JP4337289B2

JP4337289B2 - Adsorption heat pump

Info

Publication number: JP4337289B2
Application number: JP2001250017A
Authority: JP
Inventors: 伸本田; 靖林
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2001-01-29
Filing date: 2001-08-21
Publication date: 2009-09-30
Anticipated expiration: 2021-08-21
Also published as: JP2002295920A

Description

【０００１】
【発明の属する技術分野】
本発明は、雰囲気中の冷媒湿度に応じて冷媒を吸着・脱離する吸着剤を有し、低温側の熱を高温側に移動させる吸着式ヒートポンプに関するものであり、空調装置に適用して有効である。
【０００２】
【従来の技術】
吸着式ヒートポンプを用いた空調装置として、例えば特開平５−１２６４３２号公報に記載の発明では、略真空に保たれた密閉容器（吸着器）内の気相冷媒を吸着剤にて吸着することにより液相冷媒を蒸発させて、その蒸発潜熱により室内熱交換器に供給する熱媒体を冷却する。なお、以下、熱媒体と冷媒とを熱交換させる熱交換器を容器内交換器（蒸発・凝縮熱交換器）と呼ぶ。
【０００３】
ところで、吸着剤の吸着能力（吸着量）が飽和状態になると、吸着作動が停止する。そこで、吸着剤が飽和すると、吸着剤を加熱することにより吸着していた冷媒を脱離させた（再生した）後、再び、冷媒を吸着させる。なお、吸着剤から脱離した気相冷媒は、容器内熱交換器にて外気と熱交換されて冷却（凝縮）される。
【０００４】
以下、吸着剤が吸着作動しているときを吸着行程と呼び、加熱されて吸着していた冷媒を脱離しているときを脱離行程と呼ぶ。
【０００５】
【発明が解決しようとする課題】
ところで、吸着行程においては、冷媒が蒸発して密閉容器（特に、容器内熱交換器）の温度が低下するのに対して、脱離行程においては、冷媒が凝縮して密閉容器（特に、容器内熱交換器及び液相冷媒）の温度が上昇するため、密閉容器（特に、容器内熱交換器及び液相冷媒）の温度が吸着行程時と脱離行程時とで大きく相違する。
【０００６】
このため、例えば吸着行程時から脱離行程時に移行した直後においては、吸着式ヒートポンプに投入される熱エネルギの一部は、冷媒の脱離（吸着剤の加熱）のために消費されず、密閉容器（特に、容器内熱交換器及び液相冷媒の加熱）に消費されるので、吸着式ヒートポンプの成績係数（移動した熱量／投入した熱量）が低下してしまう。
【０００７】
具体的には、吸着行程時において、容器内熱交換器及びその周囲の液相冷媒温度が１０℃とし、外気温度が４０℃とすると、吸着行程時から脱離行程時に移行した直後においては、吸着式ヒートポンプに投入される熱エネルギは、１０℃の容器内熱交換器及びその周囲の液相冷媒を４０℃まで上昇させるために消費されてしまう。
【０００８】
本発明は、上記点に鑑み、吸着式ヒートポンプの成績係数（ＣＯＰ）の向上を図ることを目的とする。
【０００９】
【課題を解決するための手段】
本発明は、上記目的を達成するために、請求項１に記載の発明では、雰囲気中の冷媒湿度に応じて冷媒を吸着・脱離する第１吸着剤（４）を有し、低温側の熱を高温側に移動させる吸着式ヒートポンプであって、低温側に配置された第１熱交換器（１、２）と、高温側に配置された第２熱交換器（１、２）と、第１吸着剤（４）と熱媒体とを熱交換させる第３熱交換器（３）と、第１吸着剤（４）、冷媒及び第３熱交換器（３）が封入された密閉容器（７）と、密閉容器（７）内の冷媒湿度を調節する湿度調節手段（１２）とを備え、第３熱交換器（３）は、第１熱交換器（１、２）→第３熱交換器（３）→第２熱交換器（１、２）の順あるいは第２熱交換器（１、２）→第３熱交換器（３）→第１熱交換器（１、２）の順で熱媒体が流れるように、第１熱交換器（１、２）と第２熱交換器（１、２）との間に直列に接続されており、湿度調節手段（１２）によって密閉容器（７）内の冷媒湿度を下げて第１吸着剤（４）が吸着していた冷媒を脱離させるとともに、第２熱交換器（１、２）にて熱交換した熱媒体を第３熱交換器（３）に供給し、かつ、第３熱交換器（３）にて第１吸着剤（４）と熱交換した熱媒体を第１熱交換器（１、２）に供給する吸熱行程と、湿度調節手段（１２）によって密閉容器（７）内の冷媒湿度を上げて第１吸着剤（４）に冷媒を吸着させるとともに、吸熱工程時に対して逆向きに熱媒体が移動するように、第１熱交換器（１、２）にて熱交換した熱媒体を第３熱交換器（３）に供給し、かつ、第３熱交換器（３）にて第１吸着剤（４）と熱交換した熱媒体を第２熱交換器（１、２）に供給する放熱行程と、を交互に実行するヒートポンプを特徴としている。
【００１０】
ところで、従来の技術に係る吸着式ヒートポンプでは、図５（ｂ）に示すように、容器内熱交換器（蒸発・凝縮熱交換器）Ｈｅは、吸着行程においては低温側を冷却して吸熱する熱交換器として機能し、脱離行程においては高温側を放熱する熱交換器として機能する。
【００１１】
このため、従来の技術に係る吸着式ヒートポンプにおいて、例えば高温側の温度を４０℃とし、吸着剤の吸着・脱離作用により作り出すことができる温度差を３０℃とすると、従来の技術に係る吸着式ヒートポンプにおいては、熱媒体が連続的に循環しているので、脱離行程時における容器内熱交換器の平均温度は４０℃となり、吸着行程時における容器内熱交換器の平均温度は１０℃となる。
【００１２】
したがって、吸着行程時における容器内熱交換器の平均温度と脱離行程時における容器内熱交換器の平均温度との差は、吸着剤の吸着・脱離作用により作り出すことができる温度差と等しく、３０℃となる。
【００１３】
これに対して、本発明では、熱媒体を連続的に循環させることなく、例えば吸熱行程においては、吸着剤（４）と熱交換した熱媒体を第１熱交換器（１、２）に供給し、かつ、第２熱交換器（１、２）にて熱交換した熱媒体を第３熱交換器（３）に供給し、放熱行程においては、吸熱行程時とは逆に、第１熱交換器（１、２）にて熱交換した熱媒体を第３熱交換器（３）に供給し、かつ、吸着剤（４）と熱交換した熱媒体を第２熱交換器（１、２）に供給するので、第３熱交換器（３）は、熱媒体入口側と出口側とで温度差が発生するような温度勾配を有する。
【００１４】
このため、従来の技術に係る吸着式ヒートポンプと同様に、例えば高温側の温度を４０℃とし、吸着剤（４）の吸着・脱離作用により作り出すことができる温度差を３０℃とすると、第３熱交換器（３）により冷却された熱媒体の温度が１０℃となるので、吸熱行程における第３熱交換器（３）の平均温度は、図５（ａ）に示すように２５℃となる。
【００１５】
一方、放熱行程においては、低温側から吸熱して温度が上昇した熱媒体が第３熱交換器（３）に供給されるため、放熱行程における第３熱交換器（３）の平均温度は、吸熱行程における第３熱交換器（３）の平均温度に対して、低温側から吸熱したことによる温度上昇分（例えば、１０°）だけ上昇する。
【００１６】
このとき、低温側から吸熱したことによる温度上昇分が、吸着剤（４）の吸着・脱離作用により作り出すことができる温度差を超えることはあり得ないので、放熱行程における第３熱交換器（３）の平均温度と吸熱行程における第３熱交換器（３）の平均温度との差は、吸着剤（４）の吸着・脱離作用により作り出すことができる温度差より小さくなる。
【００１７】
したがって、本発明によれば、放熱行程における第３熱交換器（３）の平均温度と吸熱行程における第３熱交換器（３）の平均温度との差を、従来の技術に係る吸着式ヒートポンプに比べて小さくすることができるので、第３熱交換器（３）自体の温度上昇に消費される熱エネルギ量を小さくすることができる。延いては、吸着式ヒートポンプの成績係数（ＣＯＰ）の向上を図ることができる。
【００１８】
なお、湿度調節手段（１２）は、請求項２に記載の発明のごとく、冷却することにより雰囲気中の気相冷媒を吸着し、加熱されることによりその吸着した水分を脱離する吸着剤（４）を有して構成されており、吸熱工程では、第２吸着剤（４）に密閉容器（７）内の冷媒を吸着させることによって、密閉容器（７）内の冷媒湿度を下げ、放熱工程では、第２吸着剤（４）に吸着していた冷媒を密閉容器（７）中に脱離させることによって、密閉容器（７）内の冷媒湿度を上げるようになっていてもよい。
