JP4151095B2

JP4151095B2 - Refrigeration equipment

Info

Publication number: JP4151095B2
Application number: JP35821897A
Authority: JP
Inventors: 誠司井上
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 1997-12-25
Filing date: 1997-12-25
Publication date: 2008-09-17
Anticipated expiration: 2017-12-25
Also published as: JPH11190568A

Description

【０００１】
【発明の属する技術分野】
本発明は、冷媒を圧縮蒸発させることにより冷却能力を得る蒸気圧縮式冷凍機と、略真空（０．１ｍｍＨｇ）に保持された吸着器内に蒸気冷媒を吸着する吸着剤および液冷媒を収納した吸着式冷凍機とを組み合わせた冷凍装置に関するもので、空調装置に適用して有効である。
【０００２】
【従来の技術】
蒸気圧縮式冷凍機と吸着式冷凍機とを組み合わせた冷凍装置としては、特開平３−１８６１６３号公報がある。そして、上記公報に記載の発明は、蒸気圧縮式冷凍機の廃熱（凝縮熱）により、吸着式冷凍機の再生（吸着剤に吸着された蒸気冷媒を脱離させる行為）効率の向上を図るものである。
【０００３】
【発明が解決しようとする課題】
しかし、比較的小型の冷凍装置（一般家庭用または小型業務用空調装置等）では、蒸気圧縮式冷凍機からの廃熱温度が比較的低い（通常は約６０℃以下）ので、上記公報に記載の発明では、再生時に吸着剤および液冷媒を高い温度まで上げることができない。
【０００４】
したがって、上記公報に記載の発明では、吸着時と再生時との温度差が比較的小さいので、十分な冷凍能力を得ることが困難である。
本発明は、上記点に鑑み、蒸気圧縮式冷凍機と吸着式冷凍機とを組み合わせた冷凍装置において、少ない動力で十分な冷凍能力を得ることを目的とする。
【０００５】
【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、以下の技術的手段を用いる。請求項１に記載の発明では、圧縮機（１２１）、凝縮器（１２２）、減圧器（１２３）および蒸発器（１２４）を有する蒸気圧縮式冷凍機（１２０）と、液冷媒および蒸気冷媒を吸着する吸着剤（Ｓｉ）が収納された吸着器（１３１ｂ）を有する吸着式冷凍機（１３０）とを備え、吸着器（１３１ｂ）は、１つだけ設けられており、吸着状態にある吸着器（１３１ｂ）の冷却作用により凝縮器（１２２）を冷却するとともに、蒸発器（１２４）により被冷却体を冷却する状態と、凝縮器（１２２）にて発生する熱により吸着剤（Ｓｉ）を加熱して吸着された蒸気冷媒を脱離させるとともに、吸着剤（Ｓｉ）から脱離した蒸気冷媒を蒸発器（１２４）の冷却作用により凝縮させる再生状態とを一定時間毎に切り替えるようになっており、吸着器（１３１ｂ）は、吸着剤（Ｓｉ）が配置された部位に設けられて、吸着剤（Ｓｉ）と熱交換媒体とを熱交換させる吸着剤熱交換器（１３２ｂ）、および、液冷媒が位置する部位に設けられて液冷媒と熱交換媒体とを熱交換させる水熱交換器（１３３ｂ）を有し、
さらに、凝縮器（１２２）にて加熱された熱交換媒体と室外空気とを熱交換させる室外熱交換器（１３４）と、蒸発器（１２４）にて冷却された熱交換媒体と被冷却体とを熱交換させる室内熱交換器（４０）と、吸着剤熱交換器（１３２ｂ）と室外熱交換器（１３４）との間で熱交換媒体を循環させる流路、および、吸着剤熱交換器（１３２ｂ）と凝縮器（１２２）との間で熱交換媒体を循環させる流路を切り替える第１切替弁（１３６ａ、１３６ｂ）と、水熱交換器（１３３ｂ）と凝縮器（１２２）との間で熱交換媒体を循環させる流路、および、水熱交換器（１３３ｂ）と蒸発器（１２４）側との間で熱交換媒体を循環させる流路を切り替える第２切替弁（１３６ｃ、１３６ｄ）と、蒸発器（１２４）と室内熱交換器（４０）との間で熱交換媒体を循環させる流路、および、蒸発器（１２４）と水熱交換器（１３３ｂ）との間で熱交換媒体を循環させる流路とを切り替える第３切替弁（１３６ｅ、１３６ｆ）とを備える冷凍装置を特徴とする。
【０００６】
これにより、蒸気圧縮式冷凍機（１２０）の凝縮器（１２２）内の圧力を下げることができるので、蒸気圧縮式冷凍機（１２０）の圧縮機（１２１）の動力（圧縮仕事）を低減することができる。したがって、蒸気圧縮式冷凍機（１２０）と吸着式冷凍機（１３０）とを組み合わせた冷凍装置において、少ない動力で十分な冷凍能力を得ることができる。
