JP3563094B2 - Vehicle air conditioner - Google Patents

Vehicle air conditioner Download PDF

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Publication number
JP3563094B2
JP3563094B2 JP25722693A JP25722693A JP3563094B2 JP 3563094 B2 JP3563094 B2 JP 3563094B2 JP 25722693 A JP25722693 A JP 25722693A JP 25722693 A JP25722693 A JP 25722693A JP 3563094 B2 JP3563094 B2 JP 3563094B2
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Prior art keywords
heat exchanger
valve
refrigerant
compressor
air conditioner
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JP25722693A
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JPH07108824A (en
Inventor
進 池田
敏美 礒部
敦雄 井上
満 石川
昭弘 田尻
長治 佐久間
信行 由利
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Honda Motor Co Ltd
Sanden Holdings Corp
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Honda Motor Co Ltd
Sanden Corp
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  • Air-Conditioning For Vehicles (AREA)

Description

【０００１】
【産業上の利用分野】
本発明は、車室内の冷・暖房を行う車両用空気調和装置、特に電気自動車等に有用な空気調和装置に関するものである。
【０００２】
【従来の技術】
内燃機関等の熱源を有しない電気自動車等の車両には一般にヒートポンプ式の空気調和装置が用いられている。この空気調和装置は主に圧縮機，四方弁，室外熱交換器，２つの膨張手段及び室内熱交換器とから構成されており、四方弁による冷媒サイクルの切り換えで室内熱交換器を吸熱器または放熱器として使用し車室内の冷房と暖房を行っている。
【０００３】
【発明が解決しようとする課題】
上記従来の空気調和装置では基本的に冷房モードと暖房モードでの運転しか行えないため、降雨，降雪時等の多湿下で暖房を行うと車室内の窓ガラスに曇りを生じ易く、また冷房から暖房に切り換えた際に室内熱交換器に付着していた結露水が蒸発して上記同様の曇りを生じる難点がある。また、除湿のみを行おうとしても吹出温度の低下が避けられず快適性を大きく損なう難点がある。
【０００４】
本発明は上記事情に鑑みてなされたもので、暖房時に車室内の窓ガラスに曇りを生じることがなく、しかも吹出温度を低下させることなく除湿運転が行える車両用空気調和装置を提供することにある。
【０００５】
【課題を解決するための手段】
上記目的を達成するため、本発明では、圧縮機，室外熱交換器，第１の室内熱交換器，第１の膨張手段及び第２の膨張手段を備え、四方弁等による冷媒サイクルの切り換えで車室内の冷房と暖房を行うヒートポンプ式の車両用空気調和装置に、少なくとも暖房時に放熱器として使用される第２の室内熱交換器を設けると共に、第２の室内熱交換器を通過した冷媒を第２の膨張手段を通じて室外熱交換器に導く管路と、第２の室内熱交換器を通過した冷媒を第１の膨張手段を通じて第１の室内熱交換器に導く管路とを設けている。
【０００６】
【作用】
本発明に係る車両用空気調和装置では、暖房時に第２の室内熱交換器を放熱器として使用する一方、該第２の室内熱交換器を通過した冷媒の全部または一部を第１の膨張手段を通じて第１の室内熱交換器に導くことができる。つまり、第２の室内熱交換器で放熱作用を、且つ第１の室内熱交換器で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。
【０００７】
【実施例】
図１及び図２には本発明の第１実施例を示してある。同図において、１は能力可変型の電動圧縮機、２は電磁式の四方弁、３は室外熱交換器、４は第１の室内熱交換器、５は第２の室内熱交換器、６は感熱式の第１の膨張弁、７は感熱式の第２の膨張弁、８は受液器、９はアキュムレータ、１０〜１３は逆止弁、１４〜１７は電磁式の開閉弁、Ａは車室内空調用のダクト、Ｆは電動ファン、Ｄ１〜Ｄ４は電動ダンパであり、第１，第２の室内熱交換器４，５はダクトＡ内に配置されている。ここで、逆止弁１０は特許請求の範囲の請求項３に記載された第１の制御弁に相当し、逆止弁１１は特許請求の範囲の請求項３に記載された第３の制御弁に相当し、逆止弁１２は特許請求の範囲の請求項３に記載された第２の制御弁に相当する。また、開閉弁１４は特許請求の範囲の請求項７に記載された第２室内熱交換器用制御弁に相当し、開閉弁１５は特許請求の範囲の請求項６に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項５に記載された第１膨張弁用制御弁に相当し、開閉弁１７は特許請求の範囲の請求項８に記載された室外熱交換器用制御弁に相当する。
【０００８】
圧縮機１の吐出口は管路１８を介して四方弁２の第１ポート２ａに接続され、該四方弁２の第２ポート２ｂは開閉弁１７を介装した管路１９を介して室外熱交換器３の一端に接続されている。また、室外熱交換器３の他端は第２の膨張弁７，開閉弁１５，１６及び第１の膨張弁６を介装した管路２０を介して第１の室内熱交換器４の入口に接続され、該第１の室内熱交換器４の出口は管路２１を介してアキュムレータ９の入口に接続されている。更に、管路２１の途中から分岐した管路２２は四方弁２の第３ポート２ｃに接続され、アキュムレータ９の出口は管路２３を介して圧縮機１の吸入口に接続されている。
【０００９】
管路２０の室外熱交換器３の他端と第２の膨張弁７との間には逆止弁１０，１３を対向して介装した管路２４の一端が接続され、該管路２４の他端は第２の室内熱交換器５の出口に接続されている。受液器８の入口は管路２４の逆止弁１０と１３の間に、また出口は管路２０の開閉弁１５と１６の間に夫々接続されている。また、第２の室内熱交換器５の入口には開閉弁１４を介装した管路２５の一端が接続され、該管路２５の他端は逆方向の逆止弁１１，１２を夫々介装した２つの管路２５ａ，２５ｂに分岐され、一方の管路２５ａは管路１９の途中に、他方の管路２５ｂは四方弁２の第４ポート２ｄに夫々接続されている。尚、第２の室内熱交換器５における冷媒流れ方向は管路２５ａ，２５ｂの逆止弁１１，１２によって制御できるため、管路２４側の逆止弁１３は必ずしも必要なものではない。また、開閉弁１４の介装位置は第２の室内熱交換器５の出口側であってもよい。
【００１０】
ダクトＡのダンパＤ１，Ｄ２は吹出口Ａ１，Ａ２の選択を行うためのもので、各吹出口Ａ１，Ａ２の内側に回動自在に配置されている。ダンパＤ３は第２の室内熱交換器５への通風量を調整するためのもので、該室内熱交換器５の上流側に回動自在に配置されている。ダンパＤ４は吸気口Ａ３，Ａ４（室内空気と室外空気）の選択を行うためのもので、両吸気口Ａ３，Ａ４の内側に回動自在に配置されている。
【００１１】
この空気調和装置は四方弁２及び開閉弁１４〜１７による冷媒サイクルの切り換えで、冷房・除霜モード，ドライ・除霜モード，除湿・暖房モード（パラレル），除湿・暖房モード（シングル）及び暖房モードの５つのモードでの運転が可能である。以下に各モードにおける冷媒サイクル及び機能に説明する。
【００１２】
冷房・除霜モードの運転は、四方弁２を図１の実線位置に切り換え、開閉弁１４，１５を閉じ開閉弁１６，１７を開いた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この冷房・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を発揮させて車室内の冷房を行うことができる。また、室外熱交換器３で生じる放熱作用を利用して該熱交換器３の急速除霜を行うことができる。
【００１３】
ドライ・除霜モードの運転は、四方弁２を図１の実線位置に切り換え、開閉弁１５を閉じ開閉弁１４，１６，１７を開けた状態で、圧縮機１を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒の一部分は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。冷媒の残り部分は第２の室内熱交換器５に流れ込んで凝縮され、受液器８の手前で上記の冷媒と合流する。つまり、このドライ・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を、且つ第２の室内熱交換器５で放熱作用を夫々発揮させて吹出温度を低下させることなく車室内の除湿を行うことができる。ちなみに、ドライ時における温度及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。また、室外熱交換器３で生じる放熱作用を利用して該室外熱交換器３の除霜を行うことができ、しかも該除霜時における吹出温度の低下も防止できる。
【００１４】
除湿・暖房モード（パラレル）の運転は、四方弁２を図２の破線位置に切り換え、開閉弁１４，１５，１６，１７を開けた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通過した後に分流され、冷媒の一部分は第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。冷媒の残り部分は第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９の手前で上記の冷媒と合流する。つまり、この除湿・暖房モード（パラレル）の冷媒サイクルでは、室外熱交換器３で吸熱作用を発揮させ、さらに第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００１５】
除湿・暖房モード（シングル）の運転は、四方弁２を図２の破線位置に切り換え、開閉弁１５，１７を閉じ開閉弁１４，１６を開けた状態で、圧縮機１を作動させることによって行われる。同図に一点鎖線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この除湿・暖房モード（シングル）の冷媒サイクルでは、第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００１６】
暖房モードの運転は、四方弁２を図２の破線位置に切り換え、開閉弁１６を閉じ開閉弁１４，１５，１７を開けた状態で、圧縮機１を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通じて第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、暖房モードの冷媒サイクルでは、第２の室内熱交換器５で放熱作用を発揮させて車室内の暖房を行うことができる。ちなみに、同モード運転時における暖房能力は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００１７】
このように第１実施例の空気調和装置によれば、四方弁２及び開閉弁１４〜１７による冷媒サイクルの切り換えで５つのモードでの運転が可能であり、内燃機関等の熱源を有しない電気自動車等の車両において空調を好適に行える利点がある。
【００１８】
また、ドライ・除霜モードの運転時には第２の室内熱交換器５で放熱作用を発揮させて吹出温度を調整できるので、ドライまたは除霜最中に車室内に冷風が吹き出されることがない。
【００１９】
更に、２つの除湿・暖房モードの運転時には除湿しながら車室内の暖房を行うことができるので、降雨，降雪時等の多湿下であっても窓ガラスに曇りを生じることなく、また冷房から暖房に切り換えた際における曇り発生を防止して快適な暖房を実現できる。
【００２０】
更にまた、除湿・暖房モード（パラレル）の運転時には室外熱交換器３と第１の室内熱交換器４の両方で吸熱作用を発揮させているので、寒冷地等で暖房運転を行う場合における室外熱交換器３の着霜を抑制して暖房能力の低下を防止することができる。
【００２１】
尚、第１実施例に示した空気調和装置は、全ての開閉弁１４〜１７を除外した回路構成でも、四方弁２による冷媒サイクルの切り換えで、第１実施例同様のドライ・除霜モードと除湿・暖房モード（パラレル）の２つのモードでの運転が可能である。ドライ・除霜モードでは第２の室内熱交換器５への通風量をダンパＤ３で調整することにより冷房運転とドライ運転を選択でき、除霜時における吹出温度の低下も防止できる。また、開閉弁１７をオン・オフ制御することで室外熱交換器３と第２の室内熱交換器５への冷媒流量を調整することもできる。
【００２２】
また、開閉弁１４，１５，１７を除外し開閉弁１６のみを残した回路構成とすれば、四方弁２と開閉弁１６による冷媒サイクルの切り換えで、上記の２モードに第１実施例同様の暖房モードを加えた３つのモードでの運転が可能となる。
【００２３】
更に、開閉弁１４，１６，１７を除外し開閉弁１５のみを残した回路構成とすれば、四方弁２と開閉弁１５による冷媒サイクルの切り換えで、上記の２モードに第１実施例同様の除湿・暖房モード（シングル）を加えた３つのモードでの運転が可能となる。
【００２４】
更にまた、開閉弁１５，１６，１７を除外し開閉弁１４のみを残した回路構成とすれば、四方弁２と開閉弁１４による冷媒サイクルの切り換えで、上記の２モードに第１実施例同様の冷房・除霜モードを加えた３つのモードでの運転が可能となる。
【００２５】
更にまた、開閉弁１４，１５，１６を除外し開閉弁１７のみを残した回路構成とすれば、四方弁２と開閉弁１７による冷媒サイクルの切り換えで、上記のドライ・除霜モードに第１実施例同様の除湿・暖房モード（シングル）を加えた２つのモードでの運転が可能となる。
【００２６】
この他にも、開閉弁１４〜１７のうち２つまたは３つを適宜組み合わせることにより、第１実施例の空気調和装置で得られる５つの運転モードから必要モードのみを選択し設定することができる。
【００２７】
図３及び図４には本発明の第２実施例を示してある。本第２実施例は第１実施例の空気調和装置を簡略化したもので、第１実施例とは、管路２０から開閉弁１５，１６を除外した点と、第１，第２の膨張弁として開度及び閉動作を遠隔操作可能な電子式のもの（６′，７′）を用いた点で異なる。両膨張弁６′，７′における開度は感熱式のものと同様に熱交換器からの冷媒吐出温度等に基づいてコントロールされる。また、図３及び図４で示されている、逆止弁１０は特許請求の範囲の請求項３に記載された第１の制御弁に相当し、逆止弁１１は特許請求の範囲の請求項３に記載された第３の制御弁に相当し、逆止弁１２は特許請求の範囲の請求項３に記載された第２の制御弁に相当する。また、開閉弁１４は特許請求の範囲の請求項７に記載された第２室内熱交換器用制御弁に相当し、開閉弁１７は特許請求の範囲の請求項８に記載された室外熱交換器用制御弁に相当する。尚、第１実施例と同様、管路２４側の逆止弁１３は必ずしも必要なものではなく、また開閉弁１４の介装位置は第２の室内熱交換器５の出口側であってもよい。他の構成は第１実施例と同じであるため同一符号を用いその説明を省略する。
【００２８】
この空気調和装置は四方弁２と第１，第２の膨張弁６′，７′と開閉弁１４，１７による冷媒サイクルの切り換えで、冷房・除霜モード，ドライ・除霜モード，除湿・暖房モード（パラレル），除湿・暖房モード（シングル）及び暖房モードの５つのモードでの運転が可能である。以下に各モードにおける冷媒サイクル及び機能を説明する。
【００２９】
冷房・除霜モードの運転は、四方弁２を図３の実線位置に切り換え、第２の膨張弁７′及び開閉弁１４を閉じ開閉弁１７を開いた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６′及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この冷房・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を発揮させて車室内の冷房を行うことができる。また、室外熱交換器３で生じる放熱作用を利用して該熱交換器３の急速除霜を行うことができる。
【００３０】
