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JP3978660B2 - Refrigeration cycle equipment using non-azeotropic refrigerant mixture - Google Patents

Refrigeration cycle equipment using non-azeotropic refrigerant mixture Download PDF

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JP3978660B2
JP3978660B2 JP2002267712A JP2002267712A JP3978660B2 JP 3978660 B2 JP3978660 B2 JP 3978660B2 JP 2002267712 A JP2002267712 A JP 2002267712A JP 2002267712 A JP2002267712 A JP 2002267712A JP 3978660 B2 JP3978660 B2 JP 3978660B2
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refrigerant
refrigeration cycle
cooler
rectifier
low
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JP2004108596A (en
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央平 加藤
多佳志 岡崎
誠善 大林
敏郎 阿部
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Description

【０００１】
【発明の属する技術分野】
本発明は、冷媒として非共沸混合冷媒を用いる冷凍サイクル装置に関するものであり、特に冷凍サイクル内を循環する冷媒組成を変更する冷凍サイクル装置の改善に関する。
【０００２】
【従来の技術】
従来、電動機の回転数が変更できない圧縮機を搭載した空調機の容量制御やヒートポンプ式給湯器による高温出湯時の高圧圧力低減のため、冷凍サイクル内を循環する冷媒の組成を変更する冷媒組成変更手段を搭載した冷凍サイクル装置が提案されている。
これらの冷凍サイクル装置は、圧縮機の電動機の回転数を変更するインバータを用いずに高効率で幅広い能力制御幅を得ることを目的とするものであり、圧縮機、熱源側熱交換器、減圧装置、利用側熱交換器等を備えた冷凍サイクルと、低沸点冷媒と高沸点冷媒とからなる非共沸混合冷媒と、低沸点成分に富んだ冷媒を生成する冷媒精留器と、冷媒精留器から出た低沸点成分に富んだ冷媒を貯留する第１の冷媒貯留器と、高沸点成分に富んだ冷媒を貯留する第２の冷媒貯留器とを備え、第１の冷媒貯留器と第２の冷媒貯留器の液冷媒量を調整することにより冷凍サイクル内を循環する組成を連続的に変更し、常に負荷に応じた能力を発揮させることができるというものである。
【０００３】
以下冷凍サイクル装置の例である。
圧縮機の出口部と冷媒精留器の下部は、電磁弁を介して配管で接続されており、またこの配管の途中には、圧縮機の吸入配管と熱交換する冷却器が設けられている。さらに、冷媒精留器の下部とアキュムレータは、毛細管と電磁弁を介して配管で接続されている。
冷媒精留器の上部には、冷却器と第１の冷媒貯留器が環状に接続されており、冷却器は、圧縮機の吸入冷媒の一部が電磁弁を介して流入できるように構成されている。
【０００４】
圧縮機、四方弁、熱源側熱交換器、アキュムレータ、冷媒精留器、第１の冷媒貯留器、冷却器、冷却器、電磁弁、毛細管及びこれらの接続配管は室外機内に納められている。
【０００５】
また、室内機は、第１減圧装置である電子式膨張弁と利用側熱交換器で構成されている。
これらの室外機と室内機は、２本の配管で接続されており、冷凍サイクルを形成している。この冷凍サイクル内には高沸点成分と低沸点成分からなる非共沸混合冷媒が充填されている。熱源側熱交換器は、暖房運転時には蒸発器として動作し、冷房運転時には凝縮器として動作する。また利用側熱交換器は、暖房運転時には凝縮器として動作し、冷房運転時には蒸発器として動作する。
【０００６】
例えば、暖房運転時には、冷凍サイクル内の余剰な冷媒は、アキュムレータ内に貯留される。このアキュムレータ内の冷媒は、高沸点成分に富んだ液冷媒と、低沸点成分に富んだ蒸気冷媒に分離される。このため、アキュムレータ内に液冷媒が貯留されると、サイクル内を循環する冷媒組成は、充填組成に比べて低沸点成分が増加する。
【０００７】
一方、冷凍サイクル内を循環する冷媒組成の高沸点成分を増加させる場合には、圧縮機を出た高温高圧の蒸気冷媒の一部を電磁弁を開いて冷却器に流入させ、この高温の冷媒蒸気は、冷却器内で低温低圧の圧縮機吸入冷媒によって冷却され、飽和蒸気あるいは気液二相状態まで冷却される。冷却器を出た高圧の気液二相冷媒は冷媒精留器の下部へ流入し、このうち冷媒蒸気は冷媒精留器内を上昇する。
また、冷媒精留器の上部では、上昇した冷媒蒸気が冷却器に流入し、電磁弁を通って流入した低温の圧縮機への吸入冷媒によって冷却され、凝縮液化する。この液冷媒は冷媒貯留器に流入し、貯留される。
冷媒貯留器内から液冷媒が冷媒精留器の環流液として冷媒精留器へ上部より流入する。
【０００８】
即ち、冷媒精留器内では、上昇する蒸気冷媒と、下降する液冷媒とが気液接触を行い、熱および物質移動が行われ、冷媒精留器内を上昇する蒸気冷媒は徐々に低沸点成分が増加し、低沸点成分に富んだ液冷媒が冷媒貯留器内に貯留される。
【０００９】
冷媒貯留器に貯留される液冷媒の増加とともに、アキュムレータ内の液冷媒は減少し、アキュムレータ内に貯留されていた高沸点成分に富んだ液冷媒が、サイクル内へ放出され、低沸点成分に富んだ液冷媒が冷媒貯留器内に貯留されることになる。この結果、冷凍サイクル内を循環する冷媒組成を高沸点成分に富んだものにすることができる。
例えば、Ｒ３２を２３％、Ｒ１２５を２５％、Ｒ１３４ａを５２％の重量割合で混合した冷媒（Ｒ４０７Ｃ）を充填した冷凍サイクルにおいて、低沸点成分であるＲ３２の組成を４５％から５％の範囲で制御することにより、能力は充填組成（Ｒ３２の組成が２３％）での能力を１００％とすると１３０％から７０％の範囲で制御することができる。
【００１０】
以上のように、従来の発明においては、冷媒貯留器に貯留する低沸点成分に富んだ液冷媒量とアキュムレータに貯留する高沸点成分に富んだ液冷媒量を調整することにより、冷凍サイクル内を循環する冷媒組成を変更できるため、インバータによる電動機の回転数制御を行う場合に比べ、冷媒組成変更により低コストで広範囲な能力制御が可能になるというものであった（例えば、特許文献１参照）。
【００１１】
【特許文献１】
特開平１０−２６７４３６号公報（第４頁〜第７頁、図１）
【００１２】
【発明が解決しようとする課題】
しかしながら、従来の冷凍サイクル装置では、冷媒精留器の構造によって冷媒精留器下部から流出する冷媒状態が気液二相となる場合があり、そのため下流の毛細管入口部に流入する冷媒が気液二相状態と液相状態を交互に繰り返す脈動が生じ、冷媒精留器内の冷媒流量が不安定となるという課題があった。
本発明は上記のような課題を解決するためになされたもので、非共沸混合冷媒を用い、冷凍サイクル内の冷媒組成を変化させ運転する冷凍サイクル装置の冷媒精留器内の冷媒流量を安定化できる、または、冷凍サイクル内の冷媒循環組成を変化させる際、低沸点成分を早く増加させることができる等、冷凍サイクル装置の性能を向上することを目的とする。
【００１３】
【課題を解決するための手段】
本発明の冷凍サイクル装置は、冷凍サイクルと、冷媒精留器と、冷媒精留器で分離された低沸点冷媒成分を冷却する第１冷却器と、冷媒貯留器とを備え、第１開閉弁と第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、冷媒精留器の下部と冷凍サイクルの圧縮機の出口側とを接続する配管の冷媒精留器の入口側に第２減圧装置を設け、冷媒精留器の下部と冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、該第３減圧装置の冷媒精留器側に、冷媒精留器から出る冷媒を過冷却する第２冷却器を設け、第２減圧装置の圧縮機側に第３冷却器を設け、第１冷却器、第２冷却器及び第３冷却器によるそれぞれの冷媒の冷却は、第３減圧装置で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるものである。
【００１４】
また、本発明の冷凍サイクル装置は、冷凍サイクルと、冷媒精留器と、第１冷却器と、冷媒貯留器とを備え、第１開閉弁と第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、冷媒精留器の下部と冷凍サイクルの圧縮機の出口側とを接続する配管の冷媒精留器の入口側に第２減圧装置を設け、また、冷媒精留器の下部と冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、冷媒貯留器の出口側と冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続し、第３減圧装置の冷媒精留器側に、第２冷却器を設け、第２減圧装置の圧縮機側に第３冷却器を設け、第１冷却器、第２冷却器及び第３冷却器によるそれぞれの冷媒の冷却は、第３減圧装置で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるものである。
【００１５】
また、本発明の冷凍サイクル装置は、冷凍サイクルと、冷媒精留器と第１冷却器と冷媒貯留器とを備え、第１開閉弁と第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、冷媒精留器の下部と冷凍サイクルの圧縮機の出口側とを接続する配管の冷媒精留器の入口側に第２減圧装置を設け、また、冷媒精留器の下部と冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、第１冷却器の出口側と冷凍サイクルの利用側熱交換器及び熱源側熱交換器のうち、高圧側の熱交換器の出口側とを開閉弁を介して配管接続し、第３減圧装置の冷媒精留器側に、第２冷却器を設け、第２減圧装置の圧縮機側に第３冷却器を設け、第１冷却器、第２冷却器及び第３冷却器によるそれぞれの冷媒の冷却は、第３減圧装置で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるものである。
【００１６】
【発明の実施の形態】
参考例
以下、参考例として冷凍サイクル装置について説明する。
図１は本参考例における冷凍サイクル装置を示す構成図である。図において、冷凍サイクルは圧縮機１、利用側熱交換器３、第１減圧装置である膨張弁４、熱源側熱交換器５、アキュムレータ６を配管接続して構成され、これらは冷凍サイクルユニット６２内に収納されている。
また、組成分離回路は組成分離手段である冷媒精留器１１、冷媒を貯留するための冷媒貯留器１４、第１冷却器１３、第２冷却器１２、第２減圧装置である毛細管３１、第３減圧装置である毛細管３２、第１開閉弁である電磁弁２１及び第２開閉弁である電磁弁２２で構成され、第１冷却器１３と冷媒貯留器１４は冷媒精留器１１の上部に環状に接続されている。なお、これらは組成分離ユニット６３内に収納されている。
【００１７】
これら冷凍サイクルユニット６２及び組成分離ユニット６３は、第１配管２５及び第２配管２６である２本の配管で接続され、冷媒回路内を循環する冷媒組成が変更可能な冷凍サイクル装置を形成している。この冷凍サイクル装置内には、例えば高沸点成分（Ｒ１３４ａ）と低沸点成分（Ｒ３２＋Ｒ１２５）からなる３成分非共沸混合冷媒Ｒ４０７Ｃ（標準組成；Ｒ３２：Ｒ１２５：Ｒ１３４ａ＝２３：２５：５２ｗｔ％）が充填されている。
【００１８】
さらに、冷媒精留器１１には、その内部に気液の接触面積を増大させるための充填材が封入されている。
また、圧縮機１の出口側、即ち、圧縮機からの吐出冷媒が吐出する配管で、圧縮機と利用側熱交換器３とを接続する配管（後述の実施の形態２では、圧縮機と四方弁２を接続する配管）と冷媒精留器１１の下部は、第１開閉弁である電磁弁２１と毛細管３１を介して第１配管２５で接続されている。即ち、第１配管２５は第１開閉弁２１入口部と、圧縮機１と利用側熱交換器３間の配管とを接続する（後述の実施の形態２では、第１開閉弁２１入口部と、圧縮機１と四方弁２間の配管とを接続する）。
【００１９】
また、冷媒精留器１１の下部から流出した中間圧力の気液二相冷媒は、第２冷却器１２に入り液化され、毛細管３２を経て減圧されたのち、低圧の気液二相冷媒となり、第２冷却器１２に戻り、第２冷却器１２で冷媒精留器１１の下部から流出した気液二相冷媒を完全に液化させ、即ち、過冷却状態とさせ、自身は低圧蒸気冷媒となり、さらに第１冷却器１３に入り、冷媒精留器１１から出た低沸点成分の冷媒蒸気を冷却し、液化させ、第２開閉弁２６、第２配管２６を通って、アキュームレータ６の入口部に流入する。ここに、第２配管２６は、第２開閉弁２２入口部とアキュームレータ６の入口部の配管とを接続する。但し、第２配管２６は、第２開閉弁２２入口部と冷凍サイクルの低圧側の配管、即ち、第１減圧装置４とアキュームレータ６間の配管とを接続するようにしてもよい（後述の実施の形態２では、第１減圧装置４とアキュームレータ６間の配管で、第１減圧装置４の下流側の低圧配管とを接続する）。
即ち、冷凍サイクルと組成分離回路とは、第１配管２５及び第２配管２６によって接続されている。
【００２０】
また、冷凍サイクルユニット６２と組成分離ユニット６３とは、それぞれに収容される冷凍サイクルと組成分離回路とを第１配管２５及び第２配管２６によって接続しているので、既存の冷凍サイクルユニット６２へ組成分離ユニット６３を接続できる。また、接続の際、既存の冷凍サイクルユニット６２を大幅に変更することなく、接続点数も少なくでき、接続が容易である。
さらに、組成分離回路において、冷媒精留器１１に第２減圧装置である毛細管３１と第３減圧装置である毛細管３２とが接続しており、前者は圧縮機１の吐出側と、後者は同じく吸入側と接続されているため、冷媒精留器１１は中間圧で動作する。そこで、高圧で動作する場合に比べて、液組成とガス組成との差が大きくなり（非共沸性が大きくなり）、高圧で動作する場合に比べて分離効率（液・ガスの濃度差に比例）が高くなる。
【００２１】
次に、上記のように構成された本参考例の冷凍サイクル装置の動作について説明する。本参考例では、冷凍サイクル装置を利用側熱交換器３に水熱交換器を用い、熱源側熱交換器５に空気熱交換器を用いる空冷式給湯器とし、冷凍サイクル内を循環する冷媒組成を変更し、例えば、高沸点成分を増やして、高圧圧力上昇を抑制し、高温給湯を可能とする。この場合、熱源側熱交換器５は蒸発器として動作し、利用側熱交換器３は凝縮器として動作する。
【００２２】
給湯器では、夜間に冷凍サイクル装置を稼働し、水道水を給水した貯湯タンク（図示省略）からポンプ（図示省略）により利用側熱交換器３の水熱交換器に水を流し、吸熱により貯湯タンク内の水を沸き上げる。この際、初めは早く温度を上げるため、冷凍サイクルの循環冷媒の組成を低沸点成分を増加させた組成とし、または標準組成とし、加熱能力を上げる。そして、ある程度温度が上がったら（例えば、６５℃）、循環冷媒の組成を高沸点成分を増加させた組成とし、高温（例えば、７０℃）とする。
その後は、温度維持を行うが、高温（例えば、７０℃）からの温度低下（例えば、６５℃）に伴う放熱ロス分を補うため、高沸点増加組成で運転する。
利用者は、沸き上がった貯湯タンクからの温水と水道水の給水とを混合し、適切温度で使用する。
利用量が増えるにつれ、貯湯タンクの湯量は減少するが、渇水状態にならない限り、昼間の補給（給水）は行わない。渇水状態になれば、貯湯タンクに、低沸点成分増加組成で、５５℃程度の温水を貯める、または高沸点成分増加組成で少しづつ貯湯する等、適宜選択する。
【００２３】
冷媒組成を変更しない場合は、第１開閉弁２１及び第２開閉弁２２を閉とする。圧縮機１から吐出された高温高圧の蒸気冷媒は、凝縮器として動作する利用側熱交換器３で凝縮液化して中温高圧の液冷媒となり、膨張弁４で減圧され、低温低圧の気液二相冷媒となって蒸発器として動作する熱源側熱交換器５に流入する。この冷媒は、熱源側熱交換器５で蒸発気化し、アキュムレータ６を経て再び圧縮機１へ戻る。このとき、利用側熱交換器３に流入する被加熱媒体である冷水は冷媒の凝縮潜熱によって加熱されて温水となり、貯湯タンクなどに供給される。また、熱源側熱交換器５に流入する被冷却媒体である空気は冷媒の蒸発潜熱によって冷却された後、外気などへ放出される。
【００２４】
次に、冷凍サイクル内を循環する冷媒組成を変更する場合の動作について説明する。
上述した給湯運転時において、冷凍サイクル内を循環する冷媒組成の高沸点成分を増加させる場合には、電磁弁２１、２２を開状態とする。この時、圧縮機１を出た高温高圧の蒸気冷媒の一部は、電磁弁２１を通って、冷媒精留器１１の下部の入口側に設けられた毛細管３１で中間圧力まで減圧された後、冷媒精留器１１の下部へ流入し、蒸気冷媒の一部が冷媒精留器１１内を上昇する。
ここで、毛細管３１、毛細管３２の仕様は、組成分離回路内の圧力および組成分離回路を流れる冷媒流量が適正となるように決定されている。
【００２５】
また、冷媒精留器１１の上部では、上昇した冷媒蒸気が第１冷却器１３に流入し、第２冷却器を流出した低圧気液二相冷媒によって冷却され、凝縮液化する。凝縮液化した冷媒は冷媒貯留器１４に流入し、貯留される。冷媒貯留器１４内では流入した液冷媒が徐々に蓄積され、冷媒貯留器１４が満液状態となると、オーバーフローした液冷媒が冷媒精留器１１の環流液として冷媒精留器１１の上部より流入する。この際、冷媒貯留器１４を含んだ精留回路内は、中間圧で釣り合うため、冷媒は冷媒貯留器１４から冷媒精留器１１へはオーバーフローで流れる。