【００１９】
また、湿度調節手段（１２）は、請求項３に記載の発明のごとく、気相冷媒を吸入圧縮する蒸気圧縮機（１３）を有して構成してもよい。
【００２０】
また、請求項４に記載の発明のごとく、第３熱交換器（３）を、熱媒体が流通する複数本のチューブ（３ａ）、チューブ（３ａ）の長手方向両端側に配設されて各チューブ（３ａ）と連通するタンク（３ｂ）、及び各チューブ（３ａ）間に配設された波状のフィン（３ｃ）を有して構成し、第１吸着剤（４）をチューブ（３ａ）及びフィン（３ｃ）と接触するように充填接着してもよい。
【００２１】
因みに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。
【００２２】
【発明の実施の形態】
（第１実施形態）
本実施形態は、本発明に係る吸着式ヒートポンプを空調装置に適用したものであって、図１は空調装置（吸着式ヒートポンプ）の模式図である。
【００２３】
図１中、１は室内に吹き出す空気と熱媒体（本実施家形態では、水にエチレングリコール系の不凍液を混合した流体）とを熱交換する室内熱交換器（以下、室内器と略す。）であり、２は室外空気と熱媒体とを熱交換する室外熱交換器（以下、室外器と略す。）である。なお、１ａは室内器１に空気を送風する室内送風機であり、２ａは室外器２に空気を送風する室外送風機である。
【００２４】
３は熱媒体と吸着剤とを熱交換する第１吸着コア（第３熱交換器）であり、この第１吸着コア３は、図２に示すように、熱媒体が流通する複数本のチューブ３ａ、チューブ３ａの長手方向両端側に配設されて各チューブ３ａと連通するタンク３ｂ、及び各チューブ３ａ間に配設された波状のフィン３ｃからなるもので、チューブ３ａ間の隙間には、チューブ３ａ及びフィン３ｃと接触するように粒状の吸着剤４が密に充填された状態で第１吸着コア３に接着固定されている。
【００２５】
なお、吸着剤４は、図３に示すように、雰囲気中（厳密には、吸着剤４の表面近傍における）の冷媒湿度（関係湿度）に応じて冷媒を吸着・脱離するもので、冷媒湿度（関係湿度）が大きくなるほど冷媒（水分）吸着量が大きくなり、冷媒湿度（関係湿度）が小さくなるほど冷媒（水分）吸着量が小さくなる。因みに、本実施形態では、吸着剤４としてゼオライト又はシリカゲル等の固体吸着剤を使用し、冷媒として水を使用している。
【００２６】
また、図１中、５は熱媒体を室内器１、室外器２及び吸着コア３間で熱媒体を循環（行き来）させる熱媒体ディスプレーサ（ポンプ手段）である。そして、この熱媒体ディスプレーサ５は、内部のピストン５ａが紙面左側から右側に移動したときには、吸着コア３内の熱媒体を置き換えるように、室外器２内の熱媒体を吸着コア３に供給し、吸着コア３内の熱媒体を室内器１に供給する。
【００２７】
一方、ピストン５ａが紙面右側から左側に移動したときには、ピストン５ａが左側から右側に移動したときと逆向きに熱媒体を移動させるように、室内器１内の熱媒体を吸着コア３に供給し、吸着コア３内の熱媒体を室外器２に供給する。
【００２８】
また、６は第１吸着コア３と同様な構造を有する第２吸着コアであり、この第２吸着コア６にも第１吸着コア３と同様に吸着剤４が接着固定されている。そして、両吸着コア３、６（吸着剤４を含む。）及び冷媒は、内部が略真空に保持された密閉容器（吸着器）７内に収納されている。
【００２９】
なお、以下、第１吸着コア３に接着固定された吸着剤４を第１吸着剤と呼び、第２吸着コア６に接着された吸着剤４を第２吸着剤と呼ぶ。このとき、第１吸着剤の総吸着能力（総水分吸着量）と第２吸着剤の総吸着能力（総水分吸着量）とを略同等とすることが望ましい。
【００３０】
また、８は第２吸着コア６に熱媒体を循環させるポンプであり、９は第２吸着コア６に循環させる熱媒体を外気にて冷却するためのラジエータであり、１０は第２吸着コア６に循環させる熱媒体を加熱する電気ヒータ（加熱手段）であり、１１は第２吸着コア６にラジエータ９にて冷却された熱媒体を循環させる場合と、電気ヒータ１０にて加熱された熱媒体を循環させる場合とを切り替える切り替えバルブである。
【００３１】
なお、本実施形態では、第２吸着コア６に循環させる熱媒体を加熱する加熱手段として電気ヒータを採用しているが、本実施形態は、これに限定されるものではなく、エンジンやインバータ回路の廃熱等のその熱源は問わない。
【００３２】
次に、本実施形態に係る吸着式ヒートポンプ（空調装置）の作動を述べる。
【００３３】
１．冷房運転
冷房運転時には、以下の吸熱行程を最初に実行した後、放熱行程と吸熱行程とを所定時間ごとに交互に繰り返し実行する。
【００３４】
１．１冷房運転の吸熱行程
第２吸着コア６にラジエータ９にて冷却された熱媒体を循環させて第２吸着剤を冷却することにより、第２吸着剤の関係湿度を上昇させて第２吸着剤に密閉容器７内の気相冷媒を吸着させる。これにより、密閉容器７内の冷媒湿度（第１吸着剤の関係湿度）が低下するので、第１吸着剤は密閉容器７中に吸着していた冷媒を脱離する。このとき、第１吸着剤から脱離する冷媒は、吸着行程時とは逆に、蒸発潜熱に相当する熱量を第１吸着剤から奪うので、第１吸着剤の温度が低下し、第１吸着コア３内の熱媒体が冷却される。以下、この第１吸着剤の作動を脱離吸熱作動と呼ぶ。
【００３５】
そして、脱離吸熱作動と同時（併行）に、熱媒体ディスプレーサ５を作動させて、室外器２内の熱媒体を第１吸着コア３に供給し、第１吸着コア３内の熱媒体を室内器１に供給する（図１の実線で示す矢印参照）。これにより、室内器１には第１吸着コア３にて冷却された少なくとも外気温度より低い熱媒体が供給されるので、室内に吹き出す空気が冷却される。
【００３６】
１．２冷房運転の放熱行程
第２吸着コア６に電気ヒータ１０にて加熱された熱媒体を循環させて第２吸着剤を加熱することにより、第２吸着剤の関係湿度を低下させて第２吸着剤に吸着していた冷媒を密閉容器７中に脱離させる。これにより、密閉容器７内の冷媒湿度（第１吸着剤の関係湿度）が高くなるので、第１吸着剤は密閉容器７内の（第２吸着剤が脱離した）気相冷媒を吸着する。このとき、第１吸着剤は、冷媒を吸着する際に凝縮熱に相当する熱量を発し、この熱により第１吸着コア３内の熱媒体を加熱する。以下、この第１吸着コア３（第１吸着剤）の作動を吸着発熱作動と呼ぶ。
【００３７】
そして、吸着発熱作動と同時（併行）に、熱媒体ディスプレーサ５を作動させて、吸熱行程時と逆向きに熱媒体が移動するように、室内器１内の熱媒体を第１吸着コア３に供給し、第１吸着コア３内の熱媒体を室外器２に供給する（図１の破線で示す矢印参照）。これにより、室外器２には第１吸着コア３にて加熱（昇温）された熱媒体が供給されるので、第１吸着コア３にて熱媒体に与えられた熱が外気中に放熱される。
【００３８】
ここで、放熱行程において外気中に放熱される熱（気相冷媒を吸着する際に発生する熱）は、元々、吸熱行程において第１吸着剤から脱離する冷媒が、室内器１に供給する熱媒体から蒸発潜熱として吸熱した熱である。
【００３９】
したがって、吸熱行程と放熱行程とを交互に繰り返せば、低温側である室内に吹き出す空気から、高温側である室外に熱を移動させることができるので、室内の冷房を行うことができる。
【００４０】
２．暖房運転
暖房運転は、冷房運転に対して熱の移動方向を逆向きとすればよいので、その運転作動も冷房運転時と逆である。つまり、以下の放熱行程を最初に実行した後、吸熱行程と放熱行程とを所定時間ごとに交互に繰り返し実行するものである。
【００４１】
２．１暖房運転の吸熱行程
第２吸着コア６にラジエータ９にて冷却された熱媒体を循環させて第２吸着剤を冷却することにより、第２吸着剤の関係湿度を上昇させて第２吸着剤に密閉容器７内の気相冷媒を吸着させる。これにより、密閉容器７内の冷媒湿度（第１吸着剤の関係湿度）が低下するので、第１吸着剤は密閉容器７中に吸着していた冷媒を脱離する。このとき、第１吸着剤から脱離する冷媒は、吸着行程時とは逆に、蒸発潜熱に相当する熱量を第１吸着剤から奪うので、第１吸着剤の温度が低下し、第１吸着コア３内の熱媒体が冷却される。
【００４２】
