JP3816872B2 - Operation control method of refrigeration system with two evaporators - Google Patents

Operation control method of refrigeration system with two evaporators Download PDF

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Publication number
JP3816872B2
JP3816872B2 JP2002379190A JP2002379190A JP3816872B2 JP 3816872 B2 JP3816872 B2 JP 3816872B2 JP 2002379190 A JP2002379190 A JP 2002379190A JP 2002379190 A JP2002379190 A JP 2002379190A JP 3816872 B2 JP3816872 B2 JP 3816872B2
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temperature
cycle
chamber
fan
refrigeration system
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JP2004037065A (en
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ウイ ヨップ ジョン
セ ヨン キム
ギョン シキ キム
テ ヒ リ
ヤン ギュ キム
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エルジー電子株式会社
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Priority claimed from KR10-2002-0038701A external-priority patent/KR100480706B1/en
Priority claimed from KR10-2002-0038704A external-priority patent/KR100474910B1/en
Priority claimed from KR1020020038703A external-priority patent/KR20040003876A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D29/00—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2511—Evaporator distribution valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/12—Sensors measuring the inside temperature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B40/00—Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers

Description

【０００１】
【発明の属する技術分野】
本発明は、冷凍システムの運転を制御する方法に関し、特に、２つの蒸発器を備えた冷凍システムの運転制御方法に関するものである。
【０００２】
【従来の技術】
一般に、冷蔵庫は食品を新鮮に長期間保管する用途に用いられる機器であって、その構成は大きく複数の食品保管室を有する本体と、前記食品保管室を冷却するための冷凍サイクルから分けられる。
【０００３】
冷凍サイクルを構成する主要構成要素としては、圧縮機、凝縮器、蒸発器、膨張バルブがある。一般的に、圧縮機と凝縮器は本体の後方下部に設けられた機械室内に取り付けられ、蒸発器と膨張バルブは食品保管室の近傍に取り付けられ、次のような段階を介して本体の食品保管室を冷却する。
【０００４】
先ず、気相の冷媒が圧縮機で圧縮されて凝縮器に圧送された後、凝縮器で熱交換して液化される。凝縮された液相の冷媒は膨張バルブで蒸発器に噴射されながら急膨張して気化する。この時、蒸発器の周囲から熱を吸収してその冷気によって食品保管室を冷却する。気化した冷媒は再び圧縮機に戻って圧縮、液化された後、前記凝縮、膨張、気化、圧縮段階を繰り返しながら食品保管室を常に低温状態に冷却する。
【０００５】
尚、冷蔵庫の冷凍システムは、１つの蒸発器で複数の食品保管室に冷気を供給するように構成されることもあるが、最近は各食品保管室の特性を生かし、冷却性能を向上させるために複数の蒸発器を食品保管室の各々に取り付けて制御するように構成されることもある。
【０００６】
このように、複数の蒸発器を備えた冷凍システム（以下説明の便宜のため２つの蒸発器を備えた冷凍システムと称する）は、圧縮機と凝縮器を経由した冷媒が流通する冷媒配管が、２つの蒸発器（Ｆ−蒸発器とＲ−蒸発器）に各々連結され得るように分岐され、その分岐点に両分岐管の流路を開閉できるバルブ装置が取り付けられている。従って、前記バルブ装置を切り換えることにより、冷媒をＦ−蒸発器とＲ−蒸発器の何れか一方に流入するようにすることで、２つの食品保管室の何れか一つを選択して冷却することができる。
【０００７】
このような２つの蒸発器が備えられている冷凍システムは、一般的に全ての食品保管室の温度が、制御部に予め設定されている条件を満たすと、圧縮機の動作を中止、全ての食品保管室の何れか１つの温度が、制御部に設定されている温度範囲以上に上昇したときに、圧縮機を更に動作させる方法で運転されている。このような運転を繰り返しながら、各貯蔵室の温度を制御部に予め設定されている温度範囲内に維持する。
【０００８】
然しながら、前記冷凍システムを有する冷蔵庫では、２つの蒸発器の何れか一方の蒸発器にだけ冷媒を供給する方式で各室の温度を制御するので各室の温度偏差が大きくなる。即ち、何れか一方の蒸発器に冷媒が供給されるときには他の蒸発器には冷媒が供給されず、また冷気を供給するファンも停止するので、当室内の冷気循環が中止されることによって蒸発器の稼動時と停止時の食品冷凍室内の温度偏差が大きくなるという問題がある。
【０００９】
また、既述した２つの蒸発器を備えた冷凍システムでは、２つの蒸発器の何れか一方の蒸発器に冷媒を供給するサイクルを行った後、バルブ装置を切り換えて更に他の１つの蒸発器に冷媒を供給する他のサイクルを行う場合、冷媒の供給を底止した蒸発器内に既に流入している冷媒が残留するという問題がある。
【００１０】
即ち、Ｆ−蒸発器に冷媒を供給しながらＦ−サイクルをおこなった後、バルブ装置を切り換えてＲ−蒸発器に供給しながらＲ−サイクルをおこなった場合、Ｆ−蒸発器に既に流入している冷媒は、Ｒ−サイクルが行われる間、流動せず殆ど液相でＦ−蒸発器に残留する。
【００１１】
このような現象は、Ｒ−サイクルの中止及び圧縮機の動作中止時にも同様に発生するので、蒸発器に残留する冷媒を回収するための別の装置や方法を適用しない場合には、２つの蒸発器の何れか一方の蒸発器には常に冷媒が残留する。
【００１２】
従って、１つのサイクルが完了した後、蒸発器に残留する冷媒を圧縮機及び凝縮器に全量回収できないので、更に他の１つのサイクルを行う時、冷媒不足の現象が発生し、このような現象によって冷却性能が相対的に低下するという問題がある。
【００１３】
また、圧縮機を更に動作させるとき、蒸発器に残留する液相の冷媒が圧縮機に流入することとなり、圧縮機のシリンダー内での潤滑の問題が発生し、圧縮機の信頼性が確保できないという問題がある。
【００１４】
【発明が解決しようとする課題】
本発明は、こうした従来技術の問題点を解決することを技術課題としており、２つの蒸発器を備えた冷凍システムを有する冷蔵庫で、各食品保管室の温度偏差を減少させることが目的である。
【００１５】
本発明の他の目的は、２つの蒸発器を備えた冷凍システムにおいて冷凍サイクルの切り換え時に蒸発器に残留する冷媒を回収して、冷媒不足を防止し、更に圧縮機の信頼性を確保することである。
本発明の更に異なる目的は、２つの蒸発器を備えた冷凍システムの冷却性能を向上させることである。
【００１６】
【課題を解決するための手段】
上記目的を達成するために、本発明による方法は（ｃ）各室の温度を測定する段階と、（ｄ）測定された各室の温度を比較する段階と、（ｅ）各室の温度比較結果に基づき各室の蒸発器に流入する冷媒量を調節する段階含む。
ここで、段階（ｃ）は各室に取り付けられている温度センサーによって行われ、前記基準温度は、上限温度と下限温度を含むことが好ましい。
【００１７】
段階（ｅ）における各室の蒸発器に流れ込む冷媒量の調節は、前記各室の蒸発器に連結される冷媒管の分岐点に取り付けられているバルブ装置の開放比率の調節を介してなされ、各室の温度が全て前記上限温度以上の場合、前記バルブ装置の開放比率は５０％：５０％で、各室の温度が下限温度以上の温度領域で同一である場合、前記バルブ装置の開放比率は５０％：５０％で、下限温度以上の温度領域で各室の何れか１室の温度が他の室より高い場合、前記バルブ装置は相対的に高い温度を有する室の蒸発器側が更に多く開放されるように制御され、また、何れか１室の温度だけが下限値の温度未満の場合、前記バルブ装置は高い温度を有する室の蒸発器側に冷媒の全量が流入するように制御され、各室の温度が下限温度未満の場合、圧縮機の運転が停止することが好ましい。
【００１８】
また、前記本発明の他の特徴によれば、（ｂ）各室毎に複数の温度領域を設定する段階と、（ｃ）各室の温度を測定する段階と、（ｄ）測定された各室の温度を比較する段階と、また、（ｅ）各室の温度比較結果に基づき各室の蒸発器に流入する冷媒量を調節する段階とを含む方法が提供される。
【００１９】
ここで、段階（ｃ）は、各室に各々取り付けられている温度センサーによって行われ、前記温度領域は、上限温度以上の温度領域（Ａｎ温度領域）、上限温度未満で設定値温度以上の温度領域（Ｂｎ温度領域）、設定値温度未満で下限温度以上の温度領域（Ｃｎ温度領域）、下限温度未満の温度領域（Ｄｎ温度領域）を含んでおり、前記測定された各室の温度を比較する段階（ｄ）は測定された各室の温度を前記温度領域と比較する方法で行われることが好ましい。
【００２０】
また、段階（ｅ）における各室の蒸発器に流入する冷媒量の調節は、前記各室の蒸発器に連結される冷媒管の分岐点に取り付けられているバルブ装置の開放比率調節を介してなされるが、各室の温度領域が互いに同一の場合、前記バルブ装置は同一比率で開放され、この時、前記バルブ装置の開放比率は５０％：５０％で、また各室の温度が全てＤｎ温度領域に属する場合、圧縮機の運転が停止され、各室の何れか１室の温度領域だけがＤｎ温度領域に属する場合、前記バルブ装置の開放比率は、０％：１００％（Ｄｎ温度領域に属する室側：他の温度領域に属する室側）であり、各室の何れか１室の温度領域がＡｎ温度領域に属し、他の１室がＣｎ温度領域に属する場合、前記バルブ装置の開放比率は１００％：０％（Ａｎ温度領域に属する室側：Ｃｎ温度領域に属する室側）であり、各室の何れか１室の温度領域がＢｎ温度領域に属し、他の１室がＡｎ温度領域またはＣｎ温度領域に属する場合、前記バルブ装置は相対的に高い温度の温度領域に属する室側が更に多く開放されるように制御されることが望ましく、この時、前記バルブ装置の開放比率は８０％：２０％（高い温度の温度領域に属する室側：低い温度の温度領域に属する室側）であることが好ましい。
【００２１】
前記目的を達成するための本発明の更に他の特徴によれば、（ｆ）凝縮器を経た冷媒が、Ｆ−膨張装置とＦ−蒸発器とを順次的に流動するＦ−サイクルから、バルブ装置の制御によって、Ｒ−膨張装置とＲ−蒸発器とを順次に流動するＲ−サイクルに転換されるとき、所定時間（Δｔ）の間、前記バルブ装置を閉鎖した状態で前記圧縮機を運転する段階を含む方法が提供される。
【００２２】
段階（ｆ）を行う時、Ｆ−ファンを共に回転させる段階を含むことが望ましく、段階（ｆ）を行う時、凝縮器ファンを共に回転させる段階を含むことが好ましい。
【００２３】
更に、本発明の他の特徴によれば、（ｇ）凝縮器を経た冷媒がＦ−膨張装置とＦ−蒸発器とを順次に流動するＦ−サイクルと、Ｒ−膨張装置とＲ−蒸発器とを順次に流動するＲ−サイクルとの何れか一方のサイクルが完了した時、所定時間（Δｔ）の間、前記バルブ装置を閉鎖した状態で前記圧縮機を運転する段階を含んだ方法が提供される。
【００２４】
ここで、段階（ｇ）を行う時、当該ファンを回転させる段階を含むことが望ましく、また、段階（ｇ）を行う時、凝縮器ファンを共に回転させる段階を含むことが好ましい。
【００２５】
本発明の更に他の特徴によれば、凝縮器を経た冷媒がＦ−膨張装置とＦ−蒸発器とを順次的に流動するＦ−サイクルと、Ｒ−膨張装置とＲ−蒸発器とを順次に流動するＲ−サイクルとの何れか一方のサイクルが完了した時、所定時間（Δｔ）の間、前記バルブ装置を閉鎖した状態で前記圧縮機を運転する段階と、また、前記圧縮機の運転が停止した後にも、Ｆ−ファンとＲ−ファンを各々断続的に運転する段階を含む方法が提供される。
【００２６】
ここで、前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを断続的に運転する段階を包含したり、前記Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われる時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間延長運転する段階を包含したり、前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間延長運転する段階を包含したり、前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間延長運転した後断続的に運転する段階を包含することが好ましい。この時、前記Ｆ−ファン及びＲ−ファンが運転され停止される断続時間比は４：６であることが好ましい。
【００２７】
本発明の他の特徴によれば、Ｆ−サイクルまたはＲ−サイクルを選択的に行う冷凍システムの圧縮機の運転が停止した後にもＦ−ファンとＲ−ファンを各々断続的に運転する段階を包む方法が提供される。
【００２８】
ここで、前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、停止した更に１つの冷凍サイクルに属する蒸発器のファンを断続的に運転する段階を包含したり、前記Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われる時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間延長運転する段階を包含したり、前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間延長運転した後、断続的に運転する段階を包含することが好ましい。この時、前記Ｆ−ファン及びＲ−ファンが運転され停止される断続時間比は４：６であることが好ましい。
