下シリンダ３８、４０内を偏心回転する。
【００３６】
これにより、冷媒導入管９４及び下部支持部材５６に形成された吸込通路６０を経由して図示しない吸込ポートからシリンダ４０の低圧室側に吸入された低圧の冷媒は、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下シリンダ４０の高圧室側より図示しない連通路を経て中間吐出管１２１から密閉容器１２内に吐出される。これによって、密閉容器１２内は中間圧となる。
【００３７】
そして、密閉容器１２内の中間圧の冷媒ガスは、スリ−ブ１４４から出て冷媒導入管９２及び上部支持部材５４に形成された図示しない吸込通路を経由して図示しない吸込ポートから上シリンダ３８の低圧室側に吸入される。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圧高温の冷媒ガスとなり、高圧室側から図示しない吐出ポートを通り上部支持部材５４に形成された吐出消音室６２、冷媒吐出管９６を経由してガスクーラ１５４で放熱された後、内部熱交換器１６０を通過し、膨張弁１５６で減圧され、エバポレータ１５７内に流入する。
【００３８】
そこで冷媒が蒸発し、そのときに周囲から吸熱することにより冷却作用を発揮して車内が冷房される。その後、内部熱交換器１６０、アキュムレータ１５８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。
【００３９】
車室内温度が設定温度に低下すると、制御装置は多段圧縮式ロータリコンプレッサ１０を停止し、前述の如く先ず弁装置１７３を開放する。これにより第１の回転圧縮要素３２の冷媒吐出側と冷媒吸込側とが連通されて圧力平衡がとられるため、第１の回転圧縮要素３２の冷媒導入管９４からアキュムレータ１５８側にオイルが逆流してしまう不都合を回避することができる。次に、弁装置１７１、弁装置１７５の順で開放される。これにより、第２の回転圧縮要素３４の冷媒吐出側と冷媒吸込側、そして、最終的に第１の回転圧縮要素３２の冷媒吸込側と冷媒吐出側も連通されるので、多段圧縮式ロータリコンプレッサ１０の低圧、中間圧、高圧の全てが連通され、迅速に圧力平衡がとられることになる。
【００４０】
これにより、運転中の誤操作で多段圧縮式ロータリコンプレッサ１０が頻繁に運転・停止操作された場合にも、再起動にかかる時間を短縮して車室内空調の快適性を向上させながら、ロータリコンプレッサ１０が液圧縮を引き起こす不都合を防ぐことができるようになると共に、そのローラ４６、４８及びピン部等に過大な負荷がかかることにより、損傷を生じる不都合も未然に回避することができるようになる。
【００４１】
尚、実施例ではバイパス配管１７０と弁装置１７１、バイパス配管１７２と弁装置１７３、及び、バイパス配管１７４と弁装置１７５を設けたが、それに限らず、それらバイパス配管と弁装置の組み合わせの何れかのみであってもよく、バイパス配管１７０と弁装置１７１、及び、バイパス配管１７２と弁装置１７３のみ、バイパス配管１７２と弁装置１７３、及び、バイパス配管１７４と弁装置１７５のみ、バイパス配管１７０と弁装置１７１、及び、バイパス配管１７４と弁装置１７５のみの組み合わせであっても効果を奏する。
【００４２】
【発明の効果】
以上詳述した如く、請求項１の発明によれば、密閉容器内に電動要素と、この電動要素にて駆動される第１及び第２の回転圧縮要素を備え、第１の回転圧縮要素で圧縮された中間圧のＣＯ2冷媒ガスを第２の回転圧縮要素に吸引し、圧縮して吐出する多段圧縮式のロータリコンプレッサを備えて構成された冷媒回路であって、ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスするバイパス配管と、このバイパス配管の流路を開閉する弁装置とを備え、弁装置は、ロータリコンプレッサの運転中は閉じており、停止した場合にバイパス配管の流路を開放するものとしたので、ロータリコンプレッサが停止した場合、その第２の回転圧縮要素の冷媒吐出側と冷媒吸込側はバイパス配管によって連通されることになる。
【００４３】
これにより、ロータリコンプレッサが停止してから第２の回転圧縮要素の冷媒吐出側である高圧と冷媒吸込側である中間圧とが平衡圧に達するまでの時間を短縮することができるようになり、所謂多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保しつつ、信頼性の低下を回避することができるようになる。
【００４４】
請求項２の発明によれば、密閉容器内に電動要素と、この電動要素にて駆動される第１及び第２の回転圧縮要素を備え、第１の回転圧縮要素で圧縮された中間圧のＣＯ2冷媒ガスを第２の回転圧縮要素に吸引し、圧縮して吐出する多段圧縮式のロータリコンプレッサを備えて構成された冷媒回路であって、ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスする第１のバイパス配管と、ロータリコンプレッサの第１の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスする第２のバイパス配管と、ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と第１の回転圧縮要素の冷媒吸込側とをバイパスする第３のバイパス配管と、各バイパス配管の流路をそれぞれ開閉する弁装置とを備え、弁装置は、ロータリコンプレッサの運転中は第１、第２及び第３のバイパス配管の流路を閉じており、停止した場合に先ず第２のバイパス配管の流路を開放し、次に第１のバイパス配管、第３のバイパス配管の順で流路を開放するものとしたので、ロータリコンプレッサが停止した場合、先ず第１の回転圧縮要素の冷媒吐出側と冷媒吸込側が第２のバイパス配管によって連通されることになる。