そして、この脱離吸熱作動と同時（併行）に、熱媒体ディスプレーサ５を作動させて、室内器１内の熱媒体を第１吸着コア３に供給し、第１吸着コア３内の熱媒体を室外器２に供給する。これにより、室外２には第１吸着コア３にて冷却された少なくとも外気温度より低い熱媒体が供給されるので、熱媒体は室外器２にて外気から熱を吸熱する。
【００４３】
２．２暖房運転の放熱行程
第２吸着コア６に電気ヒータ１０にて加熱された熱媒体を循環させて第２吸着剤を加熱することにより、第２吸着剤の関係湿度を低下させて第２吸着剤に吸着していた冷媒を密閉容器７中に脱離させる。これにより、密閉容器７内の冷媒湿度（第１吸着剤の関係湿度）が高くなるので、第１吸着剤は密閉容器７内の（第２吸着剤が脱離した）気相冷媒を吸着する。このとき、第１吸着剤は、冷媒を吸着する際に凝縮熱に相当する熱を発し、この熱により第１吸着コア３内の熱媒体を加熱する。
【００４４】
そして、この吸着発熱作動と同時（併行）に、熱媒体ディスプレーサ５を作動させて、吸熱行程時と逆向きに熱媒体が移動するように、室外器２内の熱媒体を第１吸着コア３に供給し、第１吸着コア３内の熱媒体を室内器１に供給する。これにより、室内器２には第１吸着コア３にて加熱（昇温）された熱媒体が供給されるので、第１吸着コア３にて熱媒体に与えられた熱が室内に吹き出す空気中に放熱される。
【００４５】
ここで、放熱行程において外気中に放熱される熱（気相冷媒を吸着する際に発生する熱）は、元々、吸熱行程において第１吸着剤から脱離する冷媒が、室外器２に供給する熱媒体から蒸発潜熱として吸熱した熱である。
【００４６】
したがって、吸熱行程と放熱行程とを交互に繰り返せば、低温側である室外から、高温側である室内に熱を移動させることができるので、室内の暖房を行うことができる。
【００４７】
以上に述べた本実施形態に係る吸着式ヒートポンプの作動を換言すれば、以下のようになる。
【００４８】
すなわち、吸熱行程時に、第１吸着剤から冷媒を脱離させることにより低温側（冷房時にあっては室内、暖房時にあっては室外）から吸熱し、その吸熱した熱を密閉容器７中の気相冷媒（水蒸気）が有するエンタルピとして保持した後、放熱行程時に、密閉容器７中の気相冷媒（水蒸気）を第１吸着剤に吸着させることにより吸熱行程時に吸熱した熱を密閉容器７中の気相冷媒（水蒸気）から高温側（冷房時にあっては室外、暖房時にあっては室内）に放熱させるものである。
【００４９】
一方、これら一連の作動を第１吸着コア３の温度分布の変化に着目して説明すると、以下のようになる。
【００５０】
すなわち、吸熱行程において密閉容器７の冷媒湿度（第１吸着剤の関係湿度）を下げると、その温度分布は、図４の太い実線Ａの状態となる。そして、この状態から熱媒体を移動させると、低温側（冷房時にあっては室内、暖房時にあっては室外）から高温側（冷房時にあっては室外、暖房時にあっては室内）に向かうほど温度が高くなるような温度勾配を維持しつつ、熱媒体の移動と共にその温度が上昇して図４の細い実線Ｂの状態になる。
【００５１】
因みに、図４のグラフの右側が室外器２側を示し、図４のグラフの左側は室内器１側を示している。
【００５２】
そして、細い実線Ｂの状態から放熱行程に移行して密閉容器７の冷媒湿度（第１吸着剤の関係湿度）を上げると第１吸着剤が発熱するので、図４の細い実線Ｂがそのまま平行移動するように温度が上昇し、図４の細い破線Ｃ状態となる。そして、この状態から熱媒体を移動させると、低温側から高温側に向かうほど温度が高くなるような温度勾配を維持しつつ、熱媒体の移動と共にその温度が低下して図４の太い破線Ｄの状態になる。
【００５３】
なお、放熱行程の終了後、密閉容器７の冷媒湿度（第１吸着剤の関係湿度）を下げれば、図４の太い実線の状態に戻る。
【００５４】
次に、本実施形態の特徴（作用効果）を述べる。
【００５５】
従来の技術に係る吸着式ヒートポンプでは、図５（ｂ）に示すように、容器内熱交換器（蒸発・凝縮熱交換器）Ｈｅは、吸着行程においては低温側を冷却して吸熱する熱交換器として機能し、脱離行程においては高温側を放熱する熱交換器として機能する。
【００５６】
このため、従来の技術に係る吸着式ヒートポンプにおいて、例えば冷房運転時の外気温度を４０℃とし、吸着剤の吸着・脱離作用により作り出すことができる温度差を３０℃とすると、従来の技術に係る吸着式ヒートポンプにおいては、熱媒体が連続的に循環しているので、脱離行程時における容器内熱交換器の平均温度は４０℃となり、吸着行程時における容器内熱交換器の平均温度は１０℃となる。
【００５７】
したがって、吸着行程時における容器内熱交換器の平均温度と脱離行程時における容器内熱交換器の平均温度との差は、吸着剤の吸着・脱離作用により作り出すことができる温度差と等しく、３０℃となる。
【００５８】
これに対して、本実施形態では、熱媒体を連続的に循環させることなく、例えば冷房運転時の吸熱行程においては、室外器２内の熱媒体を第１吸着コア３に供給し、第１吸着コア３内の熱媒体を室内器１に供給し、冷房運転時の放熱行程においては、吸熱行程時と逆向きに熱媒体が移動するように、室内器１内の熱媒体を第１吸着コア３に供給し、第１吸着コア３内の熱媒体を室外器２に供給するので、第１吸着器３は、図４に示すように、第１吸着コア３の熱媒体入口側と出口側とで温度差が発生するような温度勾配を有する。
【００５９】
このため、従来の技術に係る吸着式ヒートポンプと同様に、例えば冷房運転時の外気温度を４０℃とし、第１吸着コア３（第１吸着剤）の吸着・脱離作用により作り出すことができる温度差を３０℃とすると、第１吸着コア３により冷却された熱媒体の温度が１０℃となるので、吸熱行程における第１吸着コア３の平均温度は、図５（ａ）に示すように２５℃となる。
【００６０】
一方、放熱行程においては、室内に吹き出す空気から吸熱して温度が上昇した熱媒体が第１吸着コア３に供給されるため、放熱行程における第１吸着コア３の平均温度は、吸熱行程における第１吸着コア３の平均温度に対して、室内に吹き出す空気から吸熱したことによる温度上昇分（例えば、１０°）だけ上昇する。
【００６１】
このとき、室内に吹き出す空気から吸熱したことによる温度上昇分が、第１吸着コア３（第１吸着剤）の吸着・脱離作用により作り出すことができる温度差を超えることはあり得ないので、放熱行程における第１吸着コア３の平均温度と吸熱行程における第１吸着コア３の平均温度との差は、第１吸着コア３（第１吸着剤）の吸着・脱離作用により作り出すことができる温度差より小さくなる。
【００６２】
したがって、本実施形態によれば、放熱行程における第１吸着コア３の平均温度と吸熱行程における第１吸着コア３の平均温度との差を、従来の技術に係る吸着式ヒートポンプに比べて小さくすることができるので、第１吸着コア３自体の温度上昇に消費される熱エネルギ量を小さくすることができる。延いては、吸着式ヒートポンプの成績係数（ＣＯＰ）の向上を図ることができる。
【００６３】
ところで、従来の技術に係る吸着式ヒートポンプにおいては、図５（ｂ）に示すように、容器内熱交換器Ｈｅは、液相冷媒中に浸漬しているとともに、その液面（水位）が変動するので、特に、容器内熱交換器Ｈｅが凝縮器として機能する脱離行程においては、液面（水位）が上昇し、容器内熱交換器Ｈｅと吸着剤から脱離した気相冷媒（水蒸気）との伝熱面積が小さくなり、容器内熱交換器Ｈｅの凝縮（冷却）能力が低下すると言う問題が発生する。
【００６４】
これに対して、本実施形態では、密閉容器７内の気相冷媒を吸着・脱離させることにより低温側から高温側に熱を移動させるものであり、凝縮させる必要がないので、上記のような問題は基本的に存在しない。
【００６５】
なお、本実施形態では、脱離吸熱作動と同時（併行）に、熱媒体ディスプレーサ５を作動させたが、本実施形態はこれに限定されるものではなく、脱離吸熱作動の終了後（第１吸着剤の脱離作用及び第２吸着剤の吸着作用が終了した後）、熱媒体ディスプレーサ５を作動させてもよい。同様に、吸着発熱作動の終了後（第１吸着剤の吸着作用及び第２吸着剤の脱離作用が終了した後）、熱媒体ディスプレーサ５を作動させてもよい。
【００６６】
（第２実施形態）
