JP3802237B2

JP3802237B2 - Air conditioner with ice storage tank

Info

Publication number: JP3802237B2
Application number: JP21620898A
Authority: JP
Inventors: 博和井崎; 美暁黒澤; 修桑原
Original assignee: Sanyo Electric Co Ltd
Current assignee: Sanyo Electric Co Ltd
Priority date: 1998-07-30
Filing date: 1998-07-30
Publication date: 2006-07-26
Anticipated expiration: 2018-07-30
Also published as: JP2000046433A

Description

【０００１】
【発明の属する技術分野】
本発明は、氷蓄熱槽を備えた空気調和装置に係り、氷蓄熱ユニットに蓄熱された冷熱を放熱して放冷冷房運転を実施する氷蓄熱槽を備えた空気調和装置に関する。
【０００２】
【従来の技術】
一般に、図３に示すように、圧縮機１、熱源側熱交換器２、四方弁３及び電動膨張弁４を備えた熱源側ユニット５と、氷蓄熱槽６内にコイル７が水没状態で配設されてコイル７外周に氷が形成可能な氷蓄熱ユニット８と、利用側熱交換器９を備えた利用側ユニット１０とを有し、製氷運転、放冷冷房運転、通常冷房運転を実施可能とする空気調和装置１１が知られている。
【０００３】
製氷運転は、圧縮機１からのガス冷媒が熱源側熱交換器２を経て液冷媒となり、その後に電動膨張弁４を通り、氷蓄熱槽６内のコイル７に流入して蒸発し、この氷蓄熱槽６内で製氷動作が実施された後、ガス冷媒が圧縮機１へ戻されて実施される。
【０００４】
放冷冷房運転は、熱源側ユニット５の圧縮機１を停止させ、氷蓄熱ユニット８に設置されて冷媒を圧送する液ポンプ又はガスポンプなどの循環ポンプ１２（図３では液冷媒を圧送する液ポンプ）を稼働させることによりなされている。つまり、循環ポンプ１２の稼働により、氷蓄熱ユニット８における氷蓄熱槽６のコイル７内で、氷に蓄熱された冷熱を吸収して凝縮した液冷媒が利用側熱交換器９へ圧送され、この利用側熱交換器９において液冷媒が蒸発して、この蒸発潜熱と氷の冷熱の放熱とにより放冷冷房運転が実施される。
【０００５】
通常冷房運転は、圧縮機１から熱源側熱交換器２へ導かれて液冷媒となった冷媒を、氷蓄熱槽６のコイル７内へ流すことなく、利用側熱交換器９へ供給して液冷媒を蒸発し、この蒸発潜熱により実施される。
【０００６】
【発明が解決しようとする課題】
ところで、上述の放冷冷房運転では、特に循環ポンプ１２が液ポンプの場合に、この循環ポンプ１２にキャビテーションが発生するおそれがある。更に、冷媒の種類に対応した仕様の液ポンプが必要となる。
【０００７】
本発明の課題は、上述の事情を考慮してなされたものであり、信頼性を向上させることができる氷蓄熱槽を備えた空気調和装置を提供することにある。
【０００８】
【課題を解決するための手段】
請求項１記載の発明は、圧縮機及び熱源側熱交換器を備えた熱源側ユニットと、氷蓄熱槽内にコイルが水没状態で配設されてこのコイル外周に氷が形成可能な氷蓄熱ユニットと、利用側熱交換器を備えた利用側ユニットとを有し、製氷運転、冷房運転を実施可能とする氷蓄熱槽を備えた空気調和装置において、上記氷蓄熱槽内の上記コイルと上記利用側熱交換器との間に、冷媒を貯溜可能な複数のタンクが並列状態で配設され、上記コイル内で凝縮した液冷媒が上記タンク内に貯溜されて、これらのタンク内へ交互に供給される高圧ガス冷媒により上記利用側熱交換器へ圧送可能に構成されたことを特徴とするものである。
【０００９】
請求項２記載の発明は、請求項１に記載の発明において、上記複数のタンクへ交互に供給される高圧ガス冷媒は、熱源側ユニットの圧縮機の停止時における当該圧縮機と熱源側熱交換器との間の高圧ガス冷媒であることを特徴とするものである。
【００１０】
請求項３記載の発明は、請求項１に記載の発明において、上記複数のタンクへ交互に供給される高圧ガス冷媒は、熱源側ユニットの圧縮機よりも容量の小さな小容量圧縮機から供給される高圧ガス冷媒であることを特徴とするものである。
【００１１】
請求項１に記載の発明には、次の作用がある。
氷蓄熱ユニットのコイル内において氷の冷熱により凝縮された液冷媒が複数のタンク内に貯溜され、これらの液冷媒が、タンク内へ交互に供給される高圧ガス冷媒により利用側熱交換器へ圧送可能に構成されたことから、氷蓄熱ユニットのコイル内における液冷媒を利用側熱交換器へ圧送する液ポンプが不要となり、従って、この液ポンプに発生する虞のあるキャビテーションを確実に回避でき、信頼性を向上させることができる。
【００１２】
請求項２に記載の発明には、次の作用がある。
熱源側ユニットの圧縮機の停止時における当該圧縮機と熱源側熱交換器との間の高圧ガス冷媒を複数のタンクへ交互に供給することから、この圧縮機を駆動させず、ほとんど無動力で、氷蓄熱ユニットのコイル内における過冷却状態の液冷媒を利用側熱交換器へ圧送させることができる。
【００１３】
請求項３に記載の発明には、次の作用がある。
【００１４】
熱源側ユニットの圧縮機よりも容量の小さな小容量圧縮機から供給される高圧ガス冷媒を複数のタンクへ交互に供給することから、この小容量圧縮機は汎用の圧縮機であれば良く、冷媒の種類に応じてその仕様を変更する必要がないので、部品の共用化を図ることができ、コストを低減できる。
【００１５】
【発明の実施の形態】
以下、本発明の実施の形態を図面に基づいて説明する。
【００１６】
［Ａ］第一の実施の形態