【００４５】
これにより、ロータリコンプレッサが停止してから第１の回転圧縮要素の冷媒吐出側である中間圧と冷媒吸込側である低圧とが平衡圧に達するまでの時間を短縮することができるようになり、所謂多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保できるようになる。特に、第１の回転圧縮要素から冷媒回路内に流出するオイル量も削減できるので、再起動時の液圧縮の発生も解消し、信頼性の向上を図ることができるようになる。
【００４６】
次に、第２の回転圧縮要素の冷媒吐出側と冷媒吸込側がバイパス配管によって連通されることになるので、ロータリコンプレッサが停止してから第２の回転圧縮要素の冷媒吐出側である高圧と冷媒吸込側である中間圧とが平衡圧に達するまでの時間を短縮することができるようになり、これによっても多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保しつつ、信頼性の低下を回避することができるようになる。
【００４７】
そして、次に第２の回転圧縮要素の冷媒吐出側と第１の回転圧縮要素の冷媒吸込側が最終的に第３のバイパス配管によって連通されることになるので、ロータリコンプレッサが停止してから第２の回転圧縮要素の冷媒吐出側である高圧と第２の回転圧縮要素の冷媒吸込側である中間圧と第１の回転圧縮要素の冷媒吸込側である低圧の全てが連通され、迅速に平衡圧に達することができるようになり、総じて多段圧縮式のロータリコンプレッサが再起動可能となるまでの時間を短縮して快適性を担保できるようになる。また、同様に第１の回転圧縮要素から冷媒回路内に流出するオイル量も削減できるので、これによっても再起動時の液圧縮の発生も解消し、信頼性の向上を図ることができるようになる。
【００４８】
特に請求項３の如く車室内を空調する場合に、運転中誤って頻繁な運転・停止操作が成された場合にも、快適性と信頼性の双方を向上させることが可能となるものである。
【図面の簡単な説明】
【図１】 本発明の実施例の冷媒回路を構成する多段圧縮式ロータリコンプレッサの縦断面図である。
【図２】 本発明の実施例のカーエアコンの冷媒回路図である。
【符号の説明】
１０ 多段圧縮式ロータリコンプレッサ
３２ 第１の回転圧縮要素
３４ 第２の回転圧縮要素
９２、９４ 冷媒導入管
９６ 冷媒吐出管
１５４ ガスクーラ
１５６ 膨張弁
１５７ エバポレータ
１５８ アキュムレータ
１６０ 内部熱交換器
１７０、１７２、１７４ バイパス配管
１７１、１７３、１７５ 弁装置[0001]
BACKGROUND OF THE INVENTION
The present invention includes an electric element and a rotary compression element that is driven by the electric element in a sealed container, and a refrigerant that includes a rotary compressor that compresses and discharges CO 2 refrigerant gas by the rotary compression element. It relates to the circuit.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, for example, a car air conditioner that air-conditions the interior of a car has a refrigerant circuit in which a compressor such as a rotary compressor, a gas cooler, a decompression device (expansion valve, etc.), an evaporator (evaporator), etc. ing. Then, the refrigerant gas is sucked into the low pressure chamber side of the cylinder from the suction port of the rotary compression element of the rotary compressor, and is compressed by the operation of the roller and the vane to become a high temperature and high pressure refrigerant gas. After passing through the sound deadening chamber, it flows into the gas cooler constituting the refrigerant circuit to dissipate heat, is throttled by the decompression device, and is supplied to the evaporator (evaporator). Therefore, the refrigerant evaporates, and at that time, heat is absorbed from the surroundings to exert a cooling action to air-condition the passenger compartment.
