JP3596347B2 - Refrigeration air conditioner and control method thereof - Google Patents

Refrigeration air conditioner and control method thereof Download PDF

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JP3596347B2
JP3596347B2 JP10738599A JP10738599A JP3596347B2 JP 3596347 B2 JP3596347 B2 JP 3596347B2 JP 10738599 A JP10738599 A JP 10738599A JP 10738599 A JP10738599 A JP 10738599A JP 3596347 B2 JP3596347 B2 JP 3596347B2
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refrigerant
side refrigerant
heat
heat exchanger
cycle
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JP2000002474A (en
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誠司 井上
愛一郎 加藤
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Mitsubishi Electric Corp
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Description

【０００１】
【発明の属する技術分野】
本発明は、熱源側冷媒サイクルと利用側冷媒サイクルの間で熱交換することによって加熱を行う冷凍空調装置に係わり、例えば、住宅の冷暖房などに用いられる冷凍空調装置およびその制御方法に関するものである。
【０００２】
【従来の技術】
以下に、特開昭６２−２３８９５４号公報記載の従来の冷凍空調装置として例えば冷暖房装置について説明する。
図３１において、８１は圧縮機、８２は四方弁、８３は熱源側熱交換器、８４は冷房用減圧装置、８５は暖房用減圧装置、８６は暖房時に冷房用減圧装置８４が設けられた回路を閉止する逆止弁、８７は冷房時に暖房用減圧装置８５が設けられた回路を閉止する逆止弁、８８は第１補助熱交換器で、これらを環状に連接し、熱源側冷媒サイクルを形成している。８９は第２補助熱交換器で、第１補助熱交換器８８と熱交換するように一体に形成されている。９０は冷媒貯留タンクで冷房時と暖房時の冷媒量を調整する。９１は冷房時と暖房時で冷媒の流出方向が反対となる可逆特性を有する。第２補助熱交換器８９、冷媒貯留タンク９０、冷媒搬送装置９１は熱源側冷媒サイクルと共に室外ユニットｆに収納されている。９２ａ、９２ｂは、例えば２台の利用側熱交換器で、２つの室内ユニットｇ，ｈに収納され、接続配管ｉ，ｉ’、ｊ，ｊ’で室外ユニットｆと接続されている。第２補助熱交換器８９、冷媒貯留タンク９０、冷媒搬送装置９１、利用側熱交換器９２ａ，９２ｂおよび接続配管ｉ，ｉ’、ｊ，ｊ’を環状に連接し利用側冷媒サイクルを形成している。
【０００３】
つぎに、動作について説明する。
冷房運転時は図中実線矢印で示す冷媒サイクルとなり、熱源側冷媒サイクルでは、圧縮機８１からの高温高圧ガスは四方弁８２を通り熱源側熱交換器８３で放熱すると同時に凝縮液化する。さらに、逆止弁８６を通って冷房用減圧装置８４で減圧され第１補助熱交換器８８で蒸発して四方弁８２を通り圧縮機８１へ循環する。この時利用側冷媒サイクルの第２補助熱交換器８９と第１補助熱交換器８８が熱交換し、利用側冷媒サイクル内のガス冷媒が冷却されて液化し、冷媒貯留タンク９０を通って冷媒搬送装置９１に送られる。さらに冷媒は、冷媒搬送装置９１によって接続配管ｉ，ｊを通って利用側熱交換器９２ａ，９２ｂへ送られて吸熱蒸発してその設置空間を冷房する。冷媒は蒸発によりガス化して接続配管ｉ’，ｊ’を通って第２補助熱交換器８９に循環することになる。
【０００４】
一方、暖房運転時においては、図中破線矢印で示す冷媒サイクルとなり、熱源側冷媒サイクルでは、圧縮機８１からの高温高圧ガスは四方弁８２を通り第１補助熱交換器８８に送られ、放熱すると同時に凝縮液化する。さらに、逆止弁８７を通って暖房用減圧装置８５で減圧され熱源側熱交換器８３で吸熱蒸発して四方弁８２を通って圧縮機８１へ循環する。この時利用側冷媒サイクルの第２補助熱交換器８９と第１補助熱交換器８８が熱交換し、利用側冷媒サイクル内の液冷媒が加熱されてガス化し、接続配管ｉ’，ｊ’を通って利用側熱交換器９２ａ，９２ｂへ送られ、放熱凝縮してその設置空間を暖房する。冷媒は凝縮により液化して接続配管ｉ，ｊを通って冷媒搬送装置９１へ送られ、冷媒貯留タンク９０から第２補助熱交換器８９に循環する。
【０００５】
【発明が解決しようとする課題】
従来の冷暖房装置などの冷凍空調装置は、暖房のような加熱運転を連続して行っていると、熱源側熱交換器８３の表面に霜がついてくる。熱源側熱交換器８３に霜がつくと、熱交換効率が悪くなるので、加熱運転を連続して行う場合に、所定時間例えば１時間に１度程度で、除霜運転を行っている。除霜運転では、熱源側冷媒サイクルは冷房を行なう冷却運転と同じ冷媒サイクルで運転される。このため、第２補助熱交換器８９から第１補助熱交換器８８へ吸熱作用を生じ、利用側冷媒サイクルの冷媒搬送装置９１を運転すると利用側熱交換器９２ａ，９２ｂで加熱対象である室内空気の熱を奪ってしまい、室温の低下や、暖房運転中の冷風感などにより室内空間の快適性が損なわれる。また、利用側冷媒サイクルの冷媒搬送装置９１を運転しなくても、第２補助熱交換器８９で利用側冷媒が凝縮液化され圧力が低下することにより、接続配管ｉ’，ｊ’を通って利用側熱交換器９２ａ，９２ｂで液冷媒が蒸発して室内空気から熱を奪い、同様に快適性が損なわれるという問題点があった。
【０００６】
また、上記のような構成の従来の冷凍空調装置では、利用側冷媒サイクル中の冷媒搬送装置９１は、冷房を行う冷却運転と暖房を行う加熱運転とで冷媒流出方向が逆になる特性を有する特殊なものであるため高価となる。
また、通常の冷凍空調装置に用いられている冷媒は、潜熱を利用するものでエネルギー効率がよいが、これらの冷媒を用いると、以下のような問題点を生じる。例えば、ＨＣＦＣ（ハイドロクロロフルオロカーボン）冷媒はわずかではあるがオゾン層を破壊し、ＨＦＣ（ハイドロフルオロカーボン）冷媒は地球温暖化係数が大きく高価である。また、オゾン層も破壊せず地球温暖化係数も小さいＨＣ（炭化水素系）冷媒は可燃性を有し、アンモニア冷媒は毒性を有するため、配管接続時の安全性確保にコストがかかるなど、取り扱いに注意を要する。
【０００７】
本発明は、上記のような問題点を解決するためになされたもので、熱源側冷媒サイクルの除霜運転に対して利用側冷媒サイクルでの加熱運転時の冷媒温度を安定させ、例えば利用側熱交換器で室内の暖房などを行う時の室内の快適性を損なうのを防止でき、また、快適性を向上できる冷凍空調装置およびその制御方法を得ることを目的としている。
また、ＨＣＦＣ冷媒、ＨＦＣ冷媒、ＨＣ冷媒、アンモニア冷媒など、使用に問題がある冷媒の使用量を最小限に抑えることができ、安価で安全な冷凍空調装置およびその制御方法を得ることを目的としている。
【０００８】
【課題を解決するための手段】
本発明の請求項１に係わる冷凍空調装置は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルを除霜運転するときの前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持するように前記利用側冷媒の量を充填したことを特徴とするものである。
【０００９】
また、本発明の請求項２に係わる冷凍空調装置は、熱源側冷媒サイクルの除霜運転によって補助熱交換器で利用側冷媒サイクルから奪われる熱量をＱｄ、利用側冷媒の量をＷ、前記利用側冷媒の比熱をＣｐとし、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルで除霜運転されるとき、Ｑｄ／（Ｗ・Ｃｐ）で表される前記利用側冷媒の温度低下が所定温度以下になるように前記利用側冷媒の量Ｗを充填して、前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持することを特徴とするものである。
【００１０】
また、本発明の請求項３に係わる冷凍空調装置は、利用側冷媒サイクルに設けられ熱源側冷媒サイクルで得た温熱を蓄熱する蓄熱手段を備え、前記熱源側冷媒サイクルの除霜運転によって前記補助熱交換器で前記利用側冷媒サイクルから奪われる熱量をＱｄ、前記除霜運転によって前記蓄熱手段から放熱する熱量をＱｔ、前記利用側冷媒の量をＷ、前記利用側冷媒の比熱をＣｐとし、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルで除霜運転されるとき、（Ｑｄ−Ｑｔ）／（Ｗ・Ｃｐ）で表される前記利用側冷媒の温度低下が所定温度以下になるように前記利用側冷媒の量Ｗを充填すると共に前記蓄熱手段の蓄熱容量を設定して、前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持することを特徴とするものである。
【００１１】
また、本発明の請求項４に係わる冷凍空調装置は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記利用側冷媒サイクル内に前記利用側冷媒を貯留する冷媒貯留タンクを設け、前記冷媒貯留タンクの内容積を、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルを除霜運転するときの前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持するように、前記利用側冷媒の量または蓄熱材の量を蓄えられる内容積としたものである。
【００１２】
また、本発明の請求項５に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環させて成る熱源側冷媒サイクルと、前記第１補助熱交換器と熱交換する第２補助熱交換器、冷媒貯留タンク、冷媒搬送装置、および利用側熱交換器を連接し利用側冷媒を循環させて成る利用側冷媒サイクルとを有し、前記圧縮機、前記流路切換弁、前記熱源側熱交換器、前記熱源側冷媒流量制御弁、前記第１補助熱交換器、前記第２補助熱交換器、前記冷媒貯留タンク、および前記冷媒搬送装置を一つのユニット内に収納したことを特徴とするものである。
【００１３】
また、本発明の請求項６に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環させて成る熱源側冷媒サイクルと、前記第１補助熱交換器と熱交換する第２補助熱交換器、冷媒貯留タンク、冷媒搬送装置、および利用側熱交換器を連接し利用側冷媒を循環させて成る利用側冷媒サイクルとを有し、前記圧縮機、前記流路切換弁、前記熱源側熱交換器、および前記熱源側冷媒流量制御弁を一つのユニット内に収納し、前記第１補助熱交換器、前記第２補助熱交換器、前記冷媒貯留タンク、および前記冷媒搬送装置を前記ユニットとは別の一つのユニット内に収納し、前記第１補助熱交換器の一端側と前記流路切換弁との間および前記第１補助熱交換器の他端側と前記熱源側冷媒流量制御弁との間をそれぞれ接続配管で接続したことを特徴とするものである。
【００１４】
また、本発明の請求項７に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環して成る熱源側冷媒サイクルと、第１の冷媒搬送装置、前記第１補助熱交換器と熱交換する第２補助熱交換器、および前記冷媒貯留タンクを連接し利用側冷媒を循環して成る熱輸送サイクルと、第２の冷媒搬送装置、利用側熱交換器、および前記冷媒貯留タンクを連接し前記利用側冷媒を循環して成る利用側冷媒サイクルとを有し、前記熱輸送サイクルにおいて前記第２補助熱交換器で前記第１補助熱交換器と熱交換して得た温熱を前記冷媒貯留タンクに蓄え、前記利用側冷媒サイクルにおいて前記冷媒貯留タンクに蓄えた温熱を前記利用側熱交換器で加熱に利用することを特徴とするものである。
【００１５】
また、本発明の請求項８に係わる冷凍空調装置は、冷媒貯留タンクの内部を左右に分割すると共に、喫水面よりも下側で前記分割された左右の利用側冷媒が連通可能な連通部を有する仕切りを備え、分割された左右の槽のそれぞれに２つの開口を設け、前記冷媒貯留タンクの一方の槽の２つの開口を、利用側熱交換器からの利用側冷媒の流入口と、第２補助熱交換器への前記利用側冷媒の流出口とし、前記冷媒貯留タンクの他方の槽の２つの開口を、前記第２補助熱交換器からの前記利用側冷媒の流入口と、前記利用側熱交換器への前記利用側冷媒の流出口としたことを特徴とするものである。
【００１６】
また、本発明の請求項９に係わる冷凍空調装置は、熱源側冷媒と利用側冷媒とを熱交換する補助熱交換器は、プレート式熱交換器であることを特徴とするものである。
【００１７】
また、本発明の請求項１０に係わる冷凍空調装置は、冷却運転と加熱運転とで、熱源側冷媒サイクルと利用側冷媒サイクルの間の補助熱交換器における利用側冷媒の流れ方向を切換える切換手段を備え、前記補助熱交換器で熱交換する際の熱源側冷媒と利用側冷媒の流れ方向が、冷却運転時および加熱運転時で共に対向流となるように構成したことを特徴とするものである。
【００１８】
また、本発明の請求項１１に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および補助熱交換器を連接し熱源側冷媒を循環して成る熱源側冷媒サイクルと、利用側冷媒を貯留する冷媒貯留タンク、および冷媒搬送装置を連接し前記利用側冷媒を循環して成る利用側冷媒サイクルとを備え、前記補助熱交換器を前記冷媒貯留タンク内の利用側冷媒に浸漬して前記補助熱交換器で前記熱源側冷媒と前記利用側冷媒とを熱交換して前記冷媒貯留タンクに熱を蓄え、前記利用側冷媒サイクルにおいて前記冷媒貯留タンクに蓄えた熱を加熱に利用することを特徴とするものである。
【００１９】
また、本発明の請求項１２に係わる冷凍空調装置は、補助熱交換器における利用側冷媒の伝熱面積を熱源側冷媒の伝熱面積よりも大きくしたことを特徴とするものである。
【００２０】
また、本発明の請求項１３に係わる冷凍空調装置は、冷媒貯留タンク内の補助熱交換器周辺に気泡を吹き込む気泡吹き込み手段を備えたことを特徴とするものである。
【００２１】
また、本発明の請求項１４に係わる冷凍空調装置は、冷媒貯留タンクの外部に設けられ前記冷媒貯留タンクの高さが異なる位置を接続する利用側冷媒配管と、この利用側冷媒配管を流通する利用側冷媒を加熱する熱源装置を備えたことを特徴とするものである。
【００２２】
また、本発明の請求項１５に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、補助熱交換器、冷媒貯留タンク、および冷媒搬送装置を一つのユニット内に収納したことを特徴とするものである。
【００２３】
また、本発明の請求項１６に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、および熱源側冷媒流量制御弁を一つのユニット内に収納すると共に、補助熱交換器、冷媒貯留タンク、および冷媒搬送装置を前記ユニットとは別の一つのユニット内に収納し、前記補助熱交換器の一端側と前記流路切換弁との間および前記補助熱交換器の他端側と前記熱源側冷媒流量制御弁との間をそれぞれ接続配管で接続したことを特徴とするものである。
【００２４】
また、本発明の請求項１７に係わる冷凍空調装置は、利用側冷媒を貯留する冷媒貯留タンク内に蓄熱材を設けたことを特徴とするものである。
【００２５】
また、本発明の請求項１８に係わる冷凍空調装置は、冷媒貯留タンク内に配設され、その内部を左右に分割する仕切りを備えると共に、分割された一方の槽に設けた利用側冷媒が流入する開口と、他方の槽に設けた前記利用側冷媒が流出する開口を備え、前記仕切りは、前記冷媒貯留タンクの喫水面よりも下側で前記分割された左右の利用側冷媒が連通する連通部を有することを特徴とするものである。
【００２６】
また、本発明の請求項１９に係わる冷凍空調装置は、利用側冷媒が循環する部分に、前記利用側冷媒に混入した混入物を集めるフィルタを設けたことを特徴とするものである。
【００２７】
また、本発明の請求項２０に係わる冷凍空調装置は、フィルタを、利用側冷媒を貯留する冷媒貯留タンク内に設けたことを特徴とするものである。
【００２８】
また、本発明の請求項２１に係わる冷凍空調装置は、熱源側冷媒サイクルを２系統以上の複数としたことを特徴とするものである。
【００２９】
また、本発明の請求項２２に係わる冷凍空調装置は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、その少なくとも１系統の熱源側冷媒サイクルを加熱専用の冷媒サイクルで構成したことを特徴とするものである。
【００３０】
また、本発明の請求項２３に係わる冷凍空調装置は、利用側冷媒サイクルに対して複数の熱源側冷媒サイクルを並列に接続したことを特徴とするものである。
【００３１】
また、本発明の請求項２４に係わる冷凍空調装置は、利用側冷媒サイクルに対して複数の熱源側冷媒サイクルを直列に接続したことを特徴とするものである。
【００３２】
また、本発明の請求項２５に係わる冷凍空調装置は、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却／加熱併用の冷媒サイクルとを直列に接続したことを特徴とするものである。
【００３３】
また、本発明の請求項２６に係わる冷凍空調装置は、利用側冷媒サイクルを循環する利用側冷媒の流れの向きに対して冷却／加熱併用の冷媒サイクルを上流側に接続し、加熱専用の冷媒サイクルを下流側に接続したことを特徴とするものである。
【００３４】
また、本発明の請求項２７に係わる冷凍空調装置は、利用側冷媒サイクルを循環する利用側冷媒の流れの向きに対して加熱専用の冷媒サイクルを上流側に接続し、冷却／加熱併用の冷媒サイクルを下流側に接続したことを特徴とするものである。
【００３５】
また、本発明の請求項２８に係わる冷凍空調装置は、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却／加熱併用の冷媒サイクルとを並列に接続すると共に、冷却運転時には加熱専用の冷媒サイクルと熱交換する利用側補助熱交換器には利用側冷媒が流れないように、前記利用側冷媒サイクルの冷媒流路を切換える切換手段を備えたことを特徴とするものである。
【００３６】
また、本発明の請求項２９に係わる冷凍空調装置は、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却専用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却専用の冷媒サイクルとを直列に接続したことを特徴とするものである。
【００３７】
また、本発明の請求項３０に係わる冷凍空調装置は、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却専用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却専用の冷媒サイクルとを並列に接続すると共に、加熱運転時には前記加熱専用の冷媒サイクルと熱交換する利用側補助熱交換器に利用側冷媒を循環させ、冷却運転時には冷却専用の冷媒サイクルと熱交換する利用側補助熱交換器に利用側冷媒を循環させるように、前記利用側冷媒サイクルの冷媒流路を切換える切換手段を備えたことを特徴とするものである。
【００３８】
また、本発明の請求項３１に係わる冷凍空調装置は、利用側冷媒が循環する加熱専用の熱源装置と、加熱運転時に前記加熱専用の熱源装置に前記利用側冷媒を循環させるように前記利用側冷媒サイクルの冷媒流路を切換える切換手段とを備えたことを特徴とするものである。
【００３９】
また、本発明の請求項３２に係わる冷凍空調装置は、利用側冷媒サイクルに、熱源側冷媒サイクルにより熱を供給される冷却用の利用側熱交換器と、加熱専用の熱源装置により熱を供給される加熱用の利用側熱交換器とを設け、冷却運転時に前記熱源側冷媒サイクルと前記冷却用の利用側熱交換器を動作させ、加熱運転時に前記加熱専用の熱源装置と前記加熱用の利用側熱交換器を動作させるように構成したことを特徴とするものである。
【００４０】
また、本発明の請求項３３に係わる冷凍空調装置は、冷却用の利用側熱交換器は、空気の流れに対し、加熱用の利用側熱交換器の上流側に並べて配置し、除湿運転時に冷却用および加熱用の利用側熱交換器を動作させるように構成したことを特徴とするものである。
【００４１】
また、本発明の請求項３４に係わる冷凍空調装置は、加熱専用の熱源装置は、利用側冷媒を直接的に加熱する加熱装置であることを特徴とするものである。
【００４２】
また、本発明の請求項３５に係わる冷凍空調装置は、利用側冷媒サイクルを構成する配管において、利用側熱交換器への送り側配管と前記利用側熱交換器からの戻り側配管とで、該配管の配管径、若しくは該配管の継ぎ手の径または形状を異なるように構成したことを特徴とするものである。
【００４３】
また、本発明の請求項３６に係わる冷凍空調装置は、利用側冷媒サイクル内に複数の利用側熱交換器を設け、それらの利用側熱交換器を全て互いに並列に接続したことを特徴とするものである。
【００４４】
また、本発明の請求項３７係わる冷凍空調装置は、利用側冷媒サイクル内に複数の利用側熱交換器を設け、それらの利用側熱交換器のうちの少なくとも一部を互いに直列に接続したことを特徴とするものである。
【００４５】
また、本発明の請求項３８に係わる冷凍空調装置の制御方法は、利用側冷媒サイクルを循環する冷媒は、水、若しくはエチレングリコール、プロピレングリコール、およびＤ−ソルビトールのうちのいずれか１つまたは複数を重量比で数十％以下含む水溶液であることを特徴とするものである。
【００４６】
また、本発明の請求項３９に係わる冷凍空調装置は、熱源側冷媒サイクルを蒸気圧縮式冷凍サイクルで構成し、前記熱源側冷媒サイクルを循環する冷媒は潜熱を利用するものとし、フロン系の単一冷媒、フロン系の擬似共沸混合冷媒、フロン系の非共沸冷媒、炭化水素系冷媒、およびアンモニア冷媒のうちのいずれか１つであることを特徴とするものである。
【００４７】
また、本発明の請求項４０に係わる冷凍空調装置の制御方法において、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルの容量を複数の段階に変化するように構成し、その容量の変化幅を容量が増加するにつれて大きくなるようにしたことを特徴とするものである。
【００４８】
また、本発明の請求項４１に係わる冷凍空調装置の制御方法は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、前記利用側冷媒サイクルで加熱運転中に前記熱源側冷媒サイクルのうち１系統以上が除霜運転している間に、少なくとも１系統の前記熱源側冷媒サイクルは加熱運転を継続するように制御することを特徴とするものである。
【００４９】
また、本発明の請求項４２に係わる冷凍空調装置の制御方法は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、前記熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルとをそれぞれ１系統以上設け、前記冷却／加熱併用の冷媒サイクルに蒸気圧縮式冷凍サイクルを用い、加熱運転中に前記冷却／加熱併用の冷媒サイクルのうちの１系統以上が除霜運転している間に、前記加熱専用の冷媒サイクルと前記冷却／加熱併用の冷媒サイクルのうちの少なくとも１系統の冷媒サイクルは加熱運転を継続するように制御することを特徴とするものである。
【００５０】
また、本発明の請求項４３に係わる冷凍空調装置の制御方法は、熱源側冷媒サイクルのうちの１系統以上が除霜運転している間に加熱運転を継続する熱源側冷媒サイクルは、その加熱能力を増加して加熱運転を継続するように制御することを特徴とするものである。
【００５１】
また、本発明の請求項４４に係わる冷凍空調装置の制御方法は、熱源側冷媒サイクルのうちの１系統以上が除霜運転している間に加熱運転を継続する熱源側冷媒サイクルを、加熱専用の冷媒サイクルとしたことを特徴とするものである。
【００５２】
また、本発明の請求項４５に係わる冷凍空調装置の制御方法は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルとして蒸気圧縮式冷凍サイクルを２系統以上用い、前記利用側冷媒サイクルで加熱運転中に前記熱源側冷媒サイクルのうち１系統以上が除霜運転開始条件を満たした場合、除霜運転を開始する前に熱源側冷媒サイクルの能力を増大させて加熱運転を継続し、その後に除霜運転を行うように制御することを特徴とするものである。
【００５３】
また、本発明の請求項４６に係わる冷凍空調装置の制御方法は、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、前記複数系統の熱源側冷媒サイクルのそれぞれの容量を一つまたは複数の段階に変化するように構成し、かつ全体としての前記複数系統の熱源側冷媒サイクルの合計容量を複数の段階に変化するように構成し、その合計容量の変化幅を合計容量が増加するにつれて大きくなるようにしたことを特徴とするものである。
【００５４】
また、本発明の請求項４７に係わる冷凍空調装置の制御方法は、合計容量の段階を増加させる際に、複数系統の熱源側冷媒サイクルのうちの現行で運転している熱源側冷媒サイクルは運転状態のままで前記合計容量を増加させるものとし、前記合計容量の段階を減少させる際に、複数系統の熱源側冷媒サイクルのうちの現行で停止している熱源側冷媒サイクルは停止状態のままで前記合計容量を減少させるように制御することを特徴するものである。
【００５５】
また、本発明の請求項４８に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および熱源側冷媒を貯留する冷媒貯留タンクを連接し前記熱源側冷媒を循環して成る熱源側冷媒サイクルと、補助熱交換器、および冷媒搬送装置を連接し利用側冷媒を循環して成る利用側冷媒サイクルとを備え、前記補助熱交換器を前記冷媒貯留タンク内の熱源側冷媒に浸漬して前記補助熱交換器で前記熱源側冷媒と前記利用側冷媒とを熱交換し、前記冷媒貯留タンクに蓄えた熱を前記利用側冷媒サイクルにおいて加熱に利用することを特徴とするものである。
【００５６】
【発明の実施の形態】
実施の形態１．
以下、本発明の実施の形態１による冷凍空調装置として、例えば室内の冷暖房を行う冷暖房装置について説明する。冷暖房装置では、冷却運転で室内の冷房を行い、加熱運転で室内の暖房を行っており、冷却運転を冷房運転、加熱運転を暖房運転として記す。図１は本実施の形態による冷暖房装置を示す構成図である。図において、１１は圧縮機、１２は暖房運転と冷房運転で冷媒流路を切換える流路切換弁でここでは例えば四方弁を用いる。また、１３は熱源側熱交換器、１４は熱源側冷媒流量制御弁、１５はレシーバ、１６は第１補助熱交換器、１７は室外送風機で、これらは一つのユニット内に収納されて室外ユニットｆを構成し、屋外に設置されている。圧縮機１１の吐出口は四方弁１２の第１口に接続され、四方弁１２の第２口が熱源側熱交換器１３の一端に接続されている。熱源側熱交換器１３の他端は、熱源側冷媒流量制御弁１４、レシーバ１５の順に接続され、さらに第１補助熱交換器１６の一端に接続されている。第１補助熱交換器１６の他端は四方弁１２の第４口に接続されており、四方弁１２の第３口は圧縮機１１の吸入口に接続されており、熱源側冷媒サイクルを形成している。四方弁１２は熱源側冷媒サイクルの冷房運転および暖房運転を切換えるもので、図１の実線で示すように、その第１口と第２口、第３口と第４口が接続された場合が冷房運転になり、点線で示すように、その第１口と第４口、第３口と第２口が接続された場合が暖房運転になる。この四方弁１２の代わりに例えば４つの電磁弁を設けて冷房運転と暖房運転と冷媒の流路を切換えるように構成することもできる。また、レシーバ１５は、冷房時と暖房時の熱源側冷媒サイクルの必要冷媒量の差を吸収するために設けられている。
圧縮機を用いて冷媒回路に冷媒を循環させ、冷媒の凝縮及び蒸発を利用した構成の冷媒サイクルを、蒸気圧縮式冷凍サイクルと称している。
【００５７】
さらに、１９は第２補助熱交換器で第１補助熱交換器１６と熱交換するように一体に形成されている。２０は冷媒貯留タンクで利用側冷媒サイクルの冷房時と暖房時の冷媒量の差を調整している。この冷媒貯留タンク２０は、例えば金属やプラスチックで構成する。２１は冷媒搬送装置で例えばマグネットポンプである。第２補助熱交換器１９，冷媒貯留タンク２０，冷媒搬送装置２１は、熱源側冷媒サイクルと共に室外ユニットｆに収納されている。２２ａ、２２ｂは利用側熱交換器、２３ａ、２３ｂは利用側冷媒流量制御弁で例えば開閉弁または流量調整弁で構成され、この場合には例えば熱動弁を用いる。また、２４ａ，２４ｂは室内送風機である。利用側熱交換器２２ａ，熱動弁２３ａ，室内送風機２４ａは室内ユニットｇに収納されており、利用側熱交換器２２ｂ，熱動弁２３ｂ，室内送風機２４ｂは室内ユニットｈに収納されている。この室内ユニットｇ，ｈのそれぞれは、例えば空調したい部屋の内部に設置される床置型、壁掛け型、天井吊型のものや、また、空調したい部屋の外部に利用側熱交換器を設置して、室内に冷たい空気または暖かい空気を送るようなダクト式のものや、空調したい部屋の天井や壁への埋め込まれて用いられるものなどがある。
【００５８】
冷媒搬送装置２１の吐出口は、接続配管ｉの一端に接続されており、接続配管ｉの他端は分岐して、それぞれ接続配管ｊおよび接続配管ｋの一端に接続されている。接続配管ｊおよびｋの他端は、それぞれ、熱動弁２３ａおよび熱動弁２３ｂに接続されており、これらは利用側熱交換器２２ａおよび２２ｂの一端に接続されている。利用側熱交換器２２ａおよび２２ｂの他端は接続配管ｊ’および接続配管ｋ’の一端に接続され、これらの他端は共に接続配管ｉ’の一端に接続されており、接続配管ｉ’の他端は室外ユニットｆ内で第２補助熱交換器１９の一端に接続されている。第２補助熱交換器１９の他端は、冷媒貯留タンク２０の側面の流入口に接続されており、冷媒貯留タンク２０の底面に設けた流出口は冷媒搬送装置２１の吸入口に接続されている。第２補助熱交換器１９，冷媒貯留タンク２０，冷媒搬送装置２１、室内ユニットｇ，ｈおよびこれらを接続する配管で、利用側冷媒サイクルを形成している。また、３１は冷媒の温度を検出する温度検出手段で、例えば第１温度センサである。
【００５９】
本実施の形態に係わる冷暖房に適用した冷凍空調装置では、利用側冷媒サイクルの冷媒として、顕熱を利用する冷媒を用い、例えば水、若しくはエチレングリコール，プロピレングリコール，およびＤ−ソルビトールなどの溶媒のうちのいずれか１つまたは複数を重量比で数十％以下含んだ水溶液を用いる。エチレングリコール，プロピレングリコール，およびＤ−ソルビトールなどの溶媒のうちのいずれか１つまたは複数を重量比で０％より大きくかつ数十％以下含んだ水溶液は０［℃］以下になっても凍らない特性を有する不凍液である。
この利用側冷媒サイクルの冷媒に、エチレングリコール，プロピレングリコール，およびＤ−ソルビトールなどのうちのいずれかを重量比で０％より大きくかつ数十％以下含んだ水溶液である不凍液を用いると、外気温度が低く０［℃］以下になる地域に設置しても冷媒が凍るのを防止できる。図２に、例えばプロピレングリコール水溶液の濃度とその特性のグラフを示す。図２（ａ）は水溶液の濃度に対する凍結温度（℃）、図２（ｂ）は１０［℃］および４５［℃］のときの水溶液の濃度に対する動粘度、図２（ｃ）は１０［℃］および４５［℃］のときの水溶液の濃度に対する熱伝達率である。図２（ａ）に示すように、水溶液の濃度が高くなると凍結温度が下がり、外気温度がその分だけ低くなる地域で使用しても凍結しないという利点がある。ところが、一方では図２（ｂ）に示すように動粘度が上がり、図２（ｃ）に示すように熱伝達率が下がる。このため、利用側冷媒サイクルを循環する冷媒としては、濃度が数十％以下、例えば６０％程度以下とし、本実施の形態では例えば３０％程度の濃度の水溶液を使用する。
【００６０】
冷媒貯留タンク２０は利用側の冷媒の体積膨張を吸収するように大気に開放している。また、冷媒貯留タンク２０の流出口から冷媒搬送装置２１までの配管および冷媒搬送装置２１の位置はタンク内喫水面より下方に配置する。これは、冷媒貯留タンク２０の流出口から冷媒搬送装置２１までの配管および冷媒搬送装置２１の位置をタンク内喫水面より上方に配置すると、圧力損失が大きくなり、冷媒がスムーズに流れなくなったり、冷媒が冷媒搬送装置２１の吸入口で蒸発したりして必要な流量が得られないこともあり、これらを防止するためである。また、同様の理由から冷媒貯留タンク２０の流出口から冷媒搬送装置２１までの配管は太い方が望ましく、また短い方が望ましい。
以上に述べた利用側冷媒は、地球環境保全の点で問題なく、取り扱いも容易で、かつ安価な冷媒である。
【００６１】
一方、熱源側冷媒サイクルの冷媒は、通常の冷凍空調装置に用いられている、ＨＣＦＣ（ハイドロクロロフルオロカーボン）冷媒やＨＦＣ（ハイドロフルオロカーボン）などのフロン系冷媒、ＨＣ（炭化水素系）冷媒、アンモニア冷媒などを用いる。具体的には、例えばＨＣＦＣ冷媒であるＲ２２やＨＦＣ冷媒であるＲ１３４ａなどの単一冷媒、ＨＦＣ冷媒であるＲ４１０Ａなどの擬似共沸混合冷媒、ＨＦＣ冷媒であるＲ４０７Ｃなどの非共沸混合冷媒、ＨＣ冷媒であるプロパンやイソブタン、アンモニアを用いる。
【００６２】
上記のように利用側冷媒サイクルの冷媒と熱源側冷媒サイクルの冷媒とを分離して、利用側冷媒サイクルには顕熱を利用して熱輸送する冷媒、熱願側冷媒サイクルには潜熱を利用して熱輸送する冷媒というように異なるもので構成している。そして、熱源側にエネルギー効率のよい冷媒を用い、利用側にオゾン層破壊や地球温暖化において使用に問題のない顕熱を利用する冷媒を用いることにより、冷凍空調装置全体で、エネルギー効率はよいが使用に問題のある冷媒の使用量を極力少なくしている。
もちろん熱源側冷媒サイクルの冷媒として、二酸化炭素、水、空気などの自然冷媒などを用いたり、利用側冷媒サイクルの冷媒と同じもの、即ち、エチレングリコール，プロピレングリコール，およびＤ−ソルビトールのうちのいずれか１つまたは複数を重量比で数十％以下含んだ水溶液を用いてもよい。この場合にはエネルギー効率は低下するが、前述の地球環境保全や取扱の点で全く問題のない冷凍空調装置を構成できる。
【００６３】
つぎに、動作について説明する。
冷房運転時は図１の実線の冷媒サイクルとなり、熱源側冷媒サイクルでは、四方弁１２の第１口と第２口、および第３口と第４口が接続される。圧縮機１１から吐出された高温高圧の蒸気冷媒は四方弁１２を通り熱源側熱交換器１３で室外送風機１７によって送り込まれた外気へ放熱すると同時に凝縮液化し、冷媒流量制御弁１４を通って低圧低温の気液二相冷媒となり、レシーバ１５を経由して第１補助熱交換器１６で蒸発し低圧低温の蒸気冷媒となって四方弁１２を通り圧縮機１１へ循環する。この時利用側冷媒サイクルの第２補助熱交換器１９と前記第１補助熱交換器１６とが熱交換し、利用側冷媒サイクル内の冷媒が冷却される。この冷媒は冷媒貯留タンク２０を通って冷媒搬送装置２１に送られ、この冷媒搬送装置２１によって接続配管ｉおよびｊ、ｋを通って利用側熱交換器２２ａ，２２ｂへ送られる。利用側熱交換器２２ａおよび２２ｂでは、冷媒は、室内送風機２４ａ，２４ｂによって送り込まれた室内空気から吸熱して自らは加熱され、接続配管ｊ’，ｋ’およびｉ’を通って第２補助熱交換器１９に循環する。一方、利用側熱交換器２２ａおよび２２ｂに室内送風機２４ａおよび２４ｂによって送り込まれた室内空気は、利用側熱交換器２２ａおよび２２ｂで冷媒に放熱すると同時に冷却され、室内へ再び吹出されて室内を冷房する。
【００６４】
暖房運転時は、図中破線の冷媒サイクルとなり、熱源側冷媒サイクルでは、四方弁１２の第１口と第４口、および第３口と第２口が接続される。圧縮機１１から吐出された高温高圧の蒸気冷媒は四方弁１２を通り第１補助熱交換器１６に送られ、放熱すると同時に凝縮液化し、レシーバ１５を通って冷媒流量制御弁１４で減圧されて低圧低温の気液二相冷媒となり、熱源側熱交換器１３で室外送風機１７によって送り込まれた室外空気から吸熱して蒸発し、低圧低温の蒸気冷媒となって四方弁１２を通って圧縮機１１へ循環する。この時利用側冷媒サイクルの第２補助熱交換器１９と前記第１補助熱交換器１６とが熱交換し、利用側冷媒サイクル内の冷媒が加熱される。この冷媒は冷媒貯留タンク２０を通って冷媒搬送装置２１に送られ、この冷媒搬送装置２１によって接続配管ｉおよびｊ，ｋを通って利用側熱交換器２２ａおよび２２ｂへ送られる。利用側熱交換器２２ａおよび２２ｂでは、冷媒は、室内送風機２４ａおよび２４ｂによって送り込まれた室内空気へ放熱すると同時に冷却され自らは接続配管ｊ’，ｋ’およびｉ’を通って第２補助熱交換器１９に循環する。一方、利用側熱交換器２２ａおよび２２ｂに室内送風機２４ａおよび２４ｂによって送り込まれた室内空気は、利用側熱交換器２２ａおよび２２ｂで冷媒から吸熱して加熱され、室内へ再び吹出されて室内を暖房する。
【００６５】
また、暖房運転時に熱源側冷媒サイクルが除霜運転に入った場合は、熱源側冷媒サイクルは図中実線の冷房時の冷媒サイクルと同一となり、利用側冷媒サイクル中の冷媒の顕熱を奪って熱源側熱交換器１３の表面に着いた霜を加熱して除霜する。このとき、第２補助熱交換器１９で利用側冷媒サイクルから奪われる熱量Ｑｄ［ｋＪ］は、熱源側冷媒サイクルの１時間中の加熱量［ｋＪ］のおおよそ１／３０であることが実験的に得られている。また、この除霜運転中にも室内送風機２４ａ，２４ｂを回し続けると、室内の負荷によって冷媒の温度は下がる。この室内負荷による温度低下分の熱量ＱＬ ［ｋＪ］は、除霜運転時間と利用側冷媒サイクルの暖房能力とで演算できる。利用側冷媒の温度低下ΔＴ［Ｋ］は、利用側冷媒サイクルの冷媒量をＷ［ｋｇ］、比熱をＣｐ［ｋＪ／ｋｇＫ］とすると、式（１）で表される。
ΔＴ＝（Ｑｄ＋ＱＬ ）／（Ｗ・Ｃｐ） ・・・・・・・・・・・・（１）
【００６６】
例えば熱源側冷媒サイクルの暖房能力が９．６［ｋＷ］＝［ｋＪ／ｓ］とすると、除霜時に利用側冷媒サイクルから奪われる熱量はＱｄ＝９．６［ｋＪ／ｓ］×３６００［ｓ］／３０＝１１５２［ｋＪ］である。また、除霜運転を３分間行うとした時の室内負荷による温度低下分の熱量はＱＬ ＝（暖房運転中の暖房能力）［ｋＪ／ｓ］×６０［ｓ］×３［ｍｉｎ］で演算できる。通常は除霜運転に入るのはある程度暖房運転を行った後であり、暖房能力の最大で運転していることはないため、今、１台の室内ユニットが動作しており、例えば暖房能力＝１．５［ｋＪ／ｓ］で運転しているとすると、ＱＬ ＝２７０［ｋＪ］となる。利用側冷媒サイクル内の冷媒が水でその質量を２０［ｋｇ］とすると、水の比熱は４．１９［ｋＪ／ｋｇＫ］であるので、除霜中の利用側冷媒の温度低下はΔＴ＝１７．０［Ｋ］となる。即ち、冷媒貯留タンク２０の内容積が、冷房時と暖房時の必要冷媒量差を吸収するだけの内容積（水の温度変化に伴う比容積差を吸収する容積があればよく、ほとんど０）しかない場合は、除霜運転の３分程の間に除霜運転に必要な熱だけで利用側冷媒サイクルの冷媒温度が１７．０［Ｋ］も低下してしまうことになる。
この除霜運転の間に、室内ユニットｇ，ｈ内の送風機２４ａ，２４ｂを回し続けると吹き出し空気温度が低くなってしまい、冷風感や室温の低下をもたらすので、不快であった。また、室内ユニットｇ，ｈ内の送風機２４ａ，２４ｂを停止しても暖房が不可能となり室温の低下をもたらすため、利用側冷媒の温度を暖房に適した温度に維持できなくなり、快適性の点で著しく問題であった。
【００６７】
そこで、本実施の形態に係わる冷凍空調装置は、冷媒貯留タンク２０の内容積を利用側冷媒サイクルの冷媒量と同等以上の３０［ｋｇ］を保有できる内容積とした。即ち利用側冷媒の充填量を合計５０［ｋｇ］とし、熱源側冷媒サイクルの除霜運転に伴う利用側冷媒の温度低下が、従来の１７．０［Ｋ］から２／５の６．８［Ｋ］に抑えられる。この程度の温度低下であれば、冷風感や室温低下の心配がなく暖房に適した温度に維持できるので、熱源側冷媒サイクルが除霜運転していも、室内送風機を止めるなどの運転状態を変える必要がなく、室内ユニットは暖房を続けることができる。利用側冷媒の量をこのように充填することで、利用側冷媒の温度を安定させ、室内の人間にとって不快感を感じさせることなく、室内の快適性を大幅に向上させることができる。
【００６８】
逆に、除霜運転中の利用側冷媒サイクルの冷媒温度低下ΔＴ［Ｋ］の許容値を所定温度以下になるように決めれば、冷媒貯留タンク２０が保有すべき冷媒量を求めることができる。利用側冷媒サイクルの全冷媒量が式（１）より、次の式（２）で求められる。
Ｗ＝（Ｑｄ＋ＱＬ ）／（ΔＴ・Ｃｐ） ・・・・・・・・・・・・（２）
冷媒貯留タンク２０の保有冷媒量Ｗｔ［ｋｇ］は、式（２）におけるＷを用いて式（３）より求められる。
Ｗｔ＝Ｗ−Ｗｐ ・・・・・・・・・・・・・・・・・・・・・・（３）
ここで、Ｗｐ［ｋｇ］は、利用側冷媒サイクルの冷媒貯留タンク２０以外の内容積から求められる必要冷媒量である。
前述の例で、例えば除霜運転中の利用側冷媒の温度低下ΔＴをまで許容するなら、冷媒貯留タンク２０には、
Ｗｔ＝（１１５２＋２７０）［ｋＪ］／（２［Ｋ］・４．１９［ｋＪ／ｋｇＫ］）−２０
＝１５０．０［ｋｇ］
の冷媒が保有できる内容積が必要となる。これに従って冷媒貯留タンク２０を構成して利用側冷媒を充填することで、利用側冷媒の温度低下を所定温度低下内に抑えることができ、室内の暖房に適した温度に維持できる。上記では所定温度低下ΔＴを２［Ｋ］としたが、１０［Ｋ］程度の温度低下でもそれほど室内の快適性を損なうことはないが、好ましくは５［Ｋ］程度以下にするのが望ましい。
ただし、室内負荷による温度低下分ＱＬ の演算は利用側の使い方で差があり、冷媒貯留タンク２０には、最低限利用側冷媒サイクルから奪われる熱量Ｑｄ［ｋＪ］分の容量が必要である。例えば所定温度低下ΔＴを２［Ｋ］とすると、
Ｗｔ＞１１５２［ｋＪ］／（２［Ｋ］・４．１９［ｋＪ／ｋｇＫ］）−２０
＞１１７．５［ｋｇ］となる。
即ち、少なくとも熱源側冷媒サイクルが除霜運転に必要な熱量を、冷媒貯留タンク２０に蓄えれば、除霜運転中に利用側冷媒の温度が大幅に下がることを防止でき、利用側冷媒サイクルで暖房運転している際の室内の快適性を維持できる。
【００６９】
また、利用側冷媒サイクルに例えば蓄熱材などの蓄熱手段を設け、熱源側冷媒サイクルで得た冷熱または温熱を蓄熱する構成の場合には、蓄熱手段に蓄熱した温熱を除霜運転中に放熱するので、利用側冷媒の温度低下を小さくできる。この時の蓄熱手段からの除霜運転中の放熱量をＱｔ［ｋＪ］とすると、利用側冷媒の温度低下ΔＴは式１ではなく、下式のように表される。
ΔＴ＝（Ｑｄ＋ＱＬ −Ｑｔ）／（Ｗ・Ｃｐ）
この温度低下ΔＴを所定温度以下、例えば５［Ｋ］以下になるように蓄熱手段の蓄熱容量および利用側冷媒サイクルの冷媒量を充填して、利用側冷媒の温度を暖房に適した温度に維持する。蓄熱手段からの除霜運転中の放熱量Ｑｔに基づいて蓄熱容量を設定するのは、蓄熱手段の材料や構成に応じて異なるので、それぞれの場合に適するように設定すればよい。例えば蓄熱手段が冷媒貯留タンク２０内に浸漬された煉瓦などの場合には熱源側冷媒サイクルが除霜運転を行なうときの冷媒貯留タンク２０内の利用側冷媒の温度低下と同等の温度低下になると考えられるので、このときの蓄熱手段からの放熱量が把握でき、それに基いて蓄熱容量を設定すればよい。
また、利用側冷媒の温度をその加熱を利用した運転で適した温度に維持する際、ここでは室内の暖房に利用したので除霜運転時の温度低下を１０［Ｋ］程度以下として得られるが、温室などの他の空間の暖房や、給湯や、加熱乾燥などに利用した場合には、除霜運転時の温度低下の所定温度を他の値に設定して適した温度に維持する必要がある。また給湯や加熱乾燥の場合にも暖房と同様に除霜運転時の温度低下を１０［Ｋ］程度以下として給湯または加熱乾燥に適した温度に維持するようにしてもよい。また好ましくは５［Ｋ］程度以下とすれば、支障なく温熱利用することができる。
【００７０】
図１の構成では、冷媒貯留タンク２０は室外ユニットｆの内部に一体で収納されており、室外ユニットｆは大きくなるが、予め室外ユニットｆと室内ユニットｇ，ｈを組み立てておき、現地で接続配管を接続するだけで据え付けることができ、搬入および工事に手間がかかるのを防ぐことができる工事性のよい構成となっている。
また、冷媒貯留タンク２０は、必ずしも室外ユニットｆの内部に一体で収納されていなくてもよい。例えば、図３に示すように、第１補助熱交換器１６と第２補助熱交換器１９、レシーバ１５、冷媒搬送装置２１、および冷媒貯留タンク２０だけをまとめて熱交換ユニットｄを構成し、標準ヒートポンプの室外機ｅと冷媒配管ｍ，ｍ’で接続してもよい。冷媒配管ｍ’は、第１補助熱交換器１６の一端側と四方弁１２との間を接続する接続配管であり、冷媒配管ｍは、第１補助熱交換器１６の他端側に接続されているレシーバ１５と冷媒流量制御弁１４との間を接続する接続配管である。このようにすれば、標準仕様のヒートポンプの室外ユニットをそのまま使用でき、さらに安価な冷凍空調装置を得ることができる。
【００７１】
また、上記では、除霜運転時の利用側冷媒の温度低下を所定温度以下にするために、冷媒貯留タンク２０の容量を大きくして冷媒量を増やしたが、これに限るものではない。例えば、接続配管ｉ，ｉ’，ｊ，ｊ’，ｋ，ｋ’の管径を太くすることで、利用側冷媒サイクルの冷媒量が冷媒貯留タンク２０を付加した場合と同量保有できればこれで代用してもよい。従来の接続配管内径をすべて√２倍の内径のものにすれば、利用側冷媒サイクルの冷媒保有量が従来比約２倍になるので、除霜運転中の利用側冷媒の温度低下は従来の約半分に抑えられ、利用側冷媒の温度が安定した状態で暖房運転を行うので、室内空調（暖房）の快適性を維持しやすくなる。また、従来の接続配管をすべてそれぞれ２本ずつにしても、利用側冷媒サイクルの冷媒保有量は約２倍となる。
【００７２】
また、さらに、冷媒貯留タンク２０を住宅の壁面に収納してもよい。この場合の構成を図４に示す。利用側熱交換器２２ａ，２２ｂで熱交換した後の利用側冷媒を冷媒貯留タンク２０に溜め、その底部から冷媒搬送装置２１で冷媒を吸い込み、第２補助熱交換器１９へ送り出す。第２補助熱交換器１９で吸放熱した利用側冷媒は接続配管ｉおよびｊ，ｋを通って利用側熱交換器２２ａ，２２ｂに流れ、加熱・冷却に利用される。冷媒貯留タンク２０は、住宅等建物の壁面ｙの内部に接続配管ｉ，ｊ，ｋなどと共に収納されている。図４の例では、利用側熱交換器２２ａ，２２ｂで熱交換した後の比較的室内空気温度レベルに近い温度の冷媒を冷媒貯留タンク２０に溜める構成になっている。このため、熱源側冷媒サイクルの除霜運転時の室内快適性の維持が多少難しくなるが、住宅の内壁材料および外壁材料の間に冷媒貯留タンク２０を壁面と一体に構成し収納しているので設置スペースの問題もなく、また、内壁面を通して冷媒貯留タンク２０内の冷媒から室内へ輻射空調も可能となり、室内空調の快適性向上が期待できる。冷媒貯留タンク２０の一面が内壁を兼ねていれば輻射効果はさらに高まり室内空調の快適性もさらに高まる。
【００７３】
また、図５に示すような構成でもよい。この場合、冷媒貯留タンク２０は室外ユニットｆ内に冷房運転と暖房運転との冷媒量差に相当する大きさだけあればよく、住宅等建物の壁面には第２冷媒貯留タンク１８を設置する。この構成では、第２冷媒貯留タンク１８は例えば鉄や銅やステンレスなどの耐圧性を有する密閉型の圧力容器で構成する。
図５に示した装置は、第２補助熱交換器１９で吸放熱して室温との差が大きくなり空調能力が高まった利用側冷媒を第２冷媒貯留タンク１８に溜める構成なので、図４に示した構成よりも除霜運転中の室内快適性の維持が効果的に可能となる。さらに、内壁面を通して冷媒貯留タンク２０内の冷媒から室内へ輻射空調の効果も期待できる。また、利用側冷媒が第２冷媒貯留タンク１８を上方から下方へ流れる構成だと、上方に空気が溜まって冷媒回路に滞留することになる。ところが図５では第２冷媒貯留タンク１８を下方から上方へ冷媒が流れる構成であり、たとえ第２冷媒貯留タンク１８上方に空気が存在しても、冷媒の流れと共に第２冷媒貯留タンク１８外に押し出されることになり、空気が内部に溜まって冷媒の流れに悪影響を及ぼすのを防止している。
なお、図４における冷媒貯留タンク２０および図５における第２冷媒貯留タンク１８は、建物壁面内に収納するのではなく、建物の床下、屋根上、屋上、地下などに収納してもよいことは言うまでもない。
【００７４】
図１，図３〜図５において、第１温度センサ３１は、第２補助熱交換器１９の利用側冷媒出口側の配管に設置されており、熱源側冷媒サイクルの能力は第１温度センサ３１の検出温度ＴＨ１が予め設定されている目標温度ＴＭに近づくように制御する。例えば、冷房運転の場合、第１温度センサ３１の検出温度ＴＨ１と目標温度ＴＭとの温度差ΔＴＨ１を式（４）で算出する。
ΔＴＨ１＝ＴＨ１−ＴＭ ・・・・・・・・・・・・・・・・・・（４）
この値ΔＴＨ１に比例した周波数分だけ、インバータで圧縮機１３の運転周波数を増減することによって熱源側冷媒サイクルの能力を制御する。
一方、暖房運転の場合には、目標温度ＴＭが検出温度ＴＨ１よりも高く設定されるため、温度差ΔＴＨ１を式（５）で算出する。
ΔＴＨ１＝ＴＭ−ＴＨ１ ・・・・・・・・・・・・・・・・・・（５）
この値ΔＴＨ１に比例した周波数分だけ、インバータで圧縮機１３の運転周波数を増減することによって熱源側冷媒サイクルの能力を制御する。
例えば、第２補助熱交換器１９の出口温度の目標値は、冷房運転の場合、ＴＭ＝７［℃］、暖房運転の場合、ＴＭ＝５０［℃］などとするとよい。
【００７５】
また、圧縮機１１の容量制御が運転／停止のみしかできない場合は、第１温度センサ３１の目標温度に上限ＴＭＨと下限ＴＭＬを設定し、第１温度センサ３１の検出温度ＴＨ１がＴＭＨとＴＭＬの間に収まるように圧縮機１１を運転／停止する。
例えば、冷房運転の場合、ＴＭＨ＝１０［℃］、ＴＭＬ＝７［℃］として、ＴＨ１≧ＴＭＨの時は圧縮機１１を運転、ＴＨ１≦ＴＭＬの時は圧縮機１１を停止、ＴＭＬ＜ＴＨ１＜ＴＭＨの時は圧縮機１１が運転していれば運転継続、停止していれば停止継続とする。
また、暖房運転の場合、ＴＭＨ＝５０［℃］、ＴＭＬ＝４７［℃］として、ＴＨ１≧ＴＭＨの時は圧縮機１１を停止、ＴＨ１≦ＴＭＬの時は圧縮機１１を運転、ＴＭＬ＜ＴＨ１＜ＴＭＨの時は圧縮機１１が運転していれば運転継続、停止していれば停止継続とする。
【００７６】
以上では、利用側熱交換器が２台の場合を示したが、利用側熱交換器が３台以上接続されていても、また１台の場合でも構わない。複数台の場合の接続形態において、すべてを互いに並列に接続すると、それぞれの利用側熱交換器を独立して制御でき、利用者の要求に適用しやすく汎用的である。また、すべてが並列である必要はなく、例えば、図６に示すように、利用側熱交換器２２ｃと２２ｄとが接続配管ｌ，ｌ’に直列に接続されていて、それぞれ別体の室内ユニットｐおよびｑに室内送風機２４ｃおよび２４ｄと共に収納されていてもよい。また、直列に接続されている室内ユニットｐ，ｑは必ずしもそれぞれに利用側冷媒流量制御弁は必要ではなく、図６に示すように、利用側冷媒の流れの上流の室内ユニットｐのみに例えば熱動弁２３ｃが接続されていればよい。逆に、利用側冷媒の流れの下流側の室内ユニットｑのみに熱動弁２３ｃが接続されていてもよい。
【００７７】
直列に接続された室内ユニットｐ，ｑについては、上流側の熱交換器２２ｃに比べて下流側の熱交換器２２ｄの方が能力が出難いので、上流側室内ユニットｐを例えば、居間、台所等の空調負荷の大きい部屋に設置し、下流側室内ユニットｑを例えば、寝室、浴室、洗面所、便所等の空調負荷の小さい部屋に設置するように使い分けてもよい。また、共に同一の部屋に設置されて同一空間を空調する場合でも、例えば、空調負荷の比較的大きい窓際に上流側室内ユニットｐを設置し、空調負荷の比較的小さい奥側に室内ユニットｑを設置すれば、比較的大きな空調空間の窓際と奥側の温度分布を改善し、空調室内の快適性を向上させることができる。また、同じ窓際に設置する場合でも、天井近くの壁面に能力の出る上流側室内ユニットｐを設置し、床上または床近くの壁面に能力の出難い下流側室内ユニットｑを設置すると、空調室内の上下温度分布を改善して快適性を向上させることができる。
【００７８】
また、上流側熱交換器２２ｃを空調用とし、これに直列に接続された下流側熱交換器２２ｄを床内部に設置してもよい。このようにすれば、特に暖房運転時、空調してやや温度が下がった冷媒でさらに床暖房ができるので、熱のカスケード利用ができ、省エネルギとなると共に、室内の上下温度むらを少なくできるので快適性が向上する。また、床内部に設置する熱交換器は空調用熱交換器と必ずしも直列に接続されていなくてもよく、例えば、熱交換器２２ａを空調用として設置された部屋にこれと並列に接続されている熱交換器２２ｂを床内部に設置してもよい。このようにすれば、床温度と空調温度とが個別に制御可能となるので効率的な運用ができる。また、利用側熱交換器を空調に利用するのに限らず、例えば給湯などの負荷に利用してもよい。このように複数の利用側熱交換器を直列に接続して、種々の利用温度で使うように構成すれば、エネルギを無駄なく利用できる。
【００７９】
本実施の形態に係わる冷凍空調装置の熱源側冷媒サイクルの容量、即ち定格能力は、室内ユニットｇ，ｈの定格能力合計と同等であるのが望ましいが、特に住宅に設置された場合、全室同時に空調されることは少ないため、室内ユニットｇ，ｈの定格能力合計の同等以下でよい。このようにすれば、過剰な設備を持たずに済むので、冷凍空調装置を低価格で供給することができる。
【００８０】
本実施の形態に係わる冷凍空調装置の熱源側冷媒サイクルにおいて、冷房を行う冷却運転時の適正冷媒量は暖房を行う加熱運転時のそれより多い。従って、レシーバ１５は加熱運転時に冷媒が溜まり込むように、第１補助熱交換器１６の加熱運転時の冷媒出口側とレシーバ１５の下部口が、冷媒流量制御弁１４にその上部口が、それぞれ接続されている。このように接続されているので、冷却運転時は、冷媒流量制御弁１４から送り出された気液二相冷媒が上部から流入し下部から第１補助熱交換器１６へ流出するので、レシーバ１５の内部に液冷媒が溜まり込むことはない。加熱運転時は、逆に、第１補助熱交換器１６から送り出された液冷媒が下部から流入して上部から冷媒流量制御弁１４へ流出するように接続されているので、レシーバ１５内に液冷媒が溜まり込む。また、レシーバ１５の内容積は、熱源側冷媒サイクルの冷房運転と暖房運転の適正冷媒量の差を暖房運転時に溜め込む液冷媒の密度で割った値にする。このように、熱源側冷媒サイクルは、冷房運転時、暖房運転時とも過不足なくそれぞれの適正冷媒量で運転されるので、効率のよい冷凍空調装置を得ることができる。
ただし、このレシーバ１５は必ずしも設ける必要がなく、レシーバ１５を設けていない場合には熱源側冷媒を冷房運転に必要な量だけ充填し、暖房運転では効率は多少低減するが、運転に支障が起こることがない。
【００８１】
本実施の形態に係わる冷凍空調装置における一体に形成された補助熱交換器１６および１９は、プレート式熱交換器や二重管式熱交換器あるいは多管式熱交換器が用いられる。プレート式熱交換器の方がその他の熱交換器に比べ価格は高いが圧損は小さいので、利用側冷媒サイクルの冷媒搬送装置２１の容量（揚程）が小さくてよい。従って、特に、本実施の形態に係わる冷凍空調装置が住宅に設置される場合で室外ユニットｆから室内ユニットｇ，ｈまでの距離が遠く配管ｉ，ｊ，ｋ、ｉ’，ｊ’，ｋ’が十分太く取れないような場合、二重管式熱交換器を用いると、冷媒搬送装置２１は安価な家庭用ポンプでは揚程不足になり、高価な産業用ポンプを用いざるを得なくなる。このような場合には、プレート式熱交換器を用いれば、冷媒搬送装置２１は安価な家庭用ポンプで十分であり、総合的に安価な冷凍空調装置が得られる。
また、補助熱交換器１６，１９において、第１補助熱交換器１６の熱源側の冷媒の流れは冷房運転と暖房運転で流れ方向が逆になるが、第２補助熱交換器１９の利用側の冷媒の流れは冷房運転と暖房運転で流れ方向が同じになる。従来装置では、冷房時と暖房時で冷媒の方向が逆になり、冷媒搬送装置２１として特殊なものが必要で高価であったが、本実施の形態のものは、通常のもので構成できるため、安価な市販のマグネットポンプ等を用いることが可能となっている。
【００８２】
また、補助熱交換器１６，１９としてプレート式熱交換器を用いる場合は、熱源側冷媒サイクルの接続は、一般には、冷房運転時の入口が下、出口が上となるように接続する。従って、暖房運転時は、入口が上、出口が下となる。一方、利用側冷媒サイクルの接続は、入口が下、出口が上となるように接続する。従って、冷房運転時は並行流、暖房運転時は対向流となる。一般に対向流で構成した方が熱交換機能を考慮すると好ましく冷房運転時は並行流となってしまうが、熱源側冷媒サイクルの冷媒が、例えばＲ２２やＲ４１０Ａなどの単一または擬似共沸冷媒であれば、第１補助熱交換器１６内の圧損により入口側から出口側に向かって蒸発温度が若干低下するので、温度的には対向流に近い形になり、熱源側冷媒サイクルを効率的に運用できる。
また、プレート式熱交換器を用いる場合でも、熱源側冷媒サイクルを冷房運転時の入口が上、出口が下となるように、即ち図６とは逆に、暖房運転時は入口が下、出口が上となるように接続してもよい。この場合は、利用側冷媒サイクルの接続は、入口が上、出口が下となるように接続する。このようにすると、冷房運転時に補助熱交換器１６内に流入した気液二相冷媒が溜まり込みにくいので、冷房運転時と暖房運転時の適正冷媒量の差が小さくなり、レシーバ１５の内容積が小さくて済むため、安価な冷凍空調装置を得ることができる。
【００８３】
また、図１、図３〜図６において、利用側冷媒流量制御弁２３を熱動弁として説明したが、これに限るものではなく、電磁弁など他の開閉弁でもよい。また、電子式リニア膨張弁（ＬＥＶ）などの流量制御弁でもよい。ただし、熱動弁のようにゆっくりと開閉できるものを用いると、水撃がなくて故障や騒音を低減できる。
また、利用側冷媒サイクルの冷媒として不凍液の特性を有するエチレングリコール，プロピレングリコール，およびＤ−ソルビトールなどのうちのいずれか１つまたは複数を重量比で０％より大きくかつ数十％以下含んだ水溶液を用いたが、外気温度が０［℃］以下にならない地域で用いる場合や、たとえ外気温度が０［℃］以下になっても、配管を断熱性のよいもので構成したり、配管の周囲に断熱材を巻くなどなんらかの手段を用いれば水でもよい。
【００８４】
実施の形態２．
本実施の形態では、熱源側冷媒サイクルを複数の系統有する構成とし、例えば２系統有するものについて示す。
以下、本発明の実施の形態２による冷凍空調装置として、例えば冷却運転で室内を冷房し、加熱運転で室内を暖房する冷暖房装置について説明し、冷却運転を冷房運転、加熱運転を暖房運転として記す。図７は本実施の形態による冷暖房装置を示す構成図である。図において、熱源側冷媒サイクルは、第１の圧縮機１１ａ、第１の流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａ、第１のレシーバ１５ａ、第１補助熱交換器１６ａを連接してなる第１の熱源側冷媒サイクルと、第２の圧縮機１１ｂ、第２の流路切換弁１２ｂ、第２の熱源側熱交換器１３ｂ、第２の冷媒流量制御弁１４ｂ、第２のレシーバ１５ｂ、第３補助熱交換器１６ｂを連接してなる第２の熱源側冷媒サイクルとから成っている。これら第１および第２の熱源側冷媒サイクルの容量である定格能力の合計は、実施の形態１の熱源側冷媒サイクルの定格能力と同一になるよう設定されている。
また、３２ａ，３２ｂは、第１，第２熱源側冷媒サイクルの熱源側熱交換器１３ａ，１３ｂの一端側に設けられ、熱源側冷媒の温度を検出する配管温度検出手段で、例えば配管温度センサである。
【００８５】
一方、利用側冷媒サイクルは、冷媒搬送装置２１、接続配管ｉ、接続配管ｊ，ｋ、利用側冷媒流量制御弁２３ａ，２３ｂ、利用側熱交換器２２ａ，２２ｂ、接続配管ｊ’，ｋ’、接続配管ｉ’、第２補助熱交換器１９ａ、第４補助熱交換器１９ｂ、冷媒貯留タンク２０を連接して成っている。接続配管ｋ、利用側冷媒流量制御弁２３ｂ、利用側熱交換器２２ｂ、および接続配管ｋ’は実施の形態１と同様、接続配管ｊ、利用側冷媒流量制御弁２３ａ、利用側熱交換器２２ａ、および接続配管ｊ’に並列に接続されている。また、第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂは並列に接続されており、これらはそれぞれ第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂと熱交換するように一体に形成されている。