【００２９】
【発明の実施の形態】
以下、添付図面を参照して本発明を更に詳細に説明する。
実施形態の説明において、各部と同様の構成を有する部分には同一の符号を付しており、これによる付加説明は省略する。
【００３０】
図１を参照すると、本発明が適用される冷却システムは圧縮機１、凝縮器２、バルブ装置３、２つの膨張装置１１、２１及び２つの蒸発器１２、２２を具備している。
【００３１】
凝縮器２の冷媒吐出側に連結された冷媒管は二つに分岐され、その分岐点には制御部（図示せず）からの制御によって各分岐管の冷媒流路を多様な比率で各々開放できるバルブ装置３が取り付けられている。
【００３２】
バルブ装置３を起点に分岐された各分岐管は、第１室１０に配設されたＦ−膨張装置１１と、第２室に配設されたＲ−膨張装置２１に各々連結される。
第１室１０には、Ｆ−蒸発器１２がＦ−膨張装置１１に連結されており、Ｆ−ファン１２ａがＦ−蒸発器１２に向かって取り付けられている。
【００３３】
また、第２室２０には、Ｒ−蒸発器２２がＲ−膨張装置２１に連結されており、Ｒ−ファン２２ａがＲ−蒸発器２２に向かって取り付けられている。
また、第１室１０と第２室２０には、各室の温度を測定するための温度センサー１３、２３が各々設置されており、これらは制御部と電気的に連結され測定された情報を制御部に伝える。
【００３４】
Ｆ−蒸発器１２とＲ−蒸発器２２の各吐出側の冷媒管は圧縮機１に連結されている。
このように構成された冷却システムは、本発明の種々の実施形態による方法により運転が制御され、各実施形態による詳細な説明は次の通りである。
【００３５】
第１実施形態
図２を参照すると、本発明の第１実施形態は、第１室１０と第２室２０について独立に複数の基準温度を設定する段階（Ｓ−００）、第１室１０と第２室２０の温度を測定する段階（Ｓ−１０）、測定された第１室１０と第２室２０の温度を比較する段階（Ｓ−２０）、また、第１室１０と第２室２０の温度比較結果を基準にＦ−蒸発器１２側とＲ−蒸発器２２側に各々流入する冷媒量を調節する段階（Ｓ−３０）を含む。
【００３６】
ここで、段階（Ｓ−１０）は、各温度センサー１３、２３によって行われ、測定された温度は制御部に伝送される。また、段階（Ｓ−２０）は制御部で行われるが、前記基準温度は上限温度と下限温度を含む。この時、前記上限温度と下限温度は第１室１０と第２室２０とで同一に設定することもできるが、一般的に第１室１０は冷凍室に用いられ、第２室２０は冷蔵室に用いられるので、各室の基準温度は互に異なる値を設定するのが好ましい。
【００３７】
また、段階（Ｓ−３０）で、Ｆ−蒸発器１２側とＲ−蒸発器２２側に各々流入する冷媒量の調節は、第１室１０と第２室２０の温度比較結果を基準にして、制御部がバルブ装置３の開放比率を調節することでなされるが、その詳細な開放比率を図３を参照して説明すると次のとおりである。
【００３８】
図３を参照すると、第１室１０と第２室２０の温度が上限温度以上の場合、または、第１室１０と第２室２０の温度が下限温度以上の温度領域で同一の場合には、バルブ装置３の開放比率は第１室側：第２室側が５０％：５０％に設定されており、Ｆ−蒸発器１２側とＲ−蒸発器２２側の両側に同一量の冷媒を流入させることになる。
【００３９】
また、第１室１０と第２室２０の温度が下限温度以上の温度領域に属し、何れか１室の温度が他の室より高い場合、バルブ装置３は相対的に高い温度を有する室の蒸発器側が更に多く開放されるように制御される。
【００４０】
即ち、図３に示すように、第１室が上限温度未満で下限温度以上の温度領域（ｂ１）に属し、第２室２０が上限温度以上の温度領域（ａ２温度領域）に属する場合は、バルブ装置３が第１室１０側より第２室側に多く開くように制御される。また、第１室と第２室が上限温度未満で下限温度以上の温度領域（ｂ１温度領域、ｂ２温度領域）に属する場合、バルブ装置３の温度が相対的に高い側に更に多く開放されるように制御される。
【００４１】
但し、このうち、第１室と第２室が、上限温度以上の温度領域に属する場合、バルブ装置の温度が相対的に高い側に更に多く開放されるように制御されることも良いが、図３に示すように、バルブ装置の開放比率を互いに同一に制御するのが更に好ましい。
【００４２】
また、第１室と第２室の何れか１室の温度だけが下限温度未満の場合、バルブ装置３は高い温度を保持している室の蒸発器側に冷媒の全量を流入させるように制御される。即ち、図３に示すように、第１室の温度が下限温度未満の温度領域であり、第２室の温度が下限値以上の温度領域（ｂ１、ａ１温度領域）に属する場合、バルブ装置３は第２室２０のＲ−蒸発器２２側に冷媒の全量を流入させるように制御する。第１室１０と第２室２０の温度が前記と反対の場合、第１室１０のＦ−蒸発器１２側に冷媒の全量が流入するように、バルブ装置３が制御される。
【００４３】
また、第１室と第２室の温度が、下限温度未満の温度領域（ｃ１、ｃ２温度領域）に属する場合、圧縮機１の運転が停止されて、Ｆ−蒸発器１２側やＲ−蒸発器２２側に全て冷媒を供給しないようになる。
【００４４】
第１実施形態の作用を簡略に整理すると次のとおりである。
冷凍システムの運転が開始されると、圧縮機１が起動し、冷媒は高温高圧の気体状態に圧縮されて凝縮器２へ輸送される。凝縮器２に供給された気相の冷媒は、凝縮器ファン２ａによって送風される空気との熱交換により液化される。液化された冷媒は冷媒管を介してバルブ装置３へ輸送される。
【００４５】
尚、第１室と第２室の温度センサー１３、２３は、各々室の温度を測定して制御部に伝送する。制御部では測定された各室の温度を比較した後、図３を参照して記述した方法に従いバルブ装置の開放比率を制御する。
【００４６】
バルブ装置３の開放を通じて流量が制御された冷媒は、Ｆ−膨張装置１１及びＲ−膨張装置２１で膨張した後、Ｆ−蒸発器１２及びＲ−蒸発器２２で各室の室内機と熱交換される。また、Ｆ−ファン１２ａ及びＲ−ファン２２ａによって各室に冷気が供給され各室が冷却される。
【００４７】
第１室と第２室が下限温度未満になると、圧縮機１の運転が中止され、所定時間経過後、第１室と第２室の何れか１室の温度が下限温度以上に上昇すると、圧縮機１が起動し前記段階を繰り返して、第１室と第２室を常に所定温度範囲内に維持する。
【００４８】
このような本発明の第１実施形態は、各室の温度偏差を減少させ最小化でき、各室の温度をより安定的に維持できる効果がある。
従って、本発明の第１実施形態が適用された冷蔵庫は各室に保管される食品の固有の味を一層長期間維持でき、食品保管の信頼性が更に向上される。
【００４９】
尚、各室の温度によって各蒸発器に供給される冷媒分配量を制御することを核心的な技術思想とする本発明の第１実施形態は次のように変形された実施形態によっても実現できる。
【００５０】
第１実施形態の変形実施形態
図４を参照すると、本発明の第１実施形態の変形実施形態は、第１室１０と、第２室２０とについて独立の複数の温度領域を設定する段階（Ｓ−０５）、第１室１０と、第２室の温度を測定する段階（Ｓ−１０）、測定された第１室と第２室２０の温度を比較する段階（Ｓ−２０）、および、第１室と第２室の温度比較結果を基準に、Ｆ−蒸発器１２側とＲ−蒸発器２２側に各々流入する冷媒量を調節する段階（Ｓ−３０）とを含んでいる。
【００５１】
ここで、段階（Ｓ−１０）は温度センサー１３、２３によって各々行われ、測定された温度は制御部に伝送される。また、段階（Ｓ−２０）は制御部で行われるが、前記温度領域は、上限温度以上の温度領域（Ａｎ温度領域）、上限温度未満で設定値温度以上の温度領域（Ｂｎ温度領域）、設定値温度未満で下限温度以上の温度領域（Ｃｎ温度領域）、下限温度未満の温度領域（Ｄｎ温度領域）を含む。
ここでｎは各室を識別するために付す任意の番号である。
【００５２】
尚、前記各温度領域は第１室と第２室が互いに同一に設定され得るが、一般的に第１室は冷凍室で使用し、第２室は冷蔵室で使用されるので各室の温度領域は互に異なって設定されるのが好ましい。
【００５３】
また、段階（Ｓ−２０）は測定された各室の温度を前記温度領域と比較する方法で行われる。この比較結果に基づき、段階（Ｓ−３０）で、Ｆ−蒸発器１２側とＲ−蒸発器２２側に各々流入する冷媒量を調節する。このような冷媒量の調節は、制御部がバルブ装置３の開放比率を調節することで成されるが、その詳細な開放比率は図５を参照して説明する。
【００５４】
図５を参照すると、第１室と、第２室の温度領域が互いに同一の場合、バルブ装置３は同一比率で開放されるが、この時、バルブ装置３の開放比率は５０％：５０％であることが好ましい。即ち、第１室と第２室が、Ａｎ温度領域に属したり、Ｂｎ温度領域に属したり、或いは、Ｃｎ温度領域に属する場合、バルブ装置３の開放比率は５０％：５０％に同一に開放して、Ｆ−蒸発器１２側とＲ−蒸発器２２側に各々同一量の冷媒が流入するようにする。
尚、図５に示すように、第１室１０と第２室の温度領域がＤｎ温度領域に属する場合は圧縮機１の運転が停止する。
【００５５】
また、第１室１０と第２室２０の何れか１室の温度領域だけがＤｎ温度領域に属する場合、バルブ装置３は、Ｄｎ温度領域の属する室側と、他の温度領域に属する室側との開放比率が０％：１００％になるように制御される。即ち、第１室１０だけがＤ１温度領域に属する場合は、第１室１０のＦ−蒸発器１２側に冷媒の全量を流入させ、第２室２０だけがＤ２温度領域に属する場合、第２室２０のＲ−蒸発器２２側に冷媒の全量を流入させることになる。
【００５６】
また、第１室１０と第２室２０の何れか１室の温度領域がＡｎ温度領域に属し、他の室の温度領域がＣｎ温度領域に属する場合、バルブ装置３は、Ａｎ温度領域に属する室側と、Ｃｎ温度領域に属する室側との開放比率が１００％：０％になるように制御される。即ち、図５に示すように、第１室１０がＡ１温度領域に属し、第２室２０がＣ２温度領域に属する場合、バルブ装置３は、第１室１０のＦ−蒸発器１２側に冷媒の全量が流入するように制御され、反対の場合は第２室２０のＲ−蒸発器２２側に冷媒の全量が流入するようにバルブ装置３が制御される。
【００５７】
また、第１室１０と第２室の何れか１室の温度領域がＢｎ温度領域に属し、他の１室がＡｎ温度領域またはＣｎ温度領域に属する場合、バルブ装置３は相対的に高い温度領域に属する室側が更に多く開放されるように制御される。
【００５８】
この時の好ましい開放比率は８０％：２０％（高い温度の温度領域に属する室側：低い温度の温度領域に属する室側）であるが、場合によって７０％：３０％や、６０％：４０％の開放比率でも制御され得る。
【００５９】
更に詳しくは、図５に示すように、第１室がＢ１温度領域に属し、第２室がＡ２温度領域に属する場合、また第１室１０がＣ１温度領域に属し、第２室２０がＢ２温度領域に属する場合は、第２室２０が第１室より高い温度領域に属するので、バルブ装置３は、第１室１０のＦ−蒸発器１２側より第２室２０のＲ−蒸発器側に更に多くの量の冷媒を流入させるように制御される。勿論、第１室がＡ１温度領域に属し、第２室がＢ２温度領域に属する場合、または、第１室がＢ１温度領域に属し、第２室がＣ２温度領域に属する場合、第１室の温度が第２室の温度より高い温度領域に属するので、バルブ装置３は、第２室のＲ−蒸発器側より第１室のＦ−蒸発器１２側に更に多くの量の冷媒を流入させるように制御される。
【００６０】
前記のような方法で冷媒の流動を制御する本発明の第１実施形態の変形実施形態における作用は、本発明の第１実施形態における作用と同一であり、その効果もまた同一であるので、その説明は省略する。
【００６１】
第２実施形態
本発明の第２実施形態は、凝縮器２を経た冷媒がＦ−膨張装置１１とＦ−蒸発器１２とを順次に流動するＦ−サイクルから、バルブ装置３の制御によって、Ｒ−膨張装置２１とＲ−蒸発器２２とを順次に流動するＲ−サイクルに転換する時、所定時間（Δｔ）の間バルブ装置３を閉鎖した状態で圧縮機１を運転する段階を含んでいる。
【００６２】
ここで所定時間（Δｔ）の間バルブ装置３を閉鎖し圧縮機１を運転する時、Ｆ−ファン１２ａを共に回転させてＦ−蒸発器１２内に残留した冷媒を蒸発させる段階を備えることが好ましい。また、バルブ装置３を閉鎖しながら圧縮機１を運転するときに、凝縮器２を冷却する凝縮器ファン２ａを共に回転させる段階を備えることが更に好ましい。
【００６３】
このような方法で冷凍システムの運転を制御する本発明の第２実施形態を、図１及び図６を参照して説明する。
冷凍システムの運転が開始されると、圧縮機１が起動し、冷媒は高温高圧の気体状態に圧縮されて凝縮器２へ輸送される。凝縮器２に供給された気相の冷媒は凝縮器ファン２ａによって送風される空気との熱交換により液化される。
【００６４】
液化された冷媒は冷媒管を介してバルブ装置３へ向かって流動する。バルブ装置は制御部によって冷媒の流動方向を決定する。この時、バルブ装置の切換によって、冷媒がＦ−膨張装置１１とＦ−蒸発器１２に流入されれば、Ｆ−サイクルが行われる。Ｆ−サイクルが行われる間、冷媒は、Ｆ−膨張装置で膨張された後、Ｆ−蒸発器１２で蒸発しながら熱交換して周囲の熱を吸収する。またＦ−ファン１２ａによって冷気が供給され第１室が冷却される。Ｆ−蒸発器１２を経由した冷媒は更に圧縮機１に流入して上記の各段階を繰り返す。
【００６５】
尚、Ｆ−サイクルが行われる間、図６に示すように、Ｆ−蒸発器１２側にバルブ装置３が開放され、圧縮機１とＦ−ファン１２ａ及び凝縮器ファン２ａが作動する。凝縮器ファン２ａは一般的に凝縮器２と圧縮機１を共に冷却する。
【００６６】
既述したように、Ｆ−サイクルが行われた後に、バルブ装置が所定時間（Δｔ）の間完全に閉鎖された状態で、圧縮機１が動作する。そうすると、バルブ装置３の閉鎖と共に冷媒の流動が停止し、Ｆ−膨張装置１１とＦ−蒸発器１２内に残留する冷媒が圧力差によって圧縮機１と凝縮器２側に全量流入する。この時、図６に示すように、Ｆ−ファン１２ａを共に回転させて、Ｆ−蒸発器１２内に残留する冷媒を蒸発させると共に、持続的に冷気を第１室１０内に供給する。
【００６７】
これによって、Ｆ−サイクルが停止した後にもＦ−蒸発器１２内に残っている冷気を用いて、持続的に第１室１０を冷却可能となるのみならず、気化した冷媒を容易に圧縮機１に回収できる。
【００６８】
所定時間（Δｔ）の間前記方法で運転した後、バルブ装置３をＲ−蒸発器２２側に切り換えてＲ−サイクルを行う。Ｒ−サイクルの実行時の冷媒流動はＦ−サイクル実行時に対応しているので説明を省略する。
但し、Ｒ−サイクルが行われる間、バルブ装置３がＲ−蒸発器２２側に開放され、圧縮機１が作動し、Ｒ−ファン２２ａと凝縮器ファン２ａが回転する。
【００６９】
本発明の第２実施形態では、前記方法でＦ−蒸発器１２内に残留する冷媒を全量回収して圧縮機１と凝縮器２に貯蔵した後、Ｒ−サイクルが行われるので、Ｒ−サイクルが行われる時も冷媒の全量を使用することができ、従来の冷媒不足の発生を完全に防止することができる。
【００７０】
更に、Ｒ−サイクル開始直後に、Ｆ−蒸発器１２から回収した冷媒をＲ−蒸発器２２側により迅速に供給できるので、Ｒ−サイクルがより早期に正常状態に至り、冷凍システムの冷却性能を更に向上させることができる。