[0003]
[Problems to be solved by the invention]
Here, in recent years, in order to cope with global environmental problems, it is attempted to use CO 2 (carbon dioxide), which is a natural refrigerant, as a refrigerant in a refrigerant circuit such as this type of car air conditioner without using conventional chlorofluorocarbon. However, the CO 2 refrigerant is a refrigerant having a large high-low pressure difference. For example, in the case of two-stage compression, a differential pressure of about 100 KPaG is generated between the low-pressure side and the high-pressure side. Moreover, if the gas density is high and there is a throttle part such as an expansion valve, passage resistance is likely to occur. Therefore, it takes a longer time for the high-low pressure difference in the refrigerant circuit to equilibrate after the compressor is stopped than when a conventional refrigerant is used.
[0004]
If the time until this pressure equilibrium becomes long, there is a problem that the amount of oil flowing out from the low pressure side of the rotary compressor into the refrigerant circuit increases, causing liquid compression at the time of start-up and lowering reliability.
[0005]
Also, if the pressure difference between the high and low pressures starts up before it is balanced, the rotary compressor will be overloaded and reliability will be reduced. However, the compressor stops during this time, resulting in a loss of comfort.
[0006]
Furthermore, especially in the case of a car air conditioner, there are many misoperations during operation, and the rotary compressor is frequently started and stopped, which causes a further adverse effect on reliability.
[0007]
The present invention has been made to solve the conventional technical problems, and an object of the present invention is to improve both reliability and comfort in a refrigerant circuit using CO 2 gas as a refrigerant.
[0008]
[Means for Solving the Problems]
That is, the invention of claim 1 comprises an electric element in a hermetically sealed container and first and second rotary compression elements driven by the electric element, and an intermediate pressure compressed by the first rotary compression element. A refrigerant circuit comprising a multi-stage compression rotary compressor that sucks CO 2 refrigerant gas into a second rotary compression element, compresses and discharges the refrigerant, and discharges the refrigerant from the second rotary compression element of the rotary compressor A bypass pipe that bypasses the refrigerant side and the refrigerant suction side, and a valve device that opens and closes the flow path of the bypass pipe. The valve device is closed during the operation of the rotary compressor. Since the passage is opened, when the rotary compressor stops, the refrigerant discharge side and the refrigerant suction side of the second rotary compression element are communicated with each other by a bypass pipe.
[0009]
Thereby, it becomes possible to shorten the time from when the rotary compressor stops until the high pressure on the refrigerant discharge side of the second rotary compression element and the intermediate pressure on the refrigerant suction side reach the equilibrium pressure, The time until the so-called multi-stage compression rotary compressor can be restarted is shortened to ensure comfort and avoid deterioration in reliability.
[0010]
According to a second aspect of the present invention, an intermediate pressure CO 2 refrigerant compressed in the first rotary compression element is provided with the electric element in the hermetic container and the first and second rotary compression elements driven by the electric element. A refrigerant circuit comprising a multi-stage compression rotary compressor that sucks gas into a second rotary compression element, compresses and discharges the refrigerant, and the refrigerant discharge side and refrigerant of the second rotary compression element of the rotary compressor A first bypass pipe that bypasses the suction side, a second bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the first rotary compression element of the rotary compressor, and a second rotary compression element of the rotary compressor A third bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the first rotary compression element, and a valve device that opens and closes the flow path of each bypass pipe. During the operation of the presser, the flow paths of the first, second and third bypass pipes are closed. When the presser is stopped, the flow path of the second bypass pipe is first opened, and then the first bypass pipe, Since the flow path is opened in the order of the bypass pipe 3, the refrigerant discharge side and the refrigerant suction side of the first rotary compression element are first communicated by the second bypass pipe when the rotary compressor stops. Become.
[0011]
Thereby, it becomes possible to shorten the time from when the rotary compressor stops until the intermediate pressure on the refrigerant discharge side of the first rotary compression element and the low pressure on the refrigerant suction side reach the equilibrium pressure, The so-called multi-stage compression rotary compressor can reduce the time until it can be restarted, thereby ensuring comfort. In particular, since the amount of oil flowing out from the first rotary compression element into the refrigerant circuit can be reduced, the occurrence of liquid compression at the time of restart can be eliminated, and the reliability can be improved.
[0012]
Next, since the refrigerant discharge side and the refrigerant suction side of the second rotary compression element are communicated by the bypass pipe, the high pressure and refrigerant on the refrigerant discharge side of the second rotary compression element after the rotary compressor stops The time until the intermediate pressure on the suction side reaches the equilibrium pressure can be shortened, and this also shortens the time until the multi-stage compression rotary compressor can be restarted, improving comfort. While guaranteeing, it becomes possible to avoid a decrease in reliability.