【００８６】
つぎに、動作について説明する。
冷房運転時は第１、第２の熱源側冷媒サイクルとも図中実線の冷媒サイクルとなる。また、暖房運転時は第１、第２の熱源側冷媒サイクルとも図中破線の冷媒サイクルとなる。第１、第２の熱源側冷媒サイクルの動作は、冷房運転時、暖房運転時とも実施の形態１と同様であるので割愛する。
一方、利用側冷媒サイクルでは、冷房運転の場合、冷媒貯留タンク２０を通って冷媒搬送装置２１に送られた冷媒は、この冷媒搬送装置２１によって接続配管ｉおよびｊ，ｋを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を冷房すると同時に自らは加熱されて、接続配管ｊ’，ｋ’およびｉ’を通って第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに分岐して送り込まれる。第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに送り込まれた冷媒は、第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂを通して、第１および第２の熱源側冷媒サイクルによって外気へ放熱すると同時に自らは冷却され、合流した後冷媒貯留タンク２０に戻る。暖房運転の場合も利用側冷媒の流れ方向は同じであり、動作も同様であるため割愛する。
【００８７】
第１温度センサ３１は、第２補助熱交換器１９ａおよび第４補助熱交換器１９ｄの利用側冷媒出口側接合点と冷媒貯留タンク２０との間を接続する配管に設置されており、熱源側冷媒サイクルの能力は第１温度センサ３１の検出温度ＴＨ１が予め設定されている目標温度ＴＭに近づくように制御される。例えば、冷房運転の場合、第１温度センサ３１の検出温度ＴＨ１と目標温度ＴＭとの温度差ΔＴＨ１を式（６）で演算する。
ΔＴＨ１＝ＴＨ１−ＴＭ ・・・・・・・・・・・・・・・・・・（６）
この演算した値に比例した周波数分だけインバータで第１、第２の圧縮機１１ａ、１１ｂの運転周波数を増減することによって、第１、第２の熱源側冷媒サイクルの能力を制御する。
一方、暖房運転の場合、第１温度センサ３１の検出温度ＴＨ１と目標温度ＴＭと温度差ΔＴＨ１を式（７）で演算する。
ΔＴＨ１＝ＴＭ−ＴＨ１ ・・・・・・・・・・・・・・・・・・（７）
この演算した値に比例した周波数分だけインバータで第１、第２の圧縮機１１ａ、１１ｂの運転周波数を増減することによって、第１、第２の熱源側冷媒サイクルの能力を制御する。
例えば、第１温度センサ３１の検出温度の目標値は、冷房運転の場合、ＴＭ＝７［℃］、暖房運転の場合、ＴＭ＝５０［℃］などとする。
【００８８】
圧縮機１１ａおよび１１ｂの運転周波数は、それぞれΔＴＨ１に比例した周波数分だけ増減させてもよいが、圧縮機の性能（入力−能力特性）から、２台の合計ＣＯＰ＝能力［ｋＷ］／入力［ｋＷ］が最大になる周波数の組み合わせを選択するとさらに効率がよい。例えば、図８に示すように、２台の圧縮機の合計の運転周波数を仮周波数としたものとその時の合計能力を横軸に取り、縦軸にＣＯＰを取ると、位置Ｚより左側の周波数（能力）が小さい領域は圧縮機１台運転の方が２台運転よりもＣＯＰがよい領域、位置Ｚより右側の周波数（能力）が大きい領域は圧縮機２台同一周波数運転の方が１台運転よりもＣＯＰがよい領域である。実際には、位置Ｚの前後数Ｈｚの間を切換え領域Ｂとし、これより周波数（能力）が小さい領域Ａで圧縮機１台運転、これより周波数（能力）が大きい領域Ｃで圧縮機２台の同一周波数運転とし、領域Ｂでは圧縮機運転の切換えはせず、それ以前の運転台数を継続する。
【００８９】
また、第１、第２の圧縮機１１ａ、１１ｂの運転周波数を、それぞれΔＴＨ１に比例した周波数分だけ増減する場合、圧縮機２台の合計運転周波数（仮周波数）Ｆ［Ｈｚ］あるいはその増減値ΔＦ［Ｈｚ］は、ΔＴＨ１の関数として演算するようにしてもよいし、ΔＴＨ１に対する数表として予め設定し、運転中に数表を参照するようにしてもよい。
【００９０】
第１および第２の熱源側冷媒サイクルの圧縮機の容量制御が運転／停止のみしか選択できない場合は、第１温度センサ３１の目標温度に上限ＴＭＨ、下限ＴＭＬを設定し、第１温度センサ３１の検出温度ＴＨ１がＴＭＨとＴＭＬの間に収まるように第１および第２の熱源側冷媒サイクル内の圧縮機１１ａおよび１１ｂを運転／停止する。この様子を冷房運転の場合を例に図９について説明する。
図９において、横軸は第１温度センサ３１の検出温度ＴＨ１、縦軸は熱源側冷媒サイクル中の圧縮機運転台数の増減台数を表す。ＴＭＨ＝８．５［℃］、ＴＭＬ＝７［℃］として、ＴＨ１≧ＴＭＨの時は圧縮機を１台追加運転、ＴＨ１≦ＴＭＬの時は圧縮機を１台停止、ＴＭＬ＜ＴＨ１＜ＴＭＨの時は圧縮機の運転台数は変更しない。また、暖房運転の場合も同様であり、ＴＭＨ＝５０［℃］、ＴＭＬ＝４８．５［℃］として、ＴＨ１≧ＴＭＨの時は圧縮機を１台停止、ＴＨ１≦ＴＭＬの時は圧縮機を１台追加運転、ＴＭＬ＜ＴＨ１＜ＴＭＨの時は圧縮機の運転台数は変更しない。このように、熱源側冷媒サイクルを２系統以上の複数の系統有する構成とし、それぞれの圧縮機を１台ずつ運転／停止することにより、熱源側冷媒サイクルが１系統の場合に比べて、利用側冷媒の温度変化を小さい範囲内に収めることができ、冷媒温度の安定性、ひいては、空調室内の快適性が向上する。
【００９１】
以下、複数系統の熱源側冷媒サイクルを有する冷凍空調装置において、暖房運転中に時に第１の熱源側冷媒サイクルの第１の熱源側熱交換器１３ａまたは第２の熱源側冷媒サイクルの第２の熱源側熱交換器１３ｂに霜が付着し、除霜運転を行う時の制御について説明する。
暖房運転中に第１の熱源側冷媒サイクルが除霜運転開始条件を満たした後、除霜運転に入っているときに、第２の熱源側冷媒サイクルが除霜運転開始条件を満たした場合、第１の熱源側冷媒サイクルが除霜運転終了条件を満たすまで、第２の熱源側冷媒サイクルの除霜運転を遅らせる。この時の制御装置４１の制御動作を図１０のフローチャートに示す。
【００９２】
まず、ＳＴ１では第１、第２の熱源側冷媒サイクルにおいて、配管温度センサ３２ａ、３２ｂで第１、第２配管温度を検出する。ＳＴ２で、第２の熱源側冷媒サイクルが除霜運転中かどうか判断し、除霜運転中の場合には除霜運転終了条件を満たしているかどうか判断する。即ち、ＳＴ３で第２配管温度が１０［℃］よりも低い場合には第２の熱源側冷媒サイクルでまだ除霜運転を継続する必要があるので制御処理は終了（ＥＮＤ）とする。ＳＴ３で第２配管温度が１０［℃］以上の場合には第２の熱源側冷媒サイクルで除霜運転終了条件を満たしていると判断し、ＳＴ４で第２の熱源側冷媒サイクルを除霜運転終了にする。この状態で第１、第２の熱源側冷媒サイクルはどちらも除霜運転に入っていない。そして、ＳＴ５で第１配管温度のチェックを行う。第１配管温度が例えば−７［℃］よりも低くなったら除霜運転開始条件を満たしていると判断し、第１の熱源側冷媒サイクルを除霜運転状態とし（ＳＴ６）、制御処理を終了する（ＥＮＤ）。第１配管温度が−７［℃］以上だったら、ＳＴ７で第１の熱源側冷媒サイクルは除霜運転中かどうか判断し、除霜運転中の場合には除霜運転終了条件を満たしているかどうか判断する。即ち、ＳＴ８で第２配管温度が１０［℃］よりも低い場合には第１の熱源側冷媒サイクルでまだ除霜運転を継続する必要があるので制御処理は終了（ＥＮＤ）とする。ＳＴ８で第１配管温度が１０［℃］以上の場合には第１の熱源側冷媒サイクルで除霜運転終了条件を満たしていると判断し、ＳＴ９で第１の熱源側冷媒サイクルを除霜運転終了にする。この状態で第１、第２の熱源側冷媒サイクルはどちらも除霜運転に入っていない。そして、ＳＴ１０で第２配管温度のチェックを行う。第２配管温度が−７［℃］よりも低くなったら除霜運転開始条件を満たしていると判断し、ＳＴ１１で第２の熱源側冷媒サイクルを除霜運転状態として、制御処理を終了する（ＥＮＤ）。この制御処理は所定時間間隔、例えば１分に１回の温度検出に応じて実行されるように構成しておくとよい。
【００９３】
上記のように制御すると、例えば、暖房運転中、第１の熱源側冷媒サイクルにおいて、配管温度センサ３２ａの検出温度が−７［℃］を検出したことによって第１の熱源側冷媒サイクルが除霜運転に入った後、第２の熱源側冷媒サイクルにおいても、配管温度センサ３２ｂの検出値が−７［℃］を検出した場合、制御装置４１では、第１の熱源側冷媒サイクルで、配管温度センサ３２ａの検出温度が１０［℃］以上となって除霜運転終了条件を満たすまで、第２の熱源側冷媒サイクルは除霜運転を行わず、暖房運転を継続する。第１の熱源側冷媒サイクルが除霜を終了したら、第１の熱源側冷媒サイクルは暖房運転に復帰し、第２の熱源側冷媒サイクルの除霜運転を開始する。
【００９４】
このように１系統ずつ熱源側冷媒サイクルの除霜運転を行うことによって、利用側冷媒サイクルの冷媒温度の低下が小さくなるので、温熱利用に適した温度に維持して空調室内の快適性が向上する。また、熱源側冷媒サイクルが１系統の場合に比較して、利用側冷媒サイクルの冷媒温度の低下が小さいので、冷媒貯留タンク２０を小さくすることができ、システム全体の価格を安価にすることができる。
熱源側冷媒サイクルが３以上の複数系統ある場合には、そのうちの１系統以上が除霜運転を行ってもよく、少なくとも１系統の熱源側冷媒サイクルは除霜運転ではなく暖房運転を継続して行うように制御すれば、上記と同様の効果を奏する。
また、熱源側冷媒サイクルを複数の系統にすれば、小型で安価な標準ヒートポンプをそのまま、あるいはその構成部品を流用することができるので、さらに安価な冷凍空調装置が得られる。
【００９５】
また、第１の熱源側冷媒サイクルが除霜運転していて第２の熱源側冷媒サイクルが暖房運転している場合、制御装置４１は第１温度センサ３１の検出値を目標値に近づけるため第２の熱源側冷媒サイクルの暖房能力が増大するように自動的に制御してもよい。第２の熱源側冷媒サイクルの暖房能力を増大することで、利用側冷媒サイクルの冷媒温度の低下はより小さくなる。
さらに、熱源側冷媒サイクルが３系統以上あれば、これら全ての除霜運転タイミングをずらすことによって、利用側冷媒サイクルの冷媒温度を安定させ、空調室内の快適性を維持することができる。
【００９６】
また、第１の熱源側冷媒サイクルまたは第２の熱源側冷媒サイクルのどちらかが除霜運転開始条件を満たした場合、除霜運転開始前に第１の熱源側冷媒サイクルまたは第２の熱源側冷媒サイクルのいずれか一方、または両方を最大能力で運転して、利用側冷媒サイクルの冷媒温度を予め上昇させておいてもよい。具体的手段としては、第１の熱源側冷媒サイクルまたは第２の熱源側冷媒サイクルのどちらかが除霜運転開始条件を満たした場合、第２、第４補助熱交換器１９ａ、１９ｂの合流出口に設置されている第１温度センサ３１の目標温度を、ＴＭＵ［℃］だけ上昇させることが考えられる。温度増加分ＴＭＵは、どんな値でもよいが例えば数［℃］程度とする。このとき第１温度センサ３１の目標温度はＴＭ＋ＴＭＵ［℃］となり、第１温度センサ３１の検出値ＴＨ１がこの温度に到達するまで第１の熱源側冷媒サイクルは除霜運転せずに暖房運転を継続して行い、目標温度（ＴＭ＋ＴＭＵ［℃］）に到達した後除霜運転に入るように制御装置４１で制御する。また、目標温度を上げる代わりに、例えば数分程度の一定時間、最大能力で暖房運転を行った後に除霜運転に入るようにしてもよい。
【００９７】
このように、利用側冷媒サイクルの冷媒温度を上げておいてから除霜運転に入ると、除霜運転によって利用側冷媒サイクルから熱量を奪われても、空調室内の快適性を維持することができる。目標温度の上昇分ＴＭＵは、除霜運転で下がると予想される温度の例えば１／２程度で、室内の人間が不快に感じるのをある程度防ぐことができる。ただし、この目標温度の上昇分は、利用する環境や状態によって異なるため、一概には言えず、利用側で適当な値に設定するとよい。
また、直接的に第１、第２の冷媒サイクル中の第１、第２の圧縮機１１ａ、１１ｂの運転周波数を増加させ、例えば、第１、第２の圧縮機１１ａ，１１ｂの合計周波数が８０［Ｈｚ］程度のときに例えば１２０［Ｈｚ］程度に増加し、一定時間、例えば数分程度経過した後、第１の熱源側冷媒サイクルを除霜運転するように制御装置４１で制御してもよい。
【００９８】
なお、上記で述べた複数の熱源側冷媒サイクルを有する冷凍空調装置における除霜運転の制御は、除霜運転時の利用側冷媒の温度低下を低減するために冷媒貯留タンク２０を設けていない冷凍空調装置にも適用することができる。ただし、冷媒貯留タンク２０を設ければ、さらに利用側冷媒の温度を安定させることができるのは言うまでもない。
【００９９】
次に、第１および第２の熱源側冷媒サイクルの容量制御段階を数段階に設定する制御方法について説明する。
第１および第２の熱源側冷媒サイクルのそれぞれの容量制御段階を数段階に設定する場合には、第１温度センサ３１の目標温度をＴＭと設定し、あるサンプリング間隔τ［ｈ］ごとに検出した第１温度センサ３１の検出温度ＴＨ１がＴＭの近傍に収まるように第１および第２の熱源側冷媒サイクルの容量を１段階ずつ増減する。図１１にブロック線図を示す。
ΔＴＨ１＝ＴＭ−ＴＨ１＊ ・・・・・・・・・・・・・・・・・（８）
とする。上付き＊はτ［ｈ］または２τ［ｈ］後のＴＨ１の予測値を表す。例えば冷房運転において、ΔＴＨ１＞＋αの場合、熱源側冷媒サイクルの合計容量段階Ｄを１段階減段し、ΔＴＨ１＜−αの場合、熱源側冷媒サイクルの合計容量段階Ｄを１段階増段する。容量制御段階は、図１１に示すように隣り合う容量制御段階の熱源側冷媒サイクルの合計容量（能力）への変化率がほぼ一定になるように設定しておくのがよい。
【０１００】
例えば、
｛（段階３の冷房能力） − （段階２の冷房能力）｝／（段階２の冷房能力）≒｛（段階４の冷房能力） − （段階３の冷房能力）｝ ／（段階３の冷房能力）
のように設定する。言い換えれば、容量変化幅は、容量が増加するにつれて大きくなるように設定しており、比較的大きな負荷の大きな変動にも、比較的小さな負荷の小さな変動にもハンチングを抑えながら追従することができ、利用側冷媒の温度安定性が向上し、ひいては空調室内の快適性が向上する。
【０１０１】
ここで、容量制御段階の設定方法について説明する。上述のように、どの容量制御段階から隣の容量制御段階に移行してもその容量変化率が一定になるように容量制御段階を設定する。今、容量制御段階の数をＮ段階、最大容量をＱｍａｘ［ｋＷ］、最小容量をＱｍｉｎ［ｋＷ］（停止状態を除く）とすると、各段階の変化率が一定になるための容量変化率ｒは、式（９）により求められる。
ｒＮ−１ ＝Ｑｍａｘ／Ｑｍｉｎ ・・・・・・・・・・・・・・・・（９）
即ち、最大容量と最小容量の比のＮ−１乗根が容量変化率ｒとなる。従って、容量制御段階１はＱｍｉｎ、２はＱｍｉｎ×ｒ、３はＱｍｉｎ×ｒ２ 、・・・、容量制御段階ＮはＱｍｉｎ×ｒＮ ＝Ｑｍａｘとなる。
例えば、図１１を例に挙げると、Ｑｍａｘ＝８［ｋＷ］、Ｑｍｉｎ＝１［ｋＷ］で容量制御段階はＮ＝７であるので、容量制御変化率ｒ＝（８／１）１／６ ＝１．４１４となる。従って、もし、どのような容量制御段階でも設定可能であれば、容量制御段階１は１［ｋＷ］、２は１．４１４［ｋＷ］、３は２．０［ｋＷ］、４は２．８２８［ｋＷ］、５は４．０［ｋＷ］、６は５．６５６［ｋＷ］、７は８．０［ｋＷ］となる。
【０１０２】
実際には、熱源側冷媒サイクルが２系統あり、どちらも同等の容量制御段階３段階で実現するのは困難であるため、１台あたりの容量変化率が一定になるように、Ｑｍａｘ＝４［ｋＷ］、Ｑｍｉｎ＝１［ｋＷ］、Ｎ＝３として、ｒ＝（４／１）１／２ ＝２とする。即ち、１台あたり、容量段階１は１［ｋＷ］、２は２［ｋＷ］、３は４［ｋＷ］として、２台を組合せ、それぞれの熱源側冷媒サイクルの運転が連続するように設定する。ここで、熱源側冷媒サイクルの運転が連続するようにとは、例えば、図１１で、２台の合計容量制御段階４は冷房能力４［ｋＷ］であるが、これを実現する組み合わせは、１台で容量制御段階３で運転する場合と、容量制御段階２で２台運転する場合とが考えられる。ところが、前者であると、合計容量制御段階３および５が熱源側冷媒サイクル２台運転であるため、合計容量制御段階３から４に、またさらに４から５に移行した時に短時間に熱源側冷媒サイクルの１台が運転から停止、そして再び運転ということになってシステム全体の安定性が損なわれ、また、熱源側冷媒サイクルの再起動停止時間（例えば３分）が設定されているため再起動に時間がかかり、ひいては空調室内の快適性が損なわれることが懸念されるため、後者を採用する方がよい。
このように合計容量の段階を変化させる際に、その変化が合計容量の段階を増加させる場合、複数系統の熱源側冷媒サイクルのうちの現行で運転している熱源側冷媒サイクルは運転状態のままで前記合計容量を増加させるように制御する。一方、変化が合計容量の段階を減少させる場合、複数系統の熱源側冷媒サイクルのうちの現行で停止している熱源側冷媒サイクルは停止状態のままで合計容量を減少させるように制御する。これにより合計容量の段階を変化させる際に、複数系統の熱源側冷媒サイクルのうちで運転／停止の状態変化する熱源側冷媒サイクルの数を最小にでき、システム全体の安定性を向上することができ、空調室内の快適性を維持した状態で負荷の変化に対応できる。
【０１０３】
このように、複数の熱源側冷媒サイクルを備えた冷凍空調装置においての容量制御方法は、熱源側冷媒サイクルの合計容量の変化幅が、合計容量が増加するにつれて大きくなるように設定しているので、比較的大きな負荷の大きな変動にも、比較的小さな負荷の小さな変動にもハンチングを抑えながら追従することができ、利用側冷媒の温度安定性が向上し、空調室内の快適性が向上する。
もちろん、熱源側冷媒サイクルが１台の装置の場合にも、次の段階への容量（能力）の変化率がほぼ一定になるように設定する、即ち容量変化幅を容量が増加するにつれて大きくなるように設定すると、どのような負荷の変動にもハンチングを抑えながら追従することができ、利用側冷媒の温度が安定した状態で冷房または暖房運転を行なうことができる。
【０１０４】
なお、本実施の形態では、熱源側冷媒サイクルが２台の例を示したが、熱源側冷媒サイクルは３台以上あっても構わない。複数の熱源側冷媒サイクルで構成すると、その１つの熱源側冷媒サイクルは小容量のものでよく、これに標準の蒸気圧縮式の冷凍サイクルを用いると、低価格で冷凍空調装置を構成できる。また、複数の熱源側冷媒サイクルのすべてを本実施の形態のように並列に接続すると、それぞれを独立して制御できるので望ましいが、その一部または全てが直列に接続されていてもよい。直列に接続されている場合は、上流側の冷媒サイクルで加熱または冷却された利用側冷媒を下流側の冷媒サイクルで更に加熱または冷却することになり、下流側冷媒サイクルの効率が多少悪化するが、利用側冷媒の接続に分岐がなく単純になり安価な冷凍空調装置が得られる。
【０１０５】
なお、上記で述べた複数または１台の熱源側冷媒サイクルを有する冷凍空調装置における容量制御は、除霜運転時の利用側冷媒の温度低下を低減するために冷媒貯留タンク２０を設けていない冷凍空調装置にも適用することができる。ただし、冷媒貯留タンク２０を設ければ、さらに利用側冷媒の温度を安定させることができるのは言うまでもない。
【０１０６】
実施の形態３．
以下、本発明の実施の形態３による冷凍空調装置として、例えば冷却運転で室内を冷房し、加熱運転で室内を暖房する冷暖房装置について説明し、冷却運転を冷房運転、加熱運転を暖房運転として記す。図１２は本実施の形態による冷暖房装置を示す構成図である。図において、熱源側冷媒サイクルは、第１の圧縮機１１ａ、第１の流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａ、第１のレシーバ１５ａ、第１補助熱交換器１６ａを連接してなる第１の熱源側冷媒サイクルと、第２の圧縮機１１ｂ、第２の流路切換弁１２ｂ、第２の熱源側熱交換器１３ｂ、第２の冷媒流量制御弁１４ｂ、第２のレシーバ１５ｂ、第３補助熱交換器１６ｂを連接してなる第２の熱源側冷媒サイクルとから成っている。これら第１および第２の熱源側冷媒サイクルの容量（定格能力）の合計は、１系統で構成した熱源側冷媒サイクルである実施の形態１の熱源側冷媒サイクルの容量（定格能力）と同一である。
【０１０７】
一方、利用側冷媒サイクルは、第１の冷媒搬送装置２１、接続配管ｉ、接続配管ｊ，ｋ、利用側冷媒流量制御弁２３ａ，２３ｂ、利用側熱交換器２２ａ，２２ｂ、接続配管ｊ’，ｋ’、接続配管ｉ’、冷媒貯留タンク２０を連接して成る第１の利用側冷媒サイクルと、第２の冷媒搬送装置２５、第２補助熱交換器１９ａ、第４補助熱交換器１９ｂ、冷媒貯留タンク２０を連接して成る第２の利用側冷媒サイクルとから構成されている。接続配管ｋ、利用側冷媒流量制御弁２３ｂ、利用側熱交換器２２ｂ、および接続配管ｋ’は実施の形態１と同様、接続配管ｊ、利用側冷媒流量制御弁２３ａ、利用側熱交換器２２ａ、および接続配管ｊ’に並列に接続されている。また、第２補助熱交換器１９ａと第４補助熱交換器１９ｂとは実施の形態２と同様、並列に接続されており、これらはそれぞれ第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂと熱交換するよう一体に形成されている。
第２の利用側冷媒サイクルでは、利用側冷媒を循環させて第２，第４補助熱交換器１９ａ，１９ｂでそれぞれ、第１，第３補助熱交換器１６ａ，１６ｂと熱交換し、冷媒貯留タンク２０に熱を蓄える熱輸送サイクルを構成している。
【０１０８】
さらに、圧縮機１１ａ、流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａは第１の室外ユニットｅに収納されており、圧縮機１１ｂ、流路切換弁１２ｂ、第１の熱源側熱交換器１３ｂ、第１の冷媒流量制御弁１４ｂは第２の室外ユニットｅ’に収納されている。これらは、家庭用エアコンなどの標準室外機を利用している。さらにまた、第１の冷媒搬送装置２１、第２の冷媒搬送装置２５、一体となった第１補助熱交換器１６ａおよび第２補助熱交換器１９ａ、一体となった第３補助熱交換器１６ｂおよび第４補助熱交換器１９ｂ、冷媒貯留タンク２０、第１、第２のレシーバ１５ａ、１５ｂは熱交換ユニットｄに収納されている。
【０１０９】
第１の熱源側冷媒サイクルは、第１の室外ユニットｅ内の流路切換弁１２ａの第４口と熱交換ユニットｄ内の第１補助熱交換器１６ａの一端側との間、および第１の室外ユニットｅ内の冷媒流量制御弁１４ａと熱交換ユニットｄ内の第１補助熱交換器１６ａの他端側に接続されている第１のレシーバ１５ａとの間を、それぞれ接続配管ｍ’およびｍで接続して構成されている。同様に第２の熱源側冷媒サイクルは、第２の室外ユニットｅ’内の流路切換弁１２ｂの第４口と熱交換ユニットｄ内の第３補助熱交換器１６ｂの一端側との間、および第２の室外ユニットｅ’内の冷媒流量制御弁１４ｂと熱交換ユニットｄ内の第３補助熱交換器１６ｂの他端側に接続されている第２のレシーバ１５ｂとの間を、それぞれ接続配管ｎ’およびｎで接続して構成されている。
【０１１０】
冷媒貯留タンク２０は、その内部で最上部から縦方向に仕切り２７で左右２槽に分割されている。仕切り２７は、冷媒貯留タンク２０の底面の直上またはそれより上部でその一部が開口していて左右２槽の利用側冷媒３０が連通するようになっている。さらに、冷媒貯留タンク２０の上部は大気に開放されており、利用側冷媒３０の体積膨張を吸収する。またさらに、接続配管ｓは、冷媒貯留タンク２０の左槽の底部の流出口にその一端が開口しており、その他端は冷媒搬送装置２１の吸入口に接続されている。また、接続配管ｔは、冷媒貯留タンク２０の右槽の底部の流出口にその一端が開口しており、その他端は冷媒搬送装置２５の吸入口に接続されている。また、接続配管ｒは、冷媒貯留タンク２０の左槽の側面上部の流入口にその一端が開口しており、その他端は第２，第４補助熱交換器１９ａ，１９ｂの出口側に接続されている。また、接続配管ｉ’は、冷媒貯留タンク２０の右槽の側面上部の流入口を通って、冷媒貯留タンク内に設定されているフィルタ２６の内部にその一端が開口しており、その他端は接続配管ｊ’，ｋ’の出口側に接続されている。すべての接続配管ｒ，ｓ，ｔ，およびｉ’は、冷媒貯留タンク２０内の利用側冷媒３０の喫水面下に開口している。
【０１１１】
つぎに、動作について説明する。
冷房運転時は第１、第２の熱源側冷媒サイクルとも図中実線の冷媒サイクルとなる。また、暖房運転時は第１、第２の熱源側冷媒サイクルとも図中破線の冷媒サイクルとなる。熱源側冷媒サイクルの動作は、冷房運転時、暖房運転時とも実施の形態１と同様であるので割愛する。
【０１１２】
第２の利用側冷媒サイクルにおいて、冷媒貯留タンク２０の右側の槽の底部から流出した利用側冷媒３０は、接続配管ｔを通り第２の冷媒搬送装置２５によって第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに分岐して送り込まれる。第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに送り込まれた利用側冷媒３０は、第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂを通して、第１および第２の熱源側冷媒サイクルによって外気へ放熱すると同時に自らは冷却され、接続配管ｒで合流した後冷媒貯留タンク２０の左側の槽に戻る。暖房運転の場合も動作は同様であるため割愛する。
この第２の利用側冷媒サイクルによって、第１および第２の熱源側冷媒サイクルで発生する温熱または冷熱が、冷媒貯留タンク２０に輸送されてここで蓄熱される。
【０１１３】
一方、第１の利用側冷媒サイクルでは、冷媒貯留タンク２０の左側の槽の底部から流出した利用側冷媒３０は、接続配管ｓを通り第１の冷媒搬送装置２１によって接続配管ｉおよびｊ，ｋを通って利用側熱交換器２２ａ，２２ｂへ送られる。利用側熱交換器２２ａ，２２ｂで室内送風機２４ａ，２４ｂによって送り込まれた室内空気と熱交換して、冷房運転の場合には室内を冷房すると同時に自らは加熱され、暖房運転の場合には室内を暖房すると同時に自らは冷却される。この後、接続配管ｊ’，ｋ’およびｉ’を通って冷媒貯留タンク２０の右側の槽に戻ってくる。
このように、第１の利用側冷媒サイクルでは、利用側冷媒３０を循環することにより、冷媒貯留タンク２０に蓄えられている温熱または冷熱を熱交換器２２ａ，２２ｂで負荷に利用している。
このとき、室内送風機２４ａ，２４ｂの風量は、居住者が設定する室内空気温度の目標設定値と、温度センサ３５ａ，３５ｂで検出されるそれぞれの室内空気の実際の温度との温度差に応じて数段階または連続的に変化するように設定する。
【０１１４】
本実施の形態では、利用側冷媒サイクルとして、室内ユニットｇ，ｈを循環する第１の利用側冷媒ユニットと熱輸送を行う第２の利用側冷媒サイクルで構成されている。第１の利用側冷媒サイクルを流れる冷媒の循環量は、室内ユニットｇ，ｈの運転／停止に応じて利用側冷媒流量制御弁２３ａ，２３ｂが開閉することにより変化する。ところが第２の利用側冷媒サイクルを流れる冷媒の循環は、第１の利用側冷媒サイクルを流れる冷媒の循環とは独立しており、第１の利用側冷媒サイクルの冷媒循環量が変化しても、第２の冷媒搬送装置２５によってほぼ一定に保たれる。従って、熱源側冷媒サイクルの運転状態が安定しやすい上に、第２、第４補助熱交換器１９ａ，１９ｂの出口温度、ひいては、利用側熱交換器２２ａ，２２ｂに流入する冷媒の温度も安定しやすいため、室内空調空間の温度制御が安定しやすく快適性を維持しやすい。
【０１１５】
また、利用側熱交換器へ冷媒を搬送する冷媒搬送装置２１と、第２，第４補助熱交換器１９ａ，１９ｂへ冷媒を搬送する冷媒搬送装置２５とを有し、それぞれの流量が個別に制御できる構成となっている。このため、例えば、暖房運転中に熱源側冷媒サイクルが除霜運転を開始し、利用側冷媒の温度が下がってきたら冷媒搬送装置２１を止めて低温の冷媒が利用側熱交換器に流入しないようにすることができる。そして第１の利用側冷媒サイクルの運転はそのまま維持でき、室内快適性を維持しやすい。特に、熱源側冷媒サイクルは通常、一度停止した後一定時間を経過しないと再び起動しないような制御がされているので、そのような場合には、冷媒搬送装置２５を停止したまま冷媒搬送装置２１を運転することにより、冷媒貯留タンク２０の蓄熱分で室内を所定時間の間、空調することができる。
【０１１６】
ここで、フィルタ２６は、例えば円筒状に成形されており、その底面も網目状に構成されている。円筒側面と底面の網目の粗さは均一が望ましいが、ある程度以上細かければ、底面の方が側面より粗くても、また、逆に側面の方が底面より粗くてもよい。フィルタ２６は利用側冷媒３０の注ぎ口も兼ねており、その上面は蓋になっていて、本実施の形態による冷凍空調装置が設置されてから運用されるまでの間に利用側冷媒３０を充填する時に蓋を開け、円筒状のフィルタ上面からその内部へ利用側冷媒３０を注ぎ込む。このとき、フィルタ２６は、冷媒３０が注ぎ込まれるのと同時に冷媒貯留タンク２０内に混入する混入物であるごみ、ちり等が利用側冷媒サイクル内に混入するのを防ぐ。さらに接続配管ｉ’がフィルタ２６の内部に接続されており、利用側冷媒の循環と共に、利用側冷媒サイクル内の配管、熱交換器等の腐食、摩耗等によるごみ、ちり等の混入物を集めることにより、利用側冷媒サイクルから取り除くことを可能としている。利用側冷媒サイクル内に異物が混入して利用側冷媒サイクル内を循環すると、冷媒搬送装置２５，２１の故障や、第２，第４補助熱交換器１９ａ，１９ｂおよび利用側熱交換器２２ａ，２２ｂの詰まりや、伝熱性能の低下などを招いて、システム全体の信頼性が低下することになる。フィルタ２６を設けることにより、これらの不都合が発生するのを防ぎ、信頼性を向上できる効果がある。
【０１１７】
なお、フィルタ２６の設置場所は、冷媒貯留タンク２０に限らず、利用側冷媒サイクルの配管のどこかに１つ設けてあれば、そのフィルタ２６を循環する際に混入物が集められ、それよりも下流側にごみ等が循環していくことを防ぐ。特に第２，第４の補助熱交換器１９ａ，１９ｂの入口の上流側配管に設けておくと、混入物が第２，第４の補助熱交換器１９ａ，１９ｂに流れ込むのを防ぐことができる。
また、冷媒貯留タンク２０内にフィルタ２６を設けると、前記のように冷媒貯留タンク２０は冷媒を注ぎ込むために開口を設けているので、フィルタ２６を交換したり、集まった混入物を取り除くことが容易となり、管理しやすい。
また、冷媒貯留タンク２０内において、少なくともどちらか一方の流入口から流出口へ至る利用側冷媒の流れの途中に設けられていればよく、例えば流出口近傍に設けられていてもよい。ただし、図１２のように冷媒貯留タンク２０の上方に設けるとフィルタ２６に引っかかったちりやごみなどを容易に取り除くことができ、またフィルタ２６を交換したり洗浄する際にも扱いやすい。
【０１１８】
冷媒貯留タンク２０は、その一部が連通した仕切り２７によって左右２槽に分割されている。その分割された一方の槽例えば右槽には利用側熱交換器２２ａ，２２ｂからの利用側冷媒が流入する開口が設けられ、他方の槽例えば左槽には利用側熱交換器２２ａ，２２ｂへの利用側冷媒が流出する開口が設けられている。さらに、利用側熱交換器２２ａ，２２ｂからの利用側冷媒が流入する開口が設けられた右槽には、第２，第４補助熱交換器１９ａ，１９ｂへの利用側冷媒が流出する開口が設けられ、利用側熱交換器２２ａ，２２ｂへの利用側冷媒が流出する開口が設けられている左槽には第２，第４補助熱交換器１９ａ，１９ｂからの利用側冷媒が流入する開口が設けられている。本実施の形態では冷媒貯留タンク２０の上方に２つの流入口となる開口、底部に２つの流出口となる開口が配設されている。
更に詳しくは、接続配管ｒが冷媒貯留タンク２０の左槽の上部喫水面下に、接続配管ｓが冷媒貯留タンク２０の左槽の底面に、接続配管ｔが冷媒貯留タンク２０の右槽底面に、接続配管ｉ’が冷媒貯留タンク２０の右槽の上部喫水面下で、かつ、フィルタ２６の内部に、それぞれ開口している。
【０１１９】
この構成において、例えば暖房運転時に、第２の利用側冷媒サイクルでは、第２，第４補助熱交換器１９ａ，１９ｂから流出した５０［℃］程度の高温の利用側冷媒が左槽の上部から流入し、冷媒貯留タンク２０内の利用側冷媒３０が右槽底面から流出する。このため、高温で比重の小さい冷媒が左槽の上部から溜まりはじめ、時間と共に下部まで高温の冷媒が左槽に溜まる。このように、左槽は内部の冷媒が混合されることなく上下に温度成層を形成し、高温の領域を時間と共に広げながら蓄熱することができる。このとき、第２，第４補助熱交換器１９ａ，１９ｂへ冷媒を送り出す第２の冷媒搬送装置２５の吸い込み口が接続されている接続配管ｔの入口温度はほとんど上昇せず、第２の利用側冷媒サイクルで冷媒貯留タンク２０内の低温の冷媒を取り出して熱交換するので、熱源側冷媒サイクルを効率よく運転できると共に、冷媒貯留タンク２０の左槽で十分に蓄熱することができる。また、第１の利用側冷媒サイクルでは、高温の冷媒を左槽底部から循環させて利用側熱交換器２２ａ，２２ｂで利用しており、特に、冬期の暖房立ち上げが瞬時に行えるという効果がある。
また、冷房時においても、冷媒貯留タンク２０内左槽の冷媒を右槽の冷媒よりも比較的低温に保つことができるので、夏期の冷房立ち上げを迅速に行えるという効果がある。
【０１２０】
さらに、冷媒貯留タンク２０と第１，第２の利用側冷媒サイクルとの接続は、暖房運転時には図１２のように構成しておき、冷房運転時に上下が逆になるように切換えてもよい。即ち、第２の利用側冷媒サイクルの接続配管ｒを冷媒貯留タンク２０の左側の槽の底部に接続し、第２，第４補助熱交換器１９ａ，１９ｂで熱交換した後の低温の利用側冷媒３０を下方から流入させる。そして、冷媒貯留タンク２０の左側の槽の上方から接続配管ｓを通って第１の利用側冷媒サイクルへ流出させる。また、第１の利用側冷媒サイクルの接続配管ｉ’を冷媒貯留タンク２０の右側の槽の底部に接続し、利用側熱交換器２２ａ，２２ｂから流出した利用側冷媒３０を冷媒貯留タンク２０の右側の槽の底部に流入させる。また、冷媒貯留タンク２０の右側の槽の上方から接続配管ｔを通って第２の利用側冷媒サイクルへ流出させる。
【０１２１】
このように、流入口と流出口を上下で切換えると、冷房運転時に、第２の利用側冷媒サイクルでは、第２，第４補助熱交換器１９ａ，１９ｂから流出した例えば７［℃］程度の低温の冷媒が左槽の底部に流入し、冷媒貯留タンク２０内の利用側冷媒３０が右槽上部から流出する。このため、低温で比重の大きい冷媒が左槽の底部から溜まりはじめ、時間と共に上部まで低温の冷媒が左槽に溜まる。このように、左槽は内部の冷媒が混合されることなく上下に温度成層を形成し、低温の領域を時間と共に広げながら蓄熱することができる。このとき、第２，第４補助熱交換器１９ａ，１９ｂへ冷媒を送り出す第２の冷媒搬送装置２５の吸い込み口が接続されている右槽上方の冷媒の温度はほとんど変動せず、第２の利用側冷媒サイクルで冷媒貯留タンク２０内の高温の冷媒を取り出して熱交換するので、熱源側冷媒サイクルを効率よく運転できると共に、冷媒貯留タンク２０の左槽で十分に蓄熱することができる。また、第１の利用側冷媒サイクルでは、低温の冷媒を左槽上部から循環させて利用側熱交換器２２ａ，２２ｂで利用しており、特に、夏期の冷房立ち上げが瞬時に行えるという効果がある。
このように冷媒貯留タンク２０の流入口と流出口を切換えるような構成にした時には、フィルタ２６は上方から下方の底部にまで伸ばし、暖房および冷房の両方において、第１の利用側冷媒サイクルの冷媒配管ｉ’からの流入口に配置する。
【０１２２】
またこの流入口と流出口を切換えるには、例えば左槽の場合、接続配管ｒと接続配管ｓとの間を接続する２本の接続配管を互いに交わらずに交差するような状態で設け、２本の配管のそれぞれに冷媒流路を切換える開閉弁を備え、さらに接続配管ｒと接続配管ｓにおいて、それぞれ２本の配管への分岐箇所の間に開閉弁を備えるように構成すればよい。そして、暖房運転の時には接続配管ｓ，ｔに設けた開閉弁を開とし、２本の配管に設けた開閉弁を共に閉とすれば、図１２の構成と同様になる。また、冷房運転の時には接続配管ｓ，ｔに設けた開閉弁を閉とし、２本の配管に設けた開閉弁を共に開とすれば、左槽において上方の開口が冷媒搬送装置２１の吸い込み口に接続され、第２，第４補助熱交換器１９ａ，１９ｂの出口側が底部の開口に接続され、暖房運転時とは流出口と流入口を上下で逆にできる。
また、右槽の開口においても同様であり、接続配管ｔと接続配管ｉ’にも同様に２本の接続配管と開閉弁を備えれば、流出口と流入口を上下で逆にできる。
ただし、流入口と流出口を暖房運転と冷房運転とで切換える手段はこれに限るものではなく、他の方法を用いてもよい。
【０１２３】
本実施の形態では、冷媒貯留タンク２０内をその一部が連通した仕切り２７で仕切ったので、通常の運転状態では、第１の冷媒搬送装置２１と第２の冷媒搬送装置２５の吐き出し冷媒循環量が異なり、この吐出し冷媒循環量の差によって連通部における冷媒の流れの向きが決まる。例えば、室内ユニットの多数が運転しており第１の冷媒搬送装置２１の吐き出し冷媒循環量の方が第２の冷媒搬送装置２５のそれよりも大きい時は、連通部を冷媒が左向きに流れる。また、逆に、室内ユニットの多数が停止しており第１の冷媒搬送装置２１の吐き出し冷媒循環量の方が第２の冷媒搬送装置２５のそれよりも小さい時は、連通部を冷媒が右向きに流れる。この中間の室内ユニットの運転／停止状態では、第１の冷媒搬送装置２１の吐出し冷媒循環量と第２の冷媒搬送装置２５の吐き出し冷媒循環量とがほぼ同一となる場合がある。このような場合、冷媒貯留タンク２０内の仕切り２７の連通部の冷媒流量はほとんど０となり、利用側冷媒サイクルは利用側熱交換器２２ａ，２２ｂと第２、第４の補助熱交換器１９ａ，１９ｂとが直結されたようになり、図６とほぼ同様な冷媒サイクルとなる。
なお、仕切り２７の連通する位置は冷媒貯留タンク２０の上下方向のどこでよい。図１２にような流入口，流出口の配置の場合には、暖房時には下方で右槽と左槽を連通し、冷房時には上方で右槽と左槽を連通するように、仕切りを移動可能な構成にしてもよい。この仕切り２７の移動は、例えば手動でもよいしモータや電磁弁によって連通部が移動するように構成してもよい。
【０１２４】
また、本実施の形態では、冷媒貯留タンク２０内で仕切り２７で仕切られてできた２槽は、第１の冷媒搬送装置２１の吸い込み口への流出口が設けられた左槽の容積の方が、第２の冷媒搬送装置２５の吸い込み口への流出口が設けられた右槽の容積より大きくなっている。このように構成すると、冷媒貯留タンク２０内に暖房運転時はより低温の、冷房時にはより高温の利用側熱交換器２２ａ，２２ｂからの戻り冷媒が留まることなく、スムーズに第２，第４補助熱交換器１９ａ，１９ｂに流入するので、熱源側冷媒サイクルの効率を高く維持しやすいという効果がある。
【０１２５】
第１温度センサ３１は、第２補助熱交換器１９ａおよび第４補助熱交換器１９ｄの利用側冷媒出口側接合点と冷媒貯留タンク２０との間を接続する接続配管ｒに設置されている。また、熱源側冷媒の温度を検出する配管温度センサ３２ａ，３２ｂは、第１，第２熱源側冷媒サイクルの熱源側熱交換器１３ａ，１３ｂの入口側に設けられている。３３は利用側熱交換器２２ａ，２２ｂの入口側に設けた第２温度検出手段で、例えば第２温度センサ、３４は外気温度検出手段で、例えば外気温度センサ、３５ａ，３５ｂは室内ユニットｇ，ｈに設けられた温度検出手段で、例えば空調室内の温度を検出する温度センサ、３６は利用側熱交換器２２ａ，２２ｂの出口側に設けた第３温度検出手段で、例えば第３温度センサである。
熱源側冷媒サイクルの能力は第１温度センサ３１の検出温度ＴＨ１が予め設定されている目標温度ＴＭに近づくように制御される。例えば、冷房運転の場合、第１温度センサ３１の検出温度ＴＨ１と目標温度ＴＭとの温度差
ΔＴＨ１＝ＴＨ１−ＴＭ ・・・・・・・・・・・・・・・・・（１０）
を制御装置４１内部の演算部で算出し、この値を１６進数等の温度差コードに変換して室外ユニットｅおよびｅ’に送信する。室外ユニットｅおよびｅ’は家庭用エアコン等の標準仕様で構成されていれば、熱交換ユニットｄから送られてきた温度差コードを通常の室内ユニットから送られてくる室温設定値と実際の室内（吸い込み）空気温度との差から作られる温度差コードと同様に扱い、第１，第２の室外ユニットｅ，ｅ’内に設置された制御装置４２ａ、４２ｂが圧縮機１１ａ、１１ｂおよび冷媒流量制御弁１４ａ、１４ｂを制御する。
【０１２６】
一方、暖房運転の場合も同様に、
ΔＴＨ１＝ＴＭ−ＴＨ１ ・・・・・・・・・・・・・・・・・（１１）
を制御装置４１内部の演算部で算出し、この値を１６進数等の温度差コードに変換して室外ユニットｅおよびｅ’に送信し、この値に従って制御装置４２ａ、４２ｂが圧縮機１１ａ、１１ｂおよび冷媒流量制御弁１４ａ、１４ｂを制御する。
【０１２７】
また、本実施の形態では、第１温度センサ３１の検出温度の目標値は、冷房運転の場合、ＴＭ＝７［℃］、暖房運転の場合、ＴＭ＝５０［℃］を基本とし、外気温度センサ３４の検出温度によって変更する。例えば、冷房運転時、外気温度センサ３４の検出値が２５［℃］未満であれば、第１温度センサ３１の検出温度の目標値ＴＭを１０［℃］とする。また、暖房運転時、外気温度センサ３４の検出値が１０［℃］以上であれば、第１温度センサ３１の検出温度の目標値ＴＭを４５［℃］とする。このように、外気温度と空調室温設定値との差が小さい場合には、第１温度センサ３１の目標値を空調室温設定値との差が小さくなる方向へ変更することによって、熱源側冷媒サイクルの過剰な運転が抑えられるので、効率的かつエネルギ消費の少ない冷凍空調装置を得ることができる。
【０１２８】
また、第１温度センサ３１の目標温度ＴＭは、外気温度センサ３４の検出値のみではなく、室内ユニットの運転台数や各室内ユニットの空調設定温度、運転モードなどに応じて変更してもよい。例えば、室内ユニットが２台接続されていて、暖房運転時、１台は設定温度２０［℃］、もう１台は設定温度２４［℃］の時はＴＭ＝４８［℃］、２台とも設定温度２４［℃］であればＴＭ＝５０［℃］、２台とも設定温度２２［℃］であればＴＭ＝４７［℃］、２台とも設定温度２０［℃］であればＴＭ＝４５［℃］などとする。また、冷房運転時、２台とも設定温度２６［℃］であればＴＭ＝７［℃］、１台は設定温度２６［℃］、もう１台はドライモードであればＴＭ＝９［℃］などとする。また、１台は設定温度２６［℃］でもう１台は停止している場合はＴＭ＝８［℃］などとする。
さらに、接続配管ｉ’に第３温度センサ３６を設置して、この検出値に応じて第１温度センサ３１の目標値を変更してもよい。例えば、冷房運転時に、第２温度センサ３３の検出値が７［℃］で第３温度センサの検出値が１３［℃］であれば、第１温度センサの目標値はＴＭ＝７［℃］のままとし、第２温度センサ３３の検出値が７［℃］で第３温度センサの検出値が１２［℃］となれば、第１温度センサの目標値はＴＭ＝８［℃］に変更する。
【０１２９】
本実施の形態では、第１，第２の室外ユニットｅ，ｅ’は、標準仕様のヒートポンプの室外ユニットを使用でき、安価に冷凍空調装置を構成できるという利点がある。また、熱交換ユニットｄを別体としないで、第１，第２の室外ユニットｅ，ｅ’と一体の室外ユニットとして構成しても構わない。これらを一体で構成すれば、搬入および工事の手間が省け、工事費が節約されると共に、住宅の外観、美観も損なわないことは言うまでもない。
【０１３０】
また、利用側冷媒サイクルの配管において、利用側熱交換器への送り側配管（ｉ，ｊ，ｋ）と利用側熱交換器からの戻り側配管（ｉ’，ｊ’，ｋ’）とで配管径が異なっているとよい。このようにしておけば、配管接続工事の際、例えば、送り配管ｉから送り配管ｊ，ｋへの分岐部分で、送り配管ｉが誤って戻り配管ｊ’に接続されたりして利用側熱交換器に冷媒が循環せず空調できないといったトラブルを未然に防ぐことができる。さらに、利用側熱交換器２２ａ，２２ｂの出口側および利用側冷媒流量制御弁２３ａ，２３ｂの入口側の接続部もその内径または外径が異なっているとよい。また、配管の配管径を異なるようにする代わりに、配管を接続する継ぎ手の形や大きさを異なるように構成しても同様であり、配管接続工事などの際に接続間違いが起こるのを防ぐことができ、信頼性の高い冷凍空調装置が得られる。
【０１３１】
実施の形態４．
以下、本発明の実施の形態４による冷凍空調装置として、例えば冷却運転で室内を冷房し、加熱運転で室内を暖房する冷暖房装置について説明し、冷却運転を冷房運転、加熱運転を暖房運転として記す。図１３は本実施の形態による冷暖房装置を示す構成図である。図において、熱源側冷媒サイクルは、第１の圧縮機１１ａ、第１の流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａ、第１のレシーバ１５ａ、第１補助熱交換器１６ａを連接してなる第１の熱源側冷媒サイクルと、第２の圧縮機１１ｂ、第２の流路切換弁１２ｂ、第２の熱源側熱交換器１３ｂ、第２の冷媒流量制御弁１４ｂ、第２のレシーバ１５ｂ、第３補助熱交換器１６ｂを連接してなる第２の熱源側冷媒サイクル、および第３の冷媒搬送装置２８、加熱ボイラ２９、第５の補助熱交換器１６ｃを連接してなる第３の熱源側冷媒サイクルとから成っている。これら第１および第２の熱源側冷媒サイクルの容量（定格能力）の合計は、実施の形態１の熱源側冷媒サイクルの容量（定格能力）と同一になるよう設定されている。また、第３の熱源側冷媒サイクルは加熱専用であり、これ１台だけで必要な暖房能力が発揮される容量に設定されている。
【０１３２】
また、この加熱専用の第３の熱源側冷媒サイクルは、利用側冷媒サイクルの冷媒の流れの向きに対して、冷却／加熱用の冷媒サイクルである第１，第２の熱源側冷媒サイクルよりも上流側で、第１，第２の熱源側冷媒サイクルのそれぞれと直列に接続している。また、第３の熱源側冷媒サイクルを構成する加熱装置としては、例えば灯油やガスを燃焼させて温熱を得る加熱ボイラ２９を用いており、暖房機能のみを有する。
【０１３３】
一方、利用側冷媒サイクルは、第１の冷媒搬送装置２１、接続配管ｉ、接続配管ｊ，ｋ、利用側冷媒流量制御弁２３ａ，２３ｂ、利用側熱交換器２２ａ，２２ｂ、接続配管ｊ’，ｋ’、接続配管ｉ’、冷媒貯留タンク２０を連接して成る第１の利用側冷媒サイクルと、第２の冷媒搬送装置２５、第６補助熱交換器１９ｃ、第２補助熱交換器１９ａ、第４補助熱交換器１９ｂ、冷媒貯留タンク２０を連接して成る第２の利用側冷媒サイクルとから構成されている。接続配管ｋ、利用側冷媒流量制御弁２３ｂ、利用側熱交換器２２ｂ、および接続配管ｋ’は実施の形態１と同様、接続配管ｊ、利用側冷媒流量制御弁２３ａ、利用側熱交換器２２ａ、および接続配管ｊ’に並列に接続されている。また、第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂは実施の形態２および３と同様、並列に接続されており、これらはそれぞれ第１補助熱交換器１６ａおよび第２補助熱交換器１６ｂと熱交換するよう一体に形成されている。また、第６補助熱交換器１９ｃは、第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂと直列に接続されており、第５補助熱交換器１６ｃと熱交換するように一体に形成されている。
【０１３４】
また、第１，第２の熱源側冷媒サイクルは、家庭用エアコンなどの標準的な冷媒サイクルを利用しているため、圧縮機１１ａ、流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａは第１の室外ユニットｅに収納されており、圧縮機１１ｂ、四方弁１２ｂ、第１の熱源側熱交換器１３ｂ、第１の冷媒流量制御弁１４ｂは第２の室外ユニットｅ’に収納されている。さらに、第３の熱源側冷媒サイクルも、家庭用灯油ボイラ等の標準品を利用しており、第３の冷媒搬送装置２８、加熱ボイラ２９とが室外ユニットｅ’’に収納されている。さらにまた、第１の冷媒搬送装置２１、第２の冷媒搬送装置２５、一体となった第１補助熱交換器１６ａおよび第２補助熱交換器１９ａ、一体となった第３補助熱交換器１６ｂおよび第４補助熱交換器１９ｂ、一体となった第５補助熱交換器１６ｃおよび第６補助熱交換器１９ｃ、冷媒貯留タンク２０、レシーバ１５ａ、１５ｂは熱交換ユニットｄに収納されている。
【０１３５】
第１の熱源側冷媒サイクルは、第１の室外ユニットｅと熱交換ユニットｄとの間で接続配管ｍおよびｍ’で接続されている。第２の熱源側冷媒サイクルは、第２の室外ユニットｅ’と熱交換ユニットｄとの間で接続配管ｎおよびｎ’で接続されている。第３の熱源側冷媒サイクルは、第３の室外ユニットｅ’’と熱交換ユニットｄとの間で接続配管ｏおよびｏ’で接続されている。また、冷媒貯留タンク２０内にはフィルタ２６が設置されており、接続配管ｉ’の一端が該フィルタ２６の内部に開口して接続されている。冷媒貯留タンク２０は、その内部で最上部から縦方向に仕切り２７で左右２槽に分割されており、仕切り２７の下部でその一部が開口していて左右２槽の利用側冷媒３０が連通している。さらに、冷媒貯留タンク２０の上部は大気に開放されており、冷媒貯留タンク２０に接続されているすべての接続配管は、冷媒貯留タンク２０内の利用側冷媒３０の喫水面下に開口している。
【０１３６】
つぎに、動作について説明する。
冷房運転時は、第１、第２の熱源側冷媒サイクルを運転し、第３の熱源側冷媒サイクルは停止する。この冷房運転時は第１、第２の熱源側冷媒サイクルとも図中実線の冷媒サイクルとなる。冷房運転時の第１、第２の熱源側冷媒サイクルの動作は実施の形態１と同様であるので割愛する。
一方、利用側冷媒サイクルでは、冷媒貯留タンク２０の左側の槽の底部から流出した比較的低温の利用側冷媒３０は、第１の冷媒搬送装置２１によって接続配管ｉおよびｊ、ｋを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を冷房すると同時に自らは加熱されて、接続配管ｊ’，ｋ’およびｉ’を通って冷媒貯留タンク２０の右側の槽に戻る。また、一方、冷媒貯留タンク２０の右側の槽の底部から流出した比較的高温の利用側冷媒３０は、第２の冷媒搬送装置２５によって第６補助熱交換器１９ｃ通過して第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに分岐して送り込まれる。第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに送り込まれた冷媒３０は、第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂを通して、第１および第２の熱源側冷媒サイクルによって外気へ放熱すると同時に自らは冷却され、合流した後冷媒貯留タンク２０の左側の槽の上部に戻る。
【０１３７】
暖房運転時は、第１、第２の熱源側冷媒サイクルを停止し、第３の熱源側冷媒サイクルのみ運転する。暖房運転時には、第３の冷媒搬送装置２８によって送り出された第３の熱源側冷媒は、灯油、ガス等を燃焼して得られる熱を加熱ボイラ２９で奪うと同時に自らは加熱されて、第５補助熱交換器１６ｃに流入する。ここで、第６補助熱交換器１９ｃを流れる利用側冷媒３０に放熱すると共に自らは冷却されて、再び第３の冷媒搬送装置２８に流入する。第３の熱源側冷媒サイクルを循環する冷媒には、例えば水、若しくはエチレングリコール、プロピレングリコールおよびＤ−ソルビトールなどの溶媒のうちの少なくとも１つまたは複数を重量比で数十％以下含んだ水溶液を用いる。
【０１３８】
一方、利用側冷媒サイクルでは、冷媒貯留タンク２０の左側の槽の底部から流出した比較的高温の利用側冷媒３０は、第１の冷媒搬送装置２１によって接続配管ｉおよびｊ、ｋを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を暖房すると同時に自らは冷却されて、接続配管ｊ’，ｋ’およびｉ’を通って冷媒貯留タンク２０の右側の槽の上部に戻ってくる。また、一方、冷媒貯留タンク２０の右側の槽の底部から流出した比較的低温の利用側冷媒３０は、第２の冷媒搬送装置２５によって第６補助熱交換器１９ｃに流入する。ここで、一体として形成された第５補助熱交換器１６ｃを通して第３の熱源側冷媒サイクル内を循環する第３の冷媒から熱を奪う。これと同時に自らは加熱されたのち、第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに分岐して送り込まれる。第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに送り込まれた冷媒３０は、そのまま通過して合流した後冷媒貯留タンク２０の左側の槽の上部に戻る。
【０１３９】
以上のように、本実施の形態によれば第１、第２の熱源側冷媒サイクルに直列に第３の熱源側冷媒サイクルを追加し、第１、第２の熱源側冷媒サイクルは冷房運転のみ、第３の熱源側冷媒サイクルは暖房運転のみに使用されるように構成したため、特に、冬期の外気温度が氷点下になる地方で運用され、第１、第２の熱源側冷媒サイクルであるヒートポンプでは暖房能力不足となる場合でも、暖房能力を確保しやすいという効果がある。
また、第１、第２の熱源側冷媒サイクルは冷房運転のみにしか使用しないので、除霜運転を行う必要がなく、除霜運転による利用側冷媒の温度低下も起こらない。このため、利用側冷媒の温度を加熱利用に適した温度に維持できる。
また、電気入力による第１、第２の熱源側冷媒サイクルの運用費と灯油入力による第３の熱源側冷媒サイクルの運用費とでは、同一暖房能力で比較した場合、一般的に前者の方が割高であるため、本実施の形態によれば、暖房能力は運用費が安価な第３の熱源側冷媒サイクルのみで賄うことによって、使用者が支払う空調運用費を安価に抑えられるという効果がある。
【０１４０】
また、図１４に示すように、第３の熱源側冷媒サイクルにおいて第５補助熱交換器１６ｃをバイパスするバイパス回路ｕと、第２の利用側冷媒サイクルにおいて第６補助熱交換器１９ｃをバイパスするバイパス回路ｖを設けてもよい。
このバイパス回路ｕ，ｖを設けたことによって、第３の熱源側冷媒サイクルを循環する熱源側冷媒の一部をバイパス回路ｕに流通させると共に第２の利用側冷媒サイクルを循環する利用側冷媒の一部をバイパス回路ｖに流通させる。このため、圧力損失を低減でき、第３の冷媒搬送装置２８を小型のもので構成できる。また、バイパス回路ｖを設け、加熱ボイラ２９の設定温度を例えば５５［℃］から７０［℃］に上げれば、第５，第６補助熱交換器１６ｃ，１９ｃを小型のもので構成できる。
【０１４１】
なお、本実施の形態では、ヒートポンプである第１および第２の熱源側冷媒サイクルは２台が並列に接続されている例を示したが、これらヒートポンプである冷媒サイクルが３台以上あって並列に接続されていてもよいし、１台しか接続されていなくてもよい。
また、第１および第２の熱源側冷媒サイクルは必ずしもヒートポンプである必要もなく、冷却専用の冷媒サイクルであってもよい。冷却専用の冷媒サイクルをで構成すればさらに安価な冷凍空調装置が得られる。
【０１４２】
さらに、第１、第２の熱源側冷媒サイクルは、ヒートポンプでなく臭化リチウム−水系やアンモニア−水系等の吸収式冷凍機、吸収式冷温水機や吸着式冷温水機でもよい。
また、第３の熱源側冷媒サイクルは、灯油やガスを燃焼させる加熱ボイラではなく電気ヒータを第６補助熱交換器１９ｃに巻きつけて、あるいは接触させて代用してもよい。もちろん、第３の熱源側冷媒サイクルは、ヒートポンプや吸収式あるいは吸着式冷温水機など、加熱機能を発揮するものであれば何でもよい。また、第３の熱源側冷媒サイクルは必ずしも１系統である必要はなく、灯油ボイラ、ガスボイラ、電気ヒータなどを併用して２系統以上並列または直列に接続してもよい。
【０１４３】
実施の形態５．
図１５は実施の形態５による冷凍空調装置として例えば冷暖房装置を示す構成図である。実施の形態４では、第１、第２の熱源側冷媒サイクルは冬期の暖房運転には利用せず、すべての暖房負荷を第３の熱源側冷媒サイクルで賄うようにした。これでは、第１、第２の熱源側冷媒サイクルでも暖房運転できる設備を備えていながら使用しないという無駄が生じる。そこで、本実施の形態では、図１５に示すように、第６補助熱交換器１９ｃを第２，第４補助熱交換器１９ａ，１９ｂの下流側に設置し、動作保障する外気温度の下限で必要となる暖房負荷に対して第１および第２の熱源側冷媒サイクルの能力で不足する能力分を賄うだけの設備を第３の熱源側冷媒サイクルに持たせる。このように構成した上で、第１および第２の熱源側冷媒サイクルで例えば５０［℃］程度に加熱した利用側冷媒を、さらに第５，第６補助熱交換器１６ｃ，１９ｃを通して第３の熱源側冷媒サイクルで例えば８０［℃］程度に加熱することにより、必要な能力を確保する。
【０１４４】
本実施の形態では、以上のように加熱専用の第３の熱源側冷媒サイクルと、冷却／加熱併用の第１および第２の熱源側冷媒サイクルとを利用側冷媒サイクルに対して直列に接続して構成している。そして、利用側冷媒サイクルに対して、冷却／加熱併用の第１および第２の熱源側冷媒サイクルの下流側に加熱専用の第３の熱源側冷媒サイクルを接続している。ここで、冷却／加熱併用の第１および第２の熱源側冷媒サイクルは、蒸気圧縮式冷凍サイクルで構成するものとし、その冷房機能と暖房機能を共に利用するものである。このため設備の無駄を省きながら低外気温度での暖房性能を十分確保することができると共に、第３の熱源側冷媒サイクルである加熱ボイラ２９に比べてエネルギ効率が高い第１、第２の熱源側冷媒サイクルであるヒートポンプの運転時間が増加する。さらに、第１，第２の熱源側冷媒サイクルは第１，第３補助熱交換器１６ａ，１６ｂを通して外気からの吸熱を比較的温度の低い利用側冷媒に放熱するので、効率よく運転することができ、石油資源の有効利用、二酸化炭素の排出抑制など、地球環境の保全にも役立つ。
【０１４５】
実施の形態５では、通常の暖房運転時には、第１および第２の熱源側冷媒サイクルで不足する能力を賄うために第３の熱源側冷媒サイクルを運転するように構成している。ところが、特に外気温度が低くなって、第１、第２の熱源側冷媒サイクルの発電端効率も含めて考えた一次エネルギに対する効率が加熱ボイラ２９より低くなる場合は、第１、第２の熱源側冷媒サイクルを停止して、第３の熱源側冷媒サイクルである加熱ボイラ２９のみを運転するようにしてもよい。この場合は、第３の熱源側冷媒サイクルだけで必要な暖房負荷を賄うだけの設備容量が必要であることは言うまでもない。また、逆に、特に外気温度が高い時に暖房要求がある場合に、第１、第２の熱源側冷媒サイクルであるヒートポンプの方が第３の熱源側冷媒サイクルである加熱ボイラ２９よりも一次エネルギに対する効率が高くなる場合は、第３の熱源側冷媒サイクルである加熱ボイラ２９を停止して、第１、第２の熱源側冷媒サイクルであるヒートポンプのみで暖房運転するとよい。外気温度は熱交換ユニット内に設置されている外気温度センサ３４によって検出できる。
本実施の形態の構成では、利用状況に応じて様々のパターンで第１、第２、第３の熱源側冷媒サイクルを運転でき、機器を有効利用でき、エネルギの低減を図ることができる。
【０１４６】
また、暖房運転時、第１、第２の熱源側冷媒サイクルのうちいずれか一方または両方が除霜運転時入った場合、加熱専用の第３の冷媒サイクルと冷却／加熱併用の第１、第２の冷媒サイクルのうちの少なくとも１系統の冷媒サイクルは暖房運転を継続するように制御することにより、除霜運転時の空調室内の温度を維持でき、快適性を維持しやすい冷凍空調装置を得ることができる。この制御は、例えば制御装置４１で行う。
【０１４７】
また、暖房運転時、第１、第２の熱源側冷媒サイクルのうちいずれか一方または両方が除霜運転時入った場合、制御装置４１は、第１温度センサ３１の検出温度が目標値に近づくように第３の熱源側冷媒サイクルの能力を増大させるよう制御信号を制御装置４２ｃに送るように制御することもできる。このように、第１または第２熱源側冷媒サイクルの除霜運転時に、暖房運転を行う第３の熱源側冷媒サイクルの能力を増加して暖房運転させると、利用側冷媒の温度低下が小さくなるように自動的制御され、室内の快適性の向上を図ることができる。
なお、除霜運転中に暖房能力を増加して運転させる冷媒サイクルは、加熱専用の第３の冷媒サイクルに限るものではなく、冷却／加熱併用の第１、第２の冷媒サイクルが暖房運転中の場合にはその冷媒サイクルの能力を増加して暖房運転を継続するように制御すればよい。
【０１４８】
また、暖房運転時、第１、第２の熱源側冷媒サイクルのうちいずれか一方または両方が除霜運転開始条件を満たした場合、制御装置４１は、第３の熱源側冷媒サイクルの能力を増大させるよう、例えば最大能力で運転するように制御信号を制御装置４２ｃに送るように制御すると、さらに利用側冷媒の温度低下が小さくなるように自動的制御され、室内の快適性の向上を図ることができる。
また、この場合にも、暖房能力を増加して運転させる冷媒サイクルは、加熱専用の第３の冷媒サイクルに限るものではなく、冷却／加熱併用の第１、第２の冷媒サイクルが暖房運転中の場合にはその冷媒サイクルの能力を増加して暖房運転を継続するように制御すればよい。
【０１４９】