【０００８】
さらに、吸着式冷凍機（１３０）における吸着器（１３１ｂ）を、１つだけ設ける構成としているので、冷凍装置の構成を簡素なものとして、冷凍装置の製造原価低減を図ることができる。ところで、請求項１に記載の発明では、一定時間毎に吸着状態と再生状態とを切り替えて運転するので、再生状態では被冷却体を冷却することができない場合がある。
【０００９】
そこで、請求項２に記載の発明では、蒸発器（１１４）により冷却される蓄冷材（１５０）を有するとともに、蓄冷材（１５０）は再生状態のときに被冷却体を冷却することを特徴とする。これにより、蓄冷材１５０により再生状態のときに室内空気の冷却をすることができる。請求項３に記載の発明のように、蓄冷材（１５０）は、物質の凝固融解を利用する潜熱蓄冷材であってもよい。
【００１０】
なお、上記各手段の括弧内の符号は、後述する実施形態記載の具体的手段との対応関係を示すものである。
【００１１】
【発明の実施の形態】
以下説明する第１〜第３実施形態のうち、特許請求の範囲に記載した発明の実施形態は、第２、第３実施形態であり、第１実施形態は本発明の前提となる参考例を示す。
（第１実施形態）
本実施形態は、本発明に係る冷凍装置１００を室内の冷房を図る空調装置に適用したものであり、図１は本実施形態に係る冷凍装置１００の模式図である。図１中、１１０、１２０はフロンを冷媒とする第１、２蒸気圧縮式冷凍機であり、これら第１、２蒸気圧縮式冷凍機１１０、１２０は、周知のごとく、第１、２圧縮機１１１、１２１、第１、２凝縮器（放熱器）１１２、１２２、第１、２減圧器１１３、１２３、第１、２蒸発器１１４、１２４および第１、２アキュームレータ１１５、１２５を有して構成されている。
【００１２】
因みに、第１、２圧縮機１１１、１２１は電動モータ（図示せず）により駆動されるとともに、その回転数は電動モータを制御することにより行われ、第１、２減圧器１１３、１２３はキャピラリーチューブ等の固定絞り手段である。
また、蒸発器１１４、１２４は冷媒を蒸発させることにより冷凍能力を発揮するものであり、第１、２アキュームレータ１１５、１２５各々は蒸発器１１４から流出した冷媒を気相冷媒と液相冷媒とに分離して気相冷媒を第１、２圧縮機１１１、１２１の吸入側に流出するものである。
【００１３】
１３１ａ、１３１ｂは内部が略真空（０．１ｍｍＨｇ）に保持された第１、２吸着器であり、この第１、２吸着器１３１ａ、１３１ｂ内には、液冷媒（本実施形態では水）Ｌｒと、蒸発した液冷媒（水蒸気）を吸着する吸着剤（本実施形態ではシリカゲル）Ｓｉとが収納されている。
そして、吸着剤Ｓｉが配設されている部位には第１、２吸着剤熱交換器１３２ａ、１３２ｂが配設され、液冷媒Ｌｒが位置している部位には第１、２水熱交換器１３３ａ、１３３ｂが配設されており、各熱交換器１３２ａ、１３２ｂ、１３３ａ、１３３ｂ内には熱交換媒体（本実施形態では水）が循環している。
【００１４】
また、１３４は室外に配設されて熱交換媒体と室外空気とを熱交換する室外熱交換器であり、１３５ａ〜１３５ｄは、熱交換媒体を循環させる第１〜４ポンプである。そして、各熱交換器１３２ａ、１３２ｂ、１３３ａ、１３３ｂ、１３４、第１、２凝縮器１１２、１２２および第１、２蒸発器１１４、１２４間における熱交換媒体の流通状態の制御は、第１〜４四方弁１３６ａ〜１３６ｄを切り替え制御することにより行われる。なお、第１〜４四方弁１３６ａ〜１３６ｄおよび第１〜４ポンプ１３５ａ〜１３５ｄは、電子制御装置（図示せず）により作動制御されている。
【００１５】
そして、本実施形態では、第１、２吸着器１３１ａ、１３１ｂおよび各熱交換器１３２ａ、１３２ｂ、１３３ａ、１３３ｂ、１３４等から吸着式冷凍機１３０が構成されている。
次に、冷凍装置１００の作動を述べる。
図１は第１吸着器１３１ａが吸着状態にあり、第２吸着器１３１ｂが再生状態にあるときを示しており、第１吸着器１３１ａ内では液冷媒Ｌｒの蒸発が進行するので、第１水熱交換器１３３ａを流通する熱交換媒体が冷却されて第２凝縮器１２２を冷却する。
【００１６】
このとき、第１吸着剤熱交換器１３２ａには、室外熱交換器１３４にて室外空気で冷却された熱交換媒体が流通しているので、吸着剤Ｓｉが冷却される。したがって、吸着剤Ｓｉの温度上昇が抑制されるので、吸着剤Ｓｉの吸着能力の低下を防止して、吸着式冷凍機１３０の冷却能力の低下を防止する。
一方、第２吸着剤熱交換器１３２ｂには、第１凝縮器１１２にて加熱された熱交換媒体が流通するので、第２吸着器１３１ｂの吸着剤Ｓｉは吸着した水蒸気を脱離する。また、第２水熱交換器１３３ｂには室外熱交換器１３４にて室外空気で冷却された熱交換媒体が流通しているので、脱離した水蒸気が凝縮して再生する。