図１は、本発明に係る氷蓄熱槽を備えた空気調和装置の第一の実施の形態を示す管路図である。
【００１７】
この図１に示す空気調和装置２０は、熱源側ユニット２１、氷蓄熱ユニット２２及び利用側ユニット２３を有して構成される。熱源側ユニット２１の冷媒配管２４が、氷蓄熱ユニット２２の冷媒配管２５、２６を介して利用側ユニット２３の冷媒配管２７に接続される。
【００１８】
熱源側ユニット２１は、冷媒配管２４に圧縮機２８、四方弁２９、熱源側熱交換器３０及び電動膨張弁３１が順次接続されて構成される。また、利用側ユニット２３は、冷媒配管２７に利用側熱交換器３２及び電動膨張弁３３が配設されて構成され、この電動膨張弁３３は、空調負荷に応じて開度が調整される。
【００１９】
氷蓄熱ユニット２２は、コイル３４を収容した氷蓄熱槽３５を備えると共に、冷媒配管２５に第１開閉弁３６が、冷媒配管２６に第２開閉弁３７がそれぞれ配設される。更に、冷媒配管２５には、第１開閉弁３６の配設位置よりも利用側ユニット２３側に、接続配管３８を介してコイル３４の一端が接続され、この接続配管３８に電動膨張弁３９が配設される。また、コイル３４の他端は、第３開閉弁４０を備えた接続配管４１を介して、冷媒配管２６における第２開閉弁３７配設位置の利用側ユニット２３側に接続される。
【００２０】
氷蓄熱槽３５には水が充満され、コイル３４はこの氷蓄熱槽３５内に水没状態で配設される。このコイル３４内には、空気調和装置２０の製氷運転時に熱源側熱交換器３０から液冷媒が流入して蒸発し、これにより、コイル３４の外周に氷が付着して形成される。
【００２１】
上記接続配管３８には、電動膨張弁３９とコイル３４との間に、二股に分岐する分岐配管４２を介して２個のサージタンク４３Ａ及び４３Ｂが並列状態で接続される。これらのサージタンク４３Ａ、４３Ｂが合流配管４４を介して、冷媒配管２５における第１開閉弁３６配設位置と接続配管３８接続位置との間に接続される。これにより、サージタンク４３Ａ及び４３Ｂは、氷蓄熱槽３５内のコイル３４と利用側熱交換器３２との間に配設されて、氷蓄熱槽３５内の氷に蓄熱された冷熱により凝縮された液冷媒が貯留可能に設けられる。
【００２２】
分岐配管４２には、サージタンク４３Ａ、４３Ｂの流入側に流入側逆止弁４５Ａ、４５Ｂが、また、合流配管４４には、サージタンク４３Ａ、４３Ｂの流出側に流出側逆止弁４６Ａ、４６Ｂがそれぞれ配設されている。これらの流入側逆止弁４５Ａ、４５Ｂは、氷蓄熱槽３５のコイル３４からサージタンク４３Ａ、４３Ｂへのみ流れる冷媒の流れを許容し、流出側逆止弁４６Ａ、４６Ｂは、サージタンク４３Ａ、４３Ｂから利用側熱交換器３２側へのみ流れる冷媒の流れを許容する。
【００２３】
サージタンク４３Ａ、４３Ｂは、熱源側ユニット２１の冷媒配管２４における四方弁２９と熱源側熱交換器３０との間に、分岐配管４７を介して接続される。この分岐配管４７には、サージタンク４３Ａに接続される分岐部４８Ａに第１タンク開閉弁４９が、また、サージタンク４３Ｂに接続される分岐部４８Ｂに第２タンク開閉弁５０がそれぞれ配設される。
【００２４】
これらの第１タンク開閉弁４９、第２タンク開閉弁５０が選択的に開閉されることにより、圧縮機２８の停止時におけるこの圧縮機２８と熱源側熱交換器３０との間の高圧ガス冷媒が、サージタンク４３Ａ、４３Ｂ内に交互に供給可能に構成される。これにより、サージタンク４３Ａ、４３Ｂ内に貯留された液冷媒が利用側熱交換器３２へ圧送可能に設けられる。
【００２５】
次に、空気調和装置２０の製氷運転、放冷冷房運転、通常冷房運転を説明する。
【００２６】
［Ａ−１］製氷運転
空気調和装置２０の製氷運転は、例えば、夜間１０時から翌朝８時までの電力料金の安い時間帯に、熱源側熱交換器３０からの液冷媒を氷蓄熱槽３５のコイル３４内へ供給し、氷蓄熱槽３５内に氷を作る運転である。
【００２７】
この場合には、電動膨張弁３３、第１タンク開閉弁４９及び第２タンク開閉弁５０が閉弁され、第１開閉弁３６、第２開閉弁３７、第３開閉弁４０及び電動膨張弁３９が開弁操作される。
【００２８】
この状態で、熱源側ユニット２１の圧縮機２８が稼働されると、この圧縮機２８から吐出されたガス冷媒は、熱源側熱交換器３０にて凝縮され、電動膨張弁３１及び３９を経て減圧され、氷蓄熱槽３５のコイル３４内へ流入する。このコイル３４内に流入した冷媒は蒸発して、コイル３４の外周に氷を付着した状態で形成する。その後、コイル３４内のガス冷媒は接続配管４１及び冷媒配管２６を経て四方弁２９へ至り、圧縮機２８に戻される。
【００２９】
［Ａ−２］放冷冷房運転
空気調和装置２０の放冷冷房運転は、例えば、昼間気温が上昇する時間帯に、氷蓄熱槽３５のコイル３４内で氷の冷熱により液化されてサージタンク４３Ａ、４３Ｂ内に貯留された液冷媒を、このサージタンク４３Ａ、４３Ｂから利用側熱交換器３２へ圧送することにより実施される。
【００３０】
この場合には、第１開閉弁３６、第２開閉弁３７及び電動膨張弁３９が閉弁され、電動膨張弁３３及び第３開閉弁４０が開弁操作される。また、熱源側ユニット２１の圧縮機２８は、製氷運転終了後の停止状態にある。
【００３１】
この状態で、第１タンク開閉弁４９、第２タンク開閉弁５０を選択的に開閉操作する。例えば、第１タンク開閉弁４９を開操作すると（第２タンク開閉弁５０は閉状態）、熱源側ユニット２１の圧縮機２８と熱源側熱交換器３０との間の高圧ガス冷媒が、第１タンク開閉弁４９を経てサージタンク４３Ａ内へ流入する。これにより、このサージタンク４３Ａ内の貯留液冷媒が流出側逆止弁４６Ａ、合流配管４４、冷媒配管２５及び２７を経て利用側熱交換器３２内へ流入する。サージタンク４３Ａ内に貯留した液冷媒は、氷蓄熱槽３５のコイル３４内を通り、氷蓄熱槽３５内の氷に蓄熱された冷熱により凝縮された液冷媒であるため、利用側熱交換器３２内で蒸発することにより、上記氷の冷熱の放熱（放冷）と蒸発潜熱とにより室内を効率的に冷却する。