【００７１】
尚、Ｒ−サイクルが完了し圧縮機１が停止した後にも、前記と同一の方法で所定時間運転することにより、Ｆ−サイクルが開始される時も同一の作用が得られる。本発明の第２実施形態の変形実施形態によれば、全てのサイクルを実行した後、冷媒回数作業が行われる。その内容を図と図７を参照して説明する。
【００７２】
第２実施形態の変形実施形態
図４を参照すると、本発明の第２実施形態の変形実施形態は、凝縮器２を経た冷媒がＦ−膨張装置１１とＦ−蒸発器１２とを順次に流動するＦ−サイクルと、Ｒ−膨張装置２１とＲ−蒸発器２２とを順次的に流動するＲ−サイクルとの何れか一方のサイクルが完了した時、所定時間（Δｔ）の間、バルブ装置３を閉鎖した状態で圧縮機１を作動させる段階を含んでいる。
【００７３】
ここで、バルブ装置３を閉鎖し圧縮機１を運転する時にＦ−ファン１２ａとＲ−ファン２２ａのうち、対応の何れか一方のファンを共に回転させる段階を含むことが好ましい。また、バルブ装置３を閉鎖し圧縮機１を運転するときに、凝縮器ファン２ａを共に回転させる段階を含むことが好ましい。
【００７４】
このような方法から成される本発明の第２実施形態の変形実施形態の具体的な作用は第２実施形態と同一であるので省略する。但し、本発明の第２実施形態の変形実施形態では、Ｆ−サイクルとＲ−サイクルのうち何れか一方のサイクルが完了した後にも、バルブ装置３が閉鎖され圧縮機１が作動することになる。また、圧縮機１が停止された後に再起動するとき、圧縮機内に液相の冷媒が流入しないので圧縮機の信頼性が確保される。
【００７５】
前記方法から成されている本発明の第２実施形態、および、その変形実施形態には次のような利点がある。
第一に、冷凍システムの何れかの１つのサイクルが完了した後、当該サイクルの蒸発器に残留する冷媒を圧縮機と凝縮器に回収することで、他のサイクルを行う際に冷媒不足が生じない。
【００７６】
第二に、１つのサイクルが完了した後にも当該蒸発器のファンを回転させるので、食品保管室に冷気を持続的に供給でき、熱効率が向上され、冷媒の回収を加速化できる。
【００７７】
第三に、１つのサイクルが完了した後に、蒸発器に冷媒が残留することを防止できるので、圧縮機の再起動時に液相の冷媒が流入せず、液圧縮による圧縮損失を防止できる。従って、圧縮機の信頼性が確保される。
第四に、同一容量の冷凍システムでも相対的に少量の冷媒を用いることができる。
【００７８】
第３実施形態
本発明の第３実施形態は、凝縮器２を経た冷媒がＦ−膨張装置１１とＦ−蒸発器１２とを順次的に流動するＦ−サイクルから、バルブ装置３の制御によって、冷媒がＲ−膨張装置２１とＲ−蒸発器２２とを順次に流動するＲ−サイクルに切り換える時、所定時間（Δｔ）の間、バルブ装置３を閉鎖した状態で圧縮機１を運転する段階と、圧縮機１の運転が停止した後にもＦ−ファン１２ａとＲ−ファン２２ａを各々断続的に運転する段階とを含んでいる。
【００７９】
このような方法で成された本発明の第３実施形態において、蒸発器に残留している冷媒を回収する方法は、第２実施形態と同様であるのでその説明は省略し、圧縮機の停止後、Ｆ−ファン１２ａとＲ−ファン２２ａを断続的に作動させる段階を中心に図１と図８を参照して説明する。
【００８０】
図８は、典型的な形態の２つの蒸発器を備えた冷凍システムによる、ある冷凍サイクルを示しており、該サイクルではＦ−サイクルが完了した後に、連続してＲ−サイクルに運転され、その後一定時間の間、圧縮機１が停止し、冷凍サイクルが行われないようになっている。然しながら、本発明は図８に示す冷凍サイクルに限定されず、図８の冷凍サイクルは単なる一例であることは理解されよう。
【００８１】
先ず圧縮機１が起動しＦ−サイクルが行われる間、Ｆ−ファン１２ａは連続的に回転して、Ｆ−蒸発器１２に流入した冷媒を気化させながら第１室１０を冷却する。
【００８２】
また、Ｒ−サイクルに切り換えてＲ−サイクルが行われる間、Ｒ−ファン２２ａは連続的に回転して、Ｒ−蒸発器２２に流入した冷媒を気化させながら第２室２０を冷却する。
【００８３】
Ｒ−サイクルの実行が完了したとき、圧縮機１が停止する。このように圧縮機が停止したとき、Ｆ−ファン１２ａとＲ−ファン２２ａを一定時間の周期で断続的に回転させて各サイクルが行われない間にも各蒸発器に残っている冷気を各室に吐き出して各室を冷却する。
【００８４】
このような方法で運転することにより、冷凍システムが停止した状態でも各蒸発器に残っている冷気を用いて各室を冷却可能となる。即ち、圧縮機１が停止すると蒸発器１２、２２には冷媒が流入しないが、蒸発器１２、２２の周囲の温度は各室の温度より低いので、各ファンにより冷気を各室に供給して冷却性能を向上し、各室内の温度偏差を低減可能となるので、食品保管の信頼性を向上させることができる。
【００８５】
また、各蒸発器に冷媒が供給されない間にファンを回転させて蒸発器に残留する冷媒を完全に気化させることによって、圧縮機１の再起動時液相の冷媒が圧縮機１に流入することを防止することができる。
【００８６】
尚、第３実施形態ではＦ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われる時、停止された他の１つの冷凍サイクルに属する蒸発器のファンを断続的に運転する段階を更に含むことが好ましい。即ち、図８に示すように、圧縮機１が停止している間だけではなく、Ｆ−サイクルが行われる間にも、Ｒ−ファン２２ａを断続的に回転させるものである。同様に、圧縮機１の停止時だけではなくＲ−サイクルの実行時にも、Ｆ−ファン１２ａを断続的に回転させる。このように運転すると冷却性能が更に向上する。
【００８７】
また、第３実施形態の方法は、好ましくは、Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間延長運転する段階を更に含んでいる。即ち、図８に示すように、Ｆ−サイクルが完了した後、所定時間（ｔ１）の間Ｆ−ファン１２ａを延長して運転しながら冷気を第１室１０に吐き出し、Ｒ−サイクルが完了した後、所定時間（ｔ２）の間、Ｒ−ファン２２ａを運転しながら冷気を第１室１０に吐き出すものである。これは各サイクルが行われた直後にはサイクルが行われる時と殆ど同一水準の冷気が当該蒸発器の周囲にあるので該冷気を各室に吐き出して冷却性能を向上させるためである。
【００８８】
また、本発明の第３実施形態ではＦ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われ、完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間延長運転した後断続的に運転する段階を含むことが好ましい。即ち、図８に示すように、Ｆ−サイクルが完了した後にはＦ−ファン１２ａが所定時間延長運行された後断続運転されＲ−サイクルが完了した後にはＲ−ファン２２ａが所定時間（ｔ２）延長運行された後断続運転されるものである。
【００８９】
既述したように、断続運転されるＦ−ファン１２ａ及びＲ−ファン２２ａの断続時間比、即ち、運転される時間と停止される時間の比率は４：６であることが好ましい。即ち、１０分を１周期に断続運転する時、各ファンは４分の間回転し、６分の間停止させることが好ましい。然しながら、かかる比率は冷凍システムの容量や、製品の設計目的によって変更できる。尚、既述したようにＦ−ファン１２ａとＲ−ファン２２ａが断続的に運転される理由は、各ファンを回転させるモータの寿命及び使用電力を考慮したためである。
【００９０】
尚、本発明の第３実施形態において、圧縮機の停止時に各ファンを断続的に運転する方法は、第２実施形態において開示されている運転制御方法と独立的に構成されて冷凍システムに適用され得る。
本発明による第４実施形態を図１及び図９を参照して説明する。
【００９１】
第４実施形態
図９を参照すると、本発明の第４実施形態は、Ｆ−サイクルまたはＲ−サイクルを選択的に行う冷凍システムの圧縮機１の運転が停止した後にも、Ｆ−ファン１２ａとＲ−ファン２２ａを各々断続的に運転する段階を含んでいる。
【００９２】
また、本発明の第４実施形態は、Ｆ−サイクルまたはＲ−サイクルの何れか一方の冷凍サイクルが行われる時、停止している他の１つの冷凍サイクルに属する蒸発器のファンを断続的に運転する段階を更に含むことが好ましい。
【００９３】
また、本発明の第４実施形態は、Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われ完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間（ｔ３、ｔ４）の間、延長運転する段階を更に含むことが好ましい。
【００９４】
また、本発明の第４実施形態は、Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われ完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間、延長運転した後、断続的に運転する段階を含むことが好ましい。この時、Ｆ−ファン及びＲ−ファンが運転、停止される断続時間比は４：６であることが好ましい。
【００９５】
前記方法でなされている本発明の第４実施形態の更に詳しい内容は、既に第３実施形態で開示されているのでその説明は省略する。
図９に示すように、第４実施形態はサイクル運行の先後と無関係に、Ｒ−サイクルとＦ−サイクルを選択的に運転する全ての冷凍システムに適用できる。
【００９６】
本発明の第４実施形態による冷却システムの運転制御方法は次のような利点がある。
第一に、圧縮機を停止した後にも、各ファンを断続的に回転させることによって各蒸発器に残っている冷気を各室に供給するので、各室の内部温度偏差を低減可能で、食品保管の信頼性が向上される。
【００９７】
第二に、各蒸発器に残っている冷気を全て利用可能であるので、冷却効率が向上し、各室の温度上昇速度を低減可能である。従って、実質的に圧縮機の運転時間が短縮される。
【００９８】
第三に、冷媒の流動を停止した後にも、各蒸発器内に残留している冷媒を各ファンが気化させるので、圧縮機を再起動させるとき液相の冷媒が圧縮機に流入することが防止され、これによって圧縮機の信頼性が向上される。
【００９９】
以上、本発明の好適な一実施形態を説明したが、本発明は既述の実施形態に限定されるわけではなく、本発明の技術思想に基づいて種々の変形または変更が可能である。
【０１００】
【発明の効果】
以上説明したように、本発明の２つの蒸発器を備えた冷凍システムの運転制御方法によれば以下のような効果を奏する。
第一に、各室の温度偏差を減少させ最小化でき、各室の温度をより安定的に維持できる。従って、食品保管の信頼性が一層向上する。
【０１０１】
第二に、冷凍システムの何れか一方のサイクルが完了した後、他のサイクルを行うとき冷媒不足現象が発生しない。
第三に、冷凍サイクルの熱効率が向上され、実質的に圧縮機の運転時間が短縮される。
【０１０２】
第四に、蒸発器に冷媒が残留することを防止できるので圧縮機の再起動時、液相冷媒が流入されず液圧縮による圧損が防止できる。
第五に、同一容量の冷凍システムでも相対的に小さい量の冷媒を用いることができる。
【図面の簡単な説明】
【図１】２つの蒸発器を備えた冷凍システムの概略的な構成図である。
【図２】本発明の第１実施形態による冷凍システムの運転制御方法を示すフローチャートである。
【図３】本発明の第１実施形態による冷凍システムの運転制御方法で各室の温度別バルブ装置の開放比率を示す表である。
【図４】本発明の第１実施形態の変形例による冷凍システムの運転制御方法を示すフローチャートである。
【図５】本発明の第１実施形態の変形実施形態による冷凍システムの運転制御方法において各室の温度領域別バルブ装置の開放比率を示す表である。
【図６】本発明の第２実施形態による冷凍システムの運転制御方法を示す線図である。
【図７】本発明の第２実施形態の変形例による冷凍システムの運転制御方法を示す線図である。
【図８】本発明の第３実施形態による冷凍システムの運転制御方法を示す線図である。
【図９】本発明の第４実施形態による冷凍システムの運転制御方法を示す線図である。
【符号の説明】
１…圧縮機
２…凝縮器
３…バルブ装置
１０…第１室
１１…Ｆ−膨張装置
１２…Ｆ−蒸発器
１３…温度センサー
２０…第２室
２１…Ｒ−膨張装置
２２…Ｒ−蒸発器
２３…温度センサー[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a method for controlling the operation of a refrigeration system, and more particularly, to an operation control method for a refrigeration system including two evaporators.
[0002]
[Prior art]
In general, a refrigerator is a device used for freshly storing food for a long period of time, and its structure is largely divided from a main body having a plurality of food storage rooms and a refrigeration cycle for cooling the food storage rooms.
[0003]
As main components constituting the refrigeration cycle, there are a compressor, a condenser, an evaporator, and an expansion valve. Generally, the compressor and the condenser are installed in a machine room provided at the lower rear of the main body, and the evaporator and the expansion valve are installed in the vicinity of the food storage room. Cool storage room.
[0004]
First, a gas-phase refrigerant is compressed by a compressor and pumped to a condenser, and then liquefied by exchanging heat with the condenser. The condensed liquid phase refrigerant is rapidly expanded and vaporized while being injected into the evaporator by the expansion valve. At this time, the food storage room is cooled by absorbing heat from the periphery of the evaporator. The vaporized refrigerant returns to the compressor and is compressed and liquefied, and then the food storage room is always cooled to a low temperature while repeating the condensation, expansion, vaporization, and compression steps.