第１実施形態では、第２吸着コア６（第２吸着剤）を加熱又は冷却することにより、密閉容器７内の冷媒湿度（第１吸着剤の関係湿度）が調節（制御）される。つまり、第１実施形態では、第２吸着コア６（第２吸着剤）、ラジエータ９及び電気ヒータ１０等から密閉容器７内の冷媒湿度（第１吸着剤の関係湿度）を調節する湿度調節手段（図１の一点鎖線で囲まれた部分）１２を構成した。
【００６７】
これに対して、本実施形態は、図６に示すように、気相冷媒（水蒸気）を吸入圧縮する蒸気圧縮機１３、密閉された容器内で冷媒を蒸発又は凝縮させる蒸発・凝縮器１４、蒸発・凝縮器１４を冷却する送風機１５、及び蒸気圧縮機１３の吸入側を密閉容器７側に接続し、吐出側を蒸発・凝縮器１４側に接続させる場合と、吸入側を蒸発・凝縮器１４側に接続し、吐出側を密閉容器７側に接続させる場合とを切り替える切り替えバルブ１６から湿度調節手段１２を構成したものである。
【００６８】
そして、密閉容器７の冷媒湿度（第１吸着剤の関係湿度）を下げるときには、蒸気圧縮機１３の吸入側を密閉容器７側に接続し、吐出側を蒸発・凝縮器１４側に接続した状態で送風機１５を稼働させることにより、密閉容器７内の気相冷媒を吸引して蒸発・凝縮器１４にて液化して冷媒を蓄える。
【００６９】
一方、密閉容器７の冷媒湿度（第１吸着剤の関係湿度）を上げるときには、送風機１５を停止した状態で、蒸気圧縮機１３の吸入側を蒸発・凝縮器１４側に接続し、吐出側を密閉容器７側に接続することにより、蒸発・凝縮器１４内の圧力を下げて液相冷媒を蒸発させるとともに、その蒸発した気相冷媒を吸引して密閉容器７に供給する。
【００７０】
（第３実施形態）
第１、２実施形態では、連続的に冷房運転又は暖房運転をすることができなかったが、本実施形態では、図７に示すように、第１実施形態に係る吸着式ヒートポンプを複数機（この例では、２機）用いて、第１の吸着式ヒートポンプが吸熱行程にあるときは、第２の吸着式ヒートポンプを放熱行程の稼働させ、逆に、第２の吸着式ヒートポンプが吸熱行程にあるときは、第１の吸着式ヒートポンプを放熱行程の稼働させることにより、連続的に冷房運転又は暖房運転をすることができるように構成したものである。
【００７１】
なお、図７では、第１実施形態に係る吸着式ヒートポンプを用いたが、本実施形態はこれに限定されるものではなく、第２実施形態に係る吸着式ヒートポンプを用いてもよい。
【００７２】
（その他の実施形態）
上述の実施形態では、吸着剤４としてゼオライト又はシリカゲル等の固体吸着剤を使用したが、本発明はこれに限定されるものではなく、臭化リチウム等の吸収液を含浸させたハイニカム構造体にて吸着剤を構成してもよい。
状の吸収体を用いてもよい。
【００７３】
また、上述の実施形態では、冷媒として水を用いたが、本発明はこれに限定されるものではなく、アルコール系冷媒、フロン系冷媒や炭化水素系冷媒等を用いてもよい。
【００７４】
また、湿度調節手段１２は、上述の実施形態に示されたものに限定されるものではなく、その他の手段にて湿度調節手段１２を構成してもよい。
【００７５】
また、上述の実施形態では、熱媒体を第１吸着コア３内を双方向に流通させたが、本発明はこれに限定されるものではなく、切り替えバルブを用いて第１吸着コア３内を熱媒体が一方向のみ流通するようにしてもよい。
【００７６】
また、上述の実施形態では、本発明に係る吸着式ヒートポンプを冷暖房切り替え可能な空調装置に適用したが、本発明はこれに限定されるものではなく、例えば冷房のみ若しくは暖房のみの空調装置、又は空調装置以外の用途にも適用することができる。
【００７７】
また、第１実施形態では、ポンプ８が一台であったが、図８に示すように、２台のポンプ８を切替運転することにより熱媒体を第２吸着コア６に循環させてもよい。
【図面の簡単な説明】
【図１】本発明の第１実施形態に係る吸着式ヒートポンプの模式図である。
【図２】本発明の実施形態に係る吸着式ヒートポンプに使用される吸着コアの正面図である。
【図３】吸着剤の吸着量と関係湿度との関係を示す特性図である。
【図４】本発明の実施形態に係る吸着式ヒートポンプにおける第１吸着コアの温度分布を説明するための説明図である。
【図５】（ａ）は本発明の実施形態に係る吸着式ヒートポンプの作動説明のための説明図であり、（ｂ）従来の技術に係る吸着式ヒートポンプの作動説明のための説明図である。
【図６】本発明の第２実施形態に係る吸着式ヒートポンプの模式図である。
【図７】本発明の第３実施形態に係る吸着式ヒートポンプの模式図である。
【図８】本発明のその他の実施形態に係る吸着式ヒートポンプの模式図である。
【符号の説明】
１…室内器、２…室外器、３…第１吸着コア、５…熱媒体ディスプレーサ、
６…第２吸着コア、７…密閉容器、１２…湿度調節手段。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an adsorption heat pump that has an adsorbent that adsorbs and desorbs a refrigerant according to the refrigerant humidity in the atmosphere, and moves the heat on the low temperature side to the high temperature side, and is effective when applied to an air conditioner It is.
[0002]
[Prior art]
As an air conditioner using an adsorption heat pump, for example, in the invention described in JP-A-5-126432, by adsorbing a gas-phase refrigerant in an airtight container (adsorber) maintained in a substantially vacuum state with an adsorbent. The liquid refrigerant is evaporated, and the heat medium supplied to the indoor heat exchanger is cooled by the latent heat of vaporization. Hereinafter, a heat exchanger that exchanges heat between the heat medium and the refrigerant is referred to as an in-vessel exchanger (evaporation / condensation heat exchanger).
[0003]
By the way, when the adsorption capacity (adsorption amount) of the adsorbent becomes saturated, the adsorption operation is stopped. Therefore, when the adsorbent is saturated, the adsorbed refrigerant is desorbed (regenerated) by heating the adsorbent, and then the refrigerant is adsorbed again. The gas-phase refrigerant desorbed from the adsorbent is cooled (condensed) by heat exchange with the outside air in the in-vessel heat exchanger.
[0004]
Hereinafter, the time when the adsorbent is performing the adsorption operation is referred to as an adsorption process, and the time when the adsorbed refrigerant is desorbed by heating is referred to as a desorption process.