【００１７】
そして、電子制御装置は、第１〜４四方弁１３６ａ〜１３６ｄを一定時間毎に切り替える制御することにより、両吸着器１３１ａ、１３１ｂが交互に吸着状態と再生状態とになるように制御している。因みに、図２は第２吸着器１３１ｂが吸着状態で第１吸着器１３１ａが脱離状態の場合の模式図である。
なお、図３は、吸着器１３１ａ、１３１ｂ内の吸着剤Ｓｉの状態を示す吸着等温線であり、吸着剤Ｓｉの水分吸着率は、図３に示すように、吸着剤Ｓｉの温度および液冷媒Ｌｒの温度によって決定される。そして、吸着剤Ｓｉは、Ａ点（再生状態）とＢ点（吸着状態）との差分の水分を吸着するととともに、その吸着水分量に対応する蒸発潜熱が吸着冷凍機１３０の冷凍能力となる。
【００１８】
因みに、図３から明らかなように、第１〜４四方弁１３６ａ〜１３６ｄを切り替える時間は、吸着剤Ｓｉの種類、吸着剤Ｓｉの粒径、吸着剤Ｓｉの充填量などによてって適宜選定されるものであるが、本実施形態では、約２〜１０分毎に切り替えている。
次に、本実施形態の特徴を述べる。
【００１９】
本実施形態によれば、吸着式冷凍機１３０により第２凝縮器１２２が冷却されるので、第２凝縮器１２２内の圧力を下げることができる。したがって、第２圧縮機１２１の動力（圧縮仕事）を低減することができるので、第１、２蒸気圧縮式冷凍機１１０、１２０と吸着式冷凍機１３０とを組み合わせた冷凍装置１００において、少ない動力で十分な冷凍能力を得ることができる。
【００２０】
以下、本実施形態の特徴を具体的な例を挙げて説明しておく。
図４の実線は第１蒸気圧縮式冷凍機１１０のモリエル線図であり、図４の破線は第２蒸気圧縮式冷凍機１２０のモリエル線図である。そして、図４から明らかなように、第１蒸気圧縮式冷凍機１１０の高圧側（第１凝縮器１１２側）圧力が０．８８［ＭＰａ］、低圧側（第１蒸発器１１４側）圧力が０．４６［ＭＰａ］であるので、成績係数（ＣＯＰ1 ）は約７．２である。同様に、第２蒸気圧縮式冷凍機１２０の高圧側（第２凝縮器１２２側）圧力が０．５９［ＭＰａ］、低圧側（第２蒸発器１２４側）圧力が０．３５［ＭＰａ］であるので、成績係数（ＣＯＰ2 ）は約９．９である。
【００２１】
ところで、本実施形態では、室内空気（被冷却体）の冷却は第２蒸発器１２４にて行うので、第２蒸発器１２４で必要とされる冷凍能力をＸ［Ｗ］とすれば、第２圧縮機１２１の動力は０．１Ｘ（＝Ｘ／ＣＯＰ2 ）［Ｗ］であり、第２凝縮器１２２で発生する熱量Ｑは｛Ｘ（１＋１／ＣＯＰ2 ）｝［Ｗ］となる。
そして、熱量Ｑは吸着式冷凍機１３０での冷凍能力に等しいので、吸着状態にある吸着器（１３１ａ）の水冷媒の蒸発潜熱に等しくなり、この蒸発潜熱は、再生状態にある吸着器（１３１ｂ）での蒸気冷媒の凝縮熱に等しい。したがって、熱量Ｑは第１蒸気圧縮式冷凍機１１０の冷凍能力に等しくなるので、第１圧縮機１１１の動力は０．１５Ｘ（＝Ｑ／ＣＯＰ1 ）［Ｗ］となり、合計動力は０．２５Ｘ「Ｗ］となる。
【００２２】
一方、１つの蒸気圧縮式冷凍機にてＸ［Ｗ］の冷凍能力を発揮するには、図５に示すように、高圧側圧力が１．１７［ＭＰａ］、低圧側圧力が０．３５［ＭＰａ］であるので、成績係数（ＣＯＰ）は約３．６である。したがって、１つの蒸気圧縮式冷凍機にてＸ［Ｗ］の冷凍能力を発揮するには０．２８Ｘ［Ｗ］必要とするので、本実施形態では約１０％の省動力化を図ることができる。
【００２３】
また、本実施形態では、第１蒸気圧縮冷凍機１１０は、吸着式冷凍機１３０（吸着器１３１ａ、１３１ｂ）の加熱及び冷却のみに使用していることに加えて、吸着状態にある吸着剤Ｓｉが冷却されているので、吸着剤Ｓｉの温度を吸着状態および再生状態のいずれの状態においても、等しい温度とすることができる（図３参照）。
【００２４】
したがって、吸着剤Ｓｉ自体の温度を変化させるに必要な熱量を必要としないので、吸着式冷凍機１３０の効率を向上させることができるので、さらに冷凍装置１００の効率を向上させることができる。
（第２実施形態）
本実施形態は、図６に示すように、第１蒸気圧縮式冷凍機１１０を廃止して蒸気圧縮式冷凍機を１つ（第２蒸気圧縮式冷凍機１２０のみ）とするとともに、吸着式冷凍機１３０の第１吸着器１３２ａを廃止して吸着器を１つ（第２吸着器１３２ｂのみ）としたものである。
【００２５】