[0005]
The refrigerator refrigeration system may be configured to supply cold air to a plurality of food storage rooms with a single evaporator. Recently, in order to improve the cooling performance by taking advantage of the characteristics of each food storage room. In addition, a plurality of evaporators may be installed and controlled in each of the food storage rooms.
[0006]
As described above, a refrigeration system including a plurality of evaporators (referred to as a refrigeration system including two evaporators for convenience of explanation below) includes a refrigerant pipe through which refrigerant flows through a compressor and a condenser. The branching device is branched so as to be connected to two evaporators (F-evaporator and R-evaporator), and a valve device capable of opening and closing the flow paths of both branch pipes is attached to the branching point. Therefore, by switching the valve device, the refrigerant flows into one of the F-evaporator and the R-evaporator to select and cool one of the two food storage rooms. be able to.
[0007]
Such a refrigeration system equipped with two evaporators generally stops the operation of the compressor when the temperature of all food storage rooms satisfies the conditions preset in the control unit, When the temperature of any one of the food storage rooms rises above the temperature range set in the control unit, the compressor is operated in such a way as to further operate. While repeating such operation, the temperature of each storage chamber is maintained within a temperature range preset in the control unit.
[0008]
However, in the refrigerator having the refrigeration system, since the temperature of each chamber is controlled by supplying the refrigerant only to one of the two evaporators, the temperature deviation of each chamber increases. That is, when the refrigerant is supplied to one of the evaporators, the refrigerant is not supplied to the other evaporators, and the fan that supplies the cold air is also stopped. There is a problem that the temperature deviation in the food freezer compartment during operation and stoppage of the container increases.
[0009]
Further, in the refrigeration system including the two evaporators described above, after performing a cycle of supplying the refrigerant to one of the two evaporators, the valve device is switched to another one evaporator. When the other cycle of supplying the refrigerant is performed, there is a problem that the refrigerant already flowing into the evaporator that has stopped supplying the refrigerant remains.
[0010]
That is, after performing the F-cycle while supplying the refrigerant to the F-evaporator and then switching the valve device and performing the R-cycle while supplying the R-evaporator, the flow has already flowed into the F-evaporator. The remaining refrigerant does not flow and remains in the F-evaporator in almost liquid phase during the R-cycle.
[0011]
Such a phenomenon also occurs when the R-cycle is stopped and when the operation of the compressor is stopped. Therefore, when another device or method for recovering the refrigerant remaining in the evaporator is not applied, The refrigerant always remains in one of the evaporators.
[0012]
Therefore, after the completion of one cycle, the refrigerant remaining in the evaporator cannot be recovered in its entirety in the compressor and the condenser. Therefore, when another one cycle is performed, a refrigerant shortage phenomenon occurs. Therefore, there is a problem that the cooling performance is relatively lowered.
[0013]
Further, when the compressor is further operated, the liquid-phase refrigerant remaining in the evaporator flows into the compressor, causing a problem of lubrication in the cylinder of the compressor, and the reliability of the compressor cannot be secured. There is a problem.
[0014]
[Problems to be solved by the invention]
An object of the present invention is to solve such problems of the prior art, and an object of the present invention is to reduce a temperature deviation of each food storage room in a refrigerator having a refrigeration system including two evaporators.
[0015]
Another object of the present invention is to collect refrigerant remaining in the evaporator at the time of switching between refrigeration cycles in a refrigeration system having two evaporators, to prevent refrigerant shortage, and to further ensure the reliability of the compressor. It is.
A further object of the present invention is to improve the cooling performance of a refrigeration system with two evaporators.
[0016]
[Means for Solving the Problems]
To achieve the above object, the method according to the present invention comprises (c) measuring the temperature of each chamber, (d) comparing the measured temperature of each chamber, and (e) comparing the temperature of each chamber. Adjusting the amount of refrigerant flowing into the evaporator of each chamber based on the results.
Here, the step (c) is performed by a temperature sensor attached to each chamber, and the reference temperature preferably includes an upper limit temperature and a lower limit temperature.
[0017]
Adjustment of the amount of refrigerant flowing into the evaporator of each chamber in step (e) is made through adjustment of the opening ratio of the valve device attached to the branch point of the refrigerant pipe connected to the evaporator of each chamber, When the temperature of each chamber is all equal to or higher than the upper limit temperature, the opening ratio of the valve device is 50%: 50%, and when the temperature of each chamber is the same in the temperature range equal to or higher than the lower limit temperature, the opening ratio of the valve device Is 50%: 50%, and if the temperature of any one of the chambers is higher than the other chambers in the temperature range above the lower limit temperature, the valve device has more evaporators in the chamber having a relatively high temperature. When the temperature of any one of the chambers is less than the lower limit temperature, the valve device is controlled so that the entire amount of refrigerant flows into the evaporator side of the chamber having a high temperature. , If the temperature of each chamber is less than the lower limit temperature, compress It is preferred that the operation is stopped.