また、特に第１の熱源側冷媒サイクル、第２の熱源側冷媒サイクル、第３の熱源側冷媒サイクルの容量制御が運転／停止のみしか選択できない場合は、図１６に示すように、第１温度センサ３１の検出値ＴＨ１が目標温度ＴＭに近づくように、第１、第２、第３の熱源側冷媒サイクルを順次運転するようにしてもよい。第１温度センサ３１の目標温度ＴＭに上限ＴＭＨ、下限ＴＭＬを設定し、第１温度センサ３１の検出温度ＴＨ１がＴＭＨとＴＭＬの間に収まるように第１、第２、第３の熱源側冷媒サイクルを運転／停止する。図１６において、横軸は第１温度センサ３１の検出温度ＴＨ１、縦軸は第１、第２、第３の熱源側冷媒サイクルの運転／停止を表す。例えばＴＭＨ１＝５１［℃］、ＴＭＨ２＝５０［℃］、ＴＭＨ３＝４９［℃］、ＴＭＬ１＝４９［℃］、ＴＭＬ２＝４８［℃］、ＴＭＬ３＝４７［℃］として、検出温度ＴＨ１がＴＭＬ１から順に下がってくると、熱源側冷媒サイクルを１系統づつ追加運転する。一方、検出温度ＴＨ１がＴＭＨ３から順に上がってくると、熱源側冷媒サイクルを１系統づつ停止する。例えば第１の熱源側冷媒サイクルが運転の時でＴＭＬ１＜ＴＨ１＜ＴＭＨ１の間は変更しない。また、第１，第２の熱源側冷媒サイクル運転の時でＴＭＬ２＜ＴＨ１＜ＴＭＨ２の間は変更せず、第１，第２，第３の熱源側冷媒サイクル運転の時でＴＭＬ３＜ＴＨ１＜ＴＭＨ３の間は変更しない。このように、熱源側冷媒サイクルを３系統にし、それぞれの熱源側冷媒サイクルを運転／停止することにより、熱源側冷媒サイクルが１系統の場合に比べて、利用側冷媒の温度変化を小さい範囲内に収めることができ、冷媒温度の安定性、ひいては、空調室内の快適性が向上する。
【０１５０】
実施の形態６．
図１７は本実施の形態による冷凍空調装置として例えば冷暖房装置を示す構成図である。実施の形態２〜実施の形態５では、利用側冷媒サイクルにおいて、接続配管ｉ’および接続配管ｒは、それぞれ右槽、左槽の側面から冷媒貯留タンク２０に接続して開口していたが、図１７に示すように、冷媒貯留タンク２０の底面から接続して、それぞれ上部およびフィルタ内部に開口するように構成してもよい。このようにすれば、冷媒貯留タンク２０の側面に接続部を設ける必要がなくなるため側面をすっきりすることができる。従って、冷媒貯留タンク２０の容量を維持したまま、熱交換ユニットｄの設置面積を抑えることができ、スペース効率が向上する。
【０１５１】
このとき、接続配管ｉ’およびｒの冷媒貯留タンク２０内における開口部の位置は、利用側冷媒の流出速度ｕ［ｍ／ｓ］、開口部から喫水面までの距離ｈ［ｍ］との間に、式（１２）の関係が成立しているとよい。
ｈ≧ｕ２ ／２ｇ ・・・・・・・・・・・・・・・・・・・・・（１２）
ただし、ｇ：重力加速度＝９．８［ｍ／ｓ２ ］である。右辺ｕ２ ／２ｇは、大気中で、ある開口部から鉛直上向きに速度ｕで流出した流体が到達する最高地点までの距離である。従って、この距離より喫水面までの距離ｈを長く保っておけば、冷媒貯留タンク２０の喫水面はある程度静かであり、冷媒貯留タンク２０のオーバーフロー口から中の冷媒がこぼれ出たり、接続配管ｒの開口から喫水面を抜けて噴出した冷媒が再び喫水面に戻ってくることによる撹拌効果で、温度成層が乱され、利用側冷媒温度の安定性が損なわれるようなことはない。
実際には、冷媒貯留タンク２０の喫水面より下で利用側冷媒が流出するので、タンク内冷媒の粘性により流出した冷媒が到達する最高地点までの距離は、右辺ｕ２ ／２ｇより小さくなるため、ｈはこの距離ｕ２ ／２ｇよりある程度までなら小さくても問題ない。
もちろん実施の形態３と同様、仕切り２７によって冷媒貯留タンク２０を右槽と左槽とに分割し、右槽と左槽にそれぞれ２つの開口を設けた構成になっている。このため、暖房運転では左槽は内部の冷媒が混合されることなく上下に温度成層を形成し、高温の領域を時間と共に広げながら十分に蓄熱することができる。また冷房運転では、冷媒貯留タンク２０内左槽の冷媒を右槽の冷媒よりも比較的低温に保つことができるので、夏期の冷房立ち上げを迅速に行えるという効果がある。
【０１５２】
実施の形態７．
図１８は本実施の形態による冷凍空調装置として例えば冷暖房装置を示す構成図である。実施の形態５では、冷却／加熱併用の第１、第２の熱源側冷媒サイクルと加熱専用の第３の熱源側冷媒サイクルとは直列に接続していたが、図１８に示すように、第３の熱源側冷媒サイクルと第１、第２の熱源側冷媒サイクルを並列に接続してもよい。そしてそれぞれの冷媒配管に分岐する部分よりも下流側に、流路切換手段として例えばニ方弁５１、５２を設ける。
この流路切換手段によって、冷房運転時に、第３の冷媒サイクルと熱交換する利用側補助熱交換器１９ｃには利用側冷媒が流れないように、冷媒流路を切換える。
【０１５３】
冷房運転時は、二方弁５１を閉、二方弁５２を開とし、冷却／加熱併用の冷媒サイクルである第１、第２の熱源側冷媒サイクルによって冷房運転する。ニ方弁５１によって、冷房運転時には第３の熱源側冷房サイクルと熱交換する第６補助熱交換器１９ｃには利用側冷媒が流れないように冷媒回路が切換えられている。
一方、暖房運転時は、二方弁５１を開、二方弁５２を閉とし、加熱専用の冷媒サイクルである第３の熱源側冷媒サイクルによって暖房運転する。また万が一、第３の熱源側冷媒サイクルが故障した場合には、二方弁５１を閉、二方弁５２を開として第１、第２の熱源側冷媒サイクルで暖房運転することもできる。
また、二方弁５１、二方弁５２とも開として第１、第２、第３の熱源側冷媒サイクルすべてを運転して暖房してもよい。これらの切換えは、熱交換ユニット内に設置されている外気温度センサ３４の検出温度に応じて切換えればよい。
【０１５４】
このように、加熱専用の第３の熱源側冷媒サイクルと、冷却／加熱併用の第１、第２の熱源側冷媒サイクルを並列に接続することにより、暖房能力を十分に確保でき、室内の快適性を維持しやすく、安価な冷凍空調装置を得ることができる。さらに、加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルのそれぞれを独立して制御でき、利用状況に適した運転を行うことができる。
【０１５５】
また、第１、第２の熱源側冷媒サイクルは冷却／加熱併用でなく冷却専用の冷媒サイクルで構成してもよい。この場合には、暖房運転の時には加熱専用の冷媒サイクルを動作させ、冷房運転の時には利用側冷媒の流路を切換手段で切換えると共に、冷却専用の冷媒サイクルを動作させる。
この構成では、加熱専用の冷媒サイクルと冷却専用の冷媒サイクルのそれぞれを独立して制御でき、利用状況に適した運転を行うことができ、特に無駄な機能を省き、安価な冷凍空調装置を得ることができる。
【０１５６】
実施の形態８．
図１９は本実施の形態による冷凍空調装置として例えば冷暖房装置を示す構成図である。実施の形態１〜実施の形態７では、熱源側冷媒サイクルと利用側冷媒サイクルとを熱交換する補助熱交換器群は、冷媒貯留タンク２０の外部に設置していたが、図１９に示すように、補助熱交換器１６ａ，１６ｂを冷媒貯留タンク２０の内部の利用側冷媒内に浸して設置してもよい。この時、第１および第２の熱源側冷媒サイクルは、冷媒貯留タンク２０内に設置された温度センサ３５の検出温度が目標温度に近づくように運転／停止される。このような構成にすると、実施の形態３〜実施の形態７で熱輸送サイクルとして動作している第２の利用側冷媒サイクルが必要なく、特に第２の冷媒搬送装置２５が必要なくなるため、システム全体の信頼性が向上するという効果がある。
【０１５７】
また、冷媒貯留タンク２０の内部に補助熱交換器１６ａ，１６ｂと共に蓄熱材６１を挿入しておいてもよい。この蓄熱材６１としては、例えば銅や鉄やレンガなどのブロックなど、または酢酸ナトリウムなどをカプセルやパイプなどに入れて使用する。酢酸ナトリウムを用いる場合には、顕熱と共に５０［℃］程度の潜熱も利用することができ、効果的に十分に蓄熱できる。
すなわち、冷媒貯留タンク２０の内容積を、利用側冷媒サイクルの加熱運転中に熱源側冷媒サイクルを除霜運転するときの利用側冷媒の温度を暖房に適した温度に維持するように、利用側冷媒の量または蓄熱材６１の量を蓄えられる内容積としている。
【０１５８】
このように構成すると、第１、第２の熱源側冷媒サイクルのいずれか一方または両方が除霜運転に入っても、冷媒貯留タンク２０内の蓄熱材６１の放熱により利用側冷媒温度が低下するのを防ぎ、室内空調の快適性をよりよく維持することができる。なお、第１および第２の熱源側冷媒サイクルは、冷媒搬送装置２１の吐き出し口に設置された第２温度センサ３３の検出温度が目標温度に近づくように運転／停止されるようにしてもよい。利用側熱交換器２２ａ，２２ｂへの供給冷媒温度により近い第２温度センサ３３の検出温度に基づいて、第１および第２の熱源側冷媒サイクルが運転されると、室内空調の快適性をよりよく維持することができる。また、蓄熱材６１を設けて設けていない構成と比較すると、利用側冷媒の温度低下を同等に設定すると、利用側冷媒の量を蓄熱材６１での蓄熱容量分だけ少なくできるので、冷媒貯留タンク２０を小型化することも可能である。さらに、蓄熱材６１として水よりも熱容量の大きい材質のもので構成すると、蓄熱材６１自体を小さくできる。この蓄熱材６１の蓄熱容量は、比熱と重量を決めることにより設定できるため、実施の形態１で述べたように除霜運転時の放熱量から利用側冷媒の温度低下が所定の温度以下になるように設定すれば、除霜運転時の利用側冷媒の温度を安定させることができる。
【０１５９】
また、補助熱交換器１６ａ，１６ｂは、通常の銅管を螺旋状や碁盤目状または千鳥状に配列したものを用いれば安価な冷凍空調装置を構成できる。また、フィンチューブやプレートフィン熱交換器を用いると、補助熱交換器および冷媒貯留タンク２０を小型化できる。
また、補助熱交換器１６ａ、１６ｂの少なくとも何れか一方をスパイラルフィン熱交換器で構成してもよい。図２０は、補助熱交換器１６ａをスパイラルフィン熱交換器で構成した冷媒貯留タンク２０を示す説明図であり、補助熱交換器１６ｂに関しては図示していない。銅などのフィンをスパイラル状に伝熱管の外側に固着してスパイラルフィン付き管を構成し、このスパイラルフィン熱交換器１６ａを冷媒貯留タンク２０内に貯留した利用側冷媒に浸漬するように配設している。このようなスパイラルフィン付き管では、スパイラルフィン付き管内を流れる熱源側冷媒と、冷媒貯留タンク２０内の利用側冷媒とが熱交換する際の利用側冷媒の伝熱面積、即ち管外壁面積とフィン表面積の合計が、熱源側冷媒の伝熱面積、即ち管内壁面積よりも大幅に大きくなる。このため、フィンを全く設けていない構成に比べて、水などを使用した場合の伝熱性能の悪い利用側冷媒の伝熱面積がおよそ６倍になり、熱通過率が４倍弱向上するので、補助熱交換器１６ａを大幅に小型化できる。
【０１６０】
厳密に言えば、フィンを全く設けていない伝熱管のみの構成でも管外壁面積は管内壁面積よりも伝熱管の肉厚分だけ大きいのであるが、これよりもプレートフィンやスパイラルフィンなどによって伝熱面積を大幅に大きくすると、伝熱性能を向上できる。
また、利用側冷媒の伝熱面積を熱源側冷媒の伝熱面積よりも大きくする構成は、この他に、例えば大きな金属板に伝熱管を蛇行させて固着して熱交換器１６ａとしてもよいし、また、複数枚の金属板を並列に配置し、これを複数の伝熱管が貫通するような構成としてもよい。
もちろん、実施の形態１〜実施の形態７における第２補助熱交換器１９における利用側冷媒の伝熱面積を第１補助熱交換器１６における熱源側冷媒の伝熱面積よりも大きくするように構成することもできる。
【０１６１】
また、本実施の形態のように冷媒貯留タンク２０内の利用側冷媒に浸漬させて補助熱交換器１６ａ，１６ｂを設け、伝熱管の内側を流通する熱源側冷媒と外側を流通する利用側冷媒とを熱交換する構成にすると、冷媒貯留タンク２０に冷熱を蓄熱して利用側熱交換器２２ａ，２２ｂでこの冷熱を室内や倉庫などの冷房あるいは冷凍冷蔵庫などの冷蔵や冷凍に利用する場合にも効果がある。即ち、利用側冷媒として例えば水などの凍結する媒体を使って冷熱を蓄熱する場合に、補助熱交換器１６ａ，１６ｂの周囲で利用側冷媒が凍結しても、利用側冷媒は冷媒貯留タンクの凍結していない部分を流通して冷熱を利用側熱交換器２２ａ，２２ｂへ輸送することができる。このため実施の形態１〜実施の形態７に比べ、利用側熱交換器２２ａ，２２ｂへ送る利用側冷媒の温度を低くすることができ、冷媒搬送装置２１の搬送動力の低減や、利用側熱交換器２２ａ，２２ｂでの除湿性能向上が期待できる。また、夜間電力使って補助熱交換器１６ａ，１６ｂで利用側冷媒を凍結させることによって蓄熱し、昼間、この蓄熱した冷熱を利用して冷房することによって、熱源側冷媒サイクルの設備を小型化したり、受電容量を低く抑えることなどが可能となる。
【０１６２】
さらに、実施の形態１〜実施の形態７では、熱源側冷媒サイクルで冷却運転中、補助熱交換器１６ａ，１６ｂ内部での利用側冷媒の凍結を保護するために、第１温度センサ３１での検出値が利用側冷媒の凍結温度＋４℃程度となったら熱源側冷媒サイクルを停止する、または、補助熱交換器１６ａ，１６ｂの外表面にそれぞれ第４、第５の温度センサを設置し、この検出値が利用側冷媒の凍結温度＋４℃程度となったら熱源側冷媒サイクルを停止するなどの制御が必要であったが、本実施の形態によればこれが不要となり、補助熱交換器１６ａ、１６ｂを冷媒貯留タンク２０内に配設するという比較的簡単な装置構成でシステム全体の信頼性を向上でき、安価な冷凍空調装置を得ることができる。
【０１６３】
また、図２１に示すように、冷媒貯留タンク２０内の利用側冷媒の流入口と流出口の間を分離するように、仕切り２７ａおよび２７ｂを設けてもよい。この仕切り２７ａ，２７ｂは一方が下方に連通部を有し、他方が上方に連通部を有する。そして分離した流入口側に補助熱交換器１６ａ，１６ｂを浸漬させ、流出口側は蓄熱材６１を浸漬させる。この構成では、利用側熱交換器２２ａ，２２ｂからの戻り冷媒がフィルタ２６を通って、ごみ、塵を除去された後、第１および第２の補助熱交換器１６ａおよび１６ｂで温度調整される。この後、冷媒貯留タンク２０内の蓄熱材６１を蓄熱して冷媒搬送装置２１に吸込まれるように冷媒貯留タンク２０内に流路を構成している。このため冷媒貯留タンク２０内において、効果的に補助熱交換器１６ａ，１６ｂ、蓄熱材６１と熱交換する冷媒流路を構成できる。
【０１６４】
実施の形態９．
実施の形態１〜実施の形態７では、熱源側冷媒サイクルが冷房を行う冷却運転時と暖房を行う加熱運転時とで冷媒の流れる方向が逆転するため、第１，第２補助熱交換器１６，１９での熱交換に際して、熱源側冷媒と利用側冷媒との流れの向きが暖房運転時は対向流であるのに対し、冷房運転時は並行流となっていた。ところが、熱源側冷媒サイクルにＲ４０７Ｃなどの非共沸混合冷媒が用いると、冷房運転時に利用側冷媒が第２補助熱交換器１９入口から出口に向かって冷却されて温度が低下していくのと並行して第１補助熱交換器１６の入口から出口に向かって熱源側冷媒の温度が上昇していく。このため、Ｒ２２などの単一冷媒またはＲ４１０Ａなどの擬似共沸冷媒を用いた場合よりも、熱源側の蒸発温度を低下させなければならず、効率が低下するという問題が考えられる。
【０１６５】
これに対し、本実施の形態では、熱源側冷媒としてＲ４０７Ｃなどの非共沸混合冷媒を用いた場合にも適用できるように、第２補助熱交換器１９の入口と出口とを冷房運転時と暖房運転時とで逆転させ、第１補助熱交換器１６を流れる熱源側冷媒に対して両運転共に対向流になる構成としている。
図２２は本実施の形態による冷凍空調装置として、例えば冷却運転で室内を冷房し、加熱運転で室内を暖房する冷暖房装置を示す構成図である。図において、６２は、補助熱交換器１９における利用側冷媒の流れ方向を切換える切換手段であり、例えば四方弁６２である。この四方弁６２は、その第１口が冷媒搬送装置２１の吸入口に、第２口が第２補助熱交換器１９の一端に、第３口が接続配管ｉ’の一端に、第４口が冷媒貯留タンク２０の底部開口にそれぞれ接続されている。冷房運転時は、熱源側および利用側冷媒サイクルとも図の実線の方向に冷媒が流れ、逆に、暖房運転時には図の破線の方向に冷媒が流れるように、四方弁１２および四方弁６２をそれぞれ切換える。
このため、第１、第２補助熱交換器１６、１９での熱交換が共に対向流となり、冷房・暖房運転の両運転において効果的に熱交換できる。
【０１６６】
また、図に示すように、第１温度センサ３１を冷媒搬送装置２１の出口側に設置すると、冷房・暖房運転の両方で、熱交換した後の利用側冷媒の温度を検出することができる。実施の形態１〜実施の形態７のように第２補助熱交換器１９と冷媒貯留タンク２０との間の配管に第１温度センサ３１を設けたままでは、暖房運転時は第２補助熱交換器１９の出口温度を検出することができるが、冷房運転時には流れの向きが変わってしまい入口温度になるため、利用側熱交換器２２ａ，２２ｂへの送り温度が保証できなくなる。
ただし、送り温度を保証しないという前提で第１温度センサ３１を第２補助熱交換器１９と冷媒貯留タンク２０との間の配管に設置しておく、あるいは、四方弁６２の第２口と第２補助熱交換器１９との間の配管に設置するということも可能である。前者の場合は、第１温度センサ３１の検出値は冷房運転時は第２補助熱交換器１９の入口温度、暖房運転時は出口温度になるので、その目標温度ＴＭは冷房時はＴＭ＝１２［℃］、暖房時はＴＭ＝５０［℃］などとする。このように、入口温度を検出する場合には、第２補助熱交換器１９での加熱あるいは冷却される分の温度差を考慮して運転制御するように構成すればよい。とにかく第２補助熱交換器１９出口温度が実施の形態１と同様、冷房で７［℃］、暖房で５０［℃］となるように設定すればよい。
【０１６７】
このように、本実施の形態によれば、第１，第２熱交換器１６，１９において冷房・暖房運転共に対向流とすることにより、熱源側冷媒としてＲ４０７Ｃ等の非共沸混合冷媒が用いられた場合でも冷却・加熱運転両方でのシステムを効率よく運転できるという効果がある。
【０１６８】
なお、本実施の形態では、利用側冷媒サイクルの流路の切換手段として四方弁６２を用いる例を示したが、図２３に示すように、電磁弁６３ａ，６３ｂ，６３ｃ，６３ｄを組み合わせてもよい。この場合、冷房運転時は、電磁弁６３ａおよび６３ｃが開、６３ｂおよび６３ｄが閉、暖房運転時は、電磁弁６３ｂおよび６３ｄが開、６３ａおよび６３ｃが閉となる。
図２２のように四方弁６２で構成する場合には、四方弁は４つ分の電磁弁よりも高価ではあるが冷媒配管を比較的単純に構成できる。また図２３のように４つの電磁弁６３ａ，６３ｂ，６３ｃ，６３ｄで構成する場合には、冷媒配管は多少複雑になるが価格の低減を図ることができる。
【０１６９】
図２２、図２３に示した構成では、冷媒貯留タンク２０において、第２補助熱交換器１９と接続する開口をタンク２０の上方側面に設け、四方弁６２または電磁弁６３ｃ，６３ｄと接続する開口をタンク２０の底面に設けているが、両方の開口ともタンク２０の底面に設けてもよい。冷媒貯留タンク２０の側面に接続部を設けないことにより、側面をすっきりと構成することができ、システム全体をコンパクトに構成しやすくなる。ただし、底面に２つの接続部を設ける場合には２つの接続部の間に、底面から水面までよりも短い程度の高さの分離板を設けて、冷媒貯留タンク２０に流入した利用側冷媒が、すぐに流出しないように構成した方がよい。
【０１７０】
実施の形態１０．
本発明に係わる冷凍空調装置が設置された後実際に運用されるまでの間に、利用側冷媒を充填する現地工事が発生するが、実施の形態１〜実施の形態９はすべて冷媒貯留タンク２０を大気に開放しておき、その上部から利用側冷媒を注ぎ込む構成になっていた。このため、現地での冷媒充填作業では、冷媒貯留タンク２０の上部からゴムホースやバケツを使って利用側冷媒を充填し、冷媒貯留タンク２０内が満杯になったら冷媒搬送装置２１を運転する、そして、冷媒貯留タンク２０内の冷媒が利用側熱交換器などに送られ冷媒貯留タンク２０内の冷媒が減ったら再び冷媒を充填する、という操作を繰り返す必要があり、手間がかかるという問題が考えられる。
【０１７１】
図２４は本実施の形態による冷凍空調装置として例えば冷暖房装置を示す構成図である。本実施の形態では、利用側冷媒の充填を容易にできるような構成にしている。図２４に示すように、止め弁６４ｂおよび接続口６５を備えた分岐管を冷媒搬送装置２１の吐き出し口直後に接続し、この接続点と冷媒搬送装置２１の吐き出し口との間に止め弁６４ａを設置する。例えば、利用側冷媒に水を用いる場合、現地での利用側冷媒充填作業では、止め弁６４ａを閉じ、接続口６５をゴムホースなどで水道蛇口に接続し、止め弁６４ｂを開いた後に水道蛇口を開けて利用側冷媒サイクル内に利用側冷媒である水を充填する。冷媒貯留タンク２０の適正水位まで水が充填されたら、水道蛇口、止め弁６４ｂの順に閉め、止め弁６４ａを開いてから冷媒搬送装置２１を運転すればよい。
このようにすれば、水道圧で利用側冷媒サイクルに冷媒である水を１回で容易に充填することができるので、現地冷媒充填作業の手間が省け、工事費を安価にすることができる。
【０１７２】
さらにこの構成では、冷媒貯留タンク２０を大気に開放せずに密閉型で構成してもよい。密閉型にすると開放型と比較してタンク内部を清潔に保持でき、汚れを防止でき、細菌の繁殖などを防ぐことができる。ただし、利用側冷媒が温度の変化によって多少膨張するのを吸収できるように、冷媒の喫水面から上方に多少空間を保持して密閉した方がよい。
【０１７３】
実施の形態１１．
以下、本発明の実施の形態１１による冷凍空調装置として、例えば冷却運転で室内を冷房し、加熱運転で室内を暖房する冷暖房装置について説明し、冷却運転を冷房運転、加熱運転を暖房運転として記す。図２５は本実施の形態による冷暖房装置を示す構成図である。図において、熱源側冷媒サイクルは、第１の圧縮機１１ａ、第１の流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａ、第１のレシーバ１５ａ、第１補助熱交換器１６ａを連接してなる第１の熱源側冷媒サイクルと、第２の圧縮機１１ｂ、第２の流路切換弁１２ｂ、第２の熱源側熱交換器１３ｂ、第２の冷媒流量制御弁１４ｂ、第２のレシーバ１５ｂ、第３補助熱交換器１６ｂを連接してなる第２の熱源側冷媒サイクルとからなっている。これらは、家庭用エアコンなどの標準的な蒸気圧縮式冷凍サイクルを利用しているため、圧縮機１１ａ、流路切換弁１２ａ、第１の熱源側熱交換器１３ａ、第１の冷媒流量制御弁１４ａは第１の室外ユニットｅに収納されており、圧縮機１１ｂ、流路切換弁１２ｂ、第１の熱源側熱交換器１３ｂ、第１の冷媒流量制御弁１４ｂは第２の室外ユニットｅ’に収納されている。また、室外ユニットｅ，ｅ’は制御装置４２ａ，４２ｂを備え、圧縮機１１ａ，１１ｂおよび冷媒流量制御弁１４ａ，１４ｂを制御している。
【０１７４】
一方、利用側冷媒サイクルは、第１の冷媒搬送装置２１、接続配管ｉ、接続配管ｊ，ｋ、利用側冷媒流量制御弁２３ａ，２３ｂ、利用側熱交換器２２ａ，２２ｂ、接続配管ｊ’，ｋ’、接続配管ｉ’、冷媒貯留タンク２０を連接して成る第１の利用側冷媒サイクルと、第２の冷媒搬送装置２５、第２補助熱交換器１９ａ、第４補助熱交換器１９ｂ、冷媒貯留タンク２０を連接して成る第２の利用側冷媒サイクルとから構成されている。接続配管ｋ、利用側冷媒流量制御弁２３ｂ、利用側熱交換器２２ｂ、および接続配管ｋ’は、接続配管ｊ、利用側冷媒流量制御弁２３ａ、利用側熱交換器２２ａ、および接続配管ｊ’に並列に接続されている。また、第２補助熱交換器１９ａと第４補助熱交換器１９ｂは実施の形態２，３と同様、並列に接続されており、これらはそれぞれ第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂと熱交換するよう一体に形成されている。
第２の利用側冷媒サイクルは、利用側冷媒を循環させて第２，第４補助熱交換器１９ａ，１９ｂでそれぞれ第１，第３補助熱交換器１６ａ，１６ｂと熱交換して、冷媒貯留タンク２０に熱を蓄える熱輸送サイクルを構成している。
【０１７５】
また、第１の冷媒搬送装置２１、第２の冷媒搬送装置２５、一体となった第１補助熱交換器１６ａ，第２補助熱交換器１９ａ、一体となった第３補助熱交換器１６ｂ，第４補助熱交換器１９ｂ、冷媒貯留タンク２０、レシーバ１５ａ、１５ｂは熱交換ユニットｄに収納されている。第１の熱源側冷媒サイクルは、第１の室外ユニットｅと熱交換ユニットｄとの間で接続配管ｍおよびｍ’で接続されている。第２の熱源側冷媒サイクルは、第２の室外ユニットｅ’と熱交換ユニットｄとの間で接続配管ｎおよびｎ’で接続されている。
【０１７６】
また、冷媒貯留タンク２０内にはフィルタ２６が設置されており、接続配管ｉ’の一端が該フィルタ２６の内部に開口して接続されている。冷媒貯留タンク２０は、その内部で最上部から縦方向に仕切り２７で左右２槽に分割されており、仕切り２７の下部でその一部が開口していて左右２槽の利用側冷媒３０が連通している。さらに、冷媒貯留タンク２０の上部は大気に開放されており、冷媒貯留タンク２０に接続されているすべての接続配管は、冷媒貯留タンク２０内の利用側冷媒３０の喫水面下に開口している。
【０１７７】
さらの本実施の形態では、利用側冷媒が直接循環するように接続された加熱専用の熱源装置ｅ’’を備えている。この熱源装置ｅ’’は、例えば第３の冷媒搬送装置２８、加熱ボイラ２９、制御装置４２ｃを有する。
利用側冷媒サイクル中、熱交換ユニットｄから接続配管ｊ，ｋの分岐に至る接続配管ｉには、第１の開閉弁１０１が設置されており、第１の開閉弁１０１と接続配管ｊ，ｋの分岐までの間で接続配管ｉが分岐して第２の開閉弁１０２の一端が接続されている。一方、熱交換ユニットｄから接続配管ｊ’，ｋ’の分岐に至る接続配管ｉ’には、第３の開閉弁１０３が設置されており、第３の開閉弁１０３と接続配管ｊ’，ｋ’の分岐までの間で接続配管ｉ’が分岐して第４の開閉弁１０４の一端が接続されている。第２の開閉弁１０２の他端は、第４の冷媒搬送装置１０５の冷媒出口側と接続され、第４の開閉弁１０４の他端は、熱源装置ｅ’’の冷媒入口側と接続配管ｏで接続されている。また、第４の冷媒搬送装置１０５の冷媒入口側は熱源装置ｅ’’の冷媒出口側と接続配管ｏ’で接続されている。さらに、熱源装置ｅ’’の中には、灯油、ガス等を燃焼させて得られる熱を利用した加熱ボイラ２９と、第３の冷媒搬送装置２８が収められており、接続配管ｏ、第３の冷媒搬送装置２８、加熱ボイラ２９、接続配管ｏ’の順に接続されている。制御装置４２ｃは加熱ボイラ２９、第３の冷媒搬送装置２８を制御している。
また、熱源装置ｅ’’は加熱専用であり、これ１台だけで必要な暖房能力が発揮される容量に設定されている。
【０１７８】
このような構成の場合、開閉弁１０１〜１０４は、利用側冷媒サイクルの冷媒流路を切換える切換手段を構成しており、暖房運転時に加熱専用の熱源装置ｅ’’に利用側冷媒を循環させるものである。
また、ｗは切換えユニットであり、開閉弁１０１〜１０４を１つのユニットにまとめたものである。
【０１７９】
つぎに、動作について説明する。
冷房運転時は、第１、第２の熱源側冷媒サイクルを運転し、熱源装置ｅ’’は停止する。冷房運転時は第１、第２の熱源側冷媒サイクルとも図中実線の冷媒サイクルとなる。冷房運転時の第１、第２の熱源側冷媒サイクルの動作は実施の形態１と同様であるので割愛する。
一方、利用側冷媒サイクルでは、冷房運転時には、第１の開閉弁１０１および第３の開閉弁１０３を開け、第２の開閉弁１０２および第４の開閉弁１０４を閉じる。冷媒貯留タンク２０の左側の槽の底部から流出した比較的低温の利用側冷媒３０は、第１の冷媒搬送装置２１によって接続配管ｉおよびｊ，ｋを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を冷房すると同時に自らは加熱されて、接続配管ｊ’，ｋ’および接続配管ｉ’を通って冷媒貯留タンク２０の右側の槽に戻ってくる。このとき、接続配管ｉの途中では、第２の開閉弁１０２が、また、接続配管ｉ’の途中では第４の開閉弁１０４が閉じられているので、熱源装置ｅ’’側には利用側冷媒は流れ込まない。
【０１８０】
また、一方、冷媒貯留タンク２０の右側の槽の底部から流出した比較的高温の利用側冷媒３０は、第２の冷媒搬送装置２５によって第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに分岐して送り込まれる。第２補助熱交換器１９ａおよび第４補助熱交換器１９ｂに送り込まれた利用側冷媒３０は、第１補助熱交換器１６ａおよび第３補助熱交換器１６ｂを通して、第１および第２の熱源側冷媒サイクルによって外気へ放熱すると同時に自らは冷却され、合流した後冷媒貯留タンク２０の左側の槽に戻る。
【０１８１】
暖房運転時は、第１、第２の熱源側冷媒サイクルを停止し、熱源装置ｅ’’のみ運転する。暖房運転時には、利用側冷媒サイクル中、第１の開閉弁１０１および第３の開閉弁１０３を閉じ、第２の開閉弁１０２および第４の開閉弁１０４を開ける。第３の冷媒搬送装置２８によって送り出された冷媒は、灯油、ガス等を燃焼して得られる熱を加熱ボイラ２９で奪うと同時に自らは加熱されて、第４の冷媒搬送装置１０５によって更に昇圧されて、第２の開閉弁１０２を通って、接続配管ｉに流入する。接続配管ｉに流入した利用側冷媒は、接続配管ｊ，ｋを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を暖房すると同時に自らは冷却されて、接続配管ｊ’，ｋ’を通って接続配管ｉ’へ流入する。ここで、利用側冷媒は第４の開閉弁１０４、および接続配管ｏを経由して熱源装置ｅ’’内の第３の冷媒搬送装置２８の入口側に戻る。
【０１８２】
室内ユニットｇおよびｈで暖房の要求があると、熱交換ユニットｄ内の制御装置４１に暖房要求の信号が室内ユニットから送られると共に、利用側冷媒流量制御弁２３ａ，２３ｂが開けられる。更に、この暖房要求信号は熱源装置ｅ’’内の制御装置４２ｃに送られて、熱源装置ｅ’’がその信号に従って運転を開始する。熱源装置ｅ’’は、汎用の灯油ボイラ、ガスボイラなどの熱源装置であり、循環する利用側冷媒を直接的に加熱する。そして、接続配管ｏ’へ送り出す冷媒温度があらかじめ設定されている温度になるように、制御装置４２ｃによって油またはガス等の燃焼量を制御している。暖房運転中は熱交換ユニットｄに利用側冷媒が循環することなく、また、利用側冷媒温度を制御する必要もなく、従って、新たに温度センサを追加する必要もない。室内で暖房の要求が全てなくなると、その信号が室内ユニットから熱交換ユニットｄへ送られ、熱交換ユニットｄの制御装置４１からの指令で熱源装置ｅ’’が停止すると共に、利用側冷媒流量制御弁２３ａ，２３ｂが閉じられる。
【０１８３】
以上のように、本実施の形態によれば、利用側冷媒サイクルの一部を分岐して、冷媒貯留タンク２０と並列に加熱専用の熱源装置ｅ’’を接続したので、特に、冬期の外気温度が氷点下になる地方において、第１、第２の冷媒サイクルであるヒートポンプでは暖房能力不足となる場合でも、暖房能力を確保しやすい。また、熱源装置ｅ’’内に設置された加熱ボイラ２９で利用側冷媒を直接加熱するので、熱源側冷媒サイクルと利用側冷媒サイクルを分離して熱交換器で熱交換する形態よりも効率的で省エネルギとなり、消費電力量および灯油やガス等の燃料消費量が削減され、ランニングコストを低くすることができる。
【０１８４】
なお、本実施の形態では、第１〜第４の開閉弁１０１〜１０４は切換えユニットｗ内に設置されているので、全体のシステムを構成する際に現地工事などを簡単化でき施工性が向上し、設置後の美観もよい。また、第４の冷媒搬送装置１０５も切換えユニットｗ内に設置すれば、さらに施工性が向上し、美観がよくなることは言うまでもない。
【０１８５】
本実施の形態では、熱源装置ｅ’’として、加熱ボイラ２９と第３の冷媒搬送装置２８とを一体のユニット内に装備した汎用の灯油ボイラなどを流用することを前提としている。第３の冷媒搬送装置２８は、一般に、揚程の比較的小さい小型のポンプであり、これだけでは利用側熱交換器２２ａおよび２２ｂに暖房に必要十分な流量の利用側冷媒を搬送できないため、第４の冷媒搬送装置１０５を第３の冷媒搬送装置に直列に接続して、第３の冷媒搬送装置２８の揚程不足を補っている。第４の冷媒搬送装置１０５は、熱源装置ｅ’’の冷媒出口側に設置しても、入口側に設置してもよい。また、第３の冷媒搬送装置２８が利用側熱交換器２２ａ，２２ｂで暖房に必要十分な流量の利用側冷媒を搬送できる揚程のものであれば、第４の冷媒搬送装置１０５は必要ないことは言うまでもない。
【０１８６】
実施の形態１２．
図２６は実施の形態１２による冷凍空調装置として例えば冷暖房装置を示す構成図である。実施の形態１１では、第１〜第４の開閉弁１０１〜１０４を熱交換ユニットｄの外部に設置したが、図２６に示すように、これらを熱交換ユニットｄの内部に設置することもできる。図２６において、熱交換ユニットｄ内部の接続配管ｓの途中で、第１の冷媒搬送装置２１に入口に至るまでの間に第１の開閉弁１０１を設置し、第１の開閉弁１０１と第１の冷媒搬送装置２１との間の接続配管ｓに分岐を設け、この分岐部と加熱ボイラ２９および第３の冷媒搬送装置２８を内蔵した熱源装置ｅ’’の冷媒出口側とを接続配管ｏ’で接続する。また、接続配管ｏ’の熱交換ユニットｄ内部に第２の開閉弁１０２を設置する。また、接続配管ｉ’に第３の開閉弁１０３を設置し、第３の開閉弁１０３と接続配管ｊ’，ｋ’の分岐（合流）部との間と、熱源装置ｅ’’の冷媒入口側とを接続配管ｏで接続する。そして、接続配管ｏに第４の開閉弁１０４を設置する。これら、第３、第４の開閉弁１０３、１０４は、熱交換ユニットｄの内部に設置している。
【０１８７】
次に動作について説明する。
冷房運転時は、第１、第２の熱源側冷媒サイクルを運転し、熱源装置ｅ’’は停止する。冷房運転時は第１、第２の熱源側冷媒サイクルとも図中実線の冷媒サイクルとなる。冷房運転時の第１、第２の熱源側冷媒サイクルの動作は実施の形態１と同様であるので割愛する。
一方、利用側冷媒サイクルでは、冷房運転時には、第１の開閉弁１０１および第３の開閉弁１０３を開け、第２の開閉弁１０２および第４の開閉弁１０４を閉じる。冷媒貯留タンク２０の左側の槽の底部から流出した比較的低温の利用側冷媒３０は、第１の冷媒搬送装置２１によって接続配管ｉおよびｊ，ｋを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を冷房すると同時に自らは加熱されて、接続配管ｊ’，ｋ’および接続配管ｉ’を通って冷媒貯留タンク２０の右側の槽に戻ってくる。このとき、接続配管ｓの途中では第２の開閉弁１０２が、また、接続配管ｉ’の途中では第４の開閉弁１０４が閉じられているので、熱源装置ｅ’’側には利用側冷媒は流れ込まない。
【０１８８】
暖房運転時は、第１、第２の熱源側冷媒サイクルを停止し、熱源装置ｅ’’のみ運転する。暖房運転時には、利用側冷媒サイクル中、第１の開閉弁１０１および第３の開閉弁１０３を閉じ、第２の開閉弁１０２および第４の開閉弁１０４を開ける。第３の冷媒搬送装置２８によって送り出された利用側冷媒は、灯油、ガス等を燃焼して得られる熱を加熱ボイラ２９で奪うと同時に自らは加熱されて、接続配管ｏ’、第２の開閉弁１０２を通って、接続配管ｓに流入する。接続配管ｓに流入した利用側冷媒は、第１の冷媒搬送装置２１によってさらに昇圧されて、接続配管ｉおよび接続配管ｊ，ｋを通って利用側熱交換器２２ａ，２２ｂへ送られる。そして、室内空気を暖房すると同時に自らは冷却されて、接続配管ｊ’，ｋ’および接続配管ｉ’へ流入する。ここで、利用側冷媒は第４の開閉弁１０４、および接続配管ｏを経由して熱源装置ｅ’’内の第３の冷媒搬送装置２８の入口側に戻ってくる。
【０１８９】
このように、加熱専用の熱源装置ｅ’’によって暖房運転を行うので、外気温度が低くなる場所で使用しても十分な暖房能力を得ることができ、室内の快適性を維持できる。
また、第１〜第４の開閉弁１０１〜１０４を熱交換ユニットｄの内部に収納したので、実施の形態１１のような新たな切換えユニットｗが必要なく、施工性が向上すると共に、美観を損なうことがない。また、熱源装置ｅ’’内に収納されている第３の冷媒搬送装置２８の揚程不足を補うため、新たな冷媒搬送装置を設置することなく、熱交換ユニットｄ内部に設置されている第１の冷媒搬送装置２１を利用して揚程不足を補うことができるので、新たに冷媒搬送装置１０５を必要とする実施の形態１１よりも安価な冷凍空調装置を提供できる。
【０１９０】
実施の形態１３．
実施の形態１１および実施の形態１２における冷凍空調装置では、第１の利用側冷媒サイクルは、１系統で構成して冷房および暖房を切換えて室内を空調するようにしていたが、図２７に示すように、冷房を行う冷却運転用の利用側冷媒サイクルと暖房を行う加熱運転用の利用側冷媒サイクルを設け、それぞれ個別に運転できるようにしてもよい。
【０１９１】
図２７は本実施の形態による冷凍空調装置として例えば冷暖房装置を示す構成図である。図において、室内ユニットｇ，ｈ内部には、それぞれ冷却用熱交換器２２ａ，２２ｂと加熱用熱交換器２２ｃ，２２ｄが収納されており、これらは室内送風機２４ａ，２４ｂによって送り込まれる室内空気の流れに対して、上流側に冷却用熱交換器２２ａ，２２ｂが、下流側に加熱用熱交換器２２ｃ，２２ｄが設置されている。冷却用熱交換器２２ａ，２２ｂは、実施の形態１１または１２と同様、利用側冷媒流量制御弁２３ａ，２３ｂおよび接続配管ｊ，ｋを介して接続配管ｉと、接続配管ｊ’，ｋ’を介して接続配管ｉ’とによって、熱交換ユニットｄに接続されて冷却時の利用側冷媒サイクルを構成している。一方、加熱用熱交換器２２ｃ，２２ｄは、利用側冷媒流量制御弁２３ｃ，２３ｄおよび接続配管ｘ，ｚを介して接続配管ｏ’と接続され、接続配管ｘ’，ｚ’を介して接続配管ｏと接続されている。接続配管ｏ，ｏ’は、加熱専用の熱源装置ｅ’’に接続する配管であり、加熱専用時の利用側冷媒サイクルを構成している。
【０１９２】
次に動作について説明する。
冷房運転時は、第１、第２の熱源側冷媒サイクルを運転し、熱源装置ｅ’’は停止する。冷房運転時は第１、第２の熱源側冷媒サイクルとも図中実線の冷媒サイクルとなる。冷房運転時の第１、第２の熱源側冷媒サイクルの動作は実施の形態１と同様であるので割愛する。
一方、冷却時の利用側冷媒サイクルでは、冷媒貯留タンク２０の左側の槽の底部から流出した比較的低温の利用側冷媒３０は、接続配管ｓを通って第１の冷媒搬送装置２１によって接続配管ｉおよびｊ，ｋ、利用側冷媒流量制御弁２３ａ，２３ｂを通って利用側熱交換器２２ａ，２２ｂへ送られ、室内空気を冷房すると同時に自らは加熱されて、接続配管ｊ’，ｋ’および接続配管ｉ’を通って冷媒貯留タンク２０の右側の槽に戻ってくる。このとき、熱源装置ｅ’’は停止しているので、加熱専用の利用側冷媒サイクルは機能せず、加熱用熱交換器２２ｃ，２２ｄは空調には何も寄与しない。
【０１９３】
暖房運転時は、第１、第２の熱源側冷媒サイクルを停止し、熱源装置ｅ’’のみ運転する。暖房運転時には、冷却用の利用側冷媒サイクルは機能せず、冷却用熱交換器２２ａ，２２ｂは空調には何も寄与しない。
一方、加熱専用の利用側冷媒サイクルでは、第３の冷媒搬送装置２８によって送り出された利用側冷媒は、灯油、ガス等を燃焼して得られる熱を加熱ボイラ２９で奪うと同時に自らは加熱されて、接続配管ｏ’に流出する。接続配管ｏ’には、第４の冷媒搬送装置１０５が設置されており、これによって加熱専用の利用側冷媒はさらに昇圧されて、接続配管ｘ，ｚ、利用側冷媒流量制御弁２３ｃ，２３ｄを通って暖房用熱交換器２２ｃ，２２ｄへ送られ、室内空気を暖房すると同時に自らは冷却されて、接続配管ｘ’，ｚ’および接続配管ｏを経由して熱源装置ｅ’’内の第３の冷媒搬送装置２８の入口側に戻ってくる。
【０１９４】
室内ユニットｇ，ｈで冷房の要求があると、室内ユニットｇ，ｈ内の加熱用熱交換器２２ｃ，２２ｄに接続された利用側冷媒流量制御弁２３ｃ，２３ｄを閉じると共に、冷却用熱交換器２２ａ，２２ｂに接続された利用側冷媒流量制御弁２３ａ，２３ｂを開ける。同時に、熱交換ユニットｄ内の制御装置４１に冷房要求の信号が室内ユニットから送られ、第１，第２の室外ユニットｅ，ｅ’がその信号に従って運転を開始する。第１，第２の室外ユニットｅ，ｅ’の運転容量は、第２，第４補助熱交換器１９ａ，１９ｂの下流側合流後の接続配管ｒに設置された第１の温度センサ３１の検出温度があらかじめ設定されている目標温度に近づくように制御される。室内で冷房の要求が全てなくなると、その信号が室内ユニットから熱交換ユニットｄへ送られ、熱交換ユニットｄの制御装置４１からの指令で第１，第２の室外ユニットｅ，ｅ’が停止すると共に、利用側冷媒流量制御弁２３ａ，２３ｂが閉じられる。
【０１９５】
室内ユニットｇ，ｈで暖房の要求があると、室内ユニットｇ，ｈ内の加熱用熱交換器２２ｃ，２２ｄに接続された利用側冷媒流量制御弁２３ｃ，２３ｄを開けると共に、冷却用熱交換器２２ａ，２２ｂに接続された利用側冷媒流量制御弁２３ａ，２３ｂを閉じる。同時に、熱交換ユニットｄ内の制御装置４１に暖房要求の信号が室内ユニットから送られ、更に、この暖房要求信号は熱源装置ｅ’’内の制御装置４２ｃに送られて、熱源装置ｅ’’がその信号に従って運転を開始する。熱源装置ｅ’’は、汎用の灯油ボイラ、ガスボイラ等の加熱装置であるので、接続配管ｏ’へ送り出す冷媒温度があらかじめ設定されている温度になるように、灯油またはガス等の燃焼量を制御する。従って、暖房運転中は熱交換ユニットｄでは、特に、利用側冷媒温度を制御する必要がなく、新たに温度センサを追加する必要もない。室内で暖房の要求が全てなくなると、その信号が室内ユニットから熱交換ユニットｄへ送られ、熱交換ユニットｄの制御装置４１からの指令で熱源装置ｅ’’が停止すると共に、利用側冷媒流量制御弁２３ｃ，２３ｄが閉じられる。
このように構成したことにより、加熱能力を十分に確保して温熱利用に適した温度に維持でき、かつ加熱専用の冷媒サイクルと冷却専用の冷媒サイクルをそれぞれ独立して制御でき、利用状況に適した運転を行うことができる安価な冷凍空調装置が得られる
【０１９６】
また、室内ユニットｇ，ｈで除湿の要求があると、室内ユニットｇ，ｈ内の加熱用熱交換器２２ｃ，２２ｄに接続された利用側冷媒流量制御弁２３ｃ，２３ｄを開けると共に、冷却用熱交換器２２ａ，２２ｂに接続された利用側冷媒流量制御弁２３ａ，２３ｂも開ける。同時に、熱交換ユニットｄ内の制御装置４１に暖房要求の信号が室内ユニットｇ，ｈから送られ、更に、この暖房要求信号は第１，第２の室外ユニットｅ，ｅ’と熱源装置ｅ’’に送られて、これらがその信号に従って運転を開始する。
室内ユニットｇ，ｈ内の送風機２４ａ，２４ｂで送り込まれた室内空気は、まず、冷却用熱交換器２２ａ，２２ｂに流れ込み、ここで、冷却用の利用側冷媒サイクル内の冷媒と熱交換して冷却されると共に除湿される。次に、この冷却、除湿された空気は、加熱用熱交換器２２ｃ，２２ｄに流れ込み、加熱専用の利用側冷媒サイクル内の冷媒と熱交換して加熱され、元々、室内ユニットが吸い込んだ室内空気温度とほぼ同一の温度に調節されて室内へ吹出される。室内で除湿の要求が全てなくなると、その信号が室内ユニットから熱交換ユニットｄへ送られ、熱交換ユニットｄの制御装置４１からの指令で第１，第２の室外ユニットｅ，ｅ’、および加熱専用の熱源装置ｅ’’が全て停止すると共に、利用側冷媒流量制御弁２３ａ〜２３ｄも閉じられる。
【０１９７】
以上のように、本実施の形態では、室内ユニット内に冷却用の熱交換器と加熱用の熱交換器とを設け、これらを送風機によって送り込まれる室内空気の流れに対して冷却用熱交換器、加熱用熱交換器の順に設置した。このため、除湿運転時に冷却用熱交換器２２ａ，２２ｂによって冷却、除湿された室内空気を加熱用熱交換器２２ｃ，２２ｄで再度加熱し、元々の室内空気温度とほぼ同一の温度に調節して室内に吹出すことができる。従来では冷却、除湿された空気がそのまま室内に吹き出されており、本実施の形態による構成では居住者に除湿運転時の冷風感を感じさせることなく快適な除湿空間を提供することができる。
【０１９８】
なお、冷却用熱交換器２２ａ，２２ｂと加熱用熱交換器２２ｃ、２２ｄとは送風機２４ａ，２４ｂによって送り込まれる室内空気の流れに対して冷却用熱交換器２２ａ，２２ｂ、加熱用熱交換器２２ｃ，２２ｄの順に直列に設置したが、これらを室内空気の流れに対して並列に設置してもよい。逆に、室内空気の流れに対して加熱用熱交換器２２ｃ，２２ｄ、冷却用熱交換器２２ａ，２２ｂの順に直列に設置しないほうがよい。このように設置すると、除湿するためには一度加熱された空気を更に露点以下にまで下げなければならないので、加熱分以上の冷却能力が必要となる上にエネルギの無駄になり、さらに冷風感が解消されない。
【０１９９】
また、冷却用の冷媒サイクルと暖房専用の冷媒サイクルとが独立して構成されているため、一方の室内ユニットでは冷房を行い、他方の室内ユニットでは暖房を行うという使用方法も可能である。即ち、利用側熱交換器の冷房／暖房を個別に制御でき、実際には利用側冷媒流量制御弁２３ａ〜２３ｄを使用要求に応じて行えば、熱交換器２２ａ〜２２ｄの運転／停止を任意に制御できる。
【０２００】
実施の形態１４．
実施の形態８では、冷媒貯留タンク２０内に設けた補助熱交換器１６ａ，１６ｂの小型化に対して、例えば水である利用側冷媒の伝熱面積を大きくする例を示したが、本実施の形態では、利用側冷媒の熱伝達率を向上させる構成について説明する。
【０２０１】
図２８は本実施の形態による冷凍空調装置として、例えば室内の冷暖房を行う冷暖房装置を示す構成図である。図において、冷媒貯留タンク２０内に空気管１１２を設置し、この空気管１１２内に空気搬送装置１１１より空気を送り込み、冷媒貯留タンク２０内に設けた補助熱交換器１６ａ，１６ｂの下方から空気管１１２に開けた小孔より空気を吹き出す。即ち、空気搬送装置１１と空気管１１２は、冷媒貯留タンク２０内の補助熱交換器１６ａ、１６ｂの周辺に気泡を吹き込む気泡吹き込み手段を構成している。補助熱交換器１６ａ、１６ｂの周辺に気泡を吹き込むと、冷媒貯留タンク２０内に貯留された利用側冷媒が気泡によって撹拌され、利用側冷媒の熱伝達率が向上する。このため、補助熱交換器１６ａ、１６ｂを小型化したり、受電容量を低減することができる。
なお、空気調和・衛生工学学術論文集７（’８７．１０．６−１０．８東京）氷蓄熱システムに関する研究の文献によれば、０．３［ｍ３／ｈｍ２］程度の流量の気泡を吹き出せば自然対流の約１．５倍の利用側冷媒の熱伝達率が得られることがわかっている。このため、これを目安に空気流量を設定すれば、効率のよい冷凍空調装置が得られる。
【０２０２】
本実施の形態における空気搬送装置１１１は、冷媒貯留タンク２０の液面と冷媒貯留タンク２０内の空気管１１２の最下部との距離で決まる液ヘッドに勝る静圧が出るブロワなどの送風機や空気ポンプである。また、１１３は、冷媒貯留タンク２０内に空気管１１２よりも下方に設置された仕切り板であり、利用側冷媒搬送装置２１が冷媒貯留タンク２０内に吹き込まれた気泡を吸込むことがないように配設されている。すなわち、仕切り板１１３よりも上側は利用側冷媒の気泡の存在する部分であり、仕切り板１１３よりも下側は気泡の存在しない部分であり、利用側冷媒搬送装置２１への冷媒流出口を、気泡の存在しない部分に設けている。
【０２０３】
この仕切り板１１３は、図２８では空気管１１２と分離させて設置した例を示したが、図２９のように空気管１１２と一体化してもよい。このように構成することにより、空気管１１２と仕切り板１１３とをコンパクトにかつ安価に製作することができる。
また、空気搬送装置１１１は、外気を直接吸込んで冷媒貯留タンク２０内に気泡として空気を吹き込んでもよいが、熱のロスをより小さくするため、図２８に示すように、冷媒貯留タンク２０内上部のオーバーフロー口１１４で外気に通じている空間から吸い込むようにした方がよい。
また、空気搬送装置１１３からの気泡吹き込み口は冷媒貯留タンク２０の底に設けることに限定されるものではなく、少なくとも補助熱交換器１６ａ、１６ｂの周辺に気泡を吹き込むように構成すれば、熱交換器１６ａの周辺での撹拌作用によって熱伝達率を向上することができる。また、例えば冷媒貯留タンク２０の側面側から気泡を吹き込む構成としてもよい。
また、気泡吹き込み手段は、空気搬送装置１１１で空気を吹き込む構成ではなく、電気分解によって冷媒貯留タンク２０内に気泡を発生させても、同様の効果を奏する。
【０２０４】
さらに、第３の熱源側冷媒サイクルｅ’’である加熱ボイラ２９を使用する場合は、図２８に示すように、第６の補助熱交換器１９ｃを冷媒貯留タンク２０への利用側冷媒流入口側に設置し、加熱ボイラ２９の熱源側冷媒が流れる第５の補助熱交換器１６ｃと熱交換させる。
【０２０５】
また、第３の熱源側冷媒サイクルｅ’’を使用する場合、図３０のように構成しても良い。図では、第６の補助熱交換器１９ｃのそれぞれの端を冷媒貯留タンク２０の高さが異なる位置である下部と上部を冷媒配管によって接続する。そして第６の補助熱交換器１９ｃを流れる利用側冷媒と、第３の熱源側冷媒サイクルｅ’’の第５の補助熱交換器１６ｃを循環する冷媒とを熱交換させる。
第６の補助熱交換器１９ｃで加熱された利用側冷媒は、密度が小さくなるので補助熱交換器１９ｃ内を上昇し、冷媒貯留タンク２０の上部に流入する。一方、冷媒貯留タンク２０の下部からは未加熱の密度の大きい利用側冷媒が第６の補助熱交換器１９ｃに下部から流入して循環し、冷媒貯留タンク２０内に温熱を蓄える。利用側冷媒貯留タンク２０内の利用側冷媒は、利用側冷媒搬送装置２１により利用側熱交換器２２ａ，２２ｂに送られ、室内を暖房する。
【０２０６】
図３０のように構成すると、利用側熱交換器２２ａ，２２ｂで暖房する場合、第６の補助熱交換器１９ｃが利用側冷媒サイクルとは別系統となり、利用側熱交換器２２ａ、２２ｂの冷媒循環流量が補助熱交換器１９ｃにより低下することがなく、安定して利用側冷媒サイクルの冷媒を循環させることができる。しかも、第６の補助熱交換器１９ｃに利用側冷媒を循環させる駆動力は利用側冷媒の温度差から生じる密度差であり冷媒搬送装置が必要ないため、システムの効率を向上することができる。なお、第６の補助熱交換器１９ｃと冷媒貯留タンク２０とを接続する冷媒配管は太いほうが圧力損失が小さくて効率がよいが、あまり太いと利用側冷媒の流速が遅くなり、第６の補助熱交換器１９ｃの熱交換効率が悪くなる。
【０２０７】
なお、実施の形態１〜実施の形態１４において、利用側冷媒は、水、若しくはエチレングリコール、プロピレングリコールおよびＤ−ソルビトールなどの溶媒の少なくとも１つまたは複数を重量比で数十％以下含んだ水溶液としているが、水の場合には、実施の形態１０で述べたように設置工事のときに水道圧で利用側冷媒を充填できるなど、扱いやすい。また、流量を多くできるので、熱伝達能力を大きくできる。また、利用側の冷媒搬送装置の揚程が大きくなり、冷媒搬送装置の能力を増やさなくても遠くまで水を循環させることができるので、高層住宅や敷地面積の大きな建物にも適用できるようになる。
【０２０８】
また、室内機の台数は、上記実施の形態では２台のものについて説明したがこれに限るものではなく、１台または３台以上でもよい。
【０２０９】
また、上記実施の形態１〜実施の形態１４では冷凍空調装置の一例として室内の冷暖房を行なう冷暖房装置に適用したものを説明したが、これに限るものではなく、例えば熱源側冷媒サイクルで得た冷熱または温熱を利用側冷媒サイクルで給湯や床暖房や浴室等の加熱乾燥などの加熱に利用したり、産業用や家庭用の冷凍冷蔵庫などの冷却に利用したり、さまざまな用途に利用できる。なお、給湯に利用する場合で利用側冷媒が水である場合には、冷媒貯留タンク２０に貯留した冷媒をそのまま利用すればよいので、利用側熱交換器は必要ない。
また、上記実施の形態１〜実施の形態１４では、冷媒貯留タンクに利用側冷媒を貯留するような構成としたが、冷媒貯留タンクを熱源側冷媒サイクルに連接して熱源側冷媒を貯留する構成としてもよい。このとき利用側冷媒サイクルでは冷媒貯留タンクに蓄熱した温熱または冷熱を補助熱交換器によって取り出すように構成すればよい。熱源側冷媒で蓄熱することにより、エネルギー効率のよい冷媒を利用して冷熱または温熱を蓄熱でき、冷媒貯留タンクを小型化して装置構成全体の小型化を図ることができる。
【０２１０】
【発明の効果】
本発明は、以上説明したように構成されているので、以下に記載するような効果を奏する。
【０２１１】
本発明の請求項１によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルを除霜運転するときの前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持するように前記利用側冷媒の量を充填したことにより、加熱運転時の熱源側冷媒サイクルの除霜運転に対し、利用側冷媒の温度を安定させることができ、かつ地球環境保全上や取扱上で問題のある冷媒の使用量を低減できる冷凍空調装置が得られる。
【０２１２】
また、本発明の請求項２によれば、熱源側冷媒サイクルの除霜運転によって補助熱交換器で利用側冷媒サイクルから奪われる熱量をＱｄ、利用側冷媒の量をＷ、前記利用側冷媒の比熱をＣｐとし、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルで除霜運転されるとき、Ｑｄ／（Ｗ・Ｃｐ）で表される前記利用側冷媒の温度低下が所定温度以下になるように前記利用側冷媒の量Ｗを充填して、前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持することにより、加熱運転時の熱源側冷媒サイクルの除霜運転に対し、利用側冷媒の温度を安定させることができ、温熱利用に適した温度を維持でき、かつ地球環境保全上や取扱上で問題のある冷媒の使用量を低減できる冷凍空調装置が得られる。
【０２１３】
また、本発明の請求項３によれば、利用側冷媒サイクルに設けられ熱源側冷媒サイクルで得た温熱を蓄熱する蓄熱手段を備え、前記熱源側冷媒サイクルの除霜運転によって前記補助熱交換器で前記利用側冷媒サイクルから奪われる熱量をＱｄ、前記除霜運転によって前記蓄熱手段から放熱する熱量をＱｔ、前記利用側冷媒の量をＷ、前記利用側冷媒の比熱をＣｐとし、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルで除霜運転されるとき、（Ｑｄ−Ｑｔ）／（Ｗ・Ｃｐ）で表される前記利用側冷媒の温度低下が所定温度以下になるように前記利用側冷媒の量Ｗを充填すると共に前記蓄熱手段の蓄熱容量を設定して、前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持することにより、加熱運転時の熱源側冷媒サイクルの除霜運転に対し、利用側冷媒の温度を安定させることができ、温熱利用に適した温度を維持でき、かつ地球環境保全上や取扱上で問題のある冷媒の使用量を低減でき、冷媒の充填量を低減して小型化できる冷凍空調装置が得られる。
【０２１４】
また、本発明の請求項４によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記利用側冷媒サイクル内に前記利用側冷媒を貯留する冷媒貯留タンクを設け、前記冷媒貯留タンクの内容積を、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルを除霜運転するときの前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持するように、前記利用側冷媒の量または蓄熱材の量を蓄えられる内容積としたことにより、加熱運転時の熱源側冷媒サイクルの除霜運転に対し、利用側冷媒の温度低下を低減して利用側冷媒の温度を安定させることで、温熱利用に適した温度に維持でき、かつ地球環境保全上や取扱上で問題のある冷媒の使用量を低減できる冷凍空調装置が得られる。
【０２１５】
また、本発明の請求項５によれば、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環させて成る熱源側冷媒サイクルと、前記第１補助熱交換器と熱交換する第２補助熱交換器、冷媒貯留タンク、冷媒搬送装置、および利用側熱交換器を連接し利用側冷媒を循環させて成る利用側冷媒サイクルとを有し、前記圧縮機、前記流路切換弁、前記熱源側熱交換器、前記熱源側冷媒流量制御弁、前記第１補助熱交換器、前記第２補助熱交換器、前記冷媒貯留タンク、および前記冷媒搬送装置を一つのユニット内に収納したことにより、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持でき、かつ搬入および工事に手間がかかるのを防ぐことのできる冷凍空調装置が得られる。
【０２１６】
また、本発明の請求項６に係わる冷凍空調装置は、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環させて成る熱源側冷媒サイクルと、前記第１補助熱交換器と熱交換する第２補助熱交換器、冷媒貯留タンク、冷媒搬送装置、および利用側熱交換器を連接し利用側冷媒を循環させて成る利用側冷媒サイクルとを有し、前記圧縮機、前記流路切換弁、前記熱源側熱交換器、および前記熱源側冷媒流量制御弁を一つのユニット内に収納し、前記第１補助熱交換器、前記第２補助熱交換器、前記冷媒貯留タンク、および前記冷媒搬送装置を前記ユニットとは別の一つのユニット内に収納し、前記第１補助熱交換器の一端側と前記流路切換弁との間および前記第１補助熱交換器の他端側と前記熱源側冷媒流量制御弁との間をそれぞれ接続配管で接続したことにより、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持でき、かつ標準の室外ユニットを使用した安価な冷凍空調装置が得られる。
【０２１７】
また、本発明の請求項７によれば、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環して成る熱源側冷媒サイクルと、第１の冷媒搬送装置、前記第１補助熱交換器と熱交換する第２補助熱交換器、および前記冷媒貯留タンクを連接し利用側冷媒を循環して成る熱輸送サイクルと、第２の冷媒搬送装置、利用側熱交換器、および前記冷媒貯留タンクを連接し前記利用側冷媒を循環して成る利用側冷媒サイクルとを有し、前記熱輸送サイクルにおいて前記第２補助熱交換器で前記第１補助熱交換器と熱交換して得た温熱を前記冷媒貯留タンクに蓄え、前記利用側冷媒サイクルにおいて前記冷媒貯留タンクに蓄えた温熱を前記利用側熱交換器で加熱に利用することにより、温度制御が安定しやすくなり、温熱利用に適した温度に維持でき、かつ地球環境保全上や取扱上で問題のある冷媒の使用量を低減できる冷凍空調装置が得られる。
【０２１８】
また、本発明の請求項８によれば、冷媒貯留タンクの内部を左右に分割すると共に、喫水面よりも下側で前記分割された左右の利用側冷媒が連通可能な連通部を有する仕切りを備え、分割された左右の槽のそれぞれに２つの開口を設け、前記冷媒貯留タンクの一方の槽の２つの開口を、利用側熱交換器からの利用側冷媒の流入口と、第２補助熱交換器への前記利用側冷媒の流出口とし、前記冷媒貯留タンクの他方の槽の２つの開口を、前記第２補助熱交換器からの前記利用側冷媒の流入口と、前記利用側熱交換器への前記利用側冷媒の流出口としたことにより、熱源側冷媒サイクルを効率よく運転でき、冷媒貯留タンクに十分に蓄熱して快適な冷凍空調を実現できる冷凍空調装置が得られる。
【０２１９】
また、本発明の請求項９によれば、熱源側冷媒と利用側冷媒とを熱交換する補助熱交換器をプレート式熱交換器としたことにより、容量の小さい冷媒搬送装置を用いることができ、安価な冷凍空調装置が得られる。
【０２２０】
また、本発明の請求項１０によれば、冷却運転と加熱運転とで、熱源側冷媒サイクルと利用側冷媒サイクルの間の補助熱交換器における利用側冷媒の流れ方向を切換える切換手段を備え、前記補助熱交換器で熱交換する際の熱源側冷媒と利用側冷媒の流れ方向が、冷却運転時および加熱運転時で共に対向流となるように構成したことにより、冷却・加熱運転共に効率よく熱交換でき、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【０２２１】
また、本発明の請求項１１によれば、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および補助熱交換器を連接し熱源側冷媒を循環して成る熱源側冷媒サイクルと、利用側冷媒を貯留する冷媒貯留タンク、および冷媒搬送装置を連接し前記利用側冷媒を循環して成る利用側冷媒サイクルとを備え、前記補助熱交換器を前記冷媒貯留タンク内の利用側冷媒に浸漬して前記補助熱交換器で前記熱源側冷媒と前記利用側冷媒とを熱交換して前記冷媒貯留タンクに熱を蓄え、前記利用側冷媒サイクルにおいて前記冷媒貯留タンクに蓄えた熱を加熱に利用することにより、除霜運転時の利用側冷媒の温度を安定させることができ、さらに熱源側冷媒サイクルの設備を小型化でき、かつ比較的簡単な装置構成でシステム全体の信頼性を向上でき、地球環境保全上や取扱上で問題のある冷媒の使用量を低減できる冷凍空調装置が得られる。
【０２２２】
また、本発明の請求項１２によれば、補助熱交換器における利用側冷媒の伝熱面積を熱源側冷媒の伝熱面積よりも大きくしたことにより、熱源側冷媒と利用側冷媒との熱交換おける伝熱性能を向上して除霜運転時の利用側冷媒の温度を安定させることのできる冷凍空調装置が得られる。
【０２２３】
また、本発明の請求項１３によれば、冷媒貯留タンク内の補助熱交換器周辺に気泡を吹き込む気泡吹き込み手段を備えたことにより、熱源側冷媒と利用側冷媒との熱交換おける伝熱性能を向上して除霜運転時の利用側冷媒の温度を安定させることのできる冷凍空調装装置が得られる。
【０２２４】