そして、吸着状態にある吸着器１３２ｂの冷却作用により凝縮器１２２を冷却する場合と、凝縮器１２２にて発生する熱により吸着剤Ｓｉを加熱して吸着された蒸気冷媒を脱離再生する場合とを一定時間毎に切り替えることにより、疑似的に第１実施形態に係る冷凍装置１００と同等としたものである。なお、本実施形態では、蒸発器１２４と室内に配設された室内熱交換器１４０との間を熱交換媒体（本実施形態では水）を循環させて（ブライン式により）室内空気の冷却を図っている。因みに、１３６ｅ、１３６ｆは水熱交換器１３３ｂと蒸発器１２４との間で熱交換媒体を循環させる場合と、室内熱交換器１４０と蒸発器１２４との間で熱交換媒体を循環させる場合と切り替える四方弁である。
【００２６】
これにより、第１実施形態に係る冷凍装置１００と同等の効果を得ながら、冷凍装置１００の構成を簡素なものとして、冷凍装置１００の製造原価低減を図ることができる。
（第３実施形態）
第２実施形態では、一定時間毎に吸着状態と再生状態とを切り替えて運転するので、再生状態では室内空気を冷却することができない。
【００２７】
そこで、本実施形態では、図７に示すように、熱交換媒体の循環経路（本実施形態では室内熱交換器１４０の下流側）に蓄冷材１５０を配設している。
これにより、再生状態に、第２蒸発器１２４、室内熱交換器１４０および蓄冷材１５０間に熱交換媒体を循環させれば、蓄冷材１５０により室内空気の冷却をすることができる。
【００２８】
なお、蓄冷材１５０は、物質の凝固融解を利用する潜熱蓄冷材であり、本実施形態では、冷房温度（５℃〜１５℃）程度で凝固融解するポリエチレングリコールである。
ところで、上述の実施形態では、吸着剤Ｓｉとしてシリカゲルを用いたが、本発明はこれに限定されるものではなく、吸着剤Ｓｉとして活性炭、ゼオライト、活性アルミナなどを用いてもよい。
【００２９】
また、上述の実施形態では、液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、フロンなど吸着剤Ｓｉに吸着されるものであれば、その他の物であってもよい。
また、上述の実施形態では、圧縮機１１１に液冷媒が吸入されることを防止すべく、アキュームレータ１２５を設けたが、アキュームレータ１２５を廃止して、減圧器１１３として、蒸発器１１４の出口側加熱度を所定値となるように減圧度（開度）を調節する温度式膨張弁を用いてもよい。なお、この場合に、凝縮器１１２の出口側にレシーバを設けてもよい。
【００３０】
また、上述の実施形態では、本発明に係る冷凍装置１００を空調装置に適用したが、本発明に係る冷凍装置は空調装置にその適用が限定されるものではなく、その他の物を冷却する冷凍装置としても適用することができる。
【図面の簡単な説明】
【図１】本発明の第１実施形態に係る冷凍装置において、第１吸着器が吸着状態にある場合の模式図である。
【図２】本発明の第１実施形態に係る冷凍装置において、第２吸着器が吸着状態にある場合の模式図である。
【図３】吸着剤の状態を示す吸着等温線である。
【図４】蒸気圧縮式冷凍機のモリエル線図である。
【図５】蒸気圧縮式冷凍機のモリエル線図である。
【図６】本発明の第２実施形態に係る冷凍装置の模式図である。
【図７】本発明の第３実施形態に係る冷凍装置の模式図である。
【符号の説明】
１１０…第１蒸気圧縮式冷凍機、１１１…第１圧縮機、１１２…第１凝縮器、
１１３…第１減圧器、１１４…蒸発器、１１５…第１アキュームレータ、
１２０…第２蒸気圧縮式冷凍機、１２１…第２圧縮機、１２２…第２凝縮器、
１２３…第２減圧器、１２５…第２アキュームレータ、
１３０…吸着式冷凍機、１３１ａ…第１吸着器、１３１ｂ…第２吸着器、
１３２ａ…第１吸着剤熱交換器、１３２ｂ…第２吸着剤熱交換器、
１３３ａ…第１水熱交換器、１２３ｂ…第２水熱交換器、
１３４…室外熱交換器。[0001]
BACKGROUND OF THE INVENTION
The present invention houses a vapor compression refrigerator that obtains cooling capacity by compressing and evaporating refrigerant, and an adsorbent and liquid refrigerant that adsorb vapor refrigerant in an adsorber that is held in a substantially vacuum (0.1 mmHg). The present invention relates to a refrigeration apparatus combined with an adsorption refrigerator, and is effective when applied to an air conditioner.