この状態において、冷媒精留器１１内では、上昇する蒸気冷媒と、下降する液冷媒とが気液接触を行い、熱及び物質移動が行われ、いわゆる精留作用により、冷媒精留器１１内を上昇する蒸気冷媒は徐々に低沸点成分が増加し、冷媒貯留器１４内に貯留された液冷媒は徐々に低沸点成分に富んだ状態となる。
【００２６】
以上により、冷凍サイクル装置に充填した充填冷媒組成より低沸点成分に富んだ液冷媒が冷媒貯留器１４内に貯留され、冷凍サイクル内を循環する冷媒組成を高沸点成分に富んだものとすることができる。そこで、冷媒組成を所定の高沸点成分組成とすることにより、高温給湯時の高圧圧力上昇を抑制でき、高温給湯が可能となる。
また、冷媒精留器１１の下部から流出した中間圧力の気液二相冷媒は、第２冷却器１２に入り液化され、第３減圧装置である毛細管３２を経て減圧されたのち、低圧の気液二相冷媒となり、第２冷却器１２で冷媒精留器１１の下部から流出した気液二相冷媒を完全に液化させ、即ち、過冷却状態とさせ、液単相状態にするので、毛細管３２入口部が気液二相状態であることによって生じる組成分離回路内の流量不安定現象を抑えることが可能となる。
【００２７】
一方、給湯器の使用開始時等、低温の水を温める場合は、大きな能力が要求される。この場合は、冷凍サイクル内の冷媒組成を充填冷媒組成より低沸点成分に富んだ組成とする。即ち、電磁弁２１を閉とし、電磁弁２２を開とし、冷媒貯留器１４の低沸点成分に富んだ冷媒を冷凍サイクルに流し、冷凍サイクルのアキュムレータ６内に高沸点冷媒成分を余剰液冷媒として溜める。
【００２８】
ここで、冷凍サイクル内を循環する冷媒組成の目標値と目標値への制御方法について図２および図３を用いて説明する。図２は、Ｒ４０７Ｃにおいて、所望の給湯温度（例えば７０℃）が得られる場合の低沸点成分（Ｒ３２＋Ｒ１２５）の組成と高圧圧力の関係を示したものである。図２において、アは低沸点成分の組成と高圧圧力の関係を示しており、イは圧縮機の高圧圧力の使用限界を示している。また、Ａは低沸点成分が４８ｗｔ％に相当する高圧圧力を、Ｂは低沸点成分の組成を低下させた場合の高圧圧力の変化を、Ｃは高圧圧力をイ（圧縮機の高圧圧力の使用限界）以下とする場合の低沸点成分の組成（２２ｗｔ％）を示している。
【００２９】
図２より、Ｒ４０７Ｃの標準組成における低沸点成分の組成（４８ｗｔ％）では、所望の給湯温度を得るための高圧圧力が圧縮機の使用限界値を超えるため、実際には所望の給湯温度を得る運転は実現できないことを示している。ところが、Ｒ４０７Ｃが非共沸混合冷媒であることを利用し、低沸点成分の組成を４８ｗｔ％から２２ｗｔ％へ低下させることで圧縮機の使用限界以内で所望の給湯温度を得ることができる。従って、高圧圧力を圧縮機の使用限界値以下に抑制し、かつ所定の給湯温度を得ることが可能な冷媒組成の目標値は、低沸点成分（Ｒ３２＋Ｒ１２５）の組成が２２ｗｔ％以下となる。即ち、実際の目標値は、所定の給湯温度等によりこの範囲から決定する。
【００３０】
さらに、冷媒組成の目標値への制御方法について図３を用いて説明する。図３は、電磁弁２１、２２を開放状態としてからの経過時間（組成変化運転時間）に対する冷凍サイクル内を循環する低沸点成分の冷媒４０７Ｃの標準組成からの組成変化を示している。
図３より、冷凍サイクル内を循環する冷媒組成を目標値とするためには、電磁弁２１、２２をＴｏ時間（例えば、１時間）以上開放する必要があることがわかる。すなわち、電磁弁２１、２２の開放時間を所定時間以上とすることにより、冷媒組成の所定の目標値への制御が可能となる。
なお、冷凍サイクルの冷媒組成が標準組成でない場合は、後述の組成値を検知後、同じく図３の組成変化図から検知組成値と目標値までの電磁弁２１、２２の開放時間を算出し開放する。
また、標準組成のＲ４０７Ｃ冷媒充填された冷凍サイクルの電磁弁２１、２２の開放時間による制御方法以外に、利用側熱交換器３の水熱交換器の温水入口温度を検知し、その検知値に基づいて冷媒組成を制御することも可能である。
【００３１】
実施の形態１．
以下、本発明の実施の形態１の冷凍サイクル装置について説明する。
図４において、図１と同符号は同一または相当部分を示すので、説明を省略する。
冷凍サイクルの冷媒組成は、次のようにして検知できる。
図４に示すように毛細管３２入口部が過冷却液単相であることから、毛細管３２入口部に温度検出器Ｔ２、出口部に圧力検出器Ｐ１と温度検知器Ｔ１を設置し、検出した圧力Ｐ１、温度Ｔ１およびＴ２の信号を用いて組成を演算する組成演算手段であるマイコン４１を備えることにより、特開平１１−６３７４７号公報に開示のように冷凍サイクルの循環組成を演算・検知することが可能となり、より正確な循環組成の変更が可能となる。
【００３２】
また、電磁弁２１、２２の開閉操作により、冷凍サイクル内を循環する冷媒組成を所望の濃度に変更する場合、開閉操作は、前記循環組成演算・検知結果あるいは前記図３で説明したように、予め実験およびシミュレーションにて測定してある時間と冷凍サイクル内循環組成の関係により循環組成がわかるので、それを元に冷凍サイクル循環組成が所望の濃度となるように行われる。
【００３３】
次に、冷凍サイクルの冷媒組成を高沸点成分の多い組成から標準組成に戻す、または低沸点成分を増加させる別の方法を説明する。
先に、電磁弁２１を閉とし、電磁弁２２を開とし、冷媒貯留器１４の低沸点成分に富んだ冷媒を冷凍サイクルに流し、低沸点成分を増加させる方法を説明したが、以下に記載（図５、図６、図７）のように、開閉弁、減圧装置（図７はなし）付きの配管を設けることに、より早く低沸点成分を増加させることができる。当然ながら、冷媒精留器１１による精留を行うときは、新たに設けた開閉弁は閉じる。
図５に示すように冷媒貯留器１４の出口側と第２配管２６とを第３開閉弁である電磁弁２３及び第４減圧装置である毛細管３３を介して、第３配管２７で接続することによって、冷凍サイクル循環組成を高沸点成分の多い状態から標準組成に戻そうとする（または、低沸点成分を増やす）際に、電磁弁２１を閉じ、電磁弁２２、２３を開くことで組成分離回路内圧力と圧縮機１の吸入圧力との圧力差を利用して前記第３配管２７から冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増やす）ことが可能となる。
【００３４】
また、次のようにしてもよい。
図６に示すように冷媒貯留器１４の出口側と、冷凍サイクルの低圧側の熱交換器である熱源側熱交換器５の入口側とを第４開閉弁である電磁弁２４及び第５減圧装置である毛細管３４を介した第４配管２８で接続することによって、冷凍サイクル循環組成を高沸点成分の多い組成から標準組成に戻そうとする（または、低沸点成分を増加させる）際に、電磁弁２１を閉じ、電磁弁２２、電磁弁２４を開くことで組成分離回路内圧力と圧縮機１の吸入圧力との圧力差を利用して前記第４配管２８から冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができ、循環組成を早く標準組成に戻す（または、低沸点成分を増加させる）ことができる。また、冷媒貯留器１４内の液冷媒が熱源側熱交換器５内で蒸発するため、圧縮機１の液戻りを防止することができる。但し、電磁弁２２は閉じてもよい。
前記図５、図６に示すように、冷媒貯留器１４の出口側と冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続することにより、早く冷凍サイクルに低沸点成分を増加させることができる。
【００３５】
また、次のようにしてもよい。
図７に示すように、第１冷却器１３の出口側と、冷凍サイクルの高圧側の熱交換器である利用側熱交換器３の出口側とを第５開閉弁である電磁弁３７を介して第５配管２９で接続することによって、冷凍サイクル循環組成を高沸点成分多い状態から標準組成に戻そうとする（または、低沸点成分を増加させる）際に、電磁弁２１を閉じ、電磁弁２２、電磁弁３７を開くことで圧縮機１の吐出圧力と圧縮機１の吸入圧力との圧力差を利用して、即ち、圧縮機１の吐出圧力により冷媒貯留器１４上部から高圧をかけて下部から冷媒をおしだし、冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増加させる）ことができる。
【００３６】
本実施の形態では第１冷却器１３及び第２冷却器１２で冷却する冷媒は、第３減圧装置３２で減圧された冷媒を使用し、第２冷却器１２、第１冷却器１３の順に流入させて冷却しているが、これらの冷却器１２、１３の冷却は圧縮機１に吸入される低圧の冷媒を使用してもよい。
【００３７】
また、本実施の形態１の冷凍サイクル装置によれば、第３減圧装置３２の入口側に第１温度検出手段Ｔ２を、出口側に第１圧力検出手段Ｐ１と第２温度検出手段Ｔ１を設け、第１圧力検出手段Ｐ１により検出した圧力、第１温度検出手段Ｔ２および第２温度検出手段Ｔ１により検出したそれぞれの温度を用いて冷凍サイクルの冷媒組成を演算する組成演算手段を備えたので、冷凍サイクルの冷媒循環組成を検知することができ、この検知した冷媒組成に基づいて、所望の冷媒組成に変更が可能となる。
【００３８】
実施の形態２．
以下、本発明の実施の形態２の冷凍サイクル装置について説明する。
図８は本実施の形態に係わる冷凍サイクル装置を示す構成図であり、本実施の形態では、圧縮機１と利用側熱交換器３、熱源側熱交換器５との間に冷媒流路切換手段である四方弁２を設け、両熱交換器３、５の一方に流路切換え可能としている。その他の構成は実施の形態１と同じである。
そこで、四方弁２を切換えることにより、給湯運転（温水供給運転）とチラー運転（冷水供給運転）が可能となり、熱源側熱交換器５は、給湯運転（温水供給運転）時には蒸発器として動作し、チラー運転（冷水供給運転）時には凝縮器として動作する。また、利用側熱交換器３は、給湯運転時には凝縮器として動作し、チラー運転時には蒸発器として動作する。
【００３９】
まず、給湯（温水供給）運転の場合について説明する。冷凍サイクル内の冷媒の流れを図８に実線矢印で示す。給湯運転の場合、四方弁２は実線のように接続され、圧縮機１の出口側と利用側熱交換器３の入口部が接続されるとともに、アキュムレータ６の入口部と熱源側熱交換器５の出口部がそれぞれ接続される。
圧縮機１から吐出された高温高圧の蒸気冷媒は、四方弁２を経て凝縮器として動作する利用側熱交換器３で凝縮液化して中温高圧の液冷媒となり、膨張弁４で減圧され、低温低圧の気液二相冷媒となって蒸発器として動作する熱源側熱交換器５に流入する。
この冷媒は、熱源側熱交換器５で蒸発気化し、四方弁２、アキュムレータ６を経て再び圧縮機１へ戻る。このとき、利用側熱交換器３に流入する被加熱媒体である冷水は冷媒の凝縮潜熱によって加熱されて温水となり、貯湯タンクなどに供給される。また、熱源側熱交換器５に流入する被冷却媒体である空気は冷媒の蒸発潜熱によって冷却された後、外気などへ放出される。
なお、給湯運転時の冷凍サイクル内の循環組成の変更動作は、先に説明した参考例と同様であるため省略する。
【００４０】
また、四方弁２を設けたことで、低外気温時に熱源側熱交換器５表面に霜がついた場合、四方弁２を点線のように繋いで高温冷媒を熱源側熱交換器５に流し、付着した霜を溶かす霜取り運転が可能となる。
【００４１】
また、冷凍サイクル循環組成を高沸点成分の多い組成から標準組成に戻そうとする（または、低沸点成分を増加する）動作も同じである。
即ち、図９に示すように冷媒貯留器１４の出口側と第２配管２６とを第３開閉弁である電磁弁２３及び第４減圧装置である毛細管３３を介した第３配管２７で接続することによって、冷凍サイクル循環組成を高沸点成分の多い組成から標準組成に戻そうとする（または、低沸点成分を増加する）際に、電磁弁２１を閉じ、電磁弁２２、電磁弁２３を開くことで組成分離回路内の圧力と圧縮機１の吸入圧力との圧力差を利用して第３配管２７から冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増加する）ことが可能となる。
【００４２】
また、同様に、図１０に示すように冷媒貯留器１４の出口側と、冷凍サイクルの低圧側の熱交換器である熱源側熱交換器５の入口側とを第４開閉弁である電磁弁２４及び第５減圧装置である毛細管３４を介して第４配管２８で接続することによって、冷凍サイクル循環組成を標準組成に戻そうとする（または、低沸点成分を増加する）際に、電磁弁２１を閉じ、電磁弁２２、電磁弁２４を開くことで組成分離回路内の圧力と圧縮機１の吸入圧力との圧力差を利用して前記第４配管２８から冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができ、循環組成を早く標準組成に戻す（または、低沸点成分を増加する）ことができる。また、冷媒貯留器１４内の液冷媒が熱源側熱交換器５内で蒸発するため、圧縮機１の液戻りを防止することができる。但し、電磁弁２２は閉じてもよい。
前記のように、冷凍サイクルに低沸点成分を増加させるには、図９、図１０に示すように、冷媒貯留器１４の出口側と冷凍サイクルの低圧側とを開閉弁、減圧装置を介して配管接続すればよい。
【００４３】
また、同様に、図１１に示すように第１冷却器１３の出口側と、冷凍サイクルの高圧側熱交換器である利用側熱交換器３の出口側とを第５開閉弁である電磁弁３７を介して第５配管２９で接続することによって、冷凍サイクル循環組成を標準組成に戻そうとする（または、低沸点成分を増加する）際に、電磁弁２１を閉じ、電磁弁２２、電磁弁３７を開くことで圧縮機１の吐出圧力と圧縮機１の吸入圧力との圧力差を利用して冷媒貯留器１４に貯留された低沸点成分に富む冷媒を主冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増加する）ことができる。
【００４４】
次に、チラー（冷水供給）運転時の動作について説明する。チラー運転の場合、四方弁２は点線のように接続され、圧縮機１の出口側と熱源側熱交換器５が、アキュムレータ６の入口部と利用側熱交換器３がそれぞれ接続される。図８で冷凍サイクル内の冷媒の流れを点線矢印で示す。
チラー運転時には、圧縮機１で圧縮された高温高圧の蒸気冷媒は、四方弁２を経て凝縮器として動作する熱源側熱交換器５で凝縮液化し、膨張弁４で減圧され、低圧の気液二相冷媒となって蒸発器として動作する利用側熱交換器３に流入する。この冷媒は利用側熱交換器３で蒸発し、四方弁２、アキュムレータ６を経て再び圧縮機１へ戻る。膨張弁４は、熱源側熱交換器５出口の冷媒過冷却度が適正（例えば１０℃）となるようにその開度が制御されており、冷凍サイクル内の余剰な冷媒は、アキュムレータ６内に貯留される。
なお、チラー運転時の冷凍サイクル内の循環組成変更の動作は、先に説明した給湯運転時と同様であるため省略する。
【００４５】
また、チラー運転の場合も給湯運転時と同様に、図９に示すように冷媒貯留器１４の出口側と第２配管２６とを第３開閉弁である電磁弁２３及び第４減圧装置である毛細管３３を介した第３配管２７で接続することによって、冷凍サイクル循環組成を高沸点成分の多い組成から標準組成に戻そうとする（または、低沸点成分を増加する）際に、電磁弁２１を閉じ、電磁弁２２、２３を開くことで組成分離回路内圧力と圧縮機１の吸入圧力との圧力差を利用して前記第３配管２７から冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増加する）ことが可能となる。
【００４６】
また、図示していないが、図１０において、第４配管２８は冷凍サイクル側に、それぞれ開閉弁付きの分岐配管（または、流路切換弁付きの分岐配管）を接続し、給湯運転、チラー運転に対応して低圧側となる熱交換器に接続するようにしても、冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増加する）ことが可能となる。
【００４７】
前記のように、冷凍サイクルに低沸点成分を増加させるには、冷媒貯留器１４の出口側と冷凍サイクルの低圧側とを開閉弁、減圧装置を介して配管接続すればよい。
【００４８】
また、図示していないが、図１１において、第５配管２９は冷凍サイクル側に、それぞれ開閉弁付きの分岐配管（または、流路切換弁付きの分岐配管）を接続し、給湯運転、チラー運転に対応して高圧側となる熱交換器の出口側に接続するようにしても、冷媒貯留器１４に貯留された低沸点成分に富む冷媒を冷凍サイクルへ戻すことができるので、循環組成を早く標準組成に戻す（または、低沸点成分を増加する）ことが可能となる。
【００４９】
本実施の形態においても、冷凍サイクルの低沸点成分を増加するには、電磁弁２１を閉じ、電磁弁２２を開いて行うよりも、前記の方法により、早く冷凍サイクルの低沸点成分を増加することができる。
なお、本実施の形態に記載の冷媒流路切換手段である四方弁２は、前記の実施の形態１の図４に設置して、給湯運転に加えてチラー運転（冷水供給運転）を行うこともできる。
【００５０】
なお、実施の形態１、２の冷凍サイクルに冷媒の低沸点成分を増やす構成、即ち、冷媒貯留器１４の出口側と冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続した構成、及び第１冷却器１３の出口側と冷凍サイクルの高圧側の熱交換器の出口側とを開閉弁を介して配管接続した構成等により、冷凍サイクルに冷媒の低沸点成分を早く増やす効果は、第２冷却器１２がなくても同じく得られる。
【００５１】
本実施の形態１、２の冷凍サイクル装置によれば、開閉弁２４及び減圧装置３４を介して、冷媒貯留器１４の出口側と配管接続した冷凍サイクルの低圧側が、利用側熱交換器３及び熱源側熱交換器５のうち低圧側となる熱交換器の入口側となるようにしたので、開閉弁２４を開いて低沸点成分の冷媒を冷凍サイクルに流入させる際、冷凍サイクルの冷媒組成の低沸点成分を早く増やすことができるとともに、熱交換器で蒸発し、圧縮機１への液戻りを防止できる。
【００５２】