ドライ・除霜モードの運転は、四方弁２を図３の実線位置に切り換え、第２の膨張弁７′を閉じ開閉弁１４，１７を開いた状態で、圧縮機１を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒の一部分は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６′及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。冷媒の残り部分は第２の室内熱交換器５に流れ込んで凝縮され、受液器８の手前で上記の冷媒と合流する。つまり、このドライ・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を、且つ第２の室内熱交換器５で放熱作用を夫々発揮させて吹出温度を低下させることなく車室内の除湿を行うことができる。ちなみに、ドライ時における温度及び除湿量は圧縮機の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。また、室外熱交換器３で生じる放熱作用を利用して該室外熱交換器３の除霜を行うことができ、しかも該除霜時における吹出温度の低下も防止できる。
【００３１】
除湿・暖房モード（パラレル）の運転は、四方弁２を図４の破線位置に切り換え、開閉弁１４，１７を開いた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通過した後に分流され、冷媒の一部分は第２の膨張弁７′及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。冷媒の残り部分は第１の膨張弁６′及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９の手前で上記の冷媒と合流する。つまり、この除湿・暖房モード（パラレル）の冷媒サイクルでは、室外熱交換器３で吸熱作用を発揮させ、さらに第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００３２】
除湿・暖房モード（シングル）の運転は、四方弁２を図４の破線位置に切り換え、第２の膨張弁７′及び開閉弁１７を閉じ開閉弁１４を開いた状態で、圧縮機１を作動させることによって行われる。同図に一点鎖線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６′及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この除湿・暖房モード（シングル）の冷媒サイクルでは、第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００３３】
暖房モードの運転は、四方弁２を図４の破線位置に切り換え、第１の膨張弁６′を閉じ開閉弁１４，１７を開いた状態で、圧縮機１を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通じて第２の膨張弁７′及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この暖房モードの冷媒サイクルでは、第２の室内熱交換器５で放熱作用を発揮させて車室内の暖房を行うことができる。ちなみに、同モード運転時における暖房能力は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００３４】
このように第２実施例の空気調和装置によれば、四方弁２と第１，第２の膨張弁６′，７′と開閉弁１４，１７による冷媒サイクルの切り換えで５つのモードでの運転が可能であり、内燃機関等の熱源を有しない電気自動車等の車両において空調を好適に行える利点がある。また、第１実施例の空気調和装置における開閉弁１５，１６の役割を両膨張弁６′，７′で代用して回路構成を簡略化することができる。他の効果は第１実施例と同様である。
【００３５】
尚、第２実施例に示した空気調和装置は、全ての開閉弁１４，１７を除外した回路構成でも、四方弁２及び第１，第２の膨張弁６′，７′による冷媒サイクルの切り換えで、第２実施例同様のドライ・除霜モードと除湿・暖房モード（パラレル）と除湿・暖房モード（シングル）と暖房モードの４つのモードでの運転が可能である。ドライ・除霜モードでは第２の室内熱交換器５への通風量をダンパＤ３で調整することにより冷房運転とドライ運転を選択でき、除霜時における吹出温度の低下も防止できる。また、開閉弁１７をオン・オフ制御することで室外熱交換器３と第２の室内熱交換器５への冷媒流量を調整することもできる。
【００３６】
また、開閉弁１７を除外し開閉弁１４のみを残した回路構成とすれば、四方弁２と第１，第２の膨張弁６′，７′と開閉弁１４による冷媒サイクルの切り換えで、第２実施例同様の５つのモードでの運転が可能となる。
【００３７】
更に、開閉弁１４を除外し開閉弁１７のみを残した回路構成とすれば、四方弁２と第１，第２の膨張弁６′，７′と開閉弁１７による冷媒サイクルの切り換えで、第２実施例同様のドライ・除霜モードと除湿・暖房モード（パラレル）と除湿・暖房モード（シングル）と暖房モードの４つのモードでの運転が可能である。
【００３８】
図５及び図６には本発明の第３実施例を示してある。本第３実施例は第１実施例の空気調和装置を簡略化したもので、第１実施例とは、管路１９から開閉弁１７を除外した点と、逆止弁１１，１２及び管路２５ａ，２５ｂを除外した点と、管路２５から開閉弁１４を除外し該管路２５を四方弁２の第４ポート２ｄに接続した点で異なる。また、図５及び図６で示されている、逆止弁１０は特許請求の範囲の請求項９に記載された第１の制御弁に相当し、逆止弁１３は特許請求の範囲の請求項９に記載された第２の制御弁に相当する。また、開閉弁１５は特許請求の範囲の請求項９に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項１１に記載された第１膨張弁用制御弁に相当する。尚、第２の室内熱交換器５における冷媒流れ方向を制御する逆止弁１３は管路２５側に介装されていてもよい。他の構成は第１実施例と同じであるため同一符号を用いその説明を省略する。
【００３９】
この空気調和装置は四方弁２及び開閉弁１５，１６による冷媒サイクルの切り換えで、冷房・除霜モード，除湿・暖房モード（パラレル），除湿・暖房モード（シングル）及び暖房モードの４つのモードでの運転が可能である。以下に各モードにおける冷媒サイクル及び機能を説明する。
【００４０】
冷房・除霜モードの運転は、四方弁２を図５の実線位置に切り換え、開閉弁１５を閉じ開閉弁１６を開いた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この冷房・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を発揮させて車室内の冷房を行うことができる。また、室外熱交換器３で生じる放熱作用を利用して該熱交換器３の急速除霜を行うことができる。
【００４１】
除湿・暖房モード（パラレル）の運転は、四方弁２を図６の破線位置に切り換え、開閉弁１５，１６を開けた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通過した後に分流され、冷媒の一部分は第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。冷媒の残り部分は第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９の手前で上記の冷媒と合流する。つまり、この除湿・暖房モード（パラレル）の冷媒サイクルでは、室外熱交換器３で吸熱作用を発揮させ、さらに第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００４２】
除湿・暖房モード（シングル）の運転は、四方弁２を図６の破線位置に切り換え、開閉弁１５を閉じ開閉弁１６を開けた状態で、圧縮機１を作動させることによって行われる。同図に一点鎖線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この除湿・暖房モード（シングル）の冷媒サイクルでは、第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００４３】
暖房モードの運転は、四方弁２を図６の破線位置に切り換え、開閉弁１６を閉じ開閉弁１５を開けた状態で、圧縮機１を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒は第２の室内熱交換器５に流れ込んで凝縮され、受液器８を通じて第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この暖房モードの冷媒サイクルでは、第２の室内熱交換器５で放熱作用を発揮させて車室内の暖房を行うことができる。ちなみに、同モード運転時における暖房能力は圧縮機１の吐出能力調整及びダンパＤ３の開度によってコントロール可能である。
【００４４】
このように第３実施例の空気調和装置によれば、四方弁２及び開閉弁１５，１６による冷媒サイクルの切り換えで４つのモードでの運転があり、内燃機関等の熱源を有しない電気自動車等の車両において空調を好適に行える利点がある。他の効果は第１実施例と同様である。
【００４５】
尚、第３実施例に示した空気調和装置は、全ての開閉弁１５，１６を除外した回路構成でも、四方弁２による冷媒サイクルの切り換えで、第３実施例同様の冷房・除霜モードと除湿・暖房モード（パラレル）の２つのモードでの運転が可能である。
【００４６】
また、開閉弁１５を除外し開閉弁１６のみを残した回路構成とすれば、四方弁２と開閉弁１６による冷媒サイクルの切り換えで、上記の２モードに第３実施例同様の暖房モードを加えた３つのモードでの運転が可能となる。
【００４７】
更に、開閉弁１６を除外し開閉弁１５のみを残した回路構成とすれば、四方弁２と開閉弁１５による冷媒サイクルの切り換えで、上記の２モードに第１実施例同様の除湿・暖房モード（シングル）を加えた３つのモードでの運転が可能となる。
【００４８】
図７及び図８には本発明の第４実施例を示してある。本第４実施例は第１実施例の空気調和装置にブライン・冷媒熱交換器を利用したもので、第１実施例とは、管路２４，２５を第２の室内熱交換器５から離し両者間にブライン・冷媒熱交換器（以下単にブライン熱交換器と言う）２６の冷媒路を接続した点と、ブライン熱交換器２６のブライン路一端を電動ポンプ２７を介装した管路２８を介して第２の室内熱交換器５の一端に接続した点と、ブライン熱交換器２６のブライン路他端を管路２９を介して第２の室内熱交換器５の他端に接続した点で異なる。また、図７及び図８で示されている、逆止弁１０は特許請求の範囲の請求項１６に記載された第１の制御弁に相当し、逆止弁１１は特許請求の範囲の請求項１６に記載された第３の制御弁に相当し、逆止弁１２は特許請求の範囲の請求項１６に記載された第２の制御弁に相当する。また、開閉弁１４は特許請求の範囲の請求項２０に記載されたブライン・冷媒熱交換器用制御弁に相当し、開閉弁１５は特許請求の範囲の請求項１９に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項１８に記載された第１膨張弁用制御弁に相当し、開閉弁１７は特許請求の範囲の請求項２１に記載された室外熱交換器用制御弁に相当する。尚、第１実施例と同様、管路２４側の逆止弁１３は必ずしも必要なものではなく、また開閉弁１４の介装位置はブライン熱交換器２６の冷媒路出口側であってもよい。他の構成は第１実施例と同じであるため同一符号を用いその説明を省略する。
【００４９】
この空気調和装置は四方弁２及び開閉弁１４〜１７による冷媒サイクルの切り換えで、冷房・除霜モード，ドライ・除霜モード，除湿・暖房モード（パラレル），除湿・暖房モード（シングル）及び暖房モードの５つのモードでの運転が可能である。以下に各モードにおける冷媒サイクル及び機能を説明する。
【００５０】
冷房・除霜モードの運転は、四方弁２を図７の実線位置に切り換え、開閉弁１４，１５を閉じ開閉弁１６，１７を開いた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この冷房・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を発揮させて車室内の冷房を行うことができる。また、室外熱交換器３で生じる放熱作用を利用して該熱交換器３の急速除霜を行うことができる。
【００５１】
ドライ・除霜モードの運転は、四方弁２を図７の実線位置に切り換え、開閉弁１５を閉じ開閉弁１４，１６，１７を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒の一部分は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。冷媒の残り部分はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８の手前で上記の冷媒と合流する。つまり、このドライ・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を、且つ第２の室内熱交換器５で放熱作用を夫々発揮させて吹出温度を低下させることなく車室内の除湿を行うことができる。ちなみに、ドライ時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。また、室外熱交換器３で生じる放熱作用を利用して該室外熱交換器３の除霜を行うことができ、しかも該除霜時における吹出温度の低下も防止できる。
【００５２】
除湿・暖房モード（パラレル）の運転は、四方弁２を図８の破線位置に切り換え、開閉弁１４，１５，１６，１７を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８を通過した後に分流され、冷媒の一部分は第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。加熱されたブラインは、同図に実線矢印で示すようにブライン熱交換器２７と第２の室内熱交換器５の間を循環する。冷媒の残り部分は第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９の手前で上記の冷媒と合流する。つまり、この除湿・暖房モード（パラレル）の冷媒サイクルでは、室外熱交換器３で吸熱作用を発揮させ、さらに第２の室内熱交換器５で放熱作用を発揮させ、且つ第１の室内熱交換器４で吸熱作用を発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。
【００５３】
除湿・暖房モード（シングル）の運転は、四方弁２を図８の破線位置に切り換え、開閉弁１５，１７を閉じ開閉弁１４，１６を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に一点鎖線矢印で示すように、圧縮機１から吐出した冷媒はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。加熱されたブラインは、同図に一点鎖線矢印で示すようにブライン熱交換器２６と第２の室内熱交換器５の間を循環する。つまり、この除湿・暖房モード（シングル）の冷媒サイクルでは、第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。
【００５４】
暖房モードの運転は、四方弁２を図８の破線位置に切り換え、開閉弁１６を閉じ開閉弁１４，１５，１７を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８を通じて第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。加熱されたブラインは、同図に破線矢印で示すようにブライン熱交換器２６と第２の室内熱交換器５の間を循環する。つまり、この暖房モードの冷媒サイクルでは、第２の室内熱交換器５で放熱作用を発揮させて車室内の暖房を行うことができる。ちなみに、同モード運転時における暖房能力は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。
【００５５】
このように第４実施例の空気調和装置によれば、四方弁２及び開閉弁１４〜１７による冷媒サイクルの切り換えで５つのモードでの運転が可能であり、内燃機関等の熱源を有しない電気自動車等の車両において空調を好適に行える利点がある。他の効果は第１実施例と同様である。
【００５６】
尚、第４実施例に示した空気調和装置は、全ての開閉弁１４〜１７を除外した回路構成でも、四方弁２による冷媒サイクルの切り換えで、第４実施例同様のドライ・除霜モードと除湿・暖房モード（パラレル）の２つのモードでの運転が可能である。ドライ・除霜モードでは第２の室内熱交換器５への通風量をダンパＤ３で調整することにより冷房運転とドライ運転を選択でき、除霜時における吹出温度の低下も防止できる。また、開閉弁１７をオン・オフ制御することで室外熱交換器３と第２の室内熱交換器５への冷媒流量を調整することもできる。
【００５７】
また、開閉弁１４，１５，１７を除外し開閉弁１６のみを残した回路構成とすれば、四方弁２と開閉弁１６による冷媒サイクルの切り換えで、上記の２モードに第４実施例同様の暖房モードを加えた３つのモードでの運転が可能となる。
【００５８】
更に、開閉弁１４，１６，１７を除外し開閉弁１５のみを残した回路構成とすれば、四方弁２と開閉弁１５による冷媒サイクルの切り換えで、上記の２モードに第４実施例同様の除湿・暖房モード（シングル）を加えた３つのモードでの運転が可能となる。
【００５９】
更にまた、開閉弁１５，１６，１７を除外し開閉弁１４のみを残した回路構成とすれば、四方弁２と開閉弁１４による冷媒サイクルの切り換えで、上記の２モードに第４実施例同様の冷房・除霜モードを加えた３つのモードでの運転が可能となる。
【００６０】