【００３２】
利用側熱交換器３２にて蒸発したガス冷媒は、接続配管４１及び第３開閉弁４０を経て氷蓄熱槽３５のコイル３４内へ流入し、上述の如く、氷蓄熱槽３５内の氷により液冷媒となって、流入側逆止弁４５Ｂを経てサージタンク４３Ｂ内へ流入する。
【００３３】
この時、サージタンク４３Ａ内が高圧であるため、氷蓄熱槽３５のコイル３４内の液冷媒は、サージタンク４３Ａ内へ流れることなくサージタンク４３Ｂ内へ流れる。同様に、サージタンク４３Ｂ内がサージタンク４３Ａに比べて低圧であるため、サージタンク４３Ｂ内の貯留冷媒が流出側逆止弁４６Ｂを経て利用側熱交換器３２側へ流出することもない。
【００３４】
サージタンク４３Ａ内の貯留冷媒が所定値以下まで低下した時点で第１タンク開閉弁４９を閉弁状態とし、第２タンク開閉弁５０を開弁操作させる。すると、サージタンク４３Ｂ内に貯留された液冷媒が、流出側逆止弁４６Ｂ、合流配管４４、冷媒配管２５、２７及び電動膨張弁３３を経て利用側熱交換器３２へ流入し蒸発して、前述と同様に、放冷及び蒸発潜熱により室内を効率的に冷房する。この利用側熱交換器３２からのガス冷媒は、接続配管４１及び第３開閉弁４０を経て氷蓄熱槽３５のコイル３４内で氷の冷熱により凝縮され、分岐配管４２及び流入側逆止弁４５Ａを経てサージタンク４３Ａ内へ流入する。
【００３５】
サージタンク４３Ｂ内の液冷媒が所定値以下まで低下した時点で、第２タンク開閉弁５０を閉弁し、第１タンク開閉弁４９を開弁操作して、上述の動作を繰り返す。この放冷冷房運転実施時には、一般に外気温度が高温であるため、熱源側熱交換器３０内の冷媒温度が高く、熱源側ユニット２１において圧縮機２８と熱源側熱交換器３０との間に高圧ガス冷媒が長時間維持されて、上述の放冷冷房運転が継続される。
【００３６】
しかし、上述の放冷冷房運転中に、氷蓄熱ユニット２２内で冷媒量が増加した場合には、この放冷冷房運転状態において、第１開閉弁３６を閉弁状態としたままで第２開閉弁３７を開弁操作し、四方弁２９を冷房位置に設定して圧縮機２８を稼働させ、ポンプダウンを実施する。これにより、氷蓄熱ユニット２２内の余剰の冷媒が回収され、熱源側ユニット２１における圧縮機２８と熱源側熱交換器３０との間に高圧ガス冷媒が確保されて、上述の放冷冷房運転が再び継続される。
【００３７】
［Ａ−３］通常冷房運転
空気調和装置２０の通常冷房運転は、氷蓄熱槽３５内の氷に蓄熱された冷熱を利用しないで実施される冷房運転であり、第１タンク開閉弁４９、第２タンク開閉弁５０、電動膨張弁３９及び第３開閉弁４０が閉弁され、第１開閉弁３６、第２開閉弁３７並びに電動膨張弁３１及び３３が開弁操作される。
【００３８】
この状態で、圧縮機２８が稼働されると、この圧縮機２８から吐出されたガス冷媒は、熱源側熱交換器３０にて凝縮され、電動膨張弁３１、冷媒配管２５及び電動膨張弁３３を経て利用側熱交換器３２へ流入し、この利用側熱交換器３２にて蒸発して、蒸発潜熱により室内を冷房した後、冷媒配管２６及び四方弁２９を経て圧縮機２８へ戻される。
【００３９】
上記実施の形態の空気調和装置２０は、上述のように構成されたことから、次の効果▲１▼及び▲２▼を奏する。
【００４０】
▲１▼氷蓄熱槽３５のコイル３４内において氷の冷熱により凝縮した液冷媒がサージタンク４３Ａ、４３Ｂ内に貯留され、これらの液冷媒が、サージタンク４３Ａ、４３Ｂ内へ交互に供給される高圧ガス冷媒により利用側ユニット２３へ圧送可能に構成されたことから、氷蓄熱槽３５のコイル３４内における液冷媒を利用側ユニット２３へ圧送する液ポンプなどの循環ポンプが不要となり、従って、この液ポンプに発生する恐れのあるキャビテーションを確実に回避でき、信頼性を向上させることができる。
【００４１】
▲２▼熱源側ユニット２１の圧縮機２８停止時における圧縮機２８と熱源側熱交換器３０との間の高圧ガス冷媒を、第１タンク開閉弁４９、第２タンク開閉弁５０を交互に開閉操作して分岐配管４７を介しサージタンク４３Ａ、４３Ｂ内へ交互に供給することから、圧縮機２８を駆動させず、ほとんど無動力で、氷蓄熱槽３５のコイル３４内における液冷媒を利用側熱交換器３２へ圧送させることができる。
【００４２】
［Ｂ］第二の実施の形態
図２は、本発明に係る氷蓄熱槽を備えた空気調和装置の第二の実施の形態を示す管路図である。この第二の実施の形態において、前記第一の実施の形態と同様な部分は、同一の符号を付すことにより説明を省略する。
【００４３】
この第二の実施の形態の空気調和装置６０は、前記空気調和装置２０の分岐配管４７、第１タンク開閉弁４９及び第２タンク開閉弁５０が削除され、代わりに小容量圧縮機６１及び四方弁６２が、第１配管６３、第２配管６４、第３配管６５及び第４配管６６に配設されたものである。第１配管６３、第２配管６４、第３配管６５及び第４配管６６は、それぞれの一端が四方弁６２の各ポートに接続されると共に、第１配管６３、第２配管６４の他端が小容量圧縮機６１の吐出口と吸込口にそれぞれ接続される。また、第３配管６５、第４配管６６の他端がサージタンク４３Ａ、４３Ｂにそれぞれ接続される。
【００４４】
四方弁６２の切り換え操作により、第１配管６３及び第３配管６５の連通並びに第２配管６４及び第４配管６６の連通と、第１配管６３及び第４配管６６の連通並びに第２配管６４及び第３配管６５の連通とが、選択的に切り換わる。また、上記小容量圧縮機６１は、熱源側ユニット２１における圧縮機２８よりも小さな容量（１／１０〜１／２０）の圧縮機であり、空気調和装置６０の放冷冷房運転時にのみ稼働される。この小容量圧縮機６１から吐出される冷媒は、熱源側ユニット２１の圧縮機２８から吐出される冷媒と同一組成である。