また、本発明の請求項１４によれば、冷媒貯留タンクの外部に設けられ前記冷媒貯留タンクの高さが異なる位置を接続する利用側冷媒配管と、この利用側冷媒配管を流通する利用側冷媒を加熱する熱源装置を備えたことにより、比較的簡単な構成で利用側冷媒を加熱でき、かつこの加熱によって利用側冷媒サイクルの冷媒循環には影響を及ぼすことのなく、システムの効率を向上できる冷凍空調装置が得られる。
【０２２５】
また、本発明の請求項１５によれば、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、補助熱交換器、冷媒貯留タンク、および冷媒搬送装置を一つのユニット内に収納したことにより、除霜運転時の利用側冷媒の温度を安定させることで温熱利用に適した温度に維持でき、搬入および工事に手間がかかるのを防ぐことができる冷凍空調装置が得られる。
【０２２６】
また、本発明の請求項１６によれば、圧縮機、流路切換弁、熱源側熱交換器、および熱源側冷媒流量制御弁を一つのユニット内に収納すると共に、補助熱交換器、冷媒貯留タンク、および冷媒搬送装置を前記ユニットとは別の一つのユニット内に収納し、前記補助熱交換器の一端側と前記流路切換弁との間および前記補助熱交換器の他端側と前記熱源側冷媒流量制御弁との間をそれぞれ接続配管で接続したことにより、除霜運転時の利用側冷媒の温度を安定させることで温熱利用に適した温度に維持でき、かつ標準の室外ユニットを使用でき、安価な冷凍空調装置が得られる。
【０２２７】
また、本発明の請求項１７によれば、利用側冷媒を貯留する冷媒貯留タンク内に蓄熱材を設けたことにより、冷媒貯留タンクに十分に蓄熱でき、タンクを小型にできる冷凍空調装置が得られる。
【０２２８】
また、本発明の請求項１８によれば、冷媒貯留タンク内に配設され、その内部を左右に分割する仕切りを備えると共に、分割された一方の槽に設けた利用側冷媒が流入する開口と、他方の槽に設けた前記利用側冷媒が流出する開口を備え、前記仕切りは、前記冷媒貯留タンクの喫水面よりも下側で前記分割された左右の利用側冷媒が連通する連通部を有することにより、熱源側冷媒サイクルを効率よく運転でき、冷媒貯留タンクに十分に蓄熱して快適な空調を実現できる冷凍空調装置が得られる。
【０２２９】
また、本発明の請求項１９によれば、利用側冷媒が循環する部分に、前記利用側冷媒に混入した混入物を集めるフィルタを設けたことにより、利用側冷媒にごみやちりなどの混入物が循環するのを防ぐことができ、信頼性の高い冷凍空調装置が得られる。
【０２３０】
また、本発明の請求項２０によれば、フィルタを利用側冷媒を貯留する冷媒貯留タンク内に設けたことにより、フィルタを管理しやすく、利用側冷媒にごみやちりなどの混入物が循環するのを防ぐことができ、信頼性の高い冷凍空調装置が得られる。
【０２３１】
また、本発明の請求項２１によれば、熱源側冷媒サイクルを２系統以上の複数としたことにより、除霜運転時の利用側冷媒の温度を安定させることで温熱利用に適した温度に維持でき、かつ小型の標準的な熱源側冷媒サイクルを使用でき、安価な冷凍空調装置が得られる。
【０２３２】
また、本発明の請求項２２によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、その少なくとも１系統の熱源側冷媒サイクルを加熱専用の冷媒サイクルで構成したことにより、除霜運転時の利用側冷媒の温度を安定させることで温熱利用に適した温度に維持でき、かつ小型の標準的な熱源側冷媒サイクルを使用でき、地球環境保全上や取扱上で問題のある冷媒の使用量を低減できる安価な冷凍空調装置が得られる。
【０２３３】
また、本発明の請求項２３によれば、利用側冷媒サイクルに対して複数の熱源側冷媒サイクルを並列に接続したことにより、熱源側冷媒サイクルのそれぞれを独立に制御でき、かつ安価な冷凍空調装置が得られる。
【０２３４】
また、本発明の請求項２４によれば、利用側冷媒サイクルに対して複数の熱源側冷媒サイクルを直列に接続したことにより、小型の標準的な熱源側冷媒サイクルを使用でき、配管の接続を比較的単純にでき、かつ安価な冷凍空調装置が得られる。
【０２３５】
また、本発明の請求項２５によれば、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却／加熱併用の冷媒サイクルとを直列に接続したことにより、外気温度の低い場所で使用しても加熱能力を十分に確保でき、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【０２３６】
また、本発明の請求項２６によれば、利用側冷媒サイクルを循環する利用側冷媒の流れの向きに対して冷却／加熱併用の冷媒サイクルを上流側に接続し、加熱専用の冷媒サイクルを下流側に接続したことにより、熱源側冷媒サイクルを有効に利用でき、外気温度の低い場所で使用しても加熱能力を十分に確保でき、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【０２３７】
また、本発明の請求項２７によれば、利用側冷媒サイクルを循環する利用側冷媒の流れの向きに対して加熱専用の冷媒サイクルを上流側に接続し、冷却／加熱併用の冷媒サイクルを下流側に接続したことにより、外気温度の低い場所で使用しても加熱能力を十分に確保でき、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【０２３８】
また、本発明の請求項２８によれば、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却／加熱併用の冷媒サイクルとを並列に接続すると共に、冷却運転時には加熱専用の冷媒サイクルと熱交換する利用側補助熱交換器には利用側冷媒が流れないように、前記利用側冷媒サイクルの冷媒流路を切換える切換手段を備えたことにより、温熱利用に適した温度に維持でき、かつ加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルをそれぞれ独立して制御でき、利用状況に適した運転を行うことができる冷凍空調装置が得られる。
【０２３９】
また、本発明の請求項２９によれば、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却専用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却専用の冷媒サイクルとを直列に接続したことにより、外気温度の低い場所で使用しても加熱能力を十分に確保でき、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持でき、かつ安価な冷凍空調装置が得られる。
【０２４０】
また、本発明の請求項３０によれば、熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却専用の冷媒サイクルとをそれぞれ１系統以上設け、利用側冷媒サイクルに対して前記加熱専用の冷媒サイクルと前記冷却専用の冷媒サイクルとを並列に接続すると共に、加熱運転時には前記加熱専用の冷媒サイクルと熱交換する利用側補助熱交換器に利用側冷媒を循環させ、冷却運転時には冷却専用の冷媒サイクルと熱交換する利用側補助熱交換器に利用側冷媒を循環させるように、前記利用側冷媒サイクルの冷媒流路を切換える切換手段を備えたことにより、加熱能力を十分に確保して温熱利用に適した温度に維持でき、かつ加熱専用の冷媒サイクルと冷却専用の冷媒サイクルをそれぞれ独立して制御でき、利用状況に適した運転を行うことができる安価な冷凍空調装置が得られる。
【０２４１】
また、本発明の請求項３１によれば、利用側冷媒が循環する加熱専用の熱源装置と、加熱運転時に前記加熱専用の熱源装置に前記利用側冷媒を循環させるように前記利用側冷媒サイクルの冷媒流路を切換える切換手段とを備えたことにより、外気温度の低い場所で使用しても加熱能力を十分に確保でき、温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【０２４２】
また、本発明の請求項３２によれば、利用側冷媒サイクルに、熱源側冷媒サイクルにより熱を供給される冷却用の利用側熱交換器と、加熱専用の熱源装置により熱を供給される加熱用の利用側熱交換器とを設け、冷却運転時に前記熱源側冷媒サイクルと前記冷却用の利用側熱交換器を動作させ、加熱運転時に前記加熱専用の熱源装置と前記加熱用の利用側熱交換器を動作させるように構成したことにより、温熱利用に適した温度に維持でき、利用側熱交換器の冷却／加熱を個別に制御できる冷凍空調装置が得られる。
【０２４３】
また、本発明の請求項３３によれば、冷却用の利用側熱交換器は、空気の流れに対し、加熱用の利用側熱交換器の上流側に並べて配置し、除湿運転時に冷却用および加熱用の利用側熱交換器を動作させるように構成したことにより、快適な除湿を行うことができ、外気温度の低い場所で使用しても加熱能力を十分に確保して温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【０２４４】
また、本発明の請求項３４によれば、加熱専用の熱源装置を、利用側冷媒を直接的に加熱する加熱装置としたことにより、外気温度の低い場所で使用しても加熱能力を十分に確保して温熱利用に適した温度に維持でき、かつランニングコストを低減でき安価な冷凍空調装置が得られる。
【０２４５】
また、本発明の請求項３５によれば、利用側冷媒サイクルを構成する配管において、利用側熱交換器への送り側配管と前記利用側熱交換器からの戻り側配管とで、該配管の配管径、若しくは該配管の継ぎ手の径または形状を異なるように構成したことにより、配管接続工事などの際に接続間違いが起こるのを防ぐことができ、信頼性の高い冷凍空調装置が得られる。
【０２４６】
また、本発明の請求項３６によれば、利用側冷媒サイクル内に複数の利用側熱交換器を設け、それらの利用側熱交換器を全て互いに並列に接続したことにより、それぞれの熱交換器で独立して制御できる汎用的な冷凍空調装置が得られる。
【０２４７】
また、本発明の請求項３７によれば、利用側冷媒サイクル内に複数の利用側熱交換器を設け、それらの利用側熱交換器のうちの少なくとも一部を互いに直列に接続したことにより、エネルギを無駄なく利用できる冷凍空調装置が得られる。
【０２４８】
また、本発明の請求項３８によれば、利用側冷媒サイクルを循環する冷媒を、水、若しくはエチレングリコール、プロピレングリコール、およびＤ−ソルビトールのうちのいずれか１つまたは複数を重量比で数十％以下含む水溶液としたことにより、地球環境保全の点で問題なく、取扱いも容易でかつ安価な冷媒を使用し、地球環境保全や取扱の点で問題のある冷媒の使用量を最小限に抑えることができ、かつ安価な冷凍空調装置が得られる。
【０２４９】
また、本発明の請求項３９によれば、熱源側冷媒サイクルを蒸気圧縮式冷凍サイクルで構成し、前記熱源側冷媒サイクルを循環する冷媒を潜熱を利用するものとし、フロン系の単一冷媒、フロン系の擬似共沸混合冷媒、フロン系の非共沸冷媒、炭化水素系冷媒、およびアンモニア冷媒のうちのいずれか１つとしたことにより、熱源側にはエネルギー効率のよい冷媒を用い、全体として地球環境保全や取扱の点で問題のある冷媒の使用量を最小限に抑えることができ、かつ効率のよい冷凍空調装置が得られる。
【０２５０】
また、本発明の請求項４０によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルの容量を複数の段階に変化するように構成し、その容量の変化幅を容量が増加するにつれて大きくなるようにしたことにより、負荷の様々な大きさの変動に対して、ハンチングを抑えながら追従することができ、利用側冷媒の温度安定性を向上できる冷凍空調装置の制御方法が得られる。
【０２５１】
また、本発明の請求項４１によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、前記利用側冷媒サイクルで加熱運転中に前記熱源側冷媒サイクルのうち１系統以上が除霜運転している間に、少なくとも１系統の前記熱源側冷媒サイクルは加熱運転を継続するように制御することにより、除霜運転時に利用側冷媒の温度低下を小さくでき、温熱利用に適した温度に維持できる冷凍空調装置の制御方法が得られる。
【０２５２】
また、本発明の請求項４２によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、前記熱源側冷媒サイクルに加熱専用の冷媒サイクルと冷却／加熱併用の冷媒サイクルとをそれぞれ１系統以上設け、前記冷却／加熱併用の冷媒サイクルに蒸気圧縮式冷凍サイクルを用い、加熱運転中に前記冷却／加熱併用の冷媒サイクルのうちの１系統以上が除霜運転している間に、前記加熱専用の冷媒サイクルと前記冷却／加熱併用の冷媒サイクルのうちの少なくとも１系統の冷媒サイクルは加熱運転を継続するように制御することにより、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置の制御方法が得られる。
【０２５３】
また、本発明の請求項４３によれば、熱源側冷媒サイクルのうちの１系統以上が除霜運転している間に加熱運転を継続する熱源側冷媒サイクルは、その加熱能力を増加して加熱運転を継続するように制御することにより、除霜運転時に利用側冷媒の温度低下をさらに小さくして利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置の制御方法が得られる。
【０２５４】
また、本発明の請求項４４によれば、熱源側冷媒サイクルのうちの１系統以上が除霜運転している間に加熱運転を継続する熱源側冷媒サイクルを、加熱専用の冷媒サイクルとしたことにより、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置の制御方法が得られる。
【０２５５】
また、本発明の請求項４５によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルとして蒸気圧縮式冷凍サイクルを２系統以上用い、前記利用側冷媒サイクルで加熱運転中に前記熱源側冷媒サイクルのうち１系統以上が除霜運転開始条件を満たした場合、除霜運転を開始する前に熱源側冷媒サイクルの能力を増大させて加熱運転を継続し、その後に除霜運転を行うように制御することにより、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置の制御方法が得られる。
【０２５６】
また、本発明の請求項４６によれば、熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いると共に、前記熱源側冷媒サイクルを２系統以上の複数とし、前記複数系統の熱源側冷媒サイクルのそれぞれの容量を一つまたは複数の段階に変化するように構成し、かつ全体としての前記複数系統の熱源側冷媒サイクルの合計容量を複数の段階に変化するように構成し、その合計容量の変化幅を合計容量が増加するにつれて大きくなるようにしたことにより、負荷の様々な大きさの変動に対して、ハンチングを抑えながら追従することができ、利用側冷媒の温度安定性を向上できる冷凍空調装置の制御方法が得られる。
【０２５７】
また、本発明の請求項４７によれば、合計容量の段階を増加させる際に、複数系統の熱源側冷媒サイクルのうちの現行で運転している熱源側冷媒サイクルは運転状態のままで前記合計容量を増加させるものとし、前記合計容量の段階を減少させる際に、複数系統の熱源側冷媒サイクルのうちの現行で停止している熱源側冷媒サイクルは停止状態のままで前記合計容量を減少させるように制御することにより、システム全体の安定性を向上できる冷凍空調装置の制御方法が得られる。
【０２５８】
また、本発明の請求項４８によれば、圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および熱源側冷媒を貯留する冷媒貯留タンクを連接し前記熱源側冷媒を循環して成る熱源側冷媒サイクルと、補助熱交換器、および冷媒搬送装置を連接し利用側冷媒を循環して成る利用側冷媒サイクルとを備え、前記補助熱交換器を前記冷媒貯留タンク内の熱源側冷媒に浸漬して前記補助熱交換器で前記熱源側冷媒と前記利用側冷媒とを熱交換し、前記冷媒貯留タンクに蓄えた熱を前記利用側冷媒サイクルにおいて加熱に利用することにより、冷媒貯留タンクに効率よく蓄熱して熱源側冷媒サイクルの設備を小型化でき、かつ比較的簡単な装置構成でシステム全体の信頼性を向上でき、除霜運転時の利用側冷媒の温度を安定させて温熱利用に適した温度に維持できる冷凍空調装置が得られる。
【図面の簡単な説明】
【図１】本発明の実施の形態１による冷凍空調装置を示す構成図である。
【図２】実施の形態１に係わる利用側冷媒の濃度に対する特性を示すグラフであり、図２（ａ）は凍結温度、図２（ｂ）は動粘度、図２（ｃ）は熱伝達率を示す。
【図３】実施の形態１による冷凍空調装置を示す構成図である。
【図４】実施の形態１による冷凍空調装置を示す構成図である。
【図５】実施の形態１による冷凍空調装置を示す構成図である。
【図６】実施の形態１による冷凍空調装置を示す構成図である。
【図７】本発明の実施の形態２による冷凍空調装置を示す構成図である。
【図８】実施の形態２による冷凍空調装置の制御方法に係わり、圧縮器合計能力および圧縮機合計仮周波数に対するＣＯＰを示すグラフである。
【図９】実施の形態２による冷凍空調装置の制御方法に係わり、温度センサ３１の検出温度ＴＨ１に対する圧縮機運転台数増減値を示すグラフである。
【図１０】実施の形態２による冷凍空調装置の制御方法に係わる処理手順を示すフローチャートである。
【図１１】実施の形態２による冷凍空調装置の制御方法に係わる処理を示すブロック線図である。
【図１２】本発明の実施の形態３による冷凍空調装置を示す構成図である。
【図１３】本発明の実施の形態４による冷凍空調装置を示す構成図である。
【図１４】実施の形態４による冷凍空調装置を示す構成図である。
【図１５】本発明の実施の形態５による冷凍空調装置を示す構成図である。
【図１６】実施の形態５による冷凍空調装置の制御方法に係わり、温度センサ３１の検出温度ＴＨ１に対する熱源側冷媒サイクル運転／停止を示すグラフである。
【図１７】本発明の実施の形態６による冷凍空調装置を示す構成図である。
【図１８】本発明の実施の形態７による冷凍空調装置を示す構成図である。
【図１９】本発明の実施の形態８による冷凍空調装置を示す構成図である。
【図２０】実施の形態８に係わる冷媒貯留タンクの構成を示す説明図である。
【図２１】実施の形態８による冷凍空調装置を示す構成図である。
【図２２】本発明の実施の形態９による冷凍空調装置を示す構成図である。
【図２３】実施の形態９による冷凍空調装置を示す構成図である。
【図２４】本発明の実施の形態１０による冷凍空調装置を示す構成図である。
【図２５】本発明の実施の形態１１による冷凍空調装置を示す構成図である。
【図２６】本発明の実施の形態１２による冷凍空調装置を示す構成図である。
【図２７】本発明の実施の形態１３による冷凍空調装置を示す構成図である。
【図２８】本発明の実施の形態１４による冷凍空調装置を示す構成図である。
【図２９】実施の形態１４に係わる気泡吹き込み手段の構成を示す斜視図である。
【図３０】実施の形態１４による冷凍空調装置の別の構成を示す構成図である。
【図３１】従来の冷凍空調装置を示す構成図である。
【符号の説明】
１１ 圧縮機、１２ 流路切換弁、１３ 熱源側熱交換器、１４ 熱源側冷媒流量制御弁、１５ レシーバ、１６ 第１補助熱交換器、１７ 室外送風機、１８ 第２冷媒貯留タンク、１９ 第２補助熱交換器、２０ 冷媒貯留タンク、２１ 冷媒搬送装置、２２ａ，２２ｂ，２２ｃ，２２ｄ 利用側熱交換器、２３ａ，２３ｂ 利用側冷媒流量制御弁、２４ａ，２４ｂ 室内送風機、２５ 冷媒搬送装置、２６ フィルタ、２７，２７ａ，２７ｂ 仕切り、２９ 加熱装置、３１ 温度検出手段、３４ 外気温度検出手段、３５ 温度検出手段、３６ 温度検出手段、４１，４２ａ，４２ｂ 制御装置、５１，５２ 流路切換手段、６１蓄熱材、６２ 流路切換手段、６４ａ，６４ｂ 止め弁、６５ 接続口、１１１ 空気搬送装置、１１２ 空気管、１１３ 仕切り板、ｇ，ｈ 室内ユニット、ｅ，ｅ’，ｆ 室外ユニット、ｅ’’ 熱源装置、ｊ，ｋ，ｉ’，ｊ’，ｋ’接続配管。[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a refrigeration / air-conditioning apparatus that performs heating by exchanging heat between a heat source-side refrigerant cycle and a use-side refrigerant cycle, and for example, relates to a refrigeration / air-conditioning apparatus used for cooling and heating a house and a control method thereof. .
[0002]
[Prior art]
An example of a conventional refrigeration and air-conditioning apparatus described in Japanese Patent Application Laid-Open No. Sho 62-238954 will be described below.
In FIG. 31, 81 is a compressor, 82 is a four-way valve, 83 is a heat source side heat exchanger, 84 is a cooling decompression device, 85 is a heating decompression device, and 86 is a circuit provided with a cooling decompression device 84 during heating. , A check valve 87 for closing the circuit provided with the heating depressurizing device 85 during cooling, and a first auxiliary heat exchanger 88 for connecting these in a ring shape, and a heat source side refrigerant cycle. Has formed. Reference numeral 89 denotes a second auxiliary heat exchanger, which is integrally formed so as to exchange heat with the first auxiliary heat exchanger 88. Reference numeral 90 denotes a refrigerant storage tank for adjusting the amount of refrigerant during cooling and during heating. Reference numeral 91 has a reversible characteristic in which the outflow direction of the refrigerant is opposite during cooling and during heating. The second auxiliary heat exchanger 89, the refrigerant storage tank 90, and the refrigerant transfer device 91 are housed in the outdoor unit f together with the heat source side refrigerant cycle. Reference numerals 92a and 92b denote, for example, two use-side heat exchangers housed in two indoor units g and h, and connected to the outdoor unit f by connection pipes i, i ', j and j'. The second auxiliary heat exchanger 89, the refrigerant storage tank 90, the refrigerant conveying device 91, the use side heat exchangers 92a and 92b, and the connection pipes i, i ', j, j' are connected in a ring shape to form a use side refrigerant cycle. ing.
[0003]
Next, the operation will be described.
During the cooling operation, the refrigerant cycle is indicated by a solid line arrow in the drawing. In the heat source-side refrigerant cycle, the high-temperature and high-pressure gas from the compressor 81 passes through the four-way valve 82 and radiates heat in the heat-source-side heat exchanger 83 and condenses and liquefies. Further, the pressure is reduced by the cooling pressure reducing device 84 through the check valve 86, evaporated in the first auxiliary heat exchanger 88, and circulated to the compressor 81 through the four-way valve 82. At this time, the second auxiliary heat exchanger 89 and the first auxiliary heat exchanger 88 of the use-side refrigerant cycle exchange heat, and the gas refrigerant in the use-side refrigerant cycle is cooled and liquefied. It is sent to the transport device 91. Further, the refrigerant is sent to the use-side heat exchangers 92a and 92b through the connection pipes i and j by the refrigerant transfer device 91 and absorbed and evaporated to cool the installation space. The refrigerant is gasified by evaporation and circulates to the second auxiliary heat exchanger 89 through the connection pipes i ′ and j ′.
[0004]
On the other hand, during the heating operation, the refrigerant cycle is indicated by a broken line arrow in the drawing. In the heat source-side refrigerant cycle, the high-temperature and high-pressure gas from the compressor 81 is sent to the first auxiliary heat exchanger 88 through the four-way valve 82 to release heat. At the same time, it condenses and liquefies. Further, the pressure is reduced by the heating depressurizing device 85 through the check valve 87, absorbed by the heat source side heat exchanger 83, and circulated to the compressor 81 through the four-way valve 82. At this time, the second auxiliary heat exchanger 89 and the first auxiliary heat exchanger 88 of the use side refrigerant cycle exchange heat, the liquid refrigerant in the use side refrigerant cycle is heated and gasified, and the connection pipes i ′ and j ′ are connected. The heat is then sent to the use-side heat exchangers 92a and 92b to radiate and condense to heat the installation space. The refrigerant is liquefied by condensation, sent to the refrigerant transfer device 91 through the connection pipes i and j, and circulated from the refrigerant storage tank 90 to the second auxiliary heat exchanger 89.
[0005]
[Problems to be solved by the invention]
In a conventional refrigeration / air-conditioning apparatus such as a cooling / heating apparatus, when a heating operation such as heating is continuously performed, frost is formed on the surface of the heat source side heat exchanger 83. If frost is formed on the heat source side heat exchanger 83, the heat exchange efficiency is deteriorated. Therefore, when performing the heating operation continuously, the defrosting operation is performed for a predetermined time, for example, about once every hour. In the defrosting operation, the heat source side refrigerant cycle is operated in the same refrigerant cycle as the cooling operation for performing cooling. For this reason, an endothermic action is generated from the second auxiliary heat exchanger 89 to the first auxiliary heat exchanger 88, and when the refrigerant transport device 91 of the use-side refrigerant cycle is operated, the room to be heated by the use-side heat exchangers 92a and 92b is heated. The heat of the air is taken away, and the comfort of the indoor space is impaired due to a decrease in room temperature, a feeling of cool wind during the heating operation, and the like. Further, even without operating the refrigerant transfer device 91 of the use-side refrigerant cycle, the use-side refrigerant is condensed and liquefied in the second auxiliary heat exchanger 89 and the pressure is reduced, so that the refrigerant flows through the connection pipes i ′ and j ′. The liquid refrigerant evaporates in the use-side heat exchangers 92a and 92b to take heat from the indoor air, and similarly, the comfort is impaired.
[0006]
Further, in the conventional refrigeration and air-conditioning apparatus having the above-described configuration, the refrigerant transport device 91 in the use-side refrigerant cycle has a characteristic that the refrigerant outflow direction is reversed between the cooling operation for cooling and the heating operation for heating. It is expensive because it is special.
In addition, refrigerants used in ordinary refrigeration and air conditioning systems use latent heat and have high energy efficiency. However, the use of these refrigerants causes the following problems. For example, HCFC (Hydrochlorofluorocarbon) refrigerant slightly but destroys the ozone layer, and HFC (Hydrofluorocarbon) refrigerant has a large global warming potential and is expensive. In addition, HC (hydrocarbon) refrigerant that does not destroy the ozone layer and has a low global warming potential is flammable, and ammonia refrigerant is toxic, so it is costly to ensure safety when connecting pipes. Need attention.
[0007]
The present invention has been made to solve the above-described problems, and stabilizes the refrigerant temperature during the heating operation in the use-side refrigerant cycle with respect to the defrosting operation in the heat-source-side refrigerant cycle. It is an object of the present invention to provide a refrigeration / air-conditioning apparatus and a control method thereof that can prevent the indoor comfort from being impaired when heating the room with a heat exchanger and can improve the comfort.
It is another object of the present invention to obtain an inexpensive and safe refrigeration / air-conditioning apparatus and a control method thereof, which can minimize the amount of a refrigerant having a problem in use, such as an HCFC refrigerant, an HFC refrigerant, an HC refrigerant, and an ammonia refrigerant. I have.
[0008]
[Means for Solving the Problems]
The refrigeration / air-conditioning apparatus according to claim 1 of the present invention performs the heat exchange by an auxiliary heat exchanger provided between a heat-source-side refrigerant cycle that circulates a heat-source-side refrigerant and a use-side refrigerant cycle that circulates a use-side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the heat source-side refrigerant cycle for heating in the use-side refrigerant cycle, a refrigerant that uses sensible heat is used as the use-side refrigerant, and the heating-side operation of the use-side refrigerant cycle is performed during the heating operation. The amount of the use-side refrigerant is filled so that the temperature of the use-side refrigerant when the defrosting operation of the heat source-side refrigerant cycle is maintained at a temperature suitable for heating, hot water supply, or heating and drying. .
[0009]
In the refrigeration / air-conditioning apparatus according to claim 2 of the present invention, the amount of heat deprived from the use side refrigerant cycle by the auxiliary heat exchanger by the defrosting operation of the heat source side refrigerant cycle is Qd, the amount of use side refrigerant is W, When the specific heat of the side refrigerant is Cp, and the defrosting operation is performed in the heat source side refrigerant cycle during the heating operation of the utilization side refrigerant cycle, the temperature decrease of the utilization side refrigerant represented by Qd / (W · Cp) is reduced. The amount W of the use-side refrigerant is charged so as to be equal to or lower than a predetermined temperature, and the temperature of the use-side refrigerant is maintained at a temperature suitable for heating, hot water supply, or heating and drying.
[0010]
The refrigeration and air-conditioning apparatus according to claim 3 of the present invention further includes a heat storage means provided in the use-side refrigerant cycle for storing heat obtained in the heat-source-side refrigerant cycle, and the auxiliary means is provided by a defrosting operation of the heat-source-side refrigerant cycle. The amount of heat taken from the use-side refrigerant cycle in the heat exchanger is Qd, the amount of heat radiated from the heat storage means by the defrosting operation is Qt, the amount of the use-side refrigerant is W, the specific heat of the use-side refrigerant is Cp, When the defrosting operation is performed in the heat-source-side refrigerant cycle during the heating operation of the usage-side refrigerant cycle, the temperature decrease of the usage-side refrigerant represented by (Qd-Qt) / (W · Cp) becomes equal to or less than a predetermined temperature. Filling the amount W of the use side refrigerant and setting the heat storage capacity of the heat storage means so as to maintain the temperature of the use side refrigerant at a temperature suitable for heating or hot water supply or heating and drying. Is shall.
[0011]
Further, in the refrigeration / air-conditioning apparatus according to claim 4 of the present invention, heat is exchanged by an auxiliary heat exchanger provided between a heat source-side refrigerant cycle for circulating the heat source-side refrigerant and a use-side refrigerant cycle for circulating the use-side refrigerant. In the refrigeration and air-conditioning system that uses the heat obtained in the heat source-side refrigerant cycle for heating in the use-side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use-side refrigerant, and the refrigerant is used in the use-side refrigerant cycle. Providing a refrigerant storage tank for storing the side refrigerant, heating the internal volume of the refrigerant storage tank, the temperature of the use side refrigerant when performing the defrosting operation of the heat source side refrigerant cycle during the heating operation of the use side refrigerant cycle. Alternatively, the amount of the use-side refrigerant or the amount of the heat storage material is set to an internal volume that can be stored so as to maintain a temperature suitable for hot water supply or heating and drying.
[0012]
A refrigeration / air-conditioning apparatus according to claim 5 of the present invention connects a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a first auxiliary heat exchanger to supply heat source side refrigerant. A heat source side refrigerant cycle circulated, a second auxiliary heat exchanger that exchanges heat with the first auxiliary heat exchanger, a refrigerant storage tank, a refrigerant transport device, and a use side heat exchanger are connected to circulate the use side refrigerant. And a use-side refrigerant cycle, wherein the compressor, the flow path switching valve, the heat source-side heat exchanger, the heat source-side refrigerant flow control valve, the first auxiliary heat exchanger, and the second auxiliary heat are provided. The exchanger, the refrigerant storage tank, and the refrigerant transport device are housed in one unit.
[0013]
A refrigeration / air-conditioning apparatus according to claim 6 of the present invention connects a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a first auxiliary heat exchanger to supply heat source side refrigerant. A heat source side refrigerant cycle circulated, a second auxiliary heat exchanger that exchanges heat with the first auxiliary heat exchanger, a refrigerant storage tank, a refrigerant transport device, and a use side heat exchanger are connected to circulate the use side refrigerant. Wherein the compressor, the flow path switching valve, the heat source side heat exchanger, and the heat source side refrigerant flow control valve are housed in one unit, and the first auxiliary The heat exchanger, the second auxiliary heat exchanger, the refrigerant storage tank, and the refrigerant transport device are housed in a separate unit from the unit, and one end of the first auxiliary heat exchanger and the flow The other end of the first auxiliary heat exchanger between the first and second auxiliary heat exchangers; It is characterized in that it has connected to each connecting pipe between the heat source-side refrigerant flow rate control valve and.
[0014]
A refrigeration / air-conditioning apparatus according to claim 7 of the present invention connects a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a first auxiliary heat exchanger to supply heat source side refrigerant. Circulating the heat source side refrigerant cycle, the first refrigerant transfer device, the second auxiliary heat exchanger that exchanges heat with the first auxiliary heat exchanger, and the refrigerant storage tank to circulate the use side refrigerant. A heat transfer cycle, a second refrigerant transfer device, a use side heat exchanger, and a use side refrigerant cycle that connects the refrigerant storage tank and circulates the use side refrigerant. The heat obtained by exchanging heat with the first auxiliary heat exchanger in the second auxiliary heat exchanger is stored in the refrigerant storage tank, and the heat stored in the refrigerant storage tank in the use-side refrigerant cycle is used as the use-side heat. To use it for heating in the exchanger. It is an butterfly.
[0015]
In the refrigeration / air-conditioning apparatus according to claim 8 of the present invention, the inside of the refrigerant storage tank is divided into right and left, and a communication part through which the divided right and left use-side refrigerants can communicate below the draft surface is provided. Comprising a partition having, two openings in each of the divided left and right tanks, two openings in one tank of the refrigerant storage tank, the inlet of the use-side refrigerant from the use-side heat exchanger, (2) as an outlet of the use-side refrigerant to the auxiliary heat exchanger, two openings of the other tank of the refrigerant storage tank are provided with an inlet of the use-side refrigerant from the second auxiliary heat exchanger; An outlet for the use-side refrigerant to the side heat exchanger.
[0016]
The refrigeration / air-conditioning apparatus according to claim 9 of the present invention is characterized in that the auxiliary heat exchanger for exchanging heat between the heat source side refrigerant and the use side refrigerant is a plate type heat exchanger.
[0017]
The refrigeration / air-conditioning apparatus according to claim 10 of the present invention is a switching means for switching the flow direction of the use side refrigerant in the auxiliary heat exchanger between the heat source side refrigerant cycle and the use side refrigerant cycle between the cooling operation and the heating operation. Wherein the flow direction of the heat source side refrigerant and the use side refrigerant at the time of heat exchange in the auxiliary heat exchanger is configured to be counterflow both during the cooling operation and during the heating operation. is there.
[0018]
The refrigeration / air-conditioning apparatus according to claim 11 of the present invention connects the compressor, the flow path switching valve, the heat source side heat exchanger, the heat source side refrigerant flow control valve, and the auxiliary heat exchanger to circulate the heat source side refrigerant. A heat source-side refrigerant cycle, a refrigerant storage tank for storing a use-side refrigerant, and a use-side refrigerant cycle connected to a refrigerant transport device and circulating the use-side refrigerant. The auxiliary heat exchanger immerses in the use side refrigerant in the storage tank and exchanges heat between the heat source side refrigerant and the use side refrigerant in the auxiliary heat exchanger to store heat in the refrigerant storage tank, and stores the refrigerant in the use side refrigerant cycle. The heat stored in the tank is used for heating.