また、本実施の形態１、２の冷凍サイクル装置によれば、冷凍サイクルと、冷媒精留器１１と、第１冷却器１３と、冷媒貯留器１４と、第３減圧装置３２とを備え、第１開閉弁２５、第２開閉弁２６を開閉して冷媒組成を変える冷凍サイクル装置で、冷媒貯留器１４の出口側と冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続するか、または、第１冷却器１３の出口側と冷凍サイクルの高圧側の熱交換器の出口側とを開閉弁を介して配管接続し、第３減圧装置３２の冷媒精留器１１側に、冷媒精留器１１から出る冷媒を過冷却する第２冷却器１２を設けたので、早く冷凍サイクルの冷媒の低沸点成分増加できるとともに、第３減圧装置入口は液単相となり、冷媒精留器１１及び冷媒精留器１１まわりの配管の冷媒の流量が安定し、安定的に循環組成が変更可能となる。
【００５３】
また、本実施の形態１、２の冷凍サイクル装置によれば、第２冷却器１２は、第３減圧装置３２を通過後の冷媒との熱交換で冷却するので、第２冷却器１２と第３減圧装置３２は近接して設けることができ、配管の設置が容易となる。
【００５４】
また、本実施の形態１、２の冷凍サイクル装置によれば、第１冷却器１３は、第３減圧装置３２を通過後の冷媒との熱交換で冷却するので、第１冷却器１３と第３減圧装置３２は近接して設けることができ、配管の設置が容易となる。
【００５５】
実施の形態３．
以下、本発明の実施の形態３の冷凍サイクル装置について説明する。
図１２は本実施の形態に係わる冷凍サイクル装置を示す構成図であり、実施の形態２とほぼ同様の構成であるため詳細な説明は省略する。本実施の形態では、実施の形態２の図８における第２減圧装置である毛細管３１の手前に、即ち、圧縮機１側に、第３冷却器１５を設けている。
【００５６】
第３冷却器１５には、第３減圧装置３２で減圧された冷媒が、第２冷却器１２、第１冷却器１３の順に流れた後流入する。この流入冷媒が圧縮機１の出口から流出した高温高圧蒸気冷媒を冷却する。つまり、圧縮機１の出口から流出した高温高圧蒸気冷媒は、第３冷却器１５で冷却され液単相状態となり、毛細管３３で減圧され冷媒精留器１１へは乾き度の小さい気液二相冷媒が流入することとなる。このように乾き度が小さい気液二相冷媒が冷媒精留器１１へ流入されることによって、冷媒精留器１１の下部出口状態は液単相となり、冷媒精留器１１の下部の出口側、あるいは毛細管３２の入口部における脈動を抑え組成分離回路内の流量を安定させることができる。
【００５７】
なお、第３冷却器１５で熱交換し、圧縮機１のから流出した高温高圧蒸気冷媒を冷却する冷媒は、圧縮機１に吸入される低圧の冷媒を利用してもよい。
また、本実施の形態の第３冷却器１５を設ける構成は、実施の形態１にも適用でき、同様の効果が得られる。
また、本実施の形態においても、冷凍サイクルに冷媒の低沸点成分を増やす構成、即ち、冷媒貯留器１４の出口側と冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続した構成、及び第１冷却器１３の出口側と冷凍サイクルの高圧側の熱交換器の出口側とを開閉弁を介して配管接続した構成等により、実施の形態１、２に記載と同じ効果が得られる。
【００５８】
前記の実施の形態２、３では、冷凍サイクル装置を給湯装置（温水給湯、冷水給湯）の例として説明してきたが、本冷凍サイクル装置は空気調和装置、冷凍装置としても利用できる。即ち、温水給湯は空気調和装置の暖房運転に、冷水給湯は空気調和装置の冷房運転または冷凍装置に、それぞれ対応する。また、それぞれ同様な効果が得られる。
その際、空気調和装置においては、冷凍サイクルの利用側熱交換器３が室内機となり、冷凍サイクルのその他構成と組成分離ユニット６３は室外機とするのが望ましい。また、冷凍装置では、冷凍サイクルの利用側熱交換器３でショーケースを構成し、冷凍サイクルのその他の構成と組成分離ユニット６３は室外機とするのが望ましい。
【００５９】
また、本実施の形態３の冷凍サイクル装置によれば、冷媒精留器１１の下部と冷凍サイクルの圧縮機１の出口側とを接続する配管の冷媒精留器１１の入口側に設けた第２減圧装置３１の圧縮機１側に第３冷却器１５を設けたので、圧縮機１から出た高温高圧ガス冷媒は第３冷却器１５で冷却され、液単相となり、第２減圧装置３１で減圧され、冷媒精留器１１へは乾き度が小さい気液二相として流入される。そこで、冷媒精留器１１の下部出口では液単相となり、冷媒精留器１１の出口側の脈動が抑えられ、冷媒の流れが安定する。
【００６０】
また、本実施の形態３の冷凍サイクル装置によれば、第１冷却器１３、第２冷却器１２及び第３冷却器１５によるそれぞれの冷媒の冷却は、第３減圧装置３２で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるので、第１冷却器１３、第２冷却器１２、第３冷却器１５及び第３減圧装置３２を比較的近接して設置でき、これらをまとめてユニット化でき設置、取扱いが容易になる。
【００６１】
本実施の形態２、３の冷凍サイクル装置によれば、冷凍サイクルの圧縮機１の出口側に、利用側熱交換器３または熱源側熱交換器５に冷媒流路を切換える冷媒流路切換手段２を設けたので、冷媒流路切換手段２を切換えることにより、冷凍サイクル装置を温水給湯と冷水給湯可能な給湯装置、及び、暖房と冷房可能な空気調和装置として使用できる。
【００６２】
【発明の効果】
以上説明したとおり、本発明の冷凍サイクル装置は、冷凍サイクルと、冷媒精留器と、冷媒精留器で分離された低沸点冷媒成分を冷却する第１冷却器と、冷媒貯留器とを備え、第１開閉弁と第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、冷媒精留器の下部と冷凍サイクルの圧縮機の出口側とを接続する配管の冷媒精留器の入口側に第２減圧装置を設け、冷媒精留器の下部と冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、該第３減圧装置の冷媒精留器側に、冷媒精留器から出る冷媒を過冷却する第２冷却器を設け、第２減圧装置の圧縮機側に第３冷却器を設け、第１冷却器、第２冷却器及び第３冷却器によるそれぞれの冷媒の冷却は、第３減圧装置で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるものである。
そこで、第３減圧装置入口は必ず液単相となるため、冷媒精留器及び冷媒精留器まわりの配管の冷媒の流量が安定し、安定的に循環組成が変更可能となり、非共沸混合冷媒を用いる冷凍サイクル装置の性能が向上する。
【００６３】
また、本発明の冷凍サイクル装置は、冷凍サイクルと、冷媒精留器と、第１冷却器と、冷媒貯留器とを備え、第１開閉弁と第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、冷媒精留器の下部と冷凍サイクルの圧縮機の出口側とを接続する配管の冷媒精留器の入口側に第２減圧装置を設け、また、冷媒精留器の下部と冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、冷媒貯留器の出口側と冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続し、第３減圧装置の冷媒精留器側に、第２冷却器を設け、第２減圧装置の圧縮機側に第３冷却器を設け、第１冷却器、第２冷却器及び第３冷却器によるそれぞれの冷媒の冷却は、第３減圧装置で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるものである。
そこで、冷凍サイクルの冷媒循環組成を低沸点成分が増加するように変化させる際、冷媒貯留器の出口側と冷凍サイクルの低圧側とを接続する配管の開閉弁を開くことにより、早く冷凍サイクルの冷媒の低沸点成分を増加することができ、非共沸混合冷媒を用いる冷凍サイクル装置の性能が向上する。
【００６４】
また、本発明の冷凍サイクル装置は、冷凍サイクルと、冷媒精留器と第１冷却器と冷媒貯留器とを備え、第１開閉弁と第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、冷媒精留器の下部と冷凍サイクルの圧縮機の出口側とを接続する配管の冷媒精留器の入口側に第２減圧装置を設け、また、冷媒精留器の下部と冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、第１冷却器の出口側と冷凍サイクルの高圧側の熱交換器の出口側とを開閉弁を介して配管接続し、第３減圧装置の冷媒精留器側に、第２冷却器を設け、第２減圧装置の圧縮機側に第３冷却器を設け、第１冷却器、第２冷却器及び第３冷却器によるそれぞれの冷媒の冷却は、第３減圧装置で減圧された冷媒が、第２冷却器、第１冷却器、第３冷却器の順に、それぞれの冷媒と熱交換することにより行われるものである。
そこで、冷凍サイクルの冷媒循環組成を低沸点成分が増加するように変化させる際、第１冷却器の出口側と冷凍サイクルの利用側熱交換器の出口側とを第５開閉弁を開くことにより、早く冷凍サイクルの冷媒の低沸点成分を増加することができ、非共沸混合冷媒を用いる冷凍サイクル装置の性能が向上する。
【図面の簡単な説明】
【図１】 参考例における冷凍サイクル装置の冷媒回路構成を示す図である。
【図２】 参考例における低沸点成分の組成と高圧圧力の関係を示す図である。
【図３】 参考例における組成変化運転時間と低沸点成分の組成の関係を示す図である。
【図４】 本発明の実施の形態１に係わる冷凍サイクル装置の冷媒組成の検知方法を説明する図である。
【図５】 本発明の実施の形態１に係わる冷凍サイクル装置の冷凍サイクルの低沸点成分を増加する方法を説明する図である。
【図６】 本発明の実施の形態１に係わる冷凍サイクル装置の冷凍サイクルの低沸点成分を増加する別の方法を説明する図である。
【図７】 本発明の実施の形態１に係わる冷凍サイクル装置の冷凍サイクルの低沸点成分を増加するさらに別の方法を説明する図である。
【図８】 本発明の実施の形態２に係わる冷凍サイクル装置の冷媒回路構成を示す図である。
【図９】 本発明の実施の形態２に係わる冷凍サイクル装置の冷凍サイクルの低沸点成分を増加する方法を説明する図である。
【図１０】 本発明の実施の形態２に係わる冷凍サイクル装置の冷凍サイクルの低沸点成分を増加する別の方法を説明する図である。
【図１１】 本発明の実施の形態２に係わる冷凍サイクル装置の冷凍サイクルの低沸点成分を増加するさらに別の方法を説明する図である。
【図１２】 本発明の実施の形態３に係わる冷凍サイクル装置の冷媒回路構成を示す図である。
【符号の説明】
１ 圧縮機、２ 冷媒流路切換手段、３ 利用側熱交換器、４ 第１の減圧装置、５ 熱源側熱交換器、１１ 冷媒精留器、１２ 第２冷却器、１３ 第１冷却器、１４ 冷媒貯留器、１５ 第３冷却器、２１ 第１開閉弁、２２ 第２開閉弁、３１ 第２減圧装置、３２ 第３減圧装置。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a refrigeration cycle apparatus that uses a non-azeotropic refrigerant mixture as a refrigerant, and more particularly to an improvement of a refrigeration cycle apparatus that changes a refrigerant composition circulating in the refrigeration cycle.
[0002]
[Prior art]
Refrigerant composition change that changes the composition of refrigerant circulating in the refrigeration cycle to control the capacity of air conditioners equipped with compressors that cannot change the rotation speed of electric motors and to reduce the high-pressure pressure during high-temperature hot water supply using heat pump water heaters A refrigeration cycle apparatus equipped with means has been proposed.
These refrigeration cycle devices are intended to obtain a wide range of capacity control with high efficiency without using an inverter that changes the rotation speed of the motor of the compressor. The compressor, the heat source side heat exchanger, the pressure reduction A refrigeration cycle equipped with a device, a use side heat exchanger, a non-azeotropic refrigerant mixture composed of a low-boiling refrigerant and a high-boiling refrigerant, a refrigerant rectifier that produces a refrigerant rich in low-boiling components, A first refrigerant reservoir that stores a refrigerant that is rich in low-boiling components that has been discharged from the distillation apparatus, and a second refrigerant reservoir that stores refrigerant that is rich in high-boiling components; By adjusting the amount of liquid refrigerant in the second refrigerant reservoir, the composition circulating in the refrigeration cycle can be continuously changed, and the ability according to the load can always be exhibited.
[0003]
The following is an example of a refrigeration cycle apparatus.
The outlet of the compressor and the lower part of the refrigerant rectifier are connected by piping through a solenoid valve, and a cooler for exchanging heat with the suction piping of the compressor is provided in the middle of this piping. . Furthermore, the lower part of the refrigerant rectifier and the accumulator are connected by piping through a capillary tube and an electromagnetic valve.
A cooler and a first refrigerant reservoir are annularly connected to the upper part of the refrigerant rectifier, and the cooler is configured to allow a part of the refrigerant sucked into the compressor to flow in via an electromagnetic valve. ing.
[0004]
The compressor, the four-way valve, the heat source side heat exchanger, the accumulator, the refrigerant rectifier, the first refrigerant reservoir, the cooler, the cooler, the electromagnetic valve, the capillary tube, and their connection pipes are housed in the outdoor unit.
[0005]
The indoor unit includes an electronic expansion valve that is a first pressure reducing device and a use side heat exchanger.