【００４５】
更に、前記空気調和装置２０の流入側逆止弁４５Ａ、４５Ｂ、流出側逆止弁４６Ａ、４６Ｂは、それぞれ流入側開閉弁６７Ａ、６７Ｂ、流出側開閉弁６８Ａ、６８Ｂに置き換えられて構成される。
【００４６】
製氷運転及び通常冷房運転時には、流入側開閉弁６７Ａ及び６７Ｂ、並びに流出側開閉弁６８Ａ及び６８Ｂが全て閉弁操作され、且つ小容量圧縮機６１が停止する。
【００４７】
放冷冷房運転時には、流入側開閉弁６７Ａ及び流出側開閉弁６８Ｂと、流入側開閉弁６７Ｂ及び流出側開閉弁６８Ａとが交互に開閉操作され、小容量圧縮機６１が稼働する。四方弁６２が第１配管６３及び第３配管６５を連通させ、第２配管６４及び第４配管６６を連通させる状態に切り換えられ、更に、流入側開閉弁６７Ｂ及び流出側開閉弁６８Ａが開弁操作され、流入側開閉弁６７Ａ及び流出側開閉弁６８Ｂが閉弁操作されているときには、小容量圧縮機６１にて吐出された高圧ガス冷媒は、第１配管６３、四方弁６２及び第３配管６５を経てサージタンク４３Ａ内へ流入する。これにより、このサージタンク４３Ａ内に貯留され、且つ氷蓄熱槽３５の氷の冷熱により凝縮した液冷媒が、流出側開閉弁６８Ａ、合流配管４４及び冷媒配管２５などを経て利用側熱交換器３２へ圧送され、この利用側熱交換器３２にて蒸発して室内が放冷冷房される。利用側熱交換器３２にて蒸発してガス冷媒は、接続配管４１及び第３開閉弁４０を通って氷蓄熱槽３５のコイル３４内へ至り、氷の冷熱により液冷媒となって、流入側開閉弁６７Ｂを経てサージタンク４３Ｂ内へ貯留される。
【００４８】
サージタンク４３Ａ内の液冷媒が所定値以下まで低下したときに、四方弁６２を切り換えて第１配管６３及び第４配管６６を連通状態とし、第２配管６４及び第３配管６５を連通状態とし、更に、流入側開閉弁６７Ａ及び流出側開閉弁６８Ｂを開弁操作し、流入側開閉弁６７Ｂ及び流出側開閉弁６８Ａを閉弁操作すると、小容量圧縮機６１にて吐出された高圧ガス冷媒は、第１配管６３、四方弁６２及び第４配管６６を経てサージタンク４３Ｂ内へ流入する。これにより、サージタンク４３Ｂ内に貯留された液冷媒が、流出側開閉弁６８Ｂ、合流配管４４及び冷媒配管２５等を経て利用側熱交換器３２へ圧送され、この利用側熱交換器３２にて蒸発して室内が放冷冷房される。利用側熱交換器３２にて蒸発したガス冷媒は、氷蓄熱槽３５のコイル３４内を通って氷の冷熱により凝縮され、流入側開閉弁６７Ａを経てサージタンク４３Ａ内に貯留される。
【００４９】
サージタンク４３Ｂ内の液冷媒が所定値以下まで低下したときに四方弁６２を切り換えて、上述の操作を繰り返し放冷冷房運転を継続させる。
【００５０】
従って、この第二の実施の形態の空気調和装置６０においても、前記実施の形態の効果▲１▼と同様の効果を奏する他、次の効果▲３▼を奏する。
【００５１】
▲３▼熱源側ユニット２１の圧縮機２８よりも容量の小さな小容量圧縮機６１から供給される高圧ガス冷媒を、四方弁６２の切り換え操作によりサージタンク４３Ａ、４３Ｂ内へ交互に供給することから、小容量圧縮機６１は汎用の圧縮機であればよく、冷媒の種類に応じてその仕様を変更する必要がないので、部品の共用化を図ることができ、コストを低減できる。
【００５２】
以上、一実施の形態に基づいて本発明を説明したが、本発明はこれに限定されるものではない。
【００５３】
例えば、第一の実施の形態の空気調和装置２０において、流入側逆止弁４５Ａ、４５Ｂ、流出側逆止弁４６Ａ、４６Ｂは、それぞれ、第二の実施の形態の空気調和装置６０における流入側開閉弁６７Ａ、６７Ｂ、流出側開閉弁６８Ａ、６８Ｂであってもよく、更に、空気調和装置６０の流入側開閉弁６７Ａ、６７Ｂ、流出側開閉弁６８Ａ、６８Ｂは、それぞれ、空気調和装置２０の流入側逆止弁４５Ａ、４５Ｂ、流出側逆止弁４６Ａ、４６Ｂであってもよい。また、サージタンク４３Ａ、４３Ｂは３以上あってもよい。
【００５４】
【発明の効果】
以上のように、本発明に係る氷蓄熱槽を備えた空気調和装置によれば、氷蓄熱槽内のコイルと利用側熱交換器との間に、冷媒を貯留可能な複数のタンクが並列状態で配設され、上記コイル内の液冷媒が上記タンク内に貯留されて、これらのタンク内へ交互に供給される高圧ガス冷媒により利用側熱交換器へ圧送可能に構成されたことから、氷蓄熱ユニットのコイル内における液冷媒を利用側熱交換器へ圧送する液ポンプが不要となり、液ポンプに発生するおそれのあるキャビテーションを確実に回避できるので、信頼性を向上させることができる。
【図面の簡単な説明】
【図１】本発明に係る氷蓄熱槽を備えた空気調和装置の第一の実施の形態を示す管路図である。
【図２】本発明に係る氷蓄熱槽を備えた空気調和装置の第二の実施の形態を示す管路図である。
【図３】従来の氷蓄熱槽を備えた空気調和装置を示す管路図である。
【符号の説明】
２０空気調和装置
２１熱源側ユニット
２２氷蓄熱ユニット
２３利用側ユニット
２８圧縮機
２９四方弁
３２利用側熱交換器
３４コイル
３５氷蓄熱槽
４３Ａ、４３Ｂサージタンク
４９第１タンク開閉弁
５０第２タンク開閉弁
６０空気調和装置
６１小容量圧縮機
６２四方弁[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air conditioner including an ice heat storage tank, and more particularly to an air conditioner including an ice heat storage tank that dissipates cold heat stored in an ice heat storage unit and performs a cooling and cooling operation.