更にまた、開閉弁１４，１５，１６を除外し開閉弁１７のみを残した回路構成とすれば、四方弁２と開閉弁１７による冷媒サイクルの切り換えで、上記のドライ・除霜モードに第４実施例同様の除湿・暖房モード（シングル）を加えた２つのモードでの運転が可能となる。
【００６１】
この他にも、開閉弁１４〜１７のうち２つまたは３つを適宜組み合わせることにより、第４実施例の空気調和装置で得られる５つの運転モードから必要モードのみを選択し設定することができる。
【００６２】
更にまた、第１，第２の膨張弁６，７として第２実施例で例示した閉動作可能な膨張弁６′，７′を用いれば、開閉弁１５，１６の役割を両膨張弁６′，７′で代用して回路構成を簡略化することができる。
【００６３】
図９及び図１０には本発明の第５実施例を示してある。本第５実施例は第３実施例の空気調和装置にブライン・冷媒熱交換器を利用したもので、第３実施例とは、管路２４，２５を第２の室内熱交換器５から離し両者間にブライン熱交換器２６の冷媒路を接続した点と、ブライン熱交換器２６のブライン路一端を電動ポンプ２７を介装した管路２８を介して第２の室内熱交換器５の一端に接続した点と、ブライン熱交換器２６のブライン路他端を管路２９を介して第２の室内熱交換器５の他端に接続した点で異なる。また、図９及び図１０で示されている、逆止弁１０は特許請求の範囲の請求項２２に記載された第１の制御弁に相当し、逆止弁１３は特許請求の範囲の請求項２２に記載された第２の制御弁に相当する。また、開閉弁１５は特許請求の範囲の請求項２５に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項２４に記載された第１膨張弁用制御弁に相当する。尚、第３実施例と同様、逆止弁１３は管路２５側に介装されていてもよい。他の構成は第３実施例と同じであるため同一符号を用いその説明を省略する。
【００６４】
この空気調和装置は四方弁２及び開閉弁１５，１６による冷媒サイクルの切り換えで冷房・除霜モード，除湿・暖房モード（パラレル），除湿・暖房モード（シングル）及び暖房モードの４つのモードでの運転が可能である。以下に各モードにおける冷媒サイクル及び機能を説明する。
【００６５】
冷房・除霜モードの運転は、四方弁２を図９の実線位置に切り換え、開閉弁１５を閉じ開閉弁１６を開いた状態で、圧縮機１を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒は室外熱交換器３に流れ込んで凝縮され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。つまり、この冷房・除霜モードの冷媒サイクルでは、第１の室内熱交換器４で吸熱作用を発揮させて車室内の冷房を行うことができる。また、室外熱交換器３で生じる放熱作用を利用して該熱交換器３の急速除霜を行うことができる。
【００６６】
除湿・暖房モード（パラレル）の運転は、四方弁２を図１０の実線位置に切り換え、開閉弁１５，１６を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に実線矢印で示すように、圧縮機１から吐出した冷媒はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８を通過した後に分流され、冷媒の一部分は第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。加熱されたブラインは、同図に実線矢印で示すようにブライン熱交換器２６と第２の室内熱交換器５の間を循環する。冷媒の残り部分は第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９の手前で上記の冷媒と合流する。つまり、この除湿・暖房モード（パラレル）の冷媒サイクルでは、室外熱交換器３で吸熱作用を発揮させ、さらに第２の室内熱交換器５で放熱作用を発揮させ、且つ第１の室内熱交換器４で吸熱作用を発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。
【００６７】
除湿・暖房モード（シングル）の運転は、四方弁２を図１０の実線位置に切り換え、開閉弁１５を閉じ開閉弁１６を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に一点鎖線矢印で示すように、圧縮機１から吐出した冷媒はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８を通じて第１の膨張弁６及び第１の室内熱交換器４に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。加熱されたブラインは、同図に一点鎖線矢印で示すようにブライン熱交換器２６と第２の室内熱交換器５の間を循環する。つまり、この除湿・暖房モード（シングル）の冷媒サイクルでは、第２の室内熱交換器５で放熱作用を、且つ第１の室内熱交換器４で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことができる。ちなみに、同モード運転時における暖房能力及び除湿量は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。
【００６８】
暖房モードの運転は、四方弁２を図１０の実線位置に切り換え、開閉弁１６を閉じ開閉弁１５を開けた状態で、圧縮機１及びポンプ２７を作動させることによって行われる。同図に破線矢印で示すように、圧縮機１から吐出した冷媒はブライン熱交換器２６に流れ込んでブラインと熱交換され、受液器８を通じて第２の膨張弁７及び室外熱交換器３に流れ込んで蒸発し、アキュムレータ９を通じて圧縮機１に吸入される。加熱されたブラインは、同図に破線矢印で示すようにブライン熱交換器２６と第２の室内熱交換器５の間を循環する。つまり、この暖房モードの冷媒サイクルでは、第２の室内熱交換器５で放熱作用を発揮させて車室内の暖房を行うことができる。ちなみに、同モード運転時における暖房能力は圧縮機１の吐出能力調整及びダンパＤ３の開度並びにポンプ２７の能力調整等によってコントロール可能である。
【００６９】
このように第５実施例の空気調和装置によれば、四方弁２及び開閉弁１５，１６による冷媒サイクルの切り換えで４つのモードでの運転が可能であり、内燃機関等の熱源を有しない電気自動車等の車両において空調を好適に行える利点がある。他の効果は第３実施例と同様である。
【００７０】
尚、第５実施例に示した空気調和装置は、全ての開閉弁１５，１６を除外した回路構成でも、四方弁２による冷媒サイクルの切り換えで、第５実施例同様の冷房・除霜モードと除湿・暖房モード（パラレル）の２つのモードでの運転が可能である。
【００７１】
また、開閉弁１５を除外し開閉弁１６のみを残した回路構成とすれば、四方弁２と開閉弁１６による冷媒サイクルの切り換えで、上記の２モードに第５実施例同様の暖房モードを加えた３つのモードでの運転が可能となる。
【００７２】
更に、開閉弁１６を除外し開閉弁１５のみを残した回路構成とすれば、四方弁２と開閉弁１５による冷媒サイクルの切り換えで、上記の２モードに第５実施例同様の除湿・暖房モード（シングル）を加えた３つのモードでの運転が可能となる。
【００７３】
更にまた、第１，第２の膨張弁６，７として第２実施例で例示した閉動作可能な膨張弁６′，７′を用いれば、開閉弁１５，１６の役割を両膨張弁６′，７′で代用して回路構成を簡略化することができる。
【００７４】
図１１には本発明の第６実施例を示してある。本第６実施例は第４実施例の空気調和装置にブライン加熱用の補助熱源を設けたもので、第４実施例とは、ブライン熱交換器２６内に電熱ヒータ３０を配置した点と、該電熱ヒータ３０に電源回路３１を接続した点で異なる。また、図１１で示されている、逆止弁１０は特許請求の範囲の請求項１６に記載された第１の制御弁に相当し、逆止弁１１は特許請求の範囲の請求項１６に記載された第３の制御弁に相当し、逆止弁１２は特許請求の範囲の請求項１６に記載された第２の制御弁に相当する。また、開閉弁１４は特許請求の範囲の請求項２０に記載されたブライン・冷媒熱交換器用制御弁に相当し、開閉弁１５は特許請求の範囲の請求項１９に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項１８に記載された第１ 膨張弁用制御弁に相当し、開閉弁１７は特許請求の範囲の請求項２１に記載された室外熱交換器用制御弁に相当する。
【００７５】
この空気調和装置では、２つの除湿・暖房モード及び暖房モードの運転時にブラインを電熱ヒータ３０の熱で補助的に加熱し、第２の室内熱交換器５における放熱能力を向上させることができる。また、冷房・除霜モードで室外熱交換器３の除霜を行う際に電熱ヒータ３０で加熱されたブラインを第２の室内熱交換器５に循環させれば、該熱交換器５で放熱作用を発揮させて吹出温度を調整できるので室外熱交換器３の除霜最中に車室内に冷風が吹き出されることがない。更に、外気温度が低くヒートポンプが正常に作動しない場合、或いは圧縮機１の作動が強制的に停止された場合でも、電熱ヒータ３０で加熱されたブラインを第２の室内熱交換器５に循環させ該熱交換器５で放熱作用を発揮させることで車室内の暖房を行える利点がある。他の作用，効果は第４実施例と同様である。
【００７６】
図１２には本発明の第７実施例を示してある。本第７実施例は第４実施例の空気調和装置にブライン加熱用の補助熱源を設けたもので、第４実施例とは、ブラインが流れる一方の管路２８に空気・ブライン熱交換器（以下単に空気熱交換器と言う）３２を介装した点と、該空気熱交換器３２に灯油等の液体燃料で燃焼するバーナ３３を連設した点で異なる。また、図１２で示されている、逆止弁１０は特許請求の範囲の請求項１６に記載された第１の制御弁に相当し、逆止弁１１は特許請求の範囲の請求項１６に記載された第３の制御弁に相当し、逆止弁１２は特許請求の範囲の請求項１６に記載された第２の制御弁に相当する。また、開閉弁１４は特許請求の範囲の請求項２０に記載されたブライン・冷媒熱交換器用制御弁に相当し、開閉弁１５は特許請求の範囲の請求項１９に記載された第１膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項１８に記載された第２膨張弁用制御弁に相当し、開閉弁１７は特許請求の範囲の請求項２１に記載された室外熱交換器用制御弁に相当する。
【００７７】
この空気調和装置では、２つの除湿・暖房モード及び暖房モードの運転時にブラインをバーナ３３の熱で補助的に加熱し、第２の室内熱交換器５における放熱能力を向上させることができる。また、冷房・除霜モードで室外熱交換器３の除霜を行う際にバーナ３３で加熱されたブラインを第２の室内熱交換器５に循環させれば、該熱交換器５で放熱作用を発揮させて吹出温度を調整できるので室外熱交換器３の除霜最中に車室内に冷風が吹き出されることがない。更に、外気温度が低くヒートポンプが正常に作動しない場合、或いは圧縮機１の作動が強制的に停止された場合でも、バーナ３３で加熱されたブラインを第２の室内熱交換器５に循環させ該熱交換器５で放熱作用を発揮させることで車室内の暖房を行える利点がある。他の作用，効果は第４実施例と同様である。
【００７８】
図１３には本発明の第８実施例を示してある。本第８実施例は第５実施例の空気調和装置にブライン加熱用の補助熱源を設けたもので、第５実施例とは、ブライン熱交換器２６内に電熱ヒータ３０を配置した点と、該電熱ヒータ３０に電源回路３１を接続した点で異なる。また、図１３で示されている、逆止弁１０は特許請求の範囲の請求項２２に記載された第１の制御弁に相当し、逆止弁１３は特許請求の範囲の請求項２２に記載された第２の制御弁に相当する。また、開閉弁１５は特許請求の範囲の請求項２５に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項２４に記載された第１膨張弁用制御弁に相当する。
【００７９】
この空気調和装置では、２つの除湿・暖房モード及び暖房モードの運転時にブラインを電熱ヒータ３０の熱で補助的に加熱し、第２の室内熱交換器５における放熱能力を向上させることができる。また、冷房・除霜モードで室外熱交換器３の除霜を行う際に電熱ヒータ３０で加熱されたブラインを第２の室内熱交換器５に循環させれば、該熱交換器５で放熱作用を発揮させて吹出温度を調整できるので室外熱交換器３の除霜最中に車室内に冷風が吹き出されることがない。更に、外気温度が低くヒートポンプが正常に作動しない場合、或いは圧縮機１の作動が強制的に停止された場合でも、電熱ヒータ３０で加熱されたブラインを第２の室内熱交換器５に循環させ該熱交換器５で放熱作用を発揮させることで車室内の暖房を行える利点がある。他の作用，効果は第５実施例と同様である。
【００８０】
図１４には本発明の第９実施例を示してある。本第９実施例は第５実施例の空気調和装置にブライン加熱用の補助熱源を設けたもので、第５実施例とは、ブラインが流れる一方の管路２８に空気熱交換器３２を介装した点と、該空気熱交換器３２に灯油等の液体燃料で燃焼するバーナ３３を連設した点で異なる。また、図１４で示されている、逆止弁１０は特許請求の範囲の請求項２２に記載された第１の制御弁に相当し、逆止弁１３は特許請求の範囲の請求項２２に記載された第２の制御弁に相当する。また、開閉弁１５は特許請求の範囲の請求項２５に記載された第２膨張弁用制御弁に相当し、開閉弁１６は特許請求の範囲の請求項２４に記載された第１膨張弁用制御弁に相当する。
【００８１】
この空気調和装置では、２つの除湿・暖房モード及び暖房モードの運転時にブラインをバーナ３３の熱で補助的に加熱し、第２の室内熱交換器５における放熱能力を向上させることができる。また、冷房・除霜モードで室外熱交換器３の除霜を行う際にバーナ３３で加熱されたブラインを第２の室内熱交換器５に循環させれば、該熱交換器５で放熱作用を発揮させて吹出温度を調整できるので室外熱交換器３の除霜最中に車室内に冷風が吹き出されることがない。更に、外気温度が低くヒートポンプが正常に作動しない場合、或いは圧縮機１の作動が強制的に停止された場合でも、バーナ３３で加熱されたブラインを第２の室内熱交換器５に循環させ該熱交換器５で放熱作用を発揮させることで車室内の暖房を行える利点がある。他の作用，効果は第５実施例と同様である。
【００８２】
尚、第６乃至第９実施例ではブライン熱交換器２６を備えた実施例４または６の空気調和装置に補助熱源を組み込んだ例を示したが、同補助熱源は冷媒加熱用として実施例１乃至３の空気調和装置に用いることもできる。即ち、暖房時に第２の室内熱交換器５に流入する冷媒を上記同様の補助熱源で加熱するようにすれば該第２の室内熱交換器における放熱能力を向上させることが可能であり、また暖房時に室外熱交換器３から流出する冷媒を補助熱源で加熱するようにすれば該室外熱交換器３における吸熱量不足を補うことができる。
【００８３】
上述した第１〜第９実施例では開閉弁１４〜１７として何れもオン・オフ式のものを例示したが、これら開閉弁１４〜１７は流量制御可能なものであってもよく、この場合には各弁における流量制御により室外熱交換器３及び第１，第２の室内熱交換器４，５の放熱，吸熱量を夫々コントロールすることができる。また、冷媒の流れ方向を制御する逆止弁１１〜１３はオン・オフ式の開閉弁や流量制御弁等で代用してもよい。
【００８４】
【発明の効果】
以上詳述したように、本発明に係る車両用空調装置によれば、第２の室内熱交換器を通過した冷媒の全部または一部を第１の膨張手段を通じて第１の室内熱交換器に導くことにより、第２の室内熱交換器で放熱作用を、且つ第１の室内熱交換器で吸熱作用を夫々発揮させて車室内の暖房及び除湿を同時に行うことが可能であり、降雨，降雪時等の多湿下で暖房運転を行う場合は勿論のこと、冷房から暖房に切り換えた際にも車室内の窓ガラスに曇りを生じることがなく、しかも吹出温度を低下させることなく除湿運転を行うことができ、快適な空調を実現することができる。
【図面の簡単な説明】
【図１】本発明の第１実施例を示す車両用空気調和装置の冷媒回路図
【図２】同冷媒回路図
【図３】本発明の第２実施例を示す車両用空気調和装置の冷媒回路図
【図４】同冷媒回路図
【図５】本発明の第３実施例を示す車両用空気調和装置の冷媒回路図
【図６】同冷媒回路図
【図７】本発明の第４実施例を示す車両用空気調和装置の冷媒回路図
【図８】同冷媒回路図
【図９】本発明の第５実施例を示す車両用空気調和装置の冷媒回路図
【図１０】同冷媒回路図
【図１１】本発明の第６実施例を示す車両用空気調和装置の冷媒回路図
【図１２】本発明の第７実施例を示す車両用空気調和装置の冷媒回路図
【図１３】本発明の第８実施例を示す車両用空気調和装置の冷媒回路図
【図１４】本発明の第９実施例を示す車両用空気調和装置の冷媒回路図
【符号の説明】
１…圧縮機、２…四方弁、３…室外熱交換器、４…第１の室内熱交換器、５…第２の室内熱交換器、６，６′…第１の膨張弁、７，７′…第２の膨張弁、８…受液器、９…アキュムレータ、１０〜１３…逆止弁、１４〜１７…開閉弁、１８〜２５，２５ａ，２５ｂ，２８，２９…管路、２６…ブライン・冷媒熱交換器、２７…ポンプ、３０…電熱ヒータ、３３…バーナ。[0001]
[Industrial applications]
The present invention relates to an air conditioner for a vehicle that cools and heats a passenger compartment, and more particularly to an air conditioner useful for an electric vehicle and the like.