These outdoor units and indoor units are connected by two pipes to form a refrigeration cycle. This refrigeration cycle is filled with a non-azeotropic refrigerant mixture comprising a high-boiling component and a low-boiling component. The heat source side heat exchanger operates as an evaporator during heating operation, and operates as a condenser during cooling operation. The use side heat exchanger operates as a condenser during the heating operation, and operates as an evaporator during the cooling operation.
[0006]
For example, during the heating operation, excess refrigerant in the refrigeration cycle is stored in the accumulator. The refrigerant in the accumulator is separated into a liquid refrigerant rich in high-boiling components and a vapor refrigerant rich in low-boiling components. For this reason, when a liquid refrigerant is stored in the accumulator, the refrigerant composition circulating in the cycle has a low boiling point component as compared with the filling composition.
[0007]
On the other hand, when increasing the high-boiling components of the refrigerant composition circulating in the refrigeration cycle, a part of the high-temperature and high-pressure vapor refrigerant that has exited the compressor is opened into the cooler by opening the solenoid valve. The steam is cooled by a low-temperature and low-pressure compressor suction refrigerant in the cooler, and is cooled to a saturated steam or gas-liquid two-phase state. The high-pressure gas-liquid two-phase refrigerant exiting the cooler flows into the lower part of the refrigerant rectifier, and among these, the refrigerant vapor rises in the refrigerant rectifier.
In the upper part of the refrigerant rectifier, the rising refrigerant vapor flows into the cooler, and is cooled by the refrigerant sucked into the low-temperature compressor that has flowed in through the electromagnetic valve, and is condensed and liquefied. This liquid refrigerant flows into the refrigerant reservoir and is stored.
From the inside of the refrigerant reservoir, the liquid refrigerant flows into the refrigerant rectifier from the upper part as the circulating liquid of the refrigerant rectifier.
[0008]
That is, in the refrigerant rectifier, the rising vapor refrigerant and the falling liquid refrigerant are in gas-liquid contact, heat and mass transfer are performed, and the vapor refrigerant rising in the refrigerant rectifier gradually has a low boiling point. Components increase and liquid refrigerant rich in low-boiling components is stored in the refrigerant reservoir.
[0009]
As the liquid refrigerant stored in the refrigerant reservoir increases, the liquid refrigerant in the accumulator decreases, and the liquid refrigerant rich in high-boiling components stored in the accumulator is released into the cycle and rich in low-boiling components. The liquid refrigerant is stored in the refrigerant reservoir. As a result, the refrigerant composition circulating in the refrigeration cycle can be enriched with high-boiling components.
For example, in a refrigeration cycle filled with a refrigerant (R407C) in which R32 is 23%, R125 is 25%, and R134a is mixed in a weight ratio of 52%, the composition of R32, which is a low boiling point component, is in the range of 45% to 5%. By controlling, the capacity can be controlled in the range of 130% to 70% when the capacity at the filling composition (composition of R32 is 23%) is 100%.
[0010]
As described above, in the conventional invention, by adjusting the amount of liquid refrigerant rich in low-boiling components stored in the refrigerant reservoir and the amount of liquid refrigerant rich in high-boiling components stored in the accumulator, the inside of the refrigeration cycle is adjusted. Since the circulating refrigerant composition can be changed, it is possible to perform a wide range of capacity control at a low cost by changing the refrigerant composition, compared to the case where the rotation speed control of the electric motor by the inverter is performed (see, for example, Patent Document 1). .
[0011]
[Patent Document 1]
JP-A-10-267436 (pages 4-7, FIG. 1)
[0012]
[Problems to be solved by the invention]
However, in the conventional refrigeration cycle apparatus, depending on the structure of the refrigerant rectifier, the refrigerant state flowing out from the lower part of the refrigerant rectifier may be a gas-liquid two-phase, so that the refrigerant flowing into the downstream capillary inlet is gas-liquid. The pulsation which repeats a two-phase state and a liquid phase state alternately arises, and the subject that the refrigerant | coolant flow rate in a refrigerant | coolant rectifier became unstable occurred.
The present invention has been made to solve the above-described problems, and uses a non-azeotropic refrigerant mixture to change the refrigerant composition in the refrigeration cycle and change the refrigerant flow rate in the refrigerant rectifier of the refrigeration cycle apparatus that operates. An object is to improve the performance of the refrigeration cycle apparatus, such as being able to stabilize or changing the refrigerant circulation composition in the refrigeration cycle, such that the low-boiling components can be increased quickly.
[0013]
[Means for Solving the Problems]
A refrigeration cycle apparatus of the present invention includes a refrigeration cycle, a refrigerant rectifier, a first cooler that cools a low-boiling-point refrigerant component separated by the refrigerant rectifier, and a refrigerant reservoir. In the refrigeration cycle apparatus in which the ratio of the low-boiling refrigerant component and the high-boiling refrigerant component of the non-azeotropic refrigerant mixture in the refrigeration cycle is variable by opening and closing the second on-off valve and the second on-off valve, A second pressure reducing device is provided on the inlet side of the refrigerant rectifier of the pipe connecting the outlet side of the compressor of the cycle, and a third pressure reducing device is provided on the pipe connecting the lower portion of the refrigerant rectifier and the low pressure side of the refrigeration cycle. A second cooler is provided on the refrigerant rectifier side of the third decompressor to supercool the refrigerant coming out of the refrigerant rectifier, and a third cooler is provided on the compressor side of the second decompressor. The cooling of each refrigerant by the first cooler, the second cooler, and the third cooler Decompressed refrigerant at the decompressor is, the second cooler, the first cooler, the order of the third cooler are those carried out by each of the refrigerant heat exchanger.
[0014]
In addition, the refrigeration cycle apparatus of the present invention includes a refrigeration cycle, a refrigerant rectifier, a first cooler, and a refrigerant reservoir, and opens and closes a first on-off valve and a second on-off valve, thereby refrigeration. In a refrigeration cycle apparatus in which the ratio of the low-boiling refrigerant component and the high-boiling refrigerant component of the non-azeotropic refrigerant mixture in the cycle is variable, the pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle A second decompression device is provided on the inlet side of the refrigerant rectifier, and a third decompression device is installed in a pipe connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle, and the outlet side of the refrigerant reservoir The low pressure side of the refrigeration cycle is connected to the low pressure side via an on-off valve and a pressure reducing device, a second cooler is provided on the refrigerant rectifier side of the third pressure reducing device, and a third cooling is provided on the compressor side of the second pressure reducing device. Each of the refrigerants by the first cooler, the second cooler and the third cooler Cooling refrigerant decompressed by the third decompressor, a second cooler, the first cooler, the order of the third cooler are those carried out by each of the refrigerant heat exchanger.