[0002]
[Prior art]
As a refrigerating apparatus combining a vapor compression refrigerator and an adsorption refrigerator, there is JP-A-3-186163. The invention described in the above publication seeks to improve the efficiency of regeneration of the adsorption refrigerator (the act of desorbing the vapor refrigerant adsorbed on the adsorbent) by waste heat (condensation heat) of the vapor compression refrigerator. Is.
[0003]
[Problems to be solved by the invention]
However, in a relatively small refrigeration apparatus (such as a general household or small commercial air conditioner), the waste heat temperature from the vapor compression chiller is relatively low (usually about 60 ° C. or less). In this invention, the adsorbent and the liquid refrigerant cannot be raised to a high temperature during regeneration.
[0004]
Therefore, in the invention described in the above publication, since the temperature difference between adsorption and regeneration is relatively small, it is difficult to obtain sufficient refrigeration capacity.
In view of the above points, an object of the present invention is to obtain a sufficient refrigeration capacity with a small amount of power in a refrigeration apparatus in which a vapor compression refrigerator and an adsorption refrigerator are combined.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, the present invention uses the following technical means. In the first aspect of the present invention, a vapor compression refrigerator (120) having a compressor (121), a condenser (122), a decompressor (123) and an evaporator (124), a liquid refrigerant and a vapor refrigerant are provided. An adsorption refrigerator (130) having an adsorber (131b) in which an adsorbent (Si) to be adsorbed is stored, and only one adsorber (131b) is provided and is in an adsorbing state. The condenser (122) is cooled by the cooling action of (131b), and the adsorbent (Si) is heated by the state in which the cooled object is cooled by the evaporator (124) and the heat generated in the condenser (122). with desorbing adsorbed vapor refrigerant then, become switched so that every predetermined time and a reproduction state to condense the cooling effect of the adsorbent evaporator desorbed vapor refrigerant from (Si) (124) And adsorber 131b) is a portion where the adsorbent (Si) is disposed and the adsorbent heat exchanger (132b) for exchanging heat between the adsorbent (Si) and the heat exchange medium, and the portion where the liquid refrigerant is located. A water heat exchanger (133b) for exchanging heat between the liquid refrigerant and the heat exchange medium,
Furthermore, an outdoor heat exchanger (134) for exchanging heat between the heat exchange medium heated by the condenser (122) and outdoor air, a heat exchange medium cooled by the evaporator (124), and an object to be cooled An indoor heat exchanger (40) for exchanging heat, a flow path for circulating a heat exchange medium between the adsorbent heat exchanger (132b) and the outdoor heat exchanger (134), and an adsorbent heat exchanger ( 132b) between the first switching valve (136a, 136b) for switching the flow path for circulating the heat exchange medium between the condenser (122), the water heat exchanger (133b) and the condenser (122). A flow path for circulating the heat exchange medium, and a second switching valve (136c, 136d) for switching the flow path for circulating the heat exchange medium between the water heat exchanger (133b) and the evaporator (124) side, Heat between the evaporator (124) and the indoor heat exchanger (40) Comprising passages for circulating a removable-medium, and an evaporator (124) and the water heat exchanger (133b) and the third switching valve for switching between flow circulating a heat exchange medium passage between the (136e, 136f) and Features a refrigeration system.
[0006]
Thus, it is possible to lower the pressure in the condenser (122) in the vapor compression refrigerating machine (120), vapor compression refrigerating machine (120) of the compressor (121) power (the compression work) Can be reduced. Accordingly, the refrigeration apparatus which combines a steam compression type refrigerator (120) and the adsorption type refrigerating machine (130), it is possible to obtain a sufficient cooling capacity with less power.
[0008]
Furthermore, since only one adsorber (131b) in the adsorption refrigeration machine (130) is provided, the structure of the refrigeration apparatus can be simplified and the manufacturing cost of the refrigeration apparatus can be reduced . In time and, in the invention according to claim 1, since the operation by switching the playback state and adsorbed state at regular time intervals, it may not be possible to cool the object to be cooled is in play mode.
[0009]
In view of this, the invention according to claim 2 is characterized in that the regenerator material (150) cooled by the evaporator (114) is provided, and the regenerator material (150) cools the object to be cooled in the regenerated state. To do. As a result, the indoor air can be cooled by the cold storage material 150 in the regenerated state. As in the third aspect of the present invention, the regenerator material (150) may be a latent heat regenerator material that utilizes solidification and melting of a substance.
[0010]
In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description later mentioned.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
Among the first to third embodiments described below, the embodiments of the invention described in the claims are the second and third embodiments, and the first embodiment is a reference example on which the present invention is based. Show.