[0018]
According to another aspect of the present invention, (b) a step of setting a plurality of temperature regions for each chamber, (c) a step of measuring the temperature of each chamber, and (d) each measured Comparing the chamber temperatures, and (e) adjusting the amount of refrigerant flowing into the evaporator of each chamber based on the temperature comparison result of each chamber is provided.
[0019]
Here, the step (c) is performed by a temperature sensor attached to each chamber, and the temperature region is a temperature region above the upper limit temperature (An temperature region), a temperature below the upper limit temperature and above the set temperature. It includes a region (Bn temperature region), a temperature region (Cn temperature region) that is less than the set temperature and above the lower limit temperature, and a temperature region (Dn temperature region) that is less than the lower limit temperature, and compares the measured temperatures of the respective chambers. The step (d) is preferably performed by a method of comparing the measured temperature of each chamber with the temperature range.
[0020]
Further, the adjustment of the amount of refrigerant flowing into the evaporator of each chamber in the step (e) is performed by adjusting the opening ratio of the valve device attached to the branch point of the refrigerant pipe connected to the evaporator of each chamber. However, when the temperature regions of the chambers are the same, the valve devices are opened at the same ratio. At this time, the opening ratio of the valve devices is 50%: 50%, and the temperatures of the chambers are all Dn. When belonging to the temperature region, the operation of the compressor is stopped, and when only the temperature region of any one of the chambers belongs to the Dn temperature region, the opening ratio of the valve device is 0%: 100% (Dn temperature region) If the temperature region of any one of the chambers belongs to the An temperature region and the other chamber belongs to the Cn temperature region, the valve device of the valve device The open ratio is 100%: 0% (belonging to the An temperature range) When the chamber side is a chamber side belonging to the Cn temperature region, and one of the chambers belongs to the Bn temperature region, and the other chamber belongs to the An temperature region or the Cn temperature region, the valve device Is preferably controlled so that more chamber sides belonging to a relatively high temperature region are opened, and at this time, the opening ratio of the valve device is 80%: 20% (belonging to a high temperature region). Room side: The room side belonging to a low temperature region is preferable.
[0021]
According to still another aspect of the present invention to achieve the above object, (f) the F-cycle in which the refrigerant that has passed through the condenser sequentially flows through the F-expansion device and the F-evaporator, When the apparatus is controlled to switch to the R-cycle in which the R-expansion device and the R-evaporator sequentially flow, the compressor is operated with the valve device closed for a predetermined time (Δt). There is provided a method comprising the steps of:
[0022]
When performing step (f), it is desirable to include rotating the F-fan together, and preferably when performing step (f), rotating the condenser fan together.
[0023]
Further, according to another aspect of the present invention, (g) an F-cycle in which the refrigerant that has passed through the condenser sequentially flows through the F-expansion device and the F-evaporator, an R-expansion device, and an R-evaporator A method is provided which includes a step of operating the compressor with the valve device closed for a predetermined time (Δt) when one of the R-cycle and the R-cycle flowing in sequence is completed. Is done.
[0024]
Here, when performing step (g), it is desirable to include a step of rotating the fan, and when performing step (g), it is preferable to include a step of rotating the condenser fan together.
[0025]
According to still another aspect of the present invention, the F-cycle in which the refrigerant having passed through the condenser sequentially flows through the F-expansion device and the F-evaporator, and the R-expansion device and the R-evaporator sequentially. When one of the R-cycle flowing in the cylinder is completed, the compressor is operated with the valve device closed for a predetermined time (Δt), and the compressor is operated. A method is provided including the step of intermittently operating the F-fan and the R-fan, respectively, even after the stop.
[0026]
Here, when the refrigeration cycle of any one of the F-cycle and the R-cycle is completed, the method includes intermittently operating an evaporator fan belonging to the refrigeration cycle, When any one of the refrigeration cycles of the R-cycle is performed, the method includes a step of extending the fan of the evaporator belonging to the refrigeration cycle for a predetermined time, or any one of the F-cycle and the R-cycle. When one refrigeration cycle is completed, including a step of extending the operation of the evaporator fan belonging to the refrigeration cycle for a predetermined time, or when one of the F-cycle and the R-cycle is completed Preferably, the method includes the step of intermittently operating the fan of the evaporator belonging to the refrigeration cycle after extending the operation for a predetermined time. At this time, it is preferable that the intermittent time ratio at which the F-fan and the R-fan are operated and stopped is 4: 6.
[0027]
According to another aspect of the present invention, the step of intermittently operating the F-fan and the R-fan after the operation of the compressor of the refrigeration system that selectively performs the F-cycle or the R-cycle is stopped. A method of wrapping is provided.
[0028]
Here, when the refrigeration cycle of any one of the F-cycle and the R-cycle is completed, the method further includes a step of intermittently operating the evaporator fan belonging to one more refrigeration cycle stopped, When any one of the F-cycle and the R-cycle is performed, it includes a step of extending the evaporator fan belonging to the refrigeration cycle for a predetermined time, or includes the F-cycle and the R-cycle. When any one of the refrigeration cycles is completed, it is preferable to include a step of intermittently operating the evaporator fan belonging to the refrigeration cycle after extending the operation for a predetermined time. At this time, it is preferable that the intermittent time ratio at which the F-fan and the R-fan are operated and stopped is 4: 6.
[0029]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings.
In the description of the embodiment, the same reference numerals are given to portions having the same configurations as the respective portions, and additional description thereof will be omitted.
[0030]
Referring to FIG. 1, a cooling system to which the present invention is applied includes a compressor 1, a condenser 2, a valve device 3, two expansion devices 11 and 21, and two evaporators 12 and 22.
[0031]
The refrigerant pipes connected to the refrigerant discharge side of the condenser 2 are branched into two, and at the branch points, the refrigerant flow paths of the respective branch pipes are opened at various ratios by control from a control unit (not shown). A possible valve device 3 is attached.
[0032]
Each branch pipe branched from the valve device 3 is connected to an F-expansion device 11 disposed in the first chamber 10 and an R-expansion device 21 disposed in the second chamber, respectively.
In the first chamber 10, an F-evaporator 12 is connected to an F-expansion device 11, and an F-fan 12 a is attached toward the F-evaporator 12.
[0033]
In the second chamber 20, an R-evaporator 22 is connected to an R-expansion device 21, and an R-fan 22 a is attached toward the R-evaporator 22.
The first chamber 10 and the second chamber 20 are provided with temperature sensors 13 and 23 for measuring the temperature of each chamber, and these are electrically connected to the control unit to display the measured information. Tell the control unit.
[0034]
The refrigerant pipes on the discharge sides of the F-evaporator 12 and the R-evaporator 22 are connected to the compressor 1.
The cooling system thus configured is controlled in operation by methods according to various embodiments of the present invention, and the detailed description of each embodiment is as follows.
[0035]
First embodiment
Referring to FIG. 2, in the first embodiment of the present invention, a plurality of reference temperatures are set independently for the first chamber 10 and the second chamber 20 (S-00), and the first chamber 10 and the second chamber 20 are set. Measuring the temperature of the first chamber 10 (S-10), comparing the measured temperature of the first chamber 10 and the second chamber 20 (S-20), and comparing the temperature of the first chamber 10 and the second chamber 20 A step (S-30) of adjusting the amount of refrigerant flowing into each of the F-evaporator 12 side and the R-evaporator 22 side based on the result is included.
[0036]
Here, the step (S-10) is performed by the temperature sensors 13 and 23, and the measured temperature is transmitted to the control unit. In addition, the step (S-20) is performed by the control unit, and the reference temperature includes an upper limit temperature and a lower limit temperature. At this time, the upper limit temperature and the lower limit temperature may be set to be the same in the first chamber 10 and the second chamber 20, but generally the first chamber 10 is used as a freezer and the second chamber 20 is refrigerated. Since it is used for a room, it is preferable to set different values for the reference temperature of each room.
[0037]
In addition, in the step (S-30), the adjustment of the refrigerant amount respectively flowing into the F-evaporator 12 side and the R-evaporator 22 side is adjusted based on the temperature comparison result between the first chamber 10 and the second chamber 20. The control unit adjusts the opening ratio of the valve device 3. The detailed opening ratio will be described with reference to FIG.
[0038]
Referring to FIG. 3, when the temperature of the first chamber 10 and the second chamber 20 is equal to or higher than the upper limit temperature, or when the temperature of the first chamber 10 and the second chamber 20 is the same in the temperature range equal to or higher than the lower limit temperature. The opening ratio of the valve device 3 is set to 50%: 50% on the first chamber side: second chamber side, and the same amount of refrigerant flows into both sides of the F-evaporator 12 side and the R-evaporator 22 side. I will let you.
[0039]
In addition, when the temperature of the first chamber 10 and the second chamber 20 belongs to a temperature range equal to or higher than the lower limit temperature, and the temperature of any one of the chambers is higher than the other chambers, the valve device 3 is a chamber having a relatively high temperature. Control is performed so that the evaporator side is further opened.
[0040]
That is, as shown in FIG. 3, when the first chamber belongs to a temperature region (b1) lower than the upper limit temperature and higher than the lower limit temperature, and the second chamber 20 belongs to a temperature region higher than the upper limit temperature (a2 temperature region), Control is performed so that the valve device 3 opens more to the second chamber side than to the first chamber 10 side. Further, when the first chamber and the second chamber belong to a temperature region (b1 temperature region, b2 temperature region) that is lower than the upper limit temperature and equal to or higher than the lower limit temperature, the valve device 3 is further opened to a relatively high temperature side. To be controlled.
[0041]
However, among these, when the first chamber and the second chamber belong to a temperature region equal to or higher than the upper limit temperature, the valve device may be controlled so as to be further opened to a relatively high side, As shown in FIG. 3, it is more preferable to control the opening ratios of the valve devices to be the same.
[0042]
Further, when only the temperature of one of the first chamber and the second chamber is lower than the lower limit temperature, the valve device 3 is controlled so that the entire amount of refrigerant flows into the evaporator side of the chamber holding the high temperature. Is done. That is, as shown in FIG. 3, when the temperature of the first chamber is a temperature region below the lower limit temperature and the temperature of the second chamber belongs to a temperature region (b1, a1 temperature region) equal to or higher than the lower limit value, the valve device 3 Controls so that the entire amount of the refrigerant flows into the R-evaporator 22 side of the second chamber 20. When the temperature of the first chamber 10 and the second chamber 20 is opposite to the above, the valve device 3 is controlled so that the entire amount of the refrigerant flows into the F-evaporator 12 side of the first chamber 10.
[0043]
Further, when the temperatures of the first chamber and the second chamber belong to a temperature region (c1, c2 temperature region) lower than the lower limit temperature, the operation of the compressor 1 is stopped and the F-evaporator 12 side or the R-evaporation is performed. The refrigerant is not supplied to the container 22 side.
[0044]
The operation of the first embodiment is briefly described as follows.
When the operation of the refrigeration system is started, the compressor 1 is activated, and the refrigerant is compressed into a high-temperature and high-pressure gas state and transported to the condenser 2. The gas-phase refrigerant supplied to the condenser 2 is liquefied by heat exchange with the air blown by the condenser fan 2a. The liquefied refrigerant is transported to the valve device 3 through the refrigerant pipe.
[0045]
In addition, the temperature sensors 13 and 23 of the first chamber and the second chamber measure the temperature of each chamber and transmit it to the control unit. The control unit compares the measured temperatures of the chambers, and then controls the opening ratio of the valve device according to the method described with reference to FIG.