[0002]
[Prior art]
BACKGROUND ART Generally, a heat pump type air conditioner is used for a vehicle such as an electric vehicle having no heat source such as an internal combustion engine. This air conditioner is mainly composed of a compressor, a four-way valve, an outdoor heat exchanger, two expansion means, and an indoor heat exchanger. The refrigerant cycle is switched by the four-way valve to convert the indoor heat exchanger into a heat absorber or an indoor heat exchanger. It is used as a radiator to cool and heat the cabin.
[0003]
[Problems to be solved by the invention]
In the above-mentioned conventional air conditioner, basically only operation in the cooling mode and the heating mode can be performed. Therefore, when heating is performed under humid conditions such as rainfall and snowfall, the window glass in the vehicle compartment is liable to be fogged. When switching to heating, there is a problem that the condensed water adhering to the indoor heat exchanger evaporates and fogging similar to the above occurs. Further, even if only dehumidification is performed, there is a disadvantage that a decrease in the blowing temperature is unavoidable and the comfort is greatly impaired.
[0004]
The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide an air conditioner for a vehicle that can perform a dehumidifying operation without causing fogging of a window glass in a vehicle compartment during heating and without reducing a blowing temperature. is there.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, according to the present invention, a compressor, an outdoor heat exchanger, a first indoor heat exchanger, a first expansion means and a second expansion means are provided, and a refrigerant cycle is switched by a four-way valve or the like. A heat pump type air conditioner for a vehicle that cools and heats a vehicle interior is provided with a second indoor heat exchanger that is used as a radiator at least during heating, and a refrigerant that has passed through the second indoor heat exchanger is provided. A pipe is provided for guiding the refrigerant passing through the second indoor heat exchanger to the outdoor heat exchanger through the second expansion means, and a pipe is provided for guiding the refrigerant having passed through the second indoor heat exchanger to the first indoor heat exchanger through the first expansion means. .
[0006]
[Action]
In the air conditioner for a vehicle according to the present invention, while the second indoor heat exchanger is used as a radiator during heating, all or a part of the refrigerant that has passed through the second indoor heat exchanger is subjected to the first expansion. It can be led to the first indoor heat exchanger through the means. That is, the second indoor heat exchanger exerts a heat radiation effect, and the first indoor heat exchanger exerts a heat absorption effect, thereby simultaneously heating and dehumidifying the vehicle interior.
[0007]
【Example】
1 and 2 show a first embodiment of the present invention. In the figure, 1 is a variable capacity electric compressor, 2 is an electromagnetic four-way valve, 3 is an outdoor heat exchanger, 4 is a first indoor heat exchanger, 5 is a second indoor heat exchanger, 6 Is a heat-sensitive first expansion valve, 7 is a heat-sensitive second expansion valve, 8 is a liquid receiver, 9 is an accumulator, 10 to 13 are check valves, 14 to 17 are electromagnetic on-off valves, A Is a duct for air conditioning in the vehicle interior, F is an electric fan, D1 to D4 are electric dampers, and the first and second indoor heat exchangers 4 and 5 are arranged in the duct A.Here, the check valve 10 corresponds to a first control valve described in claim 3 of the present invention, and the check valve 11 corresponds to a third control valve described in claim 3 of the present invention. The check valve 12 corresponds to a second control valve according to a third aspect of the present invention. The on-off valve 14 corresponds to the control valve for the second indoor heat exchanger described in claim 7 of the present invention, and the on-off valve 15 corresponds to the second expansion valve described in claim 6 of the present invention. The on-off valve 16 corresponds to a first expansion valve control valve described in claim 5 of the present invention, and the on-off valve 17 corresponds to claim 8 of the present invention. It corresponds to a control valve for an outdoor heat exchanger.
[0008]
A discharge port of the compressor 1 is connected to a first port 2a of the four-way valve 2 via a pipe 18 and a second port 2b of the four-way valve 2 is connected to a outdoor heat source via a pipe 19 provided with an on-off valve 17. It is connected to one end of the exchanger 3. Further, the other end of the outdoor heat exchanger 3 is connected to the inlet of the first indoor heat exchanger 4 through a pipe line 20 in which the second expansion valve 7, on-off valves 15 and 16, and the first expansion valve 6 are interposed. , And the outlet of the first indoor heat exchanger 4 is connected to the inlet of the accumulator 9 via a pipe 21. Further, a pipe 22 branched from the middle of the pipe 21 is connected to a third port 2 c of the four-way valve 2, and an outlet of the accumulator 9 is connected to a suction port of the compressor 1 via a pipe 23.
[0009]
One end of a pipe 24 in which check valves 10 and 13 are interposed facing each other is connected between the other end of the outdoor heat exchanger 3 in the pipe 20 and the second expansion valve 7. Is connected to the outlet of the second indoor heat exchanger 5. The inlet of the receiver 8 is connected between the check valves 10 and 13 in the line 24, and the outlet is connected between the on-off valves 15 and 16 in the line 20. The inlet of the second indoor heat exchanger 5 is connected to one end of a pipe 25 provided with an on-off valve 14, and the other end of the pipe 25 is connected to check valves 11 and 12 in opposite directions. The two pipes 25a and 25b are branched, and one pipe 25a is connected to the middle of the pipe 19, and the other pipe 25b is connected to the fourth port 2d of the four-way valve 2. Since the flow direction of the refrigerant in the second indoor heat exchanger 5 can be controlled by the check valves 11 and 12 of the pipes 25a and 25b, the check valve 13 on the pipe 24 side is not always necessary. The interposition position of the on-off valve 14 may be on the outlet side of the second indoor heat exchanger 5.
[0010]
The dampers D1 and D2 of the duct A are for selecting the outlets A1 and A2, and are rotatably disposed inside the outlets A1 and A2. The damper D3 is for adjusting the amount of air flow to the second indoor heat exchanger 5, and is rotatably arranged upstream of the indoor heat exchanger 5. The damper D4 is for selecting the intake ports A3, A4 (indoor air and outdoor air), and is rotatably disposed inside the intake ports A3, A4.
[0011]
In this air conditioner, the refrigerant cycle is switched by the four-way valve 2 and the on-off valves 14 to 17, and the cooling / defrosting mode, the dry / defrosting mode, the dehumidifying / heating mode (parallel), the dehumidifying / heating mode (single), and the heating Operation in five modes is possible. The refrigerant cycle and function in each mode will be described below.
[0012]
The operation in the cooling / defrosting mode is performed by switching the four-way valve 2 to the solid line position in FIG. 1, operating the compressor 1 with the on-off valves 14 and 15 closed and the on-off valves 16 and 17 open. As shown by solid arrows in the figure, the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is condensed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger 4. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the cooling / defrosting mode, the first indoor heat exchanger 4 can exert a heat absorbing effect to cool the vehicle interior. Further, rapid defrosting of the heat exchanger 3 can be performed by utilizing a heat radiation effect generated in the outdoor heat exchanger 3.
[0013]
The operation in the dry / defrosting mode is performed by switching the four-way valve 2 to the solid line position in FIG. 1, operating the compressor 1 with the on-off valve 15 closed and the on-off valves 14, 16, 17 opened. As shown by the dashed arrow in the figure, a part of the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger. 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. The remaining part of the refrigerant flows into the second indoor heat exchanger 5 and is condensed, and merges with the above-mentioned refrigerant before the liquid receiver 8. That is, in the refrigerant cycle in the dry / defrost mode, the first indoor heat exchanger 4 exerts a heat absorbing action and the second indoor heat exchanger 5 exerts a heat dissipation action, thereby reducing the blow-out temperature. Dehumidification of the vehicle interior can be performed. Incidentally, the temperature and the amount of dehumidification in the dry state can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3. In addition, it is possible to perform defrosting of the outdoor heat exchanger 3 by utilizing a heat radiation effect generated in the outdoor heat exchanger 3, and it is also possible to prevent a decrease in the blowing temperature at the time of the defrosting.
[0014]
In the dehumidification / heating mode (parallel) operation, the four-way valve 2BreakingThe operation is performed by switching the compressor to the line position and operating the compressor 1 with the on-off valves 14, 15, 16, 17 opened. As shown by a solid line arrow in the drawing, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5, is condensed, passes through the liquid receiver 8, and is divided, and a part of the refrigerant is in the second state. It flows into the expansion valve 7 and the outdoor heat exchanger 3 and evaporates, and is sucked into the compressor 1 through the accumulator 9. The remaining portion of the refrigerant flows into the first expansion valve 6 and the first indoor heat exchanger 4 and evaporates, and merges with the above-described refrigerant before the accumulator 9. That is, in the refrigerant cycle in the dehumidifying / heating mode (parallel), the outdoor heat exchanger 3 exerts a heat absorbing effect, the second indoor heat exchanger 5 emits heat, and the first indoor heat exchanger 4 Thus, the heat absorption and dehumidification of the vehicle interior can be simultaneously performed by exerting the heat absorbing effects. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0015]
In the operation in the dehumidifying / heating mode (single), the four-way valve 2 is connected as shown in FIG.BreakingThe operation is performed by switching to the line position and operating the compressor 1 with the on-off valves 15 and 17 closed and the on-off valves 14 and 16 opened. As shown by a dashed-dotted arrow in the figure, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger. It flows into the exchanger 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the dehumidification / heating mode (single), the second indoor heat exchanger 5 exerts a heat radiation effect, and the first indoor heat exchanger 4 exerts a heat absorption effect to heat and heat the vehicle interior. Dehumidification can be performed simultaneously. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0016]
In the heating mode operation, the four-way valve 2BreakingThe operation is performed by switching the compressor to the line position and operating the compressor 1 with the on-off valve 16 closed and the on-off valves 14, 15, 17 opened. As shown by the dashed arrow in the figure, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5 and is condensed, and is condensed through the liquid receiver 8 to the second expansion valve 7 and the outdoor heat exchanger 3. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. That is, in the refrigerant cycle in the heating mode, the second indoor heat exchanger 5 can exert a heat radiation effect to heat the vehicle interior. Incidentally, the heating capacity during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0017]
As described above, according to the air-conditioning apparatus of the first embodiment, it is possible to operate in five modes by switching the refrigerant cycle by the four-way valve 2 and the on-off valves 14 to 17, and to operate electricity without a heat source such as an internal combustion engine. There is an advantage that air conditioning can be suitably performed in a vehicle such as an automobile.
[0018]
In addition, during the operation in the dry / defrost mode, the blowout temperature can be adjusted by exerting the heat radiation effect in the second indoor heat exchanger 5, so that no cool air is blown into the vehicle interior during the dry or defrosting. .
[0019]
Furthermore, during operation in the two dehumidifying / heating modes, the interior of the vehicle can be heated while dehumidifying, so that the windowpane does not become cloudy even under humid conditions such as rainfall and snowfall, and from cooling to heating. , It is possible to realize comfortable heating by preventing the occurrence of fogging when switching to.
[0020]
Furthermore, during the operation in the dehumidification / heating mode (parallel), both the outdoor heat exchanger 3 and the first indoor heat exchanger 4 exhibit the heat absorbing effect, so that the outdoor operation when performing the heating operation in a cold region or the like. It is possible to prevent frost formation on the heat exchanger 3 and prevent a decrease in the heating capacity.
[0021]
Note that the air conditioner shown in the first embodiment has the same dry / defrosting mode as the first embodiment by switching the refrigerant cycle by the four-way valve 2 even in a circuit configuration excluding all the on-off valves 14 to 17. Operation in two modes of the dehumidification / heating mode (parallel) is possible. In the dry / defrost mode, the cooling operation or the dry operation can be selected by adjusting the amount of air flow to the second indoor heat exchanger 5 with the damper D3, and a decrease in the blow-out temperature during defrost can be prevented. Further, by controlling the on / off of the on-off valve 17, the flow rate of the refrigerant to the outdoor heat exchanger 3 and the second indoor heat exchanger 5 can be adjusted.
[0022]
Further, if the circuit configuration is such that the on-off valves 14, 15, and 17 are excluded and only the on-off valve 16 is left, switching of the refrigerant cycle by the four-way valve 2 and the on-off valve 16 switches the two modes to the same as in the first embodiment. Operation in three modes including the heating mode becomes possible.
[0023]
Further, if the circuit configuration is such that the on-off valves 14, 16, 17 are excluded and only the on-off valve 15 is left, the two modes are switched to the two modes by switching the refrigerant cycle by the four-way valve 2 and the on-off valve 15, as in the first embodiment. Operation in three modes including the dehumidification / heating mode (single) is possible.
[0024]
Furthermore, if the circuit configuration is such that the on-off valves 15, 16, 17 are excluded and only the on-off valve 14 is left, the refrigerant cycle is switched by the four-way valve 2 and the on-off valve 14 to switch to the above-described two modes as in the first embodiment. Operation in three modes including the cooling / defrosting mode.
[0025]
Further, if the circuit configuration is such that the on-off valves 14, 15, 16 are excluded and only the on-off valve 17 is left, the refrigerant cycle is switched by the four-way valve 2 and the on-off valve 17, and the first dry / defrosting mode is set. The operation in two modes including the dehumidification / heating mode (single) similar to the embodiment can be performed.