[0015]
Further, the refrigeration cycle apparatus of the present invention includes a refrigeration cycle, a refrigerant rectifier, a first cooler, and a refrigerant reservoir, and opens and closes a first on-off valve and a second on-off valve so that the inside of the refrigeration cycle is provided. In the refrigeration cycle apparatus in which the ratio of the low-boiling refrigerant component and the high-boiling refrigerant component of the non-azeotropic refrigerant mixture is variable, the refrigerant concentration of the pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle is A second pressure reducing device is provided on the inlet side of the still, and a third pressure reducing device is installed on a pipe connecting the lower portion of the refrigerant rectifier and the low pressure side of the refrigeration cycle, and the outlet side of the first cooler is connected to the refrigeration unit. Among the use side heat exchanger and the heat source side heat exchanger of the cycle, the outlet side of the high pressure side heat exchanger is connected by piping through an on-off valve, and the second depressurization device is connected to the refrigerant rectifier side by the second side. A cooler, a third cooler on the compressor side of the second decompressor, a first cooler, The cooling of the respective refrigerants by the cooler and the third cooler is such that the refrigerant decompressed by the third decompression device exchanges heat with the respective refrigerants in the order of the second cooler, the first cooler, and the third cooler. It is done by.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Reference example
Hereinafter, a refrigeration cycle apparatus will be described as a reference example.
FIG. 1 is a configuration diagram showing a refrigeration cycle apparatus in the present reference example. In the figure, the refrigeration cycle is configured by connecting a compressor 1, a use side heat exchanger 3, an expansion valve 4, which is a first pressure reducing device, a heat source side heat exchanger 5, and an accumulator 6. It is stored inside.
The composition separation circuit includes a refrigerant rectifier 11 as a composition separation means, a refrigerant reservoir 14 for storing refrigerant, a first cooler 13, a second cooler 12, a capillary tube 31 as a second decompression device, a first 3 A capillary 32 that is a pressure reducing device, an electromagnetic valve 21 that is a first on-off valve, and an electromagnetic valve 22 that is a second on-off valve. The first cooler 13 and the refrigerant reservoir 14 are located above the refrigerant rectifier 11. It is connected in a ring. These are housed in the composition separation unit 63.
[0017]
The refrigeration cycle unit 62 and the composition separation unit 63 are connected by two pipes that are the first pipe 25 and the second pipe 26 to form a refrigeration cycle apparatus in which the refrigerant composition circulating in the refrigerant circuit can be changed. Yes. In this refrigeration cycle apparatus, for example, a three-component non-azeotropic mixed refrigerant R407C (standard composition; R32: R125: R134a = 23: 25: 52 wt%) composed of a high boiling point component (R134a) and a low boiling point component (R32 + R125). Filled.
[0018]
Further, the refrigerant rectifier 11 is filled with a filler for increasing the gas-liquid contact area.
In addition, the outlet side of the compressor 1, that is, a pipe that discharges refrigerant discharged from the compressor, and a pipe that connects the compressor and the use side heat exchanger 3 (in Embodiment 2 described later, the compressor and the four-way The piping connecting the valve 2) and the lower part of the refrigerant rectifier 11 are connected by a first piping 25 via a solenoid valve 21 and a capillary tube 31 which are first on-off valves. That is, the first pipe 25 connects the inlet of the first on-off valve 21 and the pipe between the compressor 1 and the use side heat exchanger 3 (in the second embodiment described later, the inlet of the first on-off valve 21 and The pipe between the compressor 1 and the four-way valve 2 is connected).
[0019]
In addition, the intermediate-pressure gas-liquid two-phase refrigerant flowing out from the lower part of the refrigerant rectifier 11 enters the second cooler 12 and is liquefied and reduced in pressure through the capillary tube 32 to become a low-pressure gas-liquid two-phase refrigerant. Returning to the second cooler 12, the gas-liquid two-phase refrigerant flowing out from the lower part of the refrigerant rectifier 11 is completely liquefied by the second cooler 12, that is, in a supercooled state, itself becomes a low-pressure vapor refrigerant, Further, the refrigerant enters the first cooler 13 and cools and liquefies the low-boiling-component refrigerant vapor exiting the refrigerant rectifier 11, passes through the second on-off valve 26 and the second pipe 26, and enters the inlet of the accumulator 6. Inflow. Here, the second pipe 26 connects the inlet of the second on-off valve 22 and the pipe of the inlet of the accumulator 6. However, the second pipe 26 may connect the inlet of the second on-off valve 22 and the low-pressure side pipe of the refrigeration cycle, that is, the pipe between the first pressure reducing device 4 and the accumulator 6 (described later). In Embodiment 2, the piping between the first pressure reducing device 4 and the accumulator 6 is connected to the low pressure piping on the downstream side of the first pressure reducing device 4).
That is, the refrigeration cycle and the composition separation circuit are connected by the first pipe 25 and the second pipe 26.
[0020]
In addition, since the refrigeration cycle unit 62 and the composition separation unit 63 connect the refrigeration cycle accommodated in the refrigeration cycle unit 62 and the composition separation circuit by the first pipe 25 and the second pipe 26, respectively. A composition separation unit 63 can be connected. Further, when connecting, the number of connection points can be reduced without greatly changing the existing refrigeration cycle unit 62, and connection is easy.
Further, in the composition separation circuit, a capillary tube 31 that is a second pressure reducing device and a capillary tube 32 that is a third pressure reducing device are connected to the refrigerant rectifier 11, and the former is the discharge side of the compressor 1 and the latter is the same. Since it is connected to the suction side, the refrigerant rectifier 11 operates at an intermediate pressure. Therefore, the difference between the liquid composition and the gas composition is larger than when operating at high pressure (non-azeotropicity increases), and the separation efficiency (the concentration difference between liquid and gas is higher than when operating at high pressure). (Proportional) becomes higher.
[0021]
Next, the operation of the refrigeration cycle apparatus of the present reference example configured as described above will be described. In this reference example, the refrigeration cycle apparatus is an air-cooled water heater that uses a water heat exchanger for the use side heat exchanger 3 and an air heat exchanger for the heat source side heat exchanger 5, and the refrigerant composition that circulates in the refrigeration cycle. For example, the high-boiling point component is increased to suppress the increase in the high pressure and enable hot water supply. In this case, the heat source side heat exchanger 5 operates as an evaporator, and the use side heat exchanger 3 operates as a condenser.
[0022]
In the water heater, the refrigeration cycle apparatus is operated at night, water is passed from the hot water storage tank (not shown) supplied with tap water to the water heat exchanger of the use side heat exchanger 3 by a pump (not shown), and the hot water is stored by heat absorption. Boil the water in the tank. At this time, in order to raise the temperature quickly at the beginning, the composition of the circulating refrigerant in the refrigeration cycle is set to a composition in which the low-boiling components are increased or a standard composition to increase the heating capacity. And if temperature rises to some extent (for example, 65 degreeC), let the composition of a circulating refrigerant be the composition which increased the high boiling point component, and will be high temperature (for example, 70 degreeC).
Thereafter, the temperature is maintained, but operation is performed with a high boiling point increasing composition in order to compensate for the heat radiation loss due to a temperature drop (eg, 65 ° C.) from a high temperature (eg, 70 ° C.).
The user mixes the hot water from the heated hot water storage tank with the tap water supply and uses it at an appropriate temperature.
As the amount of water used increases, the amount of hot water in the hot water storage tank decreases, but replenishment (water supply) is not performed during the day unless it becomes drought. If the water is in a drought state, the hot water tank is appropriately selected to store hot water of about 55 ° C. with a low boiling point component increasing composition or store hot water little by little with a high boiling point component increasing component.
[0023]
When the refrigerant composition is not changed, the first on-off valve 21 and the second on-off valve 22 are closed. The high-temperature and high-pressure vapor refrigerant discharged from the compressor 1 is condensed and liquefied by the use-side heat exchanger 3 operating as a condenser to become a medium-temperature and high-pressure liquid refrigerant, and is decompressed by the expansion valve 4, and the low-temperature and low-pressure gas-liquid two is discharged. It becomes a phase refrigerant and flows into the heat source side heat exchanger 5 that operates as an evaporator. This refrigerant evaporates in the heat source side heat exchanger 5 and returns to the compressor 1 again through the accumulator 6. At this time, the cold water that is the medium to be heated flowing into the use side heat exchanger 3 is heated by the latent heat of condensation of the refrigerant to become hot water, and is supplied to a hot water storage tank or the like. In addition, air that is a medium to be cooled flowing into the heat source side heat exchanger 5 is cooled by the latent heat of vaporization of the refrigerant, and then released to the outside air.
[0024]
Next, the operation for changing the refrigerant composition circulating in the refrigeration cycle will be described.
In the hot water supply operation described above, when increasing the high boiling point component of the refrigerant composition circulating in the refrigeration cycle, the electromagnetic valves 21 and 22 are opened. At this time, after a part of the high-temperature and high-pressure vapor refrigerant exiting the compressor 1 passes through the electromagnetic valve 21 and is reduced to an intermediate pressure by the capillary tube 31 provided on the lower inlet side of the refrigerant rectifier 11. Then, it flows into the lower part of the refrigerant rectifier 11, and a part of the vapor refrigerant rises in the refrigerant rectifier 11.
Here, the specifications of the capillary tube 31 and the capillary tube 32 are determined so that the pressure in the composition separation circuit and the flow rate of the refrigerant flowing through the composition separation circuit are appropriate.
[0025]
Moreover, in the upper part of the refrigerant | coolant rectifier 11, the raised refrigerant | coolant vapor | steam flows in into the 1st cooler 13, is cooled by the low pressure gas-liquid two-phase refrigerant | coolant which flowed out the 2nd cooler, and is condensed and liquefied. The condensed and liquefied refrigerant flows into the refrigerant reservoir 14 and is stored. The liquid refrigerant that has flowed in gradually accumulates in the refrigerant reservoir 14, and when the refrigerant reservoir 14 becomes full, the overflowed liquid refrigerant flows from the upper part of the refrigerant rectifier 11 as the circulating liquid of the refrigerant rectifier 11. To do. At this time, since the inside of the rectification circuit including the refrigerant reservoir 14 is balanced by the intermediate pressure, the refrigerant flows from the refrigerant reservoir 14 to the refrigerant rectifier 11 by overflow.
In this state, in the refrigerant rectifier 11, the rising vapor refrigerant and the descending liquid refrigerant make gas-liquid contact, and heat and mass transfer are performed. The low-boiling component gradually increases in the vapor refrigerant rising, and the liquid refrigerant stored in the refrigerant reservoir 14 gradually becomes rich in low-boiling components.
[0026]
As described above, the liquid refrigerant richer in the low boiling point component than the charged refrigerant composition charged in the refrigeration cycle apparatus is stored in the refrigerant reservoir 14, and the refrigerant composition circulating in the refrigeration cycle is rich in the high boiling point component. Can do. Therefore, by setting the refrigerant composition to a predetermined high boiling point component composition, it is possible to suppress an increase in high-pressure pressure during hot water supply and to enable hot water supply.
The intermediate-pressure gas-liquid two-phase refrigerant flowing out from the lower part of the refrigerant rectifier 11 enters the second cooler 12 and is liquefied and reduced in pressure through the capillary 32 serving as the third decompression device. Since the gas-liquid two-phase refrigerant that has become a liquid two-phase refrigerant and has flowed out from the lower portion of the refrigerant rectifier 11 in the second cooler 12 is completely liquefied, that is, in a supercooled state, a liquid single-phase state is obtained. It is possible to suppress the flow rate instability phenomenon in the composition separation circuit caused by the 32 inlet portion being in a gas-liquid two-phase state.
[0027]
On the other hand, when warm water is warmed, such as when starting to use a water heater, a large capacity is required. In this case, the refrigerant composition in the refrigeration cycle is richer in lower boiling point components than the charged refrigerant composition. That is, the solenoid valve 21 is closed, the solenoid valve 22 is opened, the refrigerant rich in the low boiling point component of the refrigerant reservoir 14 is caused to flow into the refrigeration cycle, and the high boiling point refrigerant component is used as an excess liquid refrigerant in the accumulator 6 of the refrigeration cycle. Accumulate.
[0028]
Here, the target value of the refrigerant composition circulating in the refrigeration cycle and a control method for the target value will be described with reference to FIGS. FIG. 2 shows the relationship between the composition of the low boiling point component (R32 + R125) and the high pressure when a desired hot water supply temperature (for example, 70 ° C.) is obtained in R407C. In FIG. 2, a shows the relationship between the composition of the low boiling point component and the high pressure, and a shows the use limit of the high pressure of the compressor. A is a high pressure corresponding to 48 wt% of the low boiling point component, B is a change in the high pressure when the composition of the low boiling point is lowered, and C is a high pressure change (use of the high pressure of the compressor). The composition (22 wt%) of the low boiling point component in the case of (limit) or less is shown.
[0029]
From FIG. 2, the low boiling point component (48 wt%) in the standard composition of R407C has a high hot pressure for obtaining a desired hot water supply temperature that exceeds the use limit value of the compressor. It shows that driving cannot be realized. However, by utilizing the fact that R407C is a non-azeotropic refrigerant mixture, the desired hot water supply temperature can be obtained within the operating limit of the compressor by reducing the composition of the low boiling point component from 48 wt% to 22 wt%. Therefore, the target value of the refrigerant composition capable of suppressing the high pressure to be below the use limit value of the compressor and obtaining a predetermined hot water supply temperature is 22 wt% or less of the composition of the low boiling point component (R32 + R125). That is, the actual target value is determined from this range by a predetermined hot water supply temperature or the like.
[0030]
Furthermore, the control method to the target value of a refrigerant composition is demonstrated using FIG. FIG. 3 shows the composition change from the standard composition of the low-boiling-point refrigerant 407C circulating in the refrigeration cycle with respect to the elapsed time (composition change operation time) after the electromagnetic valves 21 and 22 are opened.
