JP3614626B2 - Air conditioner and method of operating air conditioner - Google Patents

Air conditioner and method of operating air conditioner Download PDF

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Publication number
JP3614626B2
JP3614626B2 JP30508897A JP30508897A JP3614626B2 JP 3614626 B2 JP3614626 B2 JP 3614626B2 JP 30508897 A JP30508897 A JP 30508897A JP 30508897 A JP30508897 A JP 30508897A JP 3614626 B2 JP3614626 B2 JP 3614626B2
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refrigerant
heat exchanger
heat
load
source side
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JPH11142018A (en
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広有 柴
等 飯島
誠司 井上
文雄 松岡
利彰 吉川
邦弘 乾
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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】
この発明は、空気調和装置に関するものである。
【０００２】
【従来の技術】
図２１は、例えば特許平７−３１８１８６号公報に示された各冷媒回路間に共通の熱交換器を備えて熱移動を行う従来の空気調和装置の装置図である。
【０００３】
図２１に基づいて、回路構成を説明する。空調ユニット１、２は室外機１と室内機６ａ，６ｂ，６ｃを環状に接続してなる冷凍サイクルＡ及びＢを構成し、熱交換器回路Ｃは、冷媒熱交換器用膨張弁ＥＶ１と空調ユニット１、２それぞれに共通する冷媒熱交換器ＨＥを備えており、蓄熱回路Ｄは蓄熱漕用膨張弁ＥＶ２と空調ユニット１、２それぞれに共通する蓄熱漕ＳＴＲを備え、室内側熱交換器８に対して並列にバイパス弁ＢＶ２を備えたバイパス回路を設置し、かつ熱交換回路Ｃを第１二方弁ＫＶ１、及び第２二方弁ＫＶ２を介して、また蓄熱回路Ｄを第３二方弁ＫＶ３、及び第４二方弁ＫＶ４を介して、各空調ユニット１、２の室外側膨張弁５と室内側膨張弁７ａ、７ｂ、７ｃとの間に接続する。
【０００４】
次に動作を図２１に基づいて説明する。
昼間冷房運転で空調ユニット１から空調ユニット２へ系統間の熱移動を行う場合、冷媒熱交換器ＨＥにおいて、空調ユニット１の室外熱交換器４を出た後、冷媒熱交換器ＨＥに流入した高温高圧の液冷媒と、空調ユニット２の室外熱交換器４を出た後、冷媒熱交換器用膨張弁ＥＶ１により減圧されて冷媒熱交換器ＨＥの第２熱交換部１３で蒸発した低温低圧の二相冷媒とが熱交換することにより、空調ユニット１から空調ユニット２へ系統間の熱移動が可能になる。
即ち、空調ユニット２における余剰冷房能力分により空調ユニット１の過冷却度が増大し、室内機６ａ、６ｂ、６ｃでの冷房能力増大が図れ、空調ユニット１の冷房負荷に対応できる。
【０００５】
昼間暖房運転で空調ユニット１から空調ユニット２へ系統間の熱移動を行う場合、冷媒熱交換器ＨＥにおいて、空調ユニット２の圧縮機２吐出後、第１バイパス弁ＢＶ１を介して冷媒熱交換器ＨＥに流入した高温高圧ガス冷媒と、空調ユニット１の室内側膨張弁７ａ、７ｂ、７ｃにて減圧され、冷媒熱交換器ＨＥに流入した低温低圧２相冷媒とが熱交換することにより、空調ユニット２から空調ユニット１へ系統間の熱移動が可能になる。
即ち、空調ユニット２における余剰暖房能力分を空調ユニット１の蒸発能力増大に補填し、つまり暖房能力増大が図れ、空調ユニット１の暖房負荷に対応できる。
【０００６】
【発明が解決しようとする課題】
従来の空気調和装置は以上のように構成されているので、複数の冷媒回路に共通の熱移動熱交換器は液管に対して並列に接続されるため、バイパス回路が必要となり、またバイパス回路上には切換弁、膨張機構を備え、さらに主液配管にも切換弁を備えるため、コストアップになるという問題点と、冷媒配管構造、及び制御が複雑になるという問題点がある。
【０００７】
また、各冷媒回路の運転目的が空気調和であり、多様な目的を持つ回路、熱のカスケード利用については想定していない。
【０００８】
また、暖房運転時に負荷の大きい冷媒回路の熱源側熱交換器を除霜する場合、共通熱交換器を介して、余剰能力のある回路の熱を除霜したい熱源側熱交換器を備える回路側に移動させて除霜を行うことについては想定していない。
【０００９】
この発明は、上記のような問題点を解消するためになされたもので、複数の空気調和装置及び冷凍装置において負荷が異なる装置間で熱移動を実現して能力補填や熱の効率的利用を可能にする空気調和装置を得ることを目的とする。
【００１０】
また、回路構造簡略化によるコストダウン、及び制御の簡略化された空気調和装置を提供することを目的としている。
【００１１】
また、熱負荷の平準化と熱のカスケード利用による効率的な熱利用を可能にする空気調和装置を提供することを目的としている。
【００１２】
また、例えば低温の冷凍機器等を想定して多目的利用、熱のカスケード利用が可能な空気調和装置を提供することを目的としている。
【００１３】
また、負荷側熱交換器の暖房運転を継続しながら熱源側熱交換器の除霜を行うことが可能な空気調和装置を提供することを目的としている。
【００１４】
また、ある冷媒回路の冷房能力をさらに大きくすることができる空気調和装置の運転方法を提供することを目的としている。
【００１５】
また、ある冷媒回路の暖房能力をさらに大きくすることができる空気調和装置の運転方法を提供することを目的としている。
【００１６】
また、暖房運転している暖房運転を継続しながらある冷媒回路の熱源側熱交換器を除霜することができる空気調和装置の運転方法を提供することを目的としている。
【００１７】
また、各冷媒回路は常時共通熱交換器に冷媒を流通しながら、冷媒回路間での熱移動を行う場合と行わない場合との切替が可能な空気調和装置の運転方法を提供することを目的としている。
【００１８】
【課題を解決するための手段】
この発明に係る空気調和装置は、圧縮機または冷媒ポンプと、四方弁または冷暖切換弁と、熱源側熱交換器と、熱源側膨張機構と、負荷側膨張機構と、負荷側熱交換器と、前記四方弁または冷暖切換弁と前記圧縮機とを環状に接続して構成される複数の冷媒回路と、この冷媒回路の熱源側膨張機構と負荷側膨張機構との間に接続され、冷媒回路によって共有されると共に、各冷媒回路間で熱移動を行わない場合でも冷媒が流通する共通熱交換器とを備えたものである。
【００１９】
また、負荷側熱交換器に冷媒を流通させないためのバイパス管と、三方弁とを備えたものである。
【００２０】
また、共通熱交換器に余剰冷媒を貯蔵する液貯め部を設けたものである。
【００２１】
また、共通熱交換器に設けられ、蓄熱・蓄冷を行うための媒体が充填された蓄熱容器を備えたものである。
【００２２】
また、少なくとも１つの冷媒回路においては、共通熱交換器が直列に複数接続され、該複数の共通熱交換器はそれぞれ別々かつ任意の複数の他の冷媒回路に共有されるものである。
【００２３】
また、複数の共通熱交換器のそれぞれの間に、前記熱源側膨張機構及び前記負荷側膨張機構と同一作用のカスケード用膨張機構が配設されたものである。
【００２４】
また、複数の冷媒回路は、空気調和装置、冷凍用装置、冷蔵用装置等に使用されるものを含むものである。
【００２５】
この発明に係る空気調和装置の運転方法は、複数冷媒回路中、冷房運転しているある冷媒回路の冷房能力をさらに大きくする場合、ある冷媒回路においては、高圧状態で冷媒を前記共通熱交換器に流通させ、余剰能力のある他の冷媒回路において、共通熱交換器を流通する冷媒は、低圧二相状態で前記共通熱交換器へ流通させ、圧縮機又は冷媒ポンプの運転容量の調整して共通熱交換器での熱移動を制御するものである。
【００２６】
また、複数冷媒回路中、暖房運転しているある冷媒回路の暖房能力をさらに大きくする場合、ある冷媒回路においては、低圧二相状態で冷媒を前記共通熱交換器に流通させ、余剰能力のある他の冷媒回路において、共通熱交換器を流通する冷媒は、高圧状態で共通熱交換器へ流通させ、圧縮機又は冷媒ポンプの運転容量の調整して共通熱交換器での熱移動を制御するものである。
【００２７】
また、複数冷媒回路中、暖房運転しているある冷媒回路の熱源側熱交換器を除霜する場合、ある冷媒回路においては、低圧二相状態で冷媒を前記共通熱交換器に流通させ、余剰能力のある他の冷媒回路において、共通熱交換器を流通する冷媒は、高圧状態で前記共通熱交換器へ流通させ、圧縮機又は冷媒ポンプの運転容量の調整して共通熱交換器での熱移動を制御するものである。
【００２８】
また、冷媒回路間で熱移動を行わない場合は、冷媒回路の全てにおいて、共通熱交換器の両端に接続している膨張機構の絞り具合をほぼ同一にする調整をし、冷媒回路間で熱移動を行う場合は、熱移動によって能力を増大する冷媒回路の共通熱交換器の両端に接続している膨張機構の絞り具合を余剰能力のある他の冷媒回路の共通熱交換器の両端に接続している膨張機構の絞り具合と異なるようにする調整をし、圧縮機又は冷媒ポンプの運転容量の調整を伴うこともあるものである。
【００２９】
この発明に係る空気調和装置は、圧縮機または冷媒ポンプと、四方弁または冷暖切換弁と、熱源側熱交換器と、熱源側膨張機構とから熱源側ユニットを構成し、負荷側膨張機構と共通熱交換器から熱移動ユニットを構成し、負荷側熱交換器から負荷側ユニットを構成するとともに、熱源側ユニットと熱移動ユニットとの接続および熱移動ユニットと負荷側ユニットを接続することにより環状回路を構成することを特徴とする。
【００３０】
【発明の実施の形態】
実施の形態１．
以下、この発明の実施の形態の一例を、図面を参照して説明する。
図１はこの発明の実施の形態の一例を示す図で、冷媒回路図である。
図において、Ａ、Ｂは熱源側ユニット、Ｘ、Ｙは負荷側ユニット、Ｕは熱移動ユニット、１ａ、１ｂは圧縮機及び加圧ポンプ、２ａ、２ｂは四方弁及び冷暖切換弁、３ａ、３ｂは熱源側熱交換器、４ａ、４ｂは熱源側膨張機構、５ａ、５ｂは負荷側熱交換器、６ａ、６ｂは負荷側膨張機構、７は共通熱交換器、７ａ、７ｂは共通熱交換器パス、１０ａ、１０ｂは吐出配管、１１ａ、１１ｂは熱源側ガス配管、１２ａ、１２ｂは負荷側ガス配管、１３ａ、１３ｂは熱源側液配管、１４ａ、１４ｂは負荷側液配管、１５ａ、１５ｂは吸入配管である。
【００３１】
この発明の空気調和装置において、１つの共通熱交換器を共有する複数の冷媒回路のうち、ある冷媒回路の冷房能力増大方法について説明する。
この場合、冷房能力を増大させるある冷媒回路において、共通熱交換器を流通する冷媒は、熱源側膨張機構ではほとんど膨張されずに高圧液状態となり共通熱交換器へ流通し、その後、負荷側膨張機構で膨張されて低圧２相となり負荷側熱交換器へと流通する。
【００３２】
一方、余剰能力のある他の冷媒回路群において、共通熱交換器を流通する冷媒は、熱源側膨張機構で膨張されて低圧２相状態となり共通熱交換器へ流通し、その後負荷側膨張機構ではほとんど膨張されないで負荷側熱交換器へと流通し、また膨張機構はこのように制御され、さらに前述の膨張機構制御と、１つの或いはそれ以上の圧縮機及び冷媒ポンプの運転容量の調整により、ある回路の高圧液側から他の回路群の低圧２相側へ熱を移動させてある回路の高圧液の過冷却度を増大させて冷房能力を増大する。
【００３３】
次に、冷房運転中のある冷媒回路の冷房能力を増大させる場合の動作を図２の冷媒回路図によって説明する。
冷媒回路１は要求運転負荷が高い等、冷房能力をさらに増大し、冷媒回路２は要求運転負荷が低い等、余剰能力がある場合を想定する。
この運転時には、熱源側熱交換器３ａ、３ｂは凝縮器として、負荷側熱交換器５ａ、５ｂは蒸発器として動作し、四方弁２ａ、２ｂは冷房モードとして制御される。
熱源側膨張機構４ａは冷媒をほとんど膨張させないようにして、熱源側膨張機構４ｂは熱源側熱交換器３ｂの出口過冷却温度、或いは負荷側熱交換器５ｂの出口過熱温度が目標値になるように調整され、負荷側膨張機構６ａは熱源側熱交換器３ａの出口過冷却温度、或いは負荷側熱交換器５ａの出口過熱温度が目標値になるようにして、負荷側膨張機構６ｂは冷媒をほとんど膨張させないように調整される。
【００３４】
次に冷媒の流れについて図２に基づいて説明する。
冷媒回路１において、圧縮機１ａから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、四方弁２ａ、熱源側ガス配管１１ａを介して熱源側熱交換器３ａへ流入し、ここで熱源側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、熱源側液配管１３ａを介して熱源側膨張機構４ａを流通するが、ここではほとんど減圧されずに高圧の液状態のまま共通熱交換器７へ流入し、ここで冷媒回路２側の低温低圧冷媒と熱交換されて、高圧の液温度は低下する。その後、負荷側膨張機構６ａで減圧され、負荷側液配管１４ａを介して負荷側熱交換器５ａへ流入し、ここで負荷側の周辺空気と熱交換されて加熱されガス化する。ガス化した冷媒は負荷側ガス配管１２ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻る。
【００３５】
一方、冷媒回路２において、圧縮機１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ｂ、四方弁２ｂ、熱源側ガス配管１１ｂを介して熱源側熱交換器３ｂへ流入し、ここで熱源側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、熱源側液配管１３ｂを介して熱源側膨張機構４ｂで減圧されて共通熱交換器７へ流入する。ここで冷媒回路１側の高圧液冷媒と熱交換されて、加熱され一部ガス化する。その後負荷側膨張機構６ｂを流通するが、ここではほとんど減圧されずに負荷側液配管１４ｂを介して負荷側熱交換器５ｂへ流入し、ここで負荷側の周辺空気と熱交換されてガス化する。ガス化した冷媒は負荷側ガス配管１２ｂ、四方弁２ｂ、吸入配管１５ｂを介して圧縮機１ｂに戻る。
【００３６】
この発明の空気調和装置において、１つの共通熱交換器を共有する複数の冷媒回路のうち、ある冷媒回路の暖房能力増大方法について説明する。
この場合、暖房能力を増大させるある冷媒回路において、共通熱交換器を流通する冷媒は、負荷側膨張機構で膨張されて減圧され低圧２相状態となり共通熱交換器へ流通し、ここで他回路を流通する高圧冷媒と熱交換し、蒸発してガス化する。その後、熱源側膨張機構ではほとんど膨張されずに熱源側熱交換器へと流通し、ここでは低圧冷媒の状態により熱源側熱交換器での蒸発作用を調整する。
【００３７】
一方、余剰能力のある他の冷媒回路群において、共通熱交換器を流通する冷媒は、負荷側膨張機構でほとんど膨張されずに負荷状況によって高圧ガス、２相或いは液状態となり共通熱交換器へ流通し、ここで前述した冷媒回路を流通する低圧２相冷媒と熱交換し、凝縮されて高圧液となる。その後熱源側膨張機構で膨張されて減圧され熱源側熱交換器へと流通する。
【００３８】
さらに前述の膨張機構制御と、１つの或いはそれ以上の圧縮機及び冷媒ポンプの運転容量の調整により、他の回路群の高圧冷媒側からある回路の低圧２相側へ熱を移動させてある回路の低圧を高くして、圧縮機吸込み密度の増大、ならびに圧縮機運転効率の向上により、冷媒循環量を増加させることで暖房能力を増大する。
【００３９】
次に、暖房運転中のある冷媒回路の暖房能力を増大させる場合の動作を図３に基づいて説明する。冷媒回路１は要求運転負荷が高い等、暖房能力をさらに増大し、冷媒回路２は要求運転負荷が低い等、余剰能力がある場合を想定する。
この運転時には、熱源側熱交換器３ａ、３ｂは蒸発器として、負荷側熱交換器５ａ、５ｂは凝縮器として動作し、四方弁２ａ、２ｂは暖房モードとして制御され、熱源側膨張機構４ａは冷媒をほとんど膨張させないようにして、熱源側膨張機構４ｂは熱源側熱交換器３ｂの出口過熱温度、或いは負荷側熱交換器５ｂの出口過冷却温度が目標値になるように調整され、負荷側膨張機構６ａは熱源側熱交換器３ａの出口過熱温度、或いは負荷側熱交換器５ａの出口過冷却温度が目標値になるようにして、負荷側膨張機構６ｂは冷媒をほとんど膨張させないように調整される。
【００４０】
次に冷媒の流れについて図３に基づいて説明する。
冷媒回路１において、圧縮機１ａから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、四方弁２ａ、負荷側ガス配管１２ａを介して負荷側熱交換器３ａへ流入し、ここで負荷側の周辺空気と熱交換されて冷され液化する。
液化した冷媒は途中、負荷側液配管１４ａを介して負荷側膨張機構６ａで減圧されて共通熱交換器７へ流入し、ここで冷媒回路２側の高温高圧冷媒と熱交換されて、加熱されて一部蒸発する。