[0046]
The refrigerant whose flow rate is controlled through the opening of the valve device 3 expands in the F-expansion device 11 and the R-expansion device 21, and then exchanges heat with the indoor unit in each chamber by the F-evaporator 12 and the R-evaporator 22. Is done. Moreover, cold air is supplied to each chamber by the F-fan 12a and the R-fan 22a to cool each chamber.
[0047]
When the first chamber and the second chamber are below the lower limit temperature, the operation of the compressor 1 is stopped, and after a predetermined time has elapsed, when the temperature of either the first chamber or the second chamber rises above the lower limit temperature, The compressor 1 is started and the above steps are repeated, so that the first chamber and the second chamber are always maintained within a predetermined temperature range.
[0048]
Such a 1st embodiment of the present invention can reduce and minimize the temperature deviation of each room, and has the effect of maintaining the temperature of each room more stably.
Therefore, the refrigerator to which the first embodiment of the present invention is applied can maintain the unique taste of the food stored in each room for a longer period of time, and the reliability of food storage is further improved.
[0049]
It should be noted that the first embodiment of the present invention whose core technical idea is to control the distribution amount of refrigerant supplied to each evaporator according to the temperature of each chamber, can also be realized by an embodiment modified as follows. .
[0050]
Modified embodiment of the first embodiment
Referring to FIG. 4, in a modified embodiment of the first embodiment of the present invention, a plurality of independent temperature regions are set for the first chamber 10 and the second chamber 20 (S-05), the first chamber. 10, the step of measuring the temperature of the second chamber (S-10), the step of comparing the measured temperature of the first chamber and the second chamber 20 (S-20), and the first chamber and the second chamber The step (S-30) of adjusting the refrigerant | coolant amount which each flows in into the F-evaporator 12 side and the R-evaporator 22 side on the basis of the temperature comparison result of this is included.
[0051]
Here, the step (S-10) is performed by the temperature sensors 13 and 23, respectively, and the measured temperature is transmitted to the controller. Further, the step (S-20) is performed by the control unit, and the temperature region is a temperature region above the upper limit temperature (An temperature region), a temperature region below the upper limit temperature and above the set temperature (Bn temperature region), It includes a temperature range (Cn temperature range) that is lower than the set temperature and is equal to or higher than the lower limit temperature, and a temperature range (Dn temperature range) that is lower than the lower limit temperature.
Here, n is an arbitrary number assigned to identify each room.
[0052]
The first chamber and the second chamber can be set to be the same as each other in the temperature range. Generally, the first chamber is used in the freezer and the second chamber is used in the refrigerator. The temperature regions are preferably set differently from each other.
[0053]
Further, the step (S-20) is performed by comparing the measured temperature of each chamber with the temperature range. Based on the comparison result, in step (S-30), the refrigerant amounts respectively flowing into the F-evaporator 12 side and the R-evaporator 22 side are adjusted. Such adjustment of the refrigerant amount is performed by the control unit adjusting the opening ratio of the valve device 3, and the detailed opening ratio will be described with reference to FIG.
[0054]
Referring to FIG. 5, when the temperature regions of the first chamber and the second chamber are the same, the valve device 3 is opened at the same ratio. At this time, the opening ratio of the valve device 3 is 50%: 50%. It is preferable that That is, when the first chamber and the second chamber belong to the An temperature region, the Bn temperature region, or the Cn temperature region, the opening ratio of the valve device 3 is equally opened to 50%: 50%. Thus, the same amount of refrigerant flows into the F-evaporator 12 side and the R-evaporator 22 side.
In addition, as shown in FIG. 5, when the temperature region of the first chamber 10 and the second chamber belongs to the Dn temperature region, the operation of the compressor 1 is stopped.
[0055]
Further, when only one of the first chamber 10 and the second chamber 20 belongs to the Dn temperature region, the valve device 3 includes the chamber side to which the Dn temperature region belongs and the chamber side to which the other temperature region belongs. The release ratio is controlled to be 0%: 100%. That is, when only the first chamber 10 belongs to the D1 temperature region, the entire amount of the refrigerant flows into the F-evaporator 12 side of the first chamber 10, and when only the second chamber 20 belongs to the D2 temperature region, The entire amount of refrigerant flows into the R-evaporator 22 side of the chamber 20.
[0056]
Further, when the temperature region of one of the first chamber 10 and the second chamber 20 belongs to the An temperature region and the temperature region of the other chamber belongs to the Cn temperature region, the valve device 3 belongs to the An temperature region. The open ratio between the room side and the room side belonging to the Cn temperature region is controlled to be 100%: 0%. That is, as shown in FIG. 5, when the first chamber 10 belongs to the A1 temperature region and the second chamber 20 belongs to the C2 temperature region, the valve device 3 has a refrigerant on the F-evaporator 12 side of the first chamber 10. In the opposite case, the valve device 3 is controlled so that the entire amount of refrigerant flows into the R-evaporator 22 side of the second chamber 20.
[0057]
Further, when the temperature range of any one of the first chamber 10 and the second chamber belongs to the Bn temperature range and the other chamber belongs to the An temperature range or the Cn temperature range, the valve device 3 has a relatively high temperature. Control is performed so that more room sides belonging to the area are opened.
[0058]
A preferable open ratio at this time is 80%: 20% (the room side belonging to the high temperature range: the room side belonging to the low temperature range), but in some cases 70%: 30% or 60%: 40 % Open ratio can also be controlled.
[0059]
More specifically, as shown in FIG. 5, when the first chamber belongs to the B1 temperature region and the second chamber belongs to the A2 temperature region, the first chamber 10 belongs to the C1 temperature region, and the second chamber 20 belongs to the B2 temperature region. When belonging to the temperature region, the second chamber 20 belongs to a higher temperature region than the first chamber, so that the valve device 3 is located on the R-evaporator side of the second chamber 20 from the F-evaporator 12 side of the first chamber 10. It is controlled to allow a larger amount of refrigerant to flow into. Of course, if the first chamber belongs to the A1 temperature range and the second chamber belongs to the B2 temperature range, or if the first chamber belongs to the B1 temperature range and the second chamber belongs to the C2 temperature range, Since the temperature belongs to a temperature region higher than the temperature of the second chamber, the valve device 3 causes a larger amount of refrigerant to flow from the R-evaporator side of the second chamber to the F-evaporator 12 side of the first chamber. To be controlled.
[0060]
Since the operation in the modified embodiment of the first embodiment of the present invention that controls the flow of the refrigerant by the method as described above is the same as the operation in the first embodiment of the present invention, the effect is also the same. The description is omitted.
[0061]
Second embodiment
In the second embodiment of the present invention, the R-expansion device 21 is controlled by the control of the valve device 3 from the F-cycle in which the refrigerant having passed through the condenser 2 sequentially flows through the F-expansion device 11 and the F-evaporator 12. And the R-evaporator 22 are switched to an R-cycle that sequentially flows, and the compressor 1 is operated with the valve device 3 closed for a predetermined time (Δt).
[0062]
Here, when the valve device 3 is closed for a predetermined time (Δt) and the compressor 1 is operated, a step of rotating the F-fan 12a together to evaporate the refrigerant remaining in the F-evaporator 12 is provided. preferable. Further, it is further preferable to provide a step of rotating together the condenser fan 2a for cooling the condenser 2 when the compressor 1 is operated while the valve device 3 is closed.
[0063]
A second embodiment of the present invention for controlling the operation of the refrigeration system by such a method will be described with reference to FIGS. 1 and 6.
When the operation of the refrigeration system is started, the compressor 1 is activated, and the refrigerant is compressed into a high-temperature and high-pressure gas state and transported to the condenser 2. The gas-phase refrigerant supplied to the condenser 2 is liquefied by heat exchange with the air blown by the condenser fan 2a.
[0064]
The liquefied refrigerant flows toward the valve device 3 through the refrigerant pipe. The valve device determines the flow direction of the refrigerant by the control unit. At this time, if the refrigerant flows into the F-expansion device 11 and the F-evaporator 12 by switching the valve device, the F-cycle is performed. During the F-cycle, the refrigerant is expanded by the F-expansion device and then exchanges heat while evaporating in the F-evaporator 12 to absorb ambient heat. In addition, cold air is supplied by the F-fan 12a to cool the first chamber. The refrigerant passing through the F-evaporator 12 further flows into the compressor 1 and repeats the above steps.
[0065]
During the F-cycle, as shown in FIG. 6, the valve device 3 is opened on the F-evaporator 12 side, and the compressor 1, the F-fan 12a, and the condenser fan 2a are operated. The condenser fan 2a generally cools the condenser 2 and the compressor 1 together.
[0066]
As described above, after the F-cycle is performed, the compressor 1 operates in a state where the valve device is completely closed for a predetermined time (Δt). Then, when the valve device 3 is closed, the flow of the refrigerant is stopped, and the refrigerant remaining in the F-expansion device 11 and the F-evaporator 12 flows into the compressor 1 and the condenser 2 side by the pressure difference. At this time, as shown in FIG. 6, the F-fan 12 a is rotated together to evaporate the refrigerant remaining in the F-evaporator 12 and continuously supply cool air into the first chamber 10.
[0067]
Accordingly, not only can the first chamber 10 be continuously cooled using the cold air remaining in the F-evaporator 12 even after the F-cycle is stopped, but the vaporized refrigerant can be easily removed from the compressor. 1 can be recovered.
[0068]
After operating by the above method for a predetermined time (Δt), the valve device 3 is switched to the R-evaporator 22 side to perform the R-cycle. The refrigerant flow at the time of execution of the R-cycle corresponds to that at the time of execution of the F-cycle, and thus description thereof is omitted.
However, during the R-cycle, the valve device 3 is opened to the R-evaporator 22 side, the compressor 1 operates, and the R-fan 22a and the condenser fan 2a rotate.
[0069]
In the second embodiment of the present invention, since the refrigerant remaining in the F-evaporator 12 is entirely collected and stored in the compressor 1 and the condenser 2 by the above method, the R-cycle is performed. The total amount of the refrigerant can be used even when the operation is performed, and the conventional shortage of refrigerant can be completely prevented.
[0070]
Further, immediately after the start of the R-cycle, the refrigerant recovered from the F-evaporator 12 can be quickly supplied to the R-evaporator 22 side, so that the R-cycle reaches a normal state earlier and the cooling performance of the refrigeration system is improved. Further improvement can be achieved.
[0071]
Even after the R-cycle is completed and the compressor 1 is stopped, the same operation can be obtained when the F-cycle is started by operating for a predetermined time in the same manner as described above. According to the modified embodiment of the second embodiment of the present invention, the refrigerant frequency work is performed after all the cycles have been executed. The contents will be described with reference to FIGS.
[0072]
Modified embodiment of the second embodiment
Referring to FIG. 4, a modified embodiment of the second embodiment of the present invention includes an F-cycle in which the refrigerant that has passed through the condenser 2 sequentially flows through the F-expansion device 11 and the F-evaporator 12, and R- When any one of the R-cycle in which the expansion device 21 and the R-evaporator 22 sequentially flow is completed, the compressor 1 with the valve device 3 closed for a predetermined time (Δt). Including a step of operating.
[0073]
Here, it is preferable to include a step of rotating any one of the F-fan 12a and the R-fan 22a together when the valve device 3 is closed and the compressor 1 is operated. Moreover, it is preferable to include the step of rotating the condenser fan 2a together when the valve device 3 is closed and the compressor 1 is operated.
[0074]
Since the specific operation of the modified embodiment of the second embodiment of the present invention formed by such a method is the same as that of the second embodiment, a description thereof will be omitted. However, in a modified embodiment of the second embodiment of the present invention, the valve device 3 is closed and the compressor 1 is operated even after any one of the F-cycle and the R-cycle is completed. . Further, when the compressor 1 is restarted after being stopped, the liquid-phase refrigerant does not flow into the compressor, so that the reliability of the compressor is ensured.
[0075]
The second embodiment of the present invention formed by the above method and its modified embodiments have the following advantages.
First, after any one cycle of the refrigeration system is completed, the refrigerant remaining in the evaporator of the cycle is recovered in the compressor and condenser, resulting in a shortage of refrigerant when performing another cycle. Absent.