[0026]
In addition, by appropriately combining two or three of the on-off valves 14 to 17, only the necessary mode can be selected and set from the five operation modes obtained in the air conditioner of the first embodiment. .
[0027]
3 and 4 show a second embodiment of the present invention. The second embodiment is a simplified version of the air conditioner of the first embodiment. The first embodiment differs from the first embodiment in that the on-off valves 15 and 16 are eliminated from the pipeline 20 and the first and second expansions. The difference is that electronic valves (6 ', 7') capable of remotely controlling the opening and closing operations are used as the valves. The degree of opening of both expansion valves 6 ', 7' is controlled based on the temperature of refrigerant discharged from the heat exchanger, as in the case of the thermal type.Further, the check valve 10 shown in FIGS. 3 and 4 corresponds to the first control valve described in claim 3 of the present invention, and the check valve 11 corresponds to the claim of the present invention. The check valve 12 corresponds to a third control valve described in claim 3, and the check valve 12 corresponds to a second control valve described in claim 3 of the claims. The on-off valve 14 corresponds to a control valve for a second indoor heat exchanger described in claim 7 of the present invention, and the on-off valve 17 corresponds to the outdoor heat exchanger described in claim 8 of the present invention. It corresponds to a control valve.As in the first embodiment, the check valve 13 on the pipe line 24 side is not always necessary, and the interposition position of the on-off valve 14 may be on the outlet side of the second indoor heat exchanger 5. Good. The other configuration is the same as that of the first embodiment, so that the same reference numerals are used and the description is omitted.
[0028]
In this air conditioner, a refrigerant cycle is switched by a four-way valve 2, first and second expansion valves 6 'and 7', and on-off valves 14 and 17 to provide a cooling / defrost mode, a dry / defrost mode, a dehumidification / heating mode. Operation in five modes of a mode (parallel), a dehumidification / heating mode (single), and a heating mode is possible. The refrigerant cycle and function in each mode will be described below.
[0029]
In the operation in the cooling / defrosting mode, the compressor 1 is operated with the four-way valve 2 switched to the solid line position in FIG. 3 and the second expansion valve 7 ′ and the on-off valve 14 closed and the on-off valve 17 opened. Done by As shown by the solid arrows in FIG. 1, the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 ′ and the first indoor heat exchanger 4. Into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the cooling / defrosting mode, the first indoor heat exchanger 4 can exert a heat absorbing effect to cool the vehicle interior. Further, rapid defrosting of the heat exchanger 3 can be performed by utilizing a heat radiation effect generated in the outdoor heat exchanger 3.
[0030]
The operation in the dry / defrost mode is performed by switching the four-way valve 2 to the solid line position in FIG. 3, operating the compressor 1 with the second expansion valve 7 'closed and the on-off valves 14, 17 opened. Is As shown by a dashed arrow in the figure, a part of the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 ′ and the first indoor heat exchange. It flows into the compressor 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. The remaining part of the refrigerant flows into the second indoor heat exchanger 5 and is condensed, and merges with the above-mentioned refrigerant before the liquid receiver 8. That is, in the refrigerant cycle in the dry / defrost mode, the first indoor heat exchanger 4 exerts a heat absorbing action and the second indoor heat exchanger 5 exerts a heat dissipation action, thereby reducing the blow-out temperature. Dehumidification of the vehicle interior can be performed. Incidentally, the temperature and the amount of dehumidification during the drying can be controlled by adjusting the discharge capacity of the compressor and the opening of the damper D3. In addition, it is possible to perform defrosting of the outdoor heat exchanger 3 by utilizing a heat radiation effect generated in the outdoor heat exchanger 3, and it is also possible to prevent a decrease in the blowing temperature at the time of the defrosting.
[0031]
In the operation in the dehumidification / heating mode (parallel), the four-way valve 2BreakingThe operation is performed by operating the compressor 1 while switching to the line position and opening the on-off valves 14 and 17. As shown by a solid line arrow in the drawing, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5, is condensed, passes through the liquid receiver 8, and is divided, and a part of the refrigerant is in the second state. It flows into the expansion valve 7 ′ and the outdoor heat exchanger 3, evaporates, and is sucked into the compressor 1 through the accumulator 9. The remaining part of the refrigerant flows into the first expansion valve 6 ′ and the first indoor heat exchanger 4, evaporates, and merges with the refrigerant before the accumulator 9. That is, in the refrigerant cycle in the dehumidifying / heating mode (parallel), the outdoor heat exchanger 3 exerts a heat absorbing effect, the second indoor heat exchanger 5 emits heat, and the first indoor heat exchanger 4 Thus, the heat absorption and dehumidification of the vehicle interior can be simultaneously performed by exerting the heat absorbing effects. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0032]
In the operation in the dehumidifying / heating mode (single), the four-way valve 2 is set to the position shown in FIG.BreakingThis is performed by operating the compressor 1 with the second expansion valve 7 'and the on-off valve 17 closed and the on-off valve 14 opened while switching to the line position. As shown by an alternate long and short dash line arrow in the drawing, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 ′ and the first indoor heat exchanger 5. It flows into the heat exchanger 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the dehumidification / heating mode (single), the second indoor heat exchanger 5 exerts a heat radiation effect, and the first indoor heat exchanger 4 exerts a heat absorption effect to heat and heat the vehicle interior. Dehumidification can be performed simultaneously. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0033]
In the heating mode operation, the four-way valve 2BreakingThis is performed by operating the compressor 1 with the first expansion valve 6 'closed and the on-off valves 14, 17 opened while switching to the line position. As shown by the dashed arrow in the drawing, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5 and is condensed, and is passed through the liquid receiver 8 to the second expansion valve 7 ′ and the outdoor heat exchanger 3. Into the compressor 1 through the accumulator 9. That is, in the refrigerant cycle in the heating mode, the second indoor heat exchanger 5 can exert a heat radiation effect to heat the vehicle interior. Incidentally, the heating capacity during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0034]
As described above, according to the air conditioner of the second embodiment, operation in five modes is performed by switching the refrigerant cycle by the four-way valve 2, the first and second expansion valves 6 'and 7', and the on-off valves 14 and 17. This is advantageous in that air conditioning can be suitably performed in a vehicle such as an electric vehicle having no heat source such as an internal combustion engine. In addition, the functions of the on-off valves 15 and 16 in the air conditioner of the first embodiment can be replaced by the two expansion valves 6 'and 7' to simplify the circuit configuration. Other effects are similar to those of the first embodiment.
[0035]
In the air conditioner shown in the second embodiment, the refrigerant cycle is switched by the four-way valve 2 and the first and second expansion valves 6 'and 7' even in a circuit configuration excluding all the on-off valves 14 and 17. Thus, it is possible to operate in the four modes of the dry / defrost mode, the dehumidification / heating mode (parallel), the dehumidification / heating mode (single), and the heating mode as in the second embodiment. In the dry / defrost mode, the cooling operation or the dry operation can be selected by adjusting the amount of air flow to the second indoor heat exchanger 5 with the damper D3, and a decrease in the blow-out temperature during defrost can be prevented. Further, by controlling the on / off of the on-off valve 17, the flow rate of the refrigerant to the outdoor heat exchanger 3 and the second indoor heat exchanger 5 can be adjusted.
[0036]
Further, if the circuit configuration is such that the on-off valve 17 is excluded and only the on-off valve 14 is left, the refrigerant cycle is switched by the four-way valve 2, the first and second expansion valves 6 ', 7' and the on-off valve 14, and Operation in the same five modes as in the second embodiment becomes possible.
[0037]
Furthermore, if the circuit configuration is such that the on-off valve 14 is excluded and only the on-off valve 17 is left, the four-way valve 2, the first and second expansion valves 6 ′, 7 ′, and the switching of the refrigerant cycle by the on-off valve 17 allow the second cycle to be performed. Operation in the four modes of the dry / defrost mode, the dehumidification / heating mode (parallel), the dehumidification / heating mode (single), and the heating mode as in the second embodiment is possible.
[0038]
5 and 6 show a third embodiment of the present invention. The third embodiment is a simplified version of the air conditioner of the first embodiment. The third embodiment differs from the first embodiment in that the on-off valve 17 is excluded from the pipe 19, and the check valves 11, 12 and the pipe The difference is that the pipes 25a and 25b are excluded, and that the on-off valve 14 is excluded from the pipe 25 and the pipe 25 is connected to the fourth port 2d of the four-way valve 2.In addition, the check valve 10 shown in FIGS. 5 and 6 corresponds to the first control valve described in claim 9, and the check valve 13 corresponds to the claim. This corresponds to the second control valve described in item 9. The on-off valve 15 corresponds to the control valve for the second expansion valve described in claim 9 of the present invention, and the on-off valve 16 corresponds to the control valve for the first expansion valve described in claim 11 of the present invention. It corresponds to a control valve.The check valve 13 for controlling the flow direction of the refrigerant in the second indoor heat exchanger 5 may be interposed on the pipe 25 side. The other configuration is the same as that of the first embodiment, so that the same reference numerals are used and the description is omitted.
[0039]
In this air conditioner, the refrigerant cycle is switched by the four-way valve 2 and the on-off valves 15 and 16, and in four modes of a cooling / defrosting mode, a dehumidifying / heating mode (parallel), a dehumidifying / heating mode (single), and a heating mode. Operation is possible. The refrigerant cycle and function in each mode will be described below.
[0040]
The operation in the cooling / defrosting mode is performed by switching the four-way valve 2 to the solid line position in FIG. 5, operating the compressor 1 with the on-off valve 15 closed and the on-off valve 16 open. As shown by solid arrows in the figure, the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is condensed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger 4. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the cooling / defrosting mode, the first indoor heat exchanger 4 can exert a heat absorbing effect to cool the vehicle interior. Further, rapid defrosting of the heat exchanger 3 can be performed by utilizing a heat radiation effect generated in the outdoor heat exchanger 3.
[0041]
In the operation in the dehumidification / heating mode (parallel), the four-way valve 2BreakingThe operation is performed by operating the compressor 1 while switching to the line position and opening the on-off valves 15 and 16. As shown by a solid line arrow in the drawing, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5, is condensed, passes through the liquid receiver 8, and is divided, and a part of the refrigerant is in the second state. It flows into the expansion valve 7 and the outdoor heat exchanger 3 and evaporates, and is sucked into the compressor 1 through the accumulator 9. The remaining portion of the refrigerant flows into the first expansion valve 6 and the first indoor heat exchanger 4 and evaporates, and merges with the above-described refrigerant before the accumulator 9. That is, in the refrigerant cycle in the dehumidifying / heating mode (parallel), the outdoor heat exchanger 3 exerts a heat absorbing effect, the second indoor heat exchanger 5 emits heat, and the first indoor heat exchanger 4 Thus, the heat absorption and dehumidification of the vehicle interior can be simultaneously performed by exerting the heat absorbing effects. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0042]
In the operation in the dehumidifying / heating mode (single), the four-way valve 2 is set to the position shown in FIG.BreakingThe operation is performed by operating the compressor 1 while switching to the line position, closing the on-off valve 15 and opening the on-off valve 16. As shown by a dashed-dotted arrow in the figure, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger. It flows into the exchanger 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the dehumidification / heating mode (single), the second indoor heat exchanger 5 exerts a heat radiation effect, and the first indoor heat exchanger 4 exerts a heat absorption effect to heat and heat the vehicle interior. Dehumidification can be performed simultaneously. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0043]
In the heating mode operation, the four-way valve 2BreakingThe operation is performed by operating the compressor 1 in a state where the switching is performed to the line position and the on-off valve 16 is closed and the on-off valve 15 is opened. As shown by the dashed arrow in the figure, the refrigerant discharged from the compressor 1 flows into the second indoor heat exchanger 5 and is condensed, and is condensed through the liquid receiver 8 to the second expansion valve 7 and the outdoor heat exchanger 3. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. That is, in the refrigerant cycle in the heating mode, the second indoor heat exchanger 5 can exert a heat radiation effect to heat the vehicle interior. Incidentally, the heating capacity during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1 and the opening of the damper D3.
[0044]
As described above, according to the air conditioner of the third embodiment, there are four modes of operation by switching the refrigerant cycle by the four-way valve 2 and the on-off valves 15 and 16, and the electric vehicle or the like without a heat source such as an internal combustion engine There is an advantage that air conditioning can be suitably performed in the vehicle. Other effects are similar to those of the first embodiment.
[0045]
The air conditioner shown in the third embodiment has the same cooling / defrosting mode as the third embodiment by switching the refrigerant cycle by the four-way valve 2 even in a circuit configuration excluding all the on-off valves 15 and 16. Operation in two modes of the dehumidification / heating mode (parallel) is possible.
[0046]
Further, if the circuit configuration is such that the on-off valve 15 is excluded and only the on-off valve 16 is left, the heating mode similar to the third embodiment is added to the two modes by switching the refrigerant cycle by the four-way valve 2 and the on-off valve 16. Operation in the three modes is also possible.
[0047]
Furthermore, if the circuit configuration is such that the on-off valve 16 is excluded and only the on-off valve 15 is left, the refrigerant cycle is switched by the four-way valve 2 and the on-off valve 15 to switch the two modes to the above-described dehumidification / heating mode as in the first embodiment. Operation in three modes including (single) is possible.
[0048]
7 and 8 show a fourth embodiment of the present invention. In the fourth embodiment, a brine / refrigerant heat exchanger is used in the air conditioner of the first embodiment. In the fourth embodiment, the pipes 24 and 25 are separated from the second indoor heat exchanger 5. A point at which a refrigerant path of a brine / refrigerant heat exchanger (hereinafter simply referred to as a brine heat exchanger) 26 is connected between the two, and a line 28 at which one end of the brine path of the brine heat exchanger 26 is provided with an electric pump 27 interposed therebetween. And a point where the other end of the brine path of the brine heat exchanger 26 is connected to the other end of the second indoor heat exchanger 5 via a pipe 29. Different.The check valve 10 shown in FIGS. 7 and 8 corresponds to the first control valve described in claim 16 of the present invention, and the check valve 11 corresponds to the claim of the present invention. The check valve 12 corresponds to a third control valve described in claim 16, and the check valve 12 corresponds to a second control valve described in claim 16 of the claims. The on-off valve 14 corresponds to a control valve for a brine / refrigerant heat exchanger described in claim 20 of the present invention, and the on-off valve 15 corresponds to the second expansion valve described in claim 19 of the present invention. The on-off valve 16 corresponds to the control valve for the first expansion valve described in claim 18 of the present invention, and the on-off valve 17 corresponds to the claim 21 of the present invention. It corresponds to a control valve for an outdoor heat exchanger.Incidentally, as in the first embodiment, the check valve 13 on the pipe line 24 side is not always necessary, and the interposition position of the on-off valve 14 may be on the refrigerant path outlet side of the brine heat exchanger 26. . The other configuration is the same as that of the first embodiment, so that the same reference numerals are used and the description is omitted.