[0013]
Then, since the refrigerant discharge side of the second rotary compression element and the refrigerant suction side of the first rotary compression element are finally communicated by the third bypass pipe, the second compressor is stopped after the rotary compressor is stopped. The high pressure on the refrigerant discharge side of the second rotary compression element, the intermediate pressure on the refrigerant suction side of the second rotary compression element, and the low pressure on the refrigerant suction side of the first rotary compression element are all communicated and quickly balanced. As a result, the time until the multi-stage compression rotary compressor can be restarted can be shortened to ensure comfort. Similarly, since the amount of oil flowing out from the first rotary compression element into the refrigerant circuit can be reduced, the occurrence of liquid compression at the time of restart can also be eliminated, thereby improving reliability. Become.
[0014]
In particular, when the vehicle interior is air-conditioned as in claim 3, it is possible to improve both comfort and reliability even if frequent driving / stopping operations are mistakenly performed during driving. .
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal side view of an internal intermediate pressure type multi-stage (two-stage) compression rotary compressor 10 having first and second rotary compression elements as an embodiment of a rotary compressor used in the refrigerant circuit of the present invention.
[0016]
In this figure, reference numeral 10 denotes an internal intermediate pressure multistage compression rotary compressor that uses carbon dioxide (CO 2 ) as a refrigerant. The multistage compression rotary compressor 10 includes a cylindrical sealed container 12 made of a steel plate, and the sealed container 12. The electric element 14 arranged and housed above the internal space of the electric element 14 and the first rotary compression element 32 (first stage) and the first rotary compression element 32 arranged below the electric element 14 and driven by the rotating shaft 16 of the electric element 14. The rotary compression mechanism section 18 is composed of two rotary compression elements 34 (second stage). The sealed container 12 has an oil reservoir at the bottom, a container body 12A that houses the electric element 14 and the rotary compression mechanism 18, and a generally bowl-shaped end cap (lid body) 12B that closes the upper opening of the container body 12A. A circular mounting hole 12D is formed in the center of the upper surface of the end cap 12B, and a terminal (wiring is omitted) 20 for supplying power to the electric element 14 is mounted in the mounting hole 12D. It has been.
[0017]
The electric element 14 includes a stator 22 attached in an annular shape along the inner peripheral surface of the upper space of the hermetic container 12, and a rotor 24 inserted and installed inside the stator 22 with a slight gap. The rotor 24 is fixed to a rotating shaft 16 that passes through the center and extends in the vertical direction.
[0018]
The stator 22 has a laminated body 26 in which donut-shaped electromagnetic steel plates are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method. Further, like the rotor 24 stator 22, it is formed of a laminated body 30 of electromagnetic steel plates, and is formed by inserting a permanent magnet MG into the laminated body 30.
[0019]
An intermediate partition plate 36 is sandwiched between the first rotary compression element 32 and the second rotary compression element 34. That is, the first rotary compression element 32 and the second rotary compression element 34 include an intermediate partition plate 36, an upper cylinder 38 and a lower cylinder 40 disposed above and below the intermediate partition plate 36, and the upper and lower cylinders 38, The upper and lower rollers 46 and 48 that are eccentrically rotated by the upper and lower eccentric portions 42 and 44 provided on the rotary shaft 16 with a phase difference of 180 degrees in the interior 40, and the upper and lower cylinders 38 and 48 abut against the upper and lower rollers 46 and 48, The vanes 50 and 52 that divide the inside of the inside 40 into a low-pressure chamber side and a high-pressure chamber side, and the upper opening surface of the upper cylinder 38 and the lower opening surface of the lower cylinder 40 are closed to serve as bearings for the rotary shaft 16. The upper support member 54 and the lower support member 56 are used as support members.
[0020]
On the other hand, the upper support member 54 and the lower support member 56 are respectively provided with a suction passage 60 (the upper suction passage is not shown) that communicates with the inside of the upper and lower cylinders 38 and 40 through a suction port (not shown), and a part thereof is recessed. Discharge silencing chambers 62 and 64 formed by closing the recessed portion with an upper cover 66 and a lower cover 68 are provided.
[0021]
The discharge silencer chamber 64 and the inside of the sealed container 12 are communicated with each other through a communication passage that penetrates the upper and lower cylinders 38 and 40 and the intermediate partition plate 36, and an intermediate discharge pipe 121 is provided upright at the upper end of the communication passage. The intermediate pressure refrigerant compressed by the first rotary compression element 32 is discharged from the intermediate discharge pipe 121 into the sealed container 12.
[0022]
An upper cover 66 that closes the upper opening of the discharge silencing chamber 62 that communicates with the inside of the upper cylinder 38 of the second rotary compression element 34 partitions the inside of the sealed container 12 into the discharge silencing chamber 62 and the electric element 14 side. .