FIG. 3 shows that the electromagnetic valves 21 and 22 need to be opened for To time (for example, 1 hour) or more in order to set the refrigerant composition circulating in the refrigeration cycle to the target value. That is, by setting the opening time of the solenoid valves 21 and 22 to a predetermined time or longer, it is possible to control the refrigerant composition to a predetermined target value.
If the refrigerant composition of the refrigeration cycle is not the standard composition, after detecting the composition value described later, the opening time of the solenoid valves 21 and 22 from the composition change diagram of FIG. 3 to the detected composition value and the target value is calculated and opened. To do.
In addition to the control method based on the opening time of the solenoid valves 21 and 22 of the refrigeration cycle filled with the R407C refrigerant of the standard composition, the hot water inlet temperature of the water heat exchanger of the use side heat exchanger 3 is detected, and the detected value is It is also possible to control the refrigerant composition based on this.
[0031]
Embodiment 1 FIG.
Hereinafter, the refrigeration cycle apparatus of Embodiment 1 of the present invention will be described.
In FIG. 4, the same reference numerals as those in FIG.
The refrigerant composition of the refrigeration cycle can be detected as follows.
As shown in FIG. 4, the capillary 32 inlet is a supercooled liquid single phase, so the temperature detector T2 is installed at the capillary 32 inlet, and the pressure detector P1 and the temperature detector T1 are installed at the outlet, and the detected pressure By calculating and detecting the circulation composition of the refrigeration cycle as disclosed in Japanese Patent Application Laid-Open No. 11-63747 by providing the microcomputer 41 which is a composition calculation means for calculating the composition using the signals of P1, temperatures T1 and T2. It becomes possible to change the circulation composition more accurately.
[0032]
Further, when the refrigerant composition circulating in the refrigeration cycle is changed to a desired concentration by opening / closing the solenoid valves 21 and 22, the opening / closing operation is performed as described in the circulation composition calculation / detection result or the above-described FIG. Since the circulation composition can be determined from the relationship between the time measured in advance through experiments and simulations and the circulation composition in the refrigeration cycle, the refrigeration cycle circulation composition is adjusted to a desired concentration based on the relationship.
[0033]
Next, another method for returning the refrigerant composition of the refrigeration cycle from the composition having a high high-boiling component to the standard composition or increasing the low-boiling component will be described.
First, the method of increasing the low boiling point component by closing the electromagnetic valve 21 and opening the electromagnetic valve 22 and flowing the refrigerant rich in the low boiling point component of the refrigerant reservoir 14 to the refrigeration cycle has been described. As shown in FIGS. 5, 6, and 7, the low boiling point component can be increased more quickly by providing a pipe with an on-off valve and a pressure reducing device (not shown in FIG. 7). Of course, when performing rectification by the refrigerant rectifier 11, the newly provided on-off valve is closed.
As shown in FIG. 5, the outlet side of the refrigerant reservoir 14 and the second pipe 26 are connected by a third pipe 27 via an electromagnetic valve 23 that is a third on-off valve and a capillary tube 33 that is a fourth pressure reducing device. Therefore, when the refrigeration cycle circulation composition is to be returned to the standard composition from the state with a large amount of high-boiling components (or when the low-boiling components are increased), the composition is separated by closing the solenoid valve 21 and opening the solenoid valves 22 and 23. Since the refrigerant rich in low boiling point components stored in the refrigerant reservoir 14 from the third pipe 27 can be returned to the refrigeration cycle using the pressure difference between the pressure in the circuit and the suction pressure of the compressor 1, the circulation composition Can be quickly returned to the standard composition (or the low-boiling components are increased).
[0034]
Further, the following may be used.
As shown in FIG. 6, the solenoid valve 24 and the fifth decompression are the fourth on-off valve between the outlet side of the refrigerant reservoir 14 and the inlet side of the heat source side heat exchanger 5 that is the low-pressure side heat exchanger of the refrigeration cycle. When the refrigeration cycle circulation composition is to be returned to the standard composition (or the low boiling point component is increased) from the composition having a high boiling point component by connecting with the fourth pipe 28 via the capillary 34 which is a device, By closing the solenoid valve 21 and opening the solenoid valve 22 and the solenoid valve 24, the pressure difference between the pressure in the composition separation circuit and the suction pressure of the compressor 1 is utilized to be stored in the refrigerant reservoir 14 from the fourth pipe 28. In addition, the refrigerant rich in low-boiling components can be returned to the refrigeration cycle, and the circulating composition can be quickly returned to the standard composition (or the low-boiling components are increased). Moreover, since the liquid refrigerant in the refrigerant reservoir 14 evaporates in the heat source side heat exchanger 5, the liquid return of the compressor 1 can be prevented. However, the electromagnetic valve 22 may be closed.
As shown in FIG. 5 and FIG. 6, the low boiling point component is quickly increased in the refrigeration cycle by connecting the outlet side of the refrigerant reservoir 14 and the low pressure side of the refrigeration cycle through an on-off valve and a pressure reducing device. be able to.
[0035]
Further, the following may be used.
As shown in FIG. 7, the outlet side of the first cooler 13 and the outlet side of the use side heat exchanger 3 that is a heat exchanger on the high pressure side of the refrigeration cycle are connected via an electromagnetic valve 37 that is a fifth on-off valve. When the refrigeration cycle circulation composition is to be returned to the standard composition from the state where there are many high-boiling components (or when the low-boiling components are increased), the solenoid valve 21 is closed, 22. Using the pressure difference between the discharge pressure of the compressor 1 and the suction pressure of the compressor 1 by opening the electromagnetic valve 37, that is, applying a high pressure from the upper part of the refrigerant reservoir 14 by the discharge pressure of the compressor 1. Since the refrigerant is poured from the lower part and the refrigerant rich in low-boiling components stored in the refrigerant reservoir 14 can be returned to the refrigeration cycle, the circulating composition can be quickly returned to the standard composition (or the low-boiling components are increased). it can.
[0036]
In the present embodiment, the refrigerant cooled by the first cooler 13 and the second cooler 12 uses the refrigerant depressurized by the third decompressor 32, and flows in the order of the second cooler 12 and the first cooler 13. However, the coolers 12 and 13 may be cooled by using a low-pressure refrigerant sucked into the compressor 1.
[0037]
Further, according to the refrigeration cycle apparatus of the first embodiment, the first temperature detection means T2 is provided on the inlet side of the third decompression device 32, and the first pressure detection means P1 and the second temperature detection means T1 are provided on the outlet side. Since it has a composition calculation means for calculating the refrigerant composition of the refrigeration cycle using the pressure detected by the first pressure detection means P1, the respective temperatures detected by the first temperature detection means T2 and the second temperature detection means T1, The refrigerant circulation composition of the refrigeration cycle can be detected, and the desired refrigerant composition can be changed based on the detected refrigerant composition.
[0038]
Embodiment 2. FIG.
Hereinafter, the refrigeration cycle apparatus of Embodiment 2 of the present invention will be described.
FIG. 8 is a block diagram showing a refrigeration cycle apparatus according to the present embodiment. In this embodiment, the refrigerant flow path is switched between the compressor 1, the use side heat exchanger 3, and the heat source side heat exchanger 5. A four-way valve 2 as a means is provided, and the flow path can be switched to one of the heat exchangers 3 and 5. Other configurations are the same as those of the first embodiment.
Therefore, by switching the four-way valve 2, a hot water supply operation (hot water supply operation) and a chiller operation (cold water supply operation) can be performed, and the heat source side heat exchanger 5 operates as an evaporator during the hot water supply operation (hot water supply operation). During chiller operation (cold water supply operation), it operates as a condenser. Further, the use side heat exchanger 3 operates as a condenser during the hot water supply operation, and operates as an evaporator during the chiller operation.
[0039]
First, the case of hot water supply (hot water supply) operation will be described. The flow of the refrigerant in the refrigeration cycle is shown by solid line arrows in FIG. In the hot water supply operation, the four-way valve 2 is connected as shown by a solid line, the outlet side of the compressor 1 and the inlet part of the use side heat exchanger 3 are connected, and the inlet part of the accumulator 6 and the heat source side heat exchanger 5. Are respectively connected to the outlets.
The high-temperature and high-pressure vapor refrigerant discharged from the compressor 1 is condensed and liquefied by the use-side heat exchanger 3 that operates as a condenser via the four-way valve 2 to become a medium-temperature and high-pressure liquid refrigerant, and is decompressed by the expansion valve 4. It becomes a low-pressure gas-liquid two-phase refrigerant and flows into the heat source side heat exchanger 5 operating as an evaporator.
This refrigerant evaporates in the heat source side heat exchanger 5 and returns to the compressor 1 again through the four-way valve 2 and the accumulator 6. At this time, the cold water that is the medium to be heated flowing into the use side heat exchanger 3 is heated by the latent heat of condensation of the refrigerant to become hot water, and is supplied to a hot water storage tank or the like. In addition, air that is a medium to be cooled flowing into the heat source side heat exchanger 5 is cooled by the latent heat of vaporization of the refrigerant, and then released to the outside air.
Note that the operation for changing the circulation composition in the refrigeration cycle during the hot water supply operation is the same as that in the reference example described above, and is therefore omitted.
[0040]
In addition, when the four-way valve 2 is provided, when the surface of the heat source side heat exchanger 5 is frosted at a low outside air temperature, the four-way valve 2 is connected as shown by a dotted line, and a high-temperature refrigerant is caused to flow to the heat source side heat exchanger 5. The defrosting operation that melts the attached frost becomes possible.
[0041]
Moreover, the operation | movement which tries to return a refrigerating-cycle circulation composition to a standard composition from a composition with many high boiling components (or increase a low boiling component) is also the same.
That is, as shown in FIG. 9, the outlet side of the refrigerant reservoir 14 and the second pipe 26 are connected by the third pipe 27 via the electromagnetic valve 23 that is the third on-off valve and the capillary tube 33 that is the fourth pressure reducing device. Thus, when returning the refrigeration cycle circulation composition from the composition having a high boiling point component to the standard composition (or increasing the low boiling point component), the solenoid valve 21 is closed and the solenoid valve 22 and the solenoid valve 23 are opened. Thus, the refrigerant rich in low boiling point components stored in the refrigerant reservoir 14 from the third pipe 27 can be returned to the refrigeration cycle by utilizing the pressure difference between the pressure in the composition separation circuit and the suction pressure of the compressor 1. Therefore, the circulating composition can be quickly returned to the standard composition (or the low-boiling components are increased).
[0042]
Similarly, as shown in FIG. 10, an electromagnetic valve that is a fourth on-off valve is provided on the outlet side of the refrigerant reservoir 14 and the inlet side of the heat source side heat exchanger 5 that is a low-pressure side heat exchanger of the refrigeration cycle. When the refrigeration cycle circulation composition is to be returned to the standard composition (or the low boiling point component is increased) by connecting the refrigeration cycle circulation composition to the standard composition by connecting with the fourth pipe 28 via the capillary 24 which is 24 and the fifth decompression device. 21 is closed, and the solenoid valve 22 and the solenoid valve 24 are opened, and the pressure difference between the pressure in the composition separation circuit and the suction pressure of the compressor 1 is utilized to be stored in the refrigerant reservoir 14 from the fourth pipe 28. The refrigerant rich in low-boiling components can be returned to the refrigeration cycle, and the circulating composition can be quickly returned to the standard composition (or the low-boiling components are increased). Moreover, since the liquid refrigerant in the refrigerant reservoir 14 evaporates in the heat source side heat exchanger 5, the liquid return of the compressor 1 can be prevented. However, the electromagnetic valve 22 may be closed.
As described above, in order to increase the low boiling point component in the refrigeration cycle, as shown in FIGS. 9 and 10, the outlet side of the refrigerant reservoir 14 and the low pressure side of the refrigeration cycle are connected via an on-off valve and a pressure reducing device. What is necessary is just piping connection.
[0043]
Similarly, as shown in FIG. 11, the outlet side of the first cooler 13 and the outlet side of the use side heat exchanger 3 which is a high pressure side heat exchanger of the refrigeration cycle are electromagnetic valves which are fifth open / close valves. When the refrigeration cycle circulation composition is to be returned to the standard composition (or the low boiling point component is increased) by connecting with the fifth pipe 29 via 37, the solenoid valve 21 is closed, the solenoid valve 22, By opening the valve 37, the refrigerant rich in low boiling point components stored in the refrigerant reservoir 14 can be returned to the main refrigeration cycle using the pressure difference between the discharge pressure of the compressor 1 and the suction pressure of the compressor 1. Therefore, the circulating composition can be quickly returned to the standard composition (or the low-boiling components are increased).
[0044]
Next, the operation at the time of chiller (cold water supply) operation will be described. In the case of chiller operation, the four-way valve 2 is connected as indicated by a dotted line, and the outlet side of the compressor 1 and the heat source side heat exchanger 5 are connected to the inlet portion of the accumulator 6 and the use side heat exchanger 3, respectively. In FIG. 8, the flow of the refrigerant in the refrigeration cycle is indicated by dotted arrows.
During the chiller operation, the high-temperature and high-pressure vapor refrigerant compressed by the compressor 1 is condensed and liquefied by the heat source side heat exchanger 5 that operates as a condenser through the four-way valve 2, is decompressed by the expansion valve 4, and is low-pressure gas-liquid. It becomes a two-phase refrigerant and flows into the use side heat exchanger 3 that operates as an evaporator. This refrigerant evaporates in the use side heat exchanger 3 and returns to the compressor 1 again through the four-way valve 2 and the accumulator 6. The opening degree of the expansion valve 4 is controlled so that the refrigerant supercooling degree at the outlet of the heat source side heat exchanger 5 is appropriate (for example, 10 ° C.), and excess refrigerant in the refrigeration cycle is stored in the accumulator 6. Stored.
Note that the operation of changing the circulation composition in the refrigeration cycle during the chiller operation is the same as that during the hot water supply operation described above, and is therefore omitted.