(First embodiment)
In the present embodiment, the refrigeration apparatus 100 according to the present invention is applied to an air conditioner that cools a room, and FIG. 1 is a schematic diagram of the refrigeration apparatus 100 according to the present embodiment. In FIG. 1, reference numerals 110 and 120 denote first and second vapor compression refrigerators using chlorofluorocarbon as a refrigerant. As is well known, these first and second vapor compression refrigerators 110 and 120 are first and second compressors. 111, 121, first and second condensers (radiators) 112, 122, first and second decompressors 113, 123, first and second evaporators 114, 124, and first and second accumulators 115, 125. It is configured.
[0012]
Incidentally, the first and second compressors 111 and 121 are driven by an electric motor (not shown), and the number of rotations is controlled by controlling the electric motor, and the first and second pressure reducers 113 and 123 are capillaries. A fixed throttle means such as a tube.
The evaporators 114 and 124 exhibit refrigeration capacity by evaporating the refrigerant. The first and second accumulators 115 and 125 each convert the refrigerant flowing out of the evaporator 114 into a gas phase refrigerant and a liquid phase refrigerant. The gas-phase refrigerant is separated and flows out to the suction side of the first and second compressors 111 and 121.
[0013]
131a and 131b are first and second adsorbers whose interiors are maintained in a substantially vacuum (0.1 mmHg), and in the first and second adsorbers 131a and 131b, a liquid refrigerant (water in this embodiment) Lr. And an adsorbent (silica gel in the present embodiment) Si that adsorbs the evaporated liquid refrigerant (water vapor).
The first and second adsorbent heat exchangers 132a and 132b are disposed at the portion where the adsorbent Si is disposed, and the first and second water heat exchangers are disposed at the portion where the liquid refrigerant Lr is located. 133a and 133b are disposed, and a heat exchange medium (water in this embodiment) circulates in each of the heat exchangers 132a, 132b, 133a, and 133b.
[0014]
Reference numeral 134 denotes an outdoor heat exchanger that is disposed outside and exchanges heat between the heat exchange medium and outdoor air, and 135a to 135d are first to fourth pumps that circulate the heat exchange medium. And the control of the flow state of the heat exchange medium between the heat exchangers 132a, 132b, 133a, 133b, 134, the first and second condensers 112, 122 and the first and second evaporators 114, 124 is performed by This is performed by switching and controlling the four-way valves 136a to 136d. The first to fourth four-way valves 136a to 136d and the first to fourth pumps 135a to 135d are controlled by an electronic control unit (not shown).
[0015]
In this embodiment, the adsorption refrigeration machine 130 includes the first and second adsorbers 131a and 131b and the heat exchangers 132a, 132b, 133a, 133b, and 134.
Next, the operation of the refrigeration apparatus 100 will be described.
FIG. 1 shows a state in which the first adsorber 131a is in an adsorbing state and the second adsorber 131b is in a regenerating state, and the evaporation of the liquid refrigerant Lr proceeds in the first adsorber 131a. The heat exchange medium flowing through the heat exchanger 133a is cooled to cool the second condenser 122.
[0016]
At this time, since the heat exchange medium cooled by the outdoor air in the outdoor heat exchanger 134 is circulating in the first adsorbent heat exchanger 132a, the adsorbent Si is cooled. Therefore, since the temperature rise of the adsorbent Si is suppressed, the decrease in the adsorption capacity of the adsorbent Si is prevented, and the decrease in the cooling capacity of the adsorption refrigeration machine 130 is prevented.
On the other hand, since the heat exchange medium heated by the first condenser 112 flows through the second adsorbent heat exchanger 132b, the adsorbent Si of the second adsorber 131b desorbs the adsorbed water vapor. Further, since the heat exchange medium cooled by the outdoor air in the outdoor heat exchanger 134 is circulated in the second water heat exchanger 133b, the desorbed water vapor is condensed and regenerated.
[0017]
Then, the electronic control device controls the first to fourth four-way valves 136a to 136d to switch at regular intervals so that the two adsorbers 131a and 131b are alternately in the adsorption state and the regeneration state. . Incidentally, FIG. 2 is a schematic diagram when the second adsorber 131b is in an adsorbing state and the first adsorber 131a is in a desorbing state.
FIG. 3 is an adsorption isotherm showing the state of the adsorbent Si in the adsorbers 131a and 131b, and the moisture adsorption rate of the adsorbent Si is shown in FIG. It is determined by the temperature of Lr. The adsorbent Si adsorbs the moisture difference between point A (regenerated state) and point B (adsorbed state), and the latent heat of vaporization corresponding to the amount of adsorbed moisture becomes the refrigeration capacity of the adsorption refrigerator 130.
[0018]
Incidentally, as is apparent from FIG. 3, the time for switching the first to fourth four-way valves 136a to 136d is appropriately determined depending on the type of the adsorbent Si, the particle diameter of the adsorbent Si, the amount of adsorbent Si filled, and the like. Although selected, in this embodiment, the switching is performed about every 2 to 10 minutes.
Next, features of the present embodiment will be described.
[0019]
According to the present embodiment, since the second condenser 122 is cooled by the adsorption refrigerator 130, the pressure in the second condenser 122 can be lowered. Therefore, since the power (compression work) of the second compressor 121 can be reduced, in the refrigeration apparatus 100 that combines the first and second vapor compression refrigeration machines 110 and 120 and the adsorption refrigeration machine 130, less power is required. Can provide sufficient refrigeration capacity.