その後、熱源側膨張機構４ａではほとんど減圧されずに熱源側液配管１３ａを介して熱源側熱交換器３ａへ流入し、ここで熱源側の周辺空気と熱交換されて加熱されガス化する。ガス化した冷媒は熱源側ガス配管１１ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻る。
【００４１】
尚、共通熱交換器７において冷媒回路２側の高温高圧冷媒との熱交換による加熱量が多く、蒸発されて過熱ガスになった場合は、その後、熱源側膨張機構４ａではほとんど減圧されずに熱源側液配管１３ａを介して熱源側熱交換器３ａへ流入するが、３ａのファンを停止させて、できるかぎり熱源側の周辺空気と熱交換させないようにした後、熱源側ガス配管１１ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻るように制御する。
【００４２】
一方、冷媒回路２において、圧縮機１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ｂ、四方弁２ｂ、負荷側ガス配管１２ｂを介して負荷側熱交換器５ｂへ流入し、ここで負荷側の周辺空気と熱交換されて冷された後、負荷側液配管１４ｂを介して負荷側膨張機構６ｂを流通するが、ここではほとんど減圧されずに共通熱交換器７へ流入する。ここで冷媒回路１側の低圧冷媒と熱交換されて、冷されて高圧液となる。
【００４３】
その後熱源側膨張機構４ｂで減圧され、熱源側液配管１３ｂを介して熱源側熱交換器３ｂへ流入し、ここで熱源側の周辺空気と熱交換されてガス化する。ガス化した冷媒は熱源側ガス配管１１ｂ、四方弁２ｂ、吸入配管１５ｂを介して圧縮機１ｂに戻る。
【００４４】
次に、本発明の空気調和装置において、１つの共通熱交換器を共有する複数の冷媒回路のうち、ある冷媒回路の熱源側熱交換器を暖房運転継続したまま除霜する方法について説明する。
この場合、除霜する熱源側熱交換器を備えるある回路において、共通熱交換器を流通する冷媒は、負荷側膨張機構で膨張されて低圧２相状態となり共通熱交換器へ流通し、その後、熱源側膨張機構でほとんど膨張されないまま熱源側熱交換器へと流通する。
【００４５】
一方、余剰能力のある他の回路群において、共通熱交換器を流通する冷媒は、負荷側膨張機構でほとんど膨張されずに高圧液、ガス及び２相状態となり共通熱交換器へ流通し、その後熱源側膨張機構で膨張されて低圧２相となり熱源側熱交換器へと流通する。
【００４６】
さらに前述の膨張機構制御と、１つの或いはそれ以上の圧縮機及び冷媒ポンプの運転容量の調整により、ある回路の低圧２相側へ他の回路群の高圧液、ガス及び２相側の熱を移動させることで、ある回路の共通熱交換器出口での冷媒状態を過熱度の大きい低圧ガスにした後、熱源側熱交換器へ流通させ、そこで凝縮させることで熱源側熱交換器を除霜する。
【００４７】
次に、暖房運転中のある冷媒回路が、暖房運転を継続しながら熱源側熱交換器を除霜する時の動作を図４に基づいて説明する。
冷媒回路１は除霜を所望する熱源側熱交換器を所有しており、冷媒回路２は暖房運転中で要求運転負荷が低い等、余剰能力がある場合を想定する。
この運転時の動作は、前述したある回路の暖房能力を他回路の余剰能力を使用して増大する場合と同一なので詳細な動作説明は省略する。
【００４８】
次に冷媒の流れについて図４に基づいて説明する。
冷媒回路１において、圧縮機１ａから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、四方弁２ａ、負荷側ガス配管１２ａを介して負荷側熱交換器５ａへ流入し、ここで負荷側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、負荷側液配管１４ａを介して負荷側膨張機構６ａで減圧されて共通熱交換器７へ流入し、ここで冷媒回路２側の高温高圧冷媒と熱交換される。
【００４９】
この時、暖房能力増大運転の時よりもさらに多い熱交換量で加熱されて蒸発し、過熱度が大きい低圧ガスとなった後、熱源側膨張機構４ａではほとんど減圧されずに熱源側液配管１３ａを介して除霜を所望する熱源側熱交換器３ａへ流入する。ここで熱源側熱交換器３ａのファンは停止しており、過熱度が大きい低圧ガス冷媒は熱源側熱交換器３ａの管やフィンと熱交換されて冷却され一部液化する。一部液化した低圧のガス冷媒は熱源側ガス配管１１ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻る。
【００５０】
一方、冷媒回路２において、圧縮機１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ｂ、四方弁２ｂ、負荷側ガス配管１２ｂを介して負荷側熱交換器５ｂへ流入し、ここで負荷側の周辺空気と熱交換されて冷された後、負荷側液配管１４ｂを介して負荷側膨張機構６ｂを流通するが、ここではほとんど減圧されずに共通熱交換器７へ流入する。ここで冷媒回路１側の低圧冷媒と熱交換されて、冷されて高圧液となる。
【００５１】
その後熱源側膨張機構４ｂで減圧され、熱源側液配管１３ｂを介して熱源側熱交換器３ｂへ流入し、ここで熱源側の周辺空気と熱交換されてガス化する。ガス化した冷媒は熱源側ガス配管１１ｂ、四方弁２ｂ、吸入配管１５ｂを介して圧縮機１ｂに戻る。
【００５２】
次に、冷房運転、暖房運転が混在している場合、冷房運転している冷媒回路の冷房能力を増大する時の動作を図５に基づいて説明する。
冷媒回路１は冷房運転していて、要求運転負荷が高い等、冷房能力をさらに増大し、冷媒回路２は暖房運転していて要求運転負荷が低い等、余剰能力がある場合を想定する。
この運転時には、熱源側熱交換器３ａ、負荷側熱交換器５ｂは凝縮器として、負荷側熱交換器５ａ、熱源側熱交換器３ｂは蒸発器として動作し、四方弁２ａは冷房モード、四方弁２ｂは暖房モードとして制御され、熱源側膨張機構４ａ、４ｂは冷媒をほとんど膨張させないようにして、負荷側膨張機構６ａは熱源側熱交換器３ａの出口過冷却温度、或いは負荷側熱交換器５ａの出口過熱温度が目標値になるように調整され、負荷側膨張機構６ｂは熱源側熱交換器３ｂの出口過熱温度、或いは負荷側熱交換器５ｂの出口過冷却温度が目標値になるように調整される。
【００５３】
次に冷媒の流れについて図５に基づいて説明する。
冷媒回路１において、圧縮機１ａから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、四方弁２ａ、熱源側ガス配管１１ａを介して熱源側熱交換器３ａへ流入し、ここで熱源側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、熱源側液配管１３ａを介して熱源側膨張機構４ａを流通するが、ここではほとんど減圧されずに高圧の液状態のまま共通熱交換器７へ流入し、ここで冷媒回路２側の低温低圧冷媒と熱交換されて、高圧の液温度は低下する。
【００５４】
その後、負荷側膨張機構６ａで減圧され、負荷側液配管１４ａを介して負荷側熱交換器５ａへ流入し、ここで負荷側の周辺空気と熱交換されて加熱されガス化する。ガス化した冷媒は負荷側ガス配管１２ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻る。
【００５５】
一方、冷媒回路２において、圧縮機１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ｂ、四方弁２ｂ、負荷側ガス配管１２ｂを介して負荷側熱交換器５ｂへ流入し、ここで負荷側の周辺空気と熱交換されて冷された後、負荷側液配管１４ｂを介して負荷側膨張機構６ｂで減圧されて共通熱交換器７へ流入する。ここで冷媒回路１側の高圧の液冷媒と熱交換されて、加熱されて一部ガス化し、その後熱源側膨張機構４ｂを流通するがここではほとんど減圧されずに、熱源側液配管１３ｂを介して熱源側熱交換器３ｂへ流入し、ここで熱源側の周辺空気と熱交換されてガス化する。ガス化した冷媒は熱源側ガス配管１１ｂ、四方弁２ｂ、吸入配管１５ｂを介して圧縮機１ｂに戻る。
【００５６】
次に、冷房運転、暖房運転が混在している場合、暖房運転している冷媒回路の暖房能力を増大する時の動作を図６に基づいて説明する。
冷媒回路１は暖房運転していて、要求運転負荷が高い等、暖房能力をさらに増大し、冷媒回路２は冷房運転していて要求運転負荷が低い等、余剰能力がある場合を想定する。
この運転時には、熱源側熱交換器３ａ、負荷側熱交換器５ｂは蒸発器として、負荷側熱交換器５ａ、熱源側熱交換器３ｂは凝縮器として動作し、四方弁２ａは暖房モード、四方弁２ｂは冷房モードとして制御され、熱源側膨張機構４ａ、４ｂは冷媒をほとんど膨張させないようにして、負荷側膨張機構６ａは負荷側熱交換器５ａの出口過冷却温度、或いは熱源側熱交換器３ａの出口過熱温度が目標値になるように調整され、負荷側膨張機構６ｂは負荷側熱交換器５ｂの出口過熱温度、或いは熱源側熱交換器３ｂの出口過冷却温度が目標値になるように調整される。
【００５７】
次に冷媒の流れについて図６に基づいて説明する。
冷媒回路１において、圧縮機１ａから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、四方弁２ａ、負荷側ガス配管１２ａを介して負荷側熱交換器５ａへ流入し、ここで負荷側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、負荷側液配管１４ａを介して負荷側膨張機構６ａで減圧されて共通熱交換器７へ流入し、ここで冷媒回路２側の高温高圧冷媒と熱交換されて、加熱されて一部蒸発する。
【００５８】
その後、熱源側膨張機構４ａではほとんど減圧されずに熱源側液配管１３ａを介して熱源側熱交換器３ａへ流入し、ここで負荷側の周辺空気と熱交換されて加熱されガス化する。ガス化した冷媒は熱源側ガス配管１１ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻る。尚、共通熱交換器７において冷媒回路２側の高温高圧冷媒との熱交換による加熱量が多く、蒸発されて加熱ガスになった冷媒は、その後、熱源側膨張機構４ａではほとんど減圧されずに熱源側液配管１３ａを介して熱源側熱交換器３ａへ流入するが、３ａのファンを停止させて、できるかぎり熱源側の周辺空気と熱交換させないようにした後、熱源側ガス配管１１ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻させるように制御する。
【００５９】
一方、冷媒回路２において、圧縮機１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ｂ、四方弁２ｂ、熱源側ガス配管１１ｂを介して熱源側熱交換器３ｂへ流入し、ここで熱源側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、熱源側液配管１３ｂを介して熱源側膨張機構４ｂを流通するがここでは減圧されずに共通熱交換器７へ流入する。ここで冷媒回路１側の低圧冷媒と熱交換されて、冷却され液温度が低下する。その後負荷側膨張機構６ｂで減圧されて負荷側液配管１４ｂを介して負荷側熱交換器５ｂへ流入し、ここで負荷側の周辺空気と熱交換されてガス化する。ガス化した冷媒は負荷側ガス配管１２ｂ、四方弁２ｂ、吸入配管１５ｂを介して圧縮機１ｂに戻る。
【００６０】
次に、この発明の空気調和装置において、１つの共通熱交換器を共有する複数の冷媒回路のうち、共通熱交換器を介してある回路から別の回路へ熱移動を行う場合と行わない場合の運転方法について説明する。
熱移動を行わない場合、全回路において、例えば、共通熱交換器の両端に接続する膨張機構の絞り具合をほぼ同一にする等の調整を行って、共通熱交換器を流通する各回路ごとの冷媒間に温度差をつけないようにする。
一方、例えば、熱移動を行う場合は、熱移動によって能力を増大する回路の膨張機構の絞り具合を余剰能力のある他の回路群の膨張機構の絞り具合と異なるようにする等の調整を行って、共通熱交換器を流通する冷媒において、熱移動されて能力を増加する回路の冷媒と熱を供給する他の回路群の冷媒の温度差をつけて熱移動しやすいようにし、さらに１つ或いはそれ以上の圧縮機及び冷媒ポンプの運転容量を調整し、共通熱交換器内を流通する冷媒流量を調整して熱移動の量を制御する。
【００６１】
なお、この実施形態において、図７に示すように吐出配管１０ａ、１０ｂの途中に油分離器２１ａ、２１ｂを設置したり、図８に示すように吸入配管１５ａ、１５ｂの途中に液分離器２２ａ、２２ｂを設置しても基本動作及び冷媒の流れ方は、油分離器や液分離器が無い場合と同一である。
【００６２】
以上のようにこの実施形態１では、両端に膨張機構を備える１つの共通熱交換器を複数の冷媒回路で共有することで、複数の冷媒回路間での熱移動を可能にし、冷房運転、暖房運転ともに要求運転負荷に対して最大能力が不足している冷媒回路に対して、余剰能力のある複数の冷媒回路群から能力を補填することを可能にしている。
【００６３】
また、熱移動量の調整は、各冷媒回路に備えられている熱源側膨張機構と負荷側膨張機構の制御により共通熱交換器で熱交換される高圧冷媒と低圧冷媒の温度差が調整され、また余剰能力がある複数の冷媒回路群の圧縮機容量を調整することで、回路を循環する冷媒量を調整し、冷媒回路間を移動させる熱量を制御する空気調和装置の提供が可能である。
【００６４】
実施形態１をビル等に適用する場合の例を図９に示す。Ｘ１、Ｘ２、Ｙ１、Ｙ２室は、あるビルの１フロアーにある部屋である。それぞれの部屋に室内機が設置され、Ｘ１、Ｘ２室室内機は室外機Ａに接続され１つの冷媒回路を形成し、Ｙ１、Ｙ２室室内機は室外機Ｂに接続され１つの冷媒回路を形成する。それぞれの冷媒回路は共通熱交換器を介して互いに不足能力を補填する。
【００６５】
実施の形態２．
図１０はこの発明の実施の形態の他の例を示す図で、冷媒回路図である。
図１の実施の形態１の冷媒回路に三方弁８ａ、８ｂ、負荷側バイパス管１６ａ、１６ｂを追加したものである。
【００６６】
図１０において、三方弁８ａ、８ｂ、負荷側バイパス管１６ａ、１６ｂは、１つの冷媒回路において全負荷側熱交換器を使用せず、かつ他の冷媒回路の能力増加のために共通熱交換器を介して熱を供給する場合に、負荷側熱交換器に冷媒を流通する代わりにバイパス管を流通させるものである。
【００６７】
この実施形態では、バイパス管に冷媒を流通させる場合は、共通熱交換器が冷媒回路中において主たる凝縮器及び蒸発器として作用する。
【００６８】
この実施形態では、負荷側熱交換器群に冷媒を流通させないためのバイパス管と三方弁を備えることで、負荷側の運転要求が無い冷媒回路が他の冷媒回路の能力補填等のために運転する場合、停止負荷熱交換器に冷媒を流通させないことで、停止負荷熱交換器への冷媒流通による騒音問題を解消する空気調和装置の提供が可能である。尚、本バイパスを使用せずに、停止負荷熱交換器のファンを停止して、冷媒を流通させたとしても、多少の熱損失はあるが、同一の効果は得られる。
【００６９】
実施の形態３．
図１１はこの発明の実施の形態の他の例を示す図で、冷媒回路図である。
実施の形態１の共通熱交換器に余剰冷媒を貯蔵する液貯め部を設けたものである。２３は液溜め容器、２３ａ、２３ｂは各冷媒回路の液溜め部である。
【００７０】
液溜め容器２３を用いることで、各回路の余剰冷媒をここに貯蔵することができるため、各冷媒回路中の液溜め用容器を撤去して、コストダウンを可能にする空気調和装置の提供を可能にする。尚、この実施形態における熱移動方法、及び冷媒の流れ方は実施形態１と同様なので説明を省略する。
【００７１】
実施の形態４．
図１２はこの発明の実施の形態の他の例を示す図で、冷媒回路図である。
実施の形態１の共通熱交換器に設けられた、蓄熱・蓄冷を行うための媒体が充填された蓄熱容器２４を追加したものである。
【００７２】
蓄熱容器２４を追加することで、各回路が深夜電力等安価な電力を使用して氷を生成し、昼間の冷房運転需要の多いときにこれを使用して能力を補填することが可能である。同時に実施の形態１で説明した能力不足回路への他回路からの能力補填が可能であることは言うまでもない。
【００７３】
冷媒の流れ方及び共通熱交換器での基本的な熱移動方法は実施の形態１と同一である。ここでは蓄冷媒体に水を使用し、深夜電力で氷を生成し、昼間にその氷を使用して冷房運転する例を図１３に基づいて説明する。
【００７４】
冷媒回路１、冷媒回路２とも夜間等、電気代が安くかつ冷房運転負荷が小さい場合は、共通熱交換器７を蒸発器、熱源側熱交換器３ａ、３ｂを凝縮器、負荷側熱交換器は冷房運転要求のある熱交換器だけを蒸発器として動作し、四方弁２ａ、２ｂは冷房モードとして制御され、熱源側膨張機構４ａ、４ｂは熱源側熱交換器３ａ、３ｂの出口過冷却温度、或いは負荷側熱交換器５ａ、５ｂか共通熱交換器７を流通する冷媒温度が目標値になるように調整され、負荷側膨張機構６ａ、６ｂはほとんど膨張されないように調整され、各回路の運転容量は蓄熱容器２４で生成する氷量に基づいて調整される。
【００７５】
次に冷媒の流れ方を図１３に基づいて示す。