[0049]
In this air conditioner, the refrigerant cycle is switched by the four-way valve 2 and the on-off valves 14 to 17, and the cooling / defrosting mode, the dry / defrosting mode, the dehumidifying / heating mode (parallel), the dehumidifying / heating mode (single), and the heating Operation in five modes is possible. The refrigerant cycle and function in each mode will be described below.
[0050]
The operation in the cooling / defrosting mode is performed by switching the four-way valve 2 to the solid line position in FIG. 7, operating the compressor 1 with the on-off valves 14, 15 closed and the on-off valves 16, 17 open. As shown by solid arrows in the figure, the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is condensed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger 4. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the cooling / defrosting mode, the first indoor heat exchanger 4 can exert a heat absorbing effect to cool the vehicle interior. Further, rapid defrosting of the heat exchanger 3 can be performed by utilizing a heat radiation effect generated in the outdoor heat exchanger 3.
[0051]
The operation in the dry / defrosting mode is performed by switching the four-way valve 2 to the position indicated by the solid line in FIG. 7, operating the compressor 1 and the pump 27 with the on-off valve 15 closed and the on-off valves 14, 16, 17 opened. Done. As shown by the dashed arrow in the figure, a part of the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is passed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger. 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. The remaining part of the refrigerant flows into the brine heat exchanger 26 and exchanges heat with the brine, and merges with the refrigerant before the liquid receiver 8. That is, in the refrigerant cycle in the dry / defrost mode, the first indoor heat exchanger 4 exerts a heat absorbing action and the second indoor heat exchanger 5 exerts a heat dissipation action, thereby reducing the blow-out temperature. Dehumidification of the vehicle interior can be performed. Incidentally, the heating capacity and the dehumidification amount during the dry time can be controlled by adjusting the discharge capacity of the compressor 1, the opening of the damper D3, the capacity of the pump 27, and the like. In addition, it is possible to perform defrosting of the outdoor heat exchanger 3 by utilizing a heat radiation effect generated in the outdoor heat exchanger 3, and it is also possible to prevent a decrease in the blowing temperature at the time of the defrosting.
[0052]
In the operation in the dehumidification / heating mode (parallel), the four-way valve 2BreakingThis is performed by operating the compressor 1 and the pump 27 while switching to the line position and opening the on-off valves 14, 15, 16, 17. As shown by the solid line arrows in the figure, the refrigerant discharged from the compressor 1 flows into the brine heat exchanger 26 and exchanges heat with the brine. After passing through the liquid receiver 8, the refrigerant is branched and a part of the refrigerant is changed to the second refrigerant. It flows into the expansion valve 7 and the outdoor heat exchanger 3 and evaporates, and is sucked into the compressor 1 through the accumulator 9. The heated brine circulates between the brine heat exchanger 27 and the second indoor heat exchanger 5 as shown by the solid arrows in FIG. The remaining portion of the refrigerant flows into the first expansion valve 6 and the first indoor heat exchanger 4 and evaporates, and merges with the above-described refrigerant before the accumulator 9. In other words, in the refrigerant cycle in the dehumidification / heating mode (parallel), the outdoor heat exchanger 3 exerts a heat absorbing action, the second indoor heat exchanger 5 exerts a heat dissipation action, and the first indoor heat exchange. The heating and dehumidification of the vehicle interior can be performed simultaneously by exerting the heat absorbing effect by the heater 4. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1, adjusting the opening of the damper D3, adjusting the capacity of the pump 27, and the like.
[0053]
For the operation in the dehumidification / heating mode (single), the four-way valve 2BreakingThe operation is performed by operating the compressor 1 and the pump 27 while switching to the line position and closing the on-off valves 15 and 17 and opening the on-off valves 14 and 16. As shown by the one-dot chain line arrow in FIG. 2, the refrigerant discharged from the compressor 1 flows into the brine heat exchanger 26 and exchanges heat with the brine, and the first expansion valve 6 and the first indoor heat through the liquid receiver 8. It flows into the exchanger 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. The heated brine circulates between the brine heat exchanger 26 and the second indoor heat exchanger 5 as indicated by a dashed line arrow in FIG. In other words, in the refrigerant cycle in the dehumidification / heating mode (single), the second indoor heat exchanger 5 exerts a heat radiation effect, and the first indoor heat exchanger 4 exerts a heat absorption effect to heat and heat the vehicle interior. Dehumidification can be performed simultaneously. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1, adjusting the opening of the damper D3, adjusting the capacity of the pump 27, and the like.
[0054]
In the heating mode operation, the four-way valve 2BreakingThe operation is performed by operating the compressor 1 and the pump 27 with the on-off valve 16 closed and the on-off valves 14, 15, 17 opened while switching to the line position. As shown by a dashed arrow in the figure, the refrigerant discharged from the compressor 1 flows into the brine heat exchanger 26 and exchanges heat with the brine, and is transferred to the second expansion valve 7 and the outdoor heat exchanger 3 through the liquid receiver 8. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. The heated brine circulates between the brine heat exchanger 26 and the second indoor heat exchanger 5 as shown by the dashed arrow in the figure. That is, in the refrigerant cycle in the heating mode, the second indoor heat exchanger 5 can exert a heat radiation effect to heat the vehicle interior. Incidentally, the heating capacity during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1, adjusting the opening of the damper D3, adjusting the capacity of the pump 27, and the like.
[0055]
As described above, according to the air-conditioning apparatus of the fourth embodiment, operation in five modes is possible by switching the refrigerant cycle by the four-way valve 2 and the on-off valves 14 to 17, and electric power without a heat source such as an internal combustion engine can be obtained. There is an advantage that air conditioning can be suitably performed in a vehicle such as an automobile. Other effects are similar to those of the first embodiment.
[0056]
Note that the air conditioner shown in the fourth embodiment has the same dry / defrost mode as the fourth embodiment by switching the refrigerant cycle by the four-way valve 2 even in a circuit configuration excluding all the on-off valves 14 to 17. Operation in two modes of the dehumidification / heating mode (parallel) is possible. In the dry / defrost mode, the cooling operation or the dry operation can be selected by adjusting the amount of air flow to the second indoor heat exchanger 5 with the damper D3, and a decrease in the blow-out temperature during defrost can be prevented. Further, by controlling the on / off of the on-off valve 17, the flow rate of the refrigerant to the outdoor heat exchanger 3 and the second indoor heat exchanger 5 can be adjusted.
[0057]
In addition, if the circuit configuration is such that the on-off valves 14, 15, 17 are excluded and only the on-off valve 16 is left, switching of the refrigerant cycle by the four-way valve 2 and the on-off valve 16 switches the above two modes to the same as in the fourth embodiment. Operation in three modes including the heating mode becomes possible.
[0058]
Further, if the circuit configuration is such that the on-off valves 14, 16, and 17 are excluded and only the on-off valve 15 is left, switching of the refrigerant cycle by the four-way valve 2 and the on-off valve 15 switches the two modes to the above-described two modes as in the fourth embodiment. Operation in three modes including the dehumidification / heating mode (single) is possible.
[0059]
Furthermore, if the circuit configuration is such that the on-off valves 15, 16, and 17 are excluded and only the on-off valve 14 is left, switching of the refrigerant cycle by the four-way valve 2 and the on-off valve 14 switches the two modes to the two modes as in the fourth embodiment. Operation in three modes including the cooling / defrosting mode.
[0060]
Further, if the circuit configuration is such that the on-off valves 14, 15, and 16 are excluded and only the on-off valve 17 is left, the four-way valve 2 and the on-off valve 17 switch the refrigerant cycle to switch to the dry / defrost mode. The operation in two modes including the dehumidification / heating mode (single) similar to the embodiment can be performed.
[0061]
In addition, by appropriately combining two or three of the on-off valves 14 to 17, only the necessary mode can be selected and set from the five operation modes obtained in the air conditioner of the fourth embodiment. .
[0062]
Further, if the expansion valves 6 ', 7' which can be closed as exemplified in the second embodiment are used as the first and second expansion valves 6, 7, the functions of the on-off valves 15, 16 will be changed to the two expansion valves 6 '. , 7 'to simplify the circuit configuration.
[0063]
9 and 10 show a fifth embodiment of the present invention. The fifth embodiment uses a brine / refrigerant heat exchanger in the air conditioner of the third embodiment. In the fifth embodiment, the pipes 24 and 25 are separated from the second indoor heat exchanger 5. One end of the brine heat exchanger 26 is connected to one end of the second indoor heat exchanger 5 through a pipe 28 having an electric pump 27 interposed therebetween. And the other end of the brine heat exchanger 26 is connected to the other end of the second indoor heat exchanger 5 via the pipe 29.The check valve 10 shown in FIGS. 9 and 10 corresponds to the first control valve described in claim 22 of the claims, and the check valve 13 corresponds to the claims of the claims. This corresponds to the second control valve described in item 22. The on-off valve 15 corresponds to a control valve for a second expansion valve described in claim 25 of the present invention, and the on-off valve 16 corresponds to a control valve for the first expansion valve described in claim 24 of the present invention. It corresponds to a control valve.Incidentally, the check valve 13 may be interposed on the pipe 25 side as in the third embodiment. The other configuration is the same as that of the third embodiment, so that the same reference numerals are used and the description is omitted.
[0064]
This air conditioner is operated in four modes of a cooling / defrosting mode, a dehumidifying / heating mode (parallel), a dehumidifying / heating mode (single), and a heating mode by switching the refrigerant cycle by the four-way valve 2 and the opening / closing valves 15 and 16. Driving is possible. The refrigerant cycle and function in each mode will be described below.
[0065]
The operation in the cooling / defrosting mode is performed by switching the four-way valve 2 to the solid line position in FIG. 9 and operating the compressor 1 with the on-off valve 15 closed and the on-off valve 16 opened. As shown by solid arrows in the figure, the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 and is condensed, and is condensed through the liquid receiver 8 to the first expansion valve 6 and the first indoor heat exchanger 4. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. In other words, in the refrigerant cycle in the cooling / defrosting mode, the first indoor heat exchanger 4 can exert a heat absorbing effect to cool the vehicle interior. Further, rapid defrosting of the heat exchanger 3 can be performed by utilizing a heat radiation effect generated in the outdoor heat exchanger 3.
[0066]
The operation in the dehumidification / heating mode (parallel) is performed by switching the four-way valve 2 to the solid line position in FIG. 10 and operating the compressor 1 and the pump 27 with the on-off valves 15 and 16 opened. As shown by the solid line arrows in the figure, the refrigerant discharged from the compressor 1 flows into the brine heat exchanger 26 and exchanges heat with the brine. After passing through the liquid receiver 8, the refrigerant is branched and a part of the refrigerant is changed to the second refrigerant. It flows into the expansion valve 7 and the outdoor heat exchanger 3 and evaporates, and is sucked into the compressor 1 through the accumulator 9. The heated brine circulates between the brine heat exchanger 26 and the second indoor heat exchanger 5 as shown by the solid arrows in FIG. The remaining portion of the refrigerant flows into the first expansion valve 6 and the first indoor heat exchanger 4 and evaporates, and merges with the above-described refrigerant before the accumulator 9. In other words, in the refrigerant cycle in the dehumidification / heating mode (parallel), the outdoor heat exchanger 3 exerts a heat absorbing action, the second indoor heat exchanger 5 exerts a heat dissipation action, and the first indoor heat exchange. The heating and dehumidification of the vehicle interior can be performed simultaneously by exerting the heat absorbing effect by the heater 4. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1, adjusting the opening of the damper D3, adjusting the capacity of the pump 27, and the like.
[0067]
The operation in the dehumidification / heating mode (single) is performed by switching the four-way valve 2 to the solid line position in FIG. 10, operating the compressor 1 and the pump 27 with the on-off valve 15 closed and the on-off valve 16 opened. . As shown by the one-dot chain line arrow in FIG. 2, the refrigerant discharged from the compressor 1 flows into the brine heat exchanger 26 and exchanges heat with the brine, and the first expansion valve 6 and the first indoor heat through the liquid receiver 8. It flows into the exchanger 4, evaporates, and is sucked into the compressor 1 through the accumulator 9. The heated brine circulates between the brine heat exchanger 26 and the second indoor heat exchanger 5 as indicated by a dashed line arrow in FIG. In other words, in the refrigerant cycle in the dehumidification / heating mode (single), the second indoor heat exchanger 5 exerts a heat radiation effect, and the first indoor heat exchanger 4 exerts a heat absorption effect to heat and heat the vehicle interior. Dehumidification can be performed simultaneously. Incidentally, the heating capacity and the dehumidification amount during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1, adjusting the opening of the damper D3, adjusting the capacity of the pump 27, and the like.
[0068]
The operation in the heating mode is performed by switching the four-way valve 2 to the solid line position in FIG. 10, operating the compressor 1 and the pump 27 with the on-off valve 16 closed and the on-off valve 15 opened. As shown by a dashed arrow in the figure, the refrigerant discharged from the compressor 1 flows into the brine heat exchanger 26 and exchanges heat with the brine, and is transferred to the second expansion valve 7 and the outdoor heat exchanger 3 through the liquid receiver 8. It flows into and evaporates, and is sucked into the compressor 1 through the accumulator 9. The heated brine circulates between the brine heat exchanger 26 and the second indoor heat exchanger 5 as shown by the dashed arrow in the figure. That is, in the refrigerant cycle in the heating mode, the second indoor heat exchanger 5 can exert a heat radiation effect to heat the vehicle interior. Incidentally, the heating capacity during the same mode operation can be controlled by adjusting the discharge capacity of the compressor 1, adjusting the opening of the damper D3, adjusting the capacity of the pump 27, and the like.
[0069]
As described above, according to the air conditioner of the fifth embodiment, it is possible to operate in four modes by switching the refrigerant cycle by the four-way valve 2 and the on-off valves 15 and 16, and to operate the electric machine without a heat source such as an internal combustion engine. There is an advantage that air conditioning can be suitably performed in a vehicle such as an automobile. Other effects are the same as in the third embodiment.
[0070]
The air conditioner shown in the fifth embodiment has the same cooling / defrosting mode as the fifth embodiment by switching the refrigerant cycle by the four-way valve 2 even in a circuit configuration excluding all the on-off valves 15 and 16. Operation in two modes of the dehumidification / heating mode (parallel) is possible.