[0020]
Hereinafter, the features of the present embodiment will be described with specific examples.
The solid line in FIG. 4 is a Mollier diagram of the first vapor compression refrigerator 110, and the broken line in FIG. 4 is a Mollier diagram of the second vapor compression refrigerator 120. As is clear from FIG. 4, the pressure on the high pressure side (first condenser 112 side) of the first vapor compression refrigerator 110 is 0.88 [MPa], and the pressure on the low pressure side (first evaporator 114 side) is Since it is 0.46 [MPa], the coefficient of performance (COP1) is about 7.2. Similarly, the high pressure side (second condenser 122 side) pressure of the second vapor compression refrigerator 120 is 0.59 [MPa], and the low pressure side (second evaporator 124 side) pressure is 0.35 [MPa]. Therefore, the coefficient of performance (COP2) is about 9.9.
[0021]
By the way, in this embodiment, since indoor air (cooled body) is cooled by the second evaporator 124, if the refrigerating capacity required by the second evaporator 124 is X [W], the second The power of the compressor 121 is 0.1X (= X / COP2) [W], and the amount of heat Q generated in the second condenser 122 is {X (1 + 1 / COP2)} [W].
Since the heat quantity Q is equal to the refrigeration capacity of the adsorption refrigerator 130, it becomes equal to the latent heat of vaporization of the water refrigerant in the adsorber (131a) in the adsorption state. This latent heat of vaporization is equivalent to the adsorber (131b in the regeneration state). It is equal to the heat of condensation of the vapor refrigerant at Therefore, the amount of heat Q is equal to the refrigeration capacity of the first vapor compression refrigerator 110, so the power of the first compressor 111 is 0.15X (= Q / COP1) [W], and the total power is 0.25X " W].
[0022]
On the other hand, in order to exhibit the refrigeration capacity of X [W] in one vapor compression refrigerator, as shown in FIG. 5, the high pressure side pressure is 1.17 [MPa] and the low pressure side pressure is 0.35 [MPa]. MPa], the coefficient of performance (COP) is about 3.6. Therefore, since 0.28X [W] is required to exhibit the refrigerating capacity of X [W] with one vapor compression refrigerator, about 10% of power saving can be achieved in this embodiment. .
[0023]
In the present embodiment, the first vapor compression refrigerator 110 is used only for heating and cooling of the adsorption refrigerator 130 (adsorbers 131a and 131b), and in addition, the adsorbent Si in an adsorption state. Since the temperature of the adsorbent Si is cooled, the temperature of the adsorbent Si can be made equal in both the adsorption state and the regeneration state (see FIG. 3).
[0024]
Therefore, since the amount of heat necessary to change the temperature of the adsorbent Si itself is not required, the efficiency of the adsorption refrigerator 130 can be improved, and the efficiency of the refrigeration apparatus 100 can be further improved.
(Second Embodiment)
In the present embodiment, as shown in FIG. 6, the first vapor compression refrigerator 110 is abolished and one vapor compression refrigerator is provided (only the second vapor compression refrigerator 120), and an adsorption refrigeration is performed. The first adsorber 132a of the machine 130 is abolished and one adsorber is provided (only the second adsorber 132b).
[0025]
The adsorbed by heating the adsorbent Si by heat generated when the at coagulation condenser 1 2 2 to cool the adsorber 132 b Rico condenser 1 2 2 by the cooling effect in the adsorption state By switching the case where the vapor refrigerant is desorbed and regenerated at regular intervals, it is equivalent to the refrigeration apparatus 100 according to the first embodiment. In the present embodiment, (the brine type) vapor Hatsuki 124 and between the disposed the indoor heat exchanger 140 into the room (in this embodiment water) heat exchange medium is circulated to cool the room air I am trying. Incidentally, 136e, if 136f is circulating and when circulating a heat exchange medium between the heat exchange medium between the indoor heat exchanger 140 and the vapor Hatsuki 124 with water heat exchanger 133b and vapor Hatsuki 124 It is a four-way valve that switches.
[0026]
Thereby, while obtaining the same effect as the refrigeration apparatus 100 according to the first embodiment, the configuration of the refrigeration apparatus 100 can be simplified, and the manufacturing cost of the refrigeration apparatus 100 can be reduced.
(Third embodiment)
In the second embodiment, since the operation is performed by switching between the adsorption state and the regeneration state at regular time intervals, the indoor air cannot be cooled in the regeneration state.
[0027]
Therefore, in the present embodiment, as shown in FIG. 7, the cold storage material 150 is disposed in the circulation path of the heat exchange medium (in the present embodiment, on the downstream side of the indoor heat exchanger 140).
Thereby, if the heat exchange medium is circulated between the second evaporator 124, the indoor heat exchanger 140, and the cold storage material 150 in the regenerated state, the indoor air can be cooled by the cold storage material 150.