[0019]
A refrigeration / air-conditioning apparatus according to claim 12 of the present invention is characterized in that the heat transfer area of the use-side refrigerant in the auxiliary heat exchanger is larger than the heat transfer area of the heat-source-side refrigerant.
[0020]
A refrigeration / air-conditioning apparatus according to a thirteenth aspect of the present invention is characterized by including a bubble blowing means for blowing bubbles around the auxiliary heat exchanger in the refrigerant storage tank.
[0021]
The refrigeration / air-conditioning apparatus according to claim 14 of the present invention circulates through the use-side refrigerant pipe provided outside the refrigerant storage tank and connecting positions where the heights of the refrigerant storage tanks are different, and the use-side refrigerant pipe. A heat source device for heating the use-side refrigerant is provided.
[0022]
A refrigeration / air-conditioning apparatus according to claim 15 of the present invention includes a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, an auxiliary heat exchanger, a refrigerant storage tank, and a refrigerant conveyance device. It is characterized by being housed in one unit.
[0023]
A refrigeration / air-conditioning apparatus according to claim 16 of the present invention includes a compressor, a flow path switching valve, a heat source side heat exchanger, and a heat source side refrigerant flow control valve housed in one unit, and an auxiliary heat exchanger. , The refrigerant storage tank, and the refrigerant transport device are housed in one unit different from the unit, and between one end of the auxiliary heat exchanger and the flow path switching valve and the other end of the auxiliary heat exchanger. And the heat source side refrigerant flow control valve is connected by a connection pipe.
[0024]
A refrigeration / air-conditioning apparatus according to claim 17 of the present invention is characterized in that a heat storage material is provided in a refrigerant storage tank that stores a use-side refrigerant.
[0025]
The refrigeration / air-conditioning apparatus according to claim 18 of the present invention is provided in the refrigerant storage tank, includes a partition that divides the inside of the refrigeration storage tank into right and left, and receives the use-side refrigerant provided in one of the divided tanks. And an opening provided in the other tank, through which the use-side refrigerant flows out, wherein the partition communicates with the divided left and right use-side refrigerants below a draft surface of the refrigerant storage tank. It has a part.
[0026]
A refrigeration / air-conditioning apparatus according to claim 19 of the present invention is characterized in that a filter for collecting contaminants mixed in the use-side refrigerant is provided in a portion where the use-side refrigerant circulates.
[0027]
A refrigeration / air-conditioning apparatus according to claim 20 of the present invention is characterized in that the filter is provided in a refrigerant storage tank that stores the use-side refrigerant.
[0028]
Further, the refrigeration / air-conditioning apparatus according to claim 21 of the present invention is characterized in that the heat source side refrigerant cycle has a plurality of two or more systems.
[0029]
In the refrigeration / air-conditioning apparatus according to claim 22 of the present invention, heat is exchanged by an auxiliary heat exchanger provided between a heat source-side refrigerant cycle for circulating the heat source-side refrigerant and a use-side refrigerant cycle for circulating the use-side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the heat-source-side refrigerant cycle for heating in the use-side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use-side refrigerant, and the heat-source-side refrigerant cycle is divided into two or more systems. , And at least one of the heat source side refrigerant cycles is constituted by a refrigerant cycle dedicated to heating.
[0030]
A refrigeration / air-conditioning apparatus according to claim 23 of the present invention is characterized in that a plurality of heat source-side refrigerant cycles are connected in parallel to a use-side refrigerant cycle.
[0031]
A refrigeration / air-conditioning apparatus according to claim 24 of the present invention is characterized in that a plurality of heat-source-side refrigerant cycles are connected in series to a use-side refrigerant cycle.
[0032]
In the refrigeration / air-conditioning apparatus according to claim 25 of the present invention, the heat source-side refrigerant cycle is provided with at least one heating-only refrigerant cycle and at least one cooling / heating-use refrigerant cycle. It is characterized in that a dedicated refrigerant cycle and the cooling / heating combined refrigerant cycle are connected in series.
[0033]
In the refrigeration / air-conditioning apparatus according to claim 26 of the present invention, a cooling / heating combined refrigerant cycle is connected upstream with respect to the flow direction of the use-side refrigerant circulating in the use-side refrigerant cycle, and the heating-only refrigerant is used. The cycle is connected to the downstream side.
[0034]
In the refrigeration / air-conditioning apparatus according to claim 27 of the present invention, a refrigerant cycle dedicated to heating is connected upstream with respect to the flow direction of the use-side refrigerant circulating in the use-side refrigerant cycle, and the refrigerant is used for both cooling and heating. The cycle is connected to the downstream side.
[0035]
In the refrigeration / air-conditioning apparatus according to claim 28 of the present invention, the heat source-side refrigerant cycle is provided with at least one heating-only refrigerant cycle and at least one cooling / heating-use refrigerant cycle, and the heating-side refrigerant cycle is heated. A dedicated refrigerant cycle and the cooling / heating combined refrigerant cycle are connected in parallel, and during the cooling operation, the use-side refrigerant does not flow to the use-side auxiliary heat exchanger that exchanges heat with the heating-dedicated refrigerant cycle, A switching means for switching a refrigerant flow path of the use-side refrigerant cycle is provided.
[0036]
Further, the refrigeration / air-conditioning apparatus according to claim 29 of the present invention is provided with at least one heating-only refrigerant cycle and at least one cooling-only refrigerant cycle in the heat-source-side refrigerant cycle, and uses only the heating-only refrigerant cycle in the use-side refrigerant cycle. A refrigerant cycle and a refrigerant cycle dedicated to cooling are connected in series.
[0037]
In the refrigeration / air-conditioning apparatus according to claim 30 of the present invention, the heat source-side refrigerant cycle is provided with at least one heating-only refrigerant cycle and at least one cooling-only refrigerant cycle, and the heating-side refrigerant cycle is dedicated to the heating. A refrigerant cycle and the cooling-dedicated refrigerant cycle are connected in parallel, and during a heating operation, a usage-side refrigerant is circulated through a usage-side auxiliary heat exchanger that exchanges heat with the heating-dedicated refrigerant cycle. Switching means for switching a refrigerant flow path of the use-side refrigerant cycle so as to circulate the use-side refrigerant to the use-side auxiliary heat exchanger that exchanges heat with the refrigerant cycle is provided.
[0038]
The refrigeration / air-conditioning apparatus according to claim 31 of the present invention is configured such that the heating-side heat source device in which the usage-side refrigerant circulates and the usage-side refrigerant so as to circulate the usage-side refrigerant in the heating-only heat source device during the heating operation. Switching means for switching the refrigerant flow path of the refrigerant cycle.
[0039]
In the refrigeration / air-conditioning apparatus according to claim 32 of the present invention, heat is supplied to a use-side refrigerant cycle by a use-side heat exchanger for cooling supplied with heat by the heat-source-side refrigerant cycle and a heat source device dedicated to heating. A heating use side heat exchanger for heating is provided, and the heat source side refrigerant cycle and the use side heat exchanger for cooling are operated during the cooling operation, and the heating only heat source device and the heating use side during the heating operation. The use side heat exchanger is configured to operate.
[0040]
Further, in the refrigeration / air-conditioning apparatus according to claim 33 of the present invention, the cooling use-side heat exchanger is arranged side by side with respect to the air flow on the upstream side of the heating use-side heat exchanger, and when the dehumidifying operation is performed. The present invention is characterized in that the cooling and heating use side heat exchangers are operated.
[0041]
A refrigeration air conditioner according to claim 34 of the present invention is characterized in that the heat source device dedicated to heating is a heating device that directly heats the use-side refrigerant.
[0042]
In the refrigeration / air-conditioning apparatus according to claim 35 of the present invention, in a pipe constituting a use-side refrigerant cycle, a feed-side pipe to a use-side heat exchanger and a return-side pipe from the use-side heat exchanger, The diameter of the pipe or the diameter or the shape of the joint of the pipe is different.
[0043]
A refrigeration / air-conditioning apparatus according to claim 36 of the present invention is characterized in that a plurality of use-side heat exchangers are provided in a use-side refrigerant cycle, and all of the use-side heat exchangers are connected in parallel with each other. Things.
[0044]
In the refrigeration / air-conditioning apparatus according to claim 37 of the present invention, a plurality of use-side heat exchangers are provided in the use-side refrigerant cycle, and at least some of the use-side heat exchangers are connected in series with each other. It is characterized by the following.
[0045]
Further, in the method for controlling a refrigerating air conditioner according to claim 38 of the present invention, the refrigerant circulating in the use-side refrigerant cycle is water, or one or more of ethylene glycol, propylene glycol, and D-sorbitol. Is an aqueous solution containing several tens of% or less by weight.
[0046]
In the refrigeration / air-conditioning apparatus according to claim 39 of the present invention, the heat source-side refrigerant cycle is constituted by a vapor compression refrigeration cycle, and the refrigerant circulating in the heat source-side refrigerant cycle uses latent heat. The refrigerant is one of one refrigerant, a chlorofluorocarbon-based azeotropic mixed refrigerant, a chlorofluorocarbon-based non-azeotropic refrigerant, a hydrocarbon-based refrigerant, and an ammonia refrigerant.
[0047]
Further, in the method for controlling a refrigeration / air-conditioning apparatus according to claim 40 of the present invention, heat is generated by an auxiliary heat exchanger provided between a heat-source-side refrigerant cycle for circulating a heat-source-side refrigerant and a use-side refrigerant cycle for circulating a use-side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the heat source-side refrigerant cycle for heating in the use-side refrigerant cycle by exchanging, while using a refrigerant that utilizes sensible heat as the use-side refrigerant, the heat-source-side refrigerant cycle The present invention is characterized in that the capacitance is changed in a plurality of stages, and the change width of the capacitance is increased as the capacitance increases.
[0048]
Further, in the control method of a refrigeration / air-conditioning apparatus according to claim 41 of the present invention, the heat source side refrigerant cycle for circulating the heat source side refrigerant and the use side refrigerant cycle provided between the use side refrigerant cycle for circulating the use side refrigerant may be used. In a refrigeration air conditioner that uses the heat obtained in the heat source side refrigerant cycle for heating in the use side refrigerant cycle by exchanging, while using a refrigerant that utilizes sensible heat as the use side refrigerant, the heat source side refrigerant cycle is At least one of the heat source side refrigerant cycles performs a heating operation while at least one of the heat source side refrigerant cycles performs a defrost operation during a heating operation in the utilization side refrigerant cycle. It is characterized in that it is controlled to continue.
[0049]
Further, in the control method of a refrigeration / air-conditioning apparatus according to claim 42 of the present invention, the heat source side refrigerant cycle for circulating the heat source side refrigerant and the use side refrigerant cycle provided between the use side refrigerant cycle for circulating the use side refrigerant generate heat. In a refrigeration air conditioner that uses the heat obtained in the heat source side refrigerant cycle for heating in the use side refrigerant cycle by exchanging, while using a refrigerant that utilizes sensible heat as the use side refrigerant, the heat source side refrigerant cycle is The heat source side refrigerant cycle includes a plurality of two or more systems, and the heat source side refrigerant cycle is provided with at least one system of a refrigerant cycle dedicated to heating and a refrigerant cycle of both cooling and heating. A vapor compression refrigeration cycle is used as the refrigerant cycle of both cooling and heating. During the heating operation, while at least one of the cooling / heating combined refrigerant cycles is performing the defrosting operation, the heating-only refrigerant cycle is Refrigerant cycle of the at least one channel of the refrigerant cycle of the cooling / heating combination is to control means controls so as to continue the heating operation.
[0050]
Further, in the method for controlling a refrigeration / air-conditioning apparatus according to claim 43 of the present invention, the heat source-side refrigerant cycle that continues the heating operation while one or more of the heat source-side refrigerant cycles is performing the defrosting operation has a heating function. It is characterized in that control is performed so as to increase the capacity and continue the heating operation.
[0051]
Further, in the method for controlling a refrigerating air conditioner according to claim 44 of the present invention, the heat source side refrigerant cycle that continues the heating operation while one or more of the heat source side refrigerant cycles performs the defrosting operation is dedicated to heating. The refrigerant cycle is characterized by the following.
[0052]
Further, in the control method of a refrigeration / air-conditioning apparatus according to claim 45 of the present invention, the heat source side refrigerant cycle circulating the heat source side refrigerant and the use side refrigerant cycle provided between the use side refrigerant cycle circulating the use side refrigerant generate heat. In a refrigeration air conditioner that uses the heat obtained in the heat source side refrigerant cycle for heating in the use side refrigerant cycle by exchanging, while using a refrigerant that utilizes sensible heat as the use side refrigerant, the heat source side refrigerant cycle If two or more vapor compression refrigeration cycles are used and one or more of the heat source side refrigerant cycles satisfy the defrosting operation start condition during the heating operation in the use side refrigerant cycle, before starting the defrosting operation. It is characterized in that the heating operation is continued by increasing the capacity of the heat source-side refrigerant cycle, and then the defrosting operation is controlled.
[0053]
Further, in the method for controlling a refrigeration / air-conditioning apparatus according to claim 46 of the present invention, the heat generated by the auxiliary heat exchanger provided between the heat-source-side refrigerant cycle for circulating the heat-source-side refrigerant and the use-side refrigerant cycle for circulating the use-side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the heat source side refrigerant cycle for heating in the use side refrigerant cycle by exchanging, while using a refrigerant that utilizes sensible heat as the use side refrigerant, the heat source side refrigerant cycle is A plurality of two or more heat source-side refrigerant cycles are configured so that each capacity of the heat source-side refrigerant cycle of the plural systems is changed to one or more stages, and the total capacity of the heat source-side refrigerant cycles of the plural systems as a whole is It is characterized in that it is configured to change in a plurality of stages, and that the change width of the total capacity increases as the total capacity increases.
[0054]
In the method for controlling a refrigeration / air-conditioning apparatus according to claim 47 of the present invention, when the stage of the total capacity is increased, the currently operating heat source side refrigerant cycle of the plurality of systems of the heat source side refrigerant cycle is operated. It is assumed that the total capacity is increased in the state, and when the stage of the total capacity is reduced, the currently stopped heat source-side refrigerant cycle of the heat source-side refrigerant cycles of a plurality of systems remains stopped. The control is performed so as to reduce the total capacity.
[0055]
Further, a refrigeration air conditioner according to claim 48 of the present invention is configured such that a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a refrigerant storage tank that stores the heat source side refrigerant are connected. A heat-source-side refrigerant cycle that circulates a heat-source-side refrigerant, and an auxiliary heat exchanger, and a use-side refrigerant cycle that connects the refrigerant conveyance device and circulates the use-side refrigerant. The heat source side refrigerant and the use side refrigerant are immersed in the heat source side refrigerant in the storage tank to exchange heat with the heat source side refrigerant and the use side refrigerant in the auxiliary heat exchanger, and the heat stored in the refrigerant storage tank is used for heating in the use side refrigerant cycle. It is characterized by doing.
[0056]
BEST MODE FOR CARRYING OUT THE INVENTION
Embodiment 1 FIG.
Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 1 of the present invention, for example, a cooling / heating apparatus that performs indoor cooling / heating will be described. In the cooling / heating device, the room is cooled by a cooling operation, and the room is heated by a heating operation. The cooling operation is referred to as a cooling operation, and the heating operation is referred to as a heating operation. FIG. 1 is a configuration diagram illustrating a cooling and heating device according to the present embodiment. In the figure, reference numeral 11 denotes a compressor, and 12 denotes a flow path switching valve for switching a refrigerant flow path between a heating operation and a cooling operation. Here, for example, a four-way valve is used. 13 is a heat source side heat exchanger, 14 is a heat source side refrigerant flow control valve, 15 is a receiver, 16 is a first auxiliary heat exchanger, 17 is an outdoor blower, and these are housed in one unit and f and is installed outdoors. A discharge port of the compressor 11 is connected to a first port of the four-way valve 12, and a second port of the four-way valve 12 is connected to one end of the heat source-side heat exchanger 13. The other end of the heat source side heat exchanger 13 is connected to the heat source side refrigerant flow control valve 14 and the receiver 15 in that order, and further connected to one end of the first auxiliary heat exchanger 16. The other end of the first auxiliary heat exchanger 16 is connected to the fourth port of the four-way valve 12, and the third port of the four-way valve 12 is connected to the suction port of the compressor 11, forming a heat source side refrigerant cycle. are doing. The four-way valve 12 switches between the cooling operation and the heating operation of the heat source side refrigerant cycle. As shown by the solid line in FIG. 1, the first port and the second port, and the third port and the fourth port are connected. A cooling operation is performed, and a heating operation is performed when the first port and the fourth port and the third port and the second port are connected as shown by a dotted line. Instead of the four-way valve 12, for example, four electromagnetic valves may be provided to switch between the cooling operation, the heating operation, and the refrigerant flow path. Further, the receiver 15 is provided to absorb a difference in the required amount of refrigerant in the heat source side refrigerant cycle during cooling and during heating.
A refrigerant cycle configured to circulate refrigerant in a refrigerant circuit using a compressor and utilize condensation and evaporation of the refrigerant is called a vapor compression refrigeration cycle.
[0057]
Further, reference numeral 19 denotes a second auxiliary heat exchanger which is integrally formed so as to exchange heat with the first auxiliary heat exchanger 16. Reference numeral 20 denotes a refrigerant storage tank that adjusts the difference between the amounts of refrigerant during cooling and during heating in the use-side refrigerant cycle. The refrigerant storage tank 20 is made of, for example, metal or plastic. Reference numeral 21 denotes a refrigerant transport device, for example, a magnet pump. The second auxiliary heat exchanger 19, the refrigerant storage tank 20, and the refrigerant transfer device 21 are housed in the outdoor unit f together with the heat source side refrigerant cycle. Reference numerals 22a and 22b denote user-side heat exchangers, and reference numerals 23a and 23b denote user-side refrigerant flow control valves, each of which comprises, for example, an on-off valve or a flow control valve. 24a and 24b are indoor blowers. The use side heat exchanger 22a, the thermal valve 23a, and the indoor blower 24a are housed in an indoor unit g, and the use side heat exchanger 22b, the thermal valve 23b, and the indoor blower 24b are housed in an indoor unit h. Each of the indoor units g and h is, for example, a floor-standing type, a wall-mounted type, or a ceiling-hanging type installed inside a room to be air-conditioned, or a use-side heat exchanger installed outside the room to be air-conditioned. There are a duct type that sends cold or warm air into a room, and a type that is embedded in a ceiling or a wall of a room to be air-conditioned.
[0058]
The discharge port of the refrigerant transfer device 21 is connected to one end of a connection pipe i, and the other end of the connection pipe i is branched and connected to one ends of a connection pipe j and a connection pipe k, respectively. The other ends of the connection pipes j and k are connected to the heat operated valves 23a and 23b, respectively, which are connected to one ends of the use side heat exchangers 22a and 22b. The other ends of the use-side heat exchangers 22a and 22b are connected to one ends of a connection pipe j ′ and a connection pipe k ′, and the other ends thereof are both connected to one end of a connection pipe i ′. The other end is connected to one end of the second auxiliary heat exchanger 19 in the outdoor unit f. The other end of the second auxiliary heat exchanger 19 is connected to an inlet on the side surface of the refrigerant storage tank 20, and an outlet provided on the bottom surface of the refrigerant storage tank 20 is connected to an inlet of the refrigerant transfer device 21. I have. The second auxiliary heat exchanger 19, the refrigerant storage tank 20, the refrigerant transport device 21, the indoor units g and h, and the pipes connecting them form a use-side refrigerant cycle. Reference numeral 31 denotes a temperature detecting means for detecting the temperature of the refrigerant, for example, a first temperature sensor.
[0059]
In the refrigeration / air-conditioning apparatus applied to the cooling and heating according to the present embodiment, a refrigerant utilizing sensible heat is used as a refrigerant in the use-side refrigerant cycle, for example, water or a solvent such as ethylene glycol, propylene glycol, and D-sorbitol. An aqueous solution containing one or more of them at several tens% by weight or less is used. An aqueous solution containing one or more of solvents such as ethylene glycol, propylene glycol, and D-sorbitol in a weight ratio of more than 0% and not more than tens of% does not freeze even when the temperature becomes 0 [° C.] or less. It is an antifreeze having characteristics.
If an antifreeze liquid, which is an aqueous solution containing more than 0% and several tens% or less by weight of ethylene glycol, propylene glycol, D-sorbitol, or the like, is used as the refrigerant of the utilization side refrigerant cycle, The refrigerant can be prevented from freezing even if it is installed in an area where the temperature is low and 0 [° C.] or less. FIG. 2 shows a graph of, for example, the concentration of an aqueous propylene glycol solution and its characteristics. 2A is a freezing temperature (° C.) with respect to the concentration of the aqueous solution, FIG. 2B is a kinematic viscosity with respect to the concentration of the aqueous solution at 10 ° C. and 45 ° C., and FIG. ] And 45 [° C.] with respect to the concentration of the aqueous solution. As shown in FIG. 2A, there is an advantage that the freezing temperature decreases as the concentration of the aqueous solution increases, and the freezing does not occur even when used in an area where the outside air temperature decreases accordingly. However, on the other hand, the kinematic viscosity increases as shown in FIG. 2B, and the heat transfer coefficient decreases as shown in FIG. 2C. For this reason, as the refrigerant circulating in the use-side refrigerant cycle, an aqueous solution having a concentration of several tens% or less, for example, about 60% or less, and an about 30% concentration in this embodiment, for example, is used.
[0060]
The refrigerant storage tank 20 is open to the atmosphere so as to absorb the volume expansion of the use-side refrigerant. The piping from the outlet of the refrigerant storage tank 20 to the refrigerant transfer device 21 and the position of the refrigerant transfer device 21 are arranged below the tank draft. This is because, when the piping from the outlet of the refrigerant storage tank 20 to the refrigerant transport device 21 and the position of the refrigerant transport device 21 are arranged above the draft in the tank, the pressure loss increases, and the refrigerant does not flow smoothly, The required flow rate may not be obtained because the refrigerant evaporates at the suction port of the refrigerant transfer device 21, and this is to prevent these. For the same reason, it is desirable that the piping from the outlet of the refrigerant storage tank 20 to the refrigerant transport device 21 be thicker and shorter.
The above-mentioned use-side refrigerant is a refrigerant that is easy to handle and inexpensive without any problem in terms of global environmental protection.
[0061]
On the other hand, the refrigerant in the heat source side refrigerant cycle is a Freon-based refrigerant such as HCFC (hydrochlorofluorocarbon) refrigerant or HFC (hydrofluorocarbon) refrigerant, an HC (hydrocarbon-based) refrigerant, and an ammonia refrigerant, which are used in a normal refrigeration and air conditioning system. And so on. Specifically, for example, a single refrigerant such as R22 which is an HCFC refrigerant or R134a which is an HFC refrigerant, a pseudo-azeotropic mixed refrigerant such as R410A which is an HFC refrigerant, a non-azeotropic mixed refrigerant such as R407C which is an HFC refrigerant, HC Use propane, isobutane, and ammonia as refrigerants.
[0062]
As described above, the refrigerant of the use-side refrigerant cycle and the refrigerant of the heat source-side refrigerant cycle are separated, and the use-side refrigerant cycle uses sensible heat to transport heat, and the heat application-side refrigerant cycle uses latent heat. It is composed of different components such as a refrigerant that transports heat. By using a refrigerant having high energy efficiency on the heat source side and using a refrigerant using sensible heat that does not cause a problem in depletion of the ozone layer and global warming on the use side, energy efficiency is high in the entire refrigeration and air conditioning system. However, the use amount of the refrigerant having a problem in use is reduced as much as possible.
Of course, natural refrigerants such as carbon dioxide, water, and air may be used as the refrigerant in the heat source-side refrigerant cycle, or the same refrigerant as the refrigerant in the use-side refrigerant cycle, that is, any one of ethylene glycol, propylene glycol, and D-sorbitol An aqueous solution containing one or more of them by several tens% or less by weight may be used. In this case, although the energy efficiency is reduced, a refrigeration / air-conditioning apparatus having no problem in terms of global environmental protection and handling can be configured.
[0063]
Next, the operation will be described.
During the cooling operation, the refrigerant cycle shown by the solid line in FIG. 1 is performed. In the heat source side refrigerant cycle, the first port and the second port, and the third port and the fourth port of the four-way valve 12 are connected. The high-temperature and high-pressure vapor refrigerant discharged from the compressor 11 passes through the four-way valve 12, radiates heat to the outside air sent by the outdoor blower 17 in the heat source side heat exchanger 13, condenses and liquefies, and passes through the refrigerant flow control valve 14 to reduce the pressure. The refrigerant becomes a low-temperature gas-liquid two-phase refrigerant, evaporates in the first auxiliary heat exchanger 16 via the receiver 15, becomes a low-pressure low-temperature vapor refrigerant, and circulates through the four-way valve 12 to the compressor 11. At this time, the second auxiliary heat exchanger 19 of the use side refrigerant cycle and the first auxiliary heat exchanger 16 exchange heat, and the refrigerant in the use side refrigerant cycle is cooled. This refrigerant is sent to the refrigerant transfer device 21 through the refrigerant storage tank 20, and is sent to the use side heat exchangers 22a and 22b through the connection pipes i, j, and k by the refrigerant transfer device 21. In the use-side heat exchangers 22a and 22b, the refrigerant absorbs heat from the indoor air sent by the indoor blowers 24a and 24b, is heated by itself, passes through the connection pipes j ′, k ′, and i ′, and passes through the second auxiliary heat exchanger. Circulates to exchanger 19. On the other hand, the indoor air sent into the use-side heat exchangers 22a and 22b by the indoor blowers 24a and 24b releases heat to the refrigerant in the use-side heat exchangers 22a and 22b and is cooled at the same time, and is blown back into the room to cool the room. I do.
[0064]
During the heating operation, the refrigerant cycle is indicated by a broken line in the figure. In the heat source side refrigerant cycle, the first port and the fourth port, and the third port and the second port of the four-way valve 12 are connected. The high-temperature and high-pressure vapor refrigerant discharged from the compressor 11 is sent to the first auxiliary heat exchanger 16 through the four-way valve 12, radiates heat and condenses and liquefies, passes through the receiver 15, and is depressurized by the refrigerant flow control valve 14. It becomes a low-pressure low-temperature gas-liquid two-phase refrigerant, absorbs heat from the outdoor air sent by the outdoor blower 17 in the heat source side heat exchanger 13, evaporates, becomes a low-pressure low-temperature vapor refrigerant, passes through the four-way valve 12, passes through the compressor 11 Circulates to At this time, the second auxiliary heat exchanger 19 of the use side refrigerant cycle and the first auxiliary heat exchanger 16 exchange heat, and the refrigerant in the use side refrigerant cycle is heated. This refrigerant is sent to the refrigerant transfer device 21 through the refrigerant storage tank 20, and is sent to the use side heat exchangers 22a and 22b through the connection pipes i, j, and k by the refrigerant transfer device 21. In the use-side heat exchangers 22a and 22b, the refrigerant radiates heat to the indoor air sent by the indoor blowers 24a and 24b, and is cooled at the same time, and passes through the connection pipes j ', k', and i 'to perform the second auxiliary heat exchange. Circulates to vessel 19. On the other hand, the indoor air sent into the use side heat exchangers 22a and 22b by the indoor blowers 24a and 24b is heated by absorbing heat from the refrigerant in the use side heat exchangers 22a and 22b, and is blown back into the room to heat the room. I do.
[0065]
Further, when the heat source side refrigerant cycle enters the defrosting operation during the heating operation, the heat source side refrigerant cycle becomes the same as the refrigerant cycle at the time of cooling indicated by the solid line in the figure, and deprives the sensible heat of the refrigerant during the use side refrigerant cycle. The frost that has reached the surface of the heat source side heat exchanger 13 is heated and defrosted. At this time, the amount of heat Qd [kJ] taken from the use-side refrigerant cycle in the second auxiliary heat exchanger 19 is approximately 1/30 of the amount of heat [kJ] in one hour of the heat source-side refrigerant cycle. Has been obtained. Also, if the indoor blowers 24a and 24b continue to rotate during the defrosting operation, the temperature of the refrigerant decreases due to the load in the room. The amount of heat QL [kJ] corresponding to the temperature decrease due to the indoor load can be calculated from the defrosting operation time and the heating capacity of the use-side refrigerant cycle. The temperature drop ΔT [K] of the use-side refrigerant is represented by Expression (1), where the amount of refrigerant in the use-side refrigerant cycle is W [kg] and the specific heat is Cp [kJ / kgK].
ΔT = (Qd + QL) / (W · Cp) (1)
[0066]
For example, assuming that the heating capacity of the heat source side refrigerant cycle is 9.6 [kW] = [kJ / s], the amount of heat taken from the usage side refrigerant cycle during defrosting is Qd = 9.6 [kJ / s] × 3600 [s] ] / 30 = 1152 [kJ]. In addition, when the defrosting operation is performed for 3 minutes, the heat amount of the temperature decrease due to the indoor load can be calculated by QL = (heating capacity during heating operation) [kJ / s] × 60 [s] × 3 [min]. . Normally, the defrosting operation is started after the heating operation is performed to some extent, and since the heating operation is not performed at the maximum heating capacity, one indoor unit is now operating. Assuming that the vehicle is operated at 1.5 [kJ / s], QL = 270 [kJ]. Assuming that the refrigerant in the use-side refrigerant cycle is water and its mass is 20 [kg], the specific heat of water is 4.19 [kJ / kgK], so the temperature decrease of the use-side refrigerant during defrosting is ΔT = 17. .0 [K]. That is, the internal volume of the refrigerant storage tank 20 is sufficient to absorb the difference in the required amount of refrigerant between the time of cooling and the time of heating. If there is only one, the refrigerant temperature of the use-side refrigerant cycle drops by 17.0 [K] only by the heat necessary for the defrosting operation during about three minutes of the defrosting operation.
If the blowers 24a and 24b in the indoor units g and h are kept rotating during the defrosting operation, the temperature of the blown air becomes low, resulting in a feeling of cool air and a drop in room temperature, which is uncomfortable. In addition, even if the blowers 24a and 24b in the indoor units g and h are stopped, heating is not possible and the room temperature is lowered, so that the temperature of the use-side refrigerant cannot be maintained at a temperature suitable for heating. Was a serious problem.
[0067]
Therefore, in the refrigeration / air-conditioning apparatus according to the present embodiment, the internal volume of the refrigerant storage tank 20 is set to an internal volume capable of holding 30 [kg] which is equal to or more than the refrigerant amount of the use-side refrigerant cycle. That is, the filling amount of the use-side refrigerant is set to a total of 50 [kg], and the temperature decrease of the use-side refrigerant due to the defrosting operation of the heat-source-side refrigerant cycle is 6.8 [2/5] of the conventional 17.0 [K]. K]. With this temperature drop, it is possible to maintain a temperature suitable for heating without worrying about a feeling of cold wind or a drop in room temperature, so even if the heat source side refrigerant cycle is performing defrosting operation, change the operating state such as stopping the indoor blower There is no need, and the indoor unit can continue to heat. By filling the amount of the use-side refrigerant in this way, the temperature of the use-side refrigerant can be stabilized, and the indoor comfort can be significantly improved without feeling uncomfortable for a person in the room.
[0068]
Conversely, if the allowable value of the refrigerant temperature decrease ΔT [K] in the use-side refrigerant cycle during the defrosting operation is determined to be equal to or lower than the predetermined temperature, the amount of refrigerant that the refrigerant storage tank 20 should hold can be obtained. The total amount of refrigerant in the use-side refrigerant cycle is obtained by the following equation (2) from equation (1).
W = (Qd + QL) / (ΔT · Cp) (2)
The refrigerant amount Wt [kg] held in the refrigerant storage tank 20 is obtained from Expression (3) using W in Expression (2).
Wt = W-Wp (3)
Here, Wp [kg] is a required amount of refrigerant obtained from the internal volume of the usage-side refrigerant cycle other than the refrigerant storage tank 20.
In the above-described example, for example, if the temperature decrease ΔT of the usage-side refrigerant during the defrosting operation is allowed, the refrigerant storage tank 20 includes:
Wt = (1152 + 270) [kJ] / (2 [K] · 4.19 [kJ / kgK])-20
= 150.0 [kg]
Needs an internal volume that can hold the refrigerant. By configuring the refrigerant storage tank 20 in accordance with this and filling the use-side refrigerant, the temperature decrease of the use-side refrigerant can be suppressed within a predetermined temperature decrease, and the temperature suitable for indoor heating can be maintained. In the above description, the predetermined temperature drop ΔT is set to 2 [K]. However, even if the temperature drop is about 10 [K], the indoor comfort is not so much impaired, but it is preferable that the temperature drop be about 5 [K] or less.
However, there is a difference in the calculation of the temperature drop QL due to the indoor load depending on the usage on the usage side, and the refrigerant storage tank 20 needs at least a capacity corresponding to the amount of heat Qd [kJ] taken from the usage-side refrigerant cycle. For example, if the predetermined temperature drop ΔT is 2 [K],
Wt> 1152 [kJ] / (2 [K] · 4.19 [kJ / kgK])-20
> 117.5 [kg].
That is, if at least the heat source-side refrigerant cycle stores the amount of heat required for the defrosting operation in the refrigerant storage tank 20, it is possible to prevent the temperature of the usage-side refrigerant from dropping significantly during the defrosting operation, Indoor comfort during heating operation can be maintained.
[0069]
In the case of a configuration in which a heat storage means such as a heat storage material is provided in the use-side refrigerant cycle and the cold or warm heat obtained in the heat source-side refrigerant cycle is stored, the heat stored in the heat storage means is radiated during the defrosting operation. Therefore, a decrease in the temperature of the use-side refrigerant can be reduced. Assuming that the amount of heat released during the defrosting operation from the heat storage means at this time is Qt [kJ], the temperature drop ΔT of the use-side refrigerant is expressed by the following expression instead of Expression 1.
ΔT = (Qd + QL−Qt) / (W · Cp)
The heat storage capacity of the heat storage means and the amount of refrigerant in the use-side refrigerant cycle are filled so that the temperature decrease ΔT is equal to or lower than a predetermined temperature, for example, 5 [K], and the temperature of the use-side refrigerant is maintained at a temperature suitable for heating. I do. Setting the heat storage capacity based on the heat release amount Qt during the defrosting operation from the heat storage means differs depending on the material and configuration of the heat storage means, and may be set as appropriate for each case. For example, when the heat storage means is a brick or the like immersed in the refrigerant storage tank 20, when the heat source-side refrigerant cycle has a temperature decrease equivalent to the temperature decrease of the use-side refrigerant in the refrigerant storage tank 20 when performing the defrosting operation. Since it is conceivable, the amount of heat radiation from the heat storage means at this time can be grasped, and the heat storage capacity may be set based on that.
In addition, when the temperature of the use-side refrigerant is maintained at a temperature suitable for the operation using the heating, the temperature drop during the defrosting operation can be obtained as about 10 [K] or less because the room is used for heating the room. In the case of using for heating, hot water supply, heating and drying of other spaces such as a greenhouse, it is necessary to set a predetermined temperature of the temperature decrease during the defrosting operation to another value and maintain the appropriate temperature. is there. Also, in the case of hot water supply or heating and drying, similarly to the heating, the temperature drop during the defrosting operation may be reduced to about 10 [K] or less to maintain a temperature suitable for hot water supply or heating and drying. If the temperature is preferably about 5 [K] or less, heat can be utilized without any trouble.
[0070]
In the configuration of FIG. 1, the refrigerant storage tank 20 is integrally housed inside the outdoor unit f, and the outdoor unit f becomes large, but the outdoor unit f and the indoor units g and h are assembled in advance and connected on site. It can be installed simply by connecting pipes, and has a construction with good workability that can prevent troubles in carrying in and construction.
Further, the refrigerant storage tank 20 does not necessarily have to be integrally housed inside the outdoor unit f. For example, as shown in FIG. 3, the first auxiliary heat exchanger 16 and the second auxiliary heat exchanger 19, the receiver 15, the refrigerant transport device 21, and the refrigerant storage tank 20 alone constitute a heat exchange unit d, The outdoor unit e of the standard heat pump may be connected to the refrigerant pipes m and m '. The refrigerant pipe m ′ is a connection pipe that connects between one end of the first auxiliary heat exchanger 16 and the four-way valve 12, and the refrigerant pipe m is connected to the other end of the first auxiliary heat exchanger 16. And a connection pipe for connecting between the receiver 15 and the refrigerant flow control valve 14. In this case, the outdoor unit of the heat pump of the standard specification can be used as it is, and an inexpensive refrigeration and air-conditioning apparatus can be obtained.
[0071]
Further, in the above description, the capacity of the refrigerant storage tank 20 is increased to increase the amount of refrigerant in order to reduce the temperature of the use-side refrigerant during the defrosting operation to a predetermined temperature or lower, but this is not a limitation. For example, by increasing the pipe diameter of the connection pipes i, i ', j, j', k, k ', if the amount of refrigerant in the use-side refrigerant cycle can be held the same as when the refrigerant storage tank 20 is added, this is the case. It may be substituted. If the inside diameter of the conventional connection pipes is all √2 times, the amount of refrigerant in the use-side refrigerant cycle becomes about twice as large as that of the conventional one, so that the temperature decrease of the use-side refrigerant during the defrosting operation is Since the heating operation is performed in a state where the temperature of the use-side refrigerant is suppressed to about half and the temperature of the use-side refrigerant is stable, the comfort of the indoor air conditioning (heating) is easily maintained. Further, even if all the conventional connection pipes are each two, the amount of refrigerant held in the use-side refrigerant cycle is approximately doubled.
[0072]
Further, the refrigerant storage tank 20 may be housed in a wall surface of a house. FIG. 4 shows the configuration in this case. The use-side refrigerant after heat exchange in the use-side heat exchangers 22 a and 22 b is stored in the refrigerant storage tank 20, the refrigerant is sucked from the bottom by the refrigerant transfer device 21, and sent out to the second auxiliary heat exchanger 19. The use-side refrigerant that has absorbed and dissipated heat in the second auxiliary heat exchanger 19 flows through the connection pipes i, j, and k to the use-side heat exchangers 22a and 22b, and is used for heating and cooling. The refrigerant storage tank 20 is housed inside a wall y of a building such as a house together with connection pipes i, j, k, and the like. In the example of FIG. 4, the refrigerant having a temperature relatively close to the indoor air temperature level after heat exchange in the use-side heat exchangers 22 a and 22 b is stored in the refrigerant storage tank 20. For this reason, it is somewhat difficult to maintain indoor comfort during the defrosting operation of the heat source side refrigerant cycle, but since the refrigerant storage tank 20 is integrally formed with the wall surface between the inner wall material and the outer wall material of the house, and is stored. There is no problem of installation space, and radiant air conditioning can be performed from the refrigerant in the refrigerant storage tank 20 to the room through the inner wall surface, thereby improving the comfort of indoor air conditioning. If one surface of the refrigerant storage tank 20 also serves as an inner wall, the radiation effect is further enhanced, and the comfort of the indoor air conditioning is further enhanced.
[0073]
Further, a configuration as shown in FIG. 5 may be used. In this case, the refrigerant storage tank 20 only needs to have a size corresponding to the refrigerant amount difference between the cooling operation and the heating operation in the outdoor unit f, and the second refrigerant storage tank 18 is installed on the wall surface of a building such as a house. In this configuration, the second refrigerant storage tank 18 is configured by a pressure-resistant closed pressure vessel made of, for example, iron, copper, or stainless steel.
Since the device shown in FIG. 5 absorbs and dissipates heat in the second auxiliary heat exchanger 19 to increase the difference between the room temperature and the air-conditioning capacity and stores the use-side refrigerant in the second refrigerant storage tank 18, the device shown in FIG. It is possible to more effectively maintain the indoor comfort during the defrosting operation than the configuration shown. Furthermore, the effect of radiation air conditioning from the refrigerant in the refrigerant storage tank 20 to the room through the inner wall surface can be expected. Further, if the usage-side refrigerant flows through the second refrigerant storage tank 18 from above to below, air will accumulate above and stay in the refrigerant circuit. However, in FIG. 5, the refrigerant flows upward from below in the second refrigerant storage tank 18. Even if air exists above the second refrigerant storage tank 18, the refrigerant flows out of the second refrigerant storage tank 18 with the flow of the refrigerant. As a result, the air is prevented from accumulating inside and adversely affecting the flow of the refrigerant.
It should be noted that the refrigerant storage tank 20 in FIG. 4 and the second refrigerant storage tank 18 in FIG. 5 may not be stored in the wall surface of the building, but may be stored under the floor of the building, on the roof, on the roof, in the basement, or the like. Needless to say.
[0074]
In FIGS. 1 and 3 to 5, the first temperature sensor 31 is installed in a pipe on the use side refrigerant outlet side of the second auxiliary heat exchanger 19, and the capacity of the heat source side refrigerant cycle is the first temperature sensor 31. Is controlled so that the detected temperature TH1 approaches a preset target temperature TM. For example, in the case of the cooling operation, the temperature difference ΔTH1 between the detected temperature TH1 of the first temperature sensor 31 and the target temperature TM is calculated by Expression (4).
ΔTH1 = TH1-TM (4)
The capacity of the heat source side refrigerant cycle is controlled by increasing and decreasing the operating frequency of the compressor 13 by an inverter by a frequency proportional to the value ΔTH1.
On the other hand, in the case of the heating operation, since the target temperature TM is set higher than the detected temperature TH1, the temperature difference ΔTH1 is calculated by the equation (5).
ΔTH1 = TM−TH1 (5)
The capacity of the heat source side refrigerant cycle is controlled by increasing and decreasing the operating frequency of the compressor 13 by an inverter by a frequency proportional to the value ΔTH1.
For example, the target value of the outlet temperature of the second auxiliary heat exchanger 19 may be TM = 7 [° C.] for the cooling operation, and TM = 50 [° C.] for the heating operation.
[0075]
When the capacity control of the compressor 11 can be performed only by the operation / stop, the upper limit TMH and the lower limit TML are set to the target temperature of the first temperature sensor 31, and the detected temperature TH1 of the first temperature sensor 31 is set to TMH and TML. The compressor 11 is operated / stopped so as to be in the middle.
For example, in the case of the cooling operation, TMH = 10 [° C.] and TML = 7 [° C.], the compressor 11 is operated when TH1 ≧ TMH, the compressor 11 is stopped when TH1 ≦ TML, and TML <TH1 < At the time of TMH, the operation is continued if the compressor 11 is operating, and is stopped if it is stopped.
In the case of the heating operation, TMH = 50 ° C. and TML = 47 ° C., the compressor 11 is stopped when TH1 ≧ TMH, the compressor 11 is operated when TH1 ≦ TML, and TML <TH1 < At the time of TMH, the operation is continued if the compressor 11 is operating, and is stopped if it is stopped.
[0076]
In the above, the case where the number of the use-side heat exchangers is two has been described. However, three or more use-side heat exchangers may be connected, or the number of the use-side heat exchangers may be one. In the case of a plurality of units, if all of them are connected in parallel with each other, each use-side heat exchanger can be controlled independently, so that it is easy to apply to the needs of the user and versatile. In addition, it is not necessary that all the units be in parallel. For example, as shown in FIG. 6, the use-side heat exchangers 22c and 22d are connected in series to the connection pipes l and l ', and each is a separate indoor unit. It may be housed in p and q together with the indoor blowers 24c and 24d. Also, the indoor units p and q connected in series do not necessarily need the use-side refrigerant flow control valves, and as shown in FIG. 6, for example, only the indoor unit p upstream of the flow of the use-side refrigerant has heat. It is only necessary that the valve 23c be connected. Conversely, the thermal valve 23c may be connected only to the indoor unit q on the downstream side of the flow of the use-side refrigerant.
[0077]
As for the indoor units p and q connected in series, the downstream heat exchanger 22d has a lower capacity than the upstream heat exchanger 22c, so that the upstream indoor unit p is, for example, a living room or a kitchen. Or the like, and the downstream indoor unit q may be properly used in a room with a small air conditioning load, such as a bedroom, a bathroom, a washroom, or a toilet. Also, even when both are installed in the same room and air-conditions the same space, for example, the upstream indoor unit p is installed near a window with a relatively large air-conditioning load, and the indoor unit q is located on the back side with a relatively small air-conditioning load. If installed, the temperature distribution near the window and the back side of a relatively large air-conditioned space can be improved, and the comfort in the air-conditioned room can be improved. Further, even in the case of being installed near the same window, if the upstream indoor unit p having the capacity is installed on the wall near the ceiling, and the downstream indoor unit q with the hard ability is installed on the wall on the floor or near the floor, the inside of the air-conditioned room may be reduced. The vertical temperature distribution can be improved to improve comfort.
[0078]
Further, the upstream heat exchanger 22c may be used for air conditioning, and the downstream heat exchanger 22d connected in series to the upstream heat exchanger 22c may be installed inside the floor. In this way, particularly during the heating operation, the floor can be further heated by the air-conditioned refrigerant whose temperature has been slightly lowered, so that the heat cascade can be used, and energy can be saved. The performance is improved. Further, the heat exchanger installed inside the floor may not necessarily be connected in series with the air-conditioning heat exchanger. For example, the heat exchanger 22a may be connected in parallel to a room installed for air-conditioning. May be installed inside the floor. With this configuration, the floor temperature and the air-conditioning temperature can be individually controlled, so that efficient operation can be performed. In addition, the usage-side heat exchanger is not limited to being used for air conditioning, but may be used for a load such as hot water supply. If a plurality of use-side heat exchangers are connected in series and used at various use temperatures, energy can be used without waste.
[0079]
It is desirable that the capacity of the heat source side refrigerant cycle of the refrigeration / air-conditioning apparatus according to the present embodiment, that is, the rated capacity, is equal to the total rated capacity of the indoor units g and h. Since it is rarely air-conditioned at the same time, it may be equal to or less than the total rated capacity of the indoor units g and h. By doing so, it is not necessary to have excessive equipment, and the refrigeration / air-conditioning apparatus can be supplied at a low price.
[0080]
In the heat source-side refrigerant cycle of the refrigeration / air-conditioning apparatus according to the present embodiment, the appropriate amount of refrigerant in the cooling operation for performing cooling is larger than that in the heating operation for performing heating. Accordingly, the refrigerant outlet side of the first auxiliary heat exchanger 16 during the heating operation and the lower port of the receiver 15 are connected to the refrigerant flow control valve 14, and the upper port thereof is connected to the refrigerant flow control valve 14 so that the refrigerant accumulates during the heating operation. It is connected. With such a connection, during the cooling operation, the gas-liquid two-phase refrigerant sent from the refrigerant flow control valve 14 flows in from the upper part and flows out from the lower part to the first auxiliary heat exchanger 16, so that the receiver 15 Liquid refrigerant does not accumulate inside. During the heating operation, on the contrary, the liquid refrigerant sent from the first auxiliary heat exchanger 16 is connected so as to flow in from the lower part and flow out from the upper part to the refrigerant flow control valve 14. Refrigerant pools. The internal volume of the receiver 15 is set to a value obtained by dividing the difference between the appropriate amounts of refrigerant in the cooling operation and the heating operation in the heat source side refrigerant cycle by the density of the liquid refrigerant stored in the heating operation. As described above, since the heat source side refrigerant cycle is operated with the appropriate amount of refrigerant in each of the cooling operation and the heating operation without excess or shortage, an efficient refrigeration / air-conditioning apparatus can be obtained.
However, it is not always necessary to provide the receiver 15. When the receiver 15 is not provided, the heat source side refrigerant is charged by an amount necessary for the cooling operation, and the efficiency is slightly reduced in the heating operation, but the operation is hindered. Nothing.
[0081]
As the integrally formed auxiliary heat exchangers 16 and 19 in the refrigeration / air-conditioning apparatus according to the present embodiment, a plate-type heat exchanger, a double-tube heat exchanger, or a multi-tube heat exchanger is used. The plate type heat exchanger is more expensive than other heat exchangers, but has a smaller pressure loss, so that the capacity (head) of the refrigerant transfer device 21 of the use-side refrigerant cycle may be smaller. Therefore, particularly when the refrigeration / air-conditioning apparatus according to the present embodiment is installed in a house, the distance from the outdoor unit f to the indoor units g and h is long and the pipes i, j, k, i ', j' and k 'are long. When the heat transfer cannot be made sufficiently thick, the use of a double-pipe heat exchanger results in shortage of the head of the refrigerant transfer device 21 with an inexpensive domestic pump, so that an expensive industrial pump must be used. In such a case, if a plate-type heat exchanger is used, an inexpensive domestic pump is sufficient as the refrigerant transfer device 21, and a comprehensively inexpensive refrigeration / air-conditioning device can be obtained.
Further, in the auxiliary heat exchangers 16 and 19, the flow direction of the refrigerant on the heat source side of the first auxiliary heat exchanger 16 is reversed in the cooling operation and the heating operation, but the flow direction of the refrigerant in the second auxiliary heat exchanger 19 is different. The flow direction of the refrigerant becomes the same in the cooling operation and the heating operation. In the conventional apparatus, the direction of the refrigerant is reversed during cooling and during heating, and a special refrigerant transfer device 21 is required and expensive, but in the present embodiment, the refrigerant transfer device 21 can be configured with a normal one. Inexpensive commercially available magnet pumps and the like can be used.
[0082]
When plate-type heat exchangers are used as the auxiliary heat exchangers 16 and 19, the connection of the heat-source-side refrigerant cycle is generally such that the inlet during cooling operation is lower and the outlet is higher. Therefore, during the heating operation, the inlet is on the upper side and the outlet is on the lower side. On the other hand, the connection of the use-side refrigerant cycle is such that the inlet is at the bottom and the outlet is at the top. Therefore, during the cooling operation, the flow is parallel, and during the heating operation, the flow is countercurrent. In general, it is preferable that the counter flow is formed in consideration of the heat exchange function, and the flow becomes parallel during the cooling operation. However, if the refrigerant of the heat source side refrigerant cycle is a single or pseudo azeotropic refrigerant such as R22 or R410A, for example. For example, the evaporation temperature slightly decreases from the inlet side to the outlet side due to the pressure loss in the first auxiliary heat exchanger 16, so that the temperature becomes close to the counterflow, and the heat source side refrigerant cycle is efficiently operated. it can.
In addition, even when the plate heat exchanger is used, the inlet of the heat source side refrigerant cycle during the cooling operation is up and the outlet is down, that is, contrary to FIG. 6, the inlet is down and the outlet is out during the heating operation. May be connected so as to face up. In this case, the connection of the use-side refrigerant cycle is such that the inlet is at the top and the outlet is at the bottom. With this configuration, the gas-liquid two-phase refrigerant that has flowed into the auxiliary heat exchanger 16 during the cooling operation is unlikely to accumulate, so that the difference between the appropriate amounts of refrigerant during the cooling operation and during the heating operation is reduced, and the internal volume of the receiver 15 is reduced. Therefore, an inexpensive refrigeration and air-conditioning apparatus can be obtained.
[0083]
Also, in FIGS. 1 and 3 to 6, the use-side refrigerant flow control valve 23 has been described as a thermal valve, but is not limited thereto, and may be another open / close valve such as a solenoid valve. Further, a flow control valve such as an electronic linear expansion valve (LEV) may be used. However, the use of a valve that can be opened and closed slowly, such as a thermal valve, eliminates water hammer and can reduce failures and noise.
In addition, an aqueous solution containing at least one of ethylene glycol, propylene glycol, D-sorbitol, and the like having antifreeze properties as a refrigerant of the use-side refrigerant cycle in a weight ratio of more than 0% and not more than several tens%. However, when used in an area where the outside air temperature does not fall below 0 [° C], or even when the outside air temperature falls below 0 [° C], the piping should be made of a material with good heat insulation properties, Water may be used if some other means is used, such as wrapping a heat insulator.
[0084]
Embodiment 2 FIG.
In the present embodiment, a configuration in which the heat source side refrigerant cycle has a plurality of systems, for example, one having two systems will be described.
Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 2 of the present invention, for example, a cooling / heating apparatus that cools a room by a cooling operation and heats a room by a heating operation will be described. . FIG. 7 is a configuration diagram illustrating a cooling and heating device according to the present embodiment. In the figure, the heat source side refrigerant cycle includes a first compressor 11a, a first flow path switching valve 12a, a first heat source side heat exchanger 13a, a first refrigerant flow control valve 14a, a first receiver 15a, A first heat source-side refrigerant cycle formed by connecting the first auxiliary heat exchanger 16a, a second compressor 11b, a second flow path switching valve 12b, a second heat source-side heat exchanger 13b, and a second heat source-side heat exchanger 13b. The refrigerant flow control valve 14b, the second receiver 15b, and the second auxiliary heat exchanger 16b are connected to form a second heat source side refrigerant cycle. The sum of the rated capacities, which are the capacities of the first and second heat source side refrigerant cycles, is set to be the same as the rated capacity of the heat source side refrigerant cycle of the first embodiment.
Reference numerals 32a and 32b denote pipe temperature detecting means provided at one end of the heat source side heat exchangers 13a and 13b of the first and second heat source side refrigerant cycles to detect the temperature of the heat source side refrigerant, for example, a pipe temperature sensor. It is.
[0085]
On the other hand, the use side refrigerant cycle includes the refrigerant transfer device 21, the connection pipe i, the connection pipes j and k, the use side refrigerant flow control valves 23a and 23b, the use side heat exchangers 22a and 22b, the connection pipes j 'and k', The connection pipe i ', the second auxiliary heat exchanger 19a, the fourth auxiliary heat exchanger 19b, and the refrigerant storage tank 20 are connected to each other. The connection pipe k, the use-side refrigerant flow control valve 23b, the use-side heat exchanger 22b, and the connection pipe k 'are the same as in the first embodiment, and the connection pipe j, the use-side refrigerant flow control valve 23a, and the use-side heat exchanger 22a , And a connection pipe j ′. Further, the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b are connected in parallel, and they are integrated so as to exchange heat with the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger 16b, respectively. Is formed.
[0086]
Next, the operation will be described.
During the cooling operation, both the first and second heat source side refrigerant cycles become the refrigerant cycle indicated by the solid line in the figure. In the heating operation, both the first and second heat source side refrigerant cycles are dashed refrigerant cycles in the drawing. The operations of the first and second heat-source-side refrigerant cycles are the same as those of the first embodiment in the cooling operation and the heating operation, and therefore will not be described.
On the other hand, in the use-side refrigerant cycle, in the cooling operation, the refrigerant sent to the refrigerant transfer device 21 through the refrigerant storage tank 20 passes through the connection pipes i, j, and k by the refrigerant transfer device 21 to use the heat of the use-side refrigerant. The air is sent to the exchangers 22a and 22b, cools the indoor air and is heated at the same time, and passes through the connection pipes j ′, k ′ and i ′ to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b. It is branched and sent. The refrigerant sent to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b passes through the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger 16b, and is subjected to the first and second heat source side refrigerant cycles. At the same time as radiating the heat to the outside air, it is cooled and returns to the refrigerant storage tank 20 after merging. In the case of the heating operation, the flow direction of the use-side refrigerant is the same, and the operation is the same, so that the description is omitted.
[0087]
The first temperature sensor 31 is installed on a pipe connecting between the use-side refrigerant outlet-side junction of the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19d and the refrigerant storage tank 20, and has a heat source side. The capacity of the refrigerant cycle is controlled such that the detected temperature TH1 of the first temperature sensor 31 approaches a preset target temperature TM. For example, in the case of the cooling operation, the temperature difference ΔTH1 between the detected temperature TH1 of the first temperature sensor 31 and the target temperature TM is calculated by Expression (6).
ΔTH1 = TH1-TM (6)
The capacity of the first and second heat source side refrigerant cycles is controlled by increasing and decreasing the operating frequencies of the first and second compressors 11a and 11b by an inverter by a frequency proportional to the calculated value.
On the other hand, in the case of the heating operation, the temperature difference ΔTH1 between the detected temperature TH1 of the first temperature sensor 31 and the target temperature TM is calculated by equation (7).
ΔTH1 = TM−TH1 (7)
The capacity of the first and second heat source side refrigerant cycles is controlled by increasing and decreasing the operating frequencies of the first and second compressors 11a and 11b by an inverter by a frequency proportional to the calculated value.
For example, the target value of the detection temperature of the first temperature sensor 31 is set to TM = 7 [° C.] in the cooling operation, and to TM = 50 [° C.] in the heating operation.
[0088]
The operating frequency of each of the compressors 11a and 11b may be increased or decreased by a frequency proportional to ΔTH1, but from the performance (input-capacity characteristic) of the compressor, the total COP of the two compressors = capacity [kW] / input [ The efficiency is further improved by selecting a combination of frequencies that maximizes [kW]. For example, as shown in FIG. 8, when the total operating frequency of the two compressors is set to the provisional frequency and the total capacity at that time is plotted on the horizontal axis, and the COP is plotted on the vertical axis, the frequency on the left side of position Z (Capacity) is the area where the COP is better in the operation of one compressor than in the operation of two compressors, and in the area where the frequency (capacity) on the right side of the position Z is higher than that of the operation of two compressors, one compressor is operated with the same frequency. This is an area where the COP is better than the operation. Actually, a switching area B is set between several Hz before and after the position Z, and one compressor is operated in an area A having a lower frequency (capacity), and two compressors are operated in an area C having a higher frequency (capability). In the region B, the compressor operation is not switched, and the number of operating units before that is continued.
[0089]
When the operating frequencies of the first and second compressors 11a and 11b are increased and decreased by a frequency proportional to ΔTH1, respectively, the total operating frequency (temporary frequency) F [Hz] of the two compressors or an increase or decrease value thereof ΔF [Hz] may be calculated as a function of ΔTH1, or may be set in advance as a numerical table for ΔTH1 and refer to the numerical table during operation.