[0002]
[Prior art]
In general, as shown in FIG. 3, a coil 7 is placed in a submerged state in a heat source unit 5 including a compressor 1, a heat source side heat exchanger 2, a four-way valve 3 and an electric expansion valve 4, and an ice heat storage tank 6. It has an ice heat storage unit 8 that can be formed on the outer periphery of the coil 7 and a use side unit 10 equipped with a use side heat exchanger 9, and can perform ice making operation, cooling cooling operation, and normal cooling operation. An air conditioner 11 is known.
[0003]
In the ice making operation, the gas refrigerant from the compressor 1 becomes a liquid refrigerant through the heat source side heat exchanger 2, and then passes through the electric expansion valve 4 to flow into the coil 7 in the ice heat storage tank 6 and evaporate. After the ice making operation is carried out in the heat storage tank 6, the gas refrigerant is returned to the compressor 1 and carried out.
[0004]
In the cooling and cooling operation, the compressor 1 of the heat source side unit 5 is stopped, and the circulating pump 12 such as a liquid pump or a gas pump that is installed in the ice heat storage unit 8 and pumps the refrigerant (in FIG. 3, a liquid pump that pumps the liquid refrigerant). ). That is, the operation of the circulation pump 12 causes the liquid refrigerant condensed by absorbing the cold stored in the ice in the coil 7 of the ice storage tank 6 in the ice storage unit 8 to be pumped to the use side heat exchanger 9. The liquid refrigerant evaporates in the use side heat exchanger 9, and the cooling and cooling operation is performed by the latent heat of evaporation and the heat radiation of ice.
[0005]
In the normal cooling operation, the refrigerant that has been led from the compressor 1 to the heat source side heat exchanger 2 to become liquid refrigerant is supplied to the use side heat exchanger 9 without flowing into the coil 7 of the ice heat storage tank 6. The liquid refrigerant is evaporated, and this latent heat of vaporization is carried out.
[0006]
[Problems to be solved by the invention]
By the way, in the above-described cooling and cooling operation, cavitation may occur in the circulation pump 12 particularly when the circulation pump 12 is a liquid pump. Furthermore, a liquid pump having specifications corresponding to the type of refrigerant is required.
[0007]
The subject of this invention is made in view of the above-mentioned situation, and is providing the air conditioning apparatus provided with the ice thermal storage tank which can improve reliability.
[0008]
[Means for Solving the Problems]
The invention according to claim 1 is a heat source side unit including a compressor and a heat source side heat exchanger, and an ice heat storage unit in which a coil is disposed in a submerged state in an ice heat storage tank so that ice can be formed on the outer periphery of the coil. And an air-conditioning apparatus having an ice heat storage tank capable of performing ice making operation and cooling operation, and the coil in the ice heat storage tank and the utilization A plurality of tanks capable of storing refrigerant are arranged in parallel with the side heat exchanger, and liquid refrigerant condensed in the coil is stored in the tank and supplied alternately to these tanks. The high-pressure gas refrigerant is configured to be capable of being pumped to the use side heat exchanger.
[0009]
According to a second aspect of the present invention, in the first aspect of the invention, the high-pressure gas refrigerant that is alternately supplied to the plurality of tanks exchanges heat with the compressor when the compressor of the heat source unit is stopped. It is a high-pressure gas refrigerant between the containers.
[0010]
According to a third aspect of the present invention, in the first aspect of the invention, the high-pressure gas refrigerant that is alternately supplied to the plurality of tanks is supplied from a small-capacity compressor having a smaller capacity than the compressor of the heat source unit. It is characterized by being a high-pressure gas refrigerant.
[0011]
The invention described in claim 1 has the following action.
Liquid refrigerant condensed by the cold heat of ice in the coil of the ice heat storage unit is stored in a plurality of tanks, and these liquid refrigerants are pumped to the heat exchanger on the use side by high-pressure gas refrigerant that is alternately supplied into the tanks. Since it is configured to be possible, a liquid pump that pumps the liquid refrigerant in the coil of the ice heat storage unit to the use-side heat exchanger is unnecessary, and therefore cavitation that may occur in the liquid pump can be reliably avoided, Reliability can be improved.
[0012]
The invention according to claim 2 has the following effects.
Since the high-pressure gas refrigerant between the compressor and the heat source side heat exchanger is alternately supplied to a plurality of tanks when the compressor of the heat source side unit is stopped, the compressor is not driven and almost no power is supplied. Further, the supercooled liquid refrigerant in the coil of the ice heat storage unit can be pumped to the use side heat exchanger.
[0013]
The invention according to claim 3 has the following effects.
[0014]
Since the high-pressure gas refrigerant supplied from the small-capacity compressor having a smaller capacity than the compressor of the heat source side unit is alternately supplied to the plurality of tanks, the small-capacity compressor may be a general-purpose compressor. Since it is not necessary to change the specification according to the type of the parts, it is possible to share the parts and reduce the cost.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0016]
[A] First Embodiment FIG. 1 is a pipeline diagram showing a first embodiment of an air conditioner equipped with an ice heat storage tank according to the present invention.
[0017]
The air conditioner 20 shown in FIG. 1 includes a heat source side unit 21, an ice heat storage unit 22, and a use side unit 23. The refrigerant pipe 24 of the heat source side unit 21 is connected to the refrigerant pipe 27 of the usage side unit 23 via the refrigerant pipes 25 and 26 of the ice heat storage unit 22.
[0018]
The heat source side unit 21 is configured by sequentially connecting a compressor 28, a four-way valve 29, a heat source side heat exchanger 30, and an electric expansion valve 31 to a refrigerant pipe 24. The use side unit 23 is configured by arranging a use side heat exchanger 32 and an electric expansion valve 33 in the refrigerant pipe 27, and the opening degree of the electric expansion valve 33 is adjusted according to the air conditioning load.