[0045]
Further, in the case of the chiller operation, similarly to the hot water supply operation, as shown in FIG. 9, the outlet side of the refrigerant reservoir 14 and the second pipe 26 are the electromagnetic valve 23 and the fourth pressure reducing device which are the third on-off valves. By connecting with the third pipe 27 via the capillary tube 33, when the refrigeration cycle circulation composition is to be returned from the composition having a high boiling point component to the standard composition (or increasing the low boiling point component), the solenoid valve 21 Is closed and the solenoid valves 22 and 23 are opened, so that the low boiling point component stored in the refrigerant reservoir 14 from the third pipe 27 is obtained using the pressure difference between the pressure in the composition separation circuit and the suction pressure of the compressor 1. Since the rich refrigerant can be returned to the refrigeration cycle, the circulation composition can be quickly returned to the standard composition (or the low-boiling components are increased).
[0046]
Although not shown, in FIG. 10, the fourth pipe 28 is connected to the refrigeration cycle side by branch pipes with on-off valves (or branch pipes with flow path switching valves), respectively, for hot water supply operation and chiller operation. Even if it is connected to a heat exchanger on the low pressure side corresponding to the refrigerant, the refrigerant rich in the low boiling point components stored in the refrigerant reservoir 14 can be returned to the refrigeration cycle, so that the circulation composition can be quickly brought to the standard composition. It is possible to return (or increase the low boiling point component).
[0047]
As described above, in order to increase the low boiling point component in the refrigeration cycle, the outlet side of the refrigerant reservoir 14 and the low pressure side of the refrigeration cycle may be connected to each other via an on-off valve and a pressure reducing device.
[0048]
Although not shown, in FIG. 11, the fifth pipe 29 is connected to the refrigeration cycle side by a branch pipe with an on-off valve (or a branch pipe with a flow path switching valve), respectively, for hot water supply operation and chiller operation. The refrigerant rich in the low-boiling components stored in the refrigerant reservoir 14 can be returned to the refrigeration cycle even if it is connected to the outlet side of the heat exchanger on the high-pressure side correspondingly. It becomes possible to return to the standard composition (or increase the low boiling point component).
[0049]
Also in the present embodiment, in order to increase the low boiling point component of the refrigeration cycle, the low boiling point component of the refrigeration cycle is increased earlier by the above method than when the electromagnetic valve 21 is closed and the electromagnetic valve 22 is opened. be able to.
Note that the four-way valve 2 which is the refrigerant flow path switching means described in the present embodiment is installed in FIG. 4 of the first embodiment, and performs a chiller operation (cold water supply operation) in addition to the hot water supply operation. You can also.
[0050]
In addition, the structure which increases the low boiling-point component of a refrigerant | coolant to the refrigerating cycle of Embodiment 1, 2, ie, the structure which connected the outlet side of the refrigerant | coolant storage device 14, and the low voltage | pressure side of the refrigerating cycle through the on-off valve and the pressure reduction device And the effect of increasing the low boiling point component of the refrigerant in the refrigeration cycle quickly by the configuration in which the outlet side of the first cooler 13 and the outlet side of the heat exchanger on the high pressure side of the refrigeration cycle are connected via an on-off valve, etc. Even without the second cooler 12, the same can be obtained.
[0051]
According to the refrigeration cycle apparatus of the first and second embodiments, the low-pressure side of the refrigeration cycle connected to the outlet side of the refrigerant reservoir 14 via the on-off valve 24 and the decompression device 34 is connected to the use-side heat exchanger 3 and Since the heat source side heat exchanger 5 is on the inlet side of the heat exchanger on the low pressure side, when the on-off valve 24 is opened and the low boiling point component refrigerant flows into the refrigeration cycle, the refrigerant composition of the refrigeration cycle The low boiling point component can be increased quickly, and the liquid can be evaporated by the heat exchanger and liquid return to the compressor 1 can be prevented.
[0052]
Moreover, according to the refrigeration cycle apparatus of the first and second embodiments, the refrigeration cycle, the refrigerant rectifier 11, the first cooler 13, the refrigerant reservoir 14, and the third decompression device 32 are provided. In the refrigeration cycle apparatus that changes the refrigerant composition by opening and closing the first on-off valve 25 and the second on-off valve 26, the outlet side of the refrigerant reservoir 14 and the low-pressure side of the refrigeration cycle are connected by piping through the on-off valve and the decompression device. Or, the outlet side of the first cooler 13 and the outlet side of the heat exchanger on the high pressure side of the refrigeration cycle are connected by piping through an on-off valve, and the refrigerant rectifier 11 side of the third decompression device 32 is Since the second cooler 12 for supercooling the refrigerant exiting from the refrigerant rectifier 11 is provided, the low boiling point component of the refrigerant in the refrigeration cycle can be increased quickly, and the inlet of the third decompression device becomes a liquid single phase, and the refrigerant rectifier 11 and the flow rate of the refrigerant around the refrigerant rectifier 11 is stable. Stably circulating composition becomes changeable.
[0053]
In addition, according to the refrigeration cycle devices of the first and second embodiments, the second cooler 12 cools by the heat exchange with the refrigerant after passing through the third decompression device 32. The three decompression devices 32 can be provided close to each other, and the piping can be easily installed.
[0054]
Further, according to the refrigeration cycle devices of the first and second embodiments, the first cooler 13 cools the third pressure reducing device 32 by heat exchange with the refrigerant after passing through, so the first cooler 13 and the first cooler 13 The three decompression devices 32 can be provided close to each other, and the piping can be easily installed.
[0055]
Embodiment 3 FIG.
Hereinafter, a refrigeration cycle apparatus according to Embodiment 3 of the present invention will be described.
FIG. 12 is a block diagram showing a refrigeration cycle apparatus according to the present embodiment, which is substantially the same as that of the second embodiment, and a detailed description thereof will be omitted. In the present embodiment, the third cooler 15 is provided in front of the capillary tube 31 that is the second decompression device in FIG. 8 of the second embodiment, that is, on the compressor 1 side.
[0056]
The refrigerant depressurized by the third depressurizing device 32 flows into the third cooler 15 after flowing in the order of the second cooler 12 and the first cooler 13. This inflowing refrigerant cools the high-temperature and high-pressure vapor refrigerant that has flowed out of the outlet of the compressor 1. That is, the high-temperature and high-pressure vapor refrigerant flowing out from the outlet of the compressor 1 is cooled by the third cooler 15 to be in a liquid single-phase state, depressurized by the capillary tube 33, and the refrigerant rectifier 11 has a low dryness. The refrigerant will flow in. Thus, when the gas-liquid two-phase refrigerant having a low dryness flows into the refrigerant rectifier 11, the lower outlet state of the refrigerant rectifier 11 becomes a liquid single phase, and the lower outlet side of the refrigerant rectifier 11. Alternatively, the pulsation at the inlet of the capillary tube 32 can be suppressed and the flow rate in the composition separation circuit can be stabilized.
[0057]
Note that the low-pressure refrigerant sucked into the compressor 1 may be used as the refrigerant that exchanges heat with the third cooler 15 and cools the high-temperature high-pressure vapor refrigerant that has flowed out of the compressor 1.
Moreover, the structure which provides the 3rd cooler 15 of this Embodiment is applicable also to Embodiment 1, and the same effect is acquired.
Also in the present embodiment, a configuration in which the low-boiling component of the refrigerant is increased in the refrigeration cycle, that is, a configuration in which the outlet side of the refrigerant reservoir 14 and the low-pressure side of the refrigeration cycle are connected by piping via an on-off valve and a decompression device. The same effect as described in the first and second embodiments can be obtained by the configuration in which the outlet side of the first cooler 13 and the outlet side of the heat exchanger on the high pressure side of the refrigeration cycle are connected by piping through an on-off valve. It is done.
[0058]
In the second and third embodiments, the refrigeration cycle apparatus has been described as an example of a hot water supply apparatus (hot water hot water supply, cold water hot water supply), but the present refrigeration cycle apparatus can also be used as an air conditioner or a refrigeration apparatus. That is, the hot water hot water supply corresponds to the heating operation of the air conditioner, and the cold water hot water supply corresponds to the cooling operation or the refrigeration device of the air conditioner. In addition, similar effects can be obtained respectively.
In that case, in the air conditioner, it is desirable that the use side heat exchanger 3 of the refrigeration cycle is an indoor unit, and the other components of the refrigeration cycle and the composition separation unit 63 are outdoor units. In the refrigeration apparatus, it is desirable that the use case heat exchanger 3 of the refrigeration cycle constitutes a showcase, and the other components of the refrigeration cycle and the composition separation unit 63 are outdoor units.
[0059]
Further, according to the refrigeration cycle apparatus of the third embodiment, the first provided on the inlet side of the refrigerant rectifier 11 of the pipe connecting the lower part of the refrigerant rectifier 11 and the outlet side of the compressor 1 of the refrigeration cycle. Since the third cooler 15 is provided on the compressor 1 side of the second decompression device 31, the high-temperature high-pressure gas refrigerant discharged from the compressor 1 is cooled by the third cooler 15 to become a liquid single phase, and the second decompression device 31. And the refrigerant rectifier 11 flows into the refrigerant rectifier 11 as a gas-liquid two phase with a low dryness. Therefore, a liquid single phase is formed at the lower outlet of the refrigerant rectifier 11, pulsation on the outlet side of the refrigerant rectifier 11 is suppressed, and the refrigerant flow is stabilized.
[0060]
Further, according to the refrigeration cycle apparatus of the third embodiment, the cooling of the respective refrigerants by the first cooler 13, the second cooler 12, and the third cooler 15 is the refrigerant that has been decompressed by the third decompressor 32. Is performed by exchanging heat with the respective refrigerants in the order of the second cooler, the first cooler, and the third cooler, so that the first cooler 13, the second cooler 12, the third cooler 15, and The third decompression device 32 can be installed relatively close, and these can be integrated into a unit, making installation and handling easy.
[0061]
According to the refrigeration cycle apparatuses of the second and third embodiments, the refrigerant flow path switching means for switching the refrigerant flow path to the use side heat exchanger 3 or the heat source side heat exchanger 5 on the outlet side of the compressor 1 of the refrigeration cycle. 2 is provided, the refrigeration cycle device can be used as a hot water supply device capable of supplying hot and cold water and an air conditioner capable of heating and cooling by switching the refrigerant flow switching means 2.
[0062]
【The invention's effect】
As described above, the refrigeration cycle apparatus of the present invention includes a refrigeration cycle, a refrigerant rectifier, a first cooler that cools a low-boiling-point refrigerant component separated by the refrigerant rectifier, and a refrigerant reservoir. In the refrigeration cycle apparatus in which the ratio of the low-boiling refrigerant component and the high-boiling refrigerant component of the non-azeotropic refrigerant mixture in the refrigeration cycle is variable by opening and closing the first on-off valve and the second on-off valve, A second pressure reducing device is provided on the inlet side of the refrigerant rectifier of the pipe connecting the lower part of the refrigeration unit and the outlet side of the compressor of the refrigeration cycle, and the pipe connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle A third pressure reducing device is provided, a second cooler for supercooling the refrigerant coming out of the refrigerant rectifier is provided on the refrigerant rectifier side of the third pressure reducing device, and a second cooler is provided on the compressor side of the second pressure reducing device. 3 coolers are provided, and the first cooler, the second cooler, and the third cooler respectively. Cooling of the refrigerant, refrigerant decompressed by the third decompressor, a second cooler, the first cooler, the order of the third cooler are those carried out by each of the refrigerant heat exchanger.
Therefore, since the inlet of the third decompression device is always in a liquid single phase, the refrigerant flow rate in the refrigerant rectifier and the piping around the refrigerant rectifier is stabilized, the circulation composition can be changed stably, and non-azeotropic mixing The performance of the refrigeration cycle apparatus using the refrigerant is improved.
[0063]
In addition, the refrigeration cycle apparatus of the present invention includes a refrigeration cycle, a refrigerant rectifier, a first cooler, and a refrigerant reservoir, and opens and closes a first on-off valve and a second on-off valve, thereby refrigeration. In a refrigeration cycle apparatus in which the ratio of the low-boiling refrigerant component and the high-boiling refrigerant component of the non-azeotropic refrigerant mixture in the cycle is variable, the pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle A second decompression device is provided on the inlet side of the refrigerant rectifier, and a third decompression device is installed in a pipe connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle, and the outlet side of the refrigerant reservoir The low pressure side of the refrigeration cycle is connected to the low pressure side via an on-off valve and a pressure reducing device, a second cooler is provided on the refrigerant rectifier side of the third pressure reducing device, and a third cooling is provided on the compressor side of the second pressure reducing device. Each of the refrigerants by the first cooler, the second cooler and the third cooler Cooling refrigerant decompressed by the third decompressor, a second cooler, the first cooler, the order of the third cooler are those carried out by each of the refrigerant heat exchanger.
Therefore, when the refrigerant circulation composition of the refrigeration cycle is changed so that the low boiling point component increases, the open / close valve of the pipe connecting the outlet side of the refrigerant reservoir and the low pressure side of the refrigeration cycle is opened to quickly The low boiling point component of the refrigerant can be increased, and the performance of the refrigeration cycle apparatus using the non-azeotropic refrigerant mixture is improved.
[0064]
Further, the refrigeration cycle apparatus of the present invention includes a refrigeration cycle, a refrigerant rectifier, a first cooler, and a refrigerant reservoir, and opens and closes a first on-off valve and a second on-off valve so that the inside of the refrigeration cycle is provided. In the refrigeration cycle apparatus in which the ratio of the low-boiling refrigerant component and the high-boiling refrigerant component of the non-azeotropic refrigerant mixture is variable, the refrigerant concentration of the pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle is A second pressure reducing device is provided on the inlet side of the still, and a third pressure reducing device is installed on a pipe connecting the lower portion of the refrigerant rectifier and the low pressure side of the refrigeration cycle, and the outlet side of the first cooler is connected to the refrigeration unit. The outlet side of the heat exchanger on the high-pressure side of the cycle is connected via an on-off valve, a second cooler is provided on the refrigerant rectifier side of the third decompression device, and the compressor side of the second decompression device is provided. A third cooler is provided, and the respective coolers by the first cooler, the second cooler, and the third cooler are provided. Cooling the refrigerant decompressed by the third decompressor, a second cooler, the first cooler, the order of the third cooler are those carried out by each of the refrigerant heat exchanger.