冷媒回路１、冷媒回路２において、圧縮機１ａ、１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、１０ｂ、四方弁２ａ、２ｂ熱源側ガス配管１２ａ、１２ｂを介して熱源側熱交換器３ａ、３ｂへ流入し、ここで熱源側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、熱源側液配管を介して熱源側膨張機構４ａ、４ｂを流通し、ここで減圧されて低圧２相のまま共通熱交換器７へ流入し、ここで蓄熱容器２４に滞留している水と熱交換して、水を氷にする。
【００７６】
その後、負荷側膨張機構６ａ、６ｂではほとんど減圧されずに、負荷側液配管１４ａ、１４ｂを介して負荷側熱交換器５ａ、５ｂへ流入し、ここで負荷側の周辺空気と熱交換されて加熱されガス化する。ガス化した低圧冷媒は負荷側ガス配管１２ａ、１２ｂ、四方弁２ａ、２ｂ、吸入配管１５ａ、１５ｂを介して圧縮機１ａ、１ｂに戻る。
【００７７】
一方、昼間でかつ冷媒回路１、冷媒回路２とも冷房運転負荷が大きい場合は、氷状態になっている蓄熱容器２４を通る共通熱交換器７を過冷却器、熱源側熱交換器３ａ、３ｂを凝縮器、負荷側熱交換器５ａ、５ｂは蒸発器として動作し、四方弁２ａ、２ｂは冷房モードとして制御され、負荷側膨張機構６ａ、６ｂは熱源側熱交換器３ａ、３ｂの出口過冷却温度、或いは負荷側熱交換器５ａ、５ｂか共通熱交換器７を流通する冷媒温度が目標値になるように調整され、熱源側膨張機構４ａ、４ｂはほとんど膨張されないように調整され、各回路の運転容量は負荷側が要求する能力に基づいて調整される。
【００７８】
以上のように、この実施形態４では、実施形態１の回路に蓄熱容器を追加したことで、例えば深夜電力を使用して氷を生成し、昼間の冷房需要が多いときに冷房能力の補填を行うことで能力不足を防いだり、運転にかかる電気代を削減する等、蓄熱・蓄冷によって能力不足時の能力充填を実現する空気調和装置の提供を可能にする。
【００７９】
実施形態４をビル等に適用する場合の例を図１４に示す。Ｘ１、Ｘ２、Ｙ１、Ｙ２室は、あるビルの１フロアーにある部屋である。それぞれの部屋に室内機が設置され、Ｘ１、Ｘ２室室内機は室外機Ａに接続され１つの冷媒回路を形成し、Ｙ１、Ｙ２室室内機は室外機Ｂに接続され１つの冷媒回路を形成する。それぞれの冷媒回路は深夜電力等安価な電気を使用して蓄熱容器に氷を作成し、昼間に氷を使用した冷房運転をする一方、共通熱交換器を介して互いに不足能力を補填する運転も行う。
【００８０】
実施の形態５．
図１５はこの発明の実施の形態の他の例を示す冷媒回路図である。
実施の形態１の冷媒回路の共通熱交換器７が７−１、７−２とに分割され、それぞれが別々の回路と共有されているものである。
【００８１】
この実施形態における熱移動方法、及び冷媒の流れ方は実施形態１と同様なので説明を省略する。
【００８２】
この実施形態では、１つの冷媒回路が複数の共通熱交換器を備え、各共通熱交換器が別々の冷媒回路と熱移動を行うことで、複数冷媒回路を経由して熱移動を行うことができ、熱のカスケード利用によるシステム全体の効率的な熱の使用を可能な空気調和装置の提供が可能である。
【００８３】
実施の形態６．
図１６はこの発明の実施の形態の他の例を示す図で、冷媒回路図である。
実施の形態５の冷媒回路の共通熱交換器の間にカスケード用膨張機構９ｃが備えられているものである。
【００８４】
次に、両端に膨張機構を接続する共通熱交換器を複数個備えるある回路が、他の低温冷凍用回路と空調用回路の暖房能力を増大する時の動作例を図１７に基づいて説明する。
冷媒回路１は低温の冷凍用回路で冷房能力の増大を要求し、冷媒回路２は空調用回路で暖房能力の増大を要求し、冷媒回路３は負荷側で暖房運転をする一方、冷媒回路１、２の能力増加を補填している場合を想定する。
【００８５】
冷媒回路１では熱源側熱交換器３ａは凝縮器として、負荷側熱交換器５ａは蒸発器として動作し、四方弁２ａは冷房モードとして制御され、熱源側膨張機構４ａは冷媒をほとんど膨張させないようにして、負荷側膨張機構６ａは熱源側熱交換器３ａの出口過冷却温度、或いは負荷側熱交換器５ａの出口過熱温度が目標値になるように膨張され調整される。
【００８６】
冷媒回路２では熱源側熱交換器３ｂを蒸発器として、また負荷側熱交換器５ｂは凝縮器として動作し、四方弁２ｂは暖房モードとして制御され、負荷側膨張機構６ｂは冷媒を膨張させて、負荷側熱交換器５ｂの出口過冷却温度、或いは熱源側熱交換器３ｂの出口過熱温度が目標値になるように膨張して調整され、熱源側膨張機構４ｂはほとんど膨張しないように調整される。
【００８７】
冷媒回路３では負荷側熱交換器５ｃを凝縮器として、熱源側熱交換器３ｃを蒸発器として動作し、四方弁２ｃを暖房モードとした場合、熱源側膨張機構４ｃ及び負荷側膨張機構６ｃは冷媒をほとんど膨張させないで、またカスケード用膨張機構９ｃは負荷側熱交換器５ｃの出口過冷却温度、或いは熱源側熱交換器３ｃの出口過熱温度が目標値になるように調整される。
【００８８】
次に冷媒の流れについて図１７に基づいて説明する。
冷媒回路１において、圧縮機１ａから吐出された高温高圧のガス冷媒は、吐出配管１０ａ、四方弁２ａ、熱源側ガス配管１１ａを介して熱源側熱交換器３ａへ流入するが、熱交換器用ファンを停止させるため、ほとんど熱交換されずに高圧ガス或いは２相状態で熱源側液配管を介して熱源側膨張機構４ａを流通するが、ここではほとんど減圧されずに高圧ガス或いは２相状態のまま共通熱交換器７−１へ流入する。ここで冷媒回路３側の共通熱交換器７−１を流通する低圧２相冷媒と熱交換されて凝縮し、高圧液となる。
【００８９】
その後、負荷側膨張機構６ａで減圧され、負荷側液配管１４ａを介して負荷側熱交換器５ａへ流入し、ここで負荷側の周辺空気と熱交換されて加熱されガス化する。ガス化した冷媒は負荷側ガス配管１２ａ、四方弁２ａ、吸入配管１５ａを介して圧縮機１ａに戻る。
【００９０】
一方、冷媒回路２において、圧縮機１ｂから吐出された高温高圧のガス冷媒は、吐出配管１０ｂ、四方弁２ｂ、負荷側ガス配管１２ｂを介して負荷側熱交換器３ｂへ流入し、ここで負荷側の周辺空気と熱交換されて冷され液化する。液化した冷媒は途中、負荷側液配管１４ｂを介して負荷側膨張機構６ｂで減圧されて低圧２相状態になり共通熱交換器７−２へ流入する。ここで冷媒回路３の共通熱交換器７−２を流通する高圧液冷媒と熱交換されて蒸発し一部ガス化する。
【００９１】
その後熱源側膨張機構４ｂを流通するが、ここではほとんど減圧されずに負荷側液配管１３ｂを介して熱源側熱交換器３ｂへ流入する。ここでは低圧冷媒状態に応じてファン風量を調整して蒸発作用を制御してガス化する。ガス化した低圧冷媒は熱源側ガス配管１１ｂ、四方弁２ｂ、吸入配管１５ｂを介して圧縮機１ｂに戻る。
【００９２】
一方、冷媒回路３において、圧縮機１ｃから吐出された高温高圧のガス冷媒は、吐出配管１０ｃ、四方弁２ｃ、負荷側ガス配管１２ｃを介して負荷側熱交換器５ｃへ流入し、ここで負荷側の周辺空気と熱交換されて冷された後、負荷側液配管１４ｃを介して負荷側膨張機構６ｃを流通するが、ここではほとんど減圧されずに高圧２相状態で共通熱交換器７−２へ流入する。ここで冷媒回路２側の低圧２相冷媒と熱交換されて、冷されて高圧液となる。
【００９３】
その後カスケード用膨張機構９ｃで減圧されて低圧２相状態になり共通熱交換器７−１へ流入する。ここで冷媒回路２側の高圧液冷媒と熱交換されて、一部ガス化する。その後、熱源側膨張機構４ｃへ流通するがここではほとんど減圧されずに、熱源側液配管１３ｃを介して熱源側熱交換器３ｃへ流入し、ここで熱源側の周辺空気と熱交換されてガス化する。ガス化した冷媒は熱源側ガス配管１１ｃ、四方弁２ｃ、吸入配管１５ｃを介して圧縮機１ｃに戻る。
【００９４】
このように負荷が小さくかつ複数の共通熱交換器を備える冷媒回路は、他の回路の冷房運転や暖房運転の能力を補填することができる。
【００９５】
同様に複数の共通熱交換器を備える回路が他の低温の冷凍用回路と空調用回路の冷房能力を増大することも可能である。以下、図１８に基づいて説明する。
【００９６】
冷媒回路１は低温の冷凍用回路で冷房能力の増大を要求し、冷媒回路２は空調用回路で冷房能力の増大を要求し、冷媒回路３は負荷側で暖房運転をする一方、冷媒回路１、２の能力増加を補填している場合を想定する。
冷房及び暖房運転動作の詳細説明は省略し、ここではポイントだけ説明する。冷媒回路１では熱源側膨張機構４ａは冷媒をほとんど膨張させないようにして、負荷側膨張機構６ａは熱源側熱交換器３ａの出口過冷却温度、或いは負荷側熱交換器５ａの出口過熱温度が目標値になるように調整され、また熱源側熱交換器３ａにおける外気との熱交換量を最小限に抑えた場合は共通熱交換器内７−１を流通する冷媒は高圧ガス、或いは２相状態になり、また熱源側熱交換器３ａにおける外気との熱交換量が多い場合は共通熱交換器７−１内を流通する冷媒は高圧２相、或いは液状態になるように調整される。
【００９７】
共通熱交換器７−１では冷媒回路３の共通熱交換器７−１を流通する低圧２相冷媒と熱交換して、冷媒回路１の共通熱交換器７−１を流通する冷媒が冷され液化する。一方、冷媒回路３の共通熱交換器７−１を流通する冷媒の温度が低いため冷媒回路１の凝縮温度が低くなり、結果、低温の蒸発温度生成が可能であり、冷凍機器に対応する冷媒回路を回路群に加えることが可能になる。
【００９８】
冷媒回路２では熱源側膨張機構４ｂは冷媒をほとんど膨張させないようにして、負荷側膨張機構６ｂは熱源側熱交換器３ｂの出口過冷却温度、或いは負荷側熱交換器５ｂの出口過熱温度が目標値になるように調整される。共通熱交換器７−２に流通する冷媒は高圧液状態であり、冷媒回路３の共通熱交換器７−２に流通する低圧２相の冷媒と熱交換を行い過冷却度が増加して冷房能力が増加する。
【００９９】
冷媒回路３では熱源側膨張機構４ｃ、カスケード用膨張機構９ｃでは冷媒をほとんど膨張させないようにして、負荷側膨張機構６ｃは負荷側熱交換器５ｃの出口過冷却温度、或いは熱源側熱交換器３ｃの出口過熱温度が目標値になるように調整され、共通熱交換器７−１、７−２内のパス７ｃａ、７ｃｂを流通する冷媒は低圧２相状態になるように調整され、それぞれ冷媒回路１の高圧のガス、２相或いは液冷媒、冷媒回路２の高圧液冷媒と熱交換されて暖められてガスになる。尚、冷媒の流れ方についての説明は省略する。
【０１００】
この実施形態では、両端に膨張機構を接続した共通熱交換器を複数個備える回路において、冷媒流れの一番上流側に位置する共通熱交換器内圧力が最も高く、一番下流側に位置する共通熱交換器内圧力が最も低くなり、その間に位置する複数の共通熱交換器内圧力は流れ順に順次少しずつ低下した値を示す。圧力の高い共通熱交換器では他の冷媒回路に熱を供給することで他の冷媒回路の主に暖房能力を増加させたり、本回路の主に冷房能力を増大したり等を可能にする一方、圧力の低い共通熱交換器では、他の冷媒回路から熱を回収して本回路の蒸発能力を補填し、主に暖房能力を増大したり、他の冷媒回路から熱を回収して主に冷房能力を増大したり等を可能にし、さらにそれぞれの共通熱交換器が、目的や所望負荷量に応じて、別々の複数の冷媒回路間で熱移動を行うことで、熱のカスケード利用による効率化、及びシステム全体としての負荷平準化を図ることが可能になる。
【０１０１】
例えば、本システムを冷凍機器を備えた店舗に設置した例を図１９に示す。Ｘ室には空気調和装置１，２，３、Ｙ室には空気調和装置４、５が設置され、またＸ室には冷凍食品などを保存するショーケース６，７，８が設置されている。
室内機１，２，３は室外機Ａに、室内機４、５は室外機Ｂに、ショーケース６，７，８は室外機Ｃに接続され各々冷媒回路を形成する。各回路は共通熱交換器を備え、共通熱交換器を介して他回路の能力補填を行う。
【０１０２】
実施の形態７．
図２０はこの発明の実施の形態の他の例を示す図で、冷媒回路図である。
実施の形態１の冷媒回路において、熱源側膨張機構３ａと負荷側熱交換器５ａの間に備えられた共通熱交換器７−１ａに平行して、例えば蓄熱容器２４に囲まれた共通熱交換器７−１ｂを備えたものである。
【０１０３】
この場合、蓄熱容器２４に生成された氷を使用する場合と、各回路で能力を補填する場合とで、使用する共通熱交換器を使い分けることで、より効率のよい運転が可能となる。尚、動作方法、及び冷媒の流れ方は既に他の実施の形態で説明したものと重複するため省略する。
【０１０４】
【発明の効果】
この発明に係る空気調和装置は、圧縮機または冷媒ポンプと、四方弁または冷暖切換弁と、熱源側熱交換器と、熱源側膨張機構と、負荷側膨張機構と、負荷側熱交換器と、前記四方弁または冷暖切換弁と前記圧縮機とを環状に接続して構成される複数の冷媒回路と、この冷媒回路の熱源側膨張機構と負荷側膨張機構との間に接続され、冷媒回路によって共有されると共に、各冷媒回路間で熱移動を行わない場合でも冷媒が流通する共通熱交換器とを備えた構成にしたので、共通熱交換器用に切換弁や膨張機構を備えたバイパス回路を設置せずに回路及び制御の簡素化が図れ、複数の冷媒回路間において余剰能力のある回路から能力不足回路へ必要な熱の授受を共通熱交換器を介して行い、能力不足回路の能力補填を可能とすることで、システム全体の熱負荷の平準化と熱のカスケード利用によるシステム全体の効率的な熱の利用を可能にする。
【０１０５】
また、負荷側熱交換器に冷媒を流通させないためのバイパス管と、三方弁とを備えたので、停止負荷熱交換器への冷媒流通による騒音問題を解消する。
【０１０６】
また、共通熱交換器に余剰冷媒を貯蔵する液貯め部を設けたので、各冷媒回路中の液溜め用容器を撤去して、コストダウンを可能にする。
【０１０７】
また、共通熱交換器に蓄熱・蓄冷を行うための媒体が充填された蓄熱容器を設けたので、各回路が深夜電力等安価な電力を使用して蓄熱・蓄冷を可能とし、昼間の暖房・冷房運転需要の多いときにこれを使用して能力を補填することが可能である。
【０１０８】
また、少なくとも１つの冷媒回路においては、共通熱交換器が直列に複数接続され、該複数の共通熱交換器はそれぞれ別々かつ任意の複数の他の冷媒回路に共有されるので、各共通熱交換器が別々の冷媒回路と熱移動を行うことで、複数冷媒回路をはさんで熱移動を行うことができ、熱のカスケード利用によるシステム全体の効率的な熱の使用を可能とする空気調和装置の提供が可能である。。
【０１０９】
また、複数の共通熱交換器の両端に膨張機構が接続されるように、各共通熱交換器の間に、カスケード用膨張機構が配設された構成にしたので、それぞれの共通熱交換器が、目的や所望負荷量に応じて、別々の複数の冷媒回路間で熱移動を行うことで、熱のカスケード利用による効率化、及びシステム全体としての負荷平準化を図ることが可能になる。。
【０１１０】
また、複数の冷媒回路は、空気調和装置、冷凍用装置、冷蔵用装置等に使用されるものを含む構成にしたので、共通熱交換器を共有する各冷媒回路は空気調和や冷凍等、目的が異なる複数の回路間で熱の授受を行うことも可能である。
【０１１１】
この発明に係る空気調和装置の運転方法は、複数冷媒回路中、冷房運転しているある冷媒回路の冷房能力をさらに大きくする場合、ある冷媒回路においては、高圧状態で冷媒を前記共通熱交換器に流通させ、余剰能力のある他の冷媒回路において、共通熱交換器を流通する冷媒は、低圧二相状態で前記共通熱交換器へ流通させ、圧縮機又は冷媒ポンプの運転容量の調整して共通熱交換器での熱移動を制御することにより、ある冷媒回路の冷房能力をさらに大きくすることができる。
【０１１２】
また、複数冷媒回路中、暖房運転しているある冷媒回路の暖房能力をさらに大きくする場合、ある冷媒回路においては、低圧二相状態で冷媒を前記共通熱交換器に流通させ、余剰能力のある他の冷媒回路において、共通熱交換器を流通する冷媒は、高圧状態で共通熱交換器へ流通させ、圧縮機又は冷媒ポンプの運転容量の調整して共通熱交換器での熱移動を制御することにより、ある冷媒回路の暖房能力をさらに大きくすることができる。
【０１１３】
また、複数冷媒回路中、暖房運転している暖房運転を継続しながらある冷媒回路の熱源側熱交換器を除霜する場合、ある冷媒回路においては、低圧二相状態で冷媒を前記共通熱交換器に流通させ、余剰能力のある他の冷媒回路において、共通熱交換器を流通する冷媒は、高圧状態で前記共通熱交換器へ流通させ、圧縮機又は冷媒ポンプの運転容量の調整して共通熱交換器での熱移動を制御することにより、暖房運転しているある冷媒回路の熱源側熱交換器を除霜することができる。
【０１１４】
また、冷媒回路間で熱移動を行わない場合は、冷媒回路の全てにおいて、共通熱交換器の両端に接続している膨張機構の絞り具合をほぼ同一にする調整を行って共通熱交換器内を流通する冷媒間の温度差を無くし、冷媒回路間で熱移動を行う場合は、熱移動によって能力を増大する冷媒回路の共通熱交換器の両端に接続している膨張機構の絞り具合を余剰能力のある他の冷媒回路の共通熱交換器の両端に接続している膨張機構の絞り具合と異なるようにする調整を行って共通熱交換器内を流通する冷媒間の温度差を確保することで熱移動を行い、圧縮機又は冷媒ポンプの運転容量を調整することにより、冷媒回路間での熱移動量を調整することが可能である。
【図面の簡単な説明】
【図１】この発明の実施の形態１を示す冷媒回路図である。
【図２】実施の形態１の一回路の冷房能力増加時の冷媒の流れを示す冷媒回路図である。
【図３】実施の形態１の一回路の暖房能力増加時の冷媒の流れを示す冷媒回路図である。
【図４】実施の形態１の一回路の暖房運転を継続しながら熱源側熱交換器の除霜時の冷媒の流れを示す冷媒回路図である。
【図５】実施の形態１の冷房・暖房運転混在時に一回路の冷房能力増加時の冷媒の流れを示す冷媒回路図である。
【図６】実施の形態１の冷房・暖房運転混在時に一回路の暖房能力増加時の冷媒の流れを示す冷媒回路図である。