[0023]
In this case, the above-mentioned carbon dioxide (CO 2 ), which is a natural refrigerant in consideration of flammability and toxicity, is used as the refrigerant, and the oil as the lubricating oil is, for example, mineral oil (mineral oil) ), Alkylbenzene oil, ether oil, ester oil, PAG (polyalkylglycol) and the like.
[0024]
On the side surface of the container main body 12A of the sealed container 12, the suction passage 60 (upper side is not shown) of the upper support member 54 and the lower support member 56, the discharge silencer chamber 62, the upper side of the upper cover 66 (on the lower end of the electric element 14). Sleeves 141, 142, 143, and 144 are welded and fixed at positions corresponding to (substantially corresponding positions). The sleeves 141 and 142 are adjacent to each other vertically, and the sleeve 143 is substantially diagonal to the sleeve 141. Further, the sleeve 144 is located at a position shifted by approximately 90 degrees from the sleeve 141.
[0025]
One end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the upper cylinder 38 is inserted and connected into the sleeve 141, and one end of the refrigerant introduction pipe 92 communicates with a suction passage (not shown) of the upper cylinder 38. The refrigerant introduction pipe 92 passes through the upper side of the sealed container 12 to reach the sleeve 144, and the other end is inserted and connected into the sleeve 144 to communicate with the sealed container 12.
[0026]
In addition, one end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the lower cylinder 40 is inserted and connected in the sleeve 142, and one end of the refrigerant introduction pipe 94 communicates with the suction passage 60 of the lower cylinder 40. The other end of the refrigerant introduction pipe 94 is connected to the lower side of the accumulator 158. In addition, a refrigerant discharge pipe 96 is inserted and connected into the sleeve 143, and one end of the refrigerant introduction pipe 96 communicates with the discharge silencer chamber 62.
[0027]
The accumulator 158 is a tank that performs gas-liquid separation of the suction refrigerant. The accumulator 158 side bracket 147 shown in FIG. 2 is connected to the bracket 147 on the airtight container 12 side that is welded and fixed to the upper side surface of the container body 12A of the airtight container 12. Attached.
[0028]
Next, FIG. 2 shows a refrigerant circuit when the present invention is applied to a car air conditioner (air conditioner). The multistage compression rotary compressor 10 described above is a part of the refrigerant circuit of the car air conditioner shown in FIG. Constitute. That is, the refrigerant discharge pipe 96 of the multistage compression rotary compressor 10 is connected to the inlet of the gas cooler 154. The piping that exits the gas cooler 154 passes through an internal heat exchanger 160 through an expansion valve 156 as a pressure reducing device, reaches an inlet of an evaporator (evaporator) 157, and an outlet of the evaporator 157 is connected to the internal heat exchanger 160, the accumulator. It is connected to the refrigerant introduction pipe 94 via 158.
[0029]
Further, the refrigerant suction side and the refrigerant discharge side of the second rotary compression element 34 are communicated with each other in the middle of a refrigerant introduction pipe (refrigerant passage) 92 for introducing the refrigerant in the hermetic container 12 into the second rotary compression element 34. One end of the first bypass pipe 170 is connected, and the other end of the bypass pipe 170 is connected to the refrigerant discharge pipe 96. The bypass pipe 170 is provided with a first valve device (electromagnetic valve) 171 that opens and closes the flow path of the bypass pipe 170.
[0030]
On the other hand, one end of a second bypass pipe 172 that connects the refrigerant suction side and the refrigerant discharge side of the first rotary compression element 32 is connected to the refrigerant introduction pipe 94 of the first rotary compression element 32. The other end of the bypass pipe 172 is connected in the middle of the refrigerant introduction pipe 92. The bypass pipe 172 is provided with a second valve device (electromagnetic valve) 173 that opens and closes the flow path of the bypass pipe 172.
[0031]
Further, one end of a third bypass pipe 174 is connected to the bypass pipe 170 on the refrigerant discharge pipe 96 side of the valve device 171, and the other end of the bypass pipe 174 is a bypass pipe 172 on the refrigerant introduction pipe 94 side of the valve device 173. It is connected to the. The bypass pipe 174 communicates with the refrigerant discharge side of the second rotary compression element 34 and the refrigerant suction side of the first rotary compression element 32, and the bypass pipe 174 opens and closes the flow path of the bypass pipe 174. Three valve devices (electromagnetic valves) 175 are provided.