[0090]
When only the operation / stop of the capacity control of the compressor in the first and second heat source side refrigerant cycles can be selected, the upper limit TMH and the lower limit TML are set to the target temperature of the first temperature sensor 31, and the first temperature sensor 31 is set. The compressors 11a and 11b in the first and second heat-source-side refrigerant cycles are operated / stopped such that the detected temperature TH1 falls between TMH and TML. This situation will be described with reference to FIG. 9 taking the case of the cooling operation as an example.
In FIG. 9, the horizontal axis represents the detected temperature TH1 of the first temperature sensor 31, and the vertical axis represents the increase / decrease in the number of operating compressors during the heat source-side refrigerant cycle. Assuming that TMH = 8.5 [° C.] and TML = 7 [° C.], one additional compressor is operated when TH1 ≧ TMH, and one compressor is stopped when TH1 ≦ TML, and TML <TH1 <TMH. At this time, the number of operating compressors is not changed. The same applies to the case of the heating operation, where TMH = 50 ° C. and TML = 48.5 ° C., one compressor is stopped when TH1 ≧ TMH, and the compressor is stopped when TH1 ≦ TML. When one additional unit is operated, and TML <TH1 <TMH, the number of operating compressors is not changed. As described above, the heat source side refrigerant cycle is configured to have two or more systems, and each compressor is operated / stopped one by one. The change in the temperature of the refrigerant can be kept within a small range, and the stability of the refrigerant temperature and, consequently, the comfort in the air-conditioned room are improved.
[0091]
Hereinafter, in a refrigeration air conditioner having a plurality of heat source side refrigerant cycles, during the heating operation, the first heat source side heat exchanger 13a of the first heat source side refrigerant cycle or the second heat source side refrigerant cycle of the second heat source side refrigerant cycle is sometimes used. Control when frost adheres to the heat source side heat exchanger 13b and the defrosting operation is performed will be described.
After the first heat source-side refrigerant cycle satisfies the defrosting operation start condition during the heating operation, and when the second heat source-side refrigerant cycle satisfies the defrosting operation start condition while the defrosting operation is being performed, The defrosting operation of the second heat source side refrigerant cycle is delayed until the first heat source side refrigerant cycle satisfies the defrosting operation end condition. The control operation of the control device 41 at this time is shown in the flowchart of FIG.
[0092]
First, in ST1, in the first and second heat source side refrigerant cycles, the first and second pipe temperatures are detected by the pipe temperature sensors 32a and 32b. In ST2, it is determined whether or not the second heat source side refrigerant cycle is in the defrosting operation, and if it is in the defrosting operation, it is determined whether or not the defrosting operation end condition is satisfied. That is, if the second pipe temperature is lower than 10 [° C.] in ST3, the defrosting operation still needs to be continued in the second heat source side refrigerant cycle, and thus the control process ends (END). If the second pipe temperature is equal to or higher than 10 ° C. in ST3, it is determined that the defrosting operation end condition is satisfied in the second heat source side refrigerant cycle, and the second heat source side refrigerant cycle is defrosted in ST4. To end. In this state, neither the first nor the second heat source side refrigerant cycle has entered the defrosting operation. Then, the first pipe temperature is checked in ST5. If the first pipe temperature is lower than, for example, −7 [° C.], it is determined that the defrosting operation start condition is satisfied, the first heat source side refrigerant cycle is set to the defrosting operation state (ST6), and the control process is ended. (END). If the first pipe temperature is −7 [° C.] or more, it is determined in ST7 whether the first heat source side refrigerant cycle is in a defrosting operation, and in the case of a defrosting operation, is the defrosting operation end condition satisfied? Judge whether or not. That is, if the second pipe temperature is lower than 10 [° C.] in ST8, the defrosting operation still needs to be continued in the first heat source side refrigerant cycle, and thus the control process ends (END). If the first pipe temperature is 10 [° C.] or more in ST8, it is determined that the first heat source side refrigerant cycle satisfies the defrosting operation end condition, and in ST9, the first heat source side refrigerant cycle is defrosted. To end. In this state, neither the first nor the second heat source side refrigerant cycle is in the defrosting operation. Then, the temperature of the second pipe is checked in ST10. When the second pipe temperature becomes lower than -7 [° C.], it is determined that the defrosting operation start condition is satisfied, and the second heat source side refrigerant cycle is set to the defrosting operation state in ST11, and the control process is ended ( END). This control process may be configured to be executed at predetermined time intervals, for example, in response to temperature detection once a minute.
[0093]
When the control is performed as described above, for example, during the heating operation, the first heat source-side refrigerant cycle is defrosted by detecting the detected temperature of the pipe temperature sensor 32a at −7 [° C.] in the first heat source-side refrigerant cycle. After the operation, in the second heat source side refrigerant cycle, if the detected value of the pipe temperature sensor 32b detects −7 [° C.], the control device 41 sets the pipe temperature in the first heat source side refrigerant cycle. Until the detection temperature of the sensor 32a becomes equal to or higher than 10 [° C.] and the defrost operation end condition is satisfied, the second heat source side refrigerant cycle does not perform the defrost operation and continues the heating operation. When the first heat source-side refrigerant cycle has finished defrosting, the first heat source-side refrigerant cycle returns to the heating operation, and starts the defrosting operation of the second heat source-side refrigerant cycle.
[0094]
By performing the defrosting operation of the heat source-side refrigerant cycle one by one in this manner, a decrease in the refrigerant temperature of the use-side refrigerant cycle is reduced, so that the temperature is maintained at a temperature suitable for using heat and the comfort in the air-conditioned room is improved. I do. In addition, since the decrease in the refrigerant temperature in the use-side refrigerant cycle is small compared to the case where the number of heat source-side refrigerant cycles is one, the refrigerant storage tank 20 can be made small, and the price of the entire system can be reduced. it can.
When there are three or more heat source-side refrigerant cycles, one or more of them may perform a defrosting operation, and at least one heat source-side refrigerant cycle continues a heating operation instead of a defrosting operation. If it is controlled to perform, the same effect as described above can be obtained.
In addition, if the heat source side refrigerant cycle is divided into a plurality of systems, a small and inexpensive standard heat pump can be used as it is or its components can be used, so that a more inexpensive refrigeration and air-conditioning apparatus can be obtained.
[0095]
When the first heat source-side refrigerant cycle is performing a defrosting operation and the second heat source-side refrigerant cycle is performing a heating operation, the control device 41 causes the detection value of the first temperature sensor 31 to approach the target value. The heating capacity of the second heat source side refrigerant cycle may be automatically controlled so as to increase. By increasing the heating capacity of the second heat source-side refrigerant cycle, the decrease in the refrigerant temperature of the use-side refrigerant cycle becomes smaller.
Furthermore, if there are three or more heat source-side refrigerant cycles, the refrigerant temperature of the use-side refrigerant cycle can be stabilized by shifting all the defrosting operation timings, and the comfort in the air-conditioned room can be maintained.
[0096]
Further, when either the first heat source side refrigerant cycle or the second heat source side refrigerant cycle satisfies the defrosting operation start condition, the first heat source side refrigerant cycle or the second heat source side before the defrosting operation starts. One or both of the refrigerant cycles may be operated at the maximum capacity to raise the refrigerant temperature of the use-side refrigerant cycle in advance. As a specific means, when either the first heat source side refrigerant cycle or the second heat source side refrigerant cycle satisfies the defrosting operation start condition, the merging outlets of the second and fourth auxiliary heat exchangers 19a and 19b. It is conceivable to raise the target temperature of the first temperature sensor 31 installed at TMU by TMU [° C.]. The temperature increment TMU may be any value, but is set to, for example, several [° C.]. At this time, the target temperature of the first temperature sensor 31 becomes TM + TMU [° C.], and the first heat source side refrigerant cycle performs the heating operation without performing the defrosting operation until the detection value TH1 of the first temperature sensor 31 reaches this temperature. The control is continuously performed by the control device 41 so as to start the defrosting operation after reaching the target temperature (TM + TMU [° C.]). Instead of raising the target temperature, the defrosting operation may be performed after the heating operation is performed at the maximum capacity for a certain period of time, for example, about several minutes.
[0097]
As described above, if the defrosting operation is performed after the refrigerant temperature of the use-side refrigerant cycle is increased, even if the amount of heat is deprived of the use-side refrigerant cycle by the defrosting operation, the comfort in the air-conditioned room can be maintained. it can. The target temperature increase TMU is, for example, about の of the temperature expected to decrease in the defrosting operation, and can prevent a person in the room from feeling uncomfortable to some extent. However, since the amount of increase in the target temperature varies depending on the environment and state of use, it cannot be said unconditionally, and the user may set an appropriate value.
In addition, the operating frequencies of the first and second compressors 11a and 11b during the first and second refrigerant cycles are directly increased, and for example, the total frequency of the first and second compressors 11a and 11b is increased. When the frequency is about 80 [Hz], the frequency increases to, for example, about 120 [Hz], and after a predetermined time, for example, about several minutes, the control device 41 controls the first heat source side refrigerant cycle to perform a defrosting operation. Is also good.
[0098]
The control of the defrosting operation in the refrigeration / air-conditioning apparatus having a plurality of heat source-side refrigerant cycles described above is performed in a refrigeration system without the refrigerant storage tank 20 in order to reduce a decrease in the temperature of the use-side refrigerant during the defrosting operation. It can also be applied to air conditioners. However, needless to say, if the refrigerant storage tank 20 is provided, the temperature of the use-side refrigerant can be further stabilized.
[0099]
Next, a control method for setting the capacity control stages of the first and second heat source side refrigerant cycles to several stages will be described.
In the case where the respective capacity control stages of the first and second heat source side refrigerant cycles are set to several stages, the target temperature of the first temperature sensor 31 is set to TM and detected at a certain sampling interval τ [h]. The capacity of the first and second heat-source-side refrigerant cycles is increased or decreased by one step so that the detected temperature TH1 of the first temperature sensor 31 falls near TM. FIG. 11 shows a block diagram.
ΔTH1 = TM−TH1 * (8)
And The superscript * indicates the predicted value of TH1 after τ [h] or 2τ [h]. For example, in the cooling operation, when ΔTH1> + α, the total capacity stage D of the heat source side refrigerant cycle is reduced by one stage, and when ΔTH1 <−α, the total capacity stage D of the heat source side refrigerant cycle is increased by one stage. The capacity control step is preferably set so that the rate of change to the total capacity (capacity) of the heat source side refrigerant cycles in the adjacent capacity control steps is substantially constant as shown in FIG.
[0100]
For example,
｛(Cooling capacity of stage 3) − (Cooling capacity of stage 2)｝ / (Cooling capacity of stage 2) ≒ ｛(Cooling capacity of stage 4) − (Cooling capacity of stage 3)｝ / (Cooling capacity of stage 3) )
Set as follows. In other words, the capacitance change width is set to increase as the capacitance increases, so that it is possible to follow a relatively large load fluctuation and a relatively small load fluctuation while suppressing hunting. Thus, the temperature stability of the use-side refrigerant is improved, and the comfort in the air-conditioned room is improved.
[0101]
Here, a setting method of the capacity control stage will be described. As described above, the capacity control stage is set such that the capacity change rate is constant regardless of the transition from any of the capacity control stages to the adjacent capacity control stage. Now, assuming that the number of capacity control stages is N, the maximum capacity is Qmax [kW], and the minimum capacity is Qmin [kW] (excluding the stopped state), the capacity change rate r for keeping the change rate of each stage constant Is obtained by Expression (9).
r N-1 = Qmax / Qmin (9)
That is, the (N-1) th root of the ratio between the maximum capacity and the minimum capacity is the capacity change rate r. Therefore, capacity control stage 1 is Qmin, 2 is Qmin × r, 3 is Qmin × r 2 ,..., The capacity control stage N is Qmin × r N = Qmax.
For example, taking FIG. 11 as an example, since Qmax = 8 [kW] and Qmin = 1 [kW] and the capacity control stage is N = 7, the capacity control change rate r = (8/1) 1/6 = 1.414. Therefore, if any capacity control stage can be set, capacity control stage 1 is 1 [kW], 2 is 1.414 [kW], 3 is 2.0 [kW], and 4 is 2.828. [KW], 5 is 4.0 [kW], 6 is 5.656 [kW], and 7 is 8.0 [kW].
[0102]
Actually, there are two heat source side refrigerant cycles, and it is difficult to realize them in three equal capacity control stages. Therefore, Qmax = 4 [ kW], Qmin = 1 [kW], and N = 3, r = (4/1) 1/2 = 2. That is, the capacity stage 1 is set to 1 [kW], 2 to 2 [kW], and 3 to 4 [kW], so that the two units are combined and set so that the operation of each heat source side refrigerant cycle is continued. . Here, the condition that the operation of the heat source side refrigerant cycle is continued means that, for example, in FIG. 11, the total capacity control stage 4 of the two units has a cooling capacity of 4 [kW]. It is conceivable that the two units are operated in the capacity control stage 2 and the two units are operated in the capacity control stage 2. However, in the former case, since the total capacity control stages 3 and 5 are two heat source side refrigerant cycles, when the total capacity control stages 3 to 4 and further from 4 to 5, the heat source side refrigerant is One of the cycles is stopped from operation and then restarted, so that the stability of the entire system is impaired. In addition, since the restart stop time (for example, 3 minutes) of the heat source side refrigerant cycle is set, the system is restarted. It takes more time, and there is a concern that the comfort in the air-conditioned room may be impaired. Therefore, it is better to adopt the latter.
When changing the stage of the total capacity in this way, if the change increases the stage of the total capacity, the currently operating heat source-side refrigerant cycle of the heat source-side refrigerant cycles of the plurality of systems remains operating. Is controlled to increase the total capacity. On the other hand, when the change decreases the stage of the total capacity, control is performed such that the currently stopped heat source-side refrigerant cycle of the plurality of heat source-side refrigerant cycles remains stopped to reduce the total capacity. Thus, when the stage of the total capacity is changed, the number of the heat source-side refrigerant cycles whose operation / stop state changes among the heat source-side refrigerant cycles of the plurality of systems can be minimized, and the stability of the entire system can be improved. It is possible to cope with a change in load while maintaining comfort in the air-conditioned room.
[0103]
As described above, the capacity control method in the refrigeration / air-conditioning apparatus including a plurality of heat source-side refrigerant cycles sets the change width of the total capacity of the heat source-side refrigerant cycle so as to increase as the total capacity increases. Therefore, it is possible to follow a large change in a relatively large load and a small change in a relatively small load while suppressing hunting, thereby improving the temperature stability of the use-side refrigerant and improving the comfort in the air-conditioned room.
Of course, even when the number of heat source side refrigerant cycles is one, the change rate of the capacity (capacity) to the next stage is set to be substantially constant, that is, the capacity change width increases as the capacity increases. With this setting, it is possible to follow any load fluctuation while suppressing hunting, and to perform cooling or heating operation in a state where the temperature of the use-side refrigerant is stable.
[0104]
In the present embodiment, the example in which the number of the heat source side refrigerant cycles is two has been described, but the number of the heat source side refrigerant cycles may be three or more. If it is composed of a plurality of heat source side refrigerant cycles, one of the heat source side refrigerant cycles may have a small capacity, and if a standard vapor compression refrigeration cycle is used for this, a refrigeration / air-conditioning apparatus can be constructed at low cost. Further, it is desirable to connect all of the plurality of heat source side refrigerant cycles in parallel as in the present embodiment, since each can be controlled independently, but a part or all of them may be connected in series. When connected in series, the utilization-side refrigerant heated or cooled in the upstream refrigerant cycle is further heated or cooled in the downstream refrigerant cycle, and the efficiency of the downstream refrigerant cycle is slightly reduced. In addition, a simple and inexpensive refrigeration / air-conditioning apparatus can be obtained without branching the connection of the use side refrigerant.
[0105]
The capacity control in the refrigeration / air-conditioning apparatus having a plurality of or one heat source-side refrigerant cycle described above is performed in a refrigeration system without the refrigerant storage tank 20 in order to reduce the temperature drop of the use-side refrigerant during the defrosting operation. It can also be applied to air conditioners. However, needless to say, if the refrigerant storage tank 20 is provided, the temperature of the use-side refrigerant can be further stabilized.
[0106]
Embodiment 3 FIG.
Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 3 of the present invention, for example, a cooling / heating apparatus that cools a room by a cooling operation and heats a room by a heating operation will be described, and the cooling operation will be described as a cooling operation and the heating operation will be described as a heating operation. . FIG. 12 is a configuration diagram illustrating a cooling and heating device according to the present embodiment. In the figure, the heat source side refrigerant cycle includes a first compressor 11a, a first flow path switching valve 12a, a first heat source side heat exchanger 13a, a first refrigerant flow control valve 14a, a first receiver 15a, A first heat source-side refrigerant cycle formed by connecting the first auxiliary heat exchanger 16a, a second compressor 11b, a second flow path switching valve 12b, a second heat source-side heat exchanger 13b, and a second heat source-side heat exchanger 13b. The refrigerant flow control valve 14b, the second receiver 15b, and the second auxiliary heat exchanger 16b are connected to form a second heat source side refrigerant cycle. The sum of the capacity (rated capacity) of these first and second heat source-side refrigerant cycles is the same as the capacity (rated capacity) of the heat source-side refrigerant cycle of the first embodiment, which is a heat source-side refrigerant cycle composed of one system. is there.
[0107]
On the other hand, the use-side refrigerant cycle includes the first refrigerant transfer device 21, the connection pipe i, the connection pipes j and k, the use-side refrigerant flow control valves 23a and 23b, the use-side heat exchangers 22a and 22b, and the connection pipes j 'and k ′, a connecting pipe i ′, a first use-side refrigerant cycle formed by connecting the refrigerant storage tank 20, a second refrigerant transfer device 25, a second auxiliary heat exchanger 19a, a fourth auxiliary heat exchanger 19b, And a second usage-side refrigerant cycle formed by connecting the refrigerant storage tanks 20. The connection pipe k, the use-side refrigerant flow control valve 23b, the use-side heat exchanger 22b, and the connection pipe k 'are the same as in the first embodiment, and the connection pipe j, the use-side refrigerant flow control valve 23a, and the use-side heat exchanger 22a , And a connection pipe j ′. Further, the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b are connected in parallel similarly to the second embodiment, and these are respectively the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger. 16b is formed integrally so as to exchange heat.
In the second use-side refrigerant cycle, the use-side refrigerant is circulated and exchanges heat with the first and third auxiliary heat exchangers 16a and 16b in the second and fourth auxiliary heat exchangers 19a and 19b, respectively, to store the refrigerant. A heat transport cycle for storing heat in the tank 20 is configured.
[0108]
Further, the compressor 11a, the flow path switching valve 12a, the first heat source side heat exchanger 13a, and the first refrigerant flow control valve 14a are housed in the first outdoor unit e, and the compressor 11b, the flow path switching The valve 12b, the first heat source side heat exchanger 13b, and the first refrigerant flow control valve 14b are housed in the second outdoor unit e '. These use standard outdoor units such as home air conditioners. Furthermore, the first refrigerant transfer device 21, the second refrigerant transfer device 25, the integrated first auxiliary heat exchanger 16a and the second auxiliary heat exchanger 19a, and the integrated third auxiliary heat exchanger 16b The fourth auxiliary heat exchanger 19b, the refrigerant storage tank 20, and the first and second receivers 15a and 15b are housed in the heat exchange unit d.
[0109]
The first heat source side refrigerant cycle is performed between the fourth port of the flow path switching valve 12a in the first outdoor unit e and one end of the first auxiliary heat exchanger 16a in the heat exchange unit d, and Between the refrigerant flow control valve 14a in the outdoor unit e and the first receiver 15a connected to the other end of the first auxiliary heat exchanger 16a in the heat exchange unit d. m. Similarly, the second heat source side refrigerant cycle is performed between the fourth port of the flow path switching valve 12b in the second outdoor unit e ′ and one end of the third auxiliary heat exchanger 16b in the heat exchange unit d. And a connection between the refrigerant flow control valve 14b in the second outdoor unit e 'and the second receiver 15b connected to the other end of the third auxiliary heat exchanger 16b in the heat exchange unit d. They are connected by pipes n 'and n.
[0110]
The refrigerant storage tank 20 is internally divided into two left and right tanks by a partition 27 in the vertical direction from the uppermost portion. The partition 27 is partially open just above or below the bottom surface of the refrigerant storage tank 20 so that the two left-hand and right-hand use-side refrigerants 30 communicate with each other. Furthermore, the upper part of the refrigerant storage tank 20 is open to the atmosphere, and absorbs the volume expansion of the use-side refrigerant 30. Further, one end of the connection pipe s is open at an outlet at the bottom of the left tank of the refrigerant storage tank 20, and the other end is connected to the suction port of the refrigerant transfer device 21. One end of the connection pipe t is open at the outlet at the bottom of the right tank of the refrigerant storage tank 20, and the other end is connected to the suction port of the refrigerant transport device 25. One end of the connection pipe r is open at the inflow port on the upper side surface of the left tank of the refrigerant storage tank 20, and the other end is connected to the outlet side of the second and fourth auxiliary heat exchangers 19a and 19b. ing. Further, the connection pipe i ′ passes through an inflow port on the upper side surface of the right tank of the refrigerant storage tank 20, one end of which is opened inside a filter 26 set in the refrigerant storage tank, and the other end is connected. The connection pipes j ′ and k ′ are connected to the outlet side. All the connection pipes r, s, t, and i ′ open below the draft surface of the use-side refrigerant 30 in the refrigerant storage tank 20.
[0111]
Next, the operation will be described.
During the cooling operation, both the first and second heat source side refrigerant cycles become the refrigerant cycle indicated by the solid line in the figure. In the heating operation, both the first and second heat source side refrigerant cycles are dashed refrigerant cycles in the drawing. The operation of the heat-source-side refrigerant cycle is the same as in the first embodiment at the time of the cooling operation and the heating operation, and therefore will not be described.
[0112]
In the second use-side refrigerant cycle, the use-side refrigerant 30 flowing out of the bottom of the tank on the right side of the refrigerant storage tank 20 passes through the connection pipe t, and the second auxiliary heat exchanger 19a and the second auxiliary heat exchanger 19a It branches and is sent to 4 auxiliary heat exchangers 19b. The use side refrigerant 30 sent to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b passes through the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger 16b, and the first and second heat source sides. At the same time as the heat is radiated to the outside air by the refrigerant cycle, the refrigerant itself is cooled, merges with the connection pipe r, and returns to the left tank of the refrigerant storage tank 20. In the case of the heating operation, the operation is the same, so that it is omitted.
With this second use-side refrigerant cycle, hot or cold heat generated in the first and second heat source-side refrigerant cycles is transported to the refrigerant storage tank 20 and stored therein.
[0113]
On the other hand, in the first usage-side refrigerant cycle, the usage-side refrigerant 30 flowing out from the bottom of the left tank of the refrigerant storage tank 20 passes through the connection pipe s and is connected by the first refrigerant transfer device 21 to the connection pipes i, j, and k. Through the heat exchangers 22a and 22b. The use side heat exchangers 22a and 22b exchange heat with the indoor air sent by the indoor blowers 24a and 24b to cool the room in the case of the cooling operation and to heat the room at the same time in the case of the heating operation. As it heats, it cools itself. After that, it returns to the tank on the right side of the refrigerant storage tank 20 through the connection pipes j ′, k ′ and i ′.
As described above, in the first usage-side refrigerant cycle, the heat or cold stored in the refrigerant storage tank 20 is used for the load by the heat exchangers 22a and 22b by circulating the usage-side refrigerant 30.
At this time, the air volume of the indoor blowers 24a and 24b depends on the temperature difference between the target set value of the indoor air temperature set by the occupant and the actual temperature of the indoor air detected by the temperature sensors 35a and 35b. Set to change several steps or continuously.
[0114]
In the present embodiment, the use-side refrigerant cycle includes a first use-side refrigerant unit that circulates through the indoor units g and h and a second use-side refrigerant cycle that performs heat transport. The circulation amount of the refrigerant flowing through the first usage-side refrigerant cycle changes by opening and closing the usage-side refrigerant flow control valves 23a and 23b according to the operation / stop of the indoor units g and h. However, the circulation of the refrigerant flowing through the second usage-side refrigerant cycle is independent of the circulation of the refrigerant flowing through the first usage-side refrigerant cycle, and even if the refrigerant circulation amount of the first usage-side refrigerant cycle changes. , Is kept substantially constant by the second refrigerant transport device 25. Accordingly, the operation state of the heat source side refrigerant cycle is easily stabilized, and the outlet temperatures of the second and fourth auxiliary heat exchangers 19a and 19b, and thus the temperature of the refrigerant flowing into the use side heat exchangers 22a and 22b are also stable. Therefore, it is easy to stabilize the temperature control of the indoor air-conditioned space and maintain comfort.
[0115]
In addition, it has a refrigerant transport device 21 that transports the refrigerant to the use side heat exchanger, and a refrigerant transport device 25 that transports the refrigerant to the second and fourth auxiliary heat exchangers 19a and 19b. It can be controlled. Therefore, for example, during the heating operation, the heat source-side refrigerant cycle starts the defrosting operation, and when the temperature of the use-side refrigerant decreases, the refrigerant transfer device 21 is stopped so that the low-temperature refrigerant does not flow into the use-side heat exchanger. Can be The operation of the first usage-side refrigerant cycle can be maintained as it is, and it is easy to maintain indoor comfort. In particular, since the heat-source-side refrigerant cycle is normally controlled so as not to be restarted until a certain time has elapsed after being once stopped, in such a case, the refrigerant transfer device 21 is kept stopped while the refrigerant transfer device 25 is stopped. By driving the air conditioner, the room can be air-conditioned for a predetermined time by the heat stored in the refrigerant storage tank 20.
[0116]
Here, the filter 26 is formed, for example, in a cylindrical shape, and the bottom surface thereof is also formed in a mesh shape. The roughness of the mesh between the cylindrical side surface and the bottom surface is desirably uniform, but if it is finer than a certain degree, the bottom surface may be coarser than the side surface, or conversely, the side surface may be coarser than the bottom surface. The filter 26 also serves as a spout for the use-side refrigerant 30, and its upper surface is a lid, and is filled with the use-side refrigerant 30 during the period from when the refrigeration / air-conditioning apparatus according to the present embodiment is installed to when it is operated. Then, the lid is opened, and the use-side refrigerant 30 is poured into the inside of the filter from the upper surface of the cylindrical filter. At this time, the filter 26 prevents dirt, dust, and the like, which are contaminants mixed in the refrigerant storage tank 20 at the same time as the refrigerant 30 is poured, from being mixed in the use-side refrigerant cycle. Further, a connection pipe i ′ is connected to the inside of the filter 26, and collects contaminants such as dirt and dust due to corrosion, abrasion, etc. of the pipes and heat exchangers in the use-side refrigerant cycle together with the circulation of the use-side refrigerant. This makes it possible to remove the refrigerant from the use-side refrigerant cycle. If foreign matter enters the use-side refrigerant cycle and circulates through the use-side refrigerant cycle, the refrigerant transfer devices 25 and 21 may fail, and the second and fourth auxiliary heat exchangers 19a and 19b and the use-side heat exchangers 22a and 22a. As a result, the reliability of the entire system is reduced due to the clogging of the 22b and a decrease in the heat transfer performance. Providing the filter 26 has the effect of preventing the occurrence of these inconveniences and improving reliability.
[0117]
In addition, the installation place of the filter 26 is not limited to the refrigerant storage tank 20, and if one is provided somewhere in the piping of the use-side refrigerant cycle, the contaminants are collected when the filter 26 circulates, Prevents refuse from circulating downstream. In particular, by providing an upstream pipe at the entrance of the second and fourth auxiliary heat exchangers 19a and 19b, it is possible to prevent contaminants from flowing into the second and fourth auxiliary heat exchangers 19a and 19b. .
Further, when the filter 26 is provided in the refrigerant storage tank 20, since the refrigerant storage tank 20 has the opening for pouring the refrigerant as described above, the filter 26 can be replaced or the collected contaminants can be removed. It is easy and easy to manage.
In the refrigerant storage tank 20, it may be provided at least in the middle of the flow of the use-side refrigerant from at least one of the inlet to the outlet, and may be provided, for example, near the outlet. However, if the filter 26 is provided above the refrigerant storage tank 20 as shown in FIG. 12, it is possible to easily remove the dust and the like caught on the filter 26, and it is also easy to handle when the filter 26 is replaced or washed.
[0118]
The refrigerant storage tank 20 is divided into two tanks on the left and right sides by a partition 27 partly communicating with the tank. One of the divided tanks such as the right tank is provided with an opening through which the use-side refrigerant flows from the use-side heat exchangers 22a and 22b, and the other tank such as the left tank is provided with the use-side heat exchangers 22a and 22b. An opening through which the use-side refrigerant flows out is provided. Further, an opening through which the use-side refrigerant flows out to the second and fourth auxiliary heat exchangers 19a and 19b is provided in the right tank provided with an opening through which the use-side refrigerant flows from the use-side heat exchangers 22a and 22b. An opening through which the use-side refrigerant flows from the second and fourth auxiliary heat exchangers 19a and 19b is provided in the left tank provided with an opening through which the use-side refrigerant flows out to the use-side heat exchangers 22a and 22b. Is provided. In the present embodiment, two openings serving as inlets are provided above the refrigerant storage tank 20, and two openings serving as outlets are provided at the bottom.
More specifically, the connection pipe r is below the upper draft of the left tank of the refrigerant storage tank 20, the connection pipe s is on the bottom of the left tank of the refrigerant storage tank 20, and the connection pipe t is on the bottom of the right tank of the refrigerant storage tank 20. The connection pipe i ′ is opened below the upper draft of the right tank of the refrigerant storage tank 20 and inside the filter 26.
[0119]
In this configuration, for example, during the heating operation, in the second use-side refrigerant cycle, the use-side refrigerant having a high temperature of about 50 ° C. flowing out of the second and fourth auxiliary heat exchangers 19a and 19b flows from the upper portion of the left tank. Then, the use-side refrigerant 30 in the refrigerant storage tank 20 flows out from the bottom surface of the right tank. For this reason, the refrigerant having a high temperature and a small specific gravity starts to accumulate from the upper portion of the left tank, and the high-temperature refrigerant accumulates to the lower portion over time with time. As described above, the left tank forms a temperature stratification above and below without mixing the internal refrigerant, and can store heat while expanding a high-temperature region with time. At this time, the inlet temperature of the connection pipe t to which the suction port of the second refrigerant transfer device 25 that sends the refrigerant to the second and fourth auxiliary heat exchangers 19a and 19b is hardly increased, and the second utilization Since the low-temperature refrigerant in the refrigerant storage tank 20 is taken out and heat-exchanged in the side refrigerant cycle, the heat source-side refrigerant cycle can be operated efficiently, and heat can be sufficiently stored in the left tank of the refrigerant storage tank 20. In the first use-side refrigerant cycle, high-temperature refrigerant is circulated from the bottom of the left tank and is used in the use-side heat exchangers 22a and 22b. In particular, the effect of instantly starting heating in winter can be obtained. is there.
Further, even during cooling, the refrigerant in the left tank in the refrigerant storage tank 20 can be kept at a relatively lower temperature than the refrigerant in the right tank, so that cooling can be started quickly in summer.
[0120]
Further, the connection between the refrigerant storage tank 20 and the first and second usage-side refrigerant cycles may be configured as shown in FIG. 12 during the heating operation, and may be switched so as to be upside down during the cooling operation. That is, the connection pipe r of the second usage-side refrigerant cycle is connected to the bottom of the tank on the left side of the refrigerant storage tank 20, and the low-temperature usage side after exchanging heat with the second and fourth auxiliary heat exchangers 19a and 19b. The refrigerant 30 flows from below. Then, the refrigerant is discharged from above the left tank of the refrigerant storage tank 20 to the first use-side refrigerant cycle through the connection pipe s. Further, the connection pipe i ′ of the first usage-side refrigerant cycle is connected to the bottom of the tank on the right side of the refrigerant storage tank 20, and the usage-side refrigerant 30 flowing out of the usage-side heat exchangers 22 a and 22 b is connected to the refrigerant storage tank 20. Flow into the bottom of the right tank. Further, the refrigerant is discharged from above the tank on the right side of the refrigerant storage tank 20 to the second use-side refrigerant cycle through the connection pipe t.
[0121]
As described above, when the inlet and the outlet are switched up and down, during the cooling operation, for example, about 7 [° C.] flowing out of the second and fourth auxiliary heat exchangers 19a and 19b in the second usage-side refrigerant cycle. The low-temperature refrigerant flows into the bottom of the left tank, and the usage-side refrigerant 30 in the refrigerant storage tank 20 flows out from the upper part of the right tank. For this reason, a low-temperature refrigerant having a large specific gravity starts to accumulate from the bottom of the left tank, and the low-temperature refrigerant accumulates in the left tank to the top with time. As described above, the left tank forms a temperature stratification above and below without mixing the refrigerant therein, and can store heat while expanding a low-temperature region with time. At this time, the temperature of the refrigerant above the right tank connected to the suction port of the second refrigerant transfer device 25 that sends the refrigerant to the second and fourth auxiliary heat exchangers 19a and 19b hardly fluctuates. Since the high-temperature refrigerant in the refrigerant storage tank 20 is taken out and heat-exchanged in the use-side refrigerant cycle, the heat-source-side refrigerant cycle can be operated efficiently, and heat can be sufficiently stored in the left tank of the refrigerant storage tank 20. Further, in the first use-side refrigerant cycle, low-temperature refrigerant is circulated from the upper portion of the left tank and is used in the use-side heat exchangers 22a and 22b. is there.
When the configuration is such that the inlet and the outlet of the refrigerant storage tank 20 are switched in this manner, the filter 26 extends from the upper portion to the lower portion, and in both heating and cooling, the refrigerant of the first use-side refrigerant cycle is used. It is arranged at the inlet from the pipe i '.
[0122]
In order to switch the inflow port and the outflow port, for example, in the case of the left tank, two connection pipes connecting the connection pipe r and the connection pipe s are provided so as to intersect each other without intersecting each other. An open / close valve for switching the refrigerant flow path may be provided in each of the two pipes, and an open / close valve may be provided between the connection pipe r and the connection pipe s between the branch points to the two pipes. When the on-off valves provided on the connection pipes s and t are opened during the heating operation and the on-off valves provided on the two pipes are both closed, the configuration becomes the same as that of FIG. When the cooling operation is performed, the on-off valves provided on the connection pipes s and t are closed, and the on-off valves provided on the two pipes are both opened. And the outlet sides of the second and fourth auxiliary heat exchangers 19a and 19b are connected to the bottom opening, so that the outlet and the inlet can be turned upside down in the heating operation.
The same applies to the opening of the right tank. If two connection pipes and an on-off valve are similarly provided in the connection pipe t and the connection pipe i ', the outlet and the inlet can be reversed up and down.
However, the means for switching the inlet and outlet between the heating operation and the cooling operation is not limited to this, and another method may be used.
[0123]
In the present embodiment, since the inside of the refrigerant storage tank 20 is partitioned by the partition 27 partly communicating therewith, in the normal operation state, the discharged refrigerant circulation of the first refrigerant transfer device 21 and the second refrigerant transfer device 25 is performed. The direction of the flow of the refrigerant in the communicating portion is determined by the difference in the amount of the discharged refrigerant circulation. For example, when many of the indoor units are operating and the discharged refrigerant circulation amount of the first refrigerant transfer device 21 is larger than that of the second refrigerant transfer device 25, the refrigerant flows to the left through the communication portion. Conversely, when many of the indoor units are stopped and the discharged refrigerant circulation amount of the first refrigerant transport device 21 is smaller than that of the second refrigerant transport device 25, the refrigerant flows rightward through the communicating portion. Flows to In the operation / stop state of the intermediate indoor unit, the discharge refrigerant circulation amount of the first refrigerant transfer device 21 and the discharge refrigerant circulation amount of the second refrigerant transfer device 25 may be substantially the same. In such a case, the flow rate of the refrigerant in the communication portion of the partition 27 in the refrigerant storage tank 20 is almost 0, and the use-side refrigerant cycle is performed by the use-side heat exchangers 22a and 22b and the second and fourth auxiliary heat exchangers 19a and 19a. 19b is directly connected, and the refrigerant cycle is substantially the same as that of FIG.
The communication position of the partition 27 may be anywhere in the vertical direction of the refrigerant storage tank 20. In the case of the arrangement of the inflow port and the outflow port as shown in FIG. 12, the partition can be moved so that the right tank and the left tank communicate with each other at the time of heating and the right tank and the left tank communicate with each other at the time of cooling. It may be configured. The movement of the partition 27 may be performed manually, for example, or the communication portion may be moved by a motor or an electromagnetic valve.
[0124]
Further, in the present embodiment, the two tanks formed by the partitions 27 in the refrigerant storage tank 20 are closer to the volume of the left tank provided with the outlet to the suction port of the first refrigerant transfer device 21. However, the volume is larger than the volume of the right tank provided with the outlet to the suction port of the second refrigerant transport device 25. With such a configuration, the return refrigerant from the use-side heat exchangers 22a and 22b, which have a lower temperature during the heating operation and a higher temperature during the cooling operation, do not remain in the refrigerant storage tank 20, and the second and fourth auxiliary fluids smoothly. Since the refrigerant flows into the heat exchangers 19a and 19b, the efficiency of the heat source side refrigerant cycle can be easily maintained at a high level.
[0125]
The first temperature sensor 31 is provided on a connection pipe r that connects between the use-side refrigerant outlet-side junction of the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19d and the refrigerant storage tank 20. The pipe temperature sensors 32a and 32b for detecting the temperature of the heat source side refrigerant are provided on the inlet side of the heat source side heat exchangers 13a and 13b of the first and second heat source side refrigerant cycles. 33 is a second temperature detecting means provided on the inlet side of the use side heat exchangers 22a and 22b, for example, a second temperature sensor, 34 is an outside air temperature detecting means, for example, an outside air temperature sensor, and 35a, 35b are indoor units g, h, a temperature sensor for detecting, for example, the temperature in the air-conditioned room; 36, a third temperature detecting means provided on the outlet side of the use-side heat exchangers 22a, 22b, for example, a third temperature sensor; is there.
The capacity of the heat source side refrigerant cycle is controlled so that the detected temperature TH1 of the first temperature sensor 31 approaches a preset target temperature TM. For example, in the case of the cooling operation, the temperature difference between the detected temperature TH1 of the first temperature sensor 31 and the target temperature TM
ΔTH1 = TH1-TM (10)
Is calculated by a calculation unit in the control device 41, and this value is converted into a temperature difference code such as a hexadecimal number and transmitted to the outdoor units e and e '. If the outdoor units e and e ′ are configured with standard specifications such as a home air conditioner, the temperature difference code sent from the heat exchange unit d is compared with the room temperature set value sent from a normal indoor unit and the actual indoor unit. (Suction) Treated in the same manner as a temperature difference code created from the difference with the air temperature, and the control devices 42a and 42b installed in the first and second outdoor units e and e 'are used to control the compressors 11a and 11b and the refrigerant flow rate. The control valves 14a and 14b are controlled.
[0126]
On the other hand, in the case of heating operation,
ΔTH1 = TM−TH1 (11)
Is calculated by a calculation unit inside the control device 41, and this value is converted into a temperature difference code such as a hexadecimal number and transmitted to the outdoor units e and e ′. According to this value, the control devices 42a and 42b make the compressors 11a and 11b And controls the refrigerant flow control valves 14a and 14b.
[0127]
Further, in the present embodiment, the target value of the detected temperature of the first temperature sensor 31 is basically TM = 7 [° C.] for the cooling operation and TM = 50 [° C.] for the heating operation, It changes according to the temperature detected by the sensor 34. For example, during the cooling operation, if the detected value of the outside air temperature sensor 34 is less than 25 [° C.], the target value TM of the detected temperature of the first temperature sensor 31 is set to 10 [° C.]. In addition, during the heating operation, if the detected value of the outside air temperature sensor 34 is 10 [° C.] or more, the target value TM of the detected temperature of the first temperature sensor 31 is set to 45 [° C.]. As described above, when the difference between the outside air temperature and the air-conditioning room temperature set value is small, the target value of the first temperature sensor 31 is changed in a direction in which the difference between the air-conditioning room temperature set value and the heat source side refrigerant cycle is reduced. Refrigeration and air conditioning can be obtained efficiently and with low energy consumption.
[0128]
Further, the target temperature TM of the first temperature sensor 31 may be changed according to not only the detection value of the outside air temperature sensor 34 but also the number of operating indoor units, the air conditioning set temperature of each indoor unit, the operation mode, and the like. For example, when two indoor units are connected, and during heating operation, when one set temperature is 20 [° C] and the other is set temperature 24 [° C], TM = 48 [° C] and both are set. If the temperature is 24 [° C], TM = 50 [° C], if both units have a set temperature of 22 [° C], TM = 47 [° C], and if both units have a set temperature of 20 [° C], TM = 45 [° C] ° C]. Also, during cooling operation, if both of the two units have a set temperature of 26 [° C], TM = 7 [° C], one unit has a set temperature of 26 [° C], and the other unit has a dry mode of TM = 9 [° C]. And so on. In addition, when one set is at a set temperature of 26 [° C.] and the other is stopped, TM = 8 [° C.] or the like.
Further, a third temperature sensor 36 may be installed in the connection pipe i ′, and the target value of the first temperature sensor 31 may be changed according to the detected value. For example, during the cooling operation, if the detection value of the second temperature sensor 33 is 7 [° C.] and the detection value of the third temperature sensor is 13 [° C.], the target value of the first temperature sensor is TM = 7 [° C.] If the detection value of the second temperature sensor 33 is 7 [° C.] and the detection value of the third temperature sensor is 12 [° C.], the target value of the first temperature sensor is changed to TM = 8 [° C.] I do.
[0129]
In the present embodiment, the first and second outdoor units e and e 'can use an outdoor unit of a standard heat pump, and have an advantage that a refrigeration / air-conditioning apparatus can be configured at low cost. Further, the heat exchange unit d may be configured as an outdoor unit integrated with the first and second outdoor units e and e 'without being separated. If these are integrally configured, labor for carrying in and construction can be saved, construction costs can be saved, and it goes without saying that the appearance and appearance of the house are not impaired.
[0130]
Further, in the piping of the usage-side refrigerant cycle, the sending-side piping (i, j, k) to the usage-side heat exchanger and the return-side piping (i ′, j ′, k ′) from the usage-side heat exchanger. The pipe diameters should be different. In this way, at the time of pipe connection work, for example, the feed pipe i is erroneously connected to the return pipe j ′ at the branch point from the feed pipe i to the feed pipes j and k, so that the use side heat exchange is performed. It is possible to prevent a trouble that the refrigerant does not circulate in the vessel and air conditioning cannot be performed. Furthermore, it is preferable that the connecting portions on the outlet side of the use side heat exchangers 22a and 22b and the inlet side of the use side refrigerant flow control valves 23a and 23b have different inner or outer diameters. Also, instead of making the pipe diameter different, it is the same even if the shape and size of the joint connecting the pipes are made different, so that mistakes in connection during pipe connection work etc. are prevented. And a highly reliable refrigeration / air-conditioning apparatus can be obtained.
[0131]
Embodiment 4 FIG.
Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 4 of the present invention, for example, a cooling / heating apparatus that cools a room by a cooling operation and heats a room by a heating operation will be described, and the cooling operation will be described as a cooling operation and the heating operation will be described as a heating operation. . FIG. 13 is a configuration diagram illustrating a cooling and heating device according to the present embodiment. In the figure, a heat source side refrigerant cycle includes a first compressor 11a, a first flow path switching valve 12a, a first heat source side heat exchanger 13a, a first refrigerant flow control valve 14a, a first receiver 15a, A first heat source-side refrigerant cycle formed by connecting the first auxiliary heat exchanger 16a, a second compressor 11b, a second flow path switching valve 12b, a second heat source-side heat exchanger 13b, and a second heat source-side heat exchanger 13b. A second heat source side refrigerant cycle in which the refrigerant flow control valve 14b, the second receiver 15b, and the third auxiliary heat exchanger 16b are connected, a third refrigerant transfer device 28, a heating boiler 29, and a fifth auxiliary heat And a third heat source side refrigerant cycle connected to the exchanger 16c. The sum of the capacity (rated capacity) of the first and second heat source side refrigerant cycles is set to be the same as the capacity (rated capacity) of the heat source side refrigerant cycle of the first embodiment. The third heat-source-side refrigerant cycle is dedicated to heating, and is set to have a capacity such that only one of the three heat source-side refrigerant cycles can exhibit the required heating capacity.
[0132]
Further, the third heat source-side refrigerant cycle dedicated to heating is, compared to the first and second heat source-side refrigerant cycles, which are cooling / heating refrigerant cycles, with respect to the flow direction of the refrigerant in the use-side refrigerant cycle. On the upstream side, it is connected in series with each of the first and second heat source side refrigerant cycles. Further, as a heating device constituting the third heat source side refrigerant cycle, for example, a heating boiler 29 that obtains heat by burning kerosene or gas is used, and has only a heating function.
[0133]
On the other hand, the use-side refrigerant cycle includes the first refrigerant transfer device 21, the connection pipe i, the connection pipes j and k, the use-side refrigerant flow control valves 23a and 23b, the use-side heat exchangers 22a and 22b, and the connection pipes j 'and k ′, a connecting pipe i ′, a first use-side refrigerant cycle connecting the refrigerant storage tank 20, a second refrigerant transfer device 25, a sixth auxiliary heat exchanger 19c, a second auxiliary heat exchanger 19a, The fourth auxiliary heat exchanger 19b is connected to a second use-side refrigerant cycle formed by connecting the refrigerant storage tank 20. The connection pipe k, the use-side refrigerant flow control valve 23b, the use-side heat exchanger 22b, and the connection pipe k 'are the same as in the first embodiment, and the connection pipe j, the use-side refrigerant flow control valve 23a, and the use-side heat exchanger 22a , And a connection pipe j ′. Further, the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b are connected in parallel similarly to the second and third embodiments, and these are connected to the first auxiliary heat exchanger 16a and the second auxiliary heat exchanger, respectively. It is formed integrally so as to exchange heat with the vessel 16b. The sixth auxiliary heat exchanger 19c is connected in series with the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b, and is integrally formed so as to exchange heat with the fifth auxiliary heat exchanger 16c. Have been.
[0134]
Further, since the first and second heat source side refrigerant cycles use a standard refrigerant cycle such as a home air conditioner, the compressor 11a, the flow path switching valve 12a, the first heat source side heat exchanger 13a The first refrigerant flow control valve 14a is housed in the first outdoor unit e, and the compressor 11b, the four-way valve 12b, the first heat source side heat exchanger 13b, and the first refrigerant flow control valve 14b are Are housed in the second outdoor unit e ′. Further, the third heat source side refrigerant cycle also uses a standard product such as a household kerosene boiler, and the third refrigerant transport device 28 and the heating boiler 29 are housed in the outdoor unit e ″. Furthermore, the first refrigerant transfer device 21, the second refrigerant transfer device 25, the integrated first auxiliary heat exchanger 16a and the second auxiliary heat exchanger 19a, and the integrated third auxiliary heat exchanger 16b The fourth auxiliary heat exchanger 19b, the integrated fifth auxiliary heat exchanger 16c and sixth auxiliary heat exchanger 19c, the refrigerant storage tank 20, and the receivers 15a and 15b are housed in the heat exchange unit d.
[0135]
The first heat source side refrigerant cycle is connected between the first outdoor unit e and the heat exchange unit d by connection pipes m and m ′. The second heat-source-side refrigerant cycle is connected between the second outdoor unit e ′ and the heat exchange unit d by connection pipes n and n ′. The third heat source side refrigerant cycle is connected between the third outdoor unit e ″ and the heat exchange unit d by connection pipes o and o ′. A filter 26 is provided in the refrigerant storage tank 20, and one end of a connection pipe i 'is opened and connected to the inside of the filter 26. The inside of the refrigerant storage tank 20 is vertically divided from the uppermost part by a partition 27 into two tanks on the left and right sides. are doing. Furthermore, the upper part of the refrigerant storage tank 20 is open to the atmosphere, and all connection pipes connected to the refrigerant storage tank 20 are opened below the draft surface of the use-side refrigerant 30 in the refrigerant storage tank 20. .
[0136]
Next, the operation will be described.
During the cooling operation, the first and second heat source side refrigerant cycles are operated, and the third heat source side refrigerant cycle is stopped. During this cooling operation, both the first and second heat source side refrigerant cycles are the refrigerant cycles indicated by solid lines in the figure. The operations of the first and second heat-source-side refrigerant cycles during the cooling operation are the same as those in the first embodiment, and will not be described.
On the other hand, in the use-side refrigerant cycle, the relatively low-temperature use-side refrigerant 30 flowing out of the bottom of the left tank of the refrigerant storage tank 20 is used by the first refrigerant transfer device 21 through the connection pipes i, j, and k. The air is sent to the side heat exchangers 22a and 22b, cools the indoor air and is heated at the same time, and returns to the tank on the right side of the refrigerant storage tank 20 through the connection pipes j ', k' and i '. On the other hand, the relatively high-temperature use-side refrigerant 30 flowing out from the bottom of the tank on the right side of the refrigerant storage tank 20 passes through the sixth auxiliary heat exchanger 19c by the second refrigerant transfer device 25, and the second auxiliary heat exchange. Branching into the heat exchanger 19a and the fourth auxiliary heat exchanger 19b. The refrigerant 30 sent to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b passes through the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger 16b, and the first and second heat source side refrigerant cycles. As a result, heat is released to the outside air, and at the same time, the refrigerant itself is cooled, merges, and returns to the upper portion of the left tank of the refrigerant storage tank 20.
[0137]
During the heating operation, the first and second heat source side refrigerant cycles are stopped, and only the third heat source side refrigerant cycle is operated. At the time of the heating operation, the third heat source side refrigerant sent out by the third refrigerant transfer device 28 removes heat obtained by burning kerosene, gas, and the like by the heating boiler 29, and at the same time, heats itself. It flows into the auxiliary heat exchanger 16c. Here, the heat is radiated to the use-side refrigerant 30 flowing through the sixth auxiliary heat exchanger 19c, and the refrigerant itself is cooled and flows into the third refrigerant transport device 28 again. As the refrigerant circulating in the third heat source side refrigerant cycle, for example, water or an aqueous solution containing at least one or more of solvents such as ethylene glycol, propylene glycol and D-sorbitol in a weight ratio of several tens% or less is used. Used.
[0138]
On the other hand, in the use-side refrigerant cycle, the relatively high-temperature use-side refrigerant 30 flowing out from the bottom of the left tank of the refrigerant storage tank 20 is used by the first refrigerant transfer device 21 through the connection pipes i, j, and k. The refrigerant is sent to the side heat exchangers 22a and 22b, heats the indoor air and is cooled at the same time, and returns to the upper part of the tank on the right side of the refrigerant storage tank 20 through the connection pipes j ', k' and i '. . On the other hand, the relatively low-temperature use-side refrigerant 30 flowing out from the bottom of the tank on the right side of the refrigerant storage tank 20 flows into the sixth auxiliary heat exchanger 19c by the second refrigerant transport device 25. Here, heat is taken from the third refrigerant circulating in the third heat source-side refrigerant cycle through the fifth auxiliary heat exchanger 16c formed integrally. At the same time, after being heated, it is branched and sent to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b. The refrigerant 30 sent to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b passes through and merges, and then returns to the upper portion of the left tank of the refrigerant storage tank 20.
[0139]
As described above, according to the present embodiment, the third heat source-side refrigerant cycle is added in series to the first and second heat source-side refrigerant cycles, and the first and second heat source-side refrigerant cycles are only in the cooling operation. Since the third heat source-side refrigerant cycle is configured to be used only for the heating operation, particularly in a heat pump that is operated in a region where the outside air temperature in winter is below freezing and is the first and second heat source-side refrigerant cycles. Even when the heating capacity is insufficient, there is an effect that the heating capacity can be easily secured.
Further, since the first and second heat source side refrigerant cycles are used only for the cooling operation, there is no need to perform the defrost operation, and the temperature of the use side refrigerant does not decrease due to the defrost operation. For this reason, the temperature of the use-side refrigerant can be maintained at a temperature suitable for heating use.
In addition, the operating cost of the first and second heat source-side refrigerant cycles by electric input and the operating cost of the third heat source-side refrigerant cycle by kerosene input are generally the same when compared with the same heating capacity. According to the present embodiment, since the heating capacity is relatively high, the heating capacity is covered only by the third heat-source-side refrigerant cycle whose operation cost is low, so that the air-conditioning operation cost paid by the user can be reduced. .
[0140]
Further, as shown in FIG. 14, a bypass circuit u for bypassing the fifth auxiliary heat exchanger 16c in the third heat source side refrigerant cycle and a bypass circuit for bypassing the sixth auxiliary heat exchanger 19c in the second use side refrigerant cycle. A bypass circuit v may be provided.
By providing the bypass circuits u and v, a part of the heat-source-side refrigerant circulating in the third heat-source-side refrigerant cycle is circulated to the bypass circuit u, and the utilization-side refrigerant circulating in the second utilization-side refrigerant cycle is also used. A part is circulated to the bypass circuit v. Therefore, the pressure loss can be reduced, and the third refrigerant transport device 28 can be configured with a small size. Further, if the bypass circuit v is provided and the set temperature of the heating boiler 29 is increased from, for example, 55 [° C.] to 70 [° C.], the fifth and sixth auxiliary heat exchangers 16 c and 19 c can be made small.
[0141]
In the present embodiment, an example is shown in which two first and second heat source side refrigerant cycles as heat pumps are connected in parallel. However, there are three or more refrigerant cycles as these heat pumps in parallel. May be connected, or only one may be connected.
Further, the first and second heat source side refrigerant cycles do not necessarily need to be heat pumps, and may be refrigerant cycles dedicated to cooling. A more inexpensive refrigeration / air-conditioning apparatus can be obtained by configuring a cooling-only refrigerant cycle.
[0142]
Further, the first and second heat source side refrigerant cycles may be not a heat pump but an absorption refrigerator such as a lithium bromide-water system or an ammonia-water system, an absorption chiller / heater or an adsorption chiller / heater.
In the third heat source side refrigerant cycle, an electric heater may be wound around or contacted with the sixth auxiliary heat exchanger 19c instead of a heating boiler for burning kerosene or gas. Of course, the third heat-source-side refrigerant cycle may be any heat pump, absorption type or adsorption type chiller / heater, as long as it exhibits a heating function. The third heat source side refrigerant cycle is not necessarily one system, and two or more systems may be connected in parallel or in series using a kerosene boiler, a gas boiler, an electric heater, or the like.
[0143]
Embodiment 5 FIG.
FIG. 15 is a configuration diagram illustrating, for example, a cooling and heating device as a refrigeration and air conditioning device according to the fifth embodiment. In the fourth embodiment, the first and second heat source side refrigerant cycles are not used for the heating operation in winter, and all the heating load is covered by the third heat source side refrigerant cycle. In this case, the first and second heat-source-side refrigerant cycles are wasteful in that they are equipped with equipment capable of performing the heating operation but are not used. Therefore, in the present embodiment, as shown in FIG. 15, the sixth auxiliary heat exchanger 19c is installed downstream of the second and fourth auxiliary heat exchangers 19a and 19b, and the lower limit of the outside air temperature at which the operation is guaranteed. The third heat-source-side refrigerant cycle is provided with equipment that can cover the shortage of the required heating load with the capacity of the first and second heat-source-side refrigerant cycles. With this configuration, the utilization-side refrigerant that has been heated to, for example, about 50 ° C. in the first and second heat-source-side refrigerant cycles is further passed through the fifth and sixth auxiliary heat exchangers 16c and 19c. The necessary capacity is ensured by heating to, for example, about 80 ° C. in the heat source side refrigerant cycle.
[0144]
In the present embodiment, as described above, the third heat source-side refrigerant cycle dedicated to heating and the first and second heat source-side refrigerant cycles combined with cooling / heating are connected in series to the utilization-side refrigerant cycle. It is composed. In addition, a third heat source-side refrigerant cycle dedicated to heating is connected downstream of the first and second heat source-side refrigerant cycles for both cooling and heating with respect to the use-side refrigerant cycle. Here, the first and second heat-source-side refrigerant cycles for both cooling and heating are configured by a vapor compression refrigeration cycle, and use both the cooling function and the heating function. For this reason, the heating performance at a low outside air temperature can be sufficiently ensured while eliminating waste of the facilities, and the first and second heat sources having higher energy efficiency than the heating boiler 29 as the third heat source side refrigerant cycle. The operation time of the heat pump, which is the side refrigerant cycle, increases. Further, the first and second heat source side refrigerant cycles dissipate heat absorbed from the outside air to the use side refrigerant having a relatively low temperature through the first and third auxiliary heat exchangers 16a and 16b. It is also useful for preserving the global environment, such as effective use of petroleum resources and reduction of carbon dioxide emissions.
[0145]
In the fifth embodiment, during the normal heating operation, the third heat source side refrigerant cycle is operated in order to cover the shortage in the first and second heat source side refrigerant cycles. However, if the outside air temperature becomes low and the efficiency with respect to primary energy including the power generation end efficiency of the first and second heat source side refrigerant cycles becomes lower than that of the heating boiler 29, the first and second heat sources The side refrigerant cycle may be stopped, and only the heating boiler 29, which is the third heat source side refrigerant cycle, may be operated. In this case, it goes without saying that the third heat source side refrigerant cycle alone needs to have a sufficient capacity to cover the required heating load. On the other hand, when there is a heating request especially when the outside air temperature is high, the heat pump as the first and second heat source side refrigerant cycles has a higher primary energy than the heating boiler 29 as the third heat source side refrigerant cycle. When the efficiency with respect to the temperature increases, the heating boiler 29 serving as the third heat source side refrigerant cycle may be stopped, and the heating operation may be performed only with the heat pump serving as the first and second heat source side refrigerant cycles. The outside air temperature can be detected by an outside air temperature sensor 34 installed in the heat exchange unit.