[0028]
The cold storage material 150 is a latent heat storage material that utilizes solidification and melting of a substance, and in this embodiment, it is polyethylene glycol that solidifies and melts at a cooling temperature (5 ° C. to 15 ° C.).
In the above embodiment, silica gel is used as the adsorbent Si. However, the present invention is not limited to this, and activated carbon, zeolite, activated alumina, or the like may be used as the adsorbent Si.
[0029]
In the above-described embodiment, water is used as the liquid refrigerant. However, the present invention is not limited to this, and any other material may be used as long as it can be adsorbed by the adsorbent Si such as alcohol or chlorofluorocarbon. May be.
In the above-described embodiment, the accumulator 125 is provided in order to prevent the liquid refrigerant from being sucked into the compressor 111. However, the accumulator 125 is abolished, and the outlet side heating of the evaporator 114 is performed as the decompressor 113. You may use the temperature type expansion valve which adjusts pressure reduction degree (opening) so that a degree may become a predetermined value. In this case, a receiver may be provided on the outlet side of the condenser 112.
[0030]
In the above-described embodiment, the refrigeration apparatus 100 according to the present invention is applied to an air conditioner. However, the application of the refrigeration apparatus according to the present invention is not limited to the air conditioner, and refrigeration for cooling other objects. It can also be applied as a device.
[Brief description of the drawings]
FIG. 1 is a schematic view when a first adsorber is in an adsorption state in a refrigeration apparatus according to a first embodiment of the present invention.
FIG. 2 is a schematic diagram when the second adsorber is in an adsorption state in the refrigeration apparatus according to the first embodiment of the present invention.
FIG. 3 is an adsorption isotherm showing the state of the adsorbent.
FIG. 4 is a Mollier diagram of a vapor compression refrigerator.
FIG. 5 is a Mollier diagram of a vapor compression refrigerator.
FIG. 6 is a schematic diagram of a refrigeration apparatus according to a second embodiment of the present invention.
FIG. 7 is a schematic diagram of a refrigeration apparatus according to a third embodiment of the present invention.
[Explanation of symbols]
110 ... first vapor compression refrigerator, 111 ... first compressor, 112 ... first condenser,
113 ... 1st decompressor, 114 ... Evaporator, 115 ... 1st accumulator,
120 ... 2nd vapor compression refrigerator, 121 ... 2nd compressor, 122 ... 2nd condenser,
123 ... second decompressor, 125 ... second accumulator,
130 ... Adsorption refrigerator, 131a ... First adsorber, 131b ... Second adsorber,
132a ... first adsorbent heat exchanger, 132b ... second adsorbent heat exchanger,
133a ... 1st water heat exchanger, 123b ... 2nd water heat exchanger,
134: Outdoor heat exchanger.

Claims

A vapor compression refrigerator (120) having a compressor (121), a condenser (122), a decompressor (123) and an evaporator (124);
An adsorption refrigerator (130) having an adsorber (131b) containing an adsorbent (Si) that adsorbs liquid refrigerant and vapor refrigerant;
Only one adsorber (131b) is provided,
The condenser (122) is cooled by the cooling action of the adsorber (131b) in the adsorption state, and the cooled object is cooled by the evaporator (124), and generated in the condenser (122). The adsorbent (Si) is heated by the generated heat to desorb the adsorbed vapor refrigerant, and the vapor refrigerant desorbed from the adsorbent (Si) is condensed by the cooling action of the evaporator (124). has become the switching so that the state at regular time intervals,
The adsorber (131b) is provided at a site where the adsorbent (Si) is disposed, and adsorbent heat exchanger (132b) for exchanging heat between the adsorbent (Si) and a heat exchange medium, and A water heat exchanger (133b) provided at a position where the liquid refrigerant is located to exchange heat between the liquid refrigerant and the heat exchange medium;
And an outdoor heat exchanger (134) for exchanging heat between the heat exchange medium heated by the condenser (122) and outdoor air;
An indoor heat exchanger (40) for exchanging heat between the heat exchange medium cooled by the evaporator (124) and the object to be cooled;
A flow path for circulating a heat exchange medium between the adsorbent heat exchanger (132b) and the outdoor heat exchanger (134), and the adsorbent heat exchanger (132b) and the condenser (122). A first switching valve (136a, 136b) for switching a flow path for circulating the heat exchange medium between
A flow path for circulating a heat exchange medium between the water heat exchanger (133b) and the condenser (122), and between the water heat exchanger (133b) and the evaporator (124) side. A second switching valve (136c, 136d) for switching the flow path for circulating the heat exchange medium;
A flow path for circulating a heat exchange medium between the evaporator (124) and the indoor heat exchanger (40), and heat between the evaporator (124) and the water heat exchanger (133b). A refrigeration apparatus comprising a third switching valve (136e, 136f) for switching between a flow path for circulating the exchange medium .

A regenerator (150) cooled by the evaporator (114);
The regenerator material (150), refrigeration system according to claim 1, characterized in that cooling the cooled body when the playback state.

The refrigerating apparatus according to claim 2 , wherein the regenerator material (150) is a latent heat regenerator material that utilizes solidification and melting of a substance.