[0032]
The valve devices 171, 173, and 175 provided in each of the bypass pipes 170, 172, and 174 are controlled to open and close by a control device (not shown). That is, when the multistage compression rotary compressor 10 is in operation, these valve devices 171, 173 and 175 are closed, and when the rotary compressor 10 is stopped, the valve devices 173, 171 and 175 are opened in this order. . As a result, the refrigerant gas can freely move through these bypass pipes 172, 170 and 174, and the refrigerant discharge side, the refrigerant suction side, and the first refrigerant compression side of the first rotary compression element 32 of the multistage compression rotary compressor 10 are provided. The pressure difference in the refrigerant circuit generated between the refrigerant discharge side and the refrigerant suction side of the second rotary compression element 34 and between the refrigerant discharge side of the second rotary compression element and the refrigerant suction side of the first rotary compression element is shortened. It becomes possible to equilibrate with time.
[0033]
Thereby, while shortening the operation prohibition period of the rotary compressor 10, it is possible to eliminate the occurrence of overload caused by starting in a state where there is a pressure difference, and to improve the reliability. In particular, since the valve device 173 is first opened to allow the refrigerant discharge side and the refrigerant suction side of the first rotary compression element 32 to communicate with each other, the oil is transferred from the first rotary compression element 32 to the accumulator 158 side of the refrigerant circuit. In such a manner that a large amount of spills out and liquid inconvenience occurs at the time of restart.
[0034]
In addition, when starting the compressor, these valve devices 171, 173, and 175 are closed by a control device (not shown) so that normal operation is performed.
[0035]
Next, the operation of the above configuration will be described. Incidentally, when the multistage compression rotary compressor 10 is started by the control device, the valve devices 171, 173 and 175 are closed as described above. When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted to the upper and lower eccentric portions 42 and 44 provided integrally with the rotary shaft 16 rotate eccentrically in the upper and lower cylinders 38 and 40.
[0036]
Thus, the low-pressure refrigerant sucked into the low-pressure chamber side of the cylinder 40 from the suction port (not shown) via the suction passage 60 formed in the refrigerant introduction pipe 94 and the lower support member 56 is operated by the rollers 48 and the vanes 52. Is compressed by the intermediate pressure to be discharged from the intermediate discharge pipe 121 into the sealed container 12 through the communication passage (not shown) from the high pressure chamber side of the lower cylinder 40. Thereby, the inside of the sealed container 12 becomes an intermediate pressure.
[0037]
Then, the intermediate-pressure refrigerant gas in the sealed container 12 exits from the sleeve 144 and passes through a suction passage (not shown) formed in the refrigerant introduction pipe 92 and the upper support member 54 from the suction port (not shown) to the upper cylinder 38. Is sucked into the low pressure chamber side. The sucked intermediate-pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the vane 50 to become high-pressure and high-temperature refrigerant gas, and is formed on the upper support member 54 from the high-pressure chamber side through a discharge port (not shown). The heat is radiated from the gas cooler 154 through the discharge silencer chamber 62 and the refrigerant discharge pipe 96, passes through the internal heat exchanger 160, is decompressed by the expansion valve 156, and flows into the evaporator 157.
[0038]
Then, the refrigerant evaporates, and at that time, the inside of the vehicle is cooled by exhibiting a cooling action by absorbing heat from the surroundings. Thereafter, the cycle of being sucked from the refrigerant introduction pipe 94 into the first rotary compression element 32 through the internal heat exchanger 160 and the accumulator 158 is repeated.
[0039]
When the vehicle interior temperature falls to the set temperature, the control device stops the multi-stage compression rotary compressor 10 and first opens the valve device 173 as described above. As a result, the refrigerant discharge side and the refrigerant suction side of the first rotary compression element 32 communicate with each other to achieve pressure balance, so that the oil flows backward from the refrigerant introduction pipe 94 of the first rotary compression element 32 to the accumulator 158 side. The inconvenience that occurs can be avoided. Next, the valve device 171 and the valve device 175 are opened in this order. As a result, the refrigerant discharge side and the refrigerant suction side of the second rotary compression element 34 and finally the refrigerant suction side and the refrigerant discharge side of the first rotary compression element 32 are also communicated with each other, so that the multistage compression rotary compressor All of the 10 low pressures, intermediate pressures, and high pressures are communicated, and the pressure is quickly balanced.
[0040]
Thus, even when the multistage compression rotary compressor 10 is frequently operated / stopped due to an erroneous operation during operation, the rotary compressor 10 is improved while reducing the time required for restart and improving the comfort of the vehicle interior air conditioning. As a result, it is possible to prevent inconveniences that cause liquid compression, and it is possible to avoid inconveniences that cause damage by applying an excessive load to the rollers 46 and 48 and the pin portions.