Therefore, when changing the refrigerant circulation composition of the refrigeration cycle so that the low boiling point component increases, the fifth on-off valve is opened on the outlet side of the first cooler and the outlet side of the use side heat exchanger of the refrigeration cycle. The low-boiling point component of the refrigerant in the refrigeration cycle can be increased quickly, and the performance of the refrigeration cycle apparatus using a non-azeotropic refrigerant mixture is improved.
[Brief description of the drawings]
FIG. 1 is a diagram showing a refrigerant circuit configuration of a refrigeration cycle apparatus in a reference example.
FIG. 2 is a graph showing the relationship between the composition of low boiling point components and high pressure in a reference example.
FIG. 3 is a graph showing the relationship between the composition change operation time and the composition of low boiling point components in a reference example.
FIG. 4 is a diagram illustrating a refrigerant composition detection method of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
FIG. 5 is a diagram illustrating a method for increasing the low boiling point component of the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
FIG. 6 is a diagram for explaining another method for increasing the low boiling point component of the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
FIG. 7 is a diagram illustrating still another method for increasing the low boiling point component of the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
FIG. 8 is a diagram showing a refrigerant circuit configuration of a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
FIG. 9 is a diagram illustrating a method for increasing the low boiling point component of the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
FIG. 10 is a diagram illustrating another method for increasing the low boiling point component of the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
FIG. 11 is a diagram illustrating still another method for increasing the low boiling point component of the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
FIG. 12 is a diagram showing a refrigerant circuit configuration of a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Compressor, 2 Refrigerant flow path switching means, 3 Use side heat exchanger, 4 1st decompression device, 5 Heat source side heat exchanger, 11 Refrigerating fractionator, 12 2nd cooler, 13 1st cooler, 14 Refrigerant reservoir, 15 3rd cooler, 21 1st on-off valve, 22 2nd on-off valve, 31 2nd decompression device, 32 3rd decompression device.

Claims (8)

圧縮機、利用側熱交換器、第１減圧装置、熱源側熱交換器を順次配管で接続してなる冷凍サイクルと、
非共沸混合冷媒を低沸点冷媒成分と高沸点冷媒成分とに分離する冷媒精留器と、
前記冷媒精留器で分離された低沸点冷媒成分を冷却する第１冷却器と、
前記第１冷却器で冷却された冷媒を貯留する冷媒貯留器とを備え、
前記冷媒精留器の下部と前記冷凍サイクルの前記圧縮機の出口側とを接続する配管に設置した第１開閉弁と、前記冷媒精留器の下部と前記冷凍サイクルの低圧側とを接続する配管に設置した第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、
前記冷媒精留器の下部と前記冷凍サイクルの前記圧縮機の出口側とを接続する配管の前記冷媒精留器の入口側に第２減圧装置を設け、
前記冷媒精留器の下部と前記冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、該第３減圧装置の前記冷媒精留器側に、前記冷媒精留器から出る冷媒を過冷却する第２冷却器を設け、
前記第２減圧装置の前記圧縮機側に第３冷却器を設け、
前記第１冷却器、前記第２冷却器及び前記第３冷却器によるそれぞれの冷媒の冷却は、前記第３減圧装置で減圧された冷媒が、前記第２冷却器、前記第１冷却器、前記第３冷却器の順に、それぞれの冷媒と熱交換することにより行われることを特徴とする冷凍サイクル装置。A refrigeration cycle in which a compressor, a use side heat exchanger, a first pressure reducing device, and a heat source side heat exchanger are sequentially connected by piping;
A refrigerant rectifier that separates a non-azeotropic refrigerant mixture into a low-boiling refrigerant component and a high-boiling refrigerant component;
A first cooler for cooling the low boiling point refrigerant component separated by the refrigerant rectifier;
A refrigerant reservoir that stores the refrigerant cooled by the first cooler,
A first on-off valve installed in a pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle, and connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle In the refrigeration cycle apparatus that varies the ratio of the low boiling point refrigerant component and the high boiling point refrigerant component of the non-azeotropic refrigerant mixture in the refrigeration cycle by opening and closing the second on-off valve installed in the pipe,
A second decompression device is provided on the inlet side of the refrigerant rectifier of a pipe connecting the lower portion of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle;
A third decompression device is installed in a pipe connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle, and the refrigerant exiting from the refrigerant rectifier is disposed on the refrigerant rectifier side of the third decompression device. Providing a second cooler for supercooling
A third cooler is provided on the compressor side of the second pressure reducing device;
The cooling of each refrigerant by the first cooler, the second cooler, and the third cooler is performed by using the second cooler, the first cooler, The refrigeration cycle apparatus is performed by exchanging heat with each refrigerant in the order of the third cooler. 圧縮機、利用側熱交換器、第１減圧装置、熱源側熱交換器を順次配管で接続してなる冷凍サイクルと、
非共沸混合冷媒を低沸点冷媒成分と高沸点冷媒成分とに分離する冷媒精留器と、
前記冷媒精留器で分離された低沸点冷媒成分を冷却する第１冷却器と、
前記第１冷却器で冷却された冷媒を貯留する冷媒貯留器とを備え、
前記冷媒精留器の下部と前記冷凍サイクルの前記圧縮機の出口側とを接続する配管に設置した第１開閉弁と、前記冷媒精留器の下部と前記冷凍サイクルの低圧側とを接続する配管に設置した第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、
前記冷媒精留器の下部と前記冷凍サイクルの前記圧縮機の出口側とを接続する配管の前記冷媒精留器の入口側に第２減圧装置を設け、
また、前記冷媒精留器の下部と前記冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、
前記冷媒貯留器の出口側と前記冷凍サイクルの低圧側とを開閉弁及び減圧装置を介して配管接続し、
前記第３減圧装置の前記冷媒精留器側に、第２冷却器を設け、
前記第２減圧装置の前記圧縮機側に第３冷却器を設け、
前記第１冷却器、前記第２冷却器及び前記第３冷却器によるそれぞれの冷媒の冷却は、前記第３減圧装置で減圧された冷媒が、前記第２冷却器、前記第１冷却器、前記第３冷却器の順に、それぞれの冷媒と熱交換することにより行われることを特徴とする冷凍サイクル装置。A refrigeration cycle in which a compressor, a use side heat exchanger, a first pressure reducing device, and a heat source side heat exchanger are sequentially connected by piping;
A refrigerant rectifier that separates a non-azeotropic refrigerant mixture into a low-boiling refrigerant component and a high-boiling refrigerant component;
A first cooler for cooling the low boiling point refrigerant component separated by the refrigerant rectifier;
A refrigerant reservoir that stores the refrigerant cooled by the first cooler,
A first on-off valve installed in a pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle, and connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle In the refrigeration cycle apparatus that varies the ratio of the low boiling point refrigerant component and the high boiling point refrigerant component of the non-azeotropic refrigerant mixture in the refrigeration cycle by opening and closing the second on-off valve installed in the pipe,
A second decompression device is provided on the inlet side of the refrigerant rectifier of a pipe connecting the lower portion of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle;
In addition, a third decompression device is installed in a pipe connecting the lower portion of the refrigerant rectifier and the low pressure side of the refrigeration cycle,
Pipe connection between the outlet side of the refrigerant reservoir and the low pressure side of the refrigeration cycle through an on-off valve and a pressure reducing device,
A second cooler is provided on the refrigerant rectifier side of the third decompression device,
A third cooler is provided on the compressor side of the second pressure reducing device;
The cooling of each refrigerant by the first cooler, the second cooler, and the third cooler is performed by using the second cooler, the first cooler, The refrigeration cycle apparatus is performed by exchanging heat with each refrigerant in the order of the third cooler. 前記冷媒貯留器の出口側と配管接続した前記冷凍サイクルの低圧側が、前記利用側熱交換器及び前記熱源側熱交換器のうち、低圧側となる熱交換器の入口側であることを特徴とする請求項２記載の冷凍サイクル装置。  The low-pressure side of the refrigeration cycle piped to the outlet side of the refrigerant reservoir is an inlet side of a heat exchanger that is a low-pressure side among the use side heat exchanger and the heat source side heat exchanger. The refrigeration cycle apparatus according to claim 2. 圧縮機、利用側熱交換器、第１減圧装置、熱源側熱交換器を順次配管で接続してなる冷凍サイクルと、
非共沸混合冷媒を低沸点冷媒成分と高沸点冷媒成分とに分離する冷媒精留器と、
前記冷媒精留器で分離された低沸点冷媒成分を冷却する第１冷却器と、
前記第１冷却器で冷却された冷媒を貯留する冷媒貯留器とを備え、
前記冷媒精留器の下部と前記冷凍サイクルの前記圧縮機の出口側とを接続する配管に設置した第１開閉弁と、前記冷媒精留器の下部と前記冷凍サイクルの低圧側とを接続する配管に設置した第２開閉弁とを開閉することにより、冷凍サイクル内の非共沸混合冷媒の低沸点冷媒成分と高沸点冷媒成分の割合を可変とする冷凍サイクル装置において、
前記冷媒精留器の下部と前記冷凍サイクルの前記圧縮機の出口側とを接続する配管の前記冷媒精留器の入口側に第２減圧装置を設け、
また、前記冷媒精留器の下部と前記冷凍サイクルの低圧側とを接続する配管に第３減圧装置を設置し、
前記第１冷却器の出口側と前記冷凍サイクルの前記利用側熱交換器及び前記熱源側熱交換器のうち、高圧側となる熱交換器の出口側とを開閉弁を介して配管接続し、
前記第３減圧装置の前記冷媒精留器側に、第２冷却器を設け、
前記第２減圧装置の前記圧縮機側に第３冷却器を設け、
前記第１冷却器、前記第２冷却器及び前記第３冷却器によるそれぞれの冷媒の冷却は、前記第３減圧装置で減圧された冷媒が、前記第２冷却器、前記第１冷却器、前記第３冷却器の順に、それぞれの冷媒と熱交換することにより行われることを特徴とする冷凍サイクル装置。A refrigeration cycle in which a compressor, a use side heat exchanger, a first pressure reducing device, and a heat source side heat exchanger are sequentially connected by piping;
A refrigerant rectifier that separates a non-azeotropic refrigerant mixture into a low-boiling refrigerant component and a high-boiling refrigerant component;
A first cooler for cooling the low boiling point refrigerant component separated by the refrigerant rectifier;
A refrigerant reservoir that stores the refrigerant cooled by the first cooler,
A first on-off valve installed in a pipe connecting the lower part of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle, and connecting the lower part of the refrigerant rectifier and the low pressure side of the refrigeration cycle In the refrigeration cycle apparatus that varies the ratio of the low boiling point refrigerant component and the high boiling point refrigerant component of the non-azeotropic refrigerant mixture in the refrigeration cycle by opening and closing the second on-off valve installed in the pipe,
A second decompression device is provided on the inlet side of the refrigerant rectifier of a pipe connecting the lower portion of the refrigerant rectifier and the outlet side of the compressor of the refrigeration cycle;
In addition, a third decompression device is installed in a pipe connecting the lower portion of the refrigerant rectifier and the low pressure side of the refrigeration cycle,
Of the outlet side of the first cooler and the use side heat exchanger and the heat source side heat exchanger of the refrigeration cycle, the outlet side of the heat exchanger that is the high pressure side is connected by piping via an on-off valve,
A second cooler is provided on the refrigerant rectifier side of the third decompression device,
A third cooler is provided on the compressor side of the second pressure reducing device;
The cooling of each refrigerant by the first cooler, the second cooler, and the third cooler is performed by using the second cooler, the first cooler, The refrigeration cycle apparatus is performed by exchanging heat with each refrigerant in the order of the third cooler. 前記第２冷却器は、前記冷媒精留器から出る冷媒を過冷却することを特徴とする請求項２から請求項４のいずれかに記載の冷凍サイクル装置。  The refrigeration cycle apparatus according to any one of claims 2 to 4, wherein the second cooler supercools the refrigerant coming out of the refrigerant rectifier. 前記第２冷却器は、前記第３減圧装置を通過後の冷媒との熱交換で冷却することを特徴とする請求項１又は請求項５に記載の冷凍サイクル装置。  The refrigeration cycle apparatus according to claim 1 or 5, wherein the second cooler cools by heat exchange with the refrigerant after passing through the third decompression device. 前記第３減圧装置の入口側に第１温度検出手段を、出口側に第１圧力検出手段と第２温度検出手段を設け、第１圧力検出手段により検出した圧力、第１温度検出手段および第２温度検出手段により検出したそれぞれの温度を用いて前記冷凍サイクルの冷媒組成を演算する組成演算手段を備えたことを特徴とする請求項１から請求項６のいずれかの請求項に記載の冷凍サイクル装置。  The first pressure detecting means is provided on the inlet side of the third pressure reducing device, the first pressure detecting means and the second temperature detecting means are provided on the outlet side, the pressure detected by the first pressure detecting means, the first temperature detecting means, and the first temperature detecting means The refrigeration according to any one of claims 1 to 6, further comprising a composition calculating means for calculating the refrigerant composition of the refrigeration cycle using each temperature detected by the two temperature detecting means. Cycle equipment. 前記冷凍サイクルの前記圧縮機の出口側に、前記利用側熱交換器または前記熱源側熱交換器に冷媒流路を切換える冷媒流路切換手段を設けたことを特徴とする請求項１から請求項７のいずれかの請求項に記載の冷凍サイクル装置。  The refrigerant flow path switching means for switching a refrigerant flow path to the use side heat exchanger or the heat source side heat exchanger is provided on the outlet side of the compressor of the refrigeration cycle. The refrigeration cycle apparatus according to claim 7.
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