[0019]
The ice heat storage unit 22 includes an ice heat storage tank 35 in which a coil 34 is accommodated, and a first opening / closing valve 36 is disposed in the refrigerant pipe 25 and a second opening / closing valve 37 is disposed in the refrigerant pipe 26. Furthermore, one end of a coil 34 is connected to the refrigerant pipe 25 via a connection pipe 38 closer to the use side unit 23 side than the position where the first on-off valve 36 is disposed, and an electric expansion valve 39 is connected to the connection pipe 38. Arranged. In addition, the other end of the coil 34 is connected to the use side unit 23 side of the refrigerant pipe 26 at the position where the second on-off valve 37 is disposed via a connection pipe 41 provided with the third on-off valve 40.
[0020]
The ice heat storage tank 35 is filled with water, and the coil 34 is disposed in the ice heat storage tank 35 in a submerged state. In the coil 34, the liquid refrigerant flows from the heat source side heat exchanger 30 and evaporates during the ice making operation of the air conditioner 20, thereby forming ice attached to the outer periphery of the coil 34.
[0021]
Two surge tanks 43 A and 43 B are connected in parallel between the electric expansion valve 39 and the coil 34 to the connection pipe 38 through a bifurcated branch pipe 42. These surge tanks 43 A and 43 B are connected between the position where the first opening / closing valve 36 is disposed and the connection position of the connection pipe 38 in the refrigerant pipe 25 via the junction pipe 44. Thus, the surge tanks 43A and 43B are disposed between the coil 34 in the ice heat storage tank 35 and the use side heat exchanger 32, and are condensed by the cold stored in the ice in the ice heat storage tank 35. A liquid refrigerant is provided so as to be stored.
[0022]
The branch pipe 42 has inflow side check valves 45A and 45B on the inflow side of the surge tanks 43A and 43B, and the junction pipe 44 has outflow side check valves 46A and 46B on the outflow side of the surge tanks 43A and 43B. Are arranged respectively. These inflow side check valves 45A and 45B allow the flow of refrigerant flowing only from the coil 34 of the ice heat storage tank 35 to the surge tanks 43A and 43B, and the outflow side check valves 46A and 46B are surge tanks 43A and 43B. The flow of the refrigerant that flows only to the use side heat exchanger 32 side is allowed.
[0023]
The surge tanks 43 A and 43 B are connected via a branch pipe 47 between the four-way valve 29 and the heat source side heat exchanger 30 in the refrigerant pipe 24 of the heat source side unit 21. In the branch pipe 47, a first tank opening / closing valve 49 is disposed at a branching portion 48A connected to the surge tank 43A, and a second tank opening / closing valve 50 is disposed at a branching portion 48B connected to the surge tank 43B. The
[0024]
The first tank opening / closing valve 49 and the second tank opening / closing valve 50 are selectively opened / closed, whereby the high-pressure gas refrigerant between the compressor 28 and the heat source side heat exchanger 30 when the compressor 28 is stopped. However, it is comprised so that it can supply alternately in surge tank 43A, 43B. Thereby, the liquid refrigerant stored in the surge tanks 43 A and 43 B is provided so as to be capable of being pumped to the use side heat exchanger 32.
[0025]
Next, the ice making operation, the cooling and cooling operation, and the normal cooling operation of the air conditioner 20 will be described.
[0026]
[A-1] Ice making operation The ice making operation of the air conditioner 20 is performed by, for example, supplying the liquid refrigerant from the heat source side heat exchanger 30 to the ice heat storage tank 35 during a time when the electricity rate is low from 10:00 to 8:00 the next morning. This is an operation for supplying ice into the coil 34 and making ice in the ice heat storage tank 35.
[0027]
In this case, the electric expansion valve 33, the first tank on-off valve 49, and the second tank on-off valve 50 are closed, and the first on-off valve 36, the second on-off valve 37, the third on-off valve 40, and the electric expansion valve 39 are closed. Is opened.
[0028]
In this state, when the compressor 28 of the heat source side unit 21 is operated, the gas refrigerant discharged from the compressor 28 is condensed in the heat source side heat exchanger 30 and decompressed through the electric expansion valves 31 and 39. And flows into the coil 34 of the ice heat storage tank 35. The refrigerant that has flowed into the coil 34 evaporates and is formed with ice attached to the outer periphery of the coil 34. Thereafter, the gas refrigerant in the coil 34 reaches the four-way valve 29 through the connection pipe 41 and the refrigerant pipe 26 and is returned to the compressor 28.
[0029]
[A-2] Cooling and cooling operation The cooling and cooling operation of the air conditioner 20 is performed by, for example, a surge tank 43A that is liquefied by the cold heat of ice in the coil 34 of the ice heat storage tank 35 during the time when the daytime temperature rises. The liquid refrigerant stored in 43B is pumped from the surge tanks 43A and 43B to the use side heat exchanger 32.
[0030]
In this case, the first on-off valve 36, the second on-off valve 37, and the electric expansion valve 39 are closed, and the electric expansion valve 33 and the third on-off valve 40 are opened. Further, the compressor 28 of the heat source side unit 21 is in a stopped state after the ice making operation is finished.
[0031]
In this state, the first tank opening / closing valve 49 and the second tank opening / closing valve 50 are selectively opened / closed. For example, when the first tank opening / closing valve 49 is opened (the second tank opening / closing valve 50 is closed), the high-pressure gas refrigerant between the compressor 28 of the heat source side unit 21 and the heat source side heat exchanger 30 becomes the first. It flows into the surge tank 43A through the tank opening / closing valve 49. Thereby, the stored liquid refrigerant in the surge tank 43A flows into the use side heat exchanger 32 through the outflow side check valve 46A, the junction pipe 44, and the refrigerant pipes 25 and 27. The liquid refrigerant stored in the surge tank 43 A is a liquid refrigerant that passes through the coil 34 of the ice heat storage tank 35 and is condensed by the cold heat stored in the ice in the ice heat storage tank 35. By evaporating inside, the room is efficiently cooled by heat radiation (cooling) of the ice and the latent heat of evaporation.
[0032]
The gas refrigerant evaporated in the use side heat exchanger 32 flows into the coil 34 of the ice heat storage tank 35 through the connection pipe 41 and the third on-off valve 40, and is liquidated by the ice in the ice heat storage tank 35 as described above. It becomes a refrigerant and flows into the surge tank 43B through the inflow side check valve 45B.