[0041]
In the embodiment, the bypass pipe 170 and the valve device 171, the bypass pipe 172 and the valve device 173, and the bypass pipe 174 and the valve device 175 are provided. The bypass pipe 170 and the valve device 171, the bypass pipe 172 and the valve device 173 only, the bypass pipe 172 and the valve device 173, the bypass pipe 174 and the valve device 175 only, the bypass pipe 170 and the valve The combination of only the device 171 and the bypass pipe 174 and the valve device 175 is effective.
[0042]
【The invention's effect】
As described above in detail, according to the first aspect of the present invention, the sealed container includes the electric element and the first and second rotary compression elements driven by the electric element. A refrigerant circuit comprising a multi-stage compression rotary compressor that sucks compressed intermediate-pressure CO 2 refrigerant gas into a second rotary compression element and compresses and discharges the compressed gas. A bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the rotary compression element and a valve device that opens and closes the flow path of the bypass pipe are provided. The valve device is closed during operation of the rotary compressor and stopped. In this case, when the rotary compressor stops, the refrigerant discharge side and the refrigerant suction side of the second rotary compression element are communicated by the bypass pipe. That.
[0043]
Thereby, it becomes possible to shorten the time from when the rotary compressor stops until the high pressure on the refrigerant discharge side of the second rotary compression element and the intermediate pressure on the refrigerant suction side reach the equilibrium pressure, The time until the so-called multi-stage compression rotary compressor can be restarted is shortened to ensure comfort and avoid deterioration in reliability.
[0044]
According to the invention of claim 2, the intermediate pressure compressed by the first rotary compression element is provided with the electric element and the first and second rotary compression elements driven by the electric element in the hermetic container. A refrigerant circuit comprising a multi-stage compression rotary compressor that sucks CO 2 refrigerant gas into a second rotary compression element, compresses and discharges the refrigerant, and discharges the refrigerant from the second rotary compression element of the rotary compressor A first bypass pipe that bypasses the refrigerant suction side and the refrigerant suction side, a second bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the first rotary compression element of the rotary compressor, and a second compressor of the rotary compressor A third bypass pipe that bypasses the refrigerant discharge side of the rotary compression element and the refrigerant suction side of the first rotary compression element; and a valve device that opens and closes the flow path of each bypass pipe. During operation of the compressor, the flow paths of the first, second and third bypass pipes are closed, and when stopped, the flow path of the second bypass pipe is first opened, and then the first bypass pipe, Since the flow path is opened in the order of the third bypass pipe, when the rotary compressor stops, the refrigerant discharge side and the refrigerant suction side of the first rotary compression element are first communicated with each other by the second bypass pipe. become.
[0045]
Thereby, it becomes possible to shorten the time from when the rotary compressor stops until the intermediate pressure on the refrigerant discharge side of the first rotary compression element and the low pressure on the refrigerant suction side reach the equilibrium pressure, The so-called multi-stage compression rotary compressor can reduce the time until it can be restarted, thereby ensuring comfort. In particular, since the amount of oil flowing out from the first rotary compression element into the refrigerant circuit can be reduced, the occurrence of liquid compression at the time of restart can be eliminated, and the reliability can be improved.
[0046]
Next, since the refrigerant discharge side and the refrigerant suction side of the second rotary compression element are communicated by the bypass pipe, the high pressure and refrigerant on the refrigerant discharge side of the second rotary compression element after the rotary compressor stops The time until the intermediate pressure on the suction side reaches the equilibrium pressure can be shortened, and this also shortens the time until the multi-stage compression rotary compressor can be restarted, improving comfort. While guaranteeing, it becomes possible to avoid a decrease in reliability.
[0047]
Then, since the refrigerant discharge side of the second rotary compression element and the refrigerant suction side of the first rotary compression element are finally communicated by the third bypass pipe, the second compressor is stopped after the rotary compressor is stopped. The high pressure on the refrigerant discharge side of the second rotary compression element, the intermediate pressure on the refrigerant suction side of the second rotary compression element, and the low pressure on the refrigerant suction side of the first rotary compression element are all communicated and quickly balanced. As a result, the time until the multi-stage compression rotary compressor can be restarted can be shortened to ensure comfort. Similarly, since the amount of oil flowing out from the first rotary compression element into the refrigerant circuit can be reduced, the occurrence of liquid compression at the time of restart can also be eliminated, thereby improving reliability. Become.
[0048]
In particular, when the vehicle interior is air-conditioned as in claim 3, it is possible to improve both comfort and reliability even if frequent driving / stopping operations are mistakenly performed during driving. .
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a multistage compression rotary compressor constituting a refrigerant circuit according to an embodiment of the present invention.