[0071]
Further, if the circuit configuration is such that the on-off valve 15 is excluded and only the on-off valve 16 is left, the heating mode similar to that of the fifth embodiment is added to the two modes by switching the refrigerant cycle by the four-way valve 2 and the on-off valve 16. Operation in the three modes is also possible.
[0072]
Furthermore, if the circuit configuration is such that the on-off valve 16 is excluded and only the on-off valve 15 is left, the refrigerant cycle is switched by the four-way valve 2 and the on-off valve 15 to switch the two modes to the above-described dehumidification / heating mode as in the fifth embodiment. Operation in three modes including (single) is possible.
[0073]
Further, if the expansion valves 6 ', 7' which can be closed as exemplified in the second embodiment are used as the first and second expansion valves 6, 7, the functions of the on-off valves 15, 16 will be changed to the two expansion valves 6 '. , 7 'to simplify the circuit configuration.
[0074]
FIG. 11 shows a sixth embodiment of the present invention. In the sixth embodiment, an auxiliary heat source for brine heating is provided in the air conditioner of the fourth embodiment. The fourth embodiment is different from the fourth embodiment in that an electric heater 30 is disposed in a brine heat exchanger 26; The difference is that a power supply circuit 31 is connected to the electric heater 30.Further, the check valve 10 shown in FIG. 11 corresponds to the first control valve described in claim 16 of the claims, and the check valve 11 corresponds to the claim 16 of the claims. The check valve 12 corresponds to the third control valve described above, and the check valve 12 corresponds to the second control valve described in claim 16 of the claims. The on-off valve 14 corresponds to a control valve for a brine / refrigerant heat exchanger described in claim 20 of the present invention, and the on-off valve 15 corresponds to the second expansion valve described in claim 19 of the present invention. The on-off valve 16 corresponds to the first control valve described in claim 18 of the claims. The on-off valve 17 corresponds to a control valve for an outdoor heat exchanger according to claim 21 of the present invention.
[0075]
In this air conditioner, the brine can be supplementarily heated by the heat of the electric heater 30 during the operation in the two dehumidifying / heating modes and the heating mode, and the heat radiation capability of the second indoor heat exchanger 5 can be improved. Further, when the brine heated by the electric heater 30 is circulated to the second indoor heat exchanger 5 when the outdoor heat exchanger 3 is defrosted in the cooling / defrosting mode, heat is radiated by the heat exchanger 5. Since the blowing temperature can be adjusted by exerting the function, no cool air is blown into the vehicle interior during the defrosting of the outdoor heat exchanger 3. Further, even when the outside air temperature is low and the heat pump does not operate normally, or when the operation of the compressor 1 is forcibly stopped, the brine heated by the electric heater 30 is circulated to the second indoor heat exchanger 5. There is an advantage that the interior of the vehicle compartment can be heated by exerting a heat radiation effect in the heat exchanger 5. Other functions and effects are the same as those of the fourth embodiment.
[0076]
FIG. 12 shows a seventh embodiment of the present invention. The seventh embodiment is different from the fourth embodiment in that an auxiliary heat source for heating brine is provided in the air conditioner of the fourth embodiment. The fourth embodiment is different from the fourth embodiment in that an air / brine heat exchanger ( The difference is that an air heat exchanger 32 is interposed and a burner 33 that burns with a liquid fuel such as kerosene is connected to the air heat exchanger 32.In addition, the check valve 10 shown in FIG. 12 corresponds to the first control valve described in claim 16 of the present invention, and the check valve 11 corresponds to claim 16 of the present invention. The check valve 12 corresponds to the third control valve described above, and the check valve 12 corresponds to the second control valve described in claim 16 of the claims. The on-off valve 14 corresponds to a control valve for a brine / refrigerant heat exchanger described in claim 20 of the present invention, and the on-off valve 15 is a first expansion valve described in claim 19 of the present invention. The on-off valve 16 corresponds to the control valve for the second expansion valve described in claim 18 of the claims, and the on-off valve 17 corresponds to the claim 21 in the claims. It corresponds to a control valve for an outdoor heat exchanger.
[0077]
In this air conditioner, the brine is supplementarily heated by the heat of the burner 33 during the operation in the two dehumidifying / heating modes and the heating mode, so that the heat radiation capability of the second indoor heat exchanger 5 can be improved. When the brine heated by the burner 33 is circulated to the second indoor heat exchanger 5 when the outdoor heat exchanger 3 is defrosted in the cooling / defrosting mode, the heat exchanger 5 has a heat radiating effect. Can be adjusted to adjust the blowing temperature, so that no cool air is blown into the vehicle interior during the defrosting of the outdoor heat exchanger 3. Furthermore, even when the outside air temperature is low and the heat pump does not operate normally, or when the operation of the compressor 1 is forcibly stopped, the brine heated by the burner 33 is circulated to the second indoor heat exchanger 5 and There is an advantage that the interior of the vehicle compartment can be heated by exerting the heat radiation effect in the heat exchanger 5. Other functions and effects are the same as those of the fourth embodiment.
[0078]
FIG. 13 shows an eighth embodiment of the present invention. In the eighth embodiment, an air conditioner of the fifth embodiment is provided with an auxiliary heat source for brine heating. The fifth embodiment is different from the fifth embodiment in that an electric heater 30 is disposed in a brine heat exchanger 26; The difference is that a power supply circuit 31 is connected to the electric heater 30.Further, the check valve 10 shown in FIG. 13 corresponds to the first control valve described in claim 22 of the claims, and the check valve 13 corresponds to claim 22 of the claims. This corresponds to the second control valve described. The on-off valve 15 corresponds to a control valve for a second expansion valve described in claim 25 of the present invention, and the on-off valve 16 corresponds to a control valve for the first expansion valve described in claim 24 of the present invention. It corresponds to a control valve.
[0079]
In this air conditioner, the brine can be supplementarily heated by the heat of the electric heater 30 during the operation in the two dehumidifying / heating modes and the heating mode, and the heat radiation capability of the second indoor heat exchanger 5 can be improved. When the brine heated by the electric heater 30 is circulated to the second indoor heat exchanger 5 when the outdoor heat exchanger 3 is defrosted in the cooling / defrosting mode, heat is radiated by the heat exchanger 5. Since the blowing temperature can be adjusted by exerting the function, no cool air is blown into the vehicle interior during the defrosting of the outdoor heat exchanger 3. Furthermore, even when the outside air temperature is low and the heat pump does not operate normally, or when the operation of the compressor 1 is forcibly stopped, the brine heated by the electric heater 30 is circulated to the second indoor heat exchanger 5. There is an advantage that the interior of the vehicle compartment can be heated by exerting a heat radiation effect in the heat exchanger 5. Other functions and effects are the same as those of the fifth embodiment.
[0080]
FIG. 14 shows a ninth embodiment of the present invention. The ninth embodiment is different from the fifth embodiment in that an auxiliary heat source for brine heating is provided in the air conditioner of the fifth embodiment. The difference is that a burner 33 that burns with a liquid fuel such as kerosene is connected to the air heat exchanger 32.Further, the check valve 10 shown in FIG. 14 corresponds to the first control valve described in claim 22 of the claims, and the check valve 13 corresponds to claim 22 of the claims. This corresponds to the second control valve described. The on-off valve 15 corresponds to a control valve for a second expansion valve described in claim 25 of the present invention, and the on-off valve 16 corresponds to a control valve for the first expansion valve described in claim 24 of the present invention. It corresponds to a control valve.
[0081]
In this air conditioner, the brine is supplementarily heated by the heat of the burner 33 during the operation in the two dehumidifying / heating modes and the heating mode, so that the heat radiation capability of the second indoor heat exchanger 5 can be improved. When the brine heated by the burner 33 is circulated to the second indoor heat exchanger 5 when the outdoor heat exchanger 3 is defrosted in the cooling / defrosting mode, the heat exchanger 5 has a heat radiating effect. Can be adjusted to adjust the blowing temperature, so that no cool air is blown into the vehicle interior during the defrosting of the outdoor heat exchanger 3. Furthermore, even when the outside air temperature is low and the heat pump does not operate normally, or when the operation of the compressor 1 is forcibly stopped, the brine heated by the burner 33 is circulated to the second indoor heat exchanger 5 and There is an advantage that the interior of the vehicle compartment can be heated by exerting the heat radiation effect in the heat exchanger 5. Other functions and effects are the same as those of the fifth embodiment.
[0082]
In the sixth to ninth embodiments, the example in which the auxiliary heat source is incorporated in the air conditioner of the fourth or sixth embodiment having the brine heat exchanger 26 is shown. It can also be used for the air conditioners of (1) to (3). That is, if the refrigerant flowing into the second indoor heat exchanger 5 during heating is heated by the same auxiliary heat source as described above, the heat radiation capability of the second indoor heat exchanger can be improved, and If the refrigerant flowing out of the outdoor heat exchanger 3 is heated by the auxiliary heat source during heating, the shortage of heat absorption in the outdoor heat exchanger 3 can be compensated.
[0083]
In the above-described first to ninth embodiments, the on-off valves are all exemplified as the on-off valves 14 to 17, but these on-off valves 14 to 17 may be of a type capable of controlling the flow rate. Can control the heat radiation and heat absorption of the outdoor heat exchanger 3 and the first and second indoor heat exchangers 4 and 5 by controlling the flow rate of each valve. Further, the check valves 11 to 13 for controlling the flow direction of the refrigerant may be replaced with an on / off type on-off valve or a flow control valve.
[0084]
【The invention's effect】
As described above in detail, according to the vehicle air conditioner of the present invention, all or part of the refrigerant that has passed through the second indoor heat exchanger is transferred to the first indoor heat exchanger through the first expansion unit. By guiding, it is possible to simultaneously perform heating and dehumidification of the vehicle cabin by exerting a heat radiation effect in the second indoor heat exchanger and a heat absorbing effect in the first indoor heat exchanger, and perform rainfall and snowfall. When the heating operation is performed under humid conditions such as when the air conditioner is switched from the cooling operation to the heating operation, the dehumidification operation is performed without fogging the window glass in the vehicle compartment and without reducing the blowing temperature. And comfortable air conditioning can be realized.
[Brief description of the drawings]
FIG. 1 is a refrigerant circuit diagram of a vehicle air conditioner showing a first embodiment of the present invention.
FIG. 2 is a circuit diagram of the same refrigerant.
FIG. 3 is a refrigerant circuit diagram of a vehicle air conditioner showing a second embodiment of the present invention.
FIG. 4 is a refrigerant circuit diagram of the same.
FIG. 5 is a refrigerant circuit diagram of a vehicle air conditioner showing a third embodiment of the present invention.
FIG. 6 is a refrigerant circuit diagram of the same.
FIG. 7 is a refrigerant circuit diagram of a vehicle air conditioner showing a fourth embodiment of the present invention.
FIG. 8 is the same refrigerant circuit diagram.
FIG. 9 is a refrigerant circuit diagram of a vehicle air conditioner showing a fifth embodiment of the present invention.
FIG. 10 is a refrigerant circuit diagram of the same.
FIG. 11 is a refrigerant circuit diagram of a vehicle air conditioner showing a sixth embodiment of the present invention.
FIG. 12 is a refrigerant circuit diagram of a vehicle air conditioner showing a seventh embodiment of the present invention.
FIG. 13 is a refrigerant circuit diagram of a vehicle air conditioner showing an eighth embodiment of the present invention.
FIG. 14 is a refrigerant circuit diagram of a vehicle air conditioner showing a ninth embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... 4-way valve, 3 ... Outdoor heat exchanger, 4 ... First indoor heat exchanger, 5 ... Second indoor heat exchanger, 6, 6 '... First expansion valve, 7, 7 ': second expansion valve, 8: liquid receiver, 9: accumulator, 10-13: check valve, 14-17: open / close valve, 18-25, 25a, 25b, 28, 29 ... conduit, 26 ... a brine / refrigerant heat exchanger, 27 ... a pump, 30 ... an electric heater, 33 ... a burner.

Claims (28)

圧縮機、室外熱交換器、第１の膨張手段、第２の膨張手段及び車室内空調用のダクト内に配置された室内熱交換器を備え、四方弁等による冷媒サイクルの切り換えで車室内の冷房と暖房を行うヒートポンプ式の車両用空気調和装置において、
室内熱交換器は、通過する冷媒がダクト内空気と熱交換してダクト内空気から吸熱する吸熱専用の第１の室内熱交換器と、通過する冷媒がダクト内空気と熱交換しダクト内に放熱する放熱専用の第２の室内熱交換器とからなると共に、
第２の室内熱交換器を通過した冷媒を第２の膨張手段を通じて室外熱交換器に導く一方の管路と、
第２の室内熱交換器を通過した冷媒を第１の膨張手段を通じて第１の室内熱交換器に導く他方の管路とを備え、
圧縮機から吐出された冷媒を室外熱交換器に導き更に前記他方の管路に導く冷房・除霜モードと、
圧縮機から吐出された冷媒を室外熱交換器及び第２の室内熱交換器に導き前記他方の管路に導くドライ・除霜モードと、
圧縮機から吐出された冷媒を第２の室内熱交換器に導き更に前記一方の管路に導く暖房モードと、
圧縮機から吐出された冷媒を第２の室内熱交換器に導き、更に前記一方の管路及び前記他方の管路の両者又は他方の管路に導く除湿・暖房モードとを有する、
ことを特徴とする車両用空気調和装置。A compressor, an outdoor heat exchanger, a first expansion unit, a second expansion unit, and an indoor heat exchanger arranged in a duct for air conditioning inside the vehicle compartment, and a refrigerant cycle switching by a four-way valve or the like switches the refrigerant cycle to the inside of the vehicle compartment. In heat pump type air conditioners for vehicles that perform cooling and heating,
The indoor heat exchanger is composed of a first indoor heat exchanger dedicated to absorbing heat, in which the passing refrigerant exchanges heat with the air in the duct and absorbs heat from the air in the duct, and the passing refrigerant exchanges heat with the air in the duct to form a heat in the duct. It consists of a second indoor heat exchanger dedicated to radiating heat,
One conduit for guiding the refrigerant having passed through the second indoor heat exchanger to the outdoor heat exchanger through the second expansion means;
A second pipe for guiding the refrigerant that has passed through the second indoor heat exchanger to the first indoor heat exchanger through the first expansion means,
A cooling / defrosting mode that guides the refrigerant discharged from the compressor to the outdoor heat exchanger and further guides the refrigerant to the other pipeline,
A dry / defrost mode in which the refrigerant discharged from the compressor is guided to the outdoor heat exchanger and the second indoor heat exchanger, and is guided to the other pipeline.