【図７】実施の形態１の冷媒回路図に油分離器を設置した場合の冷媒回路図である。
【図８】実施の形態１の冷媒回路図に液分離器を設置した場合の冷媒回路図である。
【図９】実施の形態１の冷媒回路をビルなどに設置した場合の一例を示す図である。
【図１０】この発明の実施の形態２を示す冷媒回路図である。
【図１１】この発明の実施の形態３を示す冷媒回路図である
【図１２】この発明の実施の形態４を示す冷媒回路図である
【図１３】実施の形態４の各冷媒回路が共通熱交換器を使用して蓄熱容器に氷を生成する場合の冷媒の流れを示す冷媒回路図である。
【図１４】実施の形態４の冷媒回路をビルなどに設置した場合の一例を示す図である。
【図１５】この発明の実施の形態５を示す冷媒回路図である。
【図１６】この発明の実施の形態６を示す冷媒回路図である。
【図１７】実施の形態６の空気調和装置の暖房運転と冷凍機器の能力増加時の冷媒の流れを示す冷媒回路図である。
【図１８】実施の形態６の空気調和装置の冷房運転と冷凍機器の能力増加時の冷媒の流れを示す冷媒回路図である。
【図１９】実施の形態６の冷媒回路を店舗などに設置した場合の一例を示す図である。
【図２０】この発明の実施の形態７を示す冷媒回路図である。
【図２１】従来の空気調和装置の冷媒回路図である。
【符号の説明】
Ａ，Ｂ 熱源側ユニット、Ｘ，Ｙ 負荷側ユニット、Ｕ 熱移動ユニット、１ａ，１ｂ，１ｃ 圧縮機及び加圧ポンプ、２ａ，２ｂ，２ｃ 四方弁及び冷暖切換弁、３ａ，３ｂ，３ｃ 熱源側熱交換器、４ａ，４ｂ，４ｃ 熱源側膨張機構、５ａ，５ｂ，５ｃ 負荷側熱交換器、６ａ，６ｂ，６ｃ 負荷側膨張機構、７，７−１，７−２，７−１ａ，７−１ｂ 共通熱交換器、７ａ，７ｂ，７ｃａ，７ｃｂ 共通熱交換器パス、８ａ，８ｂ 三方弁、９ｃ カスケード用膨張機構、１０ａ，１０ｂ，１０ｃ 吐出配管、１１ａ，１１ｂ，１１ｃ 熱源側ガス配管、１２ａ，１２ｂ，１２ｃ 負荷側ガス配管、１３ａ，１３ｂ，１３ｃ 熱源側液配管、１４ａ，１４ｂ，１４ｃ 負荷側液配管、１５ａ，１１５ｂ，１５ｃ吸入配管、１６ａ，１６ｂ 負荷側バイパス管、２１ａ，２１ｂ 油分離器、２２ａ，２２ｂ 液分離器、２３ 液溜め容器、２４ 蓄熱容器。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air conditioner.
[0002]
[Prior art]
FIG. 21 is an apparatus diagram of a conventional air-conditioning apparatus that includes a common heat exchanger and performs heat transfer between refrigerant circuits disclosed in, for example, Japanese Patent Laid-Open No. 7-318186.
[0003]
The circuit configuration will be described with reference to FIG. The air conditioning units 1 and 2 constitute refrigeration cycles A and B in which the outdoor unit 1 and the indoor units 6a, 6b, and 6c are connected in a ring shape, and the heat exchanger circuit C includes a refrigerant heat exchanger expansion valve EV1 and an air conditioning unit. The heat storage circuit D includes the heat storage tank expansion valve EV2 and the heat storage tank STR common to each of the air conditioning units 1 and 2, and the indoor heat exchanger 8 includes In contrast, a bypass circuit having a bypass valve BV2 is installed in parallel, the heat exchange circuit C is connected to the first two-way valve KV1 and the second two-way valve KV2, and the heat storage circuit D is connected to the third two-way valve. It connects between the outdoor side expansion valve 5 and indoor side expansion valve 7a, 7b, 7c of each air-conditioning unit 1 and 2 via KV3 and the 4th two-way valve KV4.
[0004]
Next, the operation will be described with reference to FIG.
When performing heat transfer between systems from the air conditioning unit 1 to the air conditioning unit 2 in daytime cooling operation, the refrigerant heat exchanger HE exits the outdoor heat exchanger 4 of the air conditioning unit 1 and then flows into the refrigerant heat exchanger HE. After exiting the outdoor heat exchanger 4 of the air conditioning unit 2 with the high-temperature and high-pressure liquid refrigerant, the low-temperature and low-pressure that is decompressed by the refrigerant heat exchanger expansion valve EV1 and evaporated in the second heat exchange section 13 of the refrigerant heat exchanger HE By exchanging heat with the two-phase refrigerant, heat transfer between the systems from the air conditioning unit 1 to the air conditioning unit 2 becomes possible.
That is, the degree of supercooling of the air conditioning unit 1 is increased by the excess cooling capacity of the air conditioning unit 2, the cooling capacity of the indoor units 6 a, 6 b, 6 c can be increased, and the cooling load of the air conditioning unit 1 can be handled.
[0005]
When performing heat transfer between systems from the air conditioning unit 1 to the air conditioning unit 2 during daytime heating operation, the refrigerant heat exchanger HE discharges the compressor 2 of the air conditioning unit 2 and then discharges the refrigerant heat exchanger via the first bypass valve BV1. Heat exchange is performed between the high-temperature and high-pressure gas refrigerant that has flowed into HE and the low-temperature and low-pressure two-phase refrigerant that has been decompressed by the indoor expansion valves 7a, 7b, and 7c of the air conditioning unit 1 and has flowed into the refrigerant heat exchanger HE. Heat transfer between the systems from the unit 2 to the air conditioning unit 1 becomes possible.
That is, the excess heating capacity in the air conditioning unit 2 is compensated for the increase in the evaporation capacity of the air conditioning unit 1, that is, the heating capacity can be increased, and the heating load of the air conditioning unit 1 can be dealt with.
[0006]
[Problems to be solved by the invention]
Since the conventional air conditioner is configured as described above, the heat transfer heat exchanger common to the plurality of refrigerant circuits is connected in parallel to the liquid pipe, so that a bypass circuit is required, and the bypass circuit Above this, there are a switching valve and an expansion mechanism, and a switching valve is also provided in the main liquid piping, so that there are problems that the cost is increased and that the refrigerant piping structure and control are complicated.
[0007]
In addition, the operation purpose of each refrigerant circuit is air conditioning, and the circuit having various purposes and the cascade use of heat are not assumed.
[0008]
In addition, when defrosting the heat source side heat exchanger of the refrigerant circuit having a large load during heating operation, the circuit side including the heat source side heat exchanger that wants to defrost the heat of the circuit having surplus capacity through the common heat exchanger It is not assumed that the defrosting is performed by moving to.
[0009]
The present invention has been made to solve the above-described problems, and realizes heat transfer between devices having different loads in a plurality of air conditioners and refrigeration devices to compensate for capacity and use heat efficiently. The object is to obtain an air conditioner that makes it possible.
[0010]
It is another object of the present invention to provide an air conditioner with reduced cost and simplified control by simplifying the circuit structure.
[0011]
It is another object of the present invention to provide an air conditioner that enables efficient heat utilization by leveling heat load and using heat cascade.
[0012]
Another object of the present invention is to provide an air conditioner that can be used for multipurpose use and heat cascade use assuming low temperature refrigeration equipment.
[0013]
Moreover, it aims at providing the air conditioning apparatus which can defrost a heat source side heat exchanger, continuing heating operation of a load side heat exchanger.
[0014]
It is another object of the present invention to provide a method for operating an air conditioner that can further increase the cooling capacity of a refrigerant circuit.
[0015]
Moreover, it aims at providing the operating method of the air conditioning apparatus which can enlarge the heating capability of a certain refrigerant circuit further.
[0016]
Moreover, it aims at providing the operating method of the air conditioning apparatus which can defrost the heat source side heat exchanger of a certain refrigerant circuit, continuing the heating operation which is heating operation.
[0017]
It is another object of the present invention to provide an operation method of an air conditioner capable of switching between a case where heat transfer is performed between refrigerant circuits and a case where heat transfer is not performed while each refrigerant circuit circulates refrigerant through a common heat exchanger. It is said.