FIG. 2 is a refrigerant circuit diagram of the car air conditioner according to the embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 Multistage compression rotary compressor 32 1st rotation compression element 34 2nd rotation compression element 92, 94 Refrigerant introduction pipe 96 Refrigerant discharge pipe 154 Gas cooler 156 Expansion valve 157 Evaporator 158 Accumulator 160 Internal heat exchanger 170,172,174 Bypass Piping 171, 173, 175 Valve device

Claims (3)

密閉容器内に電動要素と、該電動要素にて駆動される第１及び第２の回転圧縮要素を備え、前記第１の回転圧縮要素で圧縮された中間圧のＣＯ2冷媒ガスを前記第２の回転圧縮要素に吸引し、圧縮して吐出する多段圧縮式のロータリコンプレッサを備えて構成された冷媒回路において、
前記ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスするバイパス配管と、該バイパス配管の流路を開閉する弁装置とを備え、
前記弁装置は、前記ロータリコンプレッサの運転中は閉じており、停止した場合に前記バイパス配管の流路を開放することを特徴とするＣＯ2冷媒を用いた冷媒回路。An electric element and first and second rotary compression elements driven by the electric element are provided in the hermetic container, and the intermediate pressure CO 2 refrigerant gas compressed by the first rotary compression element is supplied to the second container. In the refrigerant circuit configured to include a multi-stage compression rotary compressor that sucks, compresses and discharges the rotary compression element
A bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the second rotary compression element of the rotary compressor, and a valve device that opens and closes the flow path of the bypass pipe;
The valve device is closed during operation of the rotary compressor, and opens the flow path of the bypass pipe when the rotary compressor is stopped. A refrigerant circuit using a CO 2 refrigerant. 密閉容器内に電動要素と、該電動要素にて駆動される第１及び第２の回転圧縮要素を備え、前記第１の回転圧縮要素で圧縮された中間圧のＣＯAn intermediate pressure CO compressed by the first rotary compression element is provided with an electric element and first and second rotary compression elements driven by the electric element in a sealed container. 22 冷媒ガスを前記第２の回転圧縮要素に吸引し、圧縮して吐出する多段圧縮式のロータリコンプレッサを備えて構成された冷媒回路において、In a refrigerant circuit comprising a multi-stage compression rotary compressor that sucks refrigerant gas into the second rotary compression element, compresses and discharges the gas,
前記ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスする第１のバイパス配管と、A first bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the second rotary compression element of the rotary compressor;
前記ロータリコンプレッサの第１の回転圧縮要素の冷媒吐出側と冷媒吸込側とをバイパスする第２のバイパス配管と、A second bypass pipe that bypasses the refrigerant discharge side and the refrigerant suction side of the first rotary compression element of the rotary compressor;
前記ロータリコンプレッサの第２の回転圧縮要素の冷媒吐出側と第１の回転圧縮要素の冷媒吸込側とをバイパスする第３のバイパス配管と、A third bypass pipe that bypasses the refrigerant discharge side of the second rotary compression element of the rotary compressor and the refrigerant suction side of the first rotary compression element;
前記各バイパス配管の流路をそれぞれ開閉する弁装置とを備え、A valve device for opening and closing each flow path of each bypass pipe,
前記弁装置は、前記ロータリコンプレッサの運転中は前記第１、第２及び第３のバイパス配管の流路を閉じており、停止した場合に先ず前記第２のバイパス配管の流路を開放し、次に前記第１のバイパス配管、前記第３のバイパス配管の順で流路を開放することを特徴とするＣＯThe valve device closes the flow paths of the first, second and third bypass pipes during operation of the rotary compressor, and first opens the flow path of the second bypass pipes when stopped. Next, the flow path is opened in the order of the first bypass pipe and the third bypass pipe. 22 冷媒を用いた冷媒回路。Refrigerant circuit using refrigerant. 車室内を空調するために用いられることを特徴とする請求項１又は請求項２に記載のＣＯThe CO according to claim 1 or 2, wherein the CO is used for air conditioning a vehicle interior. 22 冷媒を用いた冷媒回路。Refrigerant circuit using refrigerant.
JP2002188023A 2002-06-27 2002-06-27 Refrigerant circuit using CO2 refrigerant Expired - Fee Related JP3983115B2 (en)

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TWI325949B (en) * 2004-02-09 2010-06-11 Sanyo Electric Co Refrigerant system
JP2005226918A (en) * 2004-02-12 2005-08-25 Sanyo Electric Co Ltd Solar battery driven refrigerant cycle device, water heater, hot storage, cooling storage, beverage feeder, and air conditioner
JP2005226913A (en) * 2004-02-12 2005-08-25 Sanyo Electric Co Ltd Transient critical refrigerant cycle device
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