A heating mode in which the refrigerant discharged from the compressor is guided to the second indoor heat exchanger and further to the one of the pipelines;
A dehumidification / heating mode in which the refrigerant discharged from the compressor is guided to the second indoor heat exchanger, and further, both the one pipeline and the other pipeline or the other pipeline are guided.
An air conditioner for a vehicle, comprising: 第２の室内熱交換器を冷媒回路に介装されたブライン・冷媒熱交換器に接続し、ブラインを第２の室内熱交換器に循環させるようにした、
ことを特徴とする請求項１記載の車両用空気調和装置。The second indoor heat exchanger was connected to a brine / refrigerant heat exchanger interposed in the refrigerant circuit, and the brine was circulated to the second indoor heat exchanger.
The vehicle air conditioner according to claim 1, wherein: 圧縮機と、
圧縮機の吐出口にその第１ポートが接続された四方弁と、
四方弁の第２ポートにその一端が接続された室外熱交換器と、
室外熱交換器の他端に第１の制御弁を介してその入口が接続された第１の膨張弁と、
第１の膨張弁の出口にその入口が接続され、出口が圧縮機の吸入口に接続された第１の室内熱交換器と、
四方弁の第４ポートに第２の制御弁を介してその入口が接続され、出口が第１の制御弁と第１の膨張弁との間に接続された第２の室内熱交換器と、
第１の制御弁と第１の膨張弁との間にその入口が接続され、出口が室外熱交換器の他端に接続された第２の膨張弁とを備え、
四方弁の第２ポートを第３の制御弁を介して第２の室内熱交換器の入口に接続し、
四方弁の第３ポートを圧縮機の吸入口に接続した、
ことを特徴とする車両用空気調和装置。A compressor,
A four-way valve having a first port connected to a discharge port of the compressor;
An outdoor heat exchanger having one end connected to the second port of the four-way valve;
A first expansion valve having an inlet connected to the other end of the outdoor heat exchanger via a first control valve;
A first indoor heat exchanger having an inlet connected to an outlet of the first expansion valve, and an outlet connected to an inlet of the compressor;
A second indoor heat exchanger having an inlet connected to a fourth port of the four-way valve via a second control valve, and an outlet connected between the first control valve and the first expansion valve;
A second expansion valve having an inlet connected between the first control valve and the first expansion valve, and an outlet connected to the other end of the outdoor heat exchanger;
Connecting the second port of the four-way valve to the inlet of the second indoor heat exchanger via a third control valve;
The third port of the four-way valve was connected to the compressor inlet,
An air conditioner for a vehicle, comprising: 第１，第２の膨張弁として閉動作可能なものを使用した、
ことを特徴とする請求項３項記載の車両用空気調和装置。The first and second expansion valves used can be closed,
The vehicle air conditioner according to claim 3, wherein: 第１の膨張弁の入口側に第１膨張弁用制御弁を介装した、
ことを特徴とする請求項３項記載の車両用空気調和装置。A control valve for the first expansion valve interposed on the inlet side of the first expansion valve ,
The vehicle air conditioner according to claim 3, wherein: 第２の膨張弁の入口側に第２膨張弁用制御弁を介装した、
ことを特徴とする請求項３または５記載の車両用空気調和装置。A control valve for the second expansion valve is interposed on the inlet side of the second expansion valve ,
The vehicle air conditioner according to claim 3 or 5, wherein: 第２の室内熱交換器の出入口の少なくとも一方側に第２室内熱交換器用制御弁を介装した、
ことを特徴とする請求項３乃至６何れか１項記載の車両用空気調和装置。A control valve for a second indoor heat exchanger was interposed on at least one side of the entrance and exit of the second indoor heat exchanger ,
The vehicle air conditioner according to any one of claims 3 to 6, wherein: 四方弁の第２ポートと室外熱交換器の一端との間に室外熱交換器用制御弁を介装した、
ことを特徴とする請求項３乃至７何れか１項記載の車両用空気調和装置。A control valve for an outdoor heat exchanger was interposed between the second port of the four-way valve and one end of the outdoor heat exchanger ,
The vehicle air conditioner according to any one of claims 3 to 7, wherein: 圧縮機と、
圧縮機の吐出口にその第１ポートが接続された四方弁と、
四方弁の第２ポートにその一端が接続された室外熱交換器と、
室外熱交換器の他端に第１の制御弁を介してその入口が接続された第１の膨張弁と、
第１の膨張弁の出口にその入口が接続され、出口が圧縮機の吸入口に接続された第１の室内熱交換器と、
四方弁の第４ポートにその入口が接続され、出口が第１の制御弁と第１の膨張弁との間に接続された第２の室内熱交換器と、
第１の制御弁と第１の膨張弁との間にその入口が接続され、出口が室外熱交換器の他端に接続された第２の膨張弁とを備え、
四方弁の第３ポートを圧縮機の吸入口に接続し、
第２の室内熱交換器の出入口側の一方に第２の制御弁を介装し、
第２の膨張弁の入口側に第２膨張弁用制御弁を介装した、
ことを特徴とする車両用空気調和装置。A compressor,
A four-way valve having a first port connected to a discharge port of the compressor;
An outdoor heat exchanger having one end connected to the second port of the four-way valve;
A first expansion valve having an inlet connected to the other end of the outdoor heat exchanger via a first control valve;
A first indoor heat exchanger having an inlet connected to an outlet of the first expansion valve, and an outlet connected to an inlet of the compressor;
A second indoor heat exchanger having an inlet connected to the fourth port of the four-way valve and an outlet connected between the first control valve and the first expansion valve;
A second expansion valve having an inlet connected between the first control valve and the first expansion valve, and an outlet connected to the other end of the outdoor heat exchanger;
Connect the third port of the four-way valve to the suction port of the compressor,
A second control valve is interposed on one of the entrance and exit sides of the second indoor heat exchanger,
A control valve for the second expansion valve is interposed on the inlet side of the second expansion valve ,
An air conditioner for a vehicle, comprising: 第１，第２の膨張弁として閉動作可能なものを使用した、
ことを特徴とする請求項９記載の車両用空気調和装置。The first and second expansion valves used can be closed,
The vehicle air conditioner according to claim 9, wherein: 第１の膨張弁の入口側に第１膨張弁用制御弁を介装した、
ことを特徴とする請求項９記載の車両用空気調和装置。A control valve for the first expansion valve interposed on the inlet side of the first expansion valve ,
The vehicle air conditioner according to claim 9, wherein: 第２の室内熱交換器に流入する冷媒を加熱するための補助熱源を設けた、
ことを特徴とする請求項１または３乃至１１何れか１項記載の車両用空気調和装置。An auxiliary heat source for heating the refrigerant flowing into the second indoor heat exchanger was provided.
The air conditioner for a vehicle according to any one of claims 1 to 3, wherein: 室外熱交換器から流出する冷媒を加熱するための補助熱源を設けた、
ことを特徴とする請求項１または３乃至１１何れか１項記載の車両用空気調和装置。An auxiliary heat source for heating the refrigerant flowing out of the outdoor heat exchanger was provided,
The air conditioner for a vehicle according to any one of claims 1 to 3, wherein: 補助熱源が電熱ヒータである、
ことを特徴とする請求項１２または１３記載の車両用空気調和装置。The auxiliary heat source is an electric heater,
The air conditioner for a vehicle according to claim 12 or 13, wherein: 補助熱源がバーナである、
ことを特徴とする請求項１２または１３記載の車両用空気調和装置。The auxiliary heat source is a burner,
The air conditioner for a vehicle according to claim 12 or 13, wherein: 圧縮機と、
圧縮機の吐出口にその第１ポートが接続された四方弁と、
四方弁の第２ポートにその一端が接続された室外熱交換器と、
室外熱交換器の他端に第１の制御弁を介してその入口が接続された第１の膨張弁と、
第１の膨張弁の出口にその入口が接続され、出口が圧縮機の吸入口に接続された第１の室内熱交換器と、
四方弁の第４ポートに第２の制御弁を介してその冷媒路入口が接続され、冷媒路出口が第１の制御弁と第１の膨張弁との間に接続されたブライン・冷媒熱交換器と、
ブライン・冷媒熱交換器のブライン路にポンプを介して接続された第２の室内熱交換器と、
第１の制御弁と第１の膨張弁との間にその入口が接続され、出口が室外熱交換器の他端に接続された第２の膨張弁とを備え、
四方弁の第２ポートを第３の制御弁を介してブライン・冷媒熱交換器の冷媒路入口に接続し、
四方弁の第３ポートを圧縮機の吸入口に接続した、
ことを特徴とする車両用空気調和装置。A compressor,
A four-way valve having a first port connected to a discharge port of the compressor;
An outdoor heat exchanger having one end connected to the second port of the four-way valve;
A first expansion valve having an inlet connected to the other end of the outdoor heat exchanger via a first control valve;
A first indoor heat exchanger having an inlet connected to an outlet of the first expansion valve, and an outlet connected to an inlet of the compressor;
Brine / refrigerant heat exchange in which the refrigerant passage inlet is connected to the fourth port of the four-way valve via a second control valve, and the refrigerant passage outlet is connected between the first control valve and the first expansion valve. Vessels,
A second indoor heat exchanger connected to the brine path of the brine / refrigerant heat exchanger via a pump;
A second expansion valve having an inlet connected between the first control valve and the first expansion valve, and an outlet connected to the other end of the outdoor heat exchanger;
Connecting the second port of the four-way valve to the refrigerant passage inlet of the brine-refrigerant heat exchanger via a third control valve;
The third port of the four-way valve was connected to the compressor inlet,
An air conditioner for a vehicle, comprising: 第１，第２の膨張弁として閉動作可能なものを使用した、
ことを特徴とする請求項１６記載の車両用空気調和装置。The first and second expansion valves used can be closed,
The vehicle air conditioner according to claim 16, wherein: 第１の膨張弁の入口側に第１膨張弁用制御弁を介装した、
ことを特徴とする請求項１６記載の車両用空気調和装置。A control valve for the first expansion valve interposed on the inlet side of the first expansion valve ,
The vehicle air conditioner according to claim 16, wherein: 第２の膨張弁の入口側に第２膨張弁用制御弁を介装した、
ことを特徴とする請求項１６または１８記載の車両用空気調和装置。A control valve for the second expansion valve is interposed on the inlet side of the second expansion valve ,
The air conditioner for a vehicle according to claim 16 or 18, wherein: ブライン・冷媒熱交換器の冷媒路出入口の少なくとも一方側にブライ ン・冷媒熱交換器用制御弁を介装した、
ことを特徴とする請求項１６乃至１９何れか１項記載の車両用空気調和装置。It was interposed Bligh down-refrigerant heat exchanger control valves on at least one side of the refrigerant passage entrance of the brine-refrigerant heat exchanger,
The vehicle air conditioner according to any one of claims 16 to 19, wherein: 四方弁の第２ポートと室外熱交換器の一端との間に室外熱交換器用制御弁を介装した、
ことを特徴とする請求項１６乃至２０何れか１項記載の車両用空気調和装置。A control valve for an outdoor heat exchanger was interposed between the second port of the four-way valve and one end of the outdoor heat exchanger ,
The vehicle air conditioner according to any one of claims 16 to 20, wherein: 圧縮機と、
圧縮機の吐出口にその第１ポートが接続された四方弁と、
四方弁の第２ポートにその一端が接続された室外熱交換器と、
室外熱交換器の他端に第１の制御弁を介してその入口が接続された第１の膨張弁と、
第１の膨張弁の出口にその入口が接続され、出口が圧縮機の吸入口に接続された第１の室内熱交換器と、
四方弁の第４ポートにその冷媒路入口が接続され、冷媒路出口が第１の制御弁と第１の膨張弁との間に接続されたブライン・冷媒熱交換器と、
ブライン・冷媒熱交換器のブライン路にポンプを介して接続された第２の室内熱交換器と、
第１の制御弁と第１の膨張弁との間にその入口が接続され、出口が室外熱交換器の他端に接続された第２の膨張弁とを備え、
四方弁の第３ポートを圧縮機の吸入口に接続し、
ブライン・冷媒熱交換器の冷媒路出入口側一方に第２の制御弁を介装した、
ことを特徴とする車両用空気調和装置。A compressor,
A four-way valve having a first port connected to a discharge port of the compressor;
An outdoor heat exchanger having one end connected to the second port of the four-way valve;
A first expansion valve having an inlet connected to the other end of the outdoor heat exchanger via a first control valve;
A first indoor heat exchanger having an inlet connected to an outlet of the first expansion valve, and an outlet connected to an inlet of the compressor;
A brine / refrigerant heat exchanger whose refrigerant path inlet is connected to the fourth port of the four-way valve and whose refrigerant path outlet is connected between the first control valve and the first expansion valve;
A second indoor heat exchanger connected to the brine path of the brine / refrigerant heat exchanger via a pump;
A second expansion valve having an inlet connected between the first control valve and the first expansion valve, and an outlet connected to the other end of the outdoor heat exchanger;
Connect the third port of the four-way valve to the suction port of the compressor,
A second control valve was interposed on one of the refrigerant path entrance and exit sides of the brine / refrigerant heat exchanger,
An air conditioner for a vehicle, comprising: 第１，第２の膨張弁として閉動作可能なものを使用した、
ことを特徴とする請求項２２記載の車両用空気調和装置。The first and second expansion valves used can be closed,
The air conditioner for a vehicle according to claim 22, wherein: 第１の膨張弁の入口側に第１膨張弁用制御弁を介装した、
ことを特徴とする請求項２２記載の車両用空気調和装置。A control valve for the first expansion valve interposed on the inlet side of the first expansion valve ,
The air conditioner for a vehicle according to claim 22, wherein: 第２の膨張弁の入口側に第２膨張弁用制御弁を介装した、
ことを特徴とする請求項２２または２４記載の車両用空気調和装置。A control valve for the second expansion valve is interposed on the inlet side of the second expansion valve ,
The air conditioner for a vehicle according to claim 22 or 24, wherein: ブライン加熱用の補助熱源を設けた、
ことを特徴とする請求項２または１７乃至２５何れか１項記載の車両用空気調和装置。An auxiliary heat source for brine heating was provided,
The air conditioner for a vehicle according to any one of claims 2 or 17 to 25, wherein: 補助熱源が電熱ヒータである、
ことを特徴とする請求項２６記載の車両用空気調和装置。The auxiliary heat source is an electric heater,
The vehicle air conditioner according to claim 26, wherein: 補助熱源がバーナである、
ことを特徴とする請求項２６記載の車両用空気調和装置。The auxiliary heat source is a burner,
The vehicle air conditioner according to claim 26, wherein:
JP25722693A 1993-10-14 1993-10-14 Vehicle air conditioner Expired - Fee Related JP3563094B2 (en)

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