In the configuration of the present embodiment, the first, second, and third heat-source-side refrigerant cycles can be operated in various patterns according to the use situation, the equipment can be used effectively, and energy can be reduced.
[0146]
Further, when one or both of the first and second heat source side refrigerant cycles enter the defrosting operation during the heating operation, the third refrigerant cycle dedicated to heating and the first and second cooling / heating combined use are performed. By controlling the refrigerant cycle of at least one of the two refrigerant cycles to continue the heating operation, it is possible to maintain the temperature in the air-conditioned room during the defrosting operation, and obtain a refrigeration air-conditioning apparatus that is easy to maintain comfort. be able to. This control is performed by the control device 41, for example.
[0147]
Further, when one or both of the first and second heat source side refrigerant cycles enter the defrosting operation during the heating operation, the control device 41 causes the temperature detected by the first temperature sensor 31 to approach the target value. In this manner, control may be performed to send a control signal to the control device 42c so as to increase the capacity of the third heat source side refrigerant cycle. As described above, when the capacity of the third heat source side refrigerant cycle performing the heating operation is increased and the heating operation is performed during the defrosting operation of the first or second heat source side refrigerant cycle, the decrease in the temperature of the use side refrigerant is reduced. As a result, the indoor comfort can be improved.
In addition, the refrigerant cycle operated by increasing the heating capacity during the defrosting operation is not limited to the third refrigerant cycle dedicated to heating, and the first and second refrigerant cycles combined with cooling / heating are operated during the heating operation. In this case, it is sufficient to increase the capacity of the refrigerant cycle so as to continue the heating operation.
[0148]
In the heating operation, when one or both of the first and second heat source side refrigerant cycles satisfy the defrosting operation start condition, the control device 41 increases the capacity of the third heat source side refrigerant cycle. For example, when the control signal is sent to the control device 42c so as to operate at the maximum capacity, the control is automatically performed so that the temperature drop of the use-side refrigerant is further reduced, thereby improving the indoor comfort. Can be.
Also in this case, the refrigerant cycle operated by increasing the heating capacity is not limited to the third refrigerant cycle dedicated to heating, and the first and second refrigerant cycles using both cooling and heating are in the heating operation. In this case, it is sufficient to increase the capacity of the refrigerant cycle so as to continue the heating operation.
[0149]
In particular, when only the operation / stop can be selected for the capacity control of the first heat source side refrigerant cycle, the second heat source side refrigerant cycle, and the third heat source side refrigerant cycle, as shown in FIG. The first, second, and third heat source side refrigerant cycles may be sequentially operated such that the detection value TH1 of the sensor 31 approaches the target temperature TM. An upper limit TMH and a lower limit TML are set for the target temperature TM of the first temperature sensor 31, and the first, second, and third heat source side refrigerants are set so that the detected temperature TH1 of the first temperature sensor 31 falls between TMH and TML. Start / stop the cycle. In FIG. 16, the horizontal axis represents the detected temperature TH1 of the first temperature sensor 31, and the vertical axis represents the operation / stop of the first, second, and third heat source side refrigerant cycles. For example, TMH1 = 51 ° C., TMH2 = 50 ° C., TMH3 = 49 ° C., TML1 = 49 ° C., TML2 = 48 ° C., TML3 = 47 ° C., and the detected temperature TH1 is from TML1. When descending in order, the heat source side refrigerant cycle is additionally operated one system at a time. On the other hand, when the detected temperature TH1 sequentially increases from TMH3, the heat source side refrigerant cycle is stopped one by one. For example, when the first heat source side refrigerant cycle is in operation, it is not changed while TML1 <TH1 <TMH1. In addition, during the first and second heat source side refrigerant cycle operations, TML2 <TH1 <TMH2 is not changed, and during the first, second, and third heat source side refrigerant cycle operations, TML3 <TH1 <TMH3. Do not change during In this way, the heat source side refrigerant cycle is divided into three systems, and each heat source side refrigerant cycle is operated / stopped, so that the temperature change of the use side refrigerant is smaller than the case where the heat source side refrigerant cycle is one system. The stability of the refrigerant temperature and, consequently, the comfort in the air-conditioned room are improved.
[0150]
Embodiment 6 FIG.
FIG. 17 is a configuration diagram illustrating, for example, a cooling and heating device as the refrigeration and air conditioning device according to the present embodiment. In Embodiments 2 to 5, in the use-side refrigerant cycle, the connection pipe i ′ and the connection pipe r are connected to the refrigerant storage tank 20 from the side surfaces of the right tank and the left tank, respectively, and are open. As shown in FIG. 17, a connection may be made from the bottom surface of the refrigerant storage tank 20 to open the upper portion and the inside of the filter, respectively. By doing so, there is no need to provide a connecting portion on the side surface of the refrigerant storage tank 20, so that the side surface can be cleaned up. Therefore, the installation area of the heat exchange unit d can be reduced while the capacity of the refrigerant storage tank 20 is maintained, and the space efficiency is improved.
[0151]
At this time, the position of the opening of the connection pipes i ′ and r in the refrigerant storage tank 20 is between the outflow velocity u [m / s] of the use-side refrigerant and the distance h [m] from the opening to the draft surface. In addition, the relationship of Expression (12) may be satisfied.
h ≧ u 2 / 2g ... (12)
Here, g: gravity acceleration = 9.8 [m / s] 2 ]. Right side u 2 / 2g is the distance from the opening in the atmosphere to the highest point where the fluid that has flowed vertically upward at a speed u reaches. Therefore, if the distance h to the draft surface is kept longer than this distance, the draft surface of the refrigerant storage tank 20 will be somewhat quiet, and the refrigerant inside will spill out from the overflow port of the refrigerant storage tank 20, or the connection pipe r The stratification effect caused by the refrigerant ejected through the draft surface from the opening and returning to the draft surface does not disturb the temperature stratification, and does not impair the stability of the use-side refrigerant temperature.
Actually, since the use-side refrigerant flows below the draft surface of the refrigerant storage tank 20, the distance to the highest point where the refrigerant that has flowed out due to the viscosity of the refrigerant in the tank reaches the right side u 2 H is smaller than this distance u. 2 There is no problem if it is smaller than / 2 g.
Of course, similarly to the third embodiment, the refrigerant storage tank 20 is divided into a right tank and a left tank by a partition 27, and two openings are provided in the right tank and the left tank, respectively. For this reason, in the heating operation, the left tank forms a temperature stratification above and below without mixing the internal refrigerant, and can sufficiently store heat while expanding a high-temperature region with time. In the cooling operation, the refrigerant in the left tank in the refrigerant storage tank 20 can be kept at a relatively lower temperature than the refrigerant in the right tank, so that the cooling can be started quickly in summer.
[0152]
Embodiment 7 FIG.
FIG. 18 is a configuration diagram illustrating, for example, a cooling and heating device as the refrigeration and air conditioning device according to the present embodiment. In the fifth embodiment, the first and second heat-source-side refrigerant cycles for combined cooling / heating and the third heat-source-side refrigerant cycle dedicated to heating are connected in series. However, as shown in FIG. The third heat source side refrigerant cycle and the first and second heat source side refrigerant cycles may be connected in parallel. Then, for example, two-way valves 51 and 52 are provided as flow path switching means on the downstream side of the portions branched to the respective refrigerant pipes.
By this flow path switching means, the refrigerant flow path is switched so that the usage-side refrigerant does not flow through the usage-side auxiliary heat exchanger 19c that exchanges heat with the third refrigerant cycle during the cooling operation.
[0153]
During the cooling operation, the two-way valve 51 is closed and the two-way valve 52 is opened, and the cooling operation is performed by the first and second heat-source-side refrigerant cycles, which are both cooling / heating refrigerant cycles. The refrigerant circuit is switched by the two-way valve 51 so that the use-side refrigerant does not flow to the sixth auxiliary heat exchanger 19c that exchanges heat with the third heat source-side cooling cycle during the cooling operation.
On the other hand, during the heating operation, the two-way valve 51 is opened and the two-way valve 52 is closed, and the heating operation is performed by the third heat source side refrigerant cycle which is a refrigerant cycle dedicated to heating. If the third heat source side refrigerant cycle fails, the two-way valve 51 may be closed and the two-way valve 52 may be opened to perform the heating operation in the first and second heat source side refrigerant cycles.
Alternatively, both the two-way valve 51 and the two-way valve 52 may be opened to operate and heat all the first, second, and third heat source side refrigerant cycles. These switching may be performed according to the temperature detected by the outside air temperature sensor 34 installed in the heat exchange unit.
[0154]
In this way, by connecting the third heat source side refrigerant cycle dedicated to heating and the first and second heat source side refrigerant cycles combined with cooling / heating in parallel, sufficient heating capacity can be ensured, and indoor comfort can be secured. Inexpensive refrigeration and air-conditioning equipment can be obtained with easy maintenance. Furthermore, each of the refrigerant cycle dedicated to heating and the refrigerant cycle combined with cooling / heating can be independently controlled, and an operation suitable for the use situation can be performed.
[0155]
Further, the first and second heat-source-side refrigerant cycles may be configured as cooling-only refrigerant cycles instead of the combined cooling / heating. In this case, the refrigerant cycle dedicated to heating is operated during the heating operation, and the flow path of the usage-side refrigerant is switched by the switching means during the cooling operation, and the refrigerant cycle dedicated to cooling is operated.
With this configuration, each of the heating-only refrigerant cycle and the cooling-only refrigerant cycle can be independently controlled, and an operation suitable for a use situation can be performed. In particular, unnecessary functions are omitted, and an inexpensive refrigeration / air-conditioning apparatus is obtained. be able to.
[0156]
Embodiment 8 FIG.
FIG. 19 is a configuration diagram illustrating, for example, a cooling and heating device as the refrigeration and air conditioning device according to the present embodiment. In the first to seventh embodiments, the auxiliary heat exchanger group that exchanges heat between the heat source-side refrigerant cycle and the use-side refrigerant cycle is installed outside the refrigerant storage tank 20, but as shown in FIG. Alternatively, the auxiliary heat exchangers 16a and 16b may be immersed and installed in the use-side refrigerant inside the refrigerant storage tank 20. At this time, the first and second heat source side refrigerant cycles are operated / stopped such that the temperature detected by the temperature sensor 35 installed in the refrigerant storage tank 20 approaches the target temperature. With such a configuration, the second usage-side refrigerant cycle operating as the heat transport cycle in the third to seventh embodiments is not required, and in particular, the second refrigerant transport device 25 is not required. This has the effect of improving overall reliability.
[0157]
Further, the heat storage material 61 may be inserted into the refrigerant storage tank 20 together with the auxiliary heat exchangers 16a and 16b. As the heat storage material 61, for example, a block of copper, iron, brick, or the like, or sodium acetate or the like is used in a capsule or a pipe. When using sodium acetate, latent heat of about 50 [° C.] can be used together with sensible heat, and heat can be effectively and sufficiently stored.
In other words, the internal volume of the refrigerant storage tank 20 is controlled such that the temperature of the use-side refrigerant during the defrosting operation of the heat-source-side refrigerant cycle during the heating operation of the use-side refrigerant cycle is maintained at a temperature suitable for heating. The amount of the refrigerant or the amount of the heat storage material 61 is set as the internal volume that can be stored.
[0158]
With such a configuration, even if one or both of the first and second heat source side refrigerant cycles enters the defrosting operation, the use side refrigerant temperature decreases due to the heat radiation of the heat storage material 61 in the refrigerant storage tank 20. And the comfort of the indoor air conditioning can be better maintained. The first and second heat-source-side refrigerant cycles may be operated / stopped such that the temperature detected by the second temperature sensor 33 installed at the outlet of the refrigerant transfer device 21 approaches the target temperature. . When the first and second heat-source-side refrigerant cycles are operated based on the detected temperature of the second temperature sensor 33 closer to the temperature of the refrigerant supplied to the use-side heat exchangers 22a and 22b, the comfort of indoor air conditioning is improved. Can be well maintained. In addition, when compared with a configuration in which the heat storage material 61 is not provided, when the temperature decrease of the use-side refrigerant is set to be equal, the amount of the use-side refrigerant can be reduced by the heat storage capacity of the heat storage material 61. 20 can be reduced in size. Further, when the heat storage material 61 is made of a material having a larger heat capacity than water, the heat storage material 61 itself can be made smaller. Since the heat storage capacity of the heat storage material 61 can be set by determining the specific heat and the weight, as described in the first embodiment, the temperature decrease of the use-side refrigerant becomes equal to or lower than a predetermined temperature based on the amount of heat released during the defrosting operation. With this setting, the temperature of the use-side refrigerant during the defrosting operation can be stabilized.
[0159]
In addition, if the auxiliary heat exchangers 16a and 16b are formed by arranging ordinary copper tubes in a spiral shape, a grid pattern, or a staggered shape, an inexpensive refrigeration and air-conditioning apparatus can be configured. When a fin tube or a plate fin heat exchanger is used, the size of the auxiliary heat exchanger and the refrigerant storage tank 20 can be reduced.
Further, at least one of the auxiliary heat exchangers 16a and 16b may be constituted by a spiral fin heat exchanger. FIG. 20 is an explanatory diagram showing the refrigerant storage tank 20 in which the auxiliary heat exchanger 16a is formed of a spiral fin heat exchanger, and does not show the auxiliary heat exchanger 16b. A fin made of copper or the like is spirally fixed to the outside of the heat transfer tube to form a tube with a spiral fin, and the spiral fin heat exchanger 16a is disposed so as to be immersed in the use-side refrigerant stored in the refrigerant storage tank 20. are doing. In such a tube with spiral fins, a heat transfer area of the use side refrigerant when the heat source side refrigerant flowing in the tube with spiral fins and the use side refrigerant in the refrigerant storage tank 20 exchange heat, that is, the outer wall area of the tube and the fin The total surface area is significantly larger than the heat transfer area of the heat source side refrigerant, that is, the pipe inner wall area. As a result, the heat transfer area of the use-side refrigerant having poor heat transfer performance when using water or the like is approximately six times as large as the configuration in which no fins are provided, and the heat transmission rate is improved by less than four times. Therefore, the size of the auxiliary heat exchanger 16a can be greatly reduced.
[0160]
Strictly speaking, even with a heat transfer tube without fins at all, the outer wall area of the tube is larger than the inner wall area by the thickness of the heat transfer tube, but the heat transfer by plate fins, spiral fins, etc. If the area is greatly increased, the heat transfer performance can be improved.
Alternatively, the heat transfer area of the use-side refrigerant may be larger than the heat transfer area of the heat-source-side refrigerant. Alternatively, the heat exchanger 16a may be formed by, for example, meandering and fixing a heat transfer tube to a large metal plate. Alternatively, a configuration in which a plurality of metal plates are arranged in parallel and a plurality of heat transfer tubes penetrate therethrough may be used.
Of course, the configuration is such that the heat transfer area of the use-side refrigerant in the second auxiliary heat exchanger 19 in the first to seventh embodiments is larger than the heat transfer area of the heat source-side refrigerant in the first auxiliary heat exchanger 16. You can also.
[0161]
Further, as in the present embodiment, the auxiliary heat exchangers 16a and 16b are provided by being immersed in the use side refrigerant in the refrigerant storage tank 20, and the heat source side refrigerant flowing inside the heat transfer tube and the use side refrigerant flowing outside the heat transfer tube. When heat is exchanged between the storage tank 20 and the storage tank 20, cold heat is stored in the refrigerant storage tank 20 and the cold heat is used by the use-side heat exchangers 22a and 22b for cooling in a room or a warehouse or for refrigeration or freezing in a refrigerator or the like. Is also effective. That is, when cold heat is stored using a freezing medium such as water as the use-side refrigerant, even if the use-side refrigerant freezes around the auxiliary heat exchangers 16a and 16b, the use-side refrigerant is stored in the refrigerant storage tank. The cold heat can be transported to the use-side heat exchangers 22a and 22b through a portion that is not frozen. Therefore, as compared with Embodiments 1 to 7, the temperature of the use-side refrigerant sent to the use-side heat exchangers 22a and 22b can be lowered, and the transfer power of the refrigerant transfer device 21 can be reduced, and the use-side heat can be reduced. An improvement in the dehumidifying performance of the exchangers 22a and 22b can be expected. Also, the auxiliary heat exchangers 16a and 16b use the nighttime electric power to freeze the use-side refrigerant and store the heat, and in the daytime use the stored cold heat to cool the heat-source-side refrigerant cycle, thereby reducing the size of the heat source-side refrigerant cycle equipment. In addition, the power receiving capacity can be reduced.
[0162]
Further, in the first to seventh embodiments, during the cooling operation in the heat source side refrigerant cycle, the first temperature sensor 31 detects the temperature of the first temperature sensor 31 in order to protect the use side refrigerant from freezing inside the auxiliary heat exchangers 16a and 16b. When the detected value reaches about the freezing temperature of the use-side refrigerant + 4 ° C., the heat-source-side refrigerant cycle is stopped, or fourth and fifth temperature sensors are installed on the outer surfaces of the auxiliary heat exchangers 16a and 16b, respectively. When the detected value becomes approximately + 4 ° C. of the freezing temperature of the use-side refrigerant, control such as stopping the heat-source-side refrigerant cycle is necessary. However, according to the present embodiment, this is not necessary, and the auxiliary heat exchangers 16a and 16b are unnecessary. Is arranged in the refrigerant storage tank 20, the reliability of the entire system can be improved with a relatively simple apparatus configuration, and an inexpensive refrigeration and air-conditioning apparatus can be obtained.
[0163]
Further, as shown in FIG. 21, partitions 27a and 27b may be provided so as to separate between the inlet and the outlet of the use-side refrigerant in the refrigerant storage tank 20. One of the partitions 27a and 27b has a communicating portion below, and the other has a communicating portion above. The auxiliary heat exchangers 16a and 16b are immersed in the separated inlet, and the heat storage material 61 is immersed in the outlet. In this configuration, the return refrigerant from the use-side heat exchangers 22a and 22b passes through the filter 26 to remove dust and dirt, and is then temperature-controlled by the first and second auxiliary heat exchangers 16a and 16b. . Thereafter, a flow path is formed in the refrigerant storage tank 20 so that the heat storage material 61 in the refrigerant storage tank 20 is stored and sucked into the refrigerant transfer device 21. For this reason, in the refrigerant | coolant storage tank 20, the refrigerant | coolant flow path which exchanges heat with the auxiliary heat exchangers 16a and 16b and the heat storage material 61 effectively can be comprised.
[0164]
Embodiment 9 FIG.
In the first to seventh embodiments, since the heat source side refrigerant cycle reverses the flow direction of the refrigerant between the cooling operation for cooling and the heating operation for heating, the first and second auxiliary heat exchangers 16 are different. , 19, the flow directions of the heat-source-side refrigerant and the use-side refrigerant are countercurrent during the heating operation, whereas they are parallel during the cooling operation. However, when a non-azeotropic mixed refrigerant such as R407C is used in the heat source-side refrigerant cycle, the use-side refrigerant is cooled from the inlet to the outlet of the second auxiliary heat exchanger 19 during cooling operation, and the temperature decreases. Concurrently, the temperature of the heat source side refrigerant increases from the inlet to the outlet of the first auxiliary heat exchanger 16. For this reason, the evaporation temperature on the heat source side must be reduced as compared with the case where a single refrigerant such as R22 or a pseudo-azeotropic refrigerant such as R410A is used, and there is a problem that the efficiency is reduced.
[0165]
On the other hand, in the present embodiment, the inlet and the outlet of the second auxiliary heat exchanger 19 are set at the time of the cooling operation so as to be applicable to the case where a non-azeotropic mixed refrigerant such as R407C is used as the heat source side refrigerant. The configuration is configured such that the operation is reversed at the time of the heating operation, and the heat source-side refrigerant flowing through the first auxiliary heat exchanger 16 has a counterflow in both operations.
FIG. 22 is a configuration diagram illustrating, as a refrigeration / air-conditioning apparatus according to the present embodiment, for example, a cooling / heating apparatus that cools a room in a cooling operation and heats the room in a heating operation. In the figure, reference numeral 62 denotes switching means for switching the flow direction of the use-side refrigerant in the auxiliary heat exchanger 19, and is, for example, a four-way valve 62. The four-way valve 62 has a first port at the suction port of the refrigerant transfer device 21, a second port at one end of the second auxiliary heat exchanger 19, a third port at one end of the connection pipe i ′, and a fourth port. Are connected to the bottom opening of the refrigerant storage tank 20, respectively. During the cooling operation, the refrigerant flows in the direction indicated by the solid line in both the heat source side and the use side refrigerant cycle, and conversely, during the heating operation, the four-way valve 12 and the four-way valve 62 respectively Switch.
For this reason, the heat exchange in the first and second auxiliary heat exchangers 16 and 19 both become countercurrent, and the heat exchange can be effectively performed in both the cooling and heating operations.
[0166]
Further, as shown in the drawing, when the first temperature sensor 31 is installed on the outlet side of the refrigerant transport device 21, the temperature of the use-side refrigerant after heat exchange can be detected in both the cooling and heating operations. With the first temperature sensor 31 provided in the pipe between the second auxiliary heat exchanger 19 and the refrigerant storage tank 20 as in the first to seventh embodiments, the second auxiliary heat exchange is performed during the heating operation. Although the outlet temperature of the heat exchanger 19 can be detected, the flow direction changes during cooling operation, and the temperature becomes the inlet temperature, so that the sending temperature to the use-side heat exchangers 22a and 22b cannot be guaranteed.
However, the first temperature sensor 31 is installed in the pipe between the second auxiliary heat exchanger 19 and the refrigerant storage tank 20 on the premise that the feed temperature is not guaranteed, or the first temperature sensor 31 is connected to the second port of the four-way valve 62 and the second port. It is also possible to install in a pipe between the two auxiliary heat exchangers 19. In the former case, the detected value of the first temperature sensor 31 is the inlet temperature of the second auxiliary heat exchanger 19 during the cooling operation, and the outlet temperature during the heating operation. Therefore, the target temperature TM is TM = 12 during the cooling operation. [° C.] and TM = 50 [° C.] during heating. As described above, when detecting the inlet temperature, the operation may be controlled in consideration of the temperature difference corresponding to the amount of heating or cooling in the second auxiliary heat exchanger 19. Anyway, similarly to the first embodiment, the outlet temperature of the second auxiliary heat exchanger 19 may be set to 7 ° C. for cooling and 50 ° C. for heating.
[0167]
As described above, according to the present embodiment, the non-azeotropic mixed refrigerant such as R407C is used as the heat-source-side refrigerant by setting the first and second heat exchangers 16 and 19 to have the counterflow in both the cooling and heating operations. In this case, there is an effect that the system can be efficiently operated in both the cooling and heating operations.
[0168]
In the present embodiment, the example in which the four-way valve 62 is used as the switching means of the flow path of the use-side refrigerant cycle has been described. However, as shown in FIG. 23, the electromagnetic valves 63a, 63b, 63c, and 63d may be combined. Good. In this case, during the cooling operation, the solenoid valves 63a and 63c are open, and 63b and 63d are closed. During the heating operation, the solenoid valves 63b and 63d are open and 63a and 63c are closed.
In the case where the four-way valve 62 is configured as shown in FIG. 22, the four-way valve is more expensive than the four solenoid valves, but the refrigerant pipe can be configured relatively simply. In the case where the solenoid valve is composed of four solenoid valves 63a, 63b, 63c and 63d as shown in FIG. 23, the refrigerant piping is somewhat complicated, but the cost can be reduced.
[0169]
In the configuration shown in FIGS. 22 and 23, in the refrigerant storage tank 20, an opening connected to the second auxiliary heat exchanger 19 is provided on an upper side surface of the tank 20, and an opening connected to the four-way valve 62 or the electromagnetic valves 63c and 63d. Are provided on the bottom surface of the tank 20, but both openings may be provided on the bottom surface of the tank 20. By not providing a connection portion on the side surface of the refrigerant storage tank 20, the side surface can be configured neatly, and the whole system can be easily made compact. However, in the case where two connection portions are provided on the bottom surface, a separation plate having a height shorter than the height from the bottom surface to the water surface is provided between the two connection portions so that the usage-side refrigerant flowing into the refrigerant storage tank 20 can be used. , It is better to configure it so that it does not flow out immediately.
[0170]
Embodiment 10 FIG.
Although the on-site construction for charging the use-side refrigerant occurs before the refrigeration / air-conditioning apparatus according to the present invention is installed and before the refrigeration / air-conditioning apparatus is actually operated, the first to ninth embodiments are all related to the refrigerant storage tank 20. Was opened to the atmosphere, and the use-side refrigerant was poured from above. For this reason, in the on-site refrigerant charging operation, the use side refrigerant is filled from the upper part of the refrigerant storage tank 20 using a rubber hose or a bucket, and when the refrigerant storage tank 20 is full, the refrigerant transport device 21 is operated, and It is necessary to repeat the operation that the refrigerant in the refrigerant storage tank 20 is sent to the use-side heat exchanger or the like and the refrigerant in the refrigerant storage tank 20 is refilled when the refrigerant in the refrigerant storage tank 20 is reduced, which may be troublesome. .
[0171]
FIG. 24 is a configuration diagram illustrating, for example, a cooling and heating device as the refrigeration and air conditioning device according to the present embodiment. In the present embodiment, the configuration is such that charging of the usage-side refrigerant can be facilitated. As shown in FIG. 24, a branch pipe having a stop valve 64b and a connection port 65 is connected immediately after the discharge port of the refrigerant transfer device 21, and a stop valve 64a is provided between this connection point and the discharge port of the refrigerant transfer device 21. Is installed. For example, when water is used as the usage-side refrigerant, in the usage-side refrigerant charging operation at the site, the stop valve 64a is closed, the connection port 65 is connected to a water tap with a rubber hose or the like, and the water tap is opened after the stop valve 64b is opened. Open and fill the usage-side refrigerant cycle with water as the usage-side refrigerant. When the water is filled up to the appropriate water level in the refrigerant storage tank 20, the water supply faucet and the stop valve 64b are closed in this order, the stop valve 64a is opened, and then the refrigerant transfer device 21 may be operated.
In this way, since the water as the refrigerant can be easily filled into the utilization-side refrigerant cycle at one time with the tap water pressure, the labor for the on-site refrigerant charging operation can be saved, and the construction cost can be reduced.
[0172]
Further, in this configuration, the refrigerant storage tank 20 may be configured as a closed type without opening to the atmosphere. The closed type can keep the inside of the tank clean, prevent dirt, and prevent the growth of bacteria, as compared with the open type. However, in order to absorb the expansion of the usage-side refrigerant due to a change in temperature, it is preferable that the space be slightly sealed above the draft surface of the refrigerant.
[0173]
Embodiment 11 FIG.
Hereinafter, as a refrigeration / air-conditioning apparatus according to Embodiment 11 of the present invention, for example, a description will be given of a cooling / heating apparatus that cools a room by a cooling operation and heats a room by a heating operation, and describes the cooling operation as a cooling operation and the heating operation as a heating operation. . FIG. 25 is a configuration diagram showing a cooling and heating device according to the present embodiment. In the figure, the heat source side refrigerant cycle includes a first compressor 11a, a first flow path switching valve 12a, a first heat source side heat exchanger 13a, a first refrigerant flow control valve 14a, a first receiver 15a, A first heat source-side refrigerant cycle formed by connecting the first auxiliary heat exchanger 16a, a second compressor 11b, a second flow path switching valve 12b, a second heat source-side heat exchanger 13b, and a second heat source-side heat exchanger 13b. A second heat source side refrigerant cycle is formed by connecting the refrigerant flow control valve 14b, the second receiver 15b, and the third auxiliary heat exchanger 16b. Since these use a standard vapor compression refrigeration cycle such as a home air conditioner, a compressor 11a, a flow path switching valve 12a, a first heat source side heat exchanger 13a, a first refrigerant flow control valve. 14a is housed in the first outdoor unit e, and the compressor 11b, the flow path switching valve 12b, the first heat source side heat exchanger 13b, and the first refrigerant flow control valve 14b are connected to the second outdoor unit e '. It is stored in. Further, the outdoor units e and e 'include control devices 42a and 42b, and control the compressors 11a and 11b and the refrigerant flow control valves 14a and 14b.
[0174]
On the other hand, the use-side refrigerant cycle includes the first refrigerant transfer device 21, the connection pipe i, the connection pipes j and k, the use-side refrigerant flow control valves 23a and 23b, the use-side heat exchangers 22a and 22b, and the connection pipes j 'and k ′, a connecting pipe i ′, a first use-side refrigerant cycle formed by connecting the refrigerant storage tank 20, a second refrigerant transfer device 25, a second auxiliary heat exchanger 19a, a fourth auxiliary heat exchanger 19b, And a second usage-side refrigerant cycle formed by connecting the refrigerant storage tanks 20. The connection pipe k, the use-side refrigerant flow control valve 23b, the use-side heat exchanger 22b, and the connection pipe k ′ are connected pipe j, the use-side refrigerant flow control valve 23a, the use-side heat exchanger 22a, and the connection pipe j ′. Are connected in parallel. Further, the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b are connected in parallel similarly to the second and third embodiments, and these are connected to the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger, respectively. It is formed integrally so as to exchange heat with the vessel 16b.
The second usage-side refrigerant cycle circulates the usage-side refrigerant and exchanges heat with the first and third auxiliary heat exchangers 16a and 16b in the second and fourth auxiliary heat exchangers 19a and 19b, respectively, to store the refrigerant. A heat transport cycle for storing heat in the tank 20 is configured.
[0175]
Further, the first refrigerant transfer device 21, the second refrigerant transfer device 25, the integrated first auxiliary heat exchanger 16a, the second auxiliary heat exchanger 19a, the integrated third auxiliary heat exchanger 16b, The fourth auxiliary heat exchanger 19b, the refrigerant storage tank 20, and the receivers 15a and 15b are housed in the heat exchange unit d. The first heat source side refrigerant cycle is connected between the first outdoor unit e and the heat exchange unit d by connection pipes m and m ′. The second heat-source-side refrigerant cycle is connected between the second outdoor unit e ′ and the heat exchange unit d by connection pipes n and n ′.
[0176]
A filter 26 is provided in the refrigerant storage tank 20, and one end of a connection pipe i 'is opened and connected to the inside of the filter 26. The inside of the refrigerant storage tank 20 is vertically divided from the uppermost part by a partition 27 into two tanks on the left and right sides. are doing. Furthermore, the upper part of the refrigerant storage tank 20 is open to the atmosphere, and all connection pipes connected to the refrigerant storage tank 20 are opened below the draft surface of the use-side refrigerant 30 in the refrigerant storage tank 20. .
[0177]
Furthermore, in the present embodiment, a heat source device e ″ dedicated to heating is connected so that the use-side refrigerant is directly circulated. The heat source device e ″ includes, for example, a third refrigerant transport device 28, a heating boiler 29, and a control device 42c.
During the use-side refrigerant cycle, a first opening / closing valve 101 is provided in the connection pipe i from the heat exchange unit d to the branch of the connection pipes j and k, and the first opening / closing valve 101 is connected to the connection pipes j and k. The connection pipe i branches off until one end of the second opening / closing valve 102 is connected. On the other hand, a third opening / closing valve 103 is provided in the connection pipe i ′ from the heat exchange unit d to the branch of the connection pipes j ′ and k ′, and the third opening / closing valve 103 is connected to the connection pipes j ′ and k ′. The connection pipe i 'branches off until the' branch ', and one end of the fourth on-off valve 104 is connected. The other end of the second on-off valve 102 is connected to the refrigerant outlet side of the fourth refrigerant transfer device 105, and the other end of the fourth on-off valve 104 is connected to the refrigerant inlet side of the heat source device e ″ and the connection pipe o. Connected. Further, the refrigerant inlet side of the fourth refrigerant transport device 105 is connected to the refrigerant outlet side of the heat source device e ″ by a connection pipe o ′. Further, in the heat source device e ″, a heating boiler 29 using heat obtained by burning kerosene, gas, and the like, and a third refrigerant transport device 28 are housed. Is connected in the order of the refrigerant transport device 28, the heating boiler 29, and the connection pipe o '. The control device 42c controls the heating boiler 29 and the third refrigerant transport device 28.
In addition, the heat source device e ″ is dedicated to heating, and is set to have a capacity such that only one of the heat source devices e '' can exhibit a necessary heating capacity.
[0178]
In the case of such a configuration, the on-off valves 101 to 104 constitute switching means for switching the refrigerant flow path of the use-side refrigerant cycle, and circulate the use-side refrigerant to the heating-only heat source device e ″ during the heating operation. Things.
Further, w is a switching unit, which is a combination of the on-off valves 101 to 104 in one unit.
[0179]
Next, the operation will be described.
During the cooling operation, the first and second heat source side refrigerant cycles are operated, and the heat source device e ″ is stopped. During the cooling operation, both the first and second heat source side refrigerant cycles become the refrigerant cycle indicated by the solid line in the figure. The operations of the first and second heat-source-side refrigerant cycles during the cooling operation are the same as those in the first embodiment, and will not be described.
On the other hand, in the use-side refrigerant cycle, during the cooling operation, the first on-off valve 101 and the third on-off valve 103 are opened, and the second on-off valve 102 and the fourth on-off valve 104 are closed. The relatively low-temperature use-side refrigerant 30 flowing out from the bottom of the left tank of the refrigerant storage tank 20 is connected to the use-side heat exchangers 22a and 22b by the first refrigerant transfer device 21 through the connection pipes i, j, and k. The air is cooled, and at the same time as the room air is cooled, the air itself is heated and returned to the tank on the right side of the refrigerant storage tank 20 through the connection pipes j ′ and k ′ and the connection pipe i ′. At this time, the second opening / closing valve 102 is closed in the middle of the connection pipe i, and the fourth opening / closing valve 104 is closed in the middle of the connection pipe i ′. No refrigerant flows in.
[0180]
On the other hand, the relatively high-temperature use-side refrigerant 30 flowing out from the bottom of the tank on the right side of the refrigerant storage tank 20 is separated by the second refrigerant transfer device 25 into the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b. Is branched into and sent. The use side refrigerant 30 sent to the second auxiliary heat exchanger 19a and the fourth auxiliary heat exchanger 19b passes through the first auxiliary heat exchanger 16a and the third auxiliary heat exchanger 16b, and the first and second heat source sides. At the same time as the heat is released to the outside air by the refrigerant cycle, the refrigerant itself is cooled, merges, and returns to the left tank of the refrigerant storage tank 20.
[0181]
During the heating operation, the first and second heat source side refrigerant cycles are stopped, and only the heat source device e ″ is operated. During the heating operation, the first on-off valve 101 and the third on-off valve 103 are closed, and the second on-off valve 102 and the fourth on-off valve 104 are opened during the use-side refrigerant cycle. The refrigerant sent out by the third refrigerant transfer device 28 takes heat obtained by burning kerosene, gas and the like in the heating boiler 29 and at the same time heats itself and is further pressurized by the fourth refrigerant transfer device 105. Then, it flows into the connection pipe i through the second on-off valve 102. The use-side refrigerant that has flowed into the connection pipe i is sent to the use-side heat exchangers 22a and 22b through the connection pipes j and k. And flows into the connection pipe i ′. Here, the use-side refrigerant returns to the inlet side of the third refrigerant transfer device 28 in the heat source device e ″ via the fourth on-off valve 104 and the connection pipe o.
[0182]
When there is a request for heating in the indoor units g and h, a signal of a heating request is sent from the indoor unit to the control device 41 in the heat exchange unit d, and the use side refrigerant flow control valves 23a and 23b are opened. Further, the heating request signal is sent to the control device 42c in the heat source device e ″, and the heat source device e ″ starts operation according to the signal. The heat source device e ″ is a heat source device such as a general-purpose kerosene boiler or a gas boiler, and directly heats the circulating use-side refrigerant. Then, the control device 42c controls the amount of combustion of oil, gas, or the like so that the temperature of the refrigerant to be sent to the connection pipe o 'becomes a preset temperature. During the heating operation, the use-side refrigerant does not circulate in the heat exchange unit d, and there is no need to control the use-side refrigerant temperature, and thus it is not necessary to add a new temperature sensor. When all the requests for heating in the room disappear, the signal is sent from the indoor unit to the heat exchange unit d, and the heat source device e '' is stopped by a command from the control device 41 of the heat exchange unit d, and the flow rate of the use-side refrigerant is reduced. The control valves 23a and 23b are closed.
[0183]
As described above, according to the present embodiment, a part of the use-side refrigerant cycle is branched, and the heat source device e '' dedicated to heating is connected in parallel with the refrigerant storage tank 20, so that the outdoor air in winter In a region where the temperature is below freezing, even if the heating capacity of the heat pumps as the first and second refrigerant cycles is insufficient, the heating capacity can be easily secured. In addition, since the use-side refrigerant is directly heated by the heating boiler 29 installed in the heat source device e '', the heat-source-side refrigerant cycle and the use-side refrigerant cycle are separated and the heat exchange is performed more efficiently than in the heat exchanger. As a result, the energy consumption is reduced, the power consumption and the fuel consumption of kerosene and gas are reduced, and the running cost can be reduced.
[0184]
In the present embodiment, since the first to fourth on-off valves 101 to 104 are installed in the switching unit w, on-site construction and the like can be simplified when configuring the entire system, and workability is improved. And the appearance after installation is also good. In addition, if the fourth refrigerant transport device 105 is also installed in the switching unit w, it goes without saying that the workability is further improved and the appearance is improved.
[0185]
In the present embodiment, it is assumed that a general-purpose kerosene boiler in which the heating boiler 29 and the third refrigerant conveying device 28 are provided in an integrated unit is used as the heat source device e ″. In general, the third refrigerant transfer device 28 is a small-sized pump having a relatively small head and cannot transfer the use-side refrigerant at a sufficient flow rate necessary for heating to the use-side heat exchangers 22a and 22b by itself. Is connected in series to the third refrigerant transport device to compensate for the shortage of the head of the third refrigerant transport device. The fourth refrigerant transport device 105 may be installed on the refrigerant outlet side or the inlet side of the heat source device e ″. In addition, if the third refrigerant transfer device 28 is of a head that can transfer the use-side refrigerant at a sufficient flow rate necessary for heating in the use-side heat exchangers 22a and 22b, the fourth refrigerant transfer device 105 is not necessary. Needless to say.
[0186]
Embodiment 12 FIG.
FIG. 26 is a configuration diagram illustrating, for example, a cooling and heating device as a refrigeration and air conditioning device according to the twelfth embodiment. In the eleventh embodiment, the first to fourth on-off valves 101 to 104 are installed outside the heat exchange unit d. However, as shown in FIG. 26, they can be installed inside the heat exchange unit d. . In FIG. 26, a first opening / closing valve 101 is installed in the middle of the connection pipe s inside the heat exchange unit d and before reaching the inlet to the first refrigerant transfer device 21, and the first opening / closing valve 101 and the first opening / closing valve 101 are connected to each other. A branch is provided in the connection pipe s between the first refrigerant transport device 21 and the refrigerant outlet side of the heat source device e ″ incorporating the heating boiler 29 and the third refrigerant transport device 28. 'To connect. Also, the second on-off valve 102 is installed inside the heat exchange unit d of the connection pipe o '. In addition, a third on-off valve 103 is installed on the connection pipe i ′, and between the third on-off valve 103 and a branch (joining) portion of the connection pipes j ′ and k ′, and a refrigerant inlet of the heat source device e ″. Is connected with the connection pipe o. Then, the fourth on-off valve 104 is installed in the connection pipe o. These third and fourth on-off valves 103 and 104 are installed inside the heat exchange unit d.
[0187]
Next, the operation will be described.
During the cooling operation, the first and second heat source side refrigerant cycles are operated, and the heat source device e ″ is stopped. During the cooling operation, both the first and second heat source side refrigerant cycles become the refrigerant cycle indicated by the solid line in the figure. The operations of the first and second heat-source-side refrigerant cycles during the cooling operation are the same as those in the first embodiment, and will not be described.
On the other hand, in the use-side refrigerant cycle, during the cooling operation, the first on-off valve 101 and the third on-off valve 103 are opened, and the second on-off valve 102 and the fourth on-off valve 104 are closed. The relatively low-temperature use-side refrigerant 30 flowing out from the bottom of the left tank of the refrigerant storage tank 20 is connected to the use-side heat exchangers 22a and 22b by the first refrigerant transfer device 21 through the connection pipes i, j, and k. The air is cooled, and at the same time as the room air is cooled, the air itself is heated and returned to the tank on the right side of the refrigerant storage tank 20 through the connection pipes j ′ and k ′ and the connection pipe i ′. At this time, the second on-off valve 102 is closed in the middle of the connection pipe s, and the fourth on-off valve 104 is closed in the middle of the connection pipe i ′. Does not flow.
[0188]
During the heating operation, the first and second heat source side refrigerant cycles are stopped, and only the heat source device e ″ is operated. During the heating operation, the first on-off valve 101 and the third on-off valve 103 are closed, and the second on-off valve 102 and the fourth on-off valve 104 are opened during the use-side refrigerant cycle. The use-side refrigerant sent out by the third refrigerant transfer device 28 removes heat obtained by burning kerosene, gas, and the like in the heating boiler 29, and at the same time, is heated by itself, and the connection pipe o ′, the second opening and closing It flows into the connection pipe s through the valve 102. The use-side refrigerant that has flowed into the connection pipe s is further pressurized by the first refrigerant transfer device 21, and is sent to the use-side heat exchangers 22a and 22b through the connection pipe i and the connection pipes j and k. At the same time as the room air is heated, the air itself is cooled and flows into the connection pipes j ′ and k ′ and the connection pipe i ′. Here, the use-side refrigerant returns to the inlet side of the third refrigerant transfer device 28 in the heat source device e ″ via the fourth on-off valve 104 and the connection pipe o.
[0189]
As described above, since the heating operation is performed by the heat source device e ″ dedicated to heating, sufficient heating capacity can be obtained even when used in a place where the outside air temperature is low, and indoor comfort can be maintained.
Moreover, since the first to fourth on-off valves 101 to 104 are housed inside the heat exchange unit d, a new switching unit w as in the eleventh embodiment is not required, and the workability is improved and the appearance is improved. There is no loss. Further, in order to compensate for the shortage of the head of the third refrigerant transport device 28 housed in the heat source device e ″, the first refrigerant transport device d is installed inside the heat exchange unit d without installing a new refrigerant transport device. The shortage of the head can be compensated for by using the refrigerant transfer device 21 of the first embodiment, so that a refrigeration and air-conditioning device that is less expensive than the eleventh embodiment that requires the new refrigerant transfer device 105 can be provided.
[0190]
Embodiment 13 FIG.
In the refrigeration / air-conditioning apparatuses according to Embodiments 11 and 12, the first usage-side refrigerant cycle is configured with one system to switch between cooling and heating to air-condition the room. As described above, a use-side refrigerant cycle for cooling operation for performing cooling and a use-side refrigerant cycle for heating operation for performing heating may be provided so that they can be operated individually.
[0191]
FIG. 27 is a configuration diagram illustrating, for example, a cooling and heating device as the refrigeration and air conditioning device according to the present embodiment. In the figure, inside the indoor units g and h, cooling heat exchangers 22a and 22b and heating heat exchangers 22c and 22d are housed, respectively, and these are the flow of the indoor air sent by the indoor blowers 24a and 24b. On the other hand, cooling heat exchangers 22a and 22b are installed on the upstream side, and heating heat exchangers 22c and 22d are installed on the downstream side. Cooling heat exchangers 22a and 22b connect connection pipe i and connection pipes j 'and k' via use-side refrigerant flow control valves 23a and 23b and connection pipes j and k, similarly to the eleventh or twelfth embodiments. The refrigerant is connected to the heat exchange unit d via the connection pipe i ′ via the connection pipe i ′, thereby forming a use-side refrigerant cycle during cooling. On the other hand, the heating heat exchangers 22c and 22d are connected to the connection pipe o 'through the use side refrigerant flow control valves 23c and 23d and the connection pipes x and z, and are connected through the connection pipes x' and z '. o. The connection pipes o and o 'are pipes connected to the heat source device e''dedicated to heating, and constitute a use-side refrigerant cycle dedicated to heating.
[0192]
Next, the operation will be described.
During the cooling operation, the first and second heat source side refrigerant cycles are operated, and the heat source device e ″ is stopped. During the cooling operation, both the first and second heat source side refrigerant cycles become the refrigerant cycle indicated by the solid line in the figure. The operations of the first and second heat-source-side refrigerant cycles during the cooling operation are the same as those in the first embodiment, and will not be described.
On the other hand, in the use-side refrigerant cycle at the time of cooling, the relatively low-temperature use-side refrigerant 30 flowing out from the bottom of the left tank of the refrigerant storage tank 20 passes through the connection pipe s and is connected by the first refrigerant transfer device 21 to the connection pipe. i, j, and k, are sent to the use-side heat exchangers 22a and 22b through the use-side refrigerant flow control valves 23a and 23b, and are cooled at the same time as the room air is heated, so that the connection pipes j ′ and k ′ and It returns to the tank on the right side of the refrigerant storage tank 20 through the connection pipe i '. At this time, since the heat source device e ″ is stopped, the use-side refrigerant cycle dedicated to heating does not function, and the heating heat exchangers 22c and 22d do not contribute to air conditioning.
[0193]
During the heating operation, the first and second heat source side refrigerant cycles are stopped, and only the heat source device e ″ is operated. During the heating operation, the cooling use-side refrigerant cycle does not function, and the cooling heat exchangers 22a and 22b do not contribute to air conditioning.
On the other hand, in the heating-side use-side refrigerant cycle dedicated to heating, the use-side refrigerant sent out by the third refrigerant conveyance device 28 is heated at the same time as the heating boiler 29 deprives the heating boiler of heat obtained by burning kerosene, gas, and the like. And flows out to the connection pipe o '. A fourth refrigerant transport device 105 is installed in the connection pipe o ′, whereby the heating-side use-side refrigerant is further pressurized, and the connection pipes x and z and the use-side refrigerant flow control valves 23c and 23d are moved. Then, the air is sent to the heating heat exchangers 22c and 22d to heat the indoor air, and at the same time, cools itself, and passes through the connection pipes x ′ and z ′ and the connection pipe o to the third in the heat source device e ″. Returns to the inlet side of the refrigerant transport device 28.
[0194]
When there is a request for cooling in the indoor units g and h, the use side refrigerant flow control valves 23c and 23d connected to the heating heat exchangers 22c and 22d in the indoor units g and h are closed, and the cooling heat exchanger is used. The use side refrigerant flow control valves 23a and 23b connected to 22a and 22b are opened. At the same time, a signal of a cooling request is sent from the indoor unit to the control device 41 in the heat exchange unit d, and the first and second outdoor units e and e 'start operating according to the signal. The operating capacity of the first and second outdoor units e and e 'is determined by the detection of the first temperature sensor 31 installed in the connection pipe r after the downstream and the second auxiliary heat exchangers 19a and 19b merge. Control is performed so that the temperature approaches a preset target temperature. When all the requests for cooling are gone indoors, the signal is sent from the indoor unit to the heat exchange unit d, and the first and second outdoor units e and e 'are stopped by a command from the control device 41 of the heat exchange unit d. At the same time, the use-side refrigerant flow control valves 23a and 23b are closed.
[0195]
When there is a request for heating in the indoor units g and h, the use side refrigerant flow control valves 23c and 23d connected to the heating heat exchangers 22c and 22d in the indoor units g and h are opened, and the cooling heat exchanger is opened. The use side refrigerant flow control valves 23a and 23b connected to 22a and 22b are closed. At the same time, a signal of a heating request is sent from the indoor unit to the control device 41 in the heat exchange unit d, and further, this heating request signal is sent to the control device 42c in the heat source device e ″, and the heat source device e ″ Starts operation according to the signal. Since the heat source device e '' is a general-purpose kerosene boiler, gas boiler, etc. heating device, the amount of combustion of kerosene or gas is controlled so that the temperature of the refrigerant sent to the connection pipe o 'becomes a preset temperature. I do. Therefore, during the heating operation, the heat exchange unit d does not particularly need to control the use-side refrigerant temperature and does not need to add a new temperature sensor. When all the requests for heating in the room disappear, the signal is sent from the indoor unit to the heat exchange unit d, and the heat source device e '' is stopped by a command from the control device 41 of the heat exchange unit d, and the flow rate of the use-side refrigerant is reduced. The control valves 23c and 23d are closed.
With this configuration, it is possible to secure a sufficient heating capacity and maintain a temperature suitable for using heat, and to independently control a refrigerant cycle dedicated to heating and a refrigerant cycle dedicated to cooling, which is suitable for a use situation. Inexpensive refrigeration and air-conditioning system that can perform
[0196]
When there is a request for dehumidification in the indoor units g and h, the use side refrigerant flow control valves 23c and 23d connected to the heating heat exchangers 22c and 22d in the indoor units g and h are opened, and the cooling heat is released. The use side refrigerant flow control valves 23a and 23b connected to the exchangers 22a and 22b are also opened. At the same time, a heating request signal is sent from the indoor units g and h to the control device 41 in the heat exchange unit d, and the heating request signal is further transmitted to the first and second outdoor units e and e ′ and the heat source device e ′. And they start driving according to the signal.
The indoor air sent by the blowers 24a, 24b in the indoor units g, h first flows into the cooling heat exchangers 22a, 22b, where they exchange heat with the refrigerant in the cooling use side refrigerant cycle. It is cooled and dehumidified. Next, the cooled and dehumidified air flows into the heating heat exchangers 22c and 22d, exchanges heat with the refrigerant in the use-side refrigerant cycle dedicated to heating, and is heated. The temperature is adjusted to almost the same as the temperature and is blown into the room. When all the requests for dehumidification disappear in the room, the signal is sent from the indoor unit to the heat exchange unit d, and the first and second outdoor units e, e ′, and All the heat source devices e ″ dedicated to heating are stopped, and the use-side refrigerant flow control valves 23a to 23d are also closed.
[0197]
As described above, in the present embodiment, the heat exchanger for cooling and the heat exchanger for heating are provided in the indoor unit, and the heat exchanger for cooling is used for the flow of the indoor air sent by the blower. And a heat exchanger for heating. For this reason, the indoor air cooled and dehumidified by the cooling heat exchangers 22a and 22b during the dehumidifying operation is heated again by the heating heat exchangers 22c and 22d, and adjusted to a temperature substantially equal to the original indoor air temperature. Can be blown indoors. Conventionally, the cooled and dehumidified air is directly blown into the room, and the configuration according to the present embodiment can provide a comfortable dehumidifying space without giving the occupants a feeling of cool air during the dehumidifying operation.
[0198]
Note that the cooling heat exchangers 22a and 22b and the heating heat exchangers 22c and 22d serve as cooling heat exchangers 22a and 22b and a heating heat exchanger 22c for the flow of room air sent by the blowers 24a and 24b. , 22d are arranged in series in this order, but they may be arranged in parallel to the flow of room air. Conversely, it is better not to install the heating heat exchangers 22c and 22d and the cooling heat exchangers 22a and 22b in series with respect to the flow of room air. When installed in this way, once heated air must be further reduced to below the dew point in order to dehumidify, so cooling capacity more than the amount of heating is required, energy is wasted, and a feeling of cool wind is felt. Not resolved.
[0199]
Further, since the cooling-use refrigerant cycle and the heating-only refrigerant cycle are configured independently, it is also possible to use one of the indoor units for cooling and the other indoor unit for heating. That is, the cooling / heating of the use-side heat exchangers can be individually controlled, and in practice, if the use-side refrigerant flow control valves 23a to 23d are performed according to the use request, the operation / stop of the heat exchangers 22a to 22d is optional. Can be controlled.
[0200]
Embodiment 14 FIG.
In the eighth embodiment, an example has been shown in which the heat transfer area of the use-side refrigerant, for example, water, is increased in order to reduce the size of the auxiliary heat exchangers 16a and 16b provided in the refrigerant storage tank 20. In the embodiment, a configuration for improving the heat transfer coefficient of the usage-side refrigerant will be described.
[0201]
FIG. 28 is a configuration diagram showing, as a refrigeration / air-conditioning apparatus according to the present embodiment, for example, a cooling / heating apparatus for cooling / heating a room. In the figure, an air pipe 112 is installed in a refrigerant storage tank 20, air is sent from the air conveying device 111 into the air pipe 112, and air is supplied from below the auxiliary heat exchangers 16a and 16b provided in the refrigerant storage tank 20. Air is blown out from a small hole opened in the tube 112. That is, the air transfer device 11 and the air pipe 112 constitute a bubble blowing unit that blows bubbles around the auxiliary heat exchangers 16a and 16b in the refrigerant storage tank 20. When air bubbles are blown around the auxiliary heat exchangers 16a and 16b, the use-side refrigerant stored in the refrigerant storage tank 20 is stirred by the air bubbles, and the heat transfer coefficient of the use-side refrigerant is improved. Therefore, the size of the auxiliary heat exchangers 16a and 16b can be reduced, and the power receiving capacity can be reduced.
According to the literature on the research on the ice heat storage system of the Air Conditioning and Sanitary Engineering Academic Papers 7 ('87 .10.6-10.8 Tokyo), 0.3 [m 3 / Hm 2 It has been found that blowing out bubbles with a flow rate of about] can provide a heat transfer coefficient of the use-side refrigerant that is about 1.5 times that of natural convection. Therefore, if the air flow rate is set based on this, an efficient refrigeration / air-conditioning apparatus can be obtained.
[0202]
The air conveying device 111 according to the present embodiment includes a blower such as a blower or the like that generates a static pressure exceeding a liquid head determined by the distance between the liquid level of the refrigerant storage tank 20 and the lowermost part of the air pipe 112 in the refrigerant storage tank 20. It is a pump. Reference numeral 113 denotes a partition plate installed in the refrigerant storage tank 20 below the air pipe 112 so as to prevent the use-side refrigerant transfer device 21 from sucking air bubbles blown into the refrigerant storage tank 20. It is arranged. That is, the upper side of the partition plate 113 is a portion where bubbles of the use-side refrigerant are present, and the lower side of the partition plate 113 is a portion where no bubbles are present. It is provided in a portion where no bubbles exist.
[0203]
28 shows an example in which the partition plate 113 is installed separately from the air pipe 112, but may be integrated with the air pipe 112 as shown in FIG. With this configuration, the air pipe 112 and the partition plate 113 can be manufactured compactly and at low cost.
In addition, the air conveying device 111 may directly inhale the outside air and blow air as bubbles into the refrigerant storage tank 20, but in order to further reduce heat loss, as shown in FIG. It is better to suck in from the space open to the outside air at the overflow port 114.
Further, the bubble blowing port from the air conveying device 113 is not limited to being provided at the bottom of the refrigerant storage tank 20, and if it is configured to blow bubbles at least around the auxiliary heat exchangers 16a and 16b, heat The heat transfer coefficient can be improved by the stirring action around the exchanger 16a. Further, for example, a configuration may be adopted in which bubbles are blown from the side surface of the refrigerant storage tank 20.
The bubble blowing means does not have a configuration in which air is blown by the air conveying device 111, and has the same effect even when bubbles are generated in the refrigerant storage tank 20 by electrolysis.
[0204]
Further, when the heating boiler 29 which is the third heat source side refrigerant cycle e ″ is used, as shown in FIG. 28, the sixth auxiliary heat exchanger 19 c is connected to the usage side refrigerant inflow port to the refrigerant storage tank 20. And heat exchange with the fifth auxiliary heat exchanger 16c through which the heat source side refrigerant of the heating boiler 29 flows.
[0205]
When the third heat source side refrigerant cycle e ″ is used, the configuration may be as shown in FIG. In the figure, each end of the sixth auxiliary heat exchanger 19c is connected to a lower portion and an upper portion where the height of the refrigerant storage tank 20 is different by a refrigerant pipe. Then, heat exchange is performed between the utilization side refrigerant flowing through the sixth auxiliary heat exchanger 19c and the refrigerant circulating through the fifth auxiliary heat exchanger 16c of the third heat source side refrigerant cycle e ″.
The use-side refrigerant heated by the sixth auxiliary heat exchanger 19c has a lower density, so as to rise in the auxiliary heat exchanger 19c and flow into the upper part of the refrigerant storage tank 20. On the other hand, the unheated, high-density use-side refrigerant flows from the lower portion of the refrigerant storage tank 20 into the sixth auxiliary heat exchanger 19c, circulates from the lower portion, and stores heat in the refrigerant storage tank 20. The use-side refrigerant in the use-side refrigerant storage tank 20 is sent to the use-side heat exchangers 22a and 22b by the use-side refrigerant transfer device 21 to heat the room.
[0206]
When configured as shown in FIG. 30, when heating is performed by the use-side heat exchangers 22a and 22b, the sixth auxiliary heat exchanger 19c becomes a separate system from the use-side refrigerant cycle, and the refrigerant of the use-side heat exchangers 22a and 22b is changed. It is possible to stably circulate the refrigerant of the use-side refrigerant cycle without reducing the circulation flow rate by the auxiliary heat exchanger 19c. In addition, the driving force for circulating the use-side refrigerant to the sixth auxiliary heat exchanger 19c is a density difference generated from the temperature difference of the use-side refrigerant, and the refrigerant transfer device is not required, so that the efficiency of the system can be improved. The thicker the refrigerant pipe that connects the sixth auxiliary heat exchanger 19c and the refrigerant storage tank 20 is, the smaller the pressure loss is and the higher the efficiency is. However, if the refrigerant pipe is too thick, the flow rate of the use-side refrigerant becomes slow, and the sixth auxiliary The heat exchange efficiency of the heat exchanger 19c decreases.
[0207]
In Embodiments 1 to 14, the use-side refrigerant is water or an aqueous solution containing at least one or more of a solvent such as ethylene glycol, propylene glycol, and D-sorbitol in a weight ratio of several tens% or less. However, in the case of water, as described in the tenth embodiment, it is easy to handle, for example, the use side refrigerant can be filled with tap water at the time of installation work. Further, since the flow rate can be increased, the heat transfer capacity can be increased. In addition, since the head of the refrigerant transport device on the user side becomes large and water can be circulated far without increasing the capacity of the refrigerant transport device, it can be applied to high-rise houses and buildings with large site areas. .