[0076]
Second, since the evaporator fan is rotated even after one cycle is completed, cold air can be continuously supplied to the food storage room, thermal efficiency can be improved, and refrigerant recovery can be accelerated.
[0077]
Thirdly, since it is possible to prevent the refrigerant from remaining in the evaporator after one cycle is completed, the liquid-phase refrigerant does not flow in when the compressor is restarted, and compression loss due to liquid compression can be prevented. Therefore, the reliability of the compressor is ensured.
Fourth, a relatively small amount of refrigerant can be used even in the same capacity refrigeration system.
[0078]
Third embodiment
In the third embodiment of the present invention, from the F-cycle in which the refrigerant that has passed through the condenser 2 sequentially flows through the F-expansion device 11 and the F-evaporator 12, the refrigerant is R- When the expansion device 21 and the R-evaporator 22 are switched to the R-cycle that sequentially flows, the compressor 1 is operated with the valve device 3 closed for a predetermined time (Δt); This includes a step of intermittently operating the F-fan 12a and the R-fan 22a even after the operation is stopped.
[0079]
In the third embodiment of the present invention formed by such a method, the method for recovering the refrigerant remaining in the evaporator is the same as that in the second embodiment, so that the description thereof is omitted and the compressor is stopped. Subsequently, the step of intermittently operating the F-fan 12a and the R-fan 22a will be described with reference to FIGS.
[0080]
FIG. 8 shows a refrigeration cycle with a typical form of a refrigeration system with two evaporators, in which the F-cycle is completed and then continuously run into the R-cycle, after which The compressor 1 is stopped for a certain period of time so that the refrigeration cycle is not performed. However, it should be understood that the present invention is not limited to the refrigeration cycle shown in FIG. 8, and the refrigeration cycle of FIG. 8 is merely an example.
[0081]
First, while the compressor 1 is started and the F-cycle is performed, the F-fan 12a continuously rotates to cool the first chamber 10 while vaporizing the refrigerant flowing into the F-evaporator 12.
[0082]
Further, while the R-cycle is performed after switching to the R-cycle, the R-fan 22a continuously rotates and cools the second chamber 20 while vaporizing the refrigerant flowing into the R-evaporator 22.
[0083]
When the execution of the R-cycle is completed, the compressor 1 stops. When the compressor is thus stopped, the F-fan 12a and the R-fan 22a are intermittently rotated at a constant time period, and the cool air remaining in each evaporator is not changed while each cycle is performed. Exhaust into the room to cool each room.
[0084]
By operating in this manner, each chamber can be cooled using the cold air remaining in each evaporator even when the refrigeration system is stopped. That is, when the compressor 1 is stopped, the refrigerant does not flow into the evaporators 12 and 22, but the temperature around the evaporators 12 and 22 is lower than the temperature of each chamber. Since the cooling performance can be improved and the temperature deviation in each room can be reduced, the reliability of food storage can be improved.
[0085]
Further, by rotating the fan while the refrigerant is not supplied to each evaporator and completely evaporating the refrigerant remaining in the evaporator, the liquid-phase refrigerant flows into the compressor 1 when the compressor 1 is restarted. Can be prevented.
[0086]
In the third embodiment, when any one of the F-cycle and the R-cycle is performed, the step of intermittently operating the fan of the evaporator belonging to the other stopped refrigeration cycle is further performed. It is preferable to include. That is, as shown in FIG. 8, the R-fan 22a is intermittently rotated not only while the compressor 1 is stopped but also during the F-cycle. Similarly, the F-fan 12a is intermittently rotated not only when the compressor 1 is stopped but also when the R-cycle is executed. When operated in this way, the cooling performance is further improved.
[0087]
In the method of the third embodiment, preferably, when either the F-cycle or the R-cycle is completed, the fan of the evaporator belonging to the refrigeration cycle is extended for a predetermined time. Is further included. That is, as shown in FIG. 8, after the F-cycle is completed, the F-fan 12a is extended and operated for a predetermined time (t1), and cold air is discharged into the first chamber 10 to complete the R-cycle. Thereafter, cold air is discharged to the first chamber 10 while the R-fan 22a is operated for a predetermined time (t2). This is because immediately after each cycle is performed, almost the same level of cold air is present around the evaporator as when the cycle is performed, so that the cool air is discharged into each chamber to improve the cooling performance.
[0088]
Further, in the third embodiment of the present invention, after either refrigeration cycle of the F-cycle or the R-cycle is performed and completed, the evaporator fan belonging to the refrigeration cycle is extended for a predetermined time. Preferably, the method includes a step of intermittent operation. That is, as shown in FIG. 8, after the F-cycle is completed, the F-fan 12a is operated intermittently after being extended for a predetermined time, and after the R-cycle is completed, the R-fan 22a is operated for a predetermined time (t2). It will be operated intermittently after extended operation.
[0089]
As described above, it is preferable that the intermittent time ratio between the F-fan 12a and the R-fan 22a operated intermittently, that is, the ratio between the operated time and the stopped time is 4: 6. That is, when 10 minutes are intermittently operated in one cycle, each fan preferably rotates for 4 minutes and is stopped for 6 minutes. However, such ratios can vary depending on the capacity of the refrigeration system and the product design purpose. As described above, the reason why the F-fan 12a and the R-fan 22a are intermittently operated is because the life and power consumption of the motor that rotates each fan are taken into consideration.
[0090]
In the third embodiment of the present invention, the method of intermittently operating each fan when the compressor is stopped is configured independently of the operation control method disclosed in the second embodiment and applied to the refrigeration system. Can be done.
A fourth embodiment according to the present invention will be described with reference to FIGS.
[0091]
Fourth embodiment
Referring to FIG. 9, in the fourth embodiment of the present invention, even after the operation of the compressor 1 of the refrigeration system that selectively performs the F-cycle or the R-cycle is stopped, the F-fan 12a and the R-fan 22a. Each of which is operated intermittently.
[0092]
Further, in the fourth embodiment of the present invention, when any one of the F-cycle and the R-cycle is performed, the fan of the evaporator belonging to the other one refrigeration cycle is intermittently operated. Preferably, the method further includes an operation step.
[0093]
Further, according to the fourth embodiment of the present invention, when one of the F-cycle and the R-cycle is completed and completed, the evaporator fan belonging to the refrigeration cycle is set for a predetermined time (t3, t4). It is preferable that the method further includes an extended operation.
[0094]
In the fourth embodiment of the present invention, when any one of the F-cycle and the R-cycle is completed and completed, the fan of the evaporator belonging to the refrigeration cycle is extended for a predetermined time. Thereafter, it is preferable to include a step of intermittent operation. At this time, the intermittent time ratio at which the F-fan and R-fan are operated and stopped is preferably 4: 6.
[0095]
Since the detailed content of the fourth embodiment of the present invention which has been made by the above method has already been disclosed in the third embodiment, the description thereof will be omitted.
As shown in FIG. 9, the fourth embodiment can be applied to all refrigeration systems that selectively operate the R-cycle and the F-cycle regardless of the cycle operation.
[0096]
The cooling system operation control method according to the fourth embodiment of the present invention has the following advantages.
First, even after the compressor is stopped, the cooling air remaining in each evaporator is supplied to each chamber by rotating each fan intermittently. Storage reliability is improved.
[0097]
Second, since all the cold air remaining in each evaporator can be used, the cooling efficiency is improved and the temperature rise rate of each chamber can be reduced. Therefore, the operation time of the compressor is substantially shortened.
[0098]
Third, even after the refrigerant flow is stopped, each fan vaporizes the refrigerant remaining in each evaporator, so that when the compressor is restarted, liquid-phase refrigerant may flow into the compressor. This improves the reliability of the compressor.
[0099]
The preferred embodiment of the present invention has been described above, but the present invention is not limited to the above-described embodiment, and various modifications or changes can be made based on the technical idea of the present invention.
[0100]
【The invention's effect】
As described above, the operation control method for a refrigeration system including two evaporators according to the present invention has the following effects.
First, the temperature deviation of each chamber can be reduced and minimized, and the temperature of each chamber can be maintained more stably. Therefore, the reliability of food storage is further improved.
[0101]
Second, after any one cycle of the refrigeration system is completed, the refrigerant shortage phenomenon does not occur when another cycle is performed.
Third, the thermal efficiency of the refrigeration cycle is improved, and the compressor operating time is substantially shortened.
[0102]
Fourth, since the refrigerant can be prevented from remaining in the evaporator, the liquid phase refrigerant is not flowed in when the compressor is restarted, and pressure loss due to liquid compression can be prevented.
Fifth, a relatively small amount of refrigerant can be used even in the same capacity refrigeration system.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram of a refrigeration system including two evaporators.
FIG. 2 is a flowchart showing an operation control method of the refrigeration system according to the first embodiment of the present invention.
FIG. 3 is a table showing an opening ratio of a valve device according to temperature in each chamber in the operation control method of the refrigeration system according to the first embodiment of the present invention.
FIG. 4 is a flowchart showing an operation control method for a refrigeration system according to a modification of the first embodiment of the present invention.
FIG. 5 is a table showing the opening ratio of the valve device according to the temperature region of each chamber in the operation control method of the refrigeration system according to the modified embodiment of the first embodiment of the present invention.
FIG. 6 is a diagram showing an operation control method of a refrigeration system according to a second embodiment of the present invention.
FIG. 7 is a diagram showing an operation control method of a refrigeration system according to a modification of the second embodiment of the present invention.
FIG. 8 is a diagram showing an operation control method of a refrigeration system according to a third embodiment of the present invention.
FIG. 9 is a diagram showing an operation control method of a refrigeration system according to a fourth embodiment of the present invention.