[0005]
[Problems to be solved by the invention]
By the way, in the adsorption process, the refrigerant evaporates and the temperature of the sealed container (particularly, the heat exchanger in the container) decreases, whereas in the desorption process, the refrigerant condenses and forms a sealed container (in particular, the container). Since the temperature of the internal heat exchanger and the liquid phase refrigerant increases, the temperature of the sealed container (particularly, the internal heat exchanger and the liquid phase refrigerant) differs greatly between the adsorption process and the desorption process.
[0006]
For this reason, for example, immediately after the transition from the adsorption process to the desorption process, a part of the thermal energy input to the adsorption heat pump is not consumed for the desorption of the refrigerant (heating of the adsorbent), and is sealed. Since it is consumed by the container (particularly the heat exchanger in the container and the heating of the liquid phase refrigerant), the coefficient of performance (the amount of heat transferred / the amount of heat input) of the adsorption heat pump is lowered.
[0007]
Specifically, at the time of the adsorption process, when the temperature of the liquid heat exchanger in the container and the surrounding liquid phase refrigerant is 10 ° C. and the outside air temperature is 40 ° C., immediately after the transition from the adsorption process to the desorption process, The heat energy input to the adsorption heat pump is consumed to raise the in-vessel heat exchanger at 10 ° C. and the surrounding liquid-phase refrigerant to 40 ° C.
[0008]
In view of the above points, an object of the present invention is to improve the coefficient of performance (COP) of an adsorption heat pump.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, according to the present invention, in the invention described in claim 1, the refrigerant is adsorbed / desorbed according to the refrigerant humidity in the atmosphere. First An adsorption heat pump that has an adsorbent (4) and moves heat on the low temperature side to the high temperature side, the first heat exchanger (1, 2) arranged on the low temperature side, and arranged on the high temperature side A second heat exchanger (1, 2); First A third heat exchanger (3) for exchanging heat between the adsorbent (4) and the heat medium; First An airtight container (7) in which the adsorbent (4), the refrigerant and the third heat exchanger (3) are enclosed, and a humidity adjusting means (12) for adjusting the refrigerant humidity in the airtight container (7), The third heat exchanger (3) includes the first heat exchanger (1, 2) → the third heat exchanger (3) → the second heat exchanger (1,2) or the second heat exchanger (1 2) → 3rd heat exchanger (3) → first heat exchanger (1,2) and second heat exchanger ( 1, 2) is connected in series with the humidity adjusting means (12) Reduce the refrigerant humidity in the sealed container (7) First While desorbing the refrigerant adsorbed by the adsorbent (4), The heat medium heat-exchanged in the second heat exchanger (1, 2) is supplied to the third heat exchanger (3), and the first heat exchanger (3) An endothermic process of supplying a heat medium exchanged with the adsorbent (4) to the first heat exchanger (1, 2); By humidity control means (12) Increase the refrigerant humidity in the sealed container (7) First While adsorbing the refrigerant on the adsorbent (4), So that the heat medium moves in the opposite direction to the endothermic process, Supplying the heat medium exchanged in the first heat exchanger (1, 2) to the third heat exchanger (3); and First in the third heat exchanger (3) It is characterized by a heat pump that alternately performs a heat release process for supplying the heat medium exchanged with the adsorbent (4) to the second heat exchanger (1, 2).
[0010]
By the way, in the adsorption heat pump according to the prior art, as shown in FIG. 5B, the in-vessel heat exchanger (evaporation / condensation heat exchanger) He cools the low temperature side and absorbs heat in the adsorption process. It functions as a heat exchanger and functions as a heat exchanger that radiates heat on the high temperature side in the desorption process.
[0011]
Therefore, in the adsorption heat pump according to the conventional technique, for example, when the temperature on the high temperature side is 40 ° C. and the temperature difference that can be created by the adsorption / desorption action of the adsorbent is 30 ° C., the adsorption according to the conventional technique In the heat pump, since the heat medium continuously circulates, the average temperature of the in-vessel heat exchanger during the desorption stroke is 40 ° C., and the average temperature of the in-vessel heat exchanger during the adsorption stroke is 10 ° C. It becomes.
[0012]
Therefore, the difference between the average temperature of the heat exchanger in the container during the adsorption process and the average temperature of the heat exchanger in the container during the desorption process is equal to the temperature difference that can be created by the adsorption / desorption action of the adsorbent. 30 ° C.
[0013]
In contrast, in the present invention, the heat medium exchanged with the adsorbent (4) is supplied to the first heat exchanger (1, 2) without continuously circulating the heat medium, for example, in the endothermic process. In addition, the heat medium exchanged in the second heat exchanger (1, 2) is supplied to the third heat exchanger (3), and in the heat dissipation process, the first heat is opposite to that in the heat absorption process. The heat medium exchanged in the exchanger (1, 2) is supplied to the third heat exchanger (3), and the heat medium exchanged with the adsorbent (4) is supplied to the second heat exchanger (1, 2). ), The third heat exchanger (3) has a temperature gradient that causes a temperature difference between the heat medium inlet side and the outlet side.
[0014]
Therefore, as in the case of the adsorption heat pump according to the prior art, for example, when the temperature on the high temperature side is 40 ° C. and the temperature difference that can be created by the adsorption / desorption action of the adsorbent (4) is 30 ° C., Since the temperature of the heat medium cooled by the three heat exchangers (3) is 10 ° C., the average temperature of the third heat exchanger (3) in the endothermic process is 25 ° C. as shown in FIG. Become.
[0015]
On the other hand, in the heat dissipation process, the heat medium that has absorbed heat from the low temperature side and the temperature thereof is increased is supplied to the third heat exchanger (3). Therefore, the average temperature of the third heat exchanger (3) in the heat dissipation process is The average temperature of the third heat exchanger (3) in the endothermic process is increased by a temperature increase (for example, 10 °) due to heat absorption from the low temperature side.
[0016]
At this time, since the temperature rise due to the heat absorption from the low temperature side cannot exceed the temperature difference that can be created by the adsorption / desorption action of the adsorbent (4), the third heat exchanger in the heat dissipation process The difference between the average temperature of (3) and the average temperature of the third heat exchanger (3) in the endothermic process is smaller than the temperature difference that can be created by the adsorption / desorption action of the adsorbent (4).
[0017]
Therefore, according to the present invention, the difference between the average temperature of the third heat exchanger (3) in the heat dissipation process and the average temperature of the third heat exchanger (3) in the heat absorption process is determined by using the adsorption heat pump according to the related art. Therefore, the amount of heat energy consumed for the temperature rise of the third heat exchanger (3) itself can be reduced. As a result, the coefficient of performance (COP) of the adsorption heat pump can be improved.
[0018]
The humidity adjusting means (12), as in the second aspect of the invention, adsorbs the gas-phase refrigerant in the atmosphere by cooling and desorbs the adsorbed water by heating. 4) with configuration In the endothermic process, the refrigerant in the sealed container (7) is lowered by causing the second adsorbent (4) to adsorb the refrigerant in the sealed container (7), and in the heat releasing process, the second adsorbent is used. By desorbing the refrigerant adsorbed in (4) into the sealed container (7), the refrigerant humidity in the sealed container (7) is increased. Also good.
[0019]
Further, the humidity adjusting means (12) may have a vapor compressor (13) for sucking and compressing the gas-phase refrigerant, as in the third aspect of the invention.
[0020]
Further, as in the invention described in claim 4, the third heat exchanger (3) is disposed on both ends in the longitudinal direction of the plurality of tubes (3 a) and tubes (3 a) through which the heat medium flows. A tank (3b) communicating with the tube (3a), and a corrugated fin (3c) disposed between the tubes (3a). First The adsorbent (4) may be filled and bonded so as to come into contact with the tube (3a) and the fin (3c).
[0021]
Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
In this embodiment, the adsorption heat pump according to the present invention is applied to an air conditioner, and FIG. 1 is a schematic diagram of the air conditioner (adsorption heat pump).
[0023]
In FIG. 1, 1 is an indoor heat exchanger (hereinafter abbreviated as an indoor unit) that exchanges heat between air blown into the room and a heat medium (in this embodiment, a fluid in which water is mixed with an ethylene glycol antifreeze). 2 is an outdoor heat exchanger (hereinafter abbreviated as an outdoor unit) for exchanging heat between the outdoor air and the heat medium. In addition, 1a is an indoor blower that blows air to the indoor unit 1, and 2a is an outdoor blower that blows air to the outdoor unit 2.