[0033]
At this time, since the inside of the surge tank 43A is at a high pressure, the liquid refrigerant in the coil 34 of the ice heat storage tank 35 flows into the surge tank 43B without flowing into the surge tank 43A. Similarly, since the pressure in the surge tank 43B is lower than that in the surge tank 43A, the stored refrigerant in the surge tank 43B does not flow out to the use side heat exchanger 32 through the outflow check valve 46B.
[0034]
When the stored refrigerant in the surge tank 43A falls to a predetermined value or less, the first tank opening / closing valve 49 is closed, and the second tank opening / closing valve 50 is opened. Then, the liquid refrigerant stored in the surge tank 43B flows into the use side heat exchanger 32 through the outflow side check valve 46B, the junction pipe 44, the refrigerant pipes 25 and 27, and the electric expansion valve 33, and evaporates. As described above, the room is efficiently cooled by cooling and latent heat of vaporization. The gas refrigerant from the use-side heat exchanger 32 is condensed by the cold heat of ice in the coil 34 of the ice heat storage tank 35 through the connection pipe 41 and the third on-off valve 40, and is branched into the branch pipe 42 and the inflow side check valve 45A. And then flows into the surge tank 43A.
[0035]
When the liquid refrigerant in the surge tank 43B falls below a predetermined value, the second tank on / off valve 50 is closed and the first tank on / off valve 49 is opened to repeat the above operation. At the time of carrying out this cooling operation, since the outside air temperature is generally high, the refrigerant temperature in the heat source side heat exchanger 30 is high, and a high pressure is provided between the compressor 28 and the heat source side heat exchanger 30 in the heat source side unit 21. The gas refrigerant is maintained for a long time, and the above-described cooling and cooling operation is continued.
[0036]
However, if the amount of refrigerant increases in the ice heat storage unit 22 during the above-described cooling cooling operation, the second opening / closing operation is performed while the first on-off valve 36 is kept closed in this cooling cooling operation state. The valve 37 is opened, the four-way valve 29 is set to the cooling position, the compressor 28 is operated, and the pump is downed. As a result, surplus refrigerant in the ice heat storage unit 22 is recovered, high-pressure gas refrigerant is secured between the compressor 28 and the heat source side heat exchanger 30 in the heat source side unit 21, and the above-described cooling and cooling operation is performed. Will continue again.
[0037]
[A-3] Normal cooling operation The normal cooling operation of the air conditioner 20 is a cooling operation that is performed without using the cold energy stored in the ice in the ice heat storage tank 35. The two-tank on-off valve 50, the electric expansion valve 39, and the third on-off valve 40 are closed, and the first on-off valve 36, the second on-off valve 37, and the electric expansion valves 31 and 33 are opened.
[0038]
When the compressor 28 is operated in this state, the gas refrigerant discharged from the compressor 28 is condensed in the heat source side heat exchanger 30, and the electric expansion valve 31, the refrigerant pipe 25 and the electric expansion valve 33 are passed through. Then, it flows into the use side heat exchanger 32, evaporates in the use side heat exchanger 32, cools the room by latent heat of evaporation, and then returns to the compressor 28 through the refrigerant pipe 26 and the four-way valve 29.
[0039]
Since the air conditioner 20 of the above embodiment is configured as described above, the following effects (1) and (2) are achieved.
[0040]
(1) The liquid refrigerant condensed in the coil 34 of the ice heat storage tank 35 due to the cold heat of the ice is stored in the surge tanks 43A and 43B, and these liquid refrigerants are alternately supplied into the surge tanks 43A and 43B. Since the gas refrigerant can be pumped to the use side unit 23, a circulation pump such as a liquid pump for pumping the liquid refrigerant in the coil 34 of the ice heat storage tank 35 to the use side unit 23 becomes unnecessary. Cavitation that may occur in the pump can be reliably avoided and reliability can be improved.
[0041]
(2) The first tank on-off valve 49 and the second tank on-off valve 50 are alternately opened and closed with the high-pressure gas refrigerant between the compressor 28 and the heat source side heat exchanger 30 when the compressor 28 of the heat source side unit 21 is stopped. Since it is operated and alternately supplied into the surge tanks 43A and 43B via the branch pipe 47, the compressor 28 is not driven and the liquid refrigerant in the coil 34 of the ice heat storage tank 35 is used almost without any power. It can be pumped to the exchanger 32.
[0042]
[B] Second Embodiment FIG. 2 is a pipeline diagram showing a second embodiment of an air conditioner equipped with an ice heat storage tank according to the present invention. In the second embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
[0043]
In the air conditioner 60 of the second embodiment, the branch pipe 47, the first tank on / off valve 49, and the second tank on / off valve 50 of the air conditioner 20 are deleted, and a small capacity compressor 61 and four-way compressor are used instead. The valve 62 is provided in the first pipe 63, the second pipe 64, the third pipe 65, and the fourth pipe 66. One end of each of the first pipe 63, the second pipe 64, the third pipe 65, and the fourth pipe 66 is connected to each port of the four-way valve 62, and the other ends of the first pipe 63 and the second pipe 64 are connected. The small capacity compressor 61 is connected to the discharge port and the suction port, respectively. The other ends of the third pipe 65 and the fourth pipe 66 are connected to the surge tanks 43A and 43B, respectively.
[0044]
By the switching operation of the four-way valve 62, the communication of the first pipe 63 and the third pipe 65, the communication of the second pipe 64 and the fourth pipe 66, the communication of the first pipe 63 and the fourth pipe 66, and the second pipe 64 and The communication of the third pipe 65 is selectively switched. The small capacity compressor 61 is a compressor having a smaller capacity (1/10 to 1/20) than the compressor 28 in the heat source side unit 21 and is operated only during the cooling and cooling operation of the air conditioner 60. The The refrigerant discharged from the small capacity compressor 61 has the same composition as the refrigerant discharged from the compressor 28 of the heat source side unit 21.
[0045]
Further, the inflow side check valves 45A and 45B and the outflow side check valves 46A and 46B of the air conditioner 20 are replaced with inflow side on / off valves 67A and 67B and outflow side on / off valves 68A and 68B, respectively. .
[0046]
During the ice making operation and the normal cooling operation, the inflow side on / off valves 67A and 67B and the outflow side on / off valves 68A and 68B are all closed, and the small capacity compressor 61 is stopped.