[Explanation of symbols]
1 ... Compressor
2 ... Condenser
3 ... Valve device
10 ... 1st room
11 ... F-expansion device
12 ... F-evaporator
13 ... Temperature sensor
20 ... Second room
21 ... R-expansion device
22 ... R-evaporator
23 ... Temperature sensor

Claims (35)

（ｃ）各室の温度を測定する段階と、
（ｄ）測定された前記各室の温度を比較する段階と、
（ｅ）前記各室の温度比較結果に基づき前記各室の蒸発器に流入する冷媒量を調節する段階と、を含み、且つ
圧縮機が停止して、前記蒸発器への冷媒流入が中断された後、ファンを所定時間の間延長運転して前記蒸発器に残留する冷媒を気化させる段階を含む２つの蒸発器を備えた冷凍システムの運転制御方法。(C) measuring the temperature of each chamber;
(D) comparing the measured temperature of each chamber;
(E) adjusting the amount of refrigerant flowing into the evaporator of each chamber based on the temperature comparison result of each chamber, and stopping the compressor and interrupting the refrigerant flow into the evaporator And a method of controlling the operation of the refrigeration system including two evaporators, including the step of operating the fan for a predetermined time to evaporate the refrigerant remaining in the evaporator. 前記段階（ｃ）は前記各室に取り付けられている温度センサーによって行われる請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The operation control method of the refrigeration system having two evaporators according to claim 1, wherein the step (c) is performed by a temperature sensor attached to each chamber. 段階（ｃ）の前に行われ、（ａ）前記各室毎に複数の基準温度を設定する段階を更に含む請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The method for controlling operation of a refrigeration system having two evaporators according to claim 1, further comprising the step of (a) setting a plurality of reference temperatures for each of the chambers before the step (c). 前記基準温度は上限温度と下限温度を含む請求項３に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The operation control method for a refrigeration system including two evaporators according to claim 3 , wherein the reference temperature includes an upper limit temperature and a lower limit temperature. 前記各室の温度が全て前記上限温度以上の場合、前記バルブ装置の開放比率が５０％：５０％である請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。2. The operation control method for a refrigeration system having two evaporators according to claim 1, wherein when all the chamber temperatures are equal to or higher than the upper limit temperature, the opening ratio of the valve device is 50%: 50%. 前記各室の温度が下限温度以上の温度領域で同一である場合、前記バルブ装置の開放比率が５０％：５０％である請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。2. The operation control of the refrigeration system having two evaporators according to claim 1, wherein the opening ratio of the valve device is 50%: 50% when the temperature of each chamber is the same in a temperature range equal to or higher than the lower limit temperature. Method. 下限温度以上の温度領域で前記各室の何れか１室の温度が他の室より高い場合、前記バルブ装置は相対的に高い温度を有する室の蒸発器側が更に多く開放されるように制御される請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。When the temperature of any one of the chambers is higher than the other chambers in the temperature range above the lower limit temperature, the valve device is controlled so that the evaporator side of the chamber having a relatively high temperature is opened more. An operation control method for a refrigeration system comprising two evaporators according to claim 1 . 何れか１室の温度だけが下限値の温度未満の場合、前記バルブ装置が高い温度を有する室の蒸発器側に冷媒の全量を流入させるように制御する請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。If only the temperature of any one chamber is lower than the temperature lower limit value, two evaporators according to claim 1, wherein the valve device is controlled so as to flow into the whole amount of the refrigerant to the evaporator side of the chamber having a higher temperature Operation control method of refrigeration system provided with. 前記各室の温度が下限値の温度未満の場合、圧縮機の運転が停止される請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The operation control method for a refrigeration system having two evaporators according to claim 1, wherein the operation of the compressor is stopped when the temperature of each chamber is lower than the lower limit temperature. 前記段階（ｃ）前に行われ、（ｂ）前記各室毎に複数の温度領域を設定する段階を更に含む請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The operation control method for a refrigeration system having two evaporators according to claim 1, further comprising the step of (b) setting a plurality of temperature regions for each of the chambers before the step (c). 前記温度領域が、上限温度以上の温度領域（Ａｎ温度領域）、上限温度未満で設定値温度以上の温度領域（Ｂｎ温度領域）、設定値温度未満で下限温度以上の温度領域（Ｃｎ温度領域）、下限温度未満の温度領域（Ｄｎ温度領域）を含む請求項１０に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The temperature region is a temperature region above the upper limit temperature (An temperature region), a temperature region below the upper limit temperature and above the set temperature (Bn temperature region), and a temperature region below the set temperature and above the minimum temperature (Cn temperature region) The operation control method of the refrigerating system provided with two evaporators of Claim 10 including the temperature range (Dn temperature range) below a minimum temperature. 前記段階（ｄ）が測定された前記各室の温度を前記温度領域と比較する方法で行われる請求項１１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The operation control method for a refrigeration system having two evaporators according to claim 11, wherein the temperature of each chamber measured in step (d) is compared with the temperature region. 前記各室の温度領域が互いに同一である場合、前記バルブ装置が同一比率で開放される請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。If the temperature region of the chambers are identical to each other, the operation control method of a refrigeration system with two evaporators according to claim 1, wherein the valve device is opened in the same proportions. 前記バルブ装置の開放比率が５０％：５０％である請求項１３に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The method for controlling operation of a refrigeration system having two evaporators according to claim 13, wherein an opening ratio of the valve device is 50%: 50%. 前記各室の温度領域が全てＤｎ温度領域に属する場合、圧縮機の運転が停止される請求項１３に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The operation control method for a refrigeration system having two evaporators according to claim 13, wherein the operation of the compressor is stopped when all the temperature regions of the chambers belong to the Dn temperature region. 前記各室の何れか１室の温度領域だけがＤｎ温度領域に属する場合、前記バルブ装置の開放比率が０％：１００％（Ｄｎ温度領域に属する室側：他の温度領域に属する室側）である請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。When only one temperature region of each of the chambers belongs to the Dn temperature region, the opening ratio of the valve device is 0%: 100% (the chamber side belonging to the Dn temperature region: the chamber side belonging to another temperature region). The operation control method for a refrigeration system comprising two evaporators according to claim 1 . 前記各室の何れか１室の温度領域がＡｎ温度領域に属し、他の１室がＣｎ温度領域に属する場合、前記バルブ装置の開放比率が１００％：０％（Ａｎ温度領域に属する室側：Ｃｎ温度領域に属する室側）である請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。When the temperature region of any one of the chambers belongs to the An temperature region and the other chamber belongs to the Cn temperature region, the opening ratio of the valve device is 100%: 0% (the chamber side belonging to the An temperature region) The method for controlling the operation of a refrigeration system comprising two evaporators according to claim 1, wherein : a room side belonging to a Cn temperature region). 前記各室の何れか１室の温度領域がＢｎ温度領域に属し、他の１室がＡｎ温度領域またはＣｎ温度領域に属する場合、前記バルブ装置が相対的に高い温度の温度領域に属する室側が更に多く開放されるように制御される請求項１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。When the temperature range of any one of the chambers belongs to the Bn temperature range and the other one belongs to the An temperature range or the Cn temperature range, the chamber side to which the valve device belongs to a relatively high temperature range is The operation control method for a refrigeration system comprising two evaporators according to claim 1, wherein the operation is controlled so as to be opened more. 前記バルブ装置の開放比率が８０％：２０％（高い温度の温度領域に属する室側：低い温度の温度領域に属する室側）である請求項９に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The refrigeration system having two evaporators according to claim 9, wherein the opening ratio of the valve device is 80%: 20% (chamber side belonging to a high temperature range: chamber side belonging to a low temperature range). Operation control method. （ｇ）凝縮器を経た冷媒がＦ−膨張装置とＦ−蒸発器とを順次に流動するＦ−サイクルと、Ｒ−膨張装置とＲ−蒸発器とを順次に流動するＲ−サイクルとの何れか一方のサイクルが完了した時、所定時間（Δｔ）の間、前記バルブ装置を閉鎖した状態で前記圧縮機を運転する段階と、
前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間延長運転する段階を含む２つの蒸発器を備えた冷凍システムの運転制御方法。(G) Any of the F-cycle in which the refrigerant that has passed through the condenser sequentially flows in the F-expansion device and the F-evaporator, and the R-cycle in which the refrigerant sequentially flows in the R-expansion device and the R-evaporator. When either cycle is completed, the compressor is operated with the valve device closed for a predetermined time (Δt);
A refrigeration system comprising two evaporators including a step of extending a fan of an evaporator belonging to the refrigeration cycle for a predetermined time when the refrigeration cycle of either the F-cycle or the R-cycle is completed. Operation control method. 前記段階（ｇ）を行う時、当該ファンを回転させる段階を含む請求項２０に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The method for controlling operation of a refrigeration system having two evaporators according to claim 20, comprising the step of rotating the fan when performing step (g). 前記段階（ｇ）を行う時、凝縮器ファンを共に回転させる段階を含む請求項２０に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。21. The method of controlling operation of a refrigeration system having two evaporators according to claim 20, including the step of rotating a condenser fan together when performing step (g). 前記圧縮機の運転が停止した後にもＦ−ファンとＲ−ファンを各々断続的に運転する段階を含む請求項２０に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。21. The operation control method for a refrigeration system having two evaporators according to claim 20, comprising the step of intermittently operating the F-fan and the R-fan even after the operation of the compressor is stopped. 前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが行われる時、停止した他の１つの冷凍サイクルに属する蒸発器のファンを断続的に運転する段階を含む請求項２３に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。24. The method according to claim 23, further comprising intermittently operating an evaporator fan belonging to another stopped refrigeration cycle when any one of the F-cycle and the R-cycle is performed. An operation control method of a refrigeration system including two evaporators. 前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間、延長運転した後断続的に運転する段階を含む請求項２３に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The method includes the step of intermittently operating after extending a fan of an evaporator belonging to the refrigeration cycle for a predetermined time when the refrigeration cycle of any one of the F-cycle and the R-cycle is completed. 24. A method for controlling the operation of a refrigeration system comprising the two evaporators according to 23 . 前記Ｆ−ファン及びＲ−ファンが運転し停止される断続時間比は４：６である請求項２３に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The method of controlling operation of a refrigeration system having two evaporators according to claim 23, wherein an intermittent time ratio at which the F-fan and R-fan are operated and stopped is 4: 6. 前記Ｆ−ファン及びＲ−ファンが運転し停止される断続時間比は４：６である請求項２４に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。The method for controlling operation of a refrigeration system having two evaporators according to claim 24, wherein an intermittent time ratio at which the F-fan and R-fan are operated and stopped is 4: 6. 前記Ｆ−ファン及びＲ−ファンが運転し停止される断続時間比は４：６である請求項２５に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。26. The operation control method for a refrigeration system having two evaporators according to claim 25, wherein an intermittent time ratio at which the F-fan and the R-fan are operated and stopped is 4: 6. Ｆ−サイクルまたはＲ−サイクルを選択的に行う冷凍システムの圧縮機の運転が停止した後にもＦ−ファンとＲ−ファンを各々断続的に運転する段階と、
前記Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われると時、停止された他の１つの冷凍サイクルに属する蒸発器のファンを断続的に運転する段階と、を含む２つの蒸発器を備えた冷凍システムの運転制御方法。Intermittently operating the F-fan and the R-fan, respectively, after the operation of the compressor of the refrigeration system that selectively performs the F-cycle or the R-cycle,
When the refrigeration cycle of any one of the F-cycle and the R-cycle is performed, intermittently operating an evaporator fan belonging to another stopped refrigeration cycle. Control method for a refrigeration system including a container. 前記Ｆ−サイクルとＲ−サイクルの何れか一方の冷凍サイクルが行われると時、停止された他の１つの冷凍サイクルに属する蒸発器のファンを断続的に運転する段階を含む請求項２９に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。30. The method of claim 29, comprising intermittently operating an evaporator fan belonging to another stopped refrigeration cycle when one of the F-cycle and R-cycle is performed. The operation control method of the refrigerating system provided with two evaporators. 前記Ｆ−サイクルと前記Ｒ−サイクルの何れか一方の冷凍サイクルが完了した後、当該冷凍サイクルに属する蒸発器のファンを所定時間の間、延長運転した後、断続的に運転する段階を含む請求項２９に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。After the refrigeration cycle of any one of the F-cycle and the R-cycle is completed, the fan of the evaporator belonging to the refrigeration cycle is extended for a predetermined time and then intermittently operated. Item 30. A method for controlling the operation of a refrigeration system comprising the two evaporators according to Item 29 . 前記Ｆ−ファン及びＲ−ファンが運転し停止される断続時間比が４：６である請求項２９に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。30. The operation control method for a refrigeration system having two evaporators according to claim 29, wherein an intermittent time ratio at which the F-fan and the R-fan are operated and stopped is 4: 6. 前記Ｆ−ファン及びＲ−ファンが運転し停止される断続時間比が４：６である請求項３０に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。31. The operation control method for a refrigeration system having two evaporators according to claim 30, wherein an intermittent time ratio at which the F-fan and the R-fan are operated and stopped is 4: 6. 前記Ｆ−ファン及びＲ−ファンが運転し停止される断続時間比が４：６である請求項３１に記載の２つの蒸発器を備えた冷凍システムの運転制御方法。32. The operation control method for a refrigeration system having two evaporators according to claim 31, wherein an intermittent time ratio at which the F-fan and the R-fan are operated and stopped is 4: 6. 凝縮器を経た冷媒が、Ｆ−膨張装置とＦ−蒸発器を順次に流動するＦ−サイクルと、Ｒ−膨張装置とＲ−蒸発器を順次に流動するＲ−サイクルの何れか一方のサイクルが完了した時、当該冷凍サイクルに属する蒸発器のファンを所定時間の間延長運転する段階を含む２つの蒸発器を備えた冷凍システムの運転制御方法。  Either one of the F-cycle in which the refrigerant that has passed through the condenser sequentially flows through the F-expansion device and the F-evaporator, and the R-cycle in which the refrigerant flows through the R-expansion device and the R-evaporator in sequence. A method for controlling the operation of a refrigeration system comprising two evaporators, comprising the step of, when completed, extending a fan of an evaporator belonging to the refrigeration cycle for a predetermined time.
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