[0024]
Reference numeral 3 denotes a first adsorption core (third heat exchanger) for exchanging heat between the heat medium and the adsorbent, and the first adsorption core 3 includes a plurality of tubes through which the heat medium flows as shown in FIG. 3a, a tank 3b disposed on both ends of the tube 3a in the longitudinal direction and communicating with each tube 3a, and a wave-like fin 3c disposed between the tubes 3a. The granular adsorbent 4 is closely packed and fixed to the first adsorbing core 3 so as to come into contact with the tubes 3a and the fins 3c.
[0025]
As shown in FIG. 3, the adsorbent 4 adsorbs and desorbs the refrigerant in accordance with the refrigerant humidity (relative humidity) in the atmosphere (strictly, near the surface of the adsorbent 4). As the humidity (relative humidity) increases, the refrigerant (water) adsorption amount increases, and as the refrigerant humidity (relative humidity) decreases, the refrigerant (water) adsorption amount decreases. Incidentally, in the present embodiment, a solid adsorbent such as zeolite or silica gel is used as the adsorbent 4, and water is used as the refrigerant.
[0026]
In FIG. 1, reference numeral 5 denotes a heat medium displacer (pump means) that circulates the heat medium between the indoor unit 1, the outdoor unit 2, and the adsorption core 3. The heat medium displacer 5 supplies the heat medium in the outdoor unit 2 to the adsorption core 3 so as to replace the heat medium in the adsorption core 3 when the internal piston 5a moves from the left side to the right side of the drawing. The heat medium in the adsorption core 3 is supplied to the indoor unit 1.
[0027]
On the other hand, when the piston 5a moves from the right side to the left side of the page, the heat medium in the indoor unit 1 is supplied to the adsorption core 3 so that the heat medium moves in the opposite direction to that when the piston 5a moves from the left side to the right side. Then, the heat medium in the adsorption core 3 is supplied to the outdoor unit 2.
[0028]
Reference numeral 6 denotes a second adsorption core having a structure similar to that of the first adsorption core 3, and the adsorbent 4 is bonded and fixed to the second adsorption core 6 in the same manner as the first adsorption core 3. The adsorption cores 3 and 6 (including the adsorbent 4) and the refrigerant are accommodated in an airtight container (adsorber) 7 in which the inside is maintained in a substantially vacuum.
[0029]
Hereinafter, the adsorbent 4 adhered and fixed to the first adsorption core 3 is referred to as a first adsorbent, and the adsorbent 4 adhered to the second adsorption core 6 is referred to as a second adsorbent. At this time, it is desirable that the total adsorption capacity (total water adsorption amount) of the first adsorbent is substantially equal to the total adsorption capacity (total water adsorption amount) of the second adsorbent.
[0030]
Reference numeral 8 denotes a pump that circulates the heat medium in the second adsorption core 6, 9 denotes a radiator that cools the heat medium circulated in the second adsorption core 6 with outside air, and 10 denotes the second adsorption core 6. An electric heater (heating means) for heating a heat medium to be circulated in the air heater 11 is a case where the heat medium cooled by the radiator 9 is circulated through the second adsorption core 6 and a heat medium heated by the electric heater 10. This is a switching valve for switching between the case of circulating the gas.
[0031]
In the present embodiment, an electric heater is employed as a heating means for heating the heat medium circulated to the second adsorption core 6, but the present embodiment is not limited to this, and an engine or inverter circuit The heat source such as waste heat is not questioned.
[0032]
Next, the operation of the adsorption heat pump (air conditioner) according to this embodiment will be described.
[0033]
1. Cooling operation
During the cooling operation, the following endothermic process is first executed, and then the heat dissipation process and the endothermic process are repeatedly executed every predetermined time.
[0034]
1.1 Endothermic process of cooling operation
The heat medium cooled by the radiator 9 is circulated through the second adsorption core 6 to cool the second adsorbent, thereby increasing the relative humidity of the second adsorbent and allowing the second adsorbent to be contained in the sealed container 7. Adsorb gas phase refrigerant. Thereby, since the refrigerant | coolant humidity (relative humidity of a 1st adsorbent) in the airtight container 7 falls, the 1st adsorbent desorbs the refrigerant | coolant adsorbed in the airtight container 7. FIG. At this time, the refrigerant desorbed from the first adsorbent takes away the amount of heat corresponding to the latent heat of evaporation from the first adsorbent, contrary to the time of the adsorption process, so that the temperature of the first adsorbent decreases and the first adsorption The heat medium in the core 3 is cooled. Hereinafter, the operation of the first adsorbent is referred to as desorption endothermic operation.
[0035]
At the same time (in parallel) with the desorption heat absorption operation, the heat medium displacer 5 is operated to supply the heat medium in the outdoor unit 2 to the first adsorption core 3, and the heat medium in the first adsorption core 3 is transferred to the room. Is supplied to the container 1 (see the arrow indicated by the solid line in FIG. 1). As a result, the indoor unit 1 is supplied with a heat medium lower than at least the outside air temperature cooled by the first adsorption core 3, so that the air blown into the room is cooled.
[0036]
1.2 Heat dissipation process for cooling operation
The heat medium heated by the electric heater 10 was circulated through the second adsorption core 6 to heat the second adsorbent, thereby lowering the relative humidity of the second adsorbent and adsorbing the second adsorbent. The refrigerant is desorbed into the sealed container 7. As a result, the refrigerant humidity in the sealed container 7 (relative humidity of the first adsorbent) is increased, so that the first adsorbent adsorbs the gas-phase refrigerant in the sealed container 7 (with the second adsorbent desorbed). . At this time, the first adsorbent emits a heat amount corresponding to the heat of condensation when adsorbing the refrigerant, and the heat medium in the first adsorption core 3 is heated by this heat. Hereinafter, the operation of the first adsorption core 3 (first adsorbent) is referred to as adsorption heat generation operation.
[0037]
At the same time (in parallel) with the adsorption heat generation operation, the heat medium displacer 5 is operated to move the heat medium in the indoor unit 1 to the first adsorption core 3 so that the heat medium moves in the direction opposite to that during the heat absorption process. Then, the heat medium in the first adsorption core 3 is supplied to the outdoor unit 2 (see the arrow indicated by the broken line in FIG. 1). Thereby, since the heat medium heated (heated up) by the first adsorption core 3 is supplied to the outdoor unit 2, the heat given to the heat medium by the first adsorption core 3 is dissipated into the outside air. The
[0038]
Here, the heat radiated into the outside air in the heat release process (heat generated when the gas-phase refrigerant is adsorbed) is supplied to the indoor unit 1 by the refrigerant originally desorbed from the first adsorbent in the heat absorption process. This is heat absorbed from the heat medium as latent heat of evaporation.
[0039]
Therefore, if the endothermic process and the heat dissipation process are alternately repeated, the heat can be transferred from the air blown into the room on the low temperature side to the outdoor side on the high temperature side, so that the room can be cooled.
[0040]
2. Heating operation
In the heating operation, since the heat transfer direction may be opposite to that in the cooling operation, the operation operation is also opposite to that in the cooling operation. That is, after the following heat radiation process is first executed, the heat absorption process and the heat radiation process are alternately and repeatedly executed at predetermined time intervals.
[0041]
2.1 Endothermic process of heating operation
The heat medium cooled by the radiator 9 is circulated through the second adsorption core 6 to cool the second adsorbent, thereby increasing the relative humidity of the second adsorbent and allowing the second adsorbent to be contained in the sealed container 7. Adsorb gas phase refrigerant. Thereby, since the refrigerant | coolant humidity (relative humidity of a 1st adsorbent) in the airtight container 7 falls, the 1st adsorbent desorbs the refrigerant | coolant adsorbed in the airtight container 7. FIG. At this time, the refrigerant desorbed from the first adsorbent takes away the amount of heat corresponding to the latent heat of evaporation from the first adsorbent, contrary to the time of the adsorption process, so that the temperature of the first adsorbent decreases and the first adsorption The heat medium in the core 3 is cooled.
[0042]
At the same time (in parallel) with the desorption heat absorption operation, the heat medium displacer 5 is operated to supply the heat medium in the indoor unit 1 to the first adsorption core 3, and the heat medium in the first adsorption core 3 is supplied. Supply to the outdoor unit 2. As a result, the outdoor medium 2 is supplied with a heat medium that is cooled at least by the first adsorption core 3 and that is lower than the outdoor air temperature, so that the heat medium absorbs heat from the outdoor air in the outdoor unit 2.