[0208]
In the above embodiment, the number of indoor units is two. However, the number of indoor units is not limited thereto, and may be one or three or more.
[0209]
In the above-described first to fourteenth embodiments, an example has been described in which the present invention is applied to a cooling and heating device that performs indoor cooling and heating as an example of a refrigeration and air conditioning device. However, the present invention is not limited to this. It can be used for various purposes such as using cold or hot heat for heating such as hot water supply, floor heating, heating and drying of bathrooms, etc. in the use-side refrigerant cycle, cooling industrial and home refrigerators and the like. When the water is used for hot water supply and the use-side refrigerant is water, the refrigerant stored in the refrigerant storage tank 20 may be used as it is, and thus the use-side heat exchanger is not required.
In the first to fourteenth embodiments, the use-side refrigerant is stored in the refrigerant storage tank. However, the refrigerant storage tank is connected to the heat-source-side refrigerant cycle to store the heat-source-side refrigerant. It may be. At this time, in the usage-side refrigerant cycle, the heat or cold stored in the refrigerant storage tank may be extracted by the auxiliary heat exchanger. By storing heat with the heat source side refrigerant, cold or warm heat can be stored by using a refrigerant having high energy efficiency, and the size of the refrigerant storage tank can be reduced to reduce the size of the entire device configuration.
[0210]
【The invention's effect】
The present invention is configured as described above, and has the following effects.
[0211]
According to the first aspect of the present invention, the heat-source-side refrigerant is exchanged by the auxiliary heat exchanger provided between the heat-source-side refrigerant cycle for circulating the heat-source-side refrigerant and the use-side refrigerant cycle for circulating the use-side refrigerant. In a refrigeration / air-conditioning system that uses heat obtained in a cycle for heating in the use-side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use-side refrigerant, and the heat-source-side refrigerant is used during a heating operation of the use-side refrigerant cycle. By filling the amount of the use-side refrigerant so as to maintain the temperature of the use-side refrigerant during the defrosting operation at a temperature suitable for heating, hot water supply, or heating and drying, the heat source-side refrigerant cycle during the heating operation is performed. A refrigeration and air-conditioning system that can stabilize the temperature of the use-side refrigerant and reduce the amount of refrigerant that is problematic in terms of global environmental protection and handling in the defrosting operation of It is.
[0212]
According to claim 2 of the present invention, the amount of heat deprived from the use-side refrigerant cycle by the auxiliary heat exchanger by the defrosting operation of the heat-source-side refrigerant cycle is Qd, the amount of the use-side refrigerant is W, and the amount of the use-side refrigerant is W. When the specific heat is Cp and the defrosting operation is performed in the heat source-side refrigerant cycle during the heating operation of the usage-side refrigerant cycle, the temperature decrease of the usage-side refrigerant represented by Qd / (W · Cp) is equal to or lower than a predetermined temperature. By filling the amount W of the use side refrigerant so as to maintain the temperature of the use side refrigerant at a temperature suitable for heating or hot water supply or heating and drying, the defrosting of the heat source side refrigerant cycle during the heating operation is performed. A refrigeration and air-conditioning system that can stabilize the temperature of the use-side refrigerant during operation, maintain a temperature suitable for using heat, and reduce the amount of refrigerant that is problematic in global environmental conservation and handling is obtained. Can be
[0213]
According to a third aspect of the present invention, there is provided a heat storage means provided in a use-side refrigerant cycle for storing heat obtained in the heat-source-side refrigerant cycle, and the auxiliary heat exchanger is operated by a defrosting operation of the heat-source-side refrigerant cycle. The amount of heat deprived from the use-side refrigerant cycle is Qd, the amount of heat radiated from the heat storage means by the defrosting operation is Qt, the amount of the use-side refrigerant is W, and the specific heat of the use-side refrigerant is Cp. When the defrosting operation is performed in the heat source side refrigerant cycle during the heating operation of the refrigerant cycle, the temperature decrease of the use side refrigerant represented by (Qd−Qt) / (W · Cp) becomes equal to or lower than a predetermined temperature. By filling the amount W of the use-side refrigerant and setting the heat storage capacity of the heat storage means, and maintaining the temperature of the use-side refrigerant at a temperature suitable for heating, hot water supply, or heating and drying, heat during the heating operation is obtained. For the defrosting operation of the side refrigerant cycle, the temperature of the use side refrigerant can be stabilized, the temperature suitable for using heat can be maintained, and the amount of refrigerant that has problems in global environment conservation and handling is reduced. Thus, a refrigeration / air-conditioning apparatus can be obtained which can be reduced in size by reducing the amount of refrigerant charged.
[0214]
According to claim 4 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating a heat source side refrigerant and a use side refrigerant cycle for circulating a use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, while using a refrigerant that utilizes sensible heat as the use side refrigerant, the use side refrigerant is used in the use side refrigerant cycle. Providing a refrigerant storage tank to store, the internal volume of the refrigerant storage tank, heating or hot water supply or the temperature of the utilization side refrigerant when the heat source side refrigerant cycle defrosting operation during the heating operation of the utilization side refrigerant cycle. The amount of the use-side refrigerant or the amount of the heat storage material is set to an internal volume that can be stored so as to maintain the temperature suitable for heating and drying, so that the heat source-side refrigerant size during the heating operation is increased. By reducing the temperature drop of the use-side refrigerant and stabilizing the temperature of the use-side refrigerant, it is possible to maintain the temperature suitable for the use of thermal energy, while maintaining the global environment preservation and handling problems. A refrigeration / air-conditioning apparatus that can reduce the usage of a certain refrigerant can be obtained.
[0215]
According to claim 5 of the present invention, the compressor, the flow path switching valve, the heat source side heat exchanger, the heat source side refrigerant flow control valve, and the first auxiliary heat exchanger are connected to circulate the heat source side refrigerant. A heat source side refrigerant cycle, a second auxiliary heat exchanger that exchanges heat with the first auxiliary heat exchanger, a refrigerant storage tank, a refrigerant transport device, and a use side heat exchanger are connected to circulate the use side refrigerant. Having a use side refrigerant cycle, the compressor, the flow path switching valve, the heat source side heat exchanger, the heat source side refrigerant flow control valve, the first auxiliary heat exchanger, the second auxiliary heat exchanger, By storing the refrigerant storage tank and the refrigerant transport device in one unit, the temperature of the use-side refrigerant during the defrosting operation can be stabilized and maintained at a temperature suitable for using heat, and can be used for loading and construction. A refrigeration and air-conditioning system that can save time and effort Obtained.
[0216]
A refrigeration / air-conditioning apparatus according to claim 6 of the present invention connects a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a first auxiliary heat exchanger to supply heat source side refrigerant. A heat source side refrigerant cycle circulated, a second auxiliary heat exchanger that exchanges heat with the first auxiliary heat exchanger, a refrigerant storage tank, a refrigerant transport device, and a use side heat exchanger are connected to circulate the use side refrigerant. Wherein the compressor, the flow path switching valve, the heat source side heat exchanger, and the heat source side refrigerant flow control valve are housed in one unit, and the first auxiliary The heat exchanger, the second auxiliary heat exchanger, the refrigerant storage tank, and the refrigerant transport device are housed in a separate unit from the unit, and one end of the first auxiliary heat exchanger and the flow The other end of the first auxiliary heat exchanger between the first and second auxiliary heat exchangers; And the heat source-side refrigerant flow control valve are connected by connecting pipes, thereby stabilizing the temperature of the use-side refrigerant during the defrosting operation and maintaining the temperature suitable for using heat, and a standard outdoor unit. And an inexpensive refrigeration and air-conditioning system using the same is obtained.
[0217]
According to claim 7 of the present invention, the compressor, the flow path switching valve, the heat source side heat exchanger, the heat source side refrigerant flow control valve, and the first auxiliary heat exchanger are connected to circulate the heat source side refrigerant. A heat source-side refrigerant cycle, a first refrigerant transfer device, a second auxiliary heat exchanger for exchanging heat with the first auxiliary heat exchanger, and heat transfer formed by connecting the refrigerant storage tank and circulating a use-side refrigerant. A second refrigerant transfer device, a use-side heat exchanger, and a use-side refrigerant cycle that connects the refrigerant storage tank and circulates the use-side refrigerant. The heat obtained by exchanging heat with the first auxiliary heat exchanger in the auxiliary heat exchanger is stored in the refrigerant storage tank, and the heat stored in the refrigerant storage tank in the usage-side refrigerant cycle is stored in the usage-side heat exchanger. Temperature control by using for heating Stable easily, can be maintained to a temperature suitable for thermal utilization and refrigeration air conditioning system which can reduce the amount of the refrigerant that has a problem on global environmental conservation and handling can be obtained.
[0218]
According to claim 8 of the present invention, the inside of the refrigerant storage tank is divided into right and left, and a partition having a communication portion that can communicate with the divided right and left usage side refrigerant below a draft surface is provided. Two openings are provided in each of the divided left and right tanks, and two openings of one of the tanks of the refrigerant storage tank are provided with an inlet of the use-side refrigerant from the use-side heat exchanger and a second auxiliary heat source. An outlet for the use-side refrigerant to an exchanger, and two openings in the other tank of the refrigerant storage tank are provided with an inlet for the use-side refrigerant from the second auxiliary heat exchanger and the use-side heat exchange. By using the outlet of the use-side refrigerant to the vessel, it is possible to obtain a refrigeration / air-conditioning apparatus capable of efficiently operating the heat-source-side refrigerant cycle and sufficiently storing heat in the refrigerant storage tank to realize comfortable refrigeration / air-conditioning.
[0219]
According to the ninth aspect of the present invention, the auxiliary heat exchanger that exchanges heat between the heat-source-side refrigerant and the use-side refrigerant is a plate-type heat exchanger, so that a small-capacity refrigerant transfer device can be used. Thus, an inexpensive refrigeration air conditioner can be obtained.
[0220]
According to claim 10 of the present invention, the cooling operation and the heating operation include switching means for switching the flow direction of the use-side refrigerant in the auxiliary heat exchanger between the heat-source-side refrigerant cycle and the use-side refrigerant cycle, The flow direction of the heat-source-side refrigerant and the use-side refrigerant at the time of heat exchange in the auxiliary heat exchanger is configured so as to be counter-current during both the cooling operation and the heating operation, so that both the cooling and heating operations are efficiently performed. A refrigeration / air-conditioning apparatus capable of performing heat exchange, stabilizing the temperature of the use-side refrigerant during the defrosting operation, and maintaining the temperature at a temperature suitable for utilizing heat can be obtained.
[0221]
According to the eleventh aspect of the present invention, a heat source formed by connecting a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and an auxiliary heat exchanger to circulate a heat source side refrigerant. Side refrigerant cycle, a refrigerant storage tank for storing the usage-side refrigerant, and a usage-side refrigerant cycle connected to a refrigerant transport device and circulating the usage-side refrigerant, wherein the auxiliary heat exchanger is disposed inside the refrigerant storage tank. The auxiliary heat exchanger immerses the heat source-side refrigerant and the use-side refrigerant in heat and stores heat in the refrigerant storage tank, and stores heat in the refrigerant storage tank in the use-side refrigerant cycle. By utilizing the heat generated for heating, the temperature of the use side refrigerant during the defrosting operation can be stabilized, the equipment of the heat source side refrigerant cycle can be downsized, and the overall system can be constructed with a relatively simple device configuration. For reliability Can, refrigeration air conditioning system is obtained which can reduce the amount of the refrigerant that has a problem on the environmental protection and handling.
[0222]
According to the twelfth aspect of the present invention, since the heat transfer area of the use-side refrigerant in the auxiliary heat exchanger is made larger than the heat transfer area of the heat-source-side refrigerant, heat exchange between the heat-source-side refrigerant and the use-side refrigerant is achieved. A refrigeration / air-conditioning apparatus capable of improving the heat transfer performance of the refrigerant and stabilizing the temperature of the use-side refrigerant during the defrosting operation is obtained.
[0223]
Further, according to the thirteenth aspect of the present invention, by providing the bubble blowing means for blowing bubbles around the auxiliary heat exchanger in the refrigerant storage tank, heat transfer performance in heat exchange between the heat source side refrigerant and the use side refrigerant is provided. And a refrigeration / air-conditioning system capable of stabilizing the temperature of the use-side refrigerant during the defrosting operation can be obtained.
[0224]
According to the fourteenth aspect of the present invention, a use-side refrigerant pipe provided outside the refrigerant storage tank and connecting positions where the height of the refrigerant storage tank is different, and a use-side refrigerant flowing through the use-side refrigerant pipe By using the heat source device for heating the refrigerant, the use-side refrigerant can be heated with a relatively simple configuration, and this heating does not affect the refrigerant circulation of the use-side refrigerant cycle, thereby improving the efficiency of the system. A refrigeration and air conditioning device is obtained.
[0225]
Further, according to claim 15 of the present invention, the compressor, the flow path switching valve, the heat source side heat exchanger, the heat source side refrigerant flow control valve, the auxiliary heat exchanger, the refrigerant storage tank, and the refrigerant conveying device are one unit. The refrigeration and air-conditioning system that can stabilize the temperature of the use-side refrigerant during the defrosting operation and maintain it at a temperature suitable for using heat, thereby preventing trouble in carrying in and construction work, is obtained. Can be
[0226]
According to claim 16 of the present invention, the compressor, the flow path switching valve, the heat source side heat exchanger, and the heat source side refrigerant flow control valve are housed in one unit, and the auxiliary heat exchanger, the refrigerant storage The tank, and the refrigerant transfer device is housed in another unit separate from the unit, and between one end of the auxiliary heat exchanger and the flow path switching valve and the other end of the auxiliary heat exchanger and By connecting to the heat source side refrigerant flow control valve with a connection pipe, by stabilizing the temperature of the use side refrigerant during the defrosting operation, it is possible to maintain the temperature suitable for using heat, and the standard outdoor unit An inexpensive refrigeration and air-conditioning device that can be used is obtained.
[0227]
Further, according to the seventeenth aspect of the present invention, by providing the heat storage material in the refrigerant storage tank for storing the use-side refrigerant, it is possible to obtain a refrigeration air-conditioning apparatus capable of sufficiently storing heat in the refrigerant storage tank and reducing the size of the tank. Can be
[0228]
According to claim 18 of the present invention, the partition is provided in the refrigerant storage tank and divides the inside into right and left, and the opening through which the use-side refrigerant provided in one of the divided tanks flows in is provided. An opening through which the usage-side refrigerant provided in the other tank flows out, and the partition has a communication portion through which the divided left and right usage-side refrigerants communicate below the draft surface of the refrigerant storage tank. Thus, a refrigeration / air-conditioning apparatus capable of efficiently operating the heat source-side refrigerant cycle and sufficiently storing heat in the refrigerant storage tank to realize comfortable air conditioning is obtained.
[0229]
According to the nineteenth aspect of the present invention, a filter for collecting contaminants mixed in the use-side refrigerant is provided in a portion where the use-side refrigerant circulates, so that contaminants such as dust and dirt are contained in the use-side refrigerant. Can be prevented from circulating, and a highly reliable refrigeration and air-conditioning apparatus can be obtained.
[0230]
According to the twentieth aspect of the present invention, since the filter is provided in the refrigerant storage tank that stores the use-side refrigerant, the filter is easy to manage, and contaminants such as dirt and dust circulate in the use-side refrigerant. And a highly reliable refrigeration air conditioner can be obtained.
[0231]
According to the twenty-first aspect of the present invention, the temperature of the use-side refrigerant during the defrosting operation is stabilized by maintaining the temperature of the use-side refrigerant at the time of defrosting operation by using a plurality of heat source-side refrigerant cycles of two or more systems. In addition, a small-sized standard heat source-side refrigerant cycle can be used, and an inexpensive refrigeration / air-conditioning apparatus can be obtained.
[0232]
According to claim 22 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating the heat source side refrigerant and a use side refrigerant cycle for circulating the use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use side refrigerant, and the heat source side refrigerant cycle is a plurality of two or more systems. The heat source side refrigerant cycle of at least one system is constituted by a refrigerant cycle dedicated to heating, thereby stabilizing the temperature of the use side refrigerant during the defrosting operation, thereby maintaining a temperature suitable for using heat, and a small size. An inexpensive refrigeration and air-conditioning system that can use a standard heat source-side refrigerant cycle and that can reduce the amount of refrigerant that is problematic in terms of global environmental conservation and handling is obtained.
[0233]
According to the twenty-third aspect of the present invention, the plurality of heat-source-side refrigerant cycles are connected in parallel to the use-side refrigerant cycle, so that each of the heat-source-side refrigerant cycles can be independently controlled, and inexpensive refrigeration and air conditioning. A device is obtained.
[0234]
According to claim 24 of the present invention, by connecting a plurality of heat-source-side refrigerant cycles in series with respect to the use-side refrigerant cycle, a small-sized standard heat-source-side refrigerant cycle can be used, and connection of piping can be reduced. A relatively simple and inexpensive refrigeration / air-conditioning apparatus can be obtained.
[0235]
According to the twenty-fifth aspect of the present invention, the heat source-side refrigerant cycle is provided with at least one heating-only refrigerant cycle and one cooling / heating-use refrigerant cycle, and the heating-side refrigerant cycle is used for the utilization-side refrigerant cycle. By connecting the cycle and the cooling / heating combined refrigerant cycle in series, the heating capacity can be sufficiently secured even when used in a place where the outside air temperature is low, and the temperature of the use-side refrigerant during the defrosting operation is stabilized. Thus, a refrigeration / air-conditioning apparatus capable of maintaining a temperature suitable for utilizing heat can be obtained.
[0236]
According to the twenty-sixth aspect of the present invention, the cooling / heating combined use refrigerant cycle is connected to the upstream side with respect to the flow direction of the use side refrigerant circulating in the use side refrigerant cycle, and the heating-only refrigerant cycle is connected downstream. By connecting to the side, the heat source side refrigerant cycle can be used effectively, sufficient heating capacity can be secured even when used in a place with low outside air temperature, and the temperature of the use side refrigerant during defrosting operation is stabilized and the heat A refrigeration / air-conditioning device that can be maintained at a temperature suitable for use is obtained.
[0237]
According to claim 27 of the present invention, the refrigerant cycle dedicated to heating is connected to the upstream side with respect to the flow direction of the use-side refrigerant circulating in the use-side refrigerant cycle, and the refrigerant cycle combined with cooling / heating is connected to the downstream side. Refrigeration and air conditioning that can secure sufficient heating capacity even when used in places with low outside air temperature, stabilize the temperature of the use-side refrigerant during defrosting operation, and maintain it at a temperature suitable for using heat. A device is obtained.
[0238]
According to claim 28 of the present invention, the heat source-side refrigerant cycle is provided with at least one heating-only refrigerant cycle and one cooling / heating-use refrigerant cycle, and the heating-side refrigerant cycle is provided with respect to the utilization-side refrigerant cycle. The cycle is connected in parallel with the cooling / heating combined refrigerant cycle, and the use side refrigerant is prevented from flowing to the use side auxiliary heat exchanger that exchanges heat with the refrigerant cycle dedicated to heating during the cooling operation. By providing the switching means for switching the refrigerant flow path of the refrigerant cycle, it is possible to maintain the temperature suitable for utilizing heat, and to independently control the refrigerant cycle dedicated to heating and the refrigerant cycle combined with cooling / heating. And a refrigeration / air-conditioning apparatus capable of performing an operation suitable for the air conditioner.
[0239]
According to claim 29 of the present invention, the heat source-side refrigerant cycle is provided with at least one heating-only refrigerant cycle and at least one cooling-only refrigerant cycle, and the heating-side refrigerant cycle is provided with the heating-only refrigerant cycle. By connecting the refrigerant cycle dedicated to the cooling in series, it is possible to sufficiently secure the heating capacity even when used in a place where the outside air temperature is low, and to stabilize the temperature of the use-side refrigerant during the defrosting operation and use the heat. An inexpensive refrigeration / air-conditioning apparatus that can be maintained at a suitable temperature and is inexpensive can be obtained.
[0240]
According to claim 30 of the present invention, the heat source-side refrigerant cycle is provided with at least one system of a heating-only refrigerant cycle and a cooling-only refrigerant cycle, and the heating-side refrigerant cycle is provided with the heating-only refrigerant cycle. The cooling-only refrigerant cycle is connected in parallel with the cooling-only refrigerant cycle, and the usage-side refrigerant is circulated to the usage-side auxiliary heat exchanger that exchanges heat with the heating-only refrigerant cycle during the heating operation, and the cooling-only refrigerant cycle during the cooling operation. By providing switching means for switching the refrigerant flow path of the use-side refrigerant cycle so as to circulate the use-side refrigerant to the use-side auxiliary heat exchanger that exchanges heat, the heating capacity is sufficiently secured and suitable for use of warm heat. Temperature can be maintained, and the refrigerant cycle dedicated to heating and the refrigerant cycle dedicated to cooling can be controlled independently of each other. Inexpensive refrigeration and air conditioning device can be obtained.
[0241]
Further, according to claim 31 of the present invention, a heating-only heat source device in which the use-side refrigerant circulates, and the use-side refrigerant cycle to circulate the use-side refrigerant to the heating-only heat source device during the heating operation. With the provision of the switching means for switching the refrigerant flow path, it is possible to obtain a refrigerating air-conditioning apparatus capable of sufficiently securing the heating capacity even when used in a place where the outside air temperature is low and maintaining the temperature suitable for utilizing the heat.
[0242]
According to claim 32 of the present invention, the use-side refrigerant cycle includes a cooling use-side heat exchanger that is supplied with heat by the heat-source-side refrigerant cycle, and heating that is supplied with heat by the heat source device dedicated to heating. A heating-side heat exchanger for operating the heat source-side refrigerant cycle and the cooling-use side heat exchanger during the cooling operation, and a heating-only heat source device and the heating-side use heat during the heating operation. By configuring the heat exchanger to operate, it is possible to obtain a refrigeration / air-conditioning apparatus that can maintain a temperature suitable for utilizing heat and can individually control cooling / heating of the use-side heat exchanger.
[0243]
According to claim 33 of the present invention, the cooling use-side heat exchanger is arranged side by side with respect to the air flow on the upstream side of the heating use-side heat exchanger, and the cooling use-side heat exchanger during the dehumidifying operation. By operating the use side heat exchanger for heating, comfortable dehumidification can be performed, and even when used in a place with low outside air temperature, sufficient heating capacity is secured and suitable for use of warm heat A refrigeration / air-conditioning device that can be maintained at a temperature is obtained.
[0244]
According to the thirty-fourth aspect of the present invention, the heating-only heat source device is a heating device that directly heats the use-side refrigerant, so that the heating capacity can be sufficiently increased even when used in a place where the outside air temperature is low. Thus, it is possible to obtain an inexpensive refrigeration and air-conditioning apparatus which can secure the temperature suitable for utilizing the heat and can reduce the running cost.
[0245]
Further, according to claim 35 of the present invention, in the pipes constituting the use side refrigerant cycle, the feed side pipe to the use side heat exchanger and the return side pipe from the use side heat exchanger, By configuring the pipe diameter or the diameter or shape of the joint of the pipe to be different, it is possible to prevent a connection error from occurring at the time of pipe connection work or the like, and to obtain a highly reliable refrigeration / air-conditioning apparatus.
[0246]
According to claim 36 of the present invention, a plurality of use-side heat exchangers are provided in the use-side refrigerant cycle, and all of the use-side heat exchangers are connected in parallel with each other. Thus, a general-purpose refrigeration and air-conditioning apparatus that can be controlled independently can be obtained.
[0247]
According to claim 37 of the present invention, a plurality of use-side heat exchangers are provided in the use-side refrigerant cycle, and at least some of the use-side heat exchangers are connected in series with each other. A refrigeration / air-conditioning apparatus that can use energy without waste is obtained.
[0248]
According to claim 38 of the present invention, the refrigerant circulating in the use-side refrigerant cycle is water, or one or more of ethylene glycol, propylene glycol, and D-sorbitol in a weight ratio of several tens. %, The use of an inexpensive refrigerant that is easy and easy to handle in terms of global environmental protection and minimizes the amount of refrigerant that is problematic in terms of global environmental protection and handling. And an inexpensive refrigeration air conditioner can be obtained.
[0249]
According to claim 39 of the present invention, the heat-source-side refrigerant cycle is constituted by a vapor compression refrigeration cycle, and the refrigerant circulating in the heat-source-side refrigerant cycle uses latent heat. By using any one of CFC-based azeotropic mixed refrigerant, CFC-based non-azeotropic refrigerant, hydrocarbon-based refrigerant, and ammonia refrigerant, an energy-efficient refrigerant is used on the heat source side, and as a whole An efficient refrigeration / air-conditioning apparatus can be obtained in which the amount of refrigerant having a problem in terms of global environmental conservation and handling can be minimized, and the efficiency is high.
[0250]
According to claim 40 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating a heat source side refrigerant and a use side refrigerant cycle for circulating a use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use side refrigerant, and the capacity of the heat source side refrigerant cycle is divided into a plurality of stages. By changing the capacitance and increasing the capacitance as the capacitance increases, it is possible to follow variations in the size of the load while suppressing hunting. A method for controlling a refrigerating air conditioner capable of improving the temperature stability of a refrigerant is obtained.
[0251]
Further, according to claim 41 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating a heat source side refrigerant and a use side refrigerant cycle for circulating a use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use side refrigerant, and the heat source side refrigerant cycle is a plurality of two or more systems. During the heating operation in the use-side refrigerant cycle, while at least one of the heat source-side refrigerant cycles is performing the defrosting operation, at least one of the heat source-side refrigerant cycles is controlled to continue the heating operation. Thereby, the control method of the refrigeration / air-conditioning apparatus can be obtained in which the temperature drop of the use-side refrigerant can be reduced during the defrosting operation, and the temperature can be maintained at a temperature suitable for using the heat.
[0252]
According to claim 42 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating a heat source side refrigerant and a use side refrigerant cycle for circulating a use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use side refrigerant, and the heat source side refrigerant cycle is a plurality of two or more systems. In the heat source side refrigerant cycle, one or more heating-dedicated refrigerant cycles and cooling / heating combined refrigerant cycles are respectively provided in one or more systems, and a vapor compression refrigeration cycle is used as the cooling / heating combined refrigerant cycle. While one or more of the cooling / heating combined refrigerant cycles are in the defrosting operation, the heating-dedicated cooling cycle and the cooling / heating combined refrigerant cycle are performed. By controlling the refrigerant cycle of at least one system of the refrigerant to continue the heating operation, the temperature of the use-side refrigerant at the time of the defrosting operation is stabilized, and the refrigeration air-conditioning apparatus that can maintain the temperature suitable for the utilization of the heat. A control method is obtained.
[0253]
According to claim 43 of the present invention, the heat-source-side refrigerant cycle that continues the heating operation while one or more of the heat-source-side refrigerant cycles is performing the defrosting operation has an increased heating capacity to increase the heating capacity. A control method for a refrigeration / air-conditioning apparatus that controls the continuation of the operation to further reduce the temperature drop of the usage-side refrigerant during the defrosting operation, stabilizes the temperature of the usage-side refrigerant, and maintains the temperature suitable for using the heat. Is obtained.
[0254]
According to claim 44 of the present invention, the heat source-side refrigerant cycle that continues the heating operation while at least one of the heat source-side refrigerant cycles is performing the defrosting operation is a refrigerant cycle dedicated to heating. Thereby, the control method of the refrigeration / air-conditioning apparatus that can stabilize the temperature of the use-side refrigerant during the defrosting operation and maintain the temperature at a temperature suitable for using the heat can be obtained.
[0255]
Further, according to claim 45 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating a heat source side refrigerant and a use side refrigerant cycle for circulating a use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, a refrigerant using sensible heat is used as the use side refrigerant, and a vapor compression refrigeration cycle is used as the heat source side refrigerant cycle. If two or more systems are used and one or more of the heat source side refrigerant cycles satisfy the defrosting operation start condition during the heating operation in the use side refrigerant cycle, the capacity of the heat source side refrigerant cycle before starting the defrosting operation By increasing the temperature and controlling the heating operation to be continued and then performing the defrosting operation, it stabilizes the temperature of the use-side refrigerant during the defrosting operation and is suitable for heating. The method of the refrigerating and air-conditioning apparatus capable of maintaining the temperature.
[0256]
According to claim 46 of the present invention, the heat source is exchanged by an auxiliary heat exchanger provided between a heat source side refrigerant cycle for circulating a heat source side refrigerant and a use side refrigerant cycle for circulating a use side refrigerant. In a refrigeration air conditioner that uses the heat obtained in the side refrigerant cycle for heating in the use side refrigerant cycle, a refrigerant that utilizes sensible heat is used as the use side refrigerant, and the heat source side refrigerant cycle is a plurality of two or more systems. , The capacity of each of the plurality of heat source side refrigerant cycles is changed to one or more stages, and the total capacity of the plurality of heat source side refrigerant cycles as a whole is changed to a plurality of stages. And the change width of the total capacity is increased as the total capacity increases. You can follow while suppressing grayed, control method of the refrigerating and air-conditioning apparatus capable of improving the temperature stability of the use-side refrigerant can be obtained.
[0257]
According to claim 47 of the present invention, when increasing the stage of the total capacity, the currently operating heat source-side refrigerant cycle of the plurality of heat source-side refrigerant cycles remains in the operating state. The capacity is increased, and when the stage of the total capacity is decreased, the currently stopped heat source-side refrigerant cycle of the plurality of heat source-side refrigerant cycles is stopped and the total capacity is decreased while being stopped. By performing such control, it is possible to obtain a method of controlling a refrigeration and air-conditioning apparatus that can improve the stability of the entire system.
[0258]
According to claim 48 of the present invention, a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a refrigerant storage tank for storing a heat source side refrigerant are connected to each other to form the heat source side refrigerant. A heat-source-side refrigerant cycle that circulates through the auxiliary heat exchanger, and a use-side refrigerant cycle that connects the refrigerant transfer device and circulates the use-side refrigerant. By immersing in the heat source side refrigerant and exchanging heat between the heat source side refrigerant and the use side refrigerant in the auxiliary heat exchanger, the heat stored in the refrigerant storage tank is used for heating in the use side refrigerant cycle. , The heat source-side refrigerant cycle equipment can be reduced in size by efficiently storing heat in the refrigerant storage tank, the reliability of the entire system can be improved with a relatively simple device configuration, and the temperature of the use-side refrigerant during defrosting operation can be stabilized. Let's use heat Refrigeration air conditioning system is obtained which can be maintained in a suitable temperature.
[Brief description of the drawings]
FIG. 1 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 1 of the present invention.
2A and 2B are graphs showing characteristics with respect to the concentration of a use-side refrigerant according to the first embodiment, where FIG. 2A is a freezing temperature, FIG. 2B is a kinematic viscosity, and FIG. Is shown.
FIG. 3 is a configuration diagram illustrating a refrigeration / air-conditioning apparatus according to Embodiment 1.
FIG. 4 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 1.
FIG. 5 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 1.
FIG. 6 is a configuration diagram illustrating a refrigeration / air-conditioning apparatus according to Embodiment 1.
FIG. 7 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 2 of the present invention.
FIG. 8 is a graph showing a COP with respect to a total compressor capacity and a total compressor temporary frequency, according to the control method of the refrigeration / air-conditioning apparatus according to the second embodiment.
FIG. 9 is a graph showing an increase / decrease value of the number of operating compressors with respect to a detected temperature TH1 of a temperature sensor 31, according to a control method of a refrigeration / air-conditioning apparatus according to Embodiment 2.
FIG. 10 is a flowchart showing a processing procedure according to a method for controlling a refrigeration / air-conditioning apparatus according to the second embodiment.
FIG. 11 is a block diagram showing processing related to a control method of a refrigeration / air-conditioning apparatus according to Embodiment 2.
FIG. 12 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 3 of the present invention.
FIG. 13 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 4 of the present invention.
FIG. 14 is a configuration diagram illustrating a refrigeration / air-conditioning apparatus according to Embodiment 4.
FIG. 15 is a configuration diagram illustrating a refrigeration / air-conditioning apparatus according to Embodiment 5 of the present invention.
FIG. 16 is a graph showing the operation / stop of the heat source side refrigerant cycle with respect to the detected temperature TH1 of the temperature sensor 31 according to the control method of the refrigerating air conditioner according to the fifth embodiment.
FIG. 17 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 6 of the present invention.
FIG. 18 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 7 of the present invention.
FIG. 19 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 8 of the present invention.
FIG. 20 is an explanatory diagram showing a configuration of a refrigerant storage tank according to an eighth embodiment.
FIG. 21 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to an eighth embodiment.
FIG. 22 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 9 of the present invention.
FIG. 23 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to a ninth embodiment.
FIG. 24 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 10 of the present invention.
FIG. 25 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 11 of the present invention.
FIG. 26 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 12 of the present invention.
FIG. 27 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 13 of the present invention.
FIG. 28 is a configuration diagram showing a refrigeration / air-conditioning apparatus according to Embodiment 14 of the present invention.
FIG. 29 is a perspective view showing a configuration of a bubble blowing unit according to Embodiment 14.
FIG. 30 is a configuration diagram showing another configuration of the refrigeration / air-conditioning apparatus according to Embodiment 14.
FIG. 31 is a configuration diagram showing a conventional refrigeration / air-conditioning apparatus.
[Explanation of symbols]
REFERENCE SIGNS LIST 11 compressor, 12 flow path switching valve, 13 heat source side heat exchanger, 14 heat source side refrigerant flow control valve, 15 receiver, 16 first auxiliary heat exchanger, 17 outdoor blower, 18 second refrigerant storage tank, 19 second Auxiliary heat exchanger, 20 refrigerant storage tank, 21 refrigerant transfer device, 22a, 22b, 22c, 22d use side heat exchanger, 23a, 23b use side refrigerant flow control valve, 24a, 24b indoor blower, 25 refrigerant transfer device, 26 Filter, 27, 27a, 27b partition, 29 heating device, 31 temperature detecting means, 34 outside air temperature detecting means, 35 temperature detecting means, 36 temperature detecting means, 41, 42a, 42b control device, 51, 52 flow path switching means, 61 heat storage material, 62 flow path switching means, 64a, 64b stop valve, 65 connection port, 111 air transfer device, 112 air pipe, 113 partition plate, g, h Unit, e, e ', f Outdoor unit, e''heat source device, j, k, i', j ', k' connection piping.

Claims (25)

熱源側冷媒を循環させる熱源側冷媒サイクルと顕熱を利用する利用側冷媒を循環させる利用側冷媒サイクルの間に設けられ、熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する補助熱交換器と、前記補助熱交換器で加熱され冷媒搬送装置で搬送される前記利用側冷媒にて暖房または給湯または加熱乾燥を行う利用側熱交換器と、前記利用側熱交換器が暖房等の運転中に前記熱源側冷媒サイクルを除霜運転するときの前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持するように前記暖房などの運転を行う冷媒量の２倍程度以上の冷媒量を保有する利用側冷媒サイクルの内容積と、を備え、前記内容積は前記利用側冷媒サイクルに前記利用側熱交換器と直列に設けた冷媒貯留タンクの内容積または前記利用側冷媒サイクルを形成する配管の内容積であって、暖房等の運転中に前記補助熱交換器で加熱されながら冷媒を循環させる内容積であることを特徴とする冷凍空調装置。The heat source side refrigerant cycle is provided between the heat source side refrigerant cycle for circulating the heat source side refrigerant and the user side refrigerant cycle for circulating the user side refrigerant utilizing sensible heat, and the heat obtained by the heat source side refrigerant cycle by exchanging heat is used for the user side. An auxiliary heat exchanger used for heating in a refrigerant cycle, and a use-side heat exchanger that performs heating, hot water supply, or heating and drying with the use-side refrigerant that is heated by the auxiliary heat exchanger and conveyed by a refrigerant conveyance device; When the use side heat exchanger performs a defrosting operation on the heat source side refrigerant cycle during an operation such as heating, the temperature of the use side refrigerant is maintained at a temperature suitable for heating or hot water supply or heating and drying. An internal volume of a use-side refrigerant cycle having a refrigerant amount of about twice or more the amount of refrigerant to be operated, and the internal volume is provided in series with the use-side heat exchanger in the use-side refrigerant cycle. The internal volume of the medium storage tank or the internal volume of the pipe forming the utilization-side refrigerant cycle, wherein the internal volume is that the refrigerant is circulated while being heated by the auxiliary heat exchanger during an operation such as heating. Refrigeration air conditioner. 前記熱源側冷媒サイクルの除霜運転によって前記補助熱交換器で前記利用側冷媒サイクルから奪われる熱量をＱｄ、前記利用側冷媒の暖房運転等を行う量をＷ、前記利用側冷媒の比熱をＣｐとし、前記利用側冷媒サイクルの加熱運転中に前記熱源側冷媒サイクルで除霜運転されるとき、Ｑｄ/（Ｗ・Ｃｐ）で表される前記利用側温度低下が許容温度以下になるように前記利用側冷媒の量を同等以上充填して、前記利用側冷媒の温度を暖房または給湯または加熱乾燥に適した温度に維持することを特徴とする請求項１記載の冷凍空調装置。Qd is the amount of heat deprived from the use-side refrigerant cycle by the auxiliary heat exchanger by the defrosting operation of the heat-source-side refrigerant cycle, W is the amount of heating operation of the use-side refrigerant, and Cp is the specific heat of the use-side refrigerant. When the defrosting operation is performed in the heat-source-side refrigerant cycle during the heating operation of the usage-side refrigerant cycle, the use-side temperature decrease represented by Qd / (W · Cp) is equal to or lower than an allowable temperature. 2. The refrigeration / air-conditioning apparatus according to claim 1, wherein the usage-side refrigerant is charged in an amount equal to or greater than the usage-side refrigerant to maintain the temperature of the usage-side refrigerant at a temperature suitable for heating, hot water supply, or heating and drying. 前記補助熱交換器を前記冷媒貯留タンク内の利用側冷媒に浸漬することを特徴とする請求項１または２記載の冷凍空調装置。3. The refrigeration / air-conditioning apparatus according to claim 1, wherein the auxiliary heat exchanger is immersed in a use-side refrigerant in the refrigerant storage tank. 前記冷媒搬送装置を前記冷媒貯留タンクの喫水面より下方に設けたことを特徴とする請求項１ないし３のいずれか１項に記載の冷凍空調装置。The refrigeration / air-conditioning apparatus according to any one of claims 1 to 3, wherein the refrigerant transport device is provided below a draft surface of the refrigerant storage tank. 圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、及び第１補助熱交換器を連接し熱源側冷媒を循環させて成る熱源側冷媒サイクルと、前記第１補助熱交換器と熱交換する第２補助熱交換器、冷媒貯留タンク、冷媒搬送装置、及び利用側熱交換器を連接し利用側冷媒を循環させて成る利用側冷媒サイクルとを有し、前記圧縮機、前記流路切換弁、前記熱源側熱交換器、前記熱源側冷媒流量制御弁、前記第１補助熱交換器、前記第２補助熱交換器、前記冷媒貯留タンク、および前記冷媒搬送装置を一つのユニットに収納したことを特徴とする請求項１ないし４のいずれか１項に記載の冷凍空調装置。A heat source side refrigerant cycle comprising connecting a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a first auxiliary heat exchanger to circulate the heat source side refrigerant; A second auxiliary heat exchanger that exchanges heat with the exchanger, a refrigerant storage tank, a refrigerant transport device, and a utilization-side refrigerant cycle that connects the utilization-side heat exchanger and circulates the utilization-side refrigerant; The flow path switching valve, the heat source side heat exchanger, the heat source side refrigerant flow control valve, the first auxiliary heat exchanger, the second auxiliary heat exchanger, the refrigerant storage tank, and the refrigerant transfer device. The refrigeration / air-conditioning apparatus according to any one of claims 1 to 4, wherein the refrigeration and air conditioning apparatus is housed in one unit. 圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、及び第１補助熱交換器を連接し熱源側冷媒を循環させて成る熱源側冷媒サイクルと、前記第１補助熱交換器と熱交換する第２補助熱交換器、冷媒貯留タンク、冷媒搬送装置、及び利用側熱交換器を連接し利用側冷媒を循環させて成る利用側冷媒サイクルとを有し、前記圧縮機、前記流路切換弁、前記熱源側熱交換器、および前記熱源側冷媒流路制御弁を一つのユニットに収納し、前記第１補助熱交換器の一端側と前記流路切換弁との間および前記第１補助熱交換器の他端側と前記熱源側冷媒流量制御弁との間をそれぞれ接続配管で接続したことを特徴とする請求項１ないし４のいずれか１項に記載の冷凍空調装置。A heat source side refrigerant cycle comprising connecting a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a first auxiliary heat exchanger to circulate the heat source side refrigerant; A second auxiliary heat exchanger that exchanges heat with the exchanger, a refrigerant storage tank, a refrigerant transport device, and a use-side refrigerant cycle that connects the use-side heat exchanger and circulates the use-side refrigerant; , The flow path switching valve, the heat source side heat exchanger, and the heat source side refrigerant flow path control valve are housed in one unit, and between one end of the first auxiliary heat exchanger and the flow path switching valve. The refrigeration and air conditioning system according to any one of claims 1 to 4, wherein the other end of the first auxiliary heat exchanger and the heat source-side refrigerant flow control valve are connected by connection pipes, respectively. apparatus. 圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、および第１補助熱交換器を連接し熱源側冷媒を循環して成る熱源側冷媒サイクルと、第１の冷媒搬送装置、前記第１補助熱交換器と熱交換する第２補助熱交換器、および前記熱源側冷媒サイクルからの温冷熱を蓄える冷媒貯留タンクの温冷熱槽とを利用側冷媒を循環して成る熱輸送サイクルと、第２の冷媒搬送装置、利用側熱交換器、および前記冷媒貯留タンクの温冷熱槽と連通するとともに前記利用側熱交換器から戻る前記利用側冷媒を循環させる冷媒貯留タンクの利用側槽とを連接する利用側冷媒サイクルと、前記冷媒貯留タンクの温冷熱槽上部と下部に設けられ前記熱源側冷媒サイクルからの温熱を上から下に蓄熱するように、もしくは前記熱源側冷媒サイクルからの冷熱を下から上に蓄熱するように設けられた前記利用側冷媒を循環させる開口と、前記冷媒貯留タンクの利用側槽上部と下部に設けられ前記利用側熱交換器から戻る前記利用側冷媒の温熱を上から下に戻すように、もしくは前記利用側冷媒の冷熱を下から上に戻すように設けられた前記利用側冷媒を循環させる開口と、を備え、前記利用側冷媒は前記第２補助熱交換器、前記冷媒貯留タンクの温冷熱槽、前記第２の冷媒搬送装置、前記利用側熱交換器、前記冷媒貯留タンクの利用側槽、および第１の冷媒搬送装置の順に循環することを特徴とする冷凍空調装置。A heat source side refrigerant cycle including a compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, and a heat source side refrigerant circulating by connecting a first auxiliary heat exchanger and a first refrigerant conveyance; Heat generated by circulating a use-side refrigerant through an apparatus, a second auxiliary heat exchanger that exchanges heat with the first auxiliary heat exchanger, and a hot / cold heat tank of a refrigerant storage tank that stores hot / cold heat from the heat source-side refrigerant cycle. Use of a transport cycle and a second refrigerant transport device, a use-side heat exchanger, and a refrigerant storage tank that circulates the use-side refrigerant returning from the use-side heat exchanger while communicating with the hot / cold heat tank of the refrigerant storage tank. A use-side refrigerant cycle connecting the side tanks, and a heat-source-side refrigerant cycle provided so as to store heat from the heat-source-side refrigerant cycle provided at the upper and lower portions of the hot-cooled heat tank of the refrigerant storage tank, or from the heat-source-side refrigerant cycle. Cold from An opening for circulating the use-side refrigerant provided so as to store heat from bottom to top, and the heat of the use-side refrigerant returned from the use-side heat exchanger provided at the upper and lower use-side tanks of the refrigerant storage tank. And an opening for circulating the use-side refrigerant provided so as to return the cooling heat of the use-side refrigerant from the bottom to the top or from the bottom to the top. It circulates in the order of an exchanger, a hot / cold heat tank of the refrigerant storage tank, the second refrigerant transfer device, the use side heat exchanger, a use side tank of the refrigerant storage tank, and a first refrigerant transfer device. Refrigeration and air conditioning equipment. 前記冷媒貯留タンクの温冷熱槽と前記利用側槽を連通する連通部は喫水面よりも下方に設けられ、前記熱源側冷媒サイクルから蓄熱された前記利用側冷媒と前記利用側熱交換器から戻る前記利用側冷媒を混合可能であることを特徴とする請求項７記載の冷凍空調装置。A communication part that connects the hot / cold heat tank of the refrigerant storage tank and the use side tank is provided below a draft surface, and returns from the use side refrigerant and the use side heat exchanger stored in heat from the heat source side refrigerant cycle. The refrigeration / air-conditioning apparatus according to claim 7, wherein the use-side refrigerant can be mixed. 前記冷媒貯留タンクの温冷熱槽の容積を前記利用側槽の容積より大きくしたことを特徴とする請求項７または８記載の冷凍空調装置。9. The refrigeration / air-conditioning apparatus according to claim 7, wherein the capacity of the hot / cold heat tank of the refrigerant storage tank is larger than the capacity of the use side tank. 前記利用側熱交換器が暖房等の運転中に前記熱源側冷媒サイクルを除霜運転するとき、前記第１の冷媒搬送装置を停止させることを特徴とする請求項７または８または９記載の冷凍空調装置。The refrigeration system according to claim 7, wherein the first refrigerant transport device is stopped when the heat-source-side refrigerant cycle performs a defrosting operation during the operation of the use-side heat exchanger such as heating. Air conditioner. 熱源側冷媒と利用側冷媒を熱交換する前記補助熱交換器をプレート式熱交換器とするとともに、前記熱源側冷媒と利用側冷媒を対向流とするように前記利用側冷媒の流れ方向を切換える切換手段を設けたことを特徴とする請求項１ないし９のいずれか１項に記載の冷凍空調装置。The auxiliary heat exchanger that exchanges heat between the heat-source-side refrigerant and the use-side refrigerant is a plate-type heat exchanger, and the flow direction of the use-side refrigerant is switched so that the heat-source-side refrigerant and the use-side refrigerant have a counterflow. The refrigeration / air-conditioning apparatus according to any one of claims 1 to 9, further comprising switching means. 前記冷媒貯留タンク内に蓄熱手段を設けることを特徴とする請求項１ないし１１のいずれか１項に記載の冷凍空調装置。The refrigeration / air-conditioning apparatus according to any one of claims 1 to 11, wherein heat storage means is provided in the refrigerant storage tank. 前記冷媒貯留タンクの外部に設けられ前記冷媒貯留タンクの高さが異なる位置を接続する利用側冷媒配管と、この利用側冷媒配管を流通する利用側冷媒を加熱する熱源装置と、を備えたことを特徴とする請求項１ないし１２のいずれか１項に記載の冷凍空調装置。A heat-source device that heats the use-side refrigerant that is provided outside the refrigerant storage tank and that connects the positions of the refrigerant storage tanks at different heights, and that heats the use-side refrigerant flowing through the use-side refrigerant pipe. The refrigeration / air-conditioning apparatus according to any one of claims 1 to 12, wherein: 圧縮機、流路切換弁、熱源側熱交換器、熱源側冷媒流量制御弁、補助熱交換器、冷媒貯留タンク及び冷媒搬送装置を一つのユニット内に収納したことを特徴とする請求項７ないし１３のいずれか１項に記載の冷凍空調装置。The compressor, a flow path switching valve, a heat source side heat exchanger, a heat source side refrigerant flow control valve, an auxiliary heat exchanger, a refrigerant storage tank, and a refrigerant conveying device are housed in one unit. A refrigeration / air-conditioning apparatus according to any one of claims 13 to 13. 圧縮機、流路切換弁、熱源側熱交換器、及び熱源側冷媒流量制御弁を一つのユニット内に収納するとともに、補助熱交換器、冷媒貯留タンク、および冷媒搬送装置を前記ユニットとは別の一つのユニット内に収納し、前記補助熱交換器の一端側と前記流路切換弁との間および、前記補助熱交換器の他端側と前記熱源側冷媒流量制御弁との間をそれぞれ接続配管で接続したことを特徴とする請求項７ないし１３のいずれか１項に記載の冷凍空調装置。The compressor, the flow path switching valve, the heat source side heat exchanger, and the heat source side refrigerant flow control valve are housed in one unit, and the auxiliary heat exchanger, the refrigerant storage tank, and the refrigerant transfer device are separated from the unit. Housed in one unit, between the one end of the auxiliary heat exchanger and the flow path switching valve, and between the other end of the auxiliary heat exchanger and the heat source side refrigerant flow control valve, respectively. The refrigeration / air-conditioning apparatus according to any one of claims 7 to 13, wherein the refrigeration and air conditioning apparatus is connected by a connection pipe. 利用側冷媒が循環する部分に、前記利用側冷媒に混入した混入物を集めるフィルタを設けたことを特徴とする請求項１ないし１５のいずれか１項に記載の冷凍空調装置。The refrigeration / air-conditioning apparatus according to any one of claims 1 to 15, wherein a filter for collecting contaminants mixed in the use-side refrigerant is provided in a portion where the use-side refrigerant circulates. 前記フィルタを前記利用側冷媒を貯留する前記冷媒貯留タンク内に設けたことを特徴とする請求項１６に記載の冷凍空調装置。17. The refrigeration / air-conditioning apparatus according to claim 16, wherein the filter is provided in the refrigerant storage tank that stores the use-side refrigerant. 前記熱源側冷媒サイクルを２系統以上の複数とし、加熱専用の熱源側冷媒サイクルは冷却／加熱併用の熱源側冷媒サイクルとは直列に接続し、前記加熱専用の熱源側冷媒サイクルを前記冷却／加熱併用の熱源側冷媒サイクルより利用側冷媒の流れの向に対して下流側もしくは上流側に接続したことを特徴とする請求項１ないし１７のいずれか１項に記載の冷凍空調装置。The heat source-side refrigerant cycle is a plurality of two or more systems, and the heat source-side refrigerant cycle dedicated to heating is connected in series with the heat source-side refrigerant cycle combined with cooling / heating, and the heat source-side refrigerant cycle dedicated to heating is cooled / heated. The refrigeration / air-conditioning apparatus according to any one of claims 1 to 17, wherein the refrigeration / air-conditioning apparatus according to any one of claims 1 to 17, wherein the refrigeration / air-conditioning apparatus is connected to a downstream side or an upstream side with respect to a flow direction of the use side refrigerant from the combined heat source side refrigerant cycle. 前記熱源側冷媒サイクルを２系統以上の複数とし、前記加熱専用の熱源側冷媒サイクルは冷却／加熱併用の熱源側冷媒サイクルとは並列に接続するとともに、冷却運転持には前記加熱専用の熱源側冷媒サイクルと熱交換する前記利用側補助熱交換器には利用側冷媒が流れない様に、前記利用側冷媒サイクルの冷媒流路を切換える切換手段を備えたことを特徴とする請求項１ないし１８のいずれか１項に記載の冷凍空調装置。The heat source-side refrigerant cycle is a plurality of two or more systems, and the heat source-side refrigerant cycle dedicated to heating is connected in parallel with the heat source-side refrigerant cycle combined with cooling / heating. 19. A switching device for switching a refrigerant flow path of the use-side refrigerant cycle so that the use-side refrigerant does not flow through the use-side auxiliary heat exchanger that exchanges heat with the refrigerant cycle. The refrigeration air conditioner according to any one of the above. 前記熱源側冷媒サイクルを２系統以上の複数とし、前記利用側冷媒サイクルに前記熱源側冷媒サイクルから熱を供給される冷却用の利用側熱交換器と、加熱専用の熱源側冷媒サイクル熱を供給される加熱用の利用側熱交換器と、を設け、冷却用のThe heat source side refrigerant cycle is a plurality of two or more systems, and a heat use side heat exchanger for cooling, to which heat is supplied from the heat source side refrigerant cycle to the use side refrigerant cycle, and a heat source side refrigerant cycle heat exclusively for heating are supplied. And a use-side heat exchanger for heating, 熱交換器は、空気の流れに対し、加熱用の利用側熱交換器の上流側に配置し、除湿運転時に冷却用および加熱用の利用側熱交換器を動作させる様に構成したことを特徴とする請求項１ないし１９のいずれか１項に記載の冷凍空調装置。The heat exchanger is arranged upstream of the use side heat exchanger for heating with respect to the flow of air, and is configured to operate the use side heat exchanger for cooling and heating during the dehumidifying operation. The refrigeration / air-conditioning apparatus according to any one of claims 1 to 19, wherein 利用側冷媒サイクルの前記利用側熱交換器へ前記利用側冷媒を送る側の配管および前記利用側熱交換器から前記利用側冷媒を戻す側の配管では、前記配管の径を異なる様に、または、前記配管の継ぎ手の径もしくは形状を異なる様にしたことを特徴とする請求項１ないし２０のいずれか１項に記載の冷凍空調装置。In the pipe on the side that sends the use-side refrigerant to the use-side heat exchanger of the use-side refrigerant cycle and the pipe that returns the use-side refrigerant from the use-side heat exchanger, the diameter of the pipe is different, or The refrigeration / air-conditioning apparatus according to any one of claims 1 to 20, wherein a diameter or a shape of a joint of the pipe is different. 熱源側冷媒は潜熱を利用する冷媒であるとともに、顕熱を利用する利用側冷媒は、水、もしくは、エチレングリコール、プロピレングリコール、Ｄ−ソルビトールなどの溶媒の内の少なくともいずれか一つを含む水溶液であることを特徴とする請求項１ないし２１のいずれか１項に記載の冷凍空調装置。The heat-source-side refrigerant is a refrigerant that utilizes latent heat, and the utilization-side refrigerant that utilizes sensible heat is water or an aqueous solution containing at least one of solvents such as ethylene glycol, propylene glycol, and D-sorbitol. The refrigeration / air-conditioning apparatus according to any one of claims 1 to 21, wherein 熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いるとともに、前記熱源側冷媒サイクルの容量を複数の段階に変化するように構成し、その容量の変化幅を変化する隣り合う段階毎の容量が増加するにつれて大きくなるようにしたことを特徴とする冷凍空調装置の制御方法。The heat generated in the heat-source-side refrigerant cycle by exchanging heat with an auxiliary heat exchanger provided between the heat-source-side refrigerant cycle for circulating the heat-source-side refrigerant and the use-side refrigerant cycle for circulating the use-side refrigerant is used as the use-side refrigerant. In a refrigeration air conditioner used for heating in a cycle, a refrigerant using sensible heat is used as the use-side refrigerant, and the capacity of the heat source-side refrigerant cycle is changed in a plurality of stages, and the change width of the capacity is changed. The method for controlling a refrigeration and air-conditioning system, characterized in that it increases as the capacity of each adjacent step in which the temperature changes varies. 熱源側冷媒を循環させる熱源側冷媒サイクルと利用側冷媒を循環させる利用側冷媒サイクルの間に設けた補助熱交換器で熱交換することによって前記熱源側冷媒サイクルで得た温熱を前記利用側冷媒サイクルで加熱に利用する冷凍空調装置において、前記利用側冷媒として顕熱を利用する冷媒を用いるとともに、前記熱源側冷媒サイクルを２系統以上の複数とし、前記複数系統の熱源側冷媒サイクルのそれぞれの容量を一つまたは複数の段階に変化するように構成し、且つ全体としての前記複数系統の熱源側冷媒サイクルの合計容量を複数の段階に変化するように構成し、その合計容量の変化幅を変化する隣り合う段階毎の合計容量が増加するにつれて大きくなるようにしたことを特徴とする冷凍空調装置の制御方法。The heat generated in the heat-source-side refrigerant cycle by exchanging heat with an auxiliary heat exchanger provided between the heat-source-side refrigerant cycle for circulating the heat-source-side refrigerant and the use-side refrigerant cycle for circulating the use-side refrigerant is used as the use-side refrigerant. In the refrigeration air conditioner used for heating in the cycle, while using a refrigerant utilizing sensible heat as the use side refrigerant, the heat source side refrigerant cycle is a plurality of two or more systems, each of the heat source side refrigerant cycle of the plurality of systems The capacity is configured to be changed to one or more stages, and the total capacity of the heat source side refrigerant cycle of the plurality of systems as a whole is configured to be changed to a plurality of stages, and the variation width of the total capacity is A method for controlling a refrigerating and air-conditioning apparatus, wherein the total capacity is changed as the total capacity of adjacent changing stages increases. 前記熱源側冷媒サイクルを２系統以上の複数とし、前記複数系統の熱源側冷媒サイクルのそれぞれの容量を一つまたは複数の段階に変化するように構成し、且つ全体としての前記複数系統の熱源側冷媒サイクルの合計容量を複数の段階に変化するように構成し、その合計容量を増加させる際は運転中の熱源側冷媒サイクルは運転状態のままとして前記合計容量を増加させ、前記合計容量を減少させる際は停止中の熱源側冷媒サイクルは停止状態のままとして前記合計容量を減少させて、前記複数系統の熱源側冷媒サイクルの運転停止状態を継続させる制御を行うことを特徴とする請求項２４項に記載の冷凍空調装置の制御方法。The heat source side refrigerant cycle is a plurality of two or more systems, and the capacity of each of the heat source side refrigerant cycles of the plurality of systems is configured to change to one or more stages, and the heat source side of the plurality of systems as a whole The total capacity of the refrigerant cycle is configured to be changed in a plurality of stages, and when increasing the total capacity, the heat source side refrigerant cycle during operation is kept in the operating state, the total capacity is increased, and the total capacity is reduced. 25. The system according to claim 24, wherein when performing the control, the total capacity is reduced while the stopped heat source-side refrigerant cycle remains stopped, and control is performed to continue the operation stop state of the plurality of heat source-side refrigerant cycles. The method for controlling a refrigeration / air-conditioning apparatus according to the above section.
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