[0018]
[Means for Solving the Problems]
An air conditioner according to the present invention includes a compressor or a refrigerant pump, a four-way valve or a cooling / heating switching valve, a heat source side heat exchanger, a heat source side expansion mechanism, a load side expansion mechanism, a load side heat exchanger, A plurality of refrigerant circuits configured by annularly connecting the four-way valve or cooling / heating switching valve and the compressor, and connected between a heat source side expansion mechanism and a load side expansion mechanism of the refrigerant circuit, Shared In addition, the refrigerant flows even when heat transfer is not performed between the refrigerant circuits. It is equipped with a common heat exchanger.
[0019]
Moreover, a bypass pipe for preventing the refrigerant from flowing through the load side heat exchanger and a three-way valve are provided.
[0020]
Moreover, the liquid storage part which stores an excess refrigerant | coolant is provided in the common heat exchanger.
[0021]
Moreover, it is provided with the heat storage container provided in the common heat exchanger and filled with the medium for performing heat storage and cold storage.
[0022]
Further, in at least one refrigerant circuit, a plurality of common heat exchangers are connected in series, and the plurality of common heat exchangers are shared separately and by any plurality of other refrigerant circuits.
[0023]
Further, a cascade expansion mechanism having the same action as that of the heat source side expansion mechanism and the load side expansion mechanism is disposed between the plurality of common heat exchangers.
[0024]
In addition, the plurality of refrigerant circuits include those used in air conditioning apparatuses, refrigeration apparatuses, refrigeration apparatuses, and the like.
[0025]
In the operation method of the air conditioner according to the present invention, when the cooling capacity of a certain refrigerant circuit that is performing cooling operation is further increased in a plurality of refrigerant circuits, the refrigerant is supplied to the common heat exchanger in a high-pressure state in a certain refrigerant circuit. In other refrigerant circuits with surplus capacity, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a low-pressure two-phase state, and the operating capacity of the compressor or refrigerant pump is adjusted. It controls heat transfer in the common heat exchanger.
[0026]
Further, when the heating capacity of a certain refrigerant circuit that is performing heating operation is further increased in a plurality of refrigerant circuits, in the certain refrigerant circuit, the refrigerant is circulated to the common heat exchanger in a low-pressure two-phase state and has a surplus capacity. In other refrigerant circuits, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a high-pressure state, and the heat transfer in the common heat exchanger is controlled by adjusting the operating capacity of the compressor or the refrigerant pump. Is.
[0027]
In addition, when defrosting a heat source side heat exchanger of a certain refrigerant circuit that is performing heating operation in a plurality of refrigerant circuits, in a certain refrigerant circuit, the refrigerant is circulated to the common heat exchanger in a low-pressure two-phase state, and the surplus In another capable refrigerant circuit, the refrigerant circulating in the common heat exchanger is circulated to the common heat exchanger in a high-pressure state, and the operating capacity of the compressor or refrigerant pump is adjusted so that the heat in the common heat exchanger is It controls movement.
[0028]
If heat transfer is not performed between the refrigerant circuits, , Make the expansion mechanism connected to both ends of the common heat exchanger almost the same Key When performing heat transfer between refrigerant circuits ,heat Expansion mechanism throttle connecting the expansion mechanism connected to both ends of the common heat exchanger of the refrigerant circuit whose capacity is increased by movement to both ends of the common heat exchanger of another refrigerant circuit having surplus capacity Be different from the condition Key And adjusting the operating capacity of the compressor or refrigerant pump.
[0029]
The air conditioner according to the present invention includes a compressor or a refrigerant pump, a four-way valve or a cooling / heating switching valve, a heat source side heat exchanger, and a heat source side expansion mechanism, and is common to the load side expansion mechanism. A heat transfer unit is configured from the heat exchanger, a load side unit is configured from the load side heat exchanger, and the annular circuit is formed by connecting the heat source side unit and the heat transfer unit and connecting the heat transfer unit and the load side unit. It is characterized by comprising.
[0030]
DETAILED DESCRIPTION OF THE INVENTION
Embodiment 1 FIG.
Hereinafter, an example of an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a refrigerant circuit diagram showing an example of an embodiment of the present invention.
In the figure, A and B are heat source side units, X and Y are load side units, U is a heat transfer unit, 1a and 1b are compressors and pressure pumps, 2a and 2b are four-way valves and cooling / heating switching valves, 3a and 3b. Is a heat source side heat exchanger, 4a and 4b are heat source side expansion mechanisms, 5a and 5b are load side heat exchangers, 6a and 6b are load side expansion mechanisms, 7 is a common heat exchanger, 7a and 7b are common heat exchangers Paths 10a and 10b are discharge pipes, 11a and 11b are heat source side gas pipes, 12a and 12b are load side gas pipes, 13a and 13b are heat source side liquid pipes, 14a and 14b are load side liquid pipes, and 15a and 15b are suction pipes. It is piping.
[0031]
The air conditioning apparatus of this invention WHEREIN: The cooling capacity increase method of a certain refrigerant circuit is demonstrated among the some refrigerant circuits which share one common heat exchanger.
In this case, in a certain refrigerant circuit that increases the cooling capacity, the refrigerant flowing through the common heat exchanger is hardly expanded by the heat source side expansion mechanism, becomes a high-pressure liquid state, flows to the common heat exchanger, and then expands on the load side. It is expanded by the mechanism to become a low-pressure two-phase flow to the load side heat exchanger.
[0032]
On the other hand, in another refrigerant circuit group having surplus capacity, the refrigerant flowing through the common heat exchanger is expanded by the heat source side expansion mechanism to be in a low-pressure two-phase state, and then flows to the common heat exchanger, and then the load side expansion mechanism With little expansion, it flows to the load-side heat exchanger, and the expansion mechanism is controlled in this way. Further, by controlling the expansion capacity of one or more compressors and refrigerant pumps as described above, Heat is transferred from the high-pressure liquid side of a circuit to the low-pressure two-phase side of another circuit group, thereby increasing the degree of supercooling of the high-pressure liquid of a circuit and increasing the cooling capacity.
[0033]
Next, the operation for increasing the cooling capacity of a certain refrigerant circuit during the cooling operation will be described with reference to the refrigerant circuit diagram of FIG.
It is assumed that the refrigerant circuit 1 further increases the cooling capacity such as a high required operating load, and the refrigerant circuit 2 has a surplus capacity such as a low required operating load.
During this operation, the heat source side heat exchangers 3a and 3b operate as a condenser, the load side heat exchangers 5a and 5b operate as an evaporator, and the four-way valves 2a and 2b are controlled as a cooling mode.
The heat source side expansion mechanism 4a hardly expands the refrigerant, and the heat source side expansion mechanism 4b sets the outlet supercooling temperature of the heat source side heat exchanger 3b or the outlet superheat temperature of the load side heat exchanger 5b to a target value. The load side expansion mechanism 6a is adjusted so that the outlet supercooling temperature of the heat source side heat exchanger 3a or the outlet superheat temperature of the load side heat exchanger 5a becomes a target value, and the load side expansion mechanism 6b It is adjusted so that it hardly expands.
[0034]
Next, the flow of the refrigerant will be described with reference to FIG.
In the refrigerant circuit 1, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1a flows into the heat source side heat exchanger 3a through the discharge pipe 10a, the four-way valve 2a, and the heat source side gas pipe 11a. Heat exchange with ambient air cools and liquefies. The liquefied refrigerant flows through the heat source side expansion mechanism 4a through the heat source side liquid pipe 13a on the way, but here flows into the common heat exchanger 7 in a high pressure liquid state with almost no pressure reduction, and here the refrigerant circuit Heat exchange with the low-temperature low-pressure refrigerant on the second side lowers the high-pressure liquid temperature. Thereafter, the pressure is reduced by the load-side expansion mechanism 6a and flows into the load-side heat exchanger 5a via the load-side liquid pipe 14a, where it is heat-exchanged with the load-side ambient air and heated and gasified. The gasified refrigerant returns to the compressor 1a via the load side gas pipe 12a, the four-way valve 2a, and the suction pipe 15a.
[0035]
On the other hand, in the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1b flows into the heat source side heat exchanger 3b via the discharge pipe 10b, the four-way valve 2b, and the heat source side gas pipe 11b. It is cooled and liquefied by heat exchange with the surrounding ambient air. The liquefied refrigerant is decompressed by the heat source side expansion mechanism 4b through the heat source side liquid pipe 13b and flows into the common heat exchanger 7 in the middle. Here, heat is exchanged with the high-pressure liquid refrigerant on the refrigerant circuit 1 side, and it is heated and partially gasified. Thereafter, the refrigerant flows through the load-side expansion mechanism 6b, but here flows into the load-side heat exchanger 5b via the load-side liquid pipe 14b without being almost depressurized, and is exchanged with the ambient air on the load side for gasification. To do. The gasified refrigerant returns to the compressor 1b via the load side gas pipe 12b, the four-way valve 2b, and the suction pipe 15b.
[0036]
In the air conditioner of the present invention, a heating capacity increasing method for a certain refrigerant circuit among a plurality of refrigerant circuits sharing one common heat exchanger will be described.
In this case, in a refrigerant circuit that increases the heating capacity, the refrigerant that circulates through the common heat exchanger is expanded by the load-side expansion mechanism and depressurized to be in a low-pressure two-phase state, and circulates to the common heat exchanger. It exchanges heat with the high-pressure refrigerant that circulates, and evaporates to gasify. Thereafter, the heat source side expansion mechanism is hardly expanded and flows to the heat source side heat exchanger. Here, the evaporation action in the heat source side heat exchanger is adjusted according to the state of the low-pressure refrigerant.
[0037]
On the other hand, in other refrigerant circuit groups having surplus capacity, the refrigerant flowing through the common heat exchanger is hardly expanded by the load-side expansion mechanism and becomes a high-pressure gas, two-phase or liquid state depending on the load condition, and is transferred to the common heat exchanger. The heat is exchanged with the low-pressure two-phase refrigerant flowing through the refrigerant circuit described above, and condensed to become a high-pressure liquid. After that, it is expanded by the heat source side expansion mechanism, depressurized, and flows to the heat source side heat exchanger.
[0038]
Further, a circuit in which heat is transferred from the high-pressure refrigerant side of another circuit group to the low-pressure two-phase side of a circuit by adjusting the expansion mechanism control and the operation capacity of one or more compressors and refrigerant pumps. The heating capacity is increased by increasing the refrigerant circulation amount by increasing the compressor suction density and increasing the compressor operation efficiency by increasing the low pressure of the compressor.
[0039]
Next, the operation for increasing the heating capacity of a certain refrigerant circuit during the heating operation will be described with reference to FIG. It is assumed that the refrigerant circuit 1 further increases the heating capacity such as a high required operating load, and the refrigerant circuit 2 has a surplus capacity such as a low required operating load.
During this operation, the heat source side heat exchangers 3a and 3b operate as an evaporator, the load side heat exchangers 5a and 5b operate as a condenser, the four-way valves 2a and 2b are controlled as a heating mode, and the heat source side expansion mechanism 4a The heat source side expansion mechanism 4b is adjusted so that the outlet superheat temperature of the heat source side heat exchanger 3b or the outlet subcooling temperature of the load side heat exchanger 5b becomes a target value so that the refrigerant hardly expands. The expansion mechanism 6a is adjusted so that the outlet superheat temperature of the heat source side heat exchanger 3a or the outlet supercooling temperature of the load side heat exchanger 5a becomes a target value, and the load side expansion mechanism 6b hardly expands the refrigerant. Is done.
[0040]
Next, the flow of the refrigerant will be described with reference to FIG.
In the refrigerant circuit 1, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1a flows into the load-side heat exchanger 3a via the discharge pipe 10a, the four-way valve 2a, and the load-side gas pipe 12a. Heat exchange with ambient air cools and liquefies.
The liquefied refrigerant is decompressed by the load-side expansion mechanism 6a via the load-side liquid pipe 14a and flows into the common heat exchanger 7 where it is heat-exchanged with the high-temperature and high-pressure refrigerant on the refrigerant circuit 2 side and heated. Partly evaporates.
Thereafter, the heat source side expansion mechanism 4a flows into the heat source side heat exchanger 3a through the heat source side liquid pipe 13a without being depressurized, and is heat-exchanged with the ambient air on the heat source side to be heated and gasified. The gasified refrigerant returns to the compressor 1a via the heat source side gas pipe 11a, the four-way valve 2a, and the suction pipe 15a.
[0041]
In the common heat exchanger 7, when the amount of heat generated by heat exchange with the high-temperature and high-pressure refrigerant on the refrigerant circuit 2 side is large and evaporated to become superheated gas, the heat source side expansion mechanism 4a is not almost decompressed thereafter. After flowing into the heat source side heat exchanger 3a through the heat source side liquid pipe 13a, the fan of 3a is stopped to prevent heat exchange with the ambient air on the heat source side as much as possible, and then the heat source side gas pipe 11a, four-way Control is performed so as to return to the compressor 1a via the valve 2a and the suction pipe 15a.
[0042]
On the other hand, in the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1b flows into the load-side heat exchanger 5b via the discharge pipe 10b, the four-way valve 2b, and the load-side gas pipe 12b. After being cooled by exchanging heat with the surrounding ambient air, it flows through the load-side expansion mechanism 6b via the load-side liquid piping 14b, but flows into the common heat exchanger 7 with almost no pressure reduction. Here, heat is exchanged with the low-pressure refrigerant on the refrigerant circuit 1 side, and the refrigerant is cooled to become a high-pressure liquid.
[0043]
Thereafter, the pressure is reduced by the heat source side expansion mechanism 4b and flows into the heat source side heat exchanger 3b via the heat source side liquid pipe 13b, where it is heat exchanged with the ambient air on the heat source side and gasified. The gasified refrigerant returns to the compressor 1b via the heat source side gas pipe 11b, the four-way valve 2b, and the suction pipe 15b.
[0044]
Next, in the air conditioner of the present invention, a method of defrosting a heat source side heat exchanger of a certain refrigerant circuit among a plurality of refrigerant circuits sharing one common heat exchanger while continuing the heating operation will be described.
In this case, in a certain circuit including a heat source side heat exchanger for defrosting, the refrigerant flowing through the common heat exchanger is expanded by the load side expansion mechanism to be in a low pressure two-phase state, and then flows to the common heat exchanger. It circulates to the heat source side heat exchanger while being hardly expanded by the heat source side expansion mechanism.
[0045]
On the other hand, in another circuit group having surplus capacity, the refrigerant flowing through the common heat exchanger is hardly expanded by the load-side expansion mechanism, becomes a high-pressure liquid, a gas and a two-phase state, and flows to the common heat exchanger. It is expanded by the heat source side expansion mechanism to become a low pressure two-phase and flows to the heat source side heat exchanger.
[0046]
Furthermore, by controlling the expansion mechanism and adjusting the operating capacity of one or more compressors and refrigerant pumps, the high-pressure liquid, gas, and heat of the two-phase side of another circuit group are transferred to the low-pressure, two-phase side of a circuit. After moving the refrigerant state at the common heat exchanger outlet of a circuit to a low pressure gas with a large degree of superheat, it is circulated to the heat source side heat exchanger and condensed there to defrost the heat source side heat exchanger To do.
[0047]
Next, an operation when a certain refrigerant circuit in the heating operation defrosts the heat source side heat exchanger while continuing the heating operation will be described based on FIG.
It is assumed that the refrigerant circuit 1 has a heat source side heat exchanger that desires defrosting, and the refrigerant circuit 2 has a surplus capacity such as a heating operation and a low required operation load.
Since the operation during this operation is the same as the case where the heating capacity of a certain circuit is increased by using the surplus capacity of another circuit, a detailed description of the operation is omitted.
[0048]
Next, the flow of the refrigerant will be described with reference to FIG.