[0043]
2.2 Heat dissipation process for heating operation
The heat medium heated by the electric heater 10 was circulated through the second adsorption core 6 to heat the second adsorbent, thereby lowering the relative humidity of the second adsorbent and adsorbing the second adsorbent. The refrigerant is desorbed into the sealed container 7. As a result, the refrigerant humidity in the sealed container 7 (relative humidity of the first adsorbent) is increased, so that the first adsorbent adsorbs the gas-phase refrigerant in the sealed container 7 (with the second adsorbent desorbed). . At this time, the first adsorbent generates heat corresponding to the heat of condensation when adsorbing the refrigerant, and heats the heat medium in the first adsorption core 3 by this heat.
[0044]
The heat medium displacer 5 is operated at the same time as the adsorption heat generation operation, and the heat medium in the outdoor unit 2 is moved to the first adsorption core 3 so that the heat medium moves in the direction opposite to that during the heat absorption process. The heat medium in the first adsorption core 3 is supplied to the indoor unit 1. Thereby, since the heat medium heated (heated up) by the first adsorption core 3 is supplied to the indoor unit 2, the heat given to the heat medium by the first adsorption core 3 blows out into the room. Heat is dissipated.
[0045]
Here, the heat radiated into the outside air in the heat release process (heat generated when the gas-phase refrigerant is adsorbed) is originally supplied to the outdoor unit 2 by the refrigerant desorbed from the first adsorbent in the heat absorption process. This is heat absorbed from the heat medium as latent heat of evaporation.
[0046]
Therefore, if the endothermic process and the heat dissipation process are alternately repeated, heat can be transferred from the outside on the low temperature side to the room on the high temperature side, and thus the room can be heated.
[0047]
In other words, the operation of the adsorption heat pump according to the present embodiment described above is as follows.
[0048]
That is, during the endothermic process, the refrigerant is desorbed from the first adsorbent to absorb heat from the low temperature side (in the case of cooling, indoors, in the case of heating), and the absorbed heat is removed from the air in the sealed container 7. After being held as the enthalpy of the phase refrigerant (water vapor), the heat absorbed during the endothermic process is absorbed in the sealed container 7 by adsorbing the gas phase refrigerant (water vapor) in the sealed container 7 to the first adsorbent during the heat dissipation process. Heat is dissipated from the gas-phase refrigerant (water vapor) to the high temperature side (outdoors during cooling and indoors during heating).
[0049]
On the other hand, a series of these operations will be described below with a focus on the change in the temperature distribution of the first adsorption core 3.
[0050]
That is, when the refrigerant humidity (relative humidity of the first adsorbent) of the sealed container 7 is lowered in the endothermic process, the temperature distribution becomes a state indicated by a thick solid line A in FIG. When the heat medium is moved from this state, the temperature goes from the low temperature side (indoors during cooling, outdoor in heating) to the high temperature side (outdoors during cooling, indoors during heating). While maintaining a temperature gradient such that the temperature rises, the temperature rises with the movement of the heat medium, and the state becomes a thin solid line B in FIG.
[0051]
Incidentally, the right side of the graph of FIG. 4 shows the outdoor unit 2 side, and the left side of the graph of FIG. 4 shows the indoor unit 1 side.
[0052]
Then, when the refrigerant humidity (relative humidity of the first adsorbent) of the sealed container 7 is increased from the state of the thin solid line B to the heat release process, the first adsorbent generates heat, so that the thin solid line B in FIG. The temperature rises so as to move, and a thin broken line C state in FIG. 4 is obtained. When the heat medium is moved from this state, the temperature is lowered with the movement of the heat medium while maintaining a temperature gradient such that the temperature increases from the low temperature side toward the high temperature side, and the thick broken line D in FIG. It becomes the state of.
[0053]
In addition, if the refrigerant | coolant humidity (relative humidity of a 1st adsorbent) of the airtight container 7 is reduced after completion | finish of a thermal radiation process, it will return to the state of the thick continuous line of FIG.
[0054]
Next, features (effects) of this embodiment will be described.
[0055]
In the adsorption heat pump according to the prior art, as shown in FIG. 5B, the heat exchanger (evaporation / condensation heat exchanger) He in the container cools the low temperature side and absorbs heat in the adsorption process. It functions as a heat exchanger and functions as a heat exchanger that dissipates heat on the high temperature side in the desorption process.
[0056]
For this reason, in the adsorption heat pump according to the conventional technology, for example, if the outside air temperature during cooling operation is 40 ° C. and the temperature difference that can be created by the adsorption / desorption action of the adsorbent is 30 ° C., the conventional technology In such an adsorption heat pump, since the heat medium continuously circulates, the average temperature of the in-vessel heat exchanger during the desorption stroke is 40 ° C., and the average temperature of the in-vessel heat exchanger during the adsorption stroke is 10 ° C.
[0057]
Therefore, the difference between the average temperature of the heat exchanger in the container during the adsorption process and the average temperature of the heat exchanger in the container during the desorption process is equal to the temperature difference that can be created by the adsorption / desorption action of the adsorbent. 30 ° C.
[0058]
On the other hand, in the present embodiment, the heat medium in the outdoor unit 2 is supplied to the first adsorption core 3 in the heat absorption process during the cooling operation, for example, without continuously circulating the heat medium. The heat medium in the adsorption unit 3 is supplied to the indoor unit 1, and the heat medium in the indoor unit 1 is first adsorbed so that the heat medium moves in the opposite direction to that during the heat absorption process in the heat dissipation process during the cooling operation. Since it supplies to the core 3 and the heat medium in the 1st adsorption | suction core 3 is supplied to the outdoor unit 2, as shown in FIG. It has a temperature gradient that causes a temperature difference between the two sides.
[0059]
For this reason, similarly to the adsorption heat pump according to the conventional technology, for example, the outside air temperature during cooling operation is set to 40 ° C., and the temperature that can be generated by the adsorption / desorption action of the first adsorption core 3 (first adsorbent). If the difference is 30 ° C., the temperature of the heat medium cooled by the first adsorption core 3 is 10 ° C. Therefore, the average temperature of the first adsorption core 3 in the endothermic process is 25 as shown in FIG. It becomes ℃.
[0060]
On the other hand, in the heat dissipation process, the heat medium that has absorbed heat from the air blown into the room and increased in temperature is supplied to the first adsorption core 3, so that the average temperature of the first adsorption core 3 in the heat dissipation process is the first temperature in the heat absorption process. The average temperature of one adsorption core 3 is increased by a temperature increase (for example, 10 °) due to heat absorption from the air blown into the room.
[0061]
At this time, the temperature rise due to the absorption of heat from the air blown into the room cannot exceed the temperature difference that can be created by the adsorption / desorption action of the first adsorption core 3 (first adsorbent). The difference between the average temperature of the first adsorption core 3 in the heat dissipation process and the average temperature of the first adsorption core 3 in the heat absorption process can be created by the adsorption / desorption action of the first adsorption core 3 (first adsorbent). Smaller than temperature difference.
[0062]
Therefore, according to this embodiment, the difference between the average temperature of the first adsorption core 3 in the heat dissipation process and the average temperature of the first adsorption core 3 in the heat absorption process is made smaller than that of the adsorption heat pump according to the related art. Therefore, the amount of heat energy consumed for the temperature increase of the first adsorption core 3 itself can be reduced. As a result, the coefficient of performance (COP) of the adsorption heat pump can be improved.
[0063]
By the way, in the adsorption heat pump according to the conventional technique, as shown in FIG. 5B, the in-container heat exchanger He is immersed in the liquid-phase refrigerant and its liquid surface (water level) fluctuates. Therefore, in particular, in the desorption process in which the in-vessel heat exchanger He functions as a condenser, the liquid level (water level) rises, and the gas phase refrigerant (water vapor) desorbed from the in-vessel heat exchanger He and the adsorbent. ) And the heat transfer area is reduced, and the condensation (cooling) capacity of the in-vessel heat exchanger He is reduced.
[0064]
On the other hand, in the present embodiment, heat is transferred from the low temperature side to the high temperature side by adsorbing / desorbing the gas-phase refrigerant in the hermetic container 7, and it is not necessary to condense. There is basically no problem.
[0065]
In the present embodiment, the heat medium displacer 5 is operated simultaneously (in parallel) with the desorption endothermic operation. However, the present embodiment is not limited to this, and after the end of the desorption endothermic operation (first operation) After the adsorbing action of the first adsorbent and the adsorbing action of the second adsorbent are completed, the heat medium displacer 5 may be operated. Similarly, the heat medium displacer 5 may be operated after the adsorption heat generation operation is finished (after the adsorption action of the first adsorbent and the desorption action of the second adsorbent are finished).