[0047]
During the cooling and cooling operation, the inflow side on / off valve 67A and the outflow side on / off valve 68B, and the inflow side on / off valve 67B and the outflow side on / off valve 68A are alternately opened / closed to operate the small capacity compressor 61. The four-way valve 62 is switched to a state where the first pipe 63 and the third pipe 65 are communicated and the second pipe 64 and the fourth pipe 66 are communicated, and the inflow side on-off valve 67B and the outflow side on-off valve 68A are opened. When the inflow side on / off valve 67A and the outflow side on / off valve 68B are operated to close, the high-pressure gas refrigerant discharged from the small-capacity compressor 61 passes through the first pipe 63, the four-way valve 62, and the third pipe. It flows into the surge tank 43A through 65. Thereby, the liquid refrigerant stored in the surge tank 43A and condensed by the cold heat of the ice in the ice heat storage tank 35 passes through the outflow side on-off valve 68A, the junction pipe 44, the refrigerant pipe 25, etc., and the use side heat exchanger 32. And is evaporated by the use side heat exchanger 32 to cool the room. The gas refrigerant evaporated in the use side heat exchanger 32 passes through the connection pipe 41 and the third on-off valve 40 into the coil 34 of the ice heat storage tank 35 and becomes liquid refrigerant by the cold heat of ice, and becomes the inflow side. It is stored in the surge tank 43B via the on-off valve 67B.
[0048]
When the liquid refrigerant in the surge tank 43A falls below a predetermined value, the four-way valve 62 is switched to bring the first pipe 63 and the fourth pipe 66 into communication, and the second pipe 64 and third pipe 65 are put into communication. Further, when the inflow side on / off valve 67A and the outflow side on / off valve 68B are opened and the inflow side on / off valve 67B and the outflow side on / off valve 68A are closed, the high-pressure gas refrigerant discharged from the small capacity compressor 61 is opened. Flows into the surge tank 43B through the first pipe 63, the four-way valve 62, and the fourth pipe 66. Thereby, the liquid refrigerant stored in the surge tank 43B is pumped to the use side heat exchanger 32 via the outflow side opening / closing valve 68B, the junction pipe 44, the refrigerant pipe 25, etc., and in this use side heat exchanger 32 It evaporates and the room is allowed to cool and cool. The gas refrigerant evaporated in the use side heat exchanger 32 passes through the coil 34 of the ice heat storage tank 35 and is condensed by the cold heat of the ice, and is stored in the surge tank 43A via the inflow side opening / closing valve 67A.
[0049]
When the liquid refrigerant in the surge tank 43B drops below a predetermined value, the four-way valve 62 is switched, and the above operation is repeated to continue the cooling and cooling operation.
[0050]
Therefore, the air conditioner 60 of the second embodiment also exhibits the following effect (3) in addition to the same effect as the effect (1) of the above embodiment.
[0051]
(3) The high pressure gas refrigerant supplied from the small capacity compressor 61 having a smaller capacity than the compressor 28 of the heat source side unit 21 is alternately supplied into the surge tanks 43A and 43B by the switching operation of the four-way valve 62. The small-capacity compressor 61 may be a general-purpose compressor, and it is not necessary to change the specifications according to the type of the refrigerant. Therefore, the parts can be shared and the cost can be reduced.
[0052]
As mentioned above, although this invention was demonstrated based on one Embodiment, this invention is not limited to this.
[0053]
For example, in the air conditioner 20 of the first embodiment, the inflow side check valves 45A and 45B and the outflow side check valves 46A and 46B are respectively the inflow side in the air conditioner 60 of the second embodiment. The on-off valves 67A and 67B and the outflow-side on-off valves 68A and 68B may be used. Further, the inflow-side on-off valves 67A and 67B and the outflow-side on-off valves 68A and 68B of the air conditioner 60 are respectively The inflow check valves 45A and 45B and the outflow check valves 46A and 46B may be used. Further, there may be three or more surge tanks 43A and 43B.
[0054]
【The invention's effect】
As described above, according to the air conditioner including the ice heat storage tank according to the present invention, a plurality of tanks capable of storing refrigerant are arranged in parallel between the coil in the ice heat storage tank and the use side heat exchanger. The liquid refrigerant in the coil is stored in the tank and can be pumped to the use-side heat exchanger by the high-pressure gas refrigerant that is alternately supplied into the tank. The liquid pump that pumps the liquid refrigerant in the coil of the heat storage unit to the use-side heat exchanger is not required, and cavitation that may occur in the liquid pump can be reliably avoided, so that reliability can be improved.
[Brief description of the drawings]
FIG. 1 is a pipe line diagram showing a first embodiment of an air conditioner equipped with an ice heat storage tank according to the present invention.
FIG. 2 is a pipe line diagram showing a second embodiment of an air conditioner equipped with an ice heat storage tank according to the present invention.
FIG. 3 is a pipe diagram showing an air conditioner equipped with a conventional ice heat storage tank.
[Explanation of symbols]
20 air conditioner 21 heat source side unit 22 ice heat storage unit 23 use side unit 28 compressor 29 four-way valve 32 use side heat exchanger 34 coil 35 ice heat storage tank 43A, 43B surge tank 49 first tank opening / closing valve 50 second tank opening / closing Valve 60 Air conditioner 61 Small capacity compressor 62 Four-way valve

Claims

A heat source side unit having a compressor and a heat source side heat exchanger, an ice heat storage unit in which a coil is placed in a submerged state in an ice heat storage tank and ice can be formed on the outer periphery of the coil, and a use side heat exchanger. In an air conditioner having an ice heat storage tank that can be used for ice making operation and cooling operation,
A plurality of tanks capable of storing refrigerant are arranged in parallel between the coil in the ice storage tank and the use side heat exchanger, and the liquid refrigerant condensed in the coil is stored in the tank. An air conditioner equipped with an ice heat storage tank that is configured to be capable of being pumped to the use side heat exchanger by high-pressure gas refrigerant that is alternately supplied into these tanks.

The high pressure gas refrigerant supplied alternately to the plurality of tanks is a high pressure gas refrigerant between the compressor and the heat source side heat exchanger when the compressor of the heat source side unit is stopped. An air conditioner comprising the ice heat storage tank according to 1.

The high-pressure gas refrigerant that is alternately supplied to the plurality of tanks is a high-pressure gas refrigerant that is supplied from a small-capacity compressor having a capacity smaller than that of the compressor of the heat source side unit. Air conditioner with ice storage tank.