In the refrigerant circuit 1, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1a flows into the load-side heat exchanger 5a via the discharge pipe 10a, the four-way valve 2a, and the load-side gas pipe 12a. Heat exchange with ambient air cools and liquefies. The liquefied refrigerant is decompressed by the load-side expansion mechanism 6a via the load-side liquid pipe 14a and flows into the common heat exchanger 7 where it is heat-exchanged with the high-temperature and high-pressure refrigerant on the refrigerant circuit 2 side.
[0049]
At this time, after being heated and evaporated with a larger amount of heat exchange than in the heating capacity increasing operation and becoming a low pressure gas having a large degree of superheat, the heat source side expansion mechanism 4a is hardly decompressed and the heat source side liquid piping 13a. It flows into the heat source side heat exchanger 3a which desires defrosting. Here, the fan of the heat source side heat exchanger 3a is stopped, and the low-pressure gas refrigerant having a large superheat degree is cooled and partially liquefied by heat exchange with the tubes and fins of the heat source side heat exchanger 3a. The partially liquefied low-pressure gas refrigerant returns to the compressor 1a through the heat source side gas pipe 11a, the four-way valve 2a, and the suction pipe 15a.
[0050]
On the other hand, in the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1b flows into the load-side heat exchanger 5b via the discharge pipe 10b, the four-way valve 2b, and the load-side gas pipe 12b. After being cooled by exchanging heat with the surrounding ambient air, it flows through the load-side expansion mechanism 6b via the load-side liquid piping 14b, but flows into the common heat exchanger 7 with almost no pressure reduction. Here, heat is exchanged with the low-pressure refrigerant on the refrigerant circuit 1 side, and the refrigerant is cooled to become a high-pressure liquid.
[0051]
Thereafter, the pressure is reduced by the heat source side expansion mechanism 4b and flows into the heat source side heat exchanger 3b via the heat source side liquid pipe 13b, where it is heat exchanged with the ambient air on the heat source side and gasified. The gasified refrigerant returns to the compressor 1b through the heat source side gas pipe 11b, the four-way valve 2b, and the suction pipe 15b.
[0052]
Next, when cooling operation and heating operation are mixed, the operation when the cooling capacity of the refrigerant circuit that is performing the cooling operation is increased will be described with reference to FIG.
It is assumed that the refrigerant circuit 1 is in a cooling operation and the cooling capacity is further increased, for example, the required operating load is high, and the refrigerant circuit 2 is in a heating operation, and has a surplus capacity, such as a low required operating load.
During this operation, the heat source side heat exchanger 3a and the load side heat exchanger 5b operate as a condenser, the load side heat exchanger 5a and the heat source side heat exchanger 3b operate as an evaporator, the four-way valve 2a operates in a cooling mode, four-way The valve 2b is controlled as a heating mode, the heat source side expansion mechanisms 4a and 4b hardly expand the refrigerant, and the load side expansion mechanism 6a is an outlet subcooling temperature of the heat source side heat exchanger 3a or a load side heat exchanger. The load-side expansion mechanism 6b is adjusted so that the outlet superheat temperature of the heat source side heat exchanger 3b or the outlet supercooling temperature of the load side heat exchanger 5b becomes the target value. Adjusted to
[0053]
Next, the flow of the refrigerant will be described with reference to FIG.
In the refrigerant circuit 1, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1a flows into the heat source side heat exchanger 3a through the discharge pipe 10a, the four-way valve 2a, and the heat source side gas pipe 11a. Heat exchange with ambient air cools and liquefies. The liquefied refrigerant flows through the heat source side expansion mechanism 4a through the heat source side liquid pipe 13a on the way, but here flows into the common heat exchanger 7 in a high pressure liquid state with almost no pressure reduction, and here the refrigerant circuit Heat exchange with the low-temperature low-pressure refrigerant on the second side lowers the high-pressure liquid temperature.
[0054]
Thereafter, the pressure is reduced by the load-side expansion mechanism 6a and flows into the load-side heat exchanger 5a via the load-side liquid pipe 14a, where it is heat-exchanged with the load-side ambient air and heated and gasified. The gasified refrigerant returns to the compressor 1a via the load side gas pipe 12a, the four-way valve 2a, and the suction pipe 15a.
[0055]
On the other hand, in the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1b flows into the load-side heat exchanger 5b via the discharge pipe 10b, the four-way valve 2b, and the load-side gas pipe 12b. After being exchanged with the surrounding ambient air and cooled, the pressure is reduced by the load side expansion mechanism 6 b via the load side liquid pipe 14 b and flows into the common heat exchanger 7. Here, heat is exchanged with the high-pressure liquid refrigerant on the refrigerant circuit 1 side, heated and partially gasified, and then circulates through the heat source side expansion mechanism 4b, but is hardly decompressed here, via the heat source side liquid pipe 13b. Then, it flows into the heat source side heat exchanger 3b, where it is exchanged with the ambient air on the heat source side and gasified. The gasified refrigerant returns to the compressor 1b via the heat source side gas pipe 11b, the four-way valve 2b, and the suction pipe 15b.
[0056]
Next, when cooling operation and heating operation are mixed, the operation when increasing the heating capacity of the refrigerant circuit that is performing the heating operation will be described with reference to FIG.
It is assumed that the refrigerant circuit 1 is in a heating operation and the heating capacity is further increased, for example, the required operation load is high, and the refrigerant circuit 2 is in a cooling operation, and has a surplus capacity, such as a low in required operation load.
During this operation, the heat source side heat exchanger 3a and the load side heat exchanger 5b operate as an evaporator, the load side heat exchanger 5a and the heat source side heat exchanger 3b operate as a condenser, the four-way valve 2a operates in a heating mode, four-way The valve 2b is controlled as a cooling mode, the heat source side expansion mechanisms 4a and 4b hardly expand the refrigerant, and the load side expansion mechanism 6a is the outlet subcooling temperature of the load side heat exchanger 5a or the heat source side heat exchanger. 3a is adjusted so that the outlet superheat temperature becomes a target value, and the load side expansion mechanism 6b is set so that the outlet superheat temperature of the load side heat exchanger 5b or the outlet supercooling temperature of the heat source side heat exchanger 3b becomes the target value. Adjusted to
[0057]
Next, the flow of the refrigerant will be described with reference to FIG.
In the refrigerant circuit 1, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1a flows into the load-side heat exchanger 5a via the discharge pipe 10a, the four-way valve 2a, and the load-side gas pipe 12a. Heat exchange with ambient air cools and liquefies. The liquefied refrigerant is decompressed by the load-side expansion mechanism 6a via the load-side liquid pipe 14a and flows into the common heat exchanger 7 where it is heat-exchanged with the high-temperature and high-pressure refrigerant on the refrigerant circuit 2 side and heated. Partly evaporates.
[0058]
Thereafter, the heat source side expansion mechanism 4a flows into the heat source side heat exchanger 3a via the heat source side liquid pipe 13a without being depressurized, where it is heat exchanged with the ambient air on the load side to be heated and gasified. The gasified refrigerant returns to the compressor 1a via the heat source side gas pipe 11a, the four-way valve 2a, and the suction pipe 15a. In the common heat exchanger 7, the amount of heat generated by heat exchange with the high-temperature and high-pressure refrigerant on the refrigerant circuit 2 side is large, and the refrigerant that has been evaporated to become a heated gas is not reduced in pressure by the heat source side expansion mechanism 4a. After flowing into the heat source side heat exchanger 3a through the heat source side liquid pipe 13a, the fan of 3a is stopped to prevent heat exchange with the ambient air on the heat source side as much as possible, and then the heat source side gas pipe 11a, four-way Control is performed so as to return to the compressor 1a via the valve 2a and the suction pipe 15a.
[0059]
On the other hand, in the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1b flows into the heat source side heat exchanger 3b via the discharge pipe 10b, the four-way valve 2b, and the heat source side gas pipe 11b. It is cooled and liquefied by heat exchange with the surrounding ambient air. The liquefied refrigerant flows through the heat source side expansion mechanism 4b through the heat source side liquid pipe 13b, but flows into the common heat exchanger 7 without being depressurized here. Here, heat is exchanged with the low-pressure refrigerant on the refrigerant circuit 1 side, and the liquid temperature is lowered by cooling. Thereafter, the pressure is reduced by the load-side expansion mechanism 6b and flows into the load-side heat exchanger 5b via the load-side liquid pipe 14b, where it is heat-exchanged with ambient air on the load side and gasified. The gasified refrigerant returns to the compressor 1b via the load side gas pipe 12b, the four-way valve 2b, and the suction pipe 15b.
[0060]
Next, in the air-conditioning apparatus of the present invention, among a plurality of refrigerant circuits sharing one common heat exchanger, heat transfer is performed and not performed from one circuit to another through the common heat exchanger. The driving method will be described.
In the case where heat transfer is not performed, in all circuits, for example, the expansion mechanism connected to both ends of the common heat exchanger is adjusted to have substantially the same degree of throttling, and each circuit that circulates the common heat exchanger is adjusted. Avoid temperature difference between refrigerants.
On the other hand, for example, when performing heat transfer, adjustment is made such that the expansion of the expansion mechanism of the circuit whose capacity is increased by heat transfer is different from the expansion of the expansion mechanism of another circuit group having surplus capacity. Thus, in the refrigerant flowing through the common heat exchanger, heat transfer is facilitated by adding a temperature difference between the refrigerant of the circuit whose heat is transferred to increase the capacity and the refrigerant of the other circuit group supplying the heat. Or the operation capacity | capacitance of the compressor and refrigerant | coolant pump more than that is adjusted, the refrigerant | coolant flow volume distribute | circulated through the common heat exchanger is adjusted, and the amount of heat transfer is controlled.
[0061]
In this embodiment, as shown in FIG. 7, oil separators 21a and 21b are installed in the middle of the discharge pipes 10a and 10b, or as shown in FIG. 8, the liquid separator 22a is placed in the middle of the suction pipes 15a and 15b. , 22b, the basic operation and refrigerant flow are the same as when there is no oil separator or liquid separator.
[0062]
As described above, in the first embodiment, one common heat exchanger having an expansion mechanism at both ends is shared by a plurality of refrigerant circuits, thereby enabling heat transfer between the plurality of refrigerant circuits. It is possible to supplement the capacity from a plurality of refrigerant circuit groups having surplus capacity for the refrigerant circuit that has insufficient maximum capacity for the required operating load in both operations.
[0063]
In addition, the adjustment of the amount of heat transfer is performed by adjusting the temperature difference between the high-pressure refrigerant and the low-pressure refrigerant that exchange heat in the common heat exchanger by the control of the heat source side expansion mechanism and the load side expansion mechanism provided in each refrigerant circuit. It is also possible to provide an air conditioner that adjusts the compressor capacity of a plurality of refrigerant circuit groups having surplus capacity, thereby adjusting the amount of refrigerant circulating in the circuit and controlling the amount of heat that moves between refrigerant circuits.
[0064]
An example in which the first embodiment is applied to a building or the like is shown in FIG. The X1, X2, Y1, and Y2 rooms are rooms on one floor of a building. An indoor unit is installed in each room, the X1 and X2 indoor units are connected to the outdoor unit A to form one refrigerant circuit, and the Y1 and Y2 indoor units are connected to the outdoor unit B to form one refrigerant circuit. To do. Each refrigerant circuit compensates for the shortage of each other through a common heat exchanger.
[0065]
Embodiment 2. FIG.
FIG. 10 is a refrigerant circuit diagram showing another example of the embodiment of the present invention.
Three-way valves 8a and 8b and load-side bypass pipes 16a and 16b are added to the refrigerant circuit of the first embodiment shown in FIG.
[0066]
In FIG. 10, three-way valves 8a and 8b and load-side bypass pipes 16a and 16b do not use a full-load-side heat exchanger in one refrigerant circuit, and a common heat exchanger for increasing the capacity of other refrigerant circuits. In the case of supplying heat via the refrigerant, the bypass pipe is circulated instead of the refrigerant flowing through the load side heat exchanger.
[0067]
In this embodiment, when the refrigerant is circulated through the bypass pipe, the common heat exchanger functions as a main condenser and evaporator in the refrigerant circuit.
[0068]
In this embodiment, by providing a bypass pipe and a three-way valve for preventing the refrigerant from flowing through the load-side heat exchanger group, the refrigerant circuit having no load-side operation requirement can be operated to supplement the capacity of other refrigerant circuits. In this case, it is possible to provide an air conditioner that eliminates the noise problem caused by the refrigerant flow to the stop load heat exchanger by not allowing the refrigerant to flow through the stop load heat exchanger. Even if the refrigerant of the stopped load heat exchanger is stopped and the refrigerant is circulated without using this bypass, the same effect can be obtained although there is some heat loss.
[0069]
Embodiment 3 FIG.
FIG. 11 is a refrigerant circuit diagram showing another example of the embodiment of the present invention.
The common heat exchanger of Embodiment 1 is provided with a liquid storage part for storing excess refrigerant. Reference numeral 23 denotes a liquid storage container, and reference numerals 23a and 23b denote liquid storage parts of the respective refrigerant circuits.
[0070]
By using the liquid storage container 23, surplus refrigerant in each circuit can be stored here, so that the liquid storage container in each refrigerant circuit can be removed to provide an air conditioner that enables cost reduction. to enable. In addition, since the heat transfer method and the flow of the refrigerant in this embodiment are the same as those in Embodiment 1, the description thereof is omitted.
[0071]
Embodiment 4 FIG.
FIG. 12 is a refrigerant circuit diagram showing another example of the embodiment of the present invention.
The heat storage container 24 filled with the medium for performing heat storage and cold storage provided in the common heat exchanger of Embodiment 1 is added.
[0072]
By adding the heat storage container 24, it is possible for each circuit to generate ice using inexpensive power such as late-night power, and to use this to supplement the capacity when there is a great demand for cooling operation during the daytime. . At the same time, needless to say, it is possible to supplement the capacity deficiency circuit described in the first embodiment from other circuits.
[0073]
The refrigerant flow and the basic heat transfer method in the common heat exchanger are the same as those in the first embodiment. Here, an example in which water is used for the refrigerant storage body, ice is generated with midnight power, and the cooling operation is performed using the ice in the daytime will be described with reference to FIG.
[0074]
When both the refrigerant circuit 1 and the refrigerant circuit 2 have low electricity costs and a small cooling operation load, such as at night, the common heat exchanger 7 is an evaporator, the heat source side heat exchangers 3a and 3b are condensers, and the load side heat exchanger Operates only as a heat exchanger having a cooling operation request as an evaporator, the four-way valves 2a and 2b are controlled in a cooling mode, and the heat source side expansion mechanisms 4a and 4b are at the outlet subcooling temperatures of the heat source side heat exchangers 3a and 3b. Alternatively, the temperature of the refrigerant flowing through the load-side heat exchangers 5a and 5b or the common heat exchanger 7 is adjusted to a target value, and the load-side expansion mechanisms 6a and 6b are adjusted so as to hardly expand, The operating capacity is adjusted based on the amount of ice generated in the heat storage container 24.
[0075]
Next, how the refrigerant flows will be described with reference to FIG.
In the refrigerant circuit 1 and the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressors 1a and 1b exchanges heat source side heat via the discharge pipes 10a and 10b, the four-way valves 2a and 2b, and the heat source side gas pipes 12a and 12b. It flows into the containers 3a and 3b, where it is heat-exchanged with the ambient air on the heat source side and cooled and liquefied. The liquefied refrigerant flows through the heat source side expansion mechanisms 4a and 4b through the heat source side liquid piping in the middle, and is decompressed here and flows into the common heat exchanger 7 while maintaining the low pressure two-phase, where it stays in the heat storage container 24. Heat is exchanged with the water that is being used to turn the water into ice.
[0076]
Thereafter, the load-side expansion mechanisms 6a and 6b are hardly decompressed and flow into the load-side heat exchangers 5a and 5b via the load-side liquid pipes 14a and 14b, where they are exchanged with the load-side ambient air. It is heated and gasified. The gasified low-pressure refrigerant returns to the compressors 1a and 1b via the load side gas pipes 12a and 12b, the four-way valves 2a and 2b, and the suction pipes 15a and 15b.