[0066]
(Second Embodiment)
In the first embodiment, the refrigerant humidity (relative humidity of the first adsorbent) in the sealed container 7 is adjusted (controlled) by heating or cooling the second adsorption core 6 (second adsorbent). That is, in the first embodiment, the humidity adjusting means for adjusting the refrigerant humidity (relative humidity of the first adsorbent) in the sealed container 7 from the second adsorbing core 6 (second adsorbent), the radiator 9, the electric heater 10, and the like. (A portion surrounded by an alternate long and short dash line in FIG. 1) 12 was formed.
[0067]
In contrast, in the present embodiment, as shown in FIG. 6, a vapor compressor 13 that sucks and compresses a gas-phase refrigerant (water vapor), an evaporator / condenser 14 that evaporates or condenses the refrigerant in a sealed container, The blower 15 that cools the evaporator / condenser 14 and the suction side of the vapor compressor 13 are connected to the closed container 7 side, the discharge side is connected to the evaporator / condenser 14 side, and the suction side is the evaporator / condenser. The humidity adjusting means 12 is configured from a switching valve 16 that switches between connecting to the 14 side and connecting the discharge side to the closed container 7 side.
[0068]
And when reducing the refrigerant | coolant humidity (relative humidity of a 1st adsorption agent) of the airtight container 7, the suction side of the vapor compressor 13 is connected to the airtight container 7 side, and the discharge side is connected to the evaporator / condenser 14 side By operating the blower 15, the gas-phase refrigerant in the sealed container 7 is sucked and liquefied by the evaporator / condenser 14 to store the refrigerant.
[0069]
On the other hand, when increasing the refrigerant humidity (relative humidity of the first adsorbent) of the sealed container 7, with the blower 15 stopped, the suction side of the vapor compressor 13 is connected to the evaporation / condenser 14 side, and the discharge side is By connecting to the closed container 7 side, the pressure in the evaporator / condenser 14 is lowered to evaporate the liquid phase refrigerant, and the evaporated gas phase refrigerant is sucked and supplied to the closed container 7.
[0070]
(Third embodiment)
In the first and second embodiments, the cooling operation or the heating operation could not be continuously performed. However, in this embodiment, as shown in FIG. 7, the adsorption heat pump according to the first embodiment includes a plurality of ( In this example, two machines are used, and when the first adsorption heat pump is in the endothermic process, the second adsorption heat pump is operated in the heat dissipation process, and conversely, the second adsorption heat pump is in the endothermic process. In some cases, the first adsorption heat pump is configured to operate continuously in the cooling operation or the heating operation by operating in the heat dissipation stroke.
[0071]
In FIG. 7, the adsorption heat pump according to the first embodiment is used. However, the present embodiment is not limited to this, and the adsorption heat pump according to the second embodiment may be used.
[0072]
(Other embodiments)
In the above-described embodiment, a solid adsorbent such as zeolite or silica gel is used as the adsorbent 4, but the present invention is not limited to this, and the high-nickum structure impregnated with an absorbing liquid such as lithium bromide is used. An adsorbent may be configured.
A shaped absorber may be used.
[0073]
In the above-described embodiment, water is used as the refrigerant. However, the present invention is not limited to this, and an alcohol refrigerant, a chlorofluorocarbon refrigerant, a hydrocarbon refrigerant, or the like may be used.
[0074]
Further, the humidity adjusting means 12 is not limited to that shown in the above-described embodiment, and the humidity adjusting means 12 may be configured by other means.
[0075]
Further, in the above-described embodiment, the heat medium is circulated in the first adsorption core 3 in both directions. However, the present invention is not limited to this, and the inside of the first adsorption core 3 is changed using a switching valve. The heat medium may be circulated only in one direction.
[0076]
Further, in the above-described embodiment, the adsorption heat pump according to the present invention is applied to an air conditioner capable of switching between cooling and heating, but the present invention is not limited to this, for example, an air conditioner only for cooling or heating, or It can be applied to uses other than air conditioners.
[0077]
In the first embodiment, the number of the pumps 8 is one. However, as shown in FIG. 8, the heat medium may be circulated to the second adsorption core 6 by switching the two pumps 8. .
[Brief description of the drawings]
FIG. 1 is a schematic diagram of an adsorption heat pump according to a first embodiment of the present invention.
FIG. 2 is a front view of an adsorption core used in the adsorption heat pump according to the embodiment of the present invention.
FIG. 3 is a characteristic diagram showing the relationship between the amount of adsorbent adsorbed and the relative humidity.
FIG. 4 is an explanatory diagram for explaining a temperature distribution of a first adsorption core in the adsorption heat pump according to the embodiment of the present invention.
5A is an explanatory diagram for explaining the operation of the adsorption heat pump according to the embodiment of the present invention, and FIG. 5B is an explanatory diagram for explaining the operation of the adsorption heat pump according to the conventional technique. .
FIG. 6 is a schematic diagram of an adsorption heat pump according to a second embodiment of the present invention.
FIG. 7 is a schematic diagram of an adsorption heat pump according to a third embodiment of the present invention.
FIG. 8 is a schematic view of an adsorption heat pump according to another embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Indoor unit, 2 ... Outdoor unit, 3 ... 1st adsorption | suction core, 5 ... Heat-medium displacer,
6 ... 2nd adsorption | suction core, 7 ... Airtight container, 12 ... Humidity adjustment means.

Claims

An adsorption heat pump that has a first adsorbent (4) that adsorbs and desorbs refrigerant according to the refrigerant humidity in the atmosphere, and moves the heat on the low temperature side to the high temperature side,
A first heat exchanger (1, 2) arranged on the low temperature side;
A second heat exchanger (1, 2) arranged on the high temperature side;
A third heat exchanger (3) for exchanging heat between the first adsorbent (4) and the heat medium;
A sealed container (7) in which the first adsorbent (4), the refrigerant, and the third heat exchanger (3) are enclosed;
Humidity adjusting means (12) for adjusting the refrigerant humidity in the sealed container (7),
The third heat exchanger (3) includes the first heat exchanger (1,2) → the third heat exchanger (3) → the second heat exchanger (1,2) or the second heat exchanger (1,2). The first heat exchangers (1, 2) so that the heat medium flows in the order of heat exchanger (1, 2) → third heat exchanger (3) → first heat exchanger (1, 2). ) And the second heat exchanger (1, 2) in series,
The humidity adjusting means (12) lowers the refrigerant humidity in the sealed container (7) to desorb the refrigerant adsorbed by the first adsorbent (4), and the second heat exchanger (1, The heat medium exchanged in 2) is supplied to the third heat exchanger (3), and the heat medium exchanged with the first adsorbent (4) in the third heat exchanger (3). An endothermic process of supplying the first heat exchanger (1, 2) to
The humidity adjusting means (12) increases the refrigerant humidity in the closed container (7) to adsorb the refrigerant to the first adsorbent (4), and the heat medium moves in the opposite direction to the endothermic process. as described above, by supplying the heat medium exchanges heat with the first heat exchanger (1,2) in the third heat exchanger (3), and said at the third heat exchanger (3) the A heat dissipating process for supplying a heat medium exchanged with one adsorbent (4) to the second heat exchanger (1, 2);
An adsorption heat pump characterized by alternately executing

The humidity adjusting means (12) includes a second adsorbent (4) that adsorbs the gas-phase refrigerant in the atmosphere by cooling and desorbs the adsorbed moisture by being heated. And
In the endothermic process, the refrigerant in the sealed container (7) is lowered by adsorbing the refrigerant in the sealed container (7) to the second adsorbent (4),
In the heat dissipation step, the refrigerant humidity in the sealed container (7) is increased by desorbing the refrigerant adsorbed on the second adsorbent (4) into the sealed container (7). The adsorption heat pump according to claim 1.

The adsorption heat pump according to claim 1, wherein the humidity adjusting means (12) includes a vapor compressor (13) for sucking and compressing a gas phase refrigerant.

The third heat exchanger (3) includes a plurality of tubes (3a) through which a heat medium flows, and tanks (not shown) that are disposed on both ends in the longitudinal direction of the tubes (3a) and communicate with the tubes (3a). 3b), and wavy fins (3c) disposed between the tubes (3a),
The adsorption according to any one of claims 1 to 3, wherein the first adsorbent (4) is filled and bonded so as to come into contact with the tube (3a) and the fin (3c). Type heat pump.