[0077]
On the other hand, when the cooling operation load is large both in the daytime and in the refrigerant circuit 1 and the refrigerant circuit 2, the common heat exchanger 7 passing through the heat storage container 24 in the ice state is replaced by the subcooler, the heat source side heat exchangers 3a, 3b. The condensers and the load side heat exchangers 5a and 5b operate as evaporators, the four-way valves 2a and 2b are controlled in the cooling mode, and the load side expansion mechanisms 6a and 6b are connected to the outlets of the heat source side heat exchangers 3a and 3b. The cooling temperature or the temperature of the refrigerant flowing through the load side heat exchangers 5a and 5b or the common heat exchanger 7 is adjusted to a target value, and the heat source side expansion mechanisms 4a and 4b are adjusted so as to hardly expand, The operating capacity of the circuit is adjusted based on the capacity required by the load side.
[0078]
As described above, in the fourth embodiment, by adding a heat storage container to the circuit of the first embodiment, for example, ice is generated using late-night power, and the cooling capacity is compensated when there is much cooling demand in the daytime. By doing so, it will be possible to provide an air-conditioning device that can achieve capacity filling at the time of capacity shortage by heat storage and cold storage, such as preventing capacity shortages and reducing electricity costs for operation.
[0079]
An example in which the fourth embodiment is applied to a building or the like is shown in FIG. The X1, X2, Y1, and Y2 rooms are rooms on one floor of a building. An indoor unit is installed in each room, the X1 and X2 indoor units are connected to the outdoor unit A to form one refrigerant circuit, and the Y1 and Y2 indoor units are connected to the outdoor unit B to form one refrigerant circuit. To do. Each refrigerant circuit creates ice in the heat storage container using inexpensive electricity such as late-night electricity and performs cooling operation using ice in the daytime, while also supplementing each other's insufficient capacity through a common heat exchanger Do.
[0080]
Embodiment 5 FIG.
FIG. 15 is a refrigerant circuit diagram showing another example of the embodiment of the present invention.
The common heat exchanger 7 of the refrigerant circuit of Embodiment 1 is divided into 7-1 and 7-2, and each is shared with a separate circuit.
[0081]
Since the heat transfer method and the refrigerant flow in this embodiment are the same as those in the first embodiment, the description thereof is omitted.
[0082]
In this embodiment, one refrigerant circuit includes a plurality of common heat exchangers, and each common heat exchanger performs heat transfer with a separate refrigerant circuit, thereby performing heat transfer via the plurality of refrigerant circuits. It is possible to provide an air conditioner that can efficiently use heat of the entire system by using heat cascade.
[0083]
Embodiment 6 FIG.
FIG. 16 is a refrigerant circuit diagram showing another example of the embodiment of the present invention.
The expansion mechanism 9c for cascade is provided between the common heat exchangers of the refrigerant circuit of Embodiment 5.
[0084]
Next, an operation example when a circuit including a plurality of common heat exchangers connected to the expansion mechanisms at both ends increases the heating capacity of other low-temperature refrigeration circuits and air-conditioning circuits will be described with reference to FIG. .
The refrigerant circuit 1 is a low-temperature refrigeration circuit that requires an increase in cooling capacity, the refrigerant circuit 2 is an air-conditioning circuit that requires an increase in heating capacity, and the refrigerant circuit 3 performs a heating operation on the load side, while the refrigerant circuit 1 Suppose that the increase in capacity of 2 is compensated.
[0085]
In the refrigerant circuit 1, the heat source side heat exchanger 3a operates as a condenser, the load side heat exchanger 5a operates as an evaporator, the four-way valve 2a is controlled in a cooling mode, and the heat source side expansion mechanism 4a hardly expands the refrigerant. Thus, the load side expansion mechanism 6a is expanded and adjusted so that the outlet supercooling temperature of the heat source side heat exchanger 3a or the outlet superheat temperature of the load side heat exchanger 5a becomes a target value.
[0086]
In the refrigerant circuit 2, the heat source side heat exchanger 3b operates as an evaporator, the load side heat exchanger 5b operates as a condenser, the four-way valve 2b is controlled as a heating mode, and the load side expansion mechanism 6b expands the refrigerant. Then, the outlet supercooling temperature of the load side heat exchanger 5b or the outlet superheat temperature of the heat source side heat exchanger 3b is adjusted so as to become a target value, and the heat source side expansion mechanism 4b is adjusted so as to hardly expand. The
[0087]
In the refrigerant circuit 3, when the load side heat exchanger 5c is operated as a condenser and the heat source side heat exchanger 3c is operated as an evaporator, and the four-way valve 2c is set in the heating mode, the heat source side expansion mechanism 4c and the load side expansion mechanism 6c are The expansion mechanism 9c for the cascade is adjusted so that the refrigerant is hardly expanded and the outlet supercooling temperature of the load side heat exchanger 5c or the outlet superheat temperature of the heat source side heat exchanger 3c becomes a target value.
[0088]
Next, the flow of the refrigerant will be described with reference to FIG.
In the refrigerant circuit 1, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1a flows into the heat source side heat exchanger 3a through the discharge pipe 10a, the four-way valve 2a, and the heat source side gas pipe 11a. The heat source side expansion mechanism 4a is circulated through the heat source side liquid piping in the high pressure gas or two-phase state with almost no heat exchange, but here the high pressure gas or two-phase state remains almost without decompression. It flows into the common heat exchanger 7-1. Here, heat is exchanged with the low-pressure two-phase refrigerant flowing through the common heat exchanger 7-1 on the refrigerant circuit 3 side to condense into a high-pressure liquid.
[0089]
Thereafter, the pressure is reduced by the load-side expansion mechanism 6a and flows into the load-side heat exchanger 5a via the load-side liquid pipe 14a, where it is heat-exchanged with the load-side ambient air and heated and gasified. The gasified refrigerant returns to the compressor 1a via the load side gas pipe 12a, the four-way valve 2a, and the suction pipe 15a.
[0090]
On the other hand, in the refrigerant circuit 2, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1b flows into the load-side heat exchanger 3b via the discharge pipe 10b, the four-way valve 2b, and the load-side gas pipe 12b. It is cooled and liquefied by heat exchange with the surrounding ambient air. The liquefied refrigerant is depressurized by the load side expansion mechanism 6b via the load side liquid pipe 14b and becomes a low pressure two-phase state and flows into the common heat exchanger 7-2. Here, heat is exchanged with the high-pressure liquid refrigerant flowing through the common heat exchanger 7-2 of the refrigerant circuit 3 to evaporate and partially gasify.
[0091]
After that, it flows through the heat source side expansion mechanism 4b, but here flows into the heat source side heat exchanger 3b through the load side liquid pipe 13b without being depressurized. Here, the gas flow is controlled by adjusting the fan air volume according to the low-pressure refrigerant state to control the evaporation action. The gasified low-pressure refrigerant returns to the compressor 1b via the heat source side gas pipe 11b, the four-way valve 2b, and the suction pipe 15b.
[0092]
On the other hand, in the refrigerant circuit 3, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1c flows into the load-side heat exchanger 5c via the discharge pipe 10c, the four-way valve 2c, and the load-side gas pipe 12c. After the heat is exchanged with the surrounding air on the side and cooled, it flows through the load-side expansion mechanism 6c via the load-side liquid piping 14c. Here, the common heat exchanger 7- Into 2. Here, heat is exchanged with the low-pressure two-phase refrigerant on the refrigerant circuit 2 side, and the refrigerant is cooled to become a high-pressure liquid.
[0093]
Thereafter, the pressure is reduced by the expansion mechanism 9c for the cascade to become a low pressure two-phase state and flows into the common heat exchanger 7-1. Here, heat is exchanged with the high-pressure liquid refrigerant on the refrigerant circuit 2 side, and the gas is partially gasified. After that, the refrigerant flows into the heat source side expansion mechanism 4c, but is hardly decompressed here, and flows into the heat source side heat exchanger 3c via the heat source side liquid pipe 13c, where it is exchanged with the ambient air on the heat source side to be gas. Turn into. The gasified refrigerant returns to the compressor 1c via the heat source side gas pipe 11c, the four-way valve 2c, and the suction pipe 15c.
[0094]
Thus, the refrigerant circuit having a small load and including a plurality of common heat exchangers can compensate for the cooling operation and heating operation capabilities of other circuits.
[0095]
Similarly, a circuit having a plurality of common heat exchangers can increase the cooling capacity of other low-temperature refrigeration circuits and air-conditioning circuits. Hereinafter, a description will be given based on FIG.
[0096]
The refrigerant circuit 1 is a low-temperature refrigeration circuit that requires an increase in cooling capacity, the refrigerant circuit 2 is an air-conditioning circuit that requires an increase in cooling capacity, and the refrigerant circuit 3 performs heating operation on the load side, while the refrigerant circuit 1 Suppose that the increase in capacity of 2 is compensated.
A detailed description of the cooling and heating operation will be omitted, and only the points will be described here. In the refrigerant circuit 1, the heat source side expansion mechanism 4 a hardly expands the refrigerant, and the load side expansion mechanism 6 a targets the outlet supercooling temperature of the heat source side heat exchanger 3 a or the outlet superheat temperature of the load side heat exchanger 5 a. When the amount of heat exchange with the outside air in the heat source side heat exchanger 3a is minimized, the refrigerant flowing through the common heat exchanger 7-1 is a high-pressure gas or a two-phase state. When the amount of heat exchange with the outside air in the heat source side heat exchanger 3a is large, the refrigerant flowing through the common heat exchanger 7-1 is adjusted to be in a high-pressure two-phase or liquid state.
[0097]
The common heat exchanger 7-1 exchanges heat with the low-pressure two-phase refrigerant flowing through the common heat exchanger 7-1 of the refrigerant circuit 3, and the refrigerant flowing through the common heat exchanger 7-1 of the refrigerant circuit 1 is cooled. Liquefaction. On the other hand, since the temperature of the refrigerant flowing through the common heat exchanger 7-1 of the refrigerant circuit 3 is low, the condensation temperature of the refrigerant circuit 1 is lowered, and as a result, a low-temperature evaporation temperature can be generated. It becomes possible to add a circuit to a circuit group.
[0098]
In the refrigerant circuit 2, the heat source side expansion mechanism 4b hardly expands the refrigerant, and the load side expansion mechanism 6b has a target of the outlet supercooling temperature of the heat source side heat exchanger 3b or the outlet superheat temperature of the load side heat exchanger 5b. Adjusted to a value. The refrigerant flowing through the common heat exchanger 7-2 is in a high-pressure liquid state, and heat is exchanged with the low-pressure two-phase refrigerant flowing through the common heat exchanger 7-2 of the refrigerant circuit 3 so that the degree of supercooling increases and cooling is performed. Ability increases.
[0099]
In the refrigerant circuit 3, the refrigerant is hardly expanded in the heat source side expansion mechanism 4c and the cascade expansion mechanism 9c, and the load side expansion mechanism 6c is used as the outlet subcooling temperature of the load side heat exchanger 5c or the heat source side heat exchanger 3c. The outlet superheat temperature is adjusted to a target value, and the refrigerant flowing through the paths 7ca and 7cb in the common heat exchangers 7-1 and 7-2 is adjusted so as to be in a low-pressure two-phase state, respectively. Heat is exchanged with 1 high-pressure gas, 2-phase or liquid refrigerant, and high-pressure liquid refrigerant in the refrigerant circuit 2 to become a gas. Note that the description of how the refrigerant flows is omitted.
[0100]
In this embodiment, in a circuit including a plurality of common heat exchangers connected to both ends of the expansion mechanism, the pressure in the common heat exchanger located at the most upstream side of the refrigerant flow is the highest and located at the most downstream side. The pressure in the common heat exchanger becomes the lowest, and the pressures in the plurality of common heat exchangers located therebetween show values that are gradually decreased in order of flow. In common heat exchangers with high pressure, it is possible to increase the heating capacity of other refrigerant circuits by supplying heat to other refrigerant circuits, increase the cooling capacity of this circuit, etc. In common heat exchangers with low pressure, heat is recovered from other refrigerant circuits to compensate for the evaporation capacity of this circuit, mainly increasing heating capacity or recovering heat from other refrigerant circuits. The cooling capacity can be increased, etc., and each common heat exchanger performs heat transfer between multiple refrigerant circuits according to the purpose and desired load, thereby improving the efficiency of heat cascade utilization. And load leveling as a whole system can be achieved.
[0101]
For example, the example which installed this system in the store provided with the freezing apparatus is shown in FIG. Air conditioners 1, 2, and 3 are installed in the X room, air conditioners 4 and 5 are installed in the Y room, and showcases 6, 7, and 8 that store frozen foods are installed in the X room. .
The indoor units 1, 2, and 3 are connected to the outdoor unit A, the indoor units 4 and 5 are connected to the outdoor unit B, and the showcases 6, 7, and 8 are connected to the outdoor unit C to form a refrigerant circuit. Each circuit includes a common heat exchanger, and the capacity of other circuits is compensated through the common heat exchanger.
[0102]
Embodiment 7 FIG.
FIG. 20 is a refrigerant circuit diagram showing another example of the embodiment of the present invention.
In the refrigerant circuit of the first embodiment, for example, common heat exchange surrounded by the heat storage container 24 in parallel with the common heat exchanger 7-1a provided between the heat source side expansion mechanism 3a and the load side heat exchanger 5a. A device 7-1b is provided.
[0103]
In this case, a more efficient operation is possible by using different common heat exchangers depending on whether the ice generated in the heat storage container 24 is used or the capacity is supplemented in each circuit. Note that the operation method and the way of flowing the refrigerant are the same as those already described in other embodiments, and therefore will be omitted.
[0104]
【The invention's effect】
An air conditioner according to the present invention includes a compressor or a refrigerant pump, a four-way valve or a cooling / heating switching valve, a heat source side heat exchanger, a heat source side expansion mechanism, a load side expansion mechanism, a load side heat exchanger, A plurality of refrigerant circuits configured by annularly connecting the four-way valve or cooling / heating switching valve and the compressor, and connected between a heat source side expansion mechanism and a load side expansion mechanism of the refrigerant circuit, Shared In addition, the refrigerant flows even when heat transfer is not performed between the refrigerant circuits. Because it has a configuration with a common heat exchanger, it is possible to simplify the circuit and control without installing a bypass circuit with a switching valve or expansion mechanism for the common heat exchanger, and surplus capacity between multiple refrigerant circuits The necessary heat is transferred from a certain circuit to the undercapacity circuit via a common heat exchanger, and it is possible to compensate for the capacity of the undercapacity circuit, thereby leveling the thermal load of the entire system and using the cascade of heat Enables efficient use of heat throughout the system.
[0105]
Moreover, since the bypass pipe for preventing the refrigerant from flowing through the load side heat exchanger and the three-way valve are provided, the noise problem due to the refrigerant circulation to the stop load heat exchanger is solved.
[0106]
In addition, since the liquid storage part for storing the excess refrigerant is provided in the common heat exchanger, the liquid storage container in each refrigerant circuit is removed, thereby enabling cost reduction.
[0107]
In addition, since the common heat exchanger is equipped with a heat storage container filled with a medium for storing and storing heat, each circuit can store heat and cool using cheap electricity such as midnight power, This can be used to supplement capacity when there is a high demand for cooling operation.
[0108]
In at least one refrigerant circuit, a plurality of common heat exchangers are connected in series, and the plurality of common heat exchangers are shared separately and by any other plurality of other refrigerant circuits. An air conditioner that enables heat transfer across multiple refrigerant circuits by using a heat transfer system with separate refrigerant circuits, enabling efficient heat use of the entire system by using heat cascades Can be provided. .
[0109]
In addition, since the expansion mechanism for the cascade is arranged between the common heat exchangers so that the expansion mechanisms are connected to both ends of the plurality of common heat exchangers, the respective common heat exchangers Depending on the purpose and desired load amount, heat transfer is performed between a plurality of different refrigerant circuits, so that it is possible to achieve efficiency by using heat cascades and load leveling as a whole system. .
[0110]
In addition, since the plurality of refrigerant circuits are configured to include those used in an air conditioner, a refrigeration apparatus, a refrigeration apparatus, etc., each refrigerant circuit sharing a common heat exchanger has a purpose such as air conditioning and refrigeration. It is also possible to exchange heat between a plurality of circuits having different values.
[0111]
In the operation method of the air conditioner according to the present invention, when the cooling capacity of a certain refrigerant circuit that is performing cooling operation is further increased in a plurality of refrigerant circuits, the refrigerant is supplied to the common heat exchanger in a high-pressure state in a certain refrigerant circuit In other refrigerant circuits with surplus capacity, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a low-pressure two-phase state, and the operating capacity of the compressor or refrigerant pump is adjusted. By controlling the heat transfer in the common heat exchanger, the cooling capacity of a certain refrigerant circuit can be further increased.
[0112]
In addition, when the heating capacity of a certain refrigerant circuit that is in heating operation is further increased in a plurality of refrigerant circuits, the refrigerant circuit has a surplus capacity by circulating the refrigerant to the common heat exchanger in a low-pressure two-phase state. In other refrigerant circuits, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a high pressure state, and the heat transfer in the common heat exchanger is controlled by adjusting the operating capacity of the compressor or the refrigerant pump. As a result, the heating capacity of a certain refrigerant circuit can be further increased.
[0113]
Further, in the case of defrosting the heat source side heat exchanger of a certain refrigerant circuit while continuing the heating operation in the plural refrigerant circuits, in the certain refrigerant circuit, the common heat exchange is performed on the refrigerant in a low-pressure two-phase state. In other refrigerant circuits having a surplus capacity, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a high pressure state, and is adjusted by adjusting the operating capacity of the compressor or the refrigerant pump. By controlling the heat transfer in the heat exchanger, it is possible to defrost the heat source side heat exchanger of a certain refrigerant circuit that is heating.
[0114]
Also, when not transferring heat between refrigerant circuits ,cold In all the medium circuits, the expansion mechanism connected to both ends of the common heat exchanger should have the same degree of throttling. Key When removing the temperature difference between the refrigerants flowing through the common heat exchanger and transferring heat between the refrigerant circuits ,heat Expansion mechanism throttle connecting the expansion mechanism connected to both ends of the common heat exchanger of the refrigerant circuit whose capacity is increased by movement to both ends of the common heat exchanger of another refrigerant circuit having surplus capacity Be different from the condition Key By adjusting the operating capacity of the compressor or refrigerant pump, the amount of heat transfer between the refrigerant circuits can be reduced by adjusting the operating capacity of the compressor or refrigerant pump. It is possible to adjust.
[Brief description of the drawings]
FIG. 1 is a refrigerant circuit diagram showing a first embodiment of the present invention.
FIG. 2 is a refrigerant circuit diagram showing a refrigerant flow when the cooling capacity of one circuit of the first embodiment is increased.
FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow when the heating capacity of one circuit of the first embodiment is increased.
4 is a refrigerant circuit diagram showing a refrigerant flow during defrosting of the heat source side heat exchanger while continuing the heating operation of one circuit of the first embodiment. FIG.
FIG. 5 is a refrigerant circuit diagram illustrating a refrigerant flow when the cooling capacity of one circuit is increased when the cooling and heating operations of the first embodiment are mixed.
FIG. 6 is a refrigerant circuit diagram showing a refrigerant flow when heating capacity of one circuit is increased when the cooling and heating operations of the first embodiment are mixed.
7 is a refrigerant circuit diagram when an oil separator is installed in the refrigerant circuit diagram of the first embodiment. FIG.
FIG. 8 is a refrigerant circuit diagram when a liquid separator is installed in the refrigerant circuit diagram of the first embodiment.
FIG. 9 is a diagram showing an example when the refrigerant circuit according to the first embodiment is installed in a building or the like.
FIG. 10 is a refrigerant circuit diagram showing Embodiment 2 of the present invention.
FIG. 11 is a refrigerant circuit diagram showing Embodiment 3 of the present invention.
FIG. 12 is a refrigerant circuit diagram showing a fourth embodiment of the present invention.
FIG. 13 is a refrigerant circuit diagram illustrating a refrigerant flow when each refrigerant circuit of the fourth embodiment generates ice in a heat storage container using a common heat exchanger.
FIG. 14 is a diagram showing an example when the refrigerant circuit of the fourth embodiment is installed in a building or the like.
FIG. 15 is a refrigerant circuit diagram showing Embodiment 5 of the present invention.
FIG. 16 is a refrigerant circuit diagram showing Embodiment 6 of the present invention.
FIG. 17 is a refrigerant circuit diagram illustrating a refrigerant flow during heating operation of the air-conditioning apparatus according to Embodiment 6 and when the capacity of the refrigeration equipment is increased.
18 is a refrigerant circuit diagram illustrating a refrigerant flow during cooling operation of the air-conditioning apparatus according to Embodiment 6 and an increase in the capacity of the refrigeration equipment. FIG.
FIG. 19 is a diagram showing an example when the refrigerant circuit of the sixth embodiment is installed in a store or the like.
FIG. 20 is a refrigerant circuit diagram showing Embodiment 7 of the present invention.
FIG. 21 is a refrigerant circuit diagram of a conventional air conditioner.
[Explanation of symbols]
A, B Heat source side unit, X, Y Load side unit, U Heat transfer unit, 1a, 1b, 1c Compressor and pressurizing pump, 2a, 2b, 2c Four-way valve and cooling / heating switching valve, 3a, 3b, 3c Heat source side Heat exchanger, 4a, 4b, 4c Heat source side expansion mechanism, 5a, 5b, 5c Load side heat exchanger, 6a, 6b, 6c Load side expansion mechanism, 7, 7-1, 7-2, 7-1a, 7 -1b Common heat exchanger, 7a, 7b, 7ca, 7cb Common heat exchanger path, 8a, 8b Three-way valve, 9c Cascade expansion mechanism, 10a, 10b, 10c Discharge piping, 11a, 11b, 11c Heat source side gas piping, 12a, 12b, 12c Load side gas piping, 13a, 13b, 13c Heat source side liquid piping, 14a, 14b, 14c Load side liquid piping, 15a, 115b, 15c suction piping, 16a, 16b Load side bypass piping, 2 1a, 21b Oil separator, 22a, 22b Liquid separator, 23 Liquid reservoir, 24 Heat storage container.

Claims (12)

圧縮機または冷媒ポンプと、四方弁または冷暖切換弁と、熱源側熱交換器と、熱源側膨張機構と、負荷側膨張機構と、負荷側熱交換器と、前記四方弁または冷暖切換弁と前記圧縮機とを環状に接続して構成される複数の冷媒回路と、
この冷媒回路の前記熱源側膨張機構と前記負荷側膨張機構との間に接続され、前記冷媒回路によって共有されると共に、各冷媒回路間で熱移動を行わない場合でも冷媒が流通する共通熱交換器と、
を備えたことを特徴とする空気調和装置。Compressor or refrigerant pump, four-way valve or cooling / heating switching valve, heat source side heat exchanger, heat source side expansion mechanism, load side expansion mechanism, load side heat exchanger, the four-way valve or cooling / heating switching valve, and A plurality of refrigerant circuits configured by connecting the compressor in a ring shape;
Common heat exchange that is connected between the heat source side expansion mechanism and the load side expansion mechanism of the refrigerant circuit, is shared by the refrigerant circuit, and allows the refrigerant to flow even when heat transfer is not performed between the refrigerant circuits. And
An air conditioner comprising: 前記負荷側熱交換器に冷媒を流通させないためのバイパス管と、三方弁とを備えたことを特徴とする請求項１記載の空気調和装置。The air conditioner according to claim 1, further comprising a bypass pipe for preventing refrigerant from flowing through the load side heat exchanger and a three-way valve. 前記共通熱交換器に余剰冷媒を貯蔵する液貯め部を設けたことを特徴とする請求項１記載の空気調和装置。The air conditioner according to claim 1, wherein a liquid reservoir for storing excess refrigerant is provided in the common heat exchanger. 前記共通熱交換器に設けられ、蓄熱・蓄冷を行うための媒体が充填された蓄熱容器を備えたことを特徴とする請求項１記載の空気調和装置。The air conditioner according to claim 1, further comprising a heat storage container provided in the common heat exchanger and filled with a medium for storing and storing heat. 少なくとも１つの前記冷媒回路においては、前記共通熱交換器が直列に複数接続され、該複数の共通熱交換器はそれぞれ別々かつ任意の複数の他の前記冷媒回路に共有されることを特徴とする請求項１記載の空気調和装置。In at least one of the refrigerant circuits, a plurality of the common heat exchangers are connected in series, and the plurality of common heat exchangers are separately and shared by a plurality of other refrigerant circuits. The air conditioning apparatus according to claim 1. 前記複数の共通熱交換器のそれぞれの間に、前記熱源側膨張機構及び前記負荷側膨張機構と同一作用のカスケード用膨張機構が配設されていることを特徴とする請求項５記載の空気調和装置。The air conditioning according to claim 5, wherein a cascade expansion mechanism having the same action as the heat source side expansion mechanism and the load side expansion mechanism is disposed between the plurality of common heat exchangers. apparatus. 前記複数の冷媒回路は、空気調和装置、冷凍用装置、冷蔵用装置等に使用されるものを含むことを特徴とする請求項１〜６の何れかに記載の空気調和装置。The air conditioner according to any one of claims 1 to 6, wherein the plurality of refrigerant circuits include those used in an air conditioner, a refrigeration apparatus, a refrigeration apparatus, and the like. 請求項１〜６の何れかに記載した空気調和装置の運転方法であって、
前記複数冷媒回路中、冷房運転しているある冷媒回路の冷房能力をさらに大きくする場合、前記ある冷媒回路においては、高圧状態で冷媒を前記共通熱交換器に流通させ、
余剰能力のある他の前記冷媒回路において、前記共通熱交換器を流通する冷媒は、低圧二相状態で前記共通熱交換器へ流通させ、
前記圧縮機又は冷媒ポンプの運転容量の調整して前記共通熱交換器での熱移動を制御することを特徴とする空気調和装置の運転方法。An operation method for an air conditioner according to any one of claims 1 to 6 ,
In the plurality of refrigerant circuits, when further increasing the cooling capacity of a certain refrigerant circuit that is performing cooling operation, in the certain refrigerant circuit, the refrigerant is circulated to the common heat exchanger in a high-pressure state,
In the other refrigerant circuit having surplus capacity, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a low-pressure two-phase state,
An operation method of an air conditioner, wherein the heat transfer in the common heat exchanger is controlled by adjusting an operation capacity of the compressor or the refrigerant pump. 請求項１〜６の何れかに記載した空気調和装置の運転方法であって、
前記複数冷媒回路中、暖房運転しているある冷媒回路の暖房能力をさらに大きくする場合、前記ある冷媒回路においては、低圧二相状態で冷媒を前記共通熱交換器に流通させ、
余剰能力のある他の前記冷媒回路において、前記共通熱交換器を流通する冷媒は、高圧状態で前記共通熱交換器へ流通させ、
前記圧縮機又は冷媒ポンプの運転容量の調整して前記共通熱交換器での熱移動を制御することを特徴とする空気調和装置の運転方法。An operation method for an air conditioner according to any one of claims 1 to 6 ,
In the multiple refrigerant circuit, when further increasing the heating capacity of a certain refrigerant circuit that is performing heating operation, in the certain refrigerant circuit, the refrigerant is circulated to the common heat exchanger in a low-pressure two-phase state,
In the other refrigerant circuit having surplus capacity, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a high-pressure state,
An operation method of an air conditioner, wherein the heat transfer in the common heat exchanger is controlled by adjusting an operation capacity of the compressor or the refrigerant pump. 請求項１〜６の何れかに記載した空気調和装置の運転方法であって、
前記複数冷媒回路中、暖房運転しているある冷媒回路の前記熱源側熱交換器を除霜する場合、前記ある冷媒回路においては、低圧二相状態で冷媒を前記共通熱交換器に流通させ、
余剰能力のある他の前記冷媒回路において、前記共通熱交換器を流通する冷媒は、高圧状態で前記共通熱交換器へ流通させ、
前記圧縮機又は冷媒ポンプの運転容量の調整して前記共通熱交換器での熱移動を制御することを特徴とする空気調和装置の運転方法。An operation method for an air conditioner according to any one of claims 1 to 6 ,
In the plurality of refrigerant circuits, when defrosting the heat source side heat exchanger of a certain refrigerant circuit that is in a heating operation, in the certain refrigerant circuit, the refrigerant is circulated to the common heat exchanger in a low-pressure two-phase state,
In the other refrigerant circuit having surplus capacity, the refrigerant flowing through the common heat exchanger is circulated to the common heat exchanger in a high-pressure state,
An operation method of an air conditioner, wherein the heat transfer in the common heat exchanger is controlled by adjusting an operation capacity of the compressor or the refrigerant pump. 請求項１〜６の何れかに記載した空気調和装置の運転方法であって、
前記冷媒回路間で熱移動を行わない場合は、前記冷媒回路の全てにおいて、前記共通熱交換器の両端に接続している前記膨張機構の絞り具合をほぼ同一にする調整をし、
前記冷媒回路間で熱移動を行う場合は、熱移動によって能力を増大する前記冷媒回路の前記共通熱交換器の両端に接続している前記膨張機構の絞り具合を余剰能力のある前記他の冷媒回路の前記共通熱交換器の両端に接続している前記膨張機構の絞り具合と異なるようにする調整をし、前記圧縮機又は冷媒ポンプの運転容量の調整を伴うこともあることを特徴とする空気調和装置の運転方法。An operation method for an air conditioner according to any one of claims 1 to 6,
The case without the heat transfer between the refrigerant circuit, wherein all of the refrigerant circuit, before Symbol substantially identical to that tone Seioshi the throttle degree of the expansion mechanism that is connected to both ends of the common heat exchanger,
In the case where heat transfer is performed between the refrigerant circuits, the other refrigerant having a surplus capacity is provided by restricting the expansion mechanism connected to both ends of the common heat exchanger of the refrigerant circuit whose capacity is increased by heat transfer. characterized in that it is sometimes accompanied by the common heat exchanger wherein the expansion mechanism that is connected to both ends of the aperture degree different way to that tone Seioshi, adjustment of operating capacity of the compressor or refrigerant pump circuit A method for operating the air conditioner. 圧縮機または冷媒ポンプと、四方弁または冷暖切換弁と、熱源側熱交換器と、熱源側膨張機構とから熱源側ユニットを構成し、負荷側膨張機構と共通熱交換器から熱移動ユニットを構成し、負荷側熱交換器から負荷側ユニットを構成するとともに、熱源側ユニットと熱移動ユニットとの接続および熱移動ユニットと負荷側ユニットを接続することにより環状回路を構成することを特徴とする請求項１〜６の何れかに記載の空気調和装置。A compressor or refrigerant pump, a four-way valve or cooling / heating switching valve, a heat source side heat exchanger, and a heat source side expansion mechanism constitute a heat source side unit, and a load side expansion mechanism and a common heat exchanger constitute a heat transfer unit The load-side heat exchanger constitutes a load-side unit, and the annular circuit is constituted by connecting the heat-source-side unit and the heat-transfer unit and connecting the heat-transfer unit and the load-side unit. Item 7. The air conditioner according to any one of Items 1 to 6.
JP30508897A 1997-11-07 1997-11-07 Air conditioner and method of operating air conditioner Expired - Lifetime JP3614626